Patent Abstract:
A mechanical device includes a prime mover, and a number of rotating masses. Each mass is rotated simultaneously around centers of rotation in two or three planes that are at right angles to each other. The device includes one or more timing devices that are synchronized. The timing devices fix the relationship of the two simultaneous input rotations. In this device, internal energy creates an internal differential that is equalized by an external acceleration of the total mass, and internal energy is transferred to the exterior.

Full Description:
CROSS-REFERENCE TO RELATED APPLICATION 
       [0001]    This application is a continuation-in-part of PCT Application No. PCT/US2011/051782, filed on Sep. 15, 2011, the entire contents being incorporated by reference herein. This application also claims the benefit of U.S. Provisional Application No. 61/383,132 filed on Sep. 15, 2010, the entire contents being incorporated by reference herein. 
     
    
     BACKGROUND OF THE INVENTION 
       [0002]    The term “classical physics” in the context of Einstein&#39;s Theory of Special Relativity generally refers to Newtonian Physics, which generally includes the branches of physics developed prior to the development of relativity and quantum mechanics. In general, classical mechanics is based on Newton&#39;s Laws of Motion, which can be stated as follows:
       1. In the absence of a net force, a body is at rest or moves in a straight line with constant speed.   2. A body experience a force F experiences an acceleration that is related to F by F=ma, where m is the mass of the body. Alternatively, forces equal to the time derivative of momentum.   3. Whenever a first body exerts a first force F on a second body, the second body exerts a force −F on the first body. F and −F are equal in magnitude and opposite in direction.       
 
         [0006]    The “Theory of Relativity” (or “Relativity” by itself) generally refers to Albert Einstein&#39;s Theories of Special Relativity and General Relativity. Einstein&#39;s Theory of Special Relativity is often expressed in terms of mass-equivalents or E=mc 2 . According to the Principals of Relativistic Mechanics, the energy and momentum of an object with invariant mass M moving with a velocity v with respect to a given reference frame are given by: 
         [0000]        E=to γ mc 2  p=γ mv    
         [0000]    respectively.
 
Where γ (the Lorentz factor) is given by:
 
         [0000]    
       
         
           
             γ 
             = 
             
               
                 1 
                 
                   
                     1 
                     - 
                     
                       
                         ( 
                         
                           v 
                           / 
                           c 
                         
                         ) 
                       
                       2 
                     
                   
                 
               
               . 
             
           
         
       
     
         [0007]    The effects that are introduced by the theory of special relativity are wholly unfamiliar to human experience, and the theory itself has aspects that are in conflict with human logic. Yet, all the effects are real and can be measured. Our understanding of the dynamics that create these relativistic effects may be enhanced by a mechanical device that demonstrate the internal dynamics responsible for these effects. 
       BRIEF SUMMARY OF THE INVENTION 
       [0008]    A mechanical device consisting of a prime mover, and a number of rotating masses. Each mass is rotated simultaneously around centers of rotation in two or three planes that are at right angles to each other. Another part of the device consists of one or a number of timing devices that are all synchronized. These timing devices fix the relationship of the two simultaneous input rotations. One of these rotations has a variable angular velocity, the other can have a constant or variable velocity in a cycle of 360°. In the Lorentz equation γ=1/(1−(v/c) 2 ) 1/2 . The constant “c” is normally defined as the speed of light in this context. However, its meaning herein has been broadened, and c is defined herein to be “THE UNIT GOVERNING VELOCITY OF A DYNAMIC SYSTEM,” and represents the constant angular input velocity of a timing device according to the present invention. The Lorentz equation γ=1/1−(v/c) 2 ) 1/2  forms the mathematical basis for the timing device of the present invention, and (1 (v/c) 2 ) 1/2  is the cosine if v/c is defined as the sine of the angle that resides between the two vectors namely the hypotenuse and the cosine vector of a right angle triangle that occurs twice in one rotation of the timing device. The cosine of that angle is the inverse of a Lorentz factor. In a mechanical device the numerical magnitude of that factor is a result of the internal dimensional relationships. Special relativity uses the Lorentz factor to derive the relative mass or resisting force. External energy is transferred to the interior. In this device the opposite occurs, internal energy creates an internal differential that is equalized by an external acceleration of the total mass. Internal energy is transferred to the exterior. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0009]      FIG. 1  is a partially schematic elevational view of a device according to a first aspect of the invention; 
           [0010]      FIG. 1A  is a partially schematic elevational view of a device according to another aspect of the invention; 
           [0011]      FIG. 1B  is a partially schematic elevational view of a portion of the device of  FIG. 1A ; 
           [0012]      FIG. 2  is a schematic view of a single stage timing device utilized in the device of  FIG. 1 ; 
           [0013]      FIG. 3  is a partially schematic isometric view of a timing device at 0° and 360° positions; 
           [0014]      FIG. 4  is a partially schematic isometric view of the timing device of  FIG. 4  at a 180° position; 
           [0015]      FIG. 5  is a partially schematic of a mechanical version viewed along the Z-axis; 
           [0016]      FIG. 6  is a mechanical version viewed along the X axis; 
           [0017]      FIG. 7  is an isometric view of a three-ringed coupling; 
           [0018]      FIG. 8  is a relativistic curve a mass describes when subjected to a 45° relative angle of a single-stage timing device; 
           [0019]      FIG. 9  shows the relative dimensions and motions of the centers of rotation of the relativistic curve; 
           [0020]      FIG. 10  is the geometric and dynamic relation the mass is subjected to when it is at point E on the relativistic curve; and 
           [0021]      FIG. 11  is the geometric and dynamic relationships the mass is subjected to it is at point L. 
       
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
       [0022]    For purposes of description herein, the terms “upper,” “lower,” “right,” “left,” “rear” “front,” “vertical,” “horizontal,” and derivatives thereof shall relate to the invention as oriented in  FIG. 1 . However, it is to be understood that the invention may assume various alternative orientations and step sequences, except where expressly specified to the contrary. It is also to be understood that the specific devices and processes illustrated in the attached drawings and described in the following specification are simply exemplary embodiments of the inventive concepts defined in the appended claims. Hence, specific dimensions and other physical characteristics relating to the embodiments disclosed herein are not to be considered as limiting, unless the claims expressly state otherwise. 
         [0023]    A base relativistic unit may consist of two directional units, (one of these units is shown in  FIG. 1 ) one rotating clockwise and the other rotating counterclockwise. A directional unit consists of two mass units, one rotating clockwise and one counterclockwise. All rotations of all masses are timed the same by one or more timing devices. While it can be shown that the requirements of relativity can be satisfied with simultaneous input rotations of a mass in two planes and a timing device, the possibility of providing a third simultaneous input rotation is not excluded. 
         [0024]    With reference to  FIG. 1 , a directional unit according to one aspect of the present invention includes a frame  11  having an upper portion  12  and a lower portion  13  that are structurally interconnected as shown schematically by dashed line  14 . A first shaft  15  is rotatably mounted to the lower portion  13  of frame  11  by a bracket  16  and ball bearings  17 . The first shaft  15  is operably interconnected, by shafts and gears to a power source  18 . Power source  18  may comprise an electric motor or other device having a rotating output shaft  19  that is operably interconnected to the first shaft  15 . A second shaft  20  is rotatably mounted to the lower portion  13  of frame  11  for rotation about a vertical axis  25 . As discussed in more detail below, vertical axis  25  comprises the primary center of rotation of directional unit  10 . In the illustrated example, the second shaft  20  is rotatably mounted to lower portion  13  of frame  11  by ball bearings  21 , and the second shaft  20  is operably interconnected with first shaft  15  by gears  22  and  23 , such that powered rotation of first shaft  15  results in rotation of second shaft  20  about vertical axis  25 . 
         [0025]    A primary rotor  30  includes a rigid upper structure  31 , a lower rigid structure  32 , and one or more vertically extending rigid interconnecting structures  33 . The lower structure  32  is rotatably interconnected with second shaft  20  by ball bearings  34 , and upper structure  31  is rotatably interconnected with upper portion  12  of frame  11  by a pin or shaft  35  and ball bearings  34 . Thus, primary rotor  30  rotates about vertical axis  25  relative to frame  11 , as shown by the arrow  36 . 
         [0026]    Directional unit  10  also includes a vertical shaft  40  that is rotatably interconnected to upper structure  31  of primary rotor  30  by a ball bearing  41 . The vertical shaft  40  is rotatably interconnected to interconnecting structure  33  of primary rotor  30  by a bracket  42  and ball bearing  43 . Thus, shaft  40  rotates relative to primary rotor  30  about a vertical axis  45 . Vertical axis  45 , in turn, rotates about vertical axis  25  as primary rotor  30  rotates relatively to frame  11 . 
         [0027]    Vertical shaft  40  is operably interconnected with second shaft  20  by a three-ring coupler or coupling  50 . With further reference to  FIG. 7 , three-ring coupler  50  includes input/output shafts/connectors  51  and  52  that are operably connected by rings  53 ,  54 , and  55 . Shaft  51  is rigidly interconnected to ring  53  and shaft  52  is rigidly interconnected to ring  55 . Ring  53  is operably interconnected with ring  54  by arms  56 - 58 . Each arm  56 - 58  has opposite ends that are pivotally interconnected with rings  53  and  54 . Ring  54  is interconnected to ring  55  by arms  59 - 61  in a similar manner. Due to the manner in which the rings  53 - 55  are interconnected by the arms  56 - 61 , shafts  51  and  52  must rotate at the same angle or velocity and torque transmitted to either shaft  51  or  52  is transmitted to the other of the two shafts  51  and  52 . Shaft  51  rotates about an axis  62  that is parallel to an axis  63  about which shaft  52  rotates. In general, the axes  62  and  63  may be offset by a distance or dimension  65  that is normal to the axes  62  and  63 . The distance  65  may vary depending upon the positions of the rings  53 - 55 . Various three-ring couplers utilizing the same general configuration as the three-ring coupler  50  shown in  FIG. 7  are known in the prior art, such that further details concerning the three-ring coupler  50  are not believed to be required. 
         [0028]    Referring again to  FIG. 1 , shaft  52  of three-ring coupler  50  is fixed to second shaft  20 , and shaft  51  of three-ring coupler  50  is fixed to vertical shaft  40 . Thus, vertical shaft  40  rotates at the same angular velocity as second shaft  20 . A gear  68  is fixed to vertical shaft  40  and meshingly engages a gear  69  to thereby cause gear  69  to rotate about an axis  70 . Similarly, a gear  72  is fixed to shaft  40 , and drives a gear  73  for rotation about an axis  74 . The axes  70  and  74  are normal to the axis  45  of shaft  40 . A mass  76  is connected to axis/shaft  70  by an arm  77 , such that it rotates as shown by circle  80 . Similarly, a mass  78  is connected to axis/shaft  74  by an arm  79  and rotates as shown by circle  81 . 
         [0029]    A shaft  85  is also operably connected to power source  18  to provide rotation to shaft  85 . Shaft  85  is operably interconnected to shaft  35  by a timing device  90 . So the relationship of a certain differential in angular velocities, between shaft  35  and shaft  15 , are always maintained. The location of the timing device shown in  FIG. 1  is one of the possible locations. It could also be located on the frame near the power source and serve two or more directional units  10 . With further reference to  FIGS. 3 and 4 , timing device  90  includes an input shaft  91  that is rigidly connected to a first arm  92 . An output shaft  93  is rigidly connected to a second arm  94  having an elongated slot  95 . Slot  95  may be linear, or it may be curved or be wave-like in order to influence the angular velocity of the mass in a particular plane at certain areas of its path. A pin or shaft  96  is rigidly connected to first arm  92 , and a roller  97  is mounted on pin  96  for reciprocating motion within slot  95  of arm  94 . When the output shaft  93  is at 0° or 360° relative to input shaft  91 , the timing device  90  is oriented as shown in  FIG. 3 . The movement of roller  97  in slot  95  is shown by the arrow  98 . 
         [0030]    With further reference to  FIG. 2 , AV 1  is the input angular velocity, and it has a constant angular velocity. AV 2  is a constantly changing angular velocity within a cycle of 360°. It will be understood that there is no “start” of a cycle, just as there is no “start” to a circle. The maximum angle differential that occurs between arm C and A ( FIG. 2 ) is the relativistic angle of the unit and it occurs when the angle δ=90° or 270°. These are the only points in time in each cycle of 360° where AV 1 =AV 2 . The maximum differential between the angular velocities AV 1  and AV 2  occurs when δ=180° and β=0°. Both arms A and C ( FIG. 2 ) (arms  92  and  94  in  FIGS. 3 and 4 ) are angularly aligned at 180° and at δ=0° and 360°. 
         [0031]    In  FIG. 2 ,  100  designates the configuration of the device  90  as shown in  FIGS. 3 , and  101  designates the configuration shown in  FIG. 4. 102  designates a first intermediate position that is between the configurations of  FIGS. 3 and 4  (i.e., between 0° and 180°), and  103  designates a second configuration that is also between the configurations of  FIGS. 3 and 4  (i.e., between 180° and 360°). 
         [0032]    A timing device  90  may be used for each of the two simultaneous input rotations. AV 1  of the top timing device constitutes the “unit governing velocity.” As shown in  FIG. 1 , one of the two rotations of the masses  76  and  78  describing circles  80  and  81  is operably interconnected to shaft  15 , and shaft  35  is operably interconnected to rotate the Masses  76  and  78  with the rotor around axis  25 . 
         [0033]    Masses  76  and  78  rotate in opposite directions ( FIG. 1 ). In the illustrated example, mass  76  rotates in a clockwise direction, and mass  78  rotates in a counterclockwise direction. However, the direction of rotation of masses  76  and  78  could be switched, such that mass  78  rotates in a clockwise direction, and mass  76  rotates in a counterclockwise direction. Mass  76 , arm  77 , and associated structure interconnecting the first mass  76  to the vertical shaft  40  comprise a first mass unit, and the second mass  78  and associated arm  79  and other components comprise a second mass unit  84 . The multiplicity of the masses serves only one of two basic purposes, to neutralize forces in a certain axis by complimentary interference or increases the frequency of the impulse if connected sequentially. The operation of the mass units  82  and  84  will now be described in more detail in connection with  FIGS. 5 and 6 . 
         [0034]    The mass units  82  and  84  of  FIG. 1  are shown schematically in  FIGS. 6  (X-Y Plane) and  7  (Y-Z Plane). Mass units  82  and  84  are substantially the same in operation (other than the direction of rotation of the mass), such that only mass unit  82  is described in detail in connection with  FIGS. 5 and 6 . In  FIGS. 5 and 6 , a link  105  is rotatably mounted for rotation about a primary axis or center of rotation  25 . This rotation is the same as AV 2  of the timing device  90  shown in  FIG. 2 . The link  105  of  FIGS. 5 and 6  also corresponds to the primary rotor  30 , including upper and lower structures  31  and  32  shown in  FIG. 1 . In  FIGS. 5 and 6  the mass center and arm  77  are provided with the angular velocity of AV 1 . The mass center of rotation at 180° is designated  45 A in  FIG. 6 , and the mass center of rotation at 0° and 360° is designated  45  in  FIG. 6 . Thus, it will be understood that the mass unit  82  of  FIGS. 5 and 6  is a somewhat simplified representation of the mass unit utilized to illustrate the operation of the mass units  82  and  84 . 
         [0035]    As shown in  FIGS. 5 and 6 , when the mass  76  is at 0° and 360° relative to axes  45  and  25 , the arm  77  is positioned in a “−Y” direction and the distance between primary center  25  and mass  76  equals I+sin α. It will be understood that the angle α is always the same angle in the triangle in the timing device and in the mechanical device described herein. As discussed herein, the angle α is determined by the Lorentz factor. However, as the link  105  rotates about the primary axis or center of rotation  25  (Z axis), the mass moves to the position designated  76 A when the mass  76  is at 180° relative to the axis  45  and its relative distance is only 1−sin α to the primary center  25 . The relative frequency to 1 that results when the mass  76  is at 180° is (1/(1−sin α))/(1+sin α) and relative to the opposite side the relative frequency is: 
         [0000]      ((1/(1−sin α))/(1+sin α)) 1/2 =1/cos α
 
         [0036]    If v/c of the Lorentz equation 1/((1−(v/c) 2 ) 1/2  is sin α then ((1 (v/c) 2 ) 1/2 =cos α. The Lorentz factor that is used for relative mass in special relativity and the relative frequency factor of the device coincide when the relationships are the same. A relativistic device always features a relative unity and that unity can adopt any value, from one to infinity. However, the velocity it adopts can never be exceeded by any other velocity of a mass within that system. Also the relativistic factor 1/cos α once established is not influenced by velocity. 
         [0037]      FIGS. 5 and 6  show that the instantaneous centrifugal forces at the opposite 180° positions from the two simultaneous rotations in separate planes 90° from each other are complimentary constructive in one direction (direction 0°) and complimentary destructive in the other direction (direction 180°) relative to the primary center  25 . It will be understood that  FIGS. 5 and 6  are not intended to be conclusive with respect to the sum of all directional forces during the time of a complete cycle or one rotation nor is it intended to be conclusive as to the direction or magnitude of the total force differential. It is merely an indicator that a differential exists. A graphical representation concerning what occurs during a complete cycle is shown in  FIG. 8 , as discussed below. 
         [0038]      FIG. 8  shows a relativistic curve of a 45° relative angle α, where α is the maximum angular differential of the two rotations of the timing device. The relative angular velocity AV 1  was selected for rotation of the masses  76  and  78  describing circles  80  and  81  ( FIG. 1 ). 
         [0039]    The distances between points F &amp; D and D &amp; G define a relative frequency of the device=(1/FD)/DG, and the effective relative frequency is I/cos α=√(1/FD)/DG=√(1/(1−sin α))*(1/(1+sin α)). T is the time center that is used in order to project the influence of the timing device on the path of the mass.  FIG. 8  shows the path a mass  76  or  78  has to follow when subjected to the physical constraints of a single-stage timing device  90  (see also  FIG. 1 ). The path of the mass  110  as seen in the X-Y plane is shown in  FIG. 8  by the curved line that passes through the points G, E, C, F, C 1 , E 1 , back to G. The relativistic curve shown in  FIG. 8  occurs when the primary rotation has a variable angular velocity. T is the center of the time circle and the driver of the total system. 
         [0040]    Referring again to  FIG. 8 , the “normal” look of the egg-shaped circle  110  is, in a sense, very misleading. The circle  110  actually consists of four individual curves  111 ,  112 ,  113 ,  114  each with its own relative radius (distance) and relative frequency (angular velocity). There are two small transition areas just after position C and before position C′. (Going clockwise on the relativistic curve on  FIG. 11 ) The path of the mass encompasses 360°, but if the degrees of all the individual centers of rotation are added up, they seem to total 450°, the additional 90° or 45° per side are due to the relativistic differential effect. The 450° is really a mirage, purely created by the additional 45° motion at position C by the radial vector shown as member  77  in  FIG. 5 . 
         [0041]    Two of the four curves  113  and  114  have the same radius and frequency. The centers of these four individual rotations are located in empty space. Their curves are formed by a projection from the two simultaneous motions of the mass in three planes. None of these virtual centers of rotation coincides with the real centers of rotation D and m in time (the real center of rotation m is a moving center and rotates around center D). These virtual centers of rotation seem to instantaneously move from one position to another, exerting no force whatsoever on the mass due to that motion. (Motion in zero time) Therefore there is no change in energy or velocity of the mass due to the change in radius, but the frequency will change inversely proportionally to the change in radius. Normally it would be expected that the frequency would increase inversely proportional to the square of the relative distance. This is the case when the mass moves towards the center of rotation. However, the difference here is that the center of rotation moves towards or away from the mass. 
         [0042]      FIG. 9  shows the relative dimensions and motions of the centers of rotation of the relativistic curves segments and the relative motion of the mass. T is the center of the time circle that is the driver of the system, through the timing device and represents its relative unity, with a radius of 1 and a frequency of 1 and a mass of 1. As the mass travels from G to F on the relativistic curve the following motions are in evidence: 
         [0043]    The center T of rotation, moves instantaneously to position M′ changing the radius from 1 to 0.707 and the frequency from 1 to 1.414, but not effecting the tangential velocity of the mass. 
         [0044]    It must be understood, that for purposes of simplicity, the following representation has been idealized. The mass therefore has the following properties as it moves from G to E. All quantities are relative to 1: 
         [0045]    The radius=0.707 
         [0046]    The frequency=1.414 
         [0047]    The time=1/1.414=0.707 
         [0048]    The tangential velocity=1 
         [0049]    The radial force=1 2 /0.707=1.414 
         [0050]    The directional velocity in the +y direction at point E=I×0.707=0.707 
         [0051]    The average −y directional force=1.414×0.707×4/π=1.2732 
         [0052]    The relative directional −y momentum=1.2732×0.707=0.9 
         [0053]    The center M′ of rotation of curve  111  moves instantaneously to position K, changing the radius from 0.707 to 1.06 and the frequency to (0.707/1.06) 1.414=0.943, but not effecting the tangential velocity. 
         [0054]    Part of the action occurs after the rotation in the z-y plane when member  77  of  FIG. 5  completes 90° from position 0°. At that point member  105  on  FIG. 5  has only completed 54.735, therefore the mass is still accelerating radially towards the primary center D, in the +y direction due to the tangential velocity, but starting to decelerate in the same direction due to the rotation in the z-y plane that is now past 90°. Acceleration and deceleration have become complimentary destructive until the rotation in the x-y plane has reached 90° and that is the same position as position C in  FIG. 9 . Due to the reduction in the radial force the mass slowed down tangentially and directionally and reduced its frequency. This reduction in velocity and frequency is in evidence at point C. With further reference to  FIG. 9 . The center K of the rotation of curve  113  moves instantaneously to position N and the mass displays the following relative properties at C: 
         [0055]    The radius=0.5 
         [0056]    The tangential frequency for the upper curvex=0.943×1.06/0.5=2 
         [0057]    The +y directional velocity at C=0.5 
         [0058]    The +x directional velocity at C=0.5 
         [0059]    The tangential velocity of the mass at C=(0.5 2 +0.5 2 )½=0.707 
         [0000]    With further reference to  FIG. 9  and the geometry of the relativistic curve  FIG. 11 , the center of rotation N moves to Point H at the same time the mass moves from point C to point L. The motions were parallel to each other and there was no effect on the frequency or velocity of the mass, it constitutes a transition. In the curvature  112  forces from the radial and tangential rotation are complimentary destructive. This is responsible for the relativistic effect. 
         [0060]    Properties of the xy Side, as the Mass Moves from Point L to Point F 
         [0061]    The radius=0.5 
         [0062]    The frequency=2 
         [0063]    The time=0.5 
         [0064]    The effective tangential velocity=0.707 
         [0065]    The radial force=0.707 2 /0.5=1 
         [0066]    The +y relative momentum=1×0.5+0.207=0.707 The above numbers are effective numbers since the +y velocity that enters at point C is the only velocity that can be translated. See geometric mechanical calculation on  FIG. 10 . 
         [0067]    Since the effective arc in the −y and the +y direction are both 45° from G to E and from L to F, the adjustment for the directionality factor of 0.9 of the radial force does not have to be accounted for in the relativistic calculation or number. But will have to be taken into account when the relative numbers are converted into real numbers by giving the unit real size, mass and frequency. Therefore, 
         [0068]    The relative +y force=1 
         [0069]    The relative +y directional momentum=1×0.707=0.707 
         [0070]    The relative −y directional momentum=0.707×1.414=−1.000 
         [0071]    The directional relative momentum differential is −0.293 This internal differential is opposed by the total mass of the unit and the mass it is attached to, providing an acceleration for the assembly. The relativistic or Lorentz factor is 1/0.707=1.414 
         [0072]    The purpose of this numerical example is to illustrate that all the relativistic properties have been successfully incorporated into a mechanical device and are all in total agreement with those obtained by special relativity, when both have the same velocity relationships. It further demonstrates that a relativistic propulsion device can be designed to meet a specific need just like any other mechanical device. 
         [0073]    However it is to be understood that the invention may assume various alternative combinations and proportionalities in addition to those already mentioned as follows: 
         [0074]    A third input could be added in the third plane that would not change the concept of the basic system but might be helpful in optimizing its results. 
         [0075]    Four different combinations of rotation and distances are possible resulting in four families of relativistic curves. One relativistic curve of the first family has been shown and described in detail. Since all follow the same process, the general description of the others below should be considered sufficient. 
         [0076]    Family 1 
         [0077]    a) Relationships of angular velocities: 
         [0078]    Mass center of rotation m constant. Primary center of rotation D variable. 
         [0079]    b) Relationship of distances: 
         [0080]    Distance between centers of rotation relative unity 1. Radius of gyration of mass around mass center of rotation relative sin α, (relative to 1) 
         [0081]    Family 2 
         [0082]    a) Relationship of angular velocities: 
         [0083]    Mass center of rotation m variable. Primary center of rotation D constant. 
         [0084]    b) Same as FAMILY 1. 
         [0085]    Family 3 
         [0086]    a) Same as FAMILY 1. 
         [0087]    b) Relationship of distances: 
         [0088]    Distances between centers of rotation relative sin α. Radius of gyration of the mass around the mass center of rotation unity 1. 
         [0089]    Family 4 
         [0090]    a) Same as FAMILY 2. 
         [0091]    b) Same as FAMILY 3. 
         [0092]    In devices where masses rotate in three planes, the mechanical combination of relationships are the same, but there are more possible combinations since three rotations are combined with three distances. Not all combinations are necessarily used for practical exploitation, but all are useful for scientific and research purposes. 
         [0093]    With reference to  FIGS. 1A and 1B , a directional unit  10 A according to another aspect of the present invention, includes a frame having upper portions  12 A and  12 B and lower portions  13 A and  14 A. These are structurally interconnected as shown schematically by the dashed line  15 A. A first shaft  16 A is rotatably mounted to the lower frame portion  14 A by ball bearings  17 A and  19 A. The first shaft  16 A is operably connected to a power source  18 A. Power source  18 A may comprise an electric motor or other device having a rotating output that is operably connected to shaft  16 A. A miter gear  21 A is keyed to the top of shaft  16 A and forms the lower gear of the differential assembly  20 A. The operation of the differential assembly  20 A is substantially similar to differential assembly  20  described above. Shaft  16 A is located on the vertical axis  25 A that comprises the primary center of rotation of the directional unit  10 A. 
         [0094]    A primary rotor assembly  30 A includes vertical struts  31 A and  32 A that are joined by top plate  33 A and lower plate  34 A. To lower plate  34 A is fastened a tubular extension  35 A that extends into gear assembly  50 A. To the top plate  33 A is fastened shaft  36 A that is operably connected to the output angular velocity of the timing device  90 A. The operation of the timing device  90 A is substantially the same as timing device  90  described above. Unit  10 A includes four horizontal members  37 A,  38 A,  39 A, and  40 A. Horizontal members  37 A and  38 A support mass unit  82 A, and are rotated by the timing belt system  60 A. Horizontal members  39 A and  40 A support mass unit  84 A that is rotated by timing belt system  61 A. The mass unit  84 A and timing belt system  61 A are substantially the same as the corresponding components described above. 
         [0095]    A shaft  85 A is also connected to power source  18 A to provide rotation to shaft  85 A. Shaft  85 A is operably interconnected to shaft  36 A by a timing device  90 A. Thus, the relationship of a certain differential in angular velocities, between shaft  36 A and shaft  16 A, are always maintained at any given time in a rotation of 360°, regardless of the angular velocity of the power source. 
         [0096]    If the timing device  90 A is used for two simultaneous rotations in two planes as shown in  FIG. 1A , one of the two rotations of the masses  76 A and  78 A describing circles  80 A and  81 A is connected to the angular velocity of AV 1  and the rotation to AV 2 . Masses  76 A and  78 A rotate around axis  25 A. 
         [0097]    Masses  76 A and  78 A rotate in opposite directions. In the illustrated example, mass  76 A rotates in a clockwise direction, and mass  78 A rotates in a counterclockwise direction. However, the direction of rotation of masses  76 A and  78 A could be switched, such that mass  78 A rotates in a clockwise direction, and mass  76 A rotates in a counterclockwise direction. Mass  76 A, arm  77 A, and associated components comprise the first mass unit  82 A, and the second mass  78 A and associated arm  79 A and other components comprise a second mass unit  84 A. The multiplicity of the masses serves only one of two basic purposes, namely to neutralize forces in a certain axis by complimentary interference, or to increase the frequency of the impulse if connected sequentially. 
         [0098]    Referring again to  FIG. 1A , shaft  36 A of the primary rotor assembly  30 A is operably connected to the timing device  90 A. The primary rotor assembly  30 A rotates about axis  25 A with a constant variable angular velocity (AV 2 ). Shaft  36 A is rotatably supported by bearing  41 A, in upper frame portion  12 A, and bearings  42 A and  43 A in lower frame portion  13 A. Gear  51 A, is mounted on the tubular extension  35 A of the primary rotor assembly  30 A and meshes with gear  52 A that is mounted on shaft  53 A. 
         [0099]    The gear ratio between gear  51 A and  52 A is selected such that shaft  53 A rotates at ½ the angular velocity of the primary rotor assembly  30 A in bearings  54 A,  55 A in lower frame portion  13 A. Gear  56 A is mounted on shaft  53 A and meshes with gear  57 A with a gear ratio of 1 to 1. Gear  57 A is rotatably mounted with bearing  58 A on tubular extension  35 A. The differential U frame  22 A of the differential assembly  20 A is rigidly fastened to gear  57 A and rotates at ½ of the angular velocity in the same direction as the primary rotor assembly  30 A. The differential U frame  22 A is provided with a shaft  23 A rotatably mounted in bearings  24 A and  26 A. Miter gear  27 A is mounted on one side of shaft  23 A and meshes with miter gears  21 A and  28 A. Gear  28 A is mounted on shaft  44 A that resides in the tubular extension  35 A and is rotatably mounted on the lower end with bearing  59 A located in the differential U frame  22 A and at the upper end in bearing  45 A located in lower plate  34 A of the primary rotor assembly  30 A. A counter weight  29 A is also mounted on shaft  23 A with clearance provided between it and gears  21 A and  28 A to balance the differential U frame assembly. 
         [0100]    It will be understood that miter gear  27 A will have an angular velocity of ½ the angular velocity of the primary rotor  30 A plus the angular input velocity of shaft  16 A. Miter gear  28 A and shaft  44 A will then have an angular velocity of miter gear  27 A plus the angular velocity of the differential U frame  22 A or the angular velocity of the primary rotor  30 A plus the angular velocity of the shaft  16 A. 
         [0101]    Referring again to  FIG. 1B , at the top end of shaft  44 A is mounted miter gear  46 A that meshes with miter gears  47 A and  48 A. Miter gear  47 A is mounted on shaft  62 A that is rotatably mounted in strut  31 A of the primary rotor  30 A with bearings  63 A and  63 B. Miter gear  48 A is mounted on shaft  64 A that is rotatably mounted in strut  32 A of the primary rotor  30 A with bearings  65 A and  6 B. Since miter gears  47 A and  48 A with their shafts  62 A and  64 A, respectively, rotate also with the primary rotor  30 A around axis  25 A, the angular velocities of miter gears  47 A and  48 A and their respective shafts around their own axes is the angular velocity of miter gear  28 A minus the angular velocity of the primary rotor  30 A and therefore is the same as that of shaft  16 A. 
         [0102]    As shown in  FIG. 1B , timing belt pulleys  66 A and  67 A are mounted on shafts  62 A and  64 A respectively. Pulley  66 A drives timing belt  68 A and pulley  67 A drives timing belt  73 A. Timing belt  68 A drives mass unit  82 A via pulley  75 A mounted on shaft  70 A. Shaft  70 A is rotatably supported by horizontal members  37 A and  38 A with bearings  70 B,  70 C,  70 D, and  70 E. Mass arm  77 A (see  FIG. 1A ) supports mass  76 A and is rigidly mounted to shaft  70 A. Mass arm  77 A supports mass  76 A and is rigidly mounted to shaft  70 A. Similarly, shaft  74 A is rotatably supported by horizontal members  39 A and  40 A with bearings  74 B,  74 C,  74 D, and  74 E. Mass arm  79 A supports mass  78 A and is rigidly mounted to shaft  74 A. 
         [0103]    Accordingly, it will be understood that the masses rotate simultaneously in two planes, in one plane with the variable angular velocity of shaft  36 A of the primary rotor and in the other plane with the angular velocity of input shaft  16 A.

Technology Classification (CPC): 5