Abstract:
A temperature sensitive element within a timepiece which includes a casing, movement, mainspring and a bi-directional rotation to unidirectional rotation converting mechanism for winding the mainspring where the temperature sensitive element tends to angularly deflect with change in temperature and such tendency produces energy to wind the mainspring. More specifically, the invention in one form thereof utilizes a temperature sensitive bimetallic coil, which is restrained from radial deflection and the free end moves to rotate the shaft in the self-winding mechanism and effects self-winding of the timepiece. The free end of the coil will move with change in temperature. The coil is anchored at its inner end and the other end thereof, upon movement, will drive a driver member in the form of an orbit gear. In this embodiment, the orbit gear will drive a plurality of planet gears, which drive a sun gear mounted to a shaft. The shaft of the sun gear then produces rotation of a cam which drives the bi-directional to unidirectional conversion mechanism. In another embodiment of the invention, the coil will rotate a driver member, which drives a shaft of the winding mechanism. These arrangements will provide perpetual self-winding of the watch unless the watch is stored in an environment where there is extremely low tolerance temperature control.

Description:
RELATED APPLICATIONS 
     This application is a continuation-in-part of application Ser. No. 09/812,620, filed Mar. 20, 2001. 
    
    
     FIELD OF THE INVENTION 
     This invention relates to timepieces and more particularly relates to self-winding timepieces, particularly wristwatches, which are wound in response to change in temperature and may have infinite autonomy. 
     BACKGROUND OF THE INVENTION 
     Almost all, if not all, wrist watches, other than battery powered or other electrically powered watches receive energy for winding the main spring through a main spring barrel arbor from a winding weight or rotor in the watch which rotates in either direction due to movement of the watch wearers arm and wrist. Such movement of the wearer&#39;s arm and wrist produces acceleration of the winding weight or rotor in either direction about a pivotal axis and resultant bi-directional rotation of the shaft upon which it is mounted. The bi-directional rotation of this shaft is converted to unidirectional rotation of another shaft, which in turn winds the mainspring. 
     A simple and common mechanism for conversion of bi-directional rotation of one shaft in a watch to unidirectional rotation of another shaft is known as a Pellaton mechanism. A Pellaton mechanism comprises a lever, which is bifurcated at one end, and the bifurcated arms are acted upon by a rotating cam or eccentric pin to produce an eccentric oscillating motion. Spring loaded pawls on the lever engage a ratchet wheel at spaced apart locations on the ratchet wheel and unidirectionally rotate the ratchet with the rocking or oscillating motion of the lever induced by the winding weight or rotor. Examples of Pellaton mechanisms are shown in U.S. Pat. Nos. 2,696,073 and 4,174,607, as well as other references. Another mechanism for such conversion is known as a wig-wag mechanism. In this mechanism, a pinion on the bi-directionally rotatable shaft drives a linearly displaceable wig-wag gear, which will engage one of two other gears dependent on the direction of rotation of the wig-wag gear. The gear arrangement is such that the mainspring barrel will always be driven in a direction to wind the mainspring. 
     Self-winding wrist watches generally have an autonomy or power reserve of about one and one-half to three days. The terms “autonomy” and “power reserve” refer to the time a self winding wrist watch will continue to run if fully wound, but not worn. 
     Attempts to lengthen power reserve time have generally focused on the storage capacity of the mainspring. A well known watch maker, Patek Philippe, has recently announced a new limited quantity wrist watch, which will run for seven days. This watch requires two mainsprings. The mechanism of U.S. Pat. No. 5,119,348 provides room for an enlarged mainspring within and coaxial with the winding weight and is stated to store energy sufficient to keep the movement running for up to eight days. The 2000, 45 th  edition of  International Wrist Watch  magazine has reported on a wrist watch with autonomy of one thousand hours. This watch contains and extremely large mainspring and due to large power losses the time keeping is not accurate at the present time 
     The present invention departs from prior art designs of self winding watches and focusing on the mainspring by providing a new, but one of natures oldest, energy source which gives the watch essentially infinite autonomy, so long as the watch is not left in an environment of small tolerance temperature control. 
     An object of this invention is to provide a new and improved self-winding timepiece having essentially infinite autonomy. 
     Another object of this invention is to provide a watch having a new energy source for self-winding with an energy transmission system which provides essentially infinite autonomy. 
     A further object of this invention is to provide a watch having a new and improved energy source, which is responsive to change in temperature to effect self-winding. 
     A further object of this invention is to provide a watch with an element, which has movement in response to change in temperature and mechanisms for converting such movement to rotational movement for self winding of the watch. 
     SUMMARY OF THE INVENTION 
     Briefly stated, the invention comprises the provision of a temperature sensitive element within a watch which includes a casing, watch movement, mainspring and a bi-directional rotation to unidirectional rotation mechanism where the temperature sensitive element has angular motions with changes in temperature and such movement produces energy to wind the mainspring. More specifically, the invention in one form thereof utilizes a temperature sensitive bimetallic coil, which upon expansion and contraction rotates a driver member, which produces rotation of a shaft in the winding mechanism and effects self winding of the watch. The free or outer end of the coil will angularly deflect with change in temperature. The coil is anchored at the inner end thereof in a coil carrier or a stationary part of the watch and the outer end thereof, upon movement, will drive a driver member with an internal gear. The driver member, in one embodiment of the invention, will in turn drive a plurality of planet gears, which drive a sun gear, mounted to a shaft. The shaft of the sun gear then produces rotation of a cam or eccentric pin which drives the bi-directional to unidirectional conversion mechanism. This arrangement will provide substantially infinite self winding of the watch in a normal environment, even if the watch is not worn for a long period of time, so long as the watch is not stored or otherwise left in a closely temperature controlled environment. In another embodiment of the invention the driver member directly drives I the winding mechanism. 
     The invention is particularly pointed out and distinctly claimed in the concluding portion of this specification. The invention, however, together with further objects and advantages thereof may be best appreciated by reference to the following detailed description taken in conjunction with the drawings. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a diagram illustrating in functional block form the various operative portions of a wrist watch in which the invention is embodied; 
     FIG. 2 is a view of a wristwatch with the back cover partially cut away and arranged to receive structure embodying the invention; 
     FIG.  2 ( a ) is a view, partially in section, showing the manner in which supports are mounted in the watch; 
     FIG. 3 is a view a wrist watch with the back removed and structure embodying the invention within the watch 
     FIGS.  4 ( a )- 4 ( d ) are details of a carrier for a bimetallic coil which is received in the watch as shown in FIGS.  2  and  3 : 
     FIGS.  5 ( a )- 5 ( c ) are details of the connection of the free end of a bimetallic coil to an orbit gear shown in FIG.  3 : 
     FIG. 6 is a sectional view seen in the plane of lines  6 — 6  of FIG. 3; 
     FIG. 7 is a plan view of a bi-directional to unidirectional motion converting mechanism utilized in the invention. 
     FIG. 8 is a view similar to FIG. 3 illustrating a further embodiment of the invention; 
     FIG. 9 is a sectional view seen in the plane of lines  9 — 9  of FIG. 8; 
     FIG. 10 is a view of a watch with the back removed illustrating another embodiment of the invention; 
     FIG. 11 is an enlarged sectional view seen in the plane of lines  11 — 11  of FIG. 10; and 
     FIG. 12 is a plan view of another bi-directional motion converting mechanism. 
    
    
     DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS 
     FIG. 1 exemplifies in functional block form the components of a watch in which the invention is embodied. A watch  10  comprises a casing  11 , exemplified in broken line. Within the casing  11  is an energy source  12  for operating the watch, an energy transmission system  13 , which transmits energy to a bi-directional to unidirectional winding mechanism  14 , which may be a Pellaton type or wig-wag mechanism. The unidirectional winding mechanism winds the mainspring, which powers the movement of the watch, both represented by the block identified by the reference numeral  15 . Finally, there is the watch face with hands  16  driven by the mainspring through the movement. The functions represented by the reference numerals  14 ,  15  and  16  are well known in the art and are constructed with varying degrees of quality and complexity which account for the widely varying price ranges of watches. 
     The present inventions reside in the energy source  12 , the energy transmission system  13  and a modified version of winding mechanism represented by the reference numeral  14 . Only the structure and function of these portions of a timepiece embodying the invention are described in detail, in as much as the various components of a mechanical timepiece are well known. 
     Reference is now made to FIGS.  2  and  2 ( a ) which exemplify a watch casing  11  with the back cover  21  partially cut away. The back cover  21  may have a friction fit with casing  11  by means of a depending annular flange received in an annular groove  22 , or may be screwed to casing  11 FIG. 2 exemplifies a watch casing before inclusion of the present invention and FIG.  2 ( a ) illustrates a mounting detail. 
     Casing  11  includes lugs  22  for mounting of a wristband. A skeletal support frame  24  is supported in casing  11  as exemplified in FIG. 2 a . A plurality of screws  25  extend through radial passages  26  in casing  11  and are received in threaded apertures  27  in frame  24 . The entrance to passages  26  is enlarged to provide recesses for the heads  28  of mounting screws  25 . An elastomeric O-ring  29  is Included beneath the heads of screws  25  to provide shock mounting of frame  21 . Casing  11  provides an annular surface or seat  30  for mounting of a bimetallic coil carrier as hereinafter described. The coil carrier is secured in casing  11  on seat  30  by a plurality of screws received in equiangular spaced threaded apertures  30   a . Also shown is an opening  31  for receiving a winding and setting stem (not shown in FIG.  2 ). 
     A bridge member  32  for a supporting a winding mechanism, (on the side opposite that shown in FIG. 2) is secured to support frame  24  by a plurality of screws  33 ,  34  and  35 . Positioned in bridge member  32  is a ball bearing  36  receiving a shaft  37 . As hereinafter described, shaft  37  drives a winding mechanism. 
     Reference is now made to FIG. 3 taken in conjunction with FIG.  2 . FIG. 3 illustrates casing  11  with back cover  21  completely removed. A bimetal coil carrier  41 , hereinafter more fully illustrated, is seated on and secured to annular seat  29 , FIG.  2 . Coil carrier  41  has an inner upstanding annular flange  42  to, which is secured the inner end of a bimetallic coil  43 . The outer end of coil  43  is connected to a driver member drivingly rotated by coil  43 , as hereinafter pointed out. A mounting plate  44  is secured to bridge member  32  by screws  34  and  35  (FIG. 2) extending through apertures in plate  44 . Coil  43  will tend to angularly deflect with change in temperature, but since the inner end is fixed and the outer end is connected to a peripheral flange of a rototatable driver member and restrained from outward radial movement thereby, the outer end will have peripheral movement in both directions dependent upon the direction of change in temperature. While not readily apparent from the drawings, there will be a small spacing between the turns of coil  43  to permit such movement. 
     Three equiangular spaced tabs  47 ,  48 , and  49  extend from mounting plate  44  over bimetallic coil  43  and serve to retain coil  43  in coil carrier  41 . A sun gear  51  is keyed (key not shown) to shaft  37 . Three planet gears  52 ,  53  and  54  are equi-angularly, rotatably mounted in mounting plate  44  and mesh with and drive sun gear  51  in either direction of rotation. Each of planet gears  52 ,  53  and  54  have five posts which are received in recesses  56  between teeth  57  of a driver member in the form of an orbit gear  58 . Orbit gear  58  is driven by the outer end of coil  43 . Orbit gear  58  has a peripheral flange  58   a  (FIG. 5 a ). The posts, hereinafter discussed in more detail in conjunction with FIG. 6, have caps  55   a  thereon, which will overlie the edges of teeth  57  when the posts are in a recess  56 . This arrangement retains orbit gear with respect to bimetallic coil  43  and coil carrier  41  and permits orbital as well as rotational motion of orbit gear  58 . The teeth  57  of orbit gear have substantially right angle corners defining the entrance into recesses  56  and the recesses have substantially semi-circular bottoms for receiving annular posts, as shown in FIG.  6 . 
     Reference is now made to FIGS.  4 ( a )- 4 ( d ), which show coil carrier  41  and coil  43  in more detail. FIG.  4 ( a ) illustrates casing  11  with seat  30  for coil carrier  41  and screw apertures  30   a  for securing coil carrier  41  thereto. FIG.  4 ( b ) is a plan view of coil carrier  41  with a portion of coil  43  thereon and screw apertures  41   a  for securing coil carrier  41  to seat  30 . FIG.  41 ( c ), which is a section through coil carrier  41  and coil  43  also, illustrates an outer annular flange  42   a  on coil carrier  41 . In practice, the outer diameter and free end of coil  43  will extend to outer flange  42   a . The inner end  43   a  of coil  43  is anchored or secured to flange  42  at three points  57 ,  58  and  59  as shown in FIG.  4 ( c ). An enlarged detail of this anchoring is shown in FIG.  4 ( d ). The inner end  43   a  of coil  43  is secured to flange  42  by screws  61 . 
     Reference is now made to FIGS.  5 ( a )- 5 ( c ) to exemplify the connection of the free end  43   b  of coil  43  to orbit gear  58 . FIG.  5 ( a ) is a perspective view of the free end of coil  43  connected to orbit gear  58 . The upper edge of end  43   b  of coil  43  has three notches  43 ( c ) defined therein which receive screws therethrough to anchor end  43   b  to the peripheral flange of orbit gear  58  as shown in FIG.  5 ( b ). 
     As hereinafter pointed out in more detail, the coil  43  has an angular deflection of twelve degrees for every Fahrenheit degree change in temperature. This angular deflection is transferred to the orbit gear, which will orbit and rotate in either direction dependent on the direction of change in temperature. Rotation of the orbit gear is imparted to the planet gears, which rotate the sun gear and shaft  37  in either direction dependent on the direction of change in temperature. 
     Reference is now made to FIG. 6 which is a sectional view in the plane of lines  6 — 6  of FIG.  3 . Posts  55  are provided by the unthreaded shanks of screws. Caps  55   a  overlying the edges of teeth  57  are provided by the screw heads and the posts are screwed in the rims of the planet gears as exemplified by planet gear  52  in FIG. 6. A post  55  is shown in a recess of  56  of orbit gear  58 . The caps  55   a  are preferably twice the diameter of posts  55  and overlie the edges of adjacent teeth  57 . At least one post  55  of each of planet gears  52 ,  53 ,  54  is always in a recess  56 . As previously pointed out, the posts  55  with caps  55   a  overlying the edges of adjacent teeth  57  of orbit gear  58  serve to retain orbit gear  58  with respect to bimetallic coil  43  and coil carrier  41 . The angular deflection of the free end  43   b  of coil  43  with temperature change will impart orbital motion to gear  58  as well as rotational motion. 
     Reference is now made to FIG. 7, which illustrates bi-directional to unidirectional shaft rotation conversion mechanism in the form of a modified Pellaton mechanism. FIG. 7 is a view seen from the opposite side of bridge member  32  as seen in FIG. 2. A Pellaton type arrangement  63  includes a hub  63   a  with pawls  64  and  65  extending therefrom and engaging opposite sides of a ratchet wheel  66  on a shaft  67 . A pinion  68  is also on shaft  67 . Pinion  68  drives a gear  69  having the arbor  70  of the mainspring (not shown) therein. Rotation of gear  69  by pinion  68  will wind the mainspring. The hub  63   a  of Pellaton type lever  63  is rotatably mounted to a pin  63   b  which is eccentric to the axis of ball bearing  36 . A hub  36   a  is received within the inner race of ball bearing  36  to receive shaft  37  (FIG.  2 ). Eccentric pin  63   b  is mounted to the hub  36   a.    
     It will be seen the pawls  64  and  65  will drive ratchet wheel in the direction of arrow A with either direction of pin  63   b . Simplified, with clockwise rotation of pin  63   b  pawl  65  pulls the teeth of ratchet wheel  66  while pawl  65  slips, and when pin  63   b  rotates counter-clockwise, pawl  64  pushes ratchet wheel  66  in the direction of arrow A, while pawl  65  slips. Both of pawls  64  and  65  have flexibility and will ride over the teeth of ratchet wheel when not acting to rotate ratchet wheel in the direction of arrow A. 
     Shaft  37  is secured to hub  36   a . When sun gear  51  is driven the inner race of bearing  36  and hub  36   a  are driven. 
     Planetary gearing systems may have inherent problems of jamming and require a high quality manufacturing process. The load division between planet gears, the interference of the outer gear, with internal teeth, and the planetary gears and the hazard of jamming are inherent problems to be solved. In the present invention these problems are overcome by having the orbit gear provide a separate track for each planet gear, as hereinafter described. 
     Orbit gear  58 , in the embodiment shown, has thirty-six recesses  56  and teeth  57 . Planet gears  52 ,  53  and  54  each have five posts  55  engaged by orbit gear  58 . This ratio makes the planet gears pinions as driven by orbit gear  58 . This ratio also provides a separate “track” for each planet gear post. The term “track” refers to the fact that the posts of each orbit gear will enter every third recess  56  of orbit gear  58 , and only every third recess. This is further shown by each planet gear having posts at seventy-two angular degree intervals, and the orbit gear having a recess and tooth at ten angular degree-intervals. A post of each planet gear will enter each third recess  56 . The orbit gear will rotate thirty angular degrees to provide seventy-two angular rotation degrees of a planet gear. Thus, in the embodiment shown, the orbit gear provides a separate track of twelve recesses  56  and teeth  57  for the posts of each planet gear. It has been found that without the provision of a separate track for the posts of each planet gear that after a short period of operation, the posts will fail to mesh with the orbit gear recesses and binding of the planet gears will occur. 
     The number of recesses and teeth required for a selected number of planets and planet posts are selected as follows: 
     
       
         
           AB×C+D×E=Number of recesses in orbit gear 
         
       
     
     where 
     A=First planet gear calculated for given spacing. 
     B=Number of teeth (posts) on a planet gear to mesh with orbit gear. 
     C=Whole number of ratio of number of 360° rotations of a planet gear to one 3600° rotation of orbit gear. 
     D=Number of remaining planet gears. 
     E=Total number of planet gears. 
     The back of a watch embodying the invention is selected to be of a good heat conductive material, which will influence the temperature at the coil. Tests utilizing a thermometer strapped to a wrist, as a watch is, have shown the following temperature variations. 
     When the watch is on the arm for the day, it is subjected to high temperatures due to body heat (on the order of ninety-five degrees). Most watches are worn slightly loose. When the back of the watch is essentially flush on the arm the temperature is up, on the order of ninety degrees F. Due to a slight shift on the arm, the case acts as a heat sink and the temperature drops three to six degrees F. This occurs about every fifteen minutes at room temperatures of seventy-five to seventy eight degrees. In addition there are fluctuations in room temperature due to cycling of the heating or air conditioning thermostats. 
     The changes in temperature at the watch are more frequent and at a wider range when the watch is worn outside. It was found that the temperature at the watch was ninety degrees plus five degrees and minus ten degrees on a day when the outside ambient temperature was fifty degrees, all temperatures being Fahrenheit. 
     When the watch is removed at night and subjected only to ambient room temperature it will very quickly drop to ambient room temperature, usually about seventy degrees. During the night the temperature will cycle with fluctuation in room temperature as the thermostatically controlled heat cycles. When the wearer again puts on the watch in the morning, there will be an increase in temperature of the watch casing back up to the external body temperature of the wearer. Change in temperature in either direction will produce self-winding of a watch embodying the invention. 
     By way of example only, the specifications of a bimetallic coil used in the invention will be set forth. A coil used in the practice of the invention in a prototype watch was a strip of 36-10 thermostatic bimetal strip of 0.008″ thickness and 0.078″ wide. The length was forty-eight to fifty-two inches, the inside diameter was 0.850″ and the outside diameter 1.23″. This material was obtained from Hood &amp; Co., Inc. of Hamburg, Pa., through a wholesale distributor. This coil had a deflection of twelve angular degrees with a change in temperature of one degree F. 
     The movement of the free end of the coil in inches/degree temperature change is as follows: 
     
       
           d   o ×3.14/360°×12°/° F. 
       
     
     where 
     d o =outside diameter 
     pi=3.14 
     Thus, for a one degree F. temperature change the free end of the coil will move 0.1287 inches. Considering a change of temperature of four degrees F. every fifteen minutes over a fifteen-hour period, the free end of the coil will move 7.722 inches. This is more than sufficient to replace the power consumed by the watch movement from the mainspring. Even if the watch is not worn, the normal temperature cycling in a normal heated or air conditioned environment will provide infinite self-winding. If a watch embodying the invention should be left in an absolute temperature controlled environment, the watch would have autonomy of thirty-six hours. 
     The following analysis and calculations for a prototype wristwatch is set forth below with energy sometimes expressed in terms of circumferential movement of the mainspring and the bimetallic coil. 
     The gear ratios are: 
     
       
         
               
               
             
           
               
                   
               
             
             
               
                 Orbital gear to planet 
                 36:15 = 2.40:1 
               
               
                 gear 
               
               
                 Planet gear to sun gear 
                 80:22 = 3.64:1 
               
               
                 Orbit Gear to Sun Gear 
                 = 8.74:1 
               
               
                 Pellaton Mechanism 
                 1:10 360° of total rotation of shaft 37 causes 
               
               
                   
                 36° of unidirectional rotation of ratchet wheel 
               
               
                 Pinion 66 to winding 
                 10:42 
               
               
                   
               
             
          
         
       
     
     Thus one revolution of the winding wheel or gear  69  requires an equivalent of forty-two rotations of sun gear  51  or 
     
       
         360°×42 total degrees of rotation (clockwise and counter-clockwise) 
       
     
     The ratio of the two gear trains is 
     
       
         42/8.74=4.883 
       
     
     The mainspring of the watch had a barrel diameter of 0.372″. The energy release of the mainspring is 60°/hour. Thus 
     
       
         0.372×3.14/360°=0.003245″ for one angular degree of motion 
       
     
     The energy release of the mainspring per hour is 0.194676″/angular degree/hour or 4.672″ per day to drive the watch movement. 
     As previously set forth the movement of the free end  43   a  of bimetallic coil moves 0.1287″ with a one degree F. change in temperature. The free end of bimetallic coil  43  will move (plus and minus) 2.059 in an hour considering four, four-degree temperature changes every hour. 
     The ratio of movement of the bimetallic coil to the mainspring/hour is 
     
       
         2.059/0.1947=10.588 
       
     
     The loss in the gear ratios is 4.883. Therefore the ratio of energy storage in the mainspring of the watch to energy consumed by the movement of the watch which may be termed the power restoration ratio is 
     
       
         10.588/4.883=2.162 
       
     
     For unseen mechanical discrepancies surfacing in a system from wear and abuse, and assuming that only fifty percent (50%) of the foregoing power restoration is available, the power restoration ratio will still be greater than unity. The foregoing power restoration ratio was calculated using a fifteen-hour period. Following is a breakdown of a twenty-four hour cycling period. 
     1. Wearing of the watch is commenced at 7:00 AM in a seventy-degree environment. By 7:15 AM the temperature at coil will increase by twenty-five degrees (25° F.). 
     2. By 8:00 AM there will be three more temperature changes of four degrees (120° F.). 
     3. From 8:00 AM to 11:00 PM there will be sixty temperature changes of four degrees (240° F.). 
     4. Removing the watch at 11:00 PM, there will a twenty-five degree drop. 
     This totals three hundred and two (302) degrees of temperature change. The circumferential movement of the orbit gear  58  will total 
     
       
         302°×0.1287″/° F.=38.857″ 
       
     
     The energy release by the mainspring in twenty-four hours is 4.672″ times the gear ratio loss of 4.883 or 22.811. But considering the dormant hours of 11:15 PM to 7:00 AM at half of the day time rate of four degrees F. per hour, there will be a total of fifty-five degree F. changes (55° F.). This will produce an additional 7.080″ of movement of the bimetallic coil  58  and the power restoration period over this twenty-four hour period is still greater than two. 
     A further embodiment of the invention is shown in FIGS. 8 and 9. In FIG. 8 like reference numerals to those previously used in conjunction with the description in FIGS. 1-3 are used for similar parts. 
     FIG. 8 illustrates casing  11  with back cover  21  completely removed. Bimetallic coil  43  is not shown in FIG. 8 for simplicity of illustration. A mounting plate  44  is secured to bridge member  32  by screws  34  and  35  (FIG. 2) extending through apertures in plate  44  as shown in FIG.  3 . 
     The three planet gears  52 ,  53  and  54  are equi-angularly, rotatably mounted in mounting plate  44  and mesh with and drive sun gear  51  (FIG. 3) in either direction of rotation. The gears  52 ,  53 , and  54  are shown in different form in FIG. 8, as is orbiter  58 . Each of planet gears  52 ,  53  and  54  has another gear pinned thereto  52   a ,  53   a  and  54   a , respectively, which rotate therewith, as exemplified by pin or screws  80 . 
     A retaining finger  81  overlies and retains orbit gear  58  as hereafter described in conjunction with FIG.  9 . This arrangement retains orbit gear with respect to bimetallic coil  43  and coil carrier  41  and permits orbital as well as rotational motion of orbit gear  58 . 
     The operation of the embodiment of FIG. 8 is the same as that of FIG.  3 . The gears  52   a ,  53   a  and  54   a  have replaced the posts  55  of the embodiment of FIG.  3 . Instead of notches, the orbit gear has teeth  56   a  defined thereon which mesh with the teeth of gears  52   a ,  53   a  and  54   a . The gears  52   a ,  53   a  and  54   a  may be considered pinions but in view of the number of teeth thereon are referred to as gears. 
     The mounting of the gears also provides for adjustment of the depth of mesh of the teeth of gears  52   a ,  53   a  and  54   a  with the teeth of orbit gear  55 . Each pair of gears  52 ,  52   a ;  53 ,  53   a ; and  54 ,  54   a  is rotatable essentially about the axis of a retaining member  82 . Each retaining member  82  comprises a screw member having threads  83  secured in mounting member  44 , a shank  84  and a head  85  overlying retaining finger  81  and a bushing  86  disposed about shank  84 . Gears  54  and  54  a rotate about the axis of bushing  86 . Bushing  86  is slightly larger in inside diameter than shank  84 . Bushing  86  is held in compression under the head  85  of member  82  when it is tightened down. This permits adjustment of the position of the axis of bushing  86  and hence the axis of gears  54  and  54   a . This arrangement enables the positioning of the planetary gears such that they always make contact with the orbit gear at the pitch diameter of the gear teeth. This also limits the orbital movement of orbit gear, which provides a smoother operation of the planetary gear system. The same planet gear axis adjustment may be used for the planet gears of FIG.  3 . 
     In one embodiment, as shown in FIGS. 8 and 9, the gears have the following relationship: 
     
       
         
               
               
               
             
           
               
                   
                   
               
             
             
               
                   
                 Orbit gear 58 
                 72 teeth 
               
               
                   
                 Upper planet gear 54a 
                 24 teeth 
               
               
                   
                 Lower planet gear 54 
                 80 teeth 
               
               
                   
                 Sun gear 57 not shown in 
               
               
                   
                 Figure 8 
                 44 teeth 
               
               
                   
                   
               
             
          
         
       
     
     This provided a drive ratio of 4.8:1, planet to sun gear. The operation of the mechanism of FIGS. 8 and 9 is much smoother than the mechanism previous described due to the larger number of teeth. 
     It is to be noted that the ratio of the teeth of orbit gear  58  to the teeth of the upper planet gears  54   a  again provides a separate track for the teeth of each of the upper planet gears. 
     Reference is now made to FIGS. 10 and 11. FIG. 10 is a view of a watch embodying the invention with the back removed. The bimetallic coil  43  is disposed within a carrier and drive member  90  having cross arms  91  and  92 . Arms  91  and  92  are broken away at their center to show bearing member  36  and shaft  37  therebelow in bridge member  32 . Bridge member  32  is not entirely shown in FIG. 10, for clarity of illustration. The outer race of bearing  36  is supported on bridge member  32 . As coil  43  expands and contracts with temperature it will rotate member  90  and produce rotation of shaft  37  in either direction. Member  90  is fast on shaft  37  and retained thereon by a screw  37   a  extending into shaft  37 . Member  90  receives a snap-in cover ring  90   a  into peripheral flange to aid in retaining coil  43 . This allows the provision of a self-contained energy source for the watch. Member  90  with cover ring  90 a and coil  43  may be separately assembled, placed in the watch casing on shaft  37  and retaining screw  37   a  is inserted into shaft  37 . 
     The inner end of coil  43  is secured to bridge member  32 , as shown in FIG. 2, by a clip  93 . The outer end of coil  43  has previously been secured to member  90 , as previously described in conjunction with orbit gear  58  as shown in FIG.  5 ( a ) or any other suitable mariner. 
     This allows the provision of a self-contained, cartridge-type energy source for the watch. Member  90  with cover ring  90   a  and coil  43  may be separately assembled, placed in the watch casing, shaft  37  is inserted into bearing  36  in bridge member  32  and then clip  93  is secured to bridge member  32   
     In FIG. 11, shaft  37  is shown as driving a pinion gear  94  of a bi-directional winding mechanism, which will drive the barrel  95  of the mainspring as hereinafter described. The movement of the watch is located in the area identified by the reference M. 
     Another bi-directional to unidirectional winding mechanism is shown (not to scale) in FIG. 12 as it may be seen from the underside of FIG.  11 . Pinion  94  on shaft  37  engages what is termed a “wig-wag” gear  97 . Gear  97  is on a shaft  98 , which is moveable in a slot  99  to drive either of gears  101  or  102  rotatable on shafts in bridge member  32  (not shown in FIG.  12 ). Gear  97  will move longitudinally in slot  98  and rotate in a direction dependent on the direction of rotation of pinion  94 . When pinion  94  rotates in the direction of the arrow shown, it will drive wig-wag gear  97  to the position shown in slot  99 , which in turn drives gear  101  as shown. This results in rotation of gears  102  and  103  as shown. If gear  94  is rotated in the opposite direction shaft  98  will moved to the other end of slot  99  and wig-wag gear  97  will be in engagement with gear  102 . Gear  102  will rotate in the same direction and thus gear  103  will always rotate in one direction. This produces unidirectional winding of the mainspring barrel for either direction of rotation of pinion  94 . The entire mechanism shown in FIG. 12 is termed a “wig-wag” mechanism. 
     In the embodiment of FIGS. 10-12, pinion  94  will have the same total angular rotation as member  90 , since both are fast on shaft  37 . 
     
       
         
               
               
               
             
           
               
                   
                   
               
             
             
               
                   
                 pinion 94 
                 18 teeth 
               
               
                   
                 wig-wag gear 97 
                 14 teeth 
               
               
                   
                 gears 101, 102 and 103 
                 32 teeth 
               
               
                   
                   
               
             
          
         
       
     
     This provides a gear ratio of 0.5625 from pinion  94  to mainspring barrel gear  103 . 
     Consider the previous example of a twenty-four hour cycle where: 
     
       
         
               
               
               
             
           
               
                   
                   
               
             
             
               
                   
                 Coil deflection 
                 = 12°/° F. 
               
               
                   
                 Total degree F changes in twenty-four hours 
                 = 357 
               
               
                   
                 Total Equivalent Angular deflection of coil 
                 = 4284° 
               
               
                   
                 43 in 24 hours 
               
               
                   
                 Total Equivalent revolutions = rev. 
                 = 11.9 rev. 
               
               
                   
                 of member 90 in 24 hours 
               
               
                   
                 Number of equivalent revolutions of pinion 94 
                 = 11.9 
               
               
                   
                 Input Revolutions of mainspring barrel 95 is 
                 = 6.694 rev./day 
               
               
                   
                 11.9 × 18/14 × 14/32 
               
               
                   
                 Power consumption of mainspring is 60°/hour 
                 = 4 rev./day 
               
               
                   
                 Power Input to Mainspring/Power Consumption 
                 = 1.676 
               
               
                   
                   
               
             
          
         
       
     
     While the input to consumption ratio is greater than unity, the mainspring will never be over wound. As the mainspring is wound, its resistance to further winding will increase and reach a point that the coil  43  cannot overcome. At this point, the power out put torque from coil  43  will equal the resistance torque of the mainspring and a constant power input to the mainspring to drive the watch movement is established. This is sometimes referred to as the Remontaire effect. If the coil  43  cannot overcome the resistance of the mainspring, the coil will deflect angularly. 
     A unity power input to power consumption ratio would be reached if there were only enough degree F. temperature changes to provide angular movement of coil  43  equal to the power consumption from the main spring. 
     Returning to the previous example, assume that the watch was not removed at night. This would eliminate the two twenty-five degree temperature changes when the watch is removed in the evening and put back on in the morning. Then, the total temperature change in a twenty-four hour period is 302  F. 
     This will give a total angular deflection of coil  43  of 3624 degrees or 10.06 equivalent revolutions of member  90  and pinion  94 . This will result in a power input to the mainspring barrel  95  of 5.69 revolutions which is 1.69 revolutions greater than the daily power consumption of the mainspring. This is more than sufficient to overcome any mechanical losses in the system. 
     The term “bi-directional to unidirectional” has been used herein for purposes of describing two mechanisms, which convert bi-directional motion of a first shaft to unidirectional motion of another shaft. The term bi-directional to unidirectional also includes mechanisms in which there is only one direction of rotation of a shaft to unidirectional motion of another shaft. For example, in the mechanism of FIG. 12, gear  101  may be eliminated and gear  103  would be driven only during counter clockwise rotation of gear  94 . Wig-wag gear  97  would engage gear  102  only upon counter clockwise rotation of gear  94 . 
     Other bi-directional drive mechanisms, if suitable, may be utilized. Also, the wig-wag winding mechanism of FIG. 12 may be used in a timepiece which utilizes a planetary gearing energy transmission as disclosed in conjunction with FIG.  3 . 
     The direct drive embodiment of FIGS. 10 and 11 reduces the number of parts in relation to the previously described embodiments. It is especially advantageous in eliminating the planetary gearing system and any attendant problems therewith. The direct drive arrangement also makes it easier for up and down scaling in watch size and for the use of a wider variety of watch movements. The reduction of parts also reduces manufacturing costs from the standpoint of both parts and labor. The coil is also more susceptible to change in temperature due to convection. 
     The invention, while being described in relation to a wristwatch is also applicable to clocks, which are used in an environment where the temperature is controlled by normal thermostats. 
     It may thus be seen that the objects of the invention set forth above as well as those made apparent are efficiently attained. While preferred embodiments of the invention have been set forth for purposes of disclosure, modifications to the disclosed embodiments as well as other embodiments thereof may occur to those skilled in the art. Accordingly, the appended claims are intended to cover all modifications to the disclosed embodiments of the invention as well as other embodiments thereof, which do not depart from the spirit and scope of the invention.