Abstract:
The angular motion translator is a device with direct mechanical coupling which allows a user to reliably and durably change the angular relationship between two elements in a rotating frame (i.e. two output shafts) by changing the angular relationship between two elements in a static reference frame, whereby the change in the angular relationship of the elements in the rotating frame is proportional to the change in the angular relationship of the elements in the static reference frame. Essentially, the angular motion translator is comprised of two linked identical planetary gear sets facing one another as mirror images. Matching elements in the two planetary gear sets are held static, although one of the static elements may be rotated with respect to the other, matching elements are rigidly attached together so that they rotate as a single unit, and the remaining matching elements are attached to either the input shaft and the inner output shaft or the outer output shaft respectively.

Description:
BACKGROUND OF THE INVENTION  
         [0001]    This invention relates generally to controlling the relative angular relationship between two elements in a rotating system by changing the relationship between two elements in a related non-rotating system, such that the relative angular relationship between the two elements in the rotating system may easily be altered while the system rotates. More specifically, the present invention provides the ability to either incrementally or continuously alter the angular relationship between two parallel output shafts by introducing a specified angular motion change (angular displacement). Essentially, the two output shafts will, when left alone, rotate together at the same speed, but with the present invention, a user may introduce an angular motion change while the shafts continue to rotate, advancing one shaft&#39;s angular position with respect to the other shaft, using a control mechanism in a static reference frame; once the user stops introducing an angular motion change, the two shafts will again rotate together at the same speed, although the angular displacement introduced will remain. In the prior art, there were two techniques for accomplishing this goal: 1) inducing lateral motion in a shaft at the center of rotation of the system, with said motion parallel and congruent to the center of rotation, and then translating that motion into the rotating system using a rotating disk sliding through bearings on levers fixed to the rotating system, or 2) varying the pressure in a hydraulic system, with said hydraulic system translated into the rotating system through a rotating seal, such that the pressure is then utilized to move an element or elements in the rotating system.  
           [0002]    There are, however, problems inherent in these previous techniques which limit their effectiveness. Specifically, devices which use these techniques have inherently high wear factors and/or are subject to high manufacturing and maintenance costs because of the close tolerances required and the high stresses placed upon the individual components of the devices. Additionally, as these devices wear, they tend to become more unstable. The rotating disk used in the first technique described above must be able to handle all of the torque induced through the system. Because of the high relative motion of the disk to the rotating system, the rate of wear will be high and, with wear, the system will tend to oscillate. And, the hydraulic-based systems described above are inherently unstable since they do not consist of a direct mechanical coupling. Minute variations in any part of the system will impact the pressure within the hydraulic fluid and will alter the position of the driven elements, with this altering of position then changing the pressure in the hydraulic fluid to initiate positive feedback and cause, or perpetuate, an oscillation.  
           [0003]    The present invention overcomes these problems because it employs a direct mechanical coupling which allows for control of the relative angular position of two elements in the rotating system, while such control is induced in or between two static elements outside of the rotating system. Since the present invention uses gears (with meshing teeth) for a direct mechanical coupling, the forces are spread effectively throughout the device, reducing both wear and oscillation concerns.  
         SUMMARY OF THE INVENTION  
         [0004]    The Angular Motion Translator (“AMT”) consists conceptually of two inertial frames: a static reference frame, which is static relative to the observer, and a rotating frame, which rotates about an axis with respect to the static reference frame and the observer. The AMT can be used to translate an angular relationship between two elements contained within the static reference frame into a proportional angular relationship between two elements contained within the rotating frame. More specifically, an angular (rotational) displacement of one of the elements in the static reference frame with respect to the other element in the static reference frame will result in a proportional angular (rotational) displacement of one of the elements in the rotating frame with respect to the other element in the rotating frame, allowing a user of the AMT to easily alter the angular relationship between the two elements in the rotating frame.  
           [0005]    The physical embodiments of the AMT are comprised of two linked, identical planetary gear sets. Each planetary gear set is comprised of a sun gear, a planetary gear array (further comprised of one or more planet gears and a planetary carrier which links the planet gears together and which fixes their orbit around the sun gear and the central axis of the planetary gear set), and an annular gear. In such planetary gear sets, the sun gear is located at the center (on the central axis of the planetary gear set), the planet gears rotate around the outside of the sun gear in orbit (with the teeth of each planet gear meshing with the teeth of the sun gear, forming a mechanical coupling), the planetary carrier links the axis of rotation of each of the planet gears and holds the planet gears together in orbit about the sun gear (such that the planetary gear array rotates as a unit), and the annular gear encompasses the whole (with the teeth of the planet gears meshing with the teeth of the annular gear, forming a mechanical coupling).  
           [0006]    In the AMT, the two identical planetary gear sets face one another as mirror images. One of the elements of the first planetary gear set is held static, and the identical, matching element in the second planetary gear set is also held static, although the angular relationship between them may be changed. These two elements are in the static reference frame. A different element of the first planetary gear set is rigidly attached to the input shaft, with the input shaft passing through the entire AMT along the center axis (passing through the second planetary gear set without interacting with the second planetary gear set) and emerging as the inner output shaft, and the identical, matching element in the second planetary gear set is rigidly attached to the outer output shaft, which is hollow so that it does not interact with the inner output shaft. The inner output shaft and the outer output shaft are the two elements in the rotating frame. Finally, the remaining elements in both of the planetary gear sets are rigidly linked together so that they rotate as one unit. In this configuration, a change in the angular relationship between the two elements in the static reference frame produces a proportional change in the angular relationship between the two elements in the rotating frame.  
           [0007]    So in static mode, when the input shaft rotates to provide driving power, both the inner output shaft (which is essentially a continuation of the input shaft) and the outer output shaft will rotate at the same angular speed (i.e. there will be no angular displacement). If, however, one of the elements which is being held static is rotated with respect to the other element which is being held static in the other planetary gear set, this introduces an angular displacement (either adding or subtracting a proportion of the amount of rotation between the two static elements in the static reference frame to the input rotation, resulting in a change to the outer output shaft rotation). Thus, the angular relationship between the inner output shaft and the outer output shaft may be altered proportionately by rotating one of the static elements with respect to the other.  
           [0008]    Although the two planetary gear sets could be connected in any number of ways (so long as identical, matching elements in each planetary gear set are held static; another element in the first planetary gear set is rigidly connected to its sister, identical, matching element in the second planetary gear set; the remaining elements are connected to either the input shaft and the inner output shaft or the outer output shaft respectively; and the matching gears of each of the planetary gear sets are identical in size and number of teeth), there are two preferred embodiments which simplify construction due to convenient bearing placement. In the first embodiment, the input shaft is rigidly attached to the sun gear of the first planetary gear set, such that when the input shaft rotates, it causes the sun gear of the first planetary gear set to rotate. The sun gear of the first planetary gear set is also rigidly attached to the inner output shaft, such that the sun gear of the first planetary gear set is sandwiched between the input shaft and the inner output shaft (or, these three elements may be thought of as one, continuous element). The planet gears of the first planetary gear set orbit the sun gear with meshing teeth. The annular gear of the first planetary gear set encompasses the first planetary gear set, with its teeth meshing with those of the planet gears, and it is held static. The planetary carrier for the first planetary gear set is rigidly attached to the planetary carrier for the second planetary gear set, such that the planetary gear array (comprised of the planet gears and the planetary carrier) of the first planetary gear set and the planetary gear array (comprised of the planet gears and the planetary carrier) of the second planetary gear set are linked and rotate as a unit. The planetary gear arrays typically each have an equal number of planet gears, and the rotating axis of pairs of planet gears matched between the two planetary gear arrays are often fixed into a mounting-bearing assembly that is free to rotate about the primary axis (i.e. the planetary carriers of the first planetary gear set and the second planetary gear set are linked in such a way that they rest on bearings that allow them to freely rotate about the inner output shaft without interacting with the inner output shaft as it passes from the first planetary gear set on through the second planetary gear set). The annular gear for the second planetary gear set is also held static, with its teeth meshing with those of the planet gears of the second planetary gear set, which it encompasses. The planet gears of the second planetary gear set orbit the sun gear of the second planetary gear set, with meshing teeth. The sun gear of the second planetary gear set is rigidly attached to the outer output shaft, such that when the sun gear of the second planetary gear set rotates, it causes the outer output shaft to rotate. The outer output shaft is hollow, and the sun gear of the second planetary gear set also has a hollow center so that the inner output shaft, which is rigidly attached to the sun gear of the first planetary gear set, may pass through the center of the second planetary gear set without interacting with it, emerging from the second planetary gear set as the inner output shaft, within (and parallel with, along the centerline) the outer output shaft.  
           [0009]    In this embodiment, when both annular gears are held static, both output shafts rotate at the same angular velocity, moving in unison. The rotation of the input shaft, which is the same as the rotation of the inner output shaft since they are both rigidly connected to the sun gear of the first planetary gear set, is transmitted through the AMT via the sun gear in the first planetary gear set, which drives the planet gears of the first planetary gear set to rotate in orbit around the sun gear of the first planetary gear set and within the annular gear of the first planetary gear set, thereby driving the planetary carrier (and the planetary gear array as a whole) of the first planetary gear set. The planetary carrier (and the planetary gear array) of the first planetary gear set then drives the planetary gear array of the second planetary gear set, since the planetary carrier of the first planetary gear set is rigidly attached to the planetary carrier of the second planetary gear set (such that the planet gears of the second planetary gear set rotate in unison with the planet gears of the first planetary gear set), causing the sun gear of the second planetary gear set, and thereby the outer output shaft, to rotate.  
           [0010]    Since all of the gears in both of the planetary gear sets are identical (matching with their sister in the other planetary gear set), when the annular gears are held fixed, the input rotation from the input shaft is transferred through the AMT without any change so that the inner output shaft and the outer output shaft rotate at the same angular speed, and there is no angular displacement between the two output shafts. But, if the annular gear of the second planetary gear set is rotated with respect to the annular gear of the first planetary gear set (or vice versa), then the outer output shaft will receive a proportional rotation (angular displacement) with respect to the inner output shaft. Once the angular relationship between the two annular gears has ceased to change, the two output shafts will again rotate at the same angular speed, but their angular relationship will have changed proportionally to the change in the angular relationship between the two annular gears (i.e. the angular displacement would remain). The angular change in relationship between the two output shafts is equal to the angular change in relationship between the two annular gears times a scaling factor, which is the number of teeth in an annular gear divided by the number of teeth in a planet gear.  
           [0011]    In the second preferred embodiment, the input shaft is rigidly attached to the sun gear of the first planetary gear set, such that when the input shaft rotates, it causes the sun gear of the first planetary gear set to rotate. The sun gear of the first planetary gear set is also rigidly attached to the inner output shaft, such that the sun gear of the first planetary gear set is sandwiched between the input shaft and the inner output shaft (or, these three elements may be thought of as one, continuous element). The planet gears of the first planetary gear set are held in place around the sun gear (with meshing teeth) by the planetary carrier of the first planetary gear set, which is held static (while typically resting on bearings such that it does not interact with the input shaft). The annular gear of the first planetary gear set encompasses the planet gears (with meshing teeth) and is rigidly attached to the annular gear of the second planetary gear set, which encompasses the second planetary gear set. Thus, the annular gears of both planetary gear sets are linked and rotate as a single unit. The planet gears of the second planetary gear set are held in place within the annular gear of the second planetary gear set by the planetary carrier of the second planetary gear set, which is statically fixed (while typically resting on bearings such that it does not interact with the outer output shaft), except that the angular relationship between the two planetary carriers may be altered. The planet gears of the second planetary gear set surround the sun gear of the second planetary gears set (with meshing teeth), which is located at the center of the second planetary gear set. The sun gear of the second planetary gear set is hollow, such that the inner output shaft may pass through the second planetary gear set without interacting with it, and is rigidly attached to the outer output shaft, which is also hollow.  
           [0012]    In this embodiment, when both planetary carriers are held static, both output shafts rotate at the same angular velocity, moving in unison. The rotation of the input shaft, which is the same as the rotation of the inner output shaft since they are both rigidly connected to the sun gear of the first planetary gear set, is transmitted via the sun gear, through the planet gears of the first planetary gear set, to the annular gear of the first planetary gear set. The planet gears do not orbit the sun gear because they are restrained by the static planetary carrier, so that the planet gears instead rotate in place, transmitting the driving force to the annular gear and causing the annular gear to rotate. Since the annular gear of the first planetary gear set is rigidly attached to the annular gear of the second planetary gear set, the annular gear of the second planetary gear set is driven in lockstep with the annular gear of the first planetary gear set. The annular gear of the second planetary gear set acts upon the planet gears of the second planetary set, which are restrained by the static planetary carrier of the second planetary gear set so that they do not traverse the annular gear or orbit the sun gear, causing the planet gears of the second planetary gear set to rotate in place and thereby driving the sun gear of the second planetary gear set. The sun gear of the second planetary gear set drives the outer output shaft.  
           [0013]    Since all of the gears in both of the planetary gear sets are identical (matching with their sister in the other planetary gear set), when the two planetary carriers are held fixed, the input rotation from the input shaft is transferred through the AMT without any change so that the inner output shaft and the outer output shaft rotate at the same angular speed and there is no angular displacement between the two output shafts. But, if the planetary carrier for the second planetary gear set is rotated with respect to the planetary carrier of the first planetary gear set (or vice versa), then the outer output shaft will receive a proportional rotation (angular displacement) with respect to the inner output shaft. Once the angular relationship between the two planetary carriers has ceased to change, the two output shafts will again rotate at the same angular speed, but their angular relationship will have changed proportionally to the change in the angular relationship between the two planetary carriers (i.e. the angular displacement would remain). The angular change in relationship between the two output shafts is equal to the angular change in relationship between the two planetary carriers times a scaling factor, which is the number of teeth in a planet gear divided by the number of teeth in an annular gear. This embodiment provides a greater mechanical advantage for the change inducing force than in the first embodiment, since a planet gear will always have fewer teeth than an annular gear.  
           [0014]    The primary object of this invention is to allow a user to alter the angular relationship between two elements in a rotational frame. It is still another object to allow a user to alter the angular relationship between two elements in a rotating frame proportionately to a change in the relationship between two elements in a static reference frame. It is yet another object of this invention to employ direct mechanical coupling. It is yet another object to provide a durable, low-maintenance device for altering the angular relationship between two rotational elements, reducing wear and oscillation concerns. In addition to these general objects, the AMT can be used in several real-world applications. For example, an AMT device could be used for dispensing filament for a weed trimmer, for controlling the amplitude of shaking in a chute-type feeder for dry product, for operating a shutter in a motion picture camera, or for measuring torque. The use of the AMT to perform these various functions will be described in greater detail in the detailed description section below. These are only illustrative examples of possible uses for the AMT and are not exclusive; the AMT is not limited to these uses. These and other objects of the present invention will be more apparent to those skilled in the art field from the following detailed description of the AMT invention. 
       
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS  
       [0015]    Reference will be made to the drawings wherein like parts are designated by like numerals and wherein:  
         [0016]    [0016]FIG. 1 is an isometric view of the first preferred embodiment of the Angular Motion Translator, wherein the annular gears are the static elements and the planetary carriers, and thereby the planetary arrays, are linked.  
         [0017]    [0017]FIG. 2 is a longitudinal section of the first preferred embodiment of the AMT.  
         [0018]    [0018]FIG. 3 is a traverse section of the first preferred embodiment of the AMT.  
         [0019]    [0019]FIG. 4 is a cross-section of the second preferred embodiment of the Angular Motion Translator, wherein the planetary carriers are the static elements and the annular gears are linked.  
         [0020]    [0020]FIG. 5 is a cross-section of the AMT configured to dispense filament, as for a weed trimmer.  
         [0021]    [0021]FIG. 6 is an isometric view of the AMT configured to incrementally dispense filament, as for a weed trimmer.  
         [0022]    [0022]FIG. 7 is a sectional view and FIG. 8 is an isometric view of an AMT configured for controlling the amplitude of an eccentrically shaped shaker system in a shaking chute-type feeding system for dry product.  
         [0023]    [0023]FIG. 9 is an isometric view of an AMT configured as a motion picture camera shutter control system.  
         [0024]    [0024]FIG. 10 is a sectional view and FIG. 11 is an isometric view of the AMT configured as a torque measuring system. 
     
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS  
       [0025]    Referring now to the drawings in more detail, the preferred embodiments of the Angular Motion Translator (“AMT”)  50  are set forth below. The first preferred embodiment is shown in FIGS. 1, 2, and  3 . In the first preferred embodiment, the AMT  50  is comprised of two planetary gear sets  10  and  20 , with the first planetary gear set  10  comprised of a sun gear  2 , a planetary gear array (further comprised of planet gears  4  and a planetary carrier  5 , although not separately numbered in the drawings), and an annular gear  6 ; and with the second planetary gear set comprised of a sun gear  24 , a planetary gear array (further comprised of planet gears  22  and a planetary carrier  21 , although not separately numbered in the drawings), and an annular gear  23 . The input shaft  1  is rigidly attached to the sun gear  2  of the first planetary gear set  10 , such that when the input shaft  1  rotates, it causes the sun gear  2  of the first planetary gear set  10  to rotate. The sun gear  2  of the first planetary gear set  10  is also rigidly attached to the inner output shaft  3 , such that the sun gear  2  of the first planetary gear set  10  is sandwiched between the input shaft  1  and the inner output shaft  3  (or, these three elements may be thought of as one, continuous element). The planet gears  4  of the first planetary gear set  10  orbit the sun gear  2  with meshing teeth. The annular gear  6  of the first planetary gear set  10  encompasses the first planetary gear set  10 , with its teeth meshing with those of the planet gears  4 , and annular gear  6  is held static. The planetary carrier  5  for the first planetary gear set  10  is rigidly attached to the planetary carrier  21  for the second planetary gear set  20 , such that the planetary gear array of the first planetary gear set  10  and the planetary gear array of the second planetary gear set  20  are linked and rotate as a unit. The planetary gear arrays (comprised of planet gears  4  or  22  in conjunction with the respective planetary carrier  5  or  21 , and not separately numbered in the drawings) each typically have an equal number of planet gears  4  and  22 , and the rotating axis of pairs of planet gears  4  and  22  matched between the two planetary gear arrays are often fixed into a mounting-bearing assembly that is free to rotate about the primary axis (i.e. the planetary carrier  5  of the first planetary gear set  10  and the planetary carrier  21  of the second planetary gear set  20  are linked in such a way that they rest on bearings that allow them to freely rotate about the inner output shaft  3  without interacting with the inner output shaft  3  as it passes from the first planetary gear set  10  on through the second planetary gear set  20 ). The annular gear  23  of the second planetary gear set  20  is also held static, except that the angular relationship between the two annular gears  6  and  23  may be altered. The planet gears  22  of the second planetary gear set  20  traverse the annular gear  23  of the second planetary gear set  20  and orbit the sun gear  24  of the second planetary gear set  20 , with meshing teeth. The sun gear  24  of the second planetary gear set  20  is rigidly attached to the outer output shaft  25 , such that when the sun gear  24  of the second planetary gear set  20  rotates, the outer output shaft  25  also rotates. The outer output shaft  25  is hollow, and the sun gear  24  of the second planetary gear set  20  also has a hollow center so that the inner output shaft  3 , which is rigidly attached to the sun gear  2  of the first planetary gear set  10 , may pass through the center of the second planetary gear set  20  without interacting with the second planetary gear set  20 , emerging from the second planetary gear set  20  as the inner output shaft  3 , within (and parallel with, along the centerline) the outer output shaft  25 .  
         [0026]    In this embodiment, when both annular gears  6  and  23  are held static, both the inner output shaft  3  and the outer output shaft  25  rotate at the same angular velocity, moving in unison. The rotation of the input shaft  1 , which is the same as the rotation of the inner output shaft  3  since they are both rigidly connected to the sun gear  2  of the first planetary gear set  10 , is transmitted through the AMT  50  via the sun gear  2  in the first planetary gear set  10 , which drives the planet gears  4  of the first planetary gear set  10  to rotate in orbit around the sun gear  2  of the first planetary gear set  10  and within the annular gear  6  of the first planetary gear set  10 , thereby driving the planetary carrier  5  (and the planetary gear array as a whole) of the first planetary gear set  10 . The planetary carrier  5  of the first planetary gear set  10  is rigidly attached to the planetary carrier  21  of the second planetary gear set  20 , so that the planetary carrier  21  of the second planetary gear set  20  is driven in unison with the planetary carrier  5  of the first planetary gear set  10 . The planetary carrier  21  (and the planetary gear array) of the second planetary gear set  20  then drives the planet gears  22  of the second planetary gear set  20  (in unison with the rotation of the planet gears  4  of the first planetary gear set  10 ), causing the sun gear  24  of the second planetary gear set  20 , and thereby the outer output shaft  25 , to rotate.  
         [0027]    Since all of the gears in both of the planetary gear sets  10  and  20  are identical (matching with their sister in the other planetary gear set), when the annular gears  6  and  23  are held fixed, the input rotation from the input shaft  1  is transferred through the AMT  50  without any change so that the inner output shaft  3  and the outer output shaft  25  rotate at the same angular speed and there is no angular displacement between the two output shafts  3  and  25 . But, if the annular gear  23  for the second planetary gear set  20  is rotated with respect to the annular gear  6  of the first planetary gear set  10  (or vice versa), then the outer output shaft  25  will receive a proportional rotation (angular displacement) with respect to the inner output shaft  3 . Once the angular relationship between the two annular gears  6  and  23  has ceased to change, the two output shafts  3  and  25  will again rotate at the same angular speed, but their angular relationship will have changed proportionally to the change in the angular relationship between the two annular gears  6  and  23  (i.e. the angular displacement would remain). The angular change in relationship between the two output shafts  3  and  25  is equal to the angular change in relationship between the two annular gears  6  and  23  times a scaling factor, which is the number of teeth in an annular gear (either  6  or  23 ) divided by the number of teeth in a planet gear (either  4  or  22 ).  
         [0028]    The second preferred embodiment of the Angular Motion Translator  50  is shown in FIG. 4. In the second preferred embodiment, the input shaft  1  is rigidly attached to the sun gear  2  of the first planetary gear set  10 , such that when the input shaft  1  rotates, it causes the sun gear  2  of the first planetary gear set  10  to rotate. The sun gear  2  of the first planetary gear set  10  is also rigidly attached to the inner output shaft  3 , such that the sun gear  2  of the first planetary gear set  10  is sandwiched between the input shaft  1  and the inner output shaft  3  (or, these three elements may be thought of as one, continuous element). The planet gears  4  of the first planetary gear set  10  are held in place around the sun gear  2  (with meshing teeth) by the planetary carrier  5  of the first planetary gear set  10 . The planetary carrier  5  of the first planetary gear set  10  is held static. The annular gear  6  of the first planetary gear set  10  encompasses the planet gears  4  (with meshing teeth) and is rigidly attached to the annular gear  21  of the second planetary gear set  20 , which encompasses the second planetary gear set  20 . Thus, the annular gears  6  and  21  for both planetary gear sets  10  and  20  are linked and rotate in lockstep as a single unit. The planet gears  22  of the second planetary gear set  20  are held in place within the annular gear  21  of the second planetary gear set  20  by the planetary carrier  23  of the second planetary gear set  20 . The planetary carrier  23  of the second planetary gear set  20  is statically fixed, except that the angular relationship between the two planetary carriers  5  and  23  may be altered. The planet gears  22  of the second planetary gear set  20  surround the sun gear  24  of the second planetary gears set  20  (with meshing teeth), which is located at the center of the second planetary gear set  20 . The sun gear  24  of the second planetary gear set  20  is hollow, such that the inner output shaft  3  may pass through the second planetary gear set  20  without interacting with the second planetary gear set  20 , and is rigidly attached to the outer output shaft  25 , which is also hollow.  
         [0029]    In this embodiment, when both planetary carriers  5  and  23  are held static, both the inner output shaft  3  and the outer output shaft  25  rotate at the same angular velocity, moving in unison. The rotation of the input shaft  1 , which is the same as the rotation of the inner output shaft  3  since they are both rigidly connected to the sun gear  2  of the first planetary gear set  10 , is transmitted via the sun gear  2 , through the planet gears  4  of the first planetary gear set  10 , to the annular gear  6  of the first planetary gear set  10 . The planet gears  4  do not orbit the sun gear  2  because they are restrained by the static planetary carrier  5 , so that the planet gears  4  instead rotate in place, transmitting the driving force to the annular gear  6  and causing the annular gear  6  to rotate. Since the annular gear  6  of the first planetary gear set  10  is rigidly attached to the annular gear  21  of the second planetary gear set  20 , the annular gear  21  of the second planetary gear set  20  is driven in lockstep with the annular gear  6  of the first planetary gear set  10 . The annular gear  21  of the second planetary gear set  20  acts upon the planet gears  22  of the second planetary set  20 , which are restrained by the static planetary carrier  23  so that they do not traverse the annular gear  21  or orbit the sun gear  24  of the second planetary gear set  20 , causing the planet gears  22  of the second planetary gear set  20  to rotate in place and thereby driving the sun gear  24  of the second planetary gear set  20 . The sun gear  24  of the second planetary gear set  20  drives the outer output shaft  25 .  
         [0030]    Since all of the gears in both of the planetary gear sets  10  and  20  are identical (matching with their sister in the other planetary gear set), when the two planetary carriers  5  and  23  are held fixed, the input rotation from the input shaft  1  is transferred through the AMT  50  without any change so that the inner output shaft  3  and the outer output shaft  25  rotate at the same angular speed and there is no angular displacement between the two output shafts  3  and  25 . But, if the planetary carrier  23  for the second planetary gear set  20  is rotated with respect to the planetary carrier  5  of the first planetary gear set  10  (or vice versa), then the outer output shaft  25  will receive a proportional rotation (angular displacement) with respect to the inner output shaft  3 . Once the angular relationship between the two planetary carriers  5  and  23  has ceased to change, the two output shafts  3  and  25  will again rotate at the same angular speed, but their angular relationship will have changed proportionally to the change in the angular relationship between the two planetary carriers  5  and  23  (i.e. the angular displacement would remain). The angular change in relationship between the two output shafts  3  and  25  is equal to the angular change in relationship between the two planetary carriers  5  and  23  times a scaling factor, which is the number of teeth in a planet gear (either  4  or  22 ) divided by the number of teeth in an annular gear (either  6  or  21 ). This embodiment provides a greater mechanical advantage for the change inducing force than in the first embodiment, since a planet gear ( 4  or  22 ) will always have fewer teeth than an annular gear ( 6  or  21 ).  
         [0031]    These preferred embodiments of the AMT  50  may be put to various uses. FIG. 5 demonstrates an AMT  50  configured as in the first preferred embodiment as described above (although other embodiments could also be used) to act as a mechanism for continuously feeding filament  8  from a spool  7  out of a cover  26 , as for a weed trimmer. The driving power from the weed trimmer motor enters the AMT  50  as the input shaft  1 . A filament dispensing spool  7  is rigidly attached to the inner output shaft  3 , such that when said inner output shaft  3  rotates, the spool  7  also rotates with it. A length of filament  8  is wrapped around the spool  7 . A cover  26  encompasses the spool  7  without contacting the spool  7  and is rigidly attached to the outer output shaft  25 , such that when said outer output shaft  25  rotates, the cover  26  also rotates with it. The cover  26  has a feeding aperture  27 , through which the free end of the filament  8  wrapped around the spool  7  is fed. The portion of filament  8  outside of the cover  26  is used as the cutting instrument for the weed trimmer. The annular gear  23  of the second planetary gear set  20  is fixed to the chassis of the trimmer, while the annular gear  6  of the first planetary gear set  10  may be controlled by the user to rotate the inner output shaft  3  with respect to the outer output shaft  25 . The filament  8  is advanced through the aperture  27  in the cover  26  when the user causes rotation of the annular gear  6  of the first planetary gear set  10  with respect to the fixed annular gear  23  of the second planetary gear set  20 , since this causes the spool  7  to rotate with respect to the cover  26 .  
         [0032]    [0032]FIG. 6 demonstrates an AMT  50  configured as in the first preferred embodiment described above (although other embodiments could also be used) to act as a mechanism for incrementally feeding filament  8  from a spool  7 , as for a weed trimmer. The driving power from the weed trimmer motor enters the AMT  50  as the input shaft  1 . A spool  7  is free to rotate about the inner output shaft  3 . A length of filament  8  is wrapped around the spool  7 . A first feed arm  9  is rigidly attached to the inner output shaft  3 , such that when the inner output shaft  3  rotates, the first feed arm  9  rotates with it. Located on the first feed arm  9  is a one directional tension pincer  11 , which grips the filament  8  when moved in one direction, but releases the filament  8  when moved in the opposite direction. A second feed arm  26  is rigidly attached to the outer output shaft  25 , such that when the outer output shaft  25  rotates, the second feed arm  26  rotates with it. Located on the second feed arm  26  is a one directional tension pincer  27 , which grips the filament  8  when moved in one direction, but releases the filament  8  when moved in the opposite direction. The free end of the filament  8  leaves the spool  7 , passes through the one directional tension pincer  11  on the first feed arm  9 , passes through the one directional tension pincer  27  on the second feed arm  26 , and extends out to act as the cutting element for the weed trimmer.  
         [0033]    The annular gear  6  of the first planetary gears set  10  is fixed to the chassis of the weed trimmer. The annular gear  23  of the second planetary gears set  20  is spring loaded against a stop. The user may alter the angle between the annular gear  6  of the first planetary gear set  10  and the annular gear  23  of the second planetary gear set  20  by a specific amount, using a cable or lever mechanism for example, to rotate the annular gear  23  of the second planetary gear set  20  a specific amount. Then, upon release, the annular gear  23  of the second planetary gear set  20  will return against its stop. When the user imparts such a change in the angular relationship between annular gear  6  of the first planetary gears set  10  and annular gear  23  of the second planetary gear set  20 , this is translated into relative motion of the two feed arms  9  and  26 , which will draw a specific, incremental amount of filament  8  from spool  7 , using both one directional tension pincers  11  and  27 , before resetting to their original angular relationship.  
         [0034]    [0034]FIGS. 7 and 8 demonstrate an AMT  50  configured as in the first preferred embodiment described above (although other embodiments could also be used) to act as an adjustable eccentric shaker in a chute-type feeding system for dry product. The power from the shaker motor enters the AMT  50  through the input shaft  1 . A first eccentrically-shaped mass  7  is rigidly attached to the inner output shaft  3 . A second eccentrically-shaped mass  26  is rigidly attached to the outer output shaft  25 . In the preferred embodiment, each of the eccentrically-shaped masses  7  and  26  are semi-circular in shape and are equally weighted. Thus, when the two eccentrically-shaped masses  7  and  26  are exactly 180 degrees opposed, the system would be in balance, with minimum vibration; when the two eccentrically-shaped masses  7  and  26  are exactly in phase, the system would have maximum eccentricity and would produce maximum vibration. The annular gear  23  of the second planetary gear set  20  is fixed to the driving motor&#39;s frame. The annular gear  6  for the first planetary gear set  10  may be rotated by the user to control the amplitude of the vibration of the shaker feed chute, while maintaining a constant frequency. In operation, when the annular gear  6  is static, the power from the input shaft would cause both the inner output shaft  3  and the outer output shaft  25 , and thereby both of the eccentrically-shaped masses  7  and  26 , to rotate at the same angular speed. The shaker chute is a separate unit (not shown in the drawing) located above and contacting both of the eccentrically-shaped masses  7  and  26 . Thus, the AMT  50  will cause the shaker chute to vibrate due to the rotation of the two eccentrically-shaped masses  7  and  26 , with the amount of vibration depending upon the relationship between the two eccentrically-shaped masses  7  and  26 . A user may adjust the relative angular relationship of the two eccentrically-shaped masses  7  and  26 , and thereby alter the amount of vibration imparted to the chute, by rotating the annular gear  6  of the first planetary gear set  10 . Thus, the AMT  50  may be used to adjust the amount of eccentricity in a shaker chute system, thereby adjusting the amplitude of vibration of the shaker chute.  
         [0035]    [0035]FIG. 9 demonstrates an AMT  50  configured as in the first preferred embodiment described above (although other embodiments could also be used) to act as a dynamically adjustable shutter for a motion picture camera. Both the annular gear  6  of the first planetary gear set  10  and the annular gear  23  of the second planetary gear set  20  are normally held static relative to the camera frame. A shutter element  7 , which is semi-circular in the preferred embodiment, is rigidly attached to the inner output shaft  3 . A shutter element  26 , which is semi-circular in the preferred embodiment, is rigidly attached to the outer output shaft  25 . The film  8  passes behind the shutter elements  7  and  26 . In normal operation, with both annular gears  6  and  23  held static, the shutter elements  7  and  26  rotate at a constant speed, and each frame of the film  8  is advanced incrementally during the “closed” portion of the shutter cycle, when the shutter elements  7  and  26  hide the film  8 . The duration of the “closed” portion of the shutter cycle depends upon the relative position of the two shutter elements  7  and  26 . If shutter element  7  and shutter element  26  are in phase, then the “closed” period will be short (i.e. it will be half of the time for full rotation of the inner output shaft  3  or the outer output shaft  25 ); the more out of phase the shutter elements  7  and  26  are, the longer the “closed” period will be. A user may dynamically alter the amount of exposure for the film  8  by changing the angular relationship between the annular gears  6  and  23 , thereby altering the angular relationship between the shutter elements  7  and  26  to provide for more or less exposure, depending upon whether the shutter elements  7  and  26  are in phase or out of phase with each other.  
         [0036]    In addition to the AMT  50  allowing a user to alter the angular relationship of two rotating elements when two identical, matching elements in the first planetary gear set  10  and the second planetary gear set  20  are held static, the AMT has other possible uses if one of the static elements is released. If either of the static elements is released, that element will be free to rotate, and the majority of the energy in the input shaft  1  will be delivered to that free element causing it to rotate. Consequently, either of the fixed static elements could also be used as a clutch, allowing for the engagement or release of the output shafts  3  and  25 .  
         [0037]    It also follows from this characteristic that a torque must be present in each of the fixed elements that is equal to but opposite in rotation to the torque being delivered through the output shafts. By taking advantage of this fact, the AMT  50  (in any of it various embodiments, including all of the versions described above) may be used as a torque measuring device. FIGS. 10 and 11 demonstrate the preferred embodiment of the AMT  50  which is configured as in the first general preferred embodiment described above (although other embodiments could also be used) to act exclusively as a torque measurement device. For this type of configuration, only a single output shaft is required. Thus, in the preferred embodiment, the input shaft  1  is rigidly connected to the sun gear  2  of the first planetary gear set  10 . The planet gears  4  surround the sun gear  2 , are held in place (with their axis linked together) by planetary carrier  5 , and are encompassed by annular gear  6  of the first planetary gear set  10 . Planetary carrier  5  of the first planetary gear set  10  is rigidly attached to planetary carrier  21  of the second planetary gear set  20 , such that they rotate as a single unit, driving the planet gears  22  of the second planetary gear set  20 . The planet gears  22  surround sun gear  24  of the second planetary gear set  20  and are encompassed by the annular gear  23  of the second planetary gear set  20 . The sun gear  24  of the second planetary gear set  20  is rigidly attached to the output shaft  25 . The annular gear  6  of the first planetary gear set  10  is anchored, such that it is fixed static, and a first platform  7 , which is a flat plate in the preferred embodiment extending out from the annular gear  6  of the first planetary gear set  10  towards but not contacting annular gear  23  of the second planetary gear set  20 , is rigidly attached to the outer surface of the annular gear  6  parallel to the center axis of the AMT  50 . A second platform  26  is rigidly attached to the outer surface of the annular gear  23  of the second planetary gear set  20  parallel to the center axis of the AMT  50  and, in the preferred embodiment, extends back from the second planetary gear set  20  towards but not contacting the annular gear  6  of the first planetary gear set  10 . Located between the first platform  7  and the second platform  26  is a force meter  27 .  
         [0038]    So, in operation, the torque to be measured is applied to the output shaft  25 . This produces an equal and opposite torque on the annular gear  23  of the second planetary set  20 , which in turn produces a force on the force meter  27 . This force may be measured by reading the force meter  27 . A user may determine the torque being applied to the output shaft  25  by multiplying the distance (d) of the force meter from the center axis of the AMT  50  (and the center axis of the output shaft  25 ) times the measured force detected by the force meter  27 . This allows precise torque measurement without any movement of the measuring element.  
         [0039]    The uses listed above are only exemplary, and are not intended to limit the scope of the present invention in any way. And, even though the preferred embodiments listed above describe only one configuration of the AMT  50 , it is to be understood that other variants of the AMT  50  will function effectively. These and other uses of the AMT  50  will be understood by persons skilled in the art field.