Abstract:
A simultaneous multiple rotation interface where a series of discs eccentrically rotate about a central shaft to create a speed reduction between an input disc and an output disc. Each disc is engaged with the other via a series of bearings embedded within each disc.

Description:
CROSS-REFERENCE TO PRIOR APPLICATION  
       [0001]     This application is a divisional of U.S. patent application Ser. No. 10/869,303, filed Jun. 16, 2004. 
     
    
     BACKGROUND OF THE INVENTION  
       [0002]     1. Field of the Invention  
         [0003]     The present invention generally relates to a simultaneous multiple rotation interface system. In particular, the present invention relates to a simultaneous multiple rotation interface wherein power is transmitted from an input to an output by a series of loosely seeded bearings acting in concert to provide for an extremely efficient, exceptionally powerful system.  
         [0004]     2. Background Information  
         [0005]     There are several types of rotation interfaces on the market today. Most commonly, these interfaces are found in speed reducers or gearboxes. Common examples of such products include: worm gear reducers, helical gear reducers, spur gear reducers, coaxial reducers, and planetary reducers. These devices are used in several areas of industry, including manufacturing, transportation, automotive, and hardware. However, all of these known products are limited in view of the present invention. Most importantly, these products do not incorporate the used of precisely aligned, seeded bearings as a mechanism to transfer power between an input and an output. This feature makes the present invention superior in view of known prior art devices.  
         [0006]     The novel design of applicant&#39;s present invention overcomes the problems associated with products known in the art. For example, known rotation interfaces depend on gears, pins, or teeth to transfer power from an input to an output. As such, when these products fail, it is often the result of these teeth, pins, or gears giving way to the shear stress resulting from impact loading exerted upon them. In fact, it is well known in the art that the primary cause of failure in typical gearboxes is tooth breakage, or accelerated wear associated with high speed pinions. This problem is exaggerated in the common case of impact loading. However, the present invention handles these damaging forces extremely well. Bearings are relied upon to withstand such forces; because these bearings are able to rotate, or “give, ” and because the force is distributed evenly among all bearings, the invention is able to withstand forces that the prior art cannot.  
         [0007]     Friction breakdown is a common problem associated with currently available rotation interfaces. There is some degree of friction along all moving internal parts, as such, regular lubrication maintenance is essential. Without such lubrication, friction build-up would surely cause a breakdown of the device from the inside out. However, the present invention reduces virtually all internal friction as it relies on a series of reliable, highly durable bearings to transfer power. Employment of such bearings reduces “sliding part” friction because these bearings effectively bear the brunt of competing forces acting on the device. Further, these bearings are aligned so that forces acting on the system are evenly distributed among all of the bearings. Elimination of “sliding part” friction and effective force distribution among all bearings provides for an exceptionally efficient device with an extremely long working life.  
         [0008]     Another problem associated with available rotation interfaces is loss of mechanical efficiency. Often poor design, friction, wear and tear, and poor component quality produce a power loss between an input and an output. However, the unique construction of the present invention provides for a negligible power loss between the input and the output. That is, each bearing engages with or “grabs” the second drive at the same precise moment so that each drive is perfectly in sink with the other. Further, each bearing is aligned so as to produce a very tight component fit between the first drive and second drive; as such, there is practically no slack between component parts.  
         [0009]     Applicant&#39;s invention is extremely cost-effective in view of known prior art. The novel design of Applicant&#39;s invention provides for a manufacturing process that is relatively simple and cost effective. As such, the present invention is much less expensive than presently known, similar products. Applicant&#39;s invention, when incorporated as part of a larger, more expensive system, can greatly reduce the “component part” cost of the system. Also, Applicant&#39;s invention can readily be incorporated with less expensive products that would otherwise be cost prohibitive. In addition, the costs of known devices increases in nonlinear fashion as rotation interfaces are manufactured to provide for double or triple speed reductions; however, the present invention, through it novel design, produces single, double, or triple speed reduction while avoiding soaring production costs.  
         [0010]     In view of the limitations of the known prior art, there is a great need for a rotation interface that is low friction, durable, mechanically efficient, and cost-effective. Applicant&#39;s invention, by its novel design and straightforward manufacturing process, provides an improved substitute for prior art devices.  
       SUMMARY OF THE INVENTION  
       [0011]     In view of the foregoing, it is an object of the present invention to provide a device that produces double or triple speed reductions inexpensively.  
         [0012]     It is another object of the present invention to provide a device that has an extremely high power to weight ratio.  
         [0013]     It is another object of the present invention to provide a device with extremely high mechanical efficiency.  
         [0014]     It is another object of the present invention to provide a device that is highly cost-effective.  
         [0015]     It is another object of the present invention to provide a device that is extremely durable.  
         [0016]     It is another object of the present invention to provide a device having a straightforward manufacturing process.  
         [0017]     It is another object of the present invention to provide a device that can withstand extreme shear stresses generated by impact loading.  
         [0018]     It is another object of the present invention to provide a device that has exceptionally low internal friction.  
         [0019]     In satisfaction of these and other related objectives, the present invention provides a novel system to achieve an input/output rotation speed differential. The present invention provides for a highly efficient, exceptionally powerful, durable, and cost-effective interface. As will be discussed in the specification to follow, practice of the present invention involves a combination of components so aligned to provide efficient operation of any number of different devices.  
         [0020]     The preferred embodiment of the present invention incorporates a series of discs that rotate about a central pin and within the inner circumference of a radial cage. An input and an output shaft are centrally, axially aligned along the central pin and effectively sandwich the series of discs between one another.  
         [0021]     In this embodiment, an input shaft is attached to an input disc that is characterized by a centrally aligned portion and an eccentric flange extending therefrom. The eccentric flange is axially aligned, but centrally offset from the central shaft so that a large radius extends in one direction, and a small radius extends in the opposite direction. As such, as the eccentric flange rotates about the central pin, the circle formed about the diameter of the eccentric flange sweeps around the centrally aligned portion of the disc in eccentric fashion, at reduced speed.  
         [0022]     A first driver disc is mated with the input disc through a series of radially aligned, embedded bearings. The first driver disc is characterized by an enlarged inner circumference that allows for eccentric rotation about the central pin. Bearings are positioned between the discs so that the first driver disc may follow the eccentric rotation of the eccentric flange. As the first driver disc is mated with the input disc eccentric flange, it eccentrically rotates about the central pin. In addition, the first driver disc is engaged with a centrally aligned, intermediate disc. Both the first driver disc and the intermediate disc rotate at a speed equal to the input rotational speed by the reciprocal of the number of radially aligned bearings between the input disc and first driver disc.  
         [0023]     The intermediate disc also is characterized by a centrally aligned portion, and a centrally offset, eccentric flange. By the same operation as above, the circle formed about the diameter of the second eccentric flange sweeps out along the radius of the centrally aligned portion, at a reduced speed. As seen before, the second eccentric flange engages a second driver that rotates about central pin in eccentric fashion at a further reduced speed. Finally, the second driver disc is engaged with centrally aligned output disc through a series of loosely embedded bearings. These bearings are positioned to allow for the eccentric motion of the second driver disc and the central position of the output disc.  
         [0024]     In summary, the first driver disc rotates about the central pin at a reduced speed by virtue of its eccentric motion, caused by engagement with the input shaft eccentric flange. However, the first driver disc remains engaged with centrally aligned components, specifically the intermediate disc, through loosely seeded bearings. The intermediate disc centrally rotates about the central pin, sharing the reduced speed of the first driver disc. This speed reduction operation is carried out a second time on a second driver disc. The second driver disc eccentrically rotates about the central pin, at a further reduced speed, by virtue of its engagement with the intermediate disc eccentric flange. Moreover, the second driver disc remains engaged with, and shares the same rotational velocity as a centrally aligned output disc. Again, this is made possible by the radially aligned, loosely seeded bearings between the two discs.  
         [0025]     An important feature associated with the rotation interface of the present invention is that the rotational speed reduction along the interface is equal to the reciprocal of the number of bearings along the interface. As such, any number of combinations can be assembled from reduction stage to reduction stage to easily produce almost any differential between input and output speed. 
     
    
     BRIEF DESCRIPTION OF THE DRAWINGS  
       [0026]     Applicant&#39;s invention may be further understood from a description of the accompanying drawings, wherein unless otherwise specified, like referenced numerals are intended to depict like components in the various views.  
         [0027]      FIG. 1  is a cross sectional view of an embodiment of the present invention. 
     
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT  
       [0028]     Referring to  FIG. 1 , an embodiment of the present invention is generally referred to as device  100 . Device  100  contains a central pin  112 . In the preferred embodiment, central pin  112  is centered about and runs through central shaft  114 . Central pin  112  is responsible for holding input  116  and output  118  axially, centrally aligned with respect to one another.  
         [0029]     Both input  116  and output  118  contain radial flange  120  and  133 , respectively. Radial flange  120  and radial flange  122  each have central pin, receiving means  124  that slideably receives central pin  112 , and is configured to allow radial pin  112  to freely rotate within radial flange  120  and  122 . In the preferred embodiment, central pin receiving means is a cylindrical-shaped shell, bored out of flanges  120  and  122 , with a diameter sized so as to allow central pin  112  to fit within receiving means  124  and rotate freely thereof.  
         [0030]     Input disc  125  is attached to input  116 . As will be further discussed, input disc is characterized by a centrally aligned tip portion  126  and an eccentric portion  127 . Input disc  125  is centrally, axially aligned with input  116  so as to share the same rotational speed as input  116 . That is, input  116  and input disc  125  may simply be welded together along the union between input  116  and input disc  125  to provide uniform rotation. Input disc  125  further contains bearing groove  128 . Bearing groove  128  runs along the outer circumference of disc  125  in ring-like fashion, and is of a concave, half-circle shape. Bearing groove  128  receives input disc bearings  130  and allows bearings  130  to rotate about an axis parallel to central pin  112 . Bearings  130  surround disc  125 , remaining loosely embedded within groove  128  so as to allow disc  125  to rotate freely with respect to radial cage  134  and radial cage support frame  132 .  
         [0031]     Disc  125  is characterized by centrally aligned portion  126  and eccentric flange  127 . Central portion  126  is centrally, axially aligned with central pin  112 , so arranged that its radius is fixed within its plane of rotation. Disc  125  is further characterized by eccentric radial flange  127 . Eccentric radial flange  127  extends from central portion  126 , and is axially aligned, but centrally offset with respect to central pin  112 . As eccentric flange  127  rotates about pin  112 , a smaller offset circle sweeps around the larger, uniform radius of  126 . This sweeping motion of eccentric flange  127  is the mechanism responsible for providing a reduction in rotational speed through use of device  100 .  
         [0032]     First driver disc  136  is mated with eccentric flange  127  through a series of bearings  138 . Bearings  138  are embedded between flange  127  and disc  136  and positioned between the outside of flange  127  and the inside of disc  136 . That is, disc  136  is of a general bowl shape so that bearings  138  rest along the inside rim of disc  136 , where bearings  138  are supported along their inside by flange  127 . Bearings  138  are embedded between flange  127  and driver disc  136  so as to allow driver disc  136  to follow the eccentric, sweeping motion of flange  127 . Disc  136  is axially aligned and centrally offset with respect to central pin  112  and is characterized by an enlarged inner circumference  140 . Inner circumference  140  is offset with respect to pin  112  and further allows disc  136  to follow the eccentric rotation of flange  127  and rotate about pin  112  in eccentric fashion.  
         [0033]     Disc  136  contains first driver disc bearing slots  142 . In the preferred embodiment, bearing slots  142  are radially aligned, are of half-spherical shape, and have a diameter equal to the diameter of bearings  146  and the eccentricity, or offset amount of eccentric flange  127 . Such arrangement allows disc  136  to rotate about central pin  112  in eccentric fashion, while remaining engaged with centrally-aligned components within device  100 .  
         [0034]     Central disc  143  is characterized by centrally aligned portion  144  and eccentric flange  145 . Central portion  144  is centrally, axially aligned with central pin  112 , so arranged that its radius is fixed within its plane of rotation. Disc  143  is further characterized by eccentric radial flange  145 . Eccentric radial flange  145  extends from central portion  144 , and is axially aligned, but centrally offset with respect to central pin  112 . As eccentric flange  145  rotates about pin  112 , a smaller offset circle sweeps around the larger, uniform radius of central portion  144 . This sweeping motion of eccentric flange  145  is the mechanism responsible for providing a second reduction in rotational speed between input  116  and output  118 . Importantly, first driver disc  136  and central disc  143  share the same rotational speed. That is, disc  136  and disc  144  have each been singly reduced by virtue of the eccentric motion of flange  127 .  
         [0035]     Second driver disc  150  is mated with eccentric flange  145  through a series of bearings  152 . Bearings  152  are embedded between flange  145  and the inside of disc  150 . That is, disc  150  is of a general bowl shape so that bearings  152  rest along the inside rim of disc  150 , where bearings  152  are supported along their inside by flange  145 . Bearings  152  are embedded between flange  145  and driver disc  150  so as to allow second driver disc  150  to follow the eccentric, sweeping motion of flange  145 . Disc  150  is axially aligned and centrally offset with respect to central pin  112  and is characterized by an enlarged inner circumference  154 . Inner circumference  154  is offset with respect to pin  112  and further allows disc  150  to follow the eccentric rotation of flange  145  and rotate about pin  112  in eccentric fashion.  
         [0036]     Disc  150  contains second driver disc bearing slots  156 . In the preferred embodiment, bearing slots  156  are radially aligned, are of half-spherical shape, and have a diameter equal to the diameter of bearings  146  and the eccentricity, or offset amount of eccentric flange  145 . Such arrangement allows disc  150  to rotate about central pin  112  in eccentric fashion, while remaining engaged with centrally-aligned components within device  100 .  
         [0037]     Output disc  158  is mated with second driver disc  150  through a series of seeded bearings  160 . Output disc  158  contains output driver disc bearing slots  162 . In the preferred embodiment, bearing slots  162  are radially aligned, are of half-spherical shape, and have a diameter equal to the diameter of bearings  160  and the eccentricity, or offset amount of eccentric flange  145 . Such arrangement allows disc  158  to rotate about central pin  112  while remaining axially, centrally aligned with respect to central pin  112 , while remaining engaged with eccentrically rotating first driver disc  150 .  
         [0038]     Output disc  158  is centrally, axially aligned with output  118  and mates with output  118  so as to share the same rotational speed as output  118 . That is, output  118  and output disc  158  may simply be welded together along the union between output  118  and disc  158  to provide uniform rotation. Output disc  158  further contains bearing groove  164 . Bearing groove  164  runs along the outer circumference of disc  158  in ring-like fashion, and is of a concave, half-circle shape. Bearing groove  164  receives output disc bearings  166  and allows bearings  166  to rotate about an axis parallel to central pin  112 . Bearings  166  surround disc  158 , remaining loosely embedded within groove  164  so as to allow disc  158  to rotate freely with respect to radial cage  134  and radial cage support frame  132 . Importantly, second driver disc  150  and output disc  158  share the same rotational speed. That is, disc  150  and disc  158  have each been doubly reduced by virtue of the eccentric motion of flange  127  and eccentric flange  145 .  
         [0039]     Radial cage  134  and radial cage support frame surround the combination of discs mentioned above. Support frame  132  receives radial cage  134  and holds cage  134  fixed parallel to central pin  112 . Further, support frame  132  is engaged with input disc  126  and output disc  158  through bearings  130  and bearings  152  respectively. As mentioned, bearings  130  and  152  allow the combination of discs to rotate with respect to both support frame  132  and cage  134 .  
         [0040]     Although the invention has been described with reference to specific embodiments, this description is not meant to be construed in a limited sense. Various modifications of the disclosed embodiments, as well as alternative embodiments of the inventions will become apparent to persons skilled in the art upon reference to the description of the invention. It is, therefore, contemplated that the appended claims will cover such modifications that fall within the scope of the invention.