Abstract:
Device and method embodiments for a rotation powered vehicle are described, the rotation powered vehicle being capable of converting a rotational motion of a platform pivotally secured to the rotation powered vehicle in either of two angular directions into a linear motion of the rotation powered vehicle in a single linear direction for the purposes of conveyance. In some cases, the angular motion of the platform may be slight when compared to the resultant linear powered stroke of the rotation powered vehicle.

Description:
REFERENCE TO RELATED APPLICATIONS 
     This application claims priority of U.S. provisional application Ser. No. 61/789,462 filed on 15 Mar. 2013 the disclosure of which is incorporated herein by reference. 
    
    
     BACKGROUND 
     There are a variety of power methods and devices for the purposes of providing a motive force to skateboards. These methods may include but are not limited to gas power via a gasoline engine attached to the skateboard and electric motors attached to the skateboard. These methods are convenient for a rider of the board but are damaging to the environment. Other “human” power methods may include skateboards that use a “serpentine” motion of the board in order to provide a motive force, or a rider of the skateboard may simply “kick” themselves along by dropping one foot to the ground while riding the board. These human powered methods are less convenient for a rider of the skateboard. Finally, some scooter designs rely on the rotation of the board a rider stands on in one direction in order to provide power to the wheels. These scooter designs require the board to be rotated through a very large angle with respect to the ground, thus requiring that a scooter handle be in place for the rider to hold onto. These scooter designs also only power the scooter when the board rotates in one direction. What have been needed are devices and methods which provide environmentally sound strategies such as mechanical or hydraulic drive mechanisms which are configured to power the board efficiently over long distances with a minimum effort from the rider. Further, the board must be configured such that a rider of the board can easily and intuitively steer it. 
     SUMMARY 
     Some embodiments are directed at a rotation powered vehicle, the rotation powered vehicle may include a rigid chassis having a plurality of axles secured to the chassis. The rotation powered vehicle may also include a plurality of wheels which may be secured to the axles. The rotation powered vehicle may also include a rigid platform which is pivotally secured to the chassis, with the rigid platform being capable of rotating in a first angular direction or in a second angular direction with respect to the chassis. The rotation powered vehicle may also include a first drive mechanism which is configured to convert a rotational motion of the platform in the first angular direction into a translational motion of the rotation powered board in a first linear direction. The rotation powered board may also include a second drive mechanism which is configured to convert a rotational motion of the platform in the second angular direction into a translational motion of the rotation powered board in a first linear direction. 
     Some embodiments are directed at methods for propelling a rotation powered vehicle. The methods may include performing a first half power cycle by rotating a rigid platform which is pivotally secured to a chassis in a first angular direction thereby activating a first drive mechanism which is configured to convert a rotational motion of the platform in the first angular direction into a rotational motion of a plurality of wheels in the first angular direction, the wheels being engaged to a plurality of axles which are secured to the chassis. The rotational motion of the plurality of wheels in the first angular direction results in a translational motion of the rotation powered vehicle in a first linear direction. The methods may also include performing a second half power cycle by rotating the rigid platform which is pivotally secured to the chassis in a second angular direction thereby activating a second drive mechanism which is configured to convert a rotational motion of the platform in the second angular direction into a rotational motion of a plurality of the wheels in the first angular direction, with the wheels being engaged to a plurality of the axles which are secured to the chassis. Again the rotational motion of the plurality of wheels in the first angular direction results in a translational motion of the rotation powered vehicle in a first linear direction. 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         FIGS. 1 and 2  are different views of an embodiment of a rotation powered vehicle having multiple screw turbines. 
         FIGS. 3 and 4  depict the rotation powered vehicle of  FIG. 1  undergoing a rotation in a third angular direction. 
         FIGS. 5 and 6  depict the rotation powered vehicle of  FIG. 1  undergoing a rotation in a fourth angular direction. 
         FIG. 7  depicts different standing positions on the rotation powered vehicle of  FIG. 1  with a platform of the rotation powered vehicle in a neutral position. 
         FIG. 8  depicts the rotation powered vehicle of  FIG. 1  undergoing a first half power cycle as the platform rotates in a first angular direction. 
         FIG. 9  depicts the rotation powered vehicle of  FIG. 1  undergoing a second half power cycle as the platform rotates in a second angular direction. 
         FIG. 10  is a cross sectional view of a pressure chamber and a piston with a variable volume within the pressure chamber created by the pressure chamber and piston 
         FIG. 11  is a cross section view of a pressure chamber, a piston, and a flexible bladder disposed within a variable volume created by the pressure chamber and piston. 
         FIG. 12  depicts a screw turbine assembly with a turbine body shown in section view. 
         FIG. 13  is a schematic of the fluid routing for a screw drive turbine powered embodiment of a rotation powered vehicle. 
         FIG. 14  is a flowchart which depicts a first power cycle and a second power cycle for some turbine powered embodiments of a rotation powered vehicle. 
         FIG. 15  depicts an embodiment of a rotation powered vehicle with a dual direction plunger drive system. 
         FIG. 16  depicts a dual direction plunger drive embodiment. 
         FIG. 17  depicts the dual direction plunger drive embodiment of  FIG. 16  with a turbine body shown in cross section such that a plunger and a screw drive are visible. 
         FIG. 18  depicts a cross section of the turbine body of  FIG. 16  showing slots which guide the plunger shown in  FIG. 17 . 
         FIGS. 19-21  depict a half power cycle carried out by the dual direction plunger drive of  FIG. 16 . 
         FIG. 22  is a schematic of the fluid routing for a screw drive turbine powered embodiment of a rotation powered vehicle. 
         FIG. 23  depicts an embodiment of a rotation powered vehicle which incorporates multiple cross flow turbine drives. 
         FIGS. 24 and 25  show sectional views of one of the cross flow turbines of the rotation powered vehicle embodiment of  FIG. 23 . 
         FIG. 26  is a schematic of the fluid routing for a cross flow turbine powered embodiment of a rotation powered vehicle. 
         FIGS. 27-29  depict an embodiment of a rotation powered vehicle which incorporates multiple Tessla drives. 
         FIG. 30  depicts a sectional view of a Tessla turbine drive of the embodiment of a rotation powered vehicle of  FIG. 27 . 
         FIG. 31  depicts a Tessla turbine blade. 
         FIG. 32  depicts a sectional view of a Tessla turbine drive of the embodiment of a rotation powered vehicle of  FIG. 27 . 
         FIG. 33  is a schematic of the fluid routing for a Tessla turbine powered embodiment of a rotation powered vehicle. 
         FIGS. 34-37  depict a Tessla turbine embodiment with a magnetic clutch. 
         FIGS. 38-42  depict a rotation powered vehicle embodiment which incorporates a hydraulic rack and pinion drive. 
         FIG. 43  depicts the rotation powered vehicle of  FIG. 38  undergoing a first power cycle. 
         FIG. 44  depicts a pressure chamber and a drive chamber with a fluid being transferred from the pressure chamber to the drive chamber. 
         FIG. 45  depicts the rotation powered vehicle of  FIG. 38  undergoing a first power cycle. 
         FIG. 46  depicts a rack operatively engaged with a gear, both of the rotation powered vehicle embodiment of  FIG. 38 . 
         FIGS. 47 and 48  depict the rotation powered vehicle embodiment of  FIG. 38  undergoing a second power cycle. 
         FIG. 49  depicts a pressure chamber and a drive chamber with a fluid being transferred from a flexible bladder disposed within the pressure chamber and to a flexible bladder disposed within the drive chamber. 
         FIG. 50  is a flowchart which depicts a first power cycle and a second power cycle for the rotation powered vehicle embodiment of  FIG. 38 . 
         FIGS. 51-54  depict a rotation powered vehicle embodiment having a mechanical drive mechanism. 
         FIGS. 55-57  depict the rotation powered vehicle embodiment of  FIG. 51  undergoing a first power cycle. 
         FIG. 58  a rack operatively engaged with a gear, both of rotation powered vehicle embodiment of  FIG. 51 . 
         FIGS. 59 and 60  show a rack and a portion of a chassis, and the rack slidably disposed on the portion of the chassis respectively. 
         FIGS. 61 and 62  depict the rotation powered vehicle embodiment of  FIG. 51  undergoing a second power cycle. 
         FIG. 63  is a flowchart which depicts the a first power cycle and a second power cycle for the powered vehicle embodiment of  FIG. 51 . 
     
    
    
     DETAILED DESCRIPTION 
     Device and methods for a rotation powered vehicle are described, the rotation powered vehicle may have a platform which is pivotally attached to a chassis. Performing a rotational motion of the platform with respect to the chassis in either of two angular directions will result in the propulsion of the rotation powered vehicle in a single linear direction. The conversion of a rotational motion of the platform in either of two directions into a linear motion of the rotation powered vehicle in a single direction may be accomplished using multiple drive mechanisms, which may utilize hydraulic or mechanical methods and devices to accomplish the conversion. 
     Some embodiments are directed at a rotation powered vehicle on which a rider can propel themselves by rotating a platform on which they stand in either of two angular directions. The platform may be pivotally secured to chassis which may have a plurality of axles and a plurality of wheels which are secured to the axles. It is important that the rotational motion of the platform be small such that a rider of the rotation powered vehicle may comfortably stand on the platform and maintain their balance as they rotate the platform with their feet. 
     It is also important that the small rotational motion of the platform be translated into a large linear motion of the rotation powered vehicle. Two drive mechanisms are required to convert the rotational motion of the platform into a linear motion of the vehicle. Each drive mechanism takes a small rotational motion of the platform and converts it into a larger linear motion of the vehicle. One drive mechanism will convert a rotational motion of the platform in a first angular direction into a translational motion of the vehicle in a first linear direction, and the second drive mechanism will convert a rotational motion of the platform in a second angular direction into a translational motion of the vehicle in the first linear direction 
     Some embodiments of the rotation powered vehicle may be powered by a series of power cycles. Each power cycle may consist of a first half power cycle wherein the platform is rotated in the first angular direction which activates the first drive mechanism and which moves the rotation powered board in the first linear direction. The first half power cycle may be followed by a second half power cycle wherein the platform is rotated in the second angular direction which activates the second drive mechanism and which moves the rotation powered board in the first linear direction. 
     Some embodiments of the rotation powered vehicle may also allow for the steering of the vehicle through the rotation of the platform in third and fourth angular directions. Thus a rider of the rotation powered vehicle can propel the vehicle by rotating the platform in either of two angular directions both of which are in a plane which is perpendicular to the surface of the platform and which is parallel to the direction of travel. A rider of the rotation powered vehicle may then steer the board in either of two additional angular directions both of which are in a plane which is perpendicular to the surface of the platform and which is perpendicular to the direction of travel. 
     Such embodiments of the rotation powered vehicle will provide a rider of the vehicle with a more “natural” riding experience. That is to say riding the rotation powered vehicle will be very similar to surfing wherein a rider of a surfboard leans the board in either of two angular directions both of which are in a plane which is perpendicular to the surface of the board and which is perpendicular to the direction of travel in order to steer the board. Additionally, a rider of a surfboard may bounce up and down on the board in order to propel the board forward. This is a technique which surfers refer to as “pumping” the surfboard. This “pumping” motion is similar to the rotational motions of the rotation powered vehicle which propel it forward. 
     For some embodiments of the rotation powered vehicle, the midpoint of the platform with respect to the direction of travel may be secured close to the midpoint of the chassis. This allows for a rider of the rotation powered vehicle to alter the power of a power cycle by altering where their feet are on the platform in relation to the midpoint of the platform. A rider standing on with their feet spread apart along the axis of motion will have their feet positioned at points far from the midpoint of the platform and will thus generate a larger rotational moment (resulting in more power transferred to the drive mechanisms) about the midpoint of the platform. A rider standing on with their feet close together along the axis of motion will have their feet positioned at points close to the midpoint of the platform and will thus generate a small rotational moment (resulting in less power transferred to the drive mechanisms) about the midpoint of the platform. 
     Some embodiments of rotation powered vehicles discussed herein are powered using multiple turbines. Each of the turbines may be in fluid communication with a respective pressure chamber. For some embodiments the pressure chambers may be disposed between the platform and the chassis. The fluid from a respective pressure chamber may be delivered to a respective turbine during a power cycle in which the platform is rotated with respect to the chassis. The fluid may exit the respective pressure chamber and then enter the respective turbine which converts the energy of the fluid into a motive force for the rotation powered board. The conversion of fluid energy into a motive force for the rotation powered board may be performed by each respective coupled pressure chamber and turbine during a given power cycle. Turbines typically convert the energy of a fluid into rotational motion of a shaft; one example of a turbine is a screw drive turbine. 
       FIGS. 1-6  depict an embodiment of a rotation powered vehicle  10  that incorporates screw turbine drives and pressure chambers. The screw drive turbines and pressure chamber working in tandem act as the drive mechanisms which convert rotational motion of a platform of the embodiment into translational motion of the rotation powered vehicle embodiment.  FIG. 1  shows the rotation powered vehicle embodiment  10  which includes a platform  12 , a first screw turbine assembly  14 , a second screw turbine assembly  16 , a chassis  18 , and a plurality of wheels  20  coupled to the first screw turbine assembly  14  and the second screw turbine assembly  16 .  FIG. 2  shows the underside of the rotation powered vehicle embodiment  10  and shows a first pressure chamber  22 , a first piston  24 , a second pressure chamber  26 , a second piston  28 , and flexible tubing  30 . Although the flexible tubing  30  is represented by lines in the various figures, the flexible tubing  30  is capable of carrying fluid to and from the various elements of the rotation powered vehicle  10  of  FIG. 1 . 
     As seen in  FIG. 2 , the first screw turbine assembly  14  and the second screw turbine assembly  16  are pivotally secured to the chassis  18 . This allows for the steering of the rotation powered vehicle  10 . The first screw turbine assembly  14  and the second screw turbine assembly  16  may be pinned to the chassis  18 , bolted to the chassis, or any suitable coupling configuration which allows for the rotation of the turbine assemblies with respect to the chassis may be used.  FIGS. 3 and 4  depict a force represented by an arrow  32  which rotates the platform  12  in a fourth angular direction as indicated by the arrow  34  in  FIG. 4 . Rotating the platform  12  in the fourth angular direction will rotate the first screw turbine assembly  14  and the second screw turbine assembly  16  as depicted by the arrows  36  in  FIG. 3 . With the wheels  20  rotated as depicted in  FIG. 3 , the rotation powered vehicle  10  will turn in a fourth linear direction as indicated by the arrow  38  in  FIG. 4  as it is propelled in a direction which is out of the page. 
       FIGS. 5 and 6  depict a force represented by an arrow  40  which rotates the platform  12  in a third angular direction as indicated by the arrow  42  in  FIG. 4 . Rotating the platform  12  in the third angular direction will rotate the first screw turbine assembly  14  and the second screw turbine assembly  16  as depicted by the arrows  44  in  FIG. 1C . With the wheels  20  rotated as depicted in  FIG. 3 , the rotation powered vehicle  20  will turn in a third linear direction as indicated by the arrow  46  in  FIG. 4  as it is propelled in a direction which is out of the page. 
     As discussed above a rider of the rotation powered vehicle  10  may alter the power of a given power cycle by altering where their feet are on the platform  12  in relation to the midpoint of the platform  12 .  FIG. 7  depicts a first set of arrows  48  which indicate the positions of a riders feet on the platform in a first stance on the platform  12 . A second set of arrows  50  indicate the positions of a riders feet in a second stance on the platform  12 . The first stance indicated by arrows  48  will produce a given amount of power during a power cycle with the feet of the rider are positioned at the distances shown from a platform pivot point  56  which connects the platform  12  and the chassis  18 . The second stance indicated by arrows  50  will produce less power during a power cycle because the feet of the rider are positioned closer to the platform pivot point  56 . That is to say that the first stance indicated by arrows  48  will generate more of a moment around the platform pivot point  56  than the second stance indicated by arrows  50 .  FIG. 7  also indicates an arrow  52  representing a first linear direction and an arrow  54  representing a second linear direction. 
     The rotation powered vehicle embodiment  10  of  FIG. 1  is capable of undergoing a power cycle. The power cycle may include a first half power cycle wherein the platform  12  is rotated in a first angular direction about the platform pivot point  56  which is indicated by the arrow  58  in  FIG. 8 .  FIG. 8  shows the rotation powered vehicle  10  undergoing a first half power cycle with the platform rotated in the first angular direction. The power cycle may also include a second half power cycle wherein the platform is rotated in a second angular direction about the platform pivot point  56  which is indicated by the arrow  60  in  FIG. 9 .  FIG. 9  shows the rotation powered vehicle  10  undergoing a second half power cycle with the platform  12  rotated in the second angular direction. 
       FIG. 10  is a sectional view of a first pressure chamber assembly  62  of the rotation powered vehicle  10  as it undergoes a first power cycle as is shown in  FIG. 8 . As is shown in  FIG. 8 , a first piston  66  is pivotally secured to the chassis  18 . As the platform  12  rotates in the first angular direction, the first piston  66  is advanced into a first interior volume  64  of the first pressure chamber assembly  62  as shown in  FIG. 10 . As the first piston  66  advances into the first interior volume  64  as indicated by arrow  69 , a first variable volume  68  which ifs formed by the first interior volume  64  and the first piston  66  is collapsed. As the first variable volume  68  is collapsed a portion of a volume of fluid  70  is transferred out of a first pressure output port  72  as shown by arrow  73 . Also shown in  FIG. 10  is a first pressure input port  74 . A seal  76  between an outer surface  78  of the first piston  66  and the first interior volume  64  of the first pressure chamber  22  prevents fluid from leaking out of the first variable volume  68  past the first piston  66 . 
       FIG. 11  depicts another embodiment a first pressure chamber assembly  80  which is shown in  FIG. 10 . In the embodiment shown in  FIG. 11 , the variable volume  84  incorporates a first flexible bladder  82  which contains a portion of the volume of fluid  70 . As the first piston  66  advances into the first interior volume  64 , the variable volume  84  formed by the first interior volume  64  and the first piston  66  collapses. As the variable volume  84  collapses it also collapses the first flexible bladder  82 , the first flexible bladder  82  being in fluid communication with the first pressure output port  72 . As the first flexible bladder  82  collapses it forces a portion of the volume of fluid  70  out of the first pressure output port  74  as indicated by the arrow  75 . 
       FIG. 9  depicts a second pressure chamber embodiment  26 . The second pressure chamber  26  may include a second piston  28 , a second interior volume, a second pressure input port  114 , a second pressure output port  116 , and a second variable volume (not shown) all of which may be identically configured to their companion elements which are shown in  FIG. 10 . The second pressure chamber embodiment  26  may also be configured such that there is a second seal between the second piston  28  and a surface of the second interior volume again analogous to  FIG. 10 . Alternatively the second pressure chamber embodiment  26  may include a second flexible bladder which configured identically to the first flexible bladder shown in  FIG. 11 . 
     The rotation powered vehicle of  FIG. 1  may also include the first screw turbine assembly  14  and the second screw turbine assembly  16 .  FIG. 12  depicts a first screw turbine assembly  14  having a first turbine body  86  which is shown in sectional view. The first turbine body  86  may include first turbine input port  88  and a first turbine output port  90 . A first turbine blade  92  is attached to a first turbine shaft  94 , and the first turbine shaft  94  is coupled to a first ratchet  96  and a second ratchet  98 . The ratchets (and all ratchet embodiments contained within this document) may be configured as clutch bearings, or any other suitable one way bearings may be used. The use of two independent ratchets (for this embodiment and for all other embodiments discussed herein) allows for the wheels to be driven independently, without the need for a differential. The first ratchet  96  and second ratchet  98  are both supported by a first sealed bearing  100  and a second sealed bearing  102  respectively. The sealed bearings may act to prevent fluid from leaking outside the first turbine body  86 . The first turbine input port  88  is in fluid communication with the first pressure output port  72  of the first pressure chamber assembly  62 . This may be accomplished through the use of flexible tubing  30  which may connect to the first pressure output port  72  and the first turbine input port  88 . 
     As shown in  FIG. 12 , a portion of the volume of fluid  70  which has exited the first pressure output port  72  during a first half cycle may enter the first turbine input port  88  as indicated by arrow  87 . The fluid  70  may then interact with the first turbine blades  92  such that the first turbine shaft  94  rotates in the second angular direction indicated by arrow  99 . This occurs when energy from the fluid  70  is transferred to the first turbine shaft  94  thereby rotating the first turbine shaft  94 . The first ratchet  96  and the second ratchet  98  are configured to engage the first turbine shaft  94  when it rotates in the first angular direction, and the first ratchet  96  and the second ratchet  98  are configured not to engage the first turbine shaft  94  when the first turbine shaft  94  rotates in the second angular direction which is indicated by the arrow  60  in  FIG. 9 . Fluid  70  which exits the first turbine output port  90  as indicated by arrow  89  is sent to the second pressure input port  114  of the second pressure chamber  26  and into a second variable volume (not shown) which is expanding during the first half power cycle. The first ratchet  96  and second ratchet  98  then turn as indicated by arrows  99  thereby turning the wheels  20  in the first angular direction thereby propelling the rotation powered device  10  in the first linear direction. 
     The rotation powered vehicle embodiment of  FIG. 1  may also include a second screw turbine assembly  16 . The second screw turbine assembly may include a second turbine body  112 , a second turbine input port  120 , and a second turbine output port  122 . The second screw turbine assembly  16  may also include a second turbine shaft (not shown) with second screw turbine blades (not shown) attached to the second turbine shaft (not shown). The second screw turbine assembly may also include a third ratchet  124 , a fourth ratchet  126 , a third sealed bearing, and a fourth sealed bearing. The second screw turbine assembly  16  components may be configured identically to their corresponding first screw turbine assembly  14  components which are configured as shown in  FIG. 12 . 
     During a second half power cycle (shown in  FIG. 9 ), the platform  12  rotates in the second angular direction, and a portion of the volume of fluid  70  may be transferred out of the second variable volume through the second pressure output port  116  and into the second turbine input port  120 . The portion of fluid interacts with the second turbine blades and rotates the second turbine shaft in the second angular direction. This occurs when energy from the fluid  70  is transferred to the second turbine shaft thereby rotating the second turbine shaft. The third ratchet  124  and the fourth ratchet  126  are configured to engage the second turbine shaft when it rotates in the first angular direction, and the third ratchet  124  and the fourth ratchet  126  are configured not to engage the second turbine shaft when the second turbine shaft rotates in the second angular direction. Fluid  70  which exits the second turbine output port  122  is sent to the first pressure input port  74  of the first pressure chamber  22  and into the first variable volume  68  which is expanding during the second half power cycle. The third ratchet  124  and fourth ratchet  126  turn the wheels  20  in the first angular direction thereby propelling the rotation powered device  10  in the first linear direction. 
       FIG. 13  is a schematic which indicates the fluid connections for the rotation powered vehicle  10  of  FIG. 1 . The schematic represents the first screw turbine assembly  14  which includes the first ratchet  96 , the second ratchet  98 , and two wheels  20  attached to the first ratchet  96  and the second ratchet  98 . The first screw turbine assembly  14  also includes a first turbine input port  88  and a first turbine output port  90 .  FIG. 5  also depicts the first pressure chamber assembly  62 , and a first one way valve  108 . The schematic also depicts the second screw turbine assembly  16  which includes the third ratchet  124 , the fourth ratchet  126 , and two wheels  20  attached to the third ratchet  124  and the fourth ratchet  126 . The screw turbine assembly  16  also includes a second turbine input port  120  and a second turbine output port  122 .  FIG. 13  also depicts the second pressure chamber assembly  113 , and a second one way valve  110 . 
     As can be seen in  FIG. 13 , the first turbine input port  88  is in fluid communication with the first pressure output port  72 . It can also be seen that the first turbine output port  90  is in fluid communication with the second pressure input port  114 , with a first one way valve  108  between the first turbine output port  90  and the second pressure input port  114 . The first one way valve  108  ensures that fluid does not exit the second pressure input port  114  during a second half power cycle. The second turbine input  88  is in fluid communication with the second pressure output port  116 . The second turbine output port  122  is in fluid communication with the first pressure input port  74 , with a second one way valve  112  between the second turbine output port  122  and the first pressure input port  74 . The second one way valve  112  ensures that fluid does not exit the first pressure input port  74  during a first half power cycle. 
       FIG. 6  is a flowchart which represents a method embodiment for a power cycle of the rotation powered vehicle of  FIG. 1A . Boxes  138 - 142  depict the method steps first half power cycle and boxes  144 - 158  depict the method steps for the second half power cycle. Box  142  represents a query as to weather or not pressure chamber  1  (the first pressure chamber assembly  62 ) is empty. Similarly, box  158  represents a query as to weather or not pressure chamber  2  (the second pressure chamber assembly  113 ) is empty. It is important to note that the first pressure chamber assembly  62  does not need to be completely empty (it can remain partially filled with the fluid  70 ) for the first half power cycle to end and for the second half cycle to begin. Similarly, the second pressure chamber assembly  113  does not need to be completely empty (it can remain partially filled with fluid  70 ) for the second half power cycle to end and for the first half cycle to begin. 
     Note that throughout the remainder of this document the conventions for the first angular direction, the second angular direction, the third angular direction the fourth angular direction, the first linear direction, the second linear direction, the third linear direction, and the fourth linear direction which have been indicated by arrows in  FIGS. 4, 6, 7, 8, and 9  will be used in reference to other relevant figures and descriptions. 
     It is possible for turbine configurations other than the screw turbine described above to be used in order to power a given rotation powered vehicle embodiment.  FIG. 15  depicts one such a rotation powered vehicle embodiment, the rotation powered vehicle  160  depicted in  FIG. 15  incorporating a first plunger screw drive assembly  162  and a second plunger screw drive assembly  164 . Other than the first plunger screw drive assembly  162  and the second plunger screw drive assembly  164 , the rotation powered vehicle embodiment  160  may include components which may be similar to the components of the rotation powered vehicle depicted in  FIG. 1 . These components may include a platform  12 , a chassis  18 , a first pressure chamber assembly  62 , a first piston  24 , a second pressure chamber assembly  113 , a second piston  28 , and a quantity of flexible tubing  30  which connects the various input and output ports. The first pressure chamber  22  may include a first pressure input port  74  and a first pressure output port  72 , and the second pressure  26  chamber may include second pressure input port  114  and a second pressure output port  116 . Note that  FIG. 15  does not depict all of the above listed components. 
     The first plunger screw drive assembly  162  is depicted in  FIG. 16 . The first plunger screw drive assembly  162  may include a first turbine body  166 , and a first ratchet  168  and second ratchet  170 . The first ratchet  168  and second ratchet  170  may be configured as clutch bearings or any other suitable one way bearings.  FIG. 17  depicts the first plunger screw drive assembly  162  of  FIG. 16  with the first turbine body  166  in sectional view. The sectional view reveals a first turbine shaft  172 , a first screw drive  174 , a first plunger  176 , a first sealed bearing  178 , and a second sealed bearing  180 . The first plunger screw drive  162  may also include a first turbine input port  182  and a first turbine output port  184 . 
       FIG. 18  is a cross sectional view of the first turbine body  166  showing a first slot  186  and a second slot  188 , the first slot  186  and second slot  188  being keyed to a first boss  190  and a second boss  192  on the first plunger  176 . As can be seen in  FIG. 17  the first boss  190  keys into the first slot  186 , and the second boss  192  keys into the second slot  188 . This effectively “keys” the first plunger  176  into the first turbine body  166  such that it may slide along the first turbine shaft  172 , but it may not rotate over the first turbine shaft  172 . Although two bosses are depicted on the first plunger  176  and two slots are depicted in the first turbine body  166 , any suitable combination of key features which may be bosses and or slots may be used to key the first plunger  176  to the first turbine body  166 . For example one slot (or notch) could be disposed on the first plunger  176 , with the slot coupling to a single boss disposed on the first turbine body  166 . 
     While the first plunger  176  is “keyed” to the first turbine body  166 , it may also incorporate a first threaded hole  194  which engages with the first screw drive  174 . The first threaded hole  194  may be engaged with the first screw drive  174  such that as the first plunger  176  advances within the first turbine body  166  guided by the first slot  186  and the second slot  188 , the first threaded hole  194  of the first plunger  176  will rotate the first turbine shaft  172 . The first turbine shaft  172  will rotate in either a first angular direction or in a second angular direction depending on the direction motion of the first plunger  176  along the first turbine shaft  172 . 
     The motion of the first plunger  176  during a first half power cycle is depicted in  FIGS. 19-21 .  FIG. 19  depicts a portion of a volume of fluid  70  from the first pressure output port  72  entering the first turbine input port  182  as indicated by arrow  189 . The fluid advances the first plunger  176  along the first turbine shaft  172  as depicted by the arrows  195 . As the first plunger  176  moves along the first turbine shaft  172 , the first threaded hole  194  interacts with the first screw drive  174  thereby resulting in the rotation of the first turbine shaft  172  in the first angular direction. The rotation of the first turbine shaft  172  in the first angular direction results in the rotation of the first ratchet  168  and second ratchet  170  in the first angular direction as indicated by arrows  193 . This is because the first ratchet  168  and the second ratchet  170  are configured to engage with and rotate with the first turbine shaft  172  when it moves in the first angular direction, and the first ratchet  168  and the second ratchet  170  are configured to not engage with the first turbine shaft  172  when it rotates in the second angular direction. The rotation of the first ratchet  168  and the second ratchet  170  in the first angular direction results in the rotation of the wheels  20  attached to the first ratchet  168  and second ratchet  170  in the first angular direction and therefore a translation of the rotation powered vehicle  160  in the first linear direction (as shown by arrow  52  in  FIG. 7 ). As the plunger  176  advances in the direction indicated by arrow  195 , fluid  70  exits the first turbine output port  184  as indicated by arrow  191 . 
     The rotation powered vehicle of  FIG. 15  may also include a second plunger screw drive assembly  164  which may be configured similarly to the first plunger screw drive which is shown in  FIG. 8B . The second plunger screw drive assembly may include a second turbine body, a third ratchet  171  and fourth ratchet  173 , a second screw drive, a second plunger, a third and fourth sealed bearing, a second turbine input port  183 , and a second turbine output port  185 . The second plunger screw drive may undergo a second half power cycle which is analogous to the first half power cycle which has been discussed above. 
     A power cycle for the rotation powered vehicle embodiment  160  depicted in  FIG. 15  is carried out analogously to the power cycle of the rotation powered vehicle  10  depicted in  FIG. 1 .  FIG. 22  is a schematic which indicates the fluid connections and fluid paths for the rotation powered vehicle  160  of  FIG. 15 . The schematic represents the first plunger screw drive assembly  162  which includes the first ratchet  168 , the second ratchet  170 , and two wheels  20  attached to the first ratchet  168  and the second ratchet  170 . The first plunger screw drive assembly  162  also includes a first turbine input port  182  and a first turbine output port  184 .  FIG. 22  also depicts the first pressure chamber assembly  62 , and a first one way valve  108 . The schematic also depicts the second plunger screw drive assembly  164  which includes the third ratchet  171 , the fourth ratchet  173 , and two wheels  20  attached to the third ratchet  171  and the fourth ratchet  173 . The second plunger screw drive assembly  164  also includes a second turbine input port  183  and a second turbine output port  185 .  FIG. 22  also depicts the second pressure chamber assembly  113 , and a second one way valve  110 . 
     As can be seen in  FIG. 22  the first turbine input port  182  is in fluid communication with the first pressure output port  72 . It can also be seen that the first turbine output port  184  is in fluid communication with the second pressure input port  114 , with a first one way valve  108  between the first turbine output port  184  and the second pressure input port  114 . The first one way valve  108  ensures that fluid does not exit the second pressure input port  114  during a second half power cycle. The second turbine input port  183  is in fluid communication with the second pressure output port  116 . The second turbine output port  185  is in fluid communication with the first pressure input port  74 , with a second one way valve  112  between the second turbine output port  185  and the first pressure input port  74 . The second one way valve  112  ensures that fluid does not exit the first pressure input port  74  during a first half power cycle. 
     A power cycle for the rotation powered vehicle embodiment  160  depicted in  FIG. 15  is carried out analogously to the power cycle of the rotation powered vehicle  10  depicted in  FIG. 1 . That is to say the flowchart depicted in  FIG. 15  can be applied to the rotation powered vehicle  160  depicted in  FIG. 15  in that the methods for carrying out a first half power cycle and a second half power cycle described in the flowchart in  FIG. 14  may also be applied to rotation powered vehicle  160  depicted in  FIG. 15 . The only difference being the manner in which the first and second turbine shafts are rotated in the first angular direction during a first half or second half power cycle. For the rotation powered vehicle depicted  10  in  FIG. 1 , the first and second turbine shafts are rotated in the first angular direction when fluid interacts with the first and second turbine blades respectively. For the rotation powered vehicle embodiment depicted in  FIG. 15  the first and second turbine shafts are rotated in the first angular direction as the first and second plungers engage with and rotate the first and second screw drives respectively. 
     Another embodiment of a rotation powered vehicle with yet another type of turbine drive is depicted in  FIG. 23 . The rotation powered vehicle embodiment  196  incorporates a first cross flow turbine assembly  198  and a second cross flow turbine assembly  200 . Other than the first cross flow turbine assembly  198  and the second cross flow turbine assembly  200 , the rotation powered vehicle embodiment  196  may include components which may be similar to the components of the rotation powered vehicle  10  depicted in  FIG. 1 . These components may include a platform  12 , a chassis  18 , a first pressure chamber assembly  62 , a second pressure chamber assembly  113 , and a quantity of flexible tubing  30 . The first pressure chamber assembly may include a first pressure input port  74  and a first pressure output port  72 , and the second pressure chamber assembly  113  may include second pressure input port  114  and a second pressure output port  116 . 
       FIG. 24  depicts the first cross flow turbine assembly  196  which may include a first turbine body  202  having a first turbine input port  204  and a first turbine output port  206 . The first cross flow turbine assembly  196  may also include a first turbine shaft  208  and first turbine blades  210  secured to the first turbine shaft  208 . The first cross flow turbine assembly  196  may also include a first ratchet  212 , a second ratchet  214 , a first sealed bearing  216 , and a second sealed bearing  218 . 
     The first cross flow turbine assembly  196  can carry out a half power cycle as depicted in  FIG. 24 .  FIG. 24  depicts a portion of a volume of fluid  70  (as indicated by arrow  201 ) from the first pressure output port  72  entering the first turbine input port  204  which rotates the first turbine blades  210  and therefore the first turbine shaft  208  in the first angular direction (as indicated by arrow  199 ). The fluid  70  which enters the first turbine input port  204  interacts with the turbine blades  210  such that the energy of the fluid  70  is converted into rotational motion (as indicated by arrow  199 ) of the first turbine shaft  208 . The first ratchet  212  and the second ratchet  214  are configured to engage with and rotate with the first turbine shaft  208  when it moves in the first angular direction, and the first ratchet  212  and the second ratchet  214  are configured to not engage with the first turbine shaft  208  when it rotates in the second angular direction. The rotation of the first ratchet  212  and the second ratchet  214  in the first angular direction (as indicated by arrows  197 ) results in the rotation of the wheels  20  attached to the first ratchet  212  and second ratchet  214  in the first angular direction and therefore a translation of the rotation powered vehicle  196  in the first linear direction. The fluid  70  may then exit the first cross flow turbine assembly  196  through the first turbine output port  206  as indicated by arrow  203  in  FIG. 24 . 
     The second cross flow turbine assembly  200  may include a second turbine body having a second turbine input port  205  and a second turbine output port  207 . The assembly may also include a second turbine shaft, second turbine blades, a third ratchet  215 , a fourth ratchet  217 , a third sealed bearing and a fourth sealed bearing. All of these components may be configured similarly to their respective counterparts which are shown in  FIG. 24 . 
     A power cycle for the rotation powered vehicle embodiment  196  depicted in  FIG. 23  is carried out analogously to the power cycle of the rotation powered vehicle  10  depicted in  FIG. 1 .  FIG. 26  is a schematic which indicates the fluid connections for the rotation powered vehicle  196  of  FIG. 23 . The schematic represents the first cross flow turbine assembly  198  which includes the first ratchet  212 , the second ratchet  214 , and two wheels  20  attached to the first ratchet  212  and the second ratchet  214 . The first cross flow turbine assembly  198  also includes a first turbine input port  204  and a first turbine output port  206 .  FIG. 26  also depicts the first pressure chamber assembly  62 , and a first one way valve  108 . The schematic also depicts the second cross flow turbine assembly  200  which includes the third ratchet  215 , the fourth ratchet  217 , and two wheels  20  attached to the third ratchet  215  and the fourth ratchet  217 . The second cross flow turbine assembly  200  also includes a second turbine input port  205  and a second turbine output port  207 .  FIG. 26  also depicts the second pressure chamber assembly  113 , and a second one way valve  110 . 
     As can be seen in  FIG. 26 , the first turbine input port  204  is in fluid communication with the first pressure output port  72 . It can also be seen that the first turbine output port  206  is in fluid communication with the second pressure input port  114 , with a first one way valve  108  between the first turbine output port  90  and the second pressure input port  114 . The first one way valve  108  ensures that fluid does not exit the second pressure input port  114  during a second half power cycle. The second turbine input  205  is in fluid communication with the second pressure output port  116 . The second turbine output port  207  is in fluid communication with the first pressure input port  74 , with a second one way valve  112  between the second turbine output port  207  and the first pressure input port  74 . The second one way valve  112  ensures that fluid does not exit the first pressure input port  74  during a first half power cycle. 
     A power cycle for the rotation powered vehicle embodiment  196  depicted in  FIG. 23  is carried out analogously to the power cycle of the rotation powered vehicle  10  depicted in  FIG. 1 . That is to say the flowchart depicted in  FIG. 15  can be applied to the rotation powered vehicle  196  depicted in  FIG. 23 . The only difference being the manner in which the first and second turbine blades interact with the fluid. For the case of the rotation powered board embodiment  10  of  FIG. 1 , the first and second turbine blades are screw turbine blades. For the case of the rotation powered board embodiment  196  of  FIG. 23 , the first and second turbine blades are cross flow turbine blades. 
     Another embodiment of a rotation powered vehicle with yet another type of turbine drive is depicted in  FIGS. 27-29 . The rotation powered vehicle embodiment  220  incorporates a first Tessla turbine assembly  222  and a second Tessla turbine assembly  224 . Other than the first Tessla turbine assembly  222  and the second Tessla turbine assembly  224 , the rotation powered vehicle embodiment  220  may include components which may be similar to the components of the rotation powered vehicle  10  depicted in  FIG. 1 . These components may include a platform  10 , a chassis  18 , a first pressure chamber assembly  62 , a second pressure chamber  113 , and a quantity of flexible tubing  30 . The first pressure chamber assembly  62  may include a first pressure input port  74  and a first pressure output port  72 , and the second pressure chamber assembly  113  may include second pressure input port  114  and a second pressure output port  116 . 
       FIG. 30  is depicts the first Tessla turbine assembly  222  which may include a first turbine body  226  having a first turbine input port  228  and a first turbine output port  230 . The first Tessla turbine assembly  222  may also include a first turbine shaft  232  and first turbine blades  234  secured to the first turbine shaft  232 . The first Tessla turbine assembly  222  may also include a first ratchet  238 , a second ratchet  240 , a first sealed bearing  242 , and a second sealed bearing  244 . A single Tessla turbine blade is shown in  FIG. 31 . The Tessla turbine blades  234  are configured side by side as shown in  FIG. 32 . As shown in  FIG. 30 , fluid  70  may enter the first turbine body  226  through the first turbine input port  228  as indicated by arrow  233 . The fluid  70  may then exit the first turbine body through the first turbine output port  230  as indicated by arrow  235 . The fluid  70  interacts with the turbine blades  234  such that energy from the fluid  70  is transferred to the turbine blades  234 . As shown in  FIG. 31 , as fluid enters the first turbine body  226  and interacts with the Tessla turbine blade  234  the fluid spirals (as indicated by arrow  241  in  FIG. 31 ) toward the center of the Tessla turbine blade  234  where it can exit the space between two Tessla turbine blades  234  in a series of holes  236  which are near the first turbine shaft  232 . The fluid transfers energy to the Tessla turbine blades  234  as it spirals towards the holes  236  thereby causing the Tessla turbine blades  234  to rotate as indicated by arrow  239 . The rotation of the Tessla turbine blades  234  results in the rotation of the first turbine shaft  232  which in turn results in the rotation of the first ratchet  238  and the second ratchet  240  as indicated by arrows  237  in  FIG. 30 . 
     The first Tessla turbine assembly  222  can carry out a half power cycle as depicted in  FIG. 30 .  FIG. 30  depicts a portion of a volume of fluid  70  from the first pressure output port  72  entering the first turbine input port  228  which rotates the first turbine blades  234  and therefore the first turbine shaft  232  in the first angular direction. The first ratchet  238  and the second ratchet  240  are configured to engage with and rotate with the first turbine shaft  232  when it moves in the first angular direction, and the first ratchet  238  and the second ratchet  240  are configured to not engage with the first turbine shaft  232  when it rotates in the second angular direction. The rotation of the first ratchet  238  and the second ratchet  240  in the first angular direction results in the rotation of the wheels  20  attached to the first ratchet  238  and second ratchet  240  in the first angular direction and therefore a translation of the rotation powered vehicle  220  in the first linear direction. 
     The first Tessla turbine assembly  222  depicted in  FIGS. 30 and 31  may also include a first spring  246 , a second spring  248 , a first bushing  250 , and a second bushing  252 . The first spring  246  may apply a force to the first bushing  250  in order to provide a rotational fluid seal between the first bushing  250  and the first turbine body  226 . Similarly, the second spring  248  may apply a force to the second bushing  252  in order to provide a rotational fluid seal between the second bushing  252  bushing and the first turbine body  226 . 
     The second cross flow turbine assembly  224  may include a second turbine body having a second turbine input port  229  and a second turbine output port  231 . The assembly may also include a second turbine shaft, second turbine blades, a third ratchet  243 , a fourth ratchet  245 , a third sealed bearing and a fourth sealed bearing. All of these components may be configured similarly to their respective counterparts which are shown in  FIG. 30 . 
     A power cycle for the rotation powered vehicle embodiment  220  depicted in  FIG. 27  is carried out analogously to the power cycle of the rotation powered vehicle  10  depicted in  FIG. 1 .  FIG. 33  is a schematic which indicates the fluid connections for the rotation powered vehicle  220  of  FIG. 27 . The schematic represents the first Tessla turbine assembly  222  which includes the first ratchet  238 , the second ratchet  240 , and two wheels  20  attached to the first ratchet  238  and the second ratchet  240 . The first Tessla assembly  222  also includes a first turbine input port  228  and a first turbine output port  230 .  FIG. 33  also depicts the first pressure chamber assembly  62 , and a first one way valve  108 . The schematic also depicts the second Tessla turbine assembly  224  which includes the third ratchet  243 , the fourth ratchet  245 , and two wheels  20  attached to the third ratchet  243  and the fourth ratchet  245 . The second Tessla turbine assembly  224  also includes a second turbine input port  229  and a second turbine output port  231 .  FIG. 33  also depicts the second pressure chamber assembly  113 , and a second one way valve  110 . 
     As can be seen in  FIG. 33 , the first turbine input port  228  is in fluid communication with the first pressure output port  72 . It can also be seen that the first turbine output port  230  is in fluid communication with the second pressure input port  114 , with a first one way valve  108  between the first turbine output port  90  and the second pressure input port  114 . The first one way valve  108  ensures that fluid does not exit the second pressure input port  114  during a second half power cycle. The second turbine input  229  is in fluid communication with the second pressure output port  116 . The second turbine output port  231  is in fluid communication with the first pressure input port  74 , with a second one way valve  112  between the second turbine output port  207  and the first pressure input port  74 . The second one way valve  112  ensures that fluid does not exit the first pressure input port  74  during a first half power cycle. 
     A power cycle for the rotation powered vehicle embodiment  220  depicted in  FIG. 27  is carried out analogously to the power cycle of the rotation powered vehicle  10  depicted in  FIG. 1 . That is to say flowchart depicted in  FIG. 15  can be applied to the rotation powered vehicle  220  depicted in  FIG. 27 . The only difference being the manner in which the first and second turbine blades interact with the fluid. For the case of the rotation powered board embodiment  10  of  FIG. 1 , the first and second turbine blades are screw turbine blades. For the case of the rotation powered board embodiment  220  of  FIG. 10 , the first and second turbine blades are Tessla turbine blades. 
       FIGS. 34-37  depict a Tessla turbine assembly embodiment  250  which includes a magnetic clutch feature. The Tessla turbine assembly embodiment  250  may include a turbine body  252 , a turbine input port  254 , a turbine output port  256 , a turbine shaft  258 , and turbine blades  260 . The Tessla turbine assembly  250  may also include a first magnet  262 , a second magnet  264 , a third magnet  266 , a fourth magnet  268 , a first ratchet  270 , a second ratchet  272 , a first bearing  274 , and a second bearing  276 . The Tessla turbine assembly embodiment  250  may also include a first collet, a second collet  257 , a first bearing  274 , a second bearing  275 , a third bearing  276 , and a fourth bearing  277 . 
     The purpose of the magnetic clutch is to isolate the fluid around the turbine blades from the ratchets which drive the wheels. This will prevent fluid from leaking around the turbine shaft  258  and exiting the turbine body  252 .  FIGS. 36 and 37  depict a partial rotation of the magnetic clutch. The third magnet  266  may be magnetically coupled to the fourth magnet  268 . As the turbine shaft  258  rotates the third magnet  266  in the first angular direction (as indicated by arrow  269 ), the fourth magnet  268  also rotates in the first angular direction (as indicated by arrow  271 ) thereby rotating the second ratchet  272  in the first angular direction. The same thing happens to the first magnet  262  and second magnet  264 : as the turbine shaft  258  rotates the second magnet  264  in the first angular direction, the first magnet  262  also rotates in the first angular direction thereby rotating the first ratchet  270  in the first angular direction. The magnetic clutch configuration may be used on any of the rotation powered vehicle turbine embodiments which are discussed in the document. 
     Yet another embodiment of a rotation powered vehicle is depicted in  FIGS. 38-42 . The rotation powered board embodiment  278  uses the transfer of fluid between two chambers to provide power to the wheels for a given half power cycle. This rotation powered board  298  may include a chassis  280  and a rigid platform  282  which is pivotally secured to the chassis  280  by a platform pivot section  283 . The rotation powered board  298  may also include a first pressure chamber  284  which may be secured to the platform  282 , and which may incorporate a first pressure port  286  which is in fluid communication with a first pressure interior volume  288 . 
     A first pressure piston  290  (see  FIG. 44 ) may be pivotally secured to the chassis  280 , and the first pressure piston  290  may be slidably disposed within the first pressure interior volume  288 . The first pressure piston  290  and the first pressure interior volume  288  may form a first variable volume  292 . The first variable volume  292  will expand when the platform  282  rotates in the first angular direction, and the first variable volume  292  will contract when the platform  282  is rotated in the second angular direction. The expansion and contraction of the first variable volume  292  is the result of the movement of the first pressure piston  290  within the first pressure interior volume  288 . 
     A first drive chamber  294  (see  FIG. 44 ) may be secured to the chassis  280 . The first drive chamber  294  can include a first drive interior volume  296  disposed within the first drive chamber  294 , and a first drive port  298  which is in fluid communication with the first drive interior volume  296 . The first drive port  298  is also in fluid communication with the first pressure port  286 . A first drive piston  300  may be disposed within the first drive interior volume  296  and a first rack  302  may be rigidly secured to the first drive piston  300 . Together the first drive piston  300  and the first drive interior volume  296  form a second variable volume  304 . The second variable volume  304  may expand when fluid enters the first drive port  298  thereby extending the first rack  302  from the first drive chamber  294 , or the second variable volume  304  may contract when fluid exits the first drive port  298  thereby retracting the first rack  302  into the first drive chamber  294 . 
     The rotation powered board  298  may also include a second pressure chamber  306  which may be secured to the platform  282 , and which may incorporate a second pressure port  308  which is in fluid communication with a second pressure interior volume  310 . A second pressure piston  312  may be pivotally secured to the chassis  280 , and the second pressure piston  312  may be slidably disposed within the second pressure interior volume  310 . The second pressure piston  312  and the second pressure interior volume  310  may form a third variable volume  314 . The third variable volume  314  will expand when the platform  282  rotates in the first angular direction, and the third variable volume  314  will contract when the platform  282  is rotated in the second angular direction. The expansion and contraction of the third variable volume  314  is the result of the movement of the second pressure piston  312  within the second pressure interior volume  310 . 
     A second drive chamber  316  may be secured to the chassis  280 . The second drive chamber  316  can include a second drive interior volume  318  disposed within the second drive chamber  316 , and a second drive port  320  which is in fluid communication with the second drive interior volume  318 . The second drive port  320  is also in fluid communication with the second pressure port  308 . A second drive piston  322  may be disposed within the second drive interior volume  318  and a second rack  324  may be rigidly secured to the second drive piston  322 . Together the second drive piston  322  and the second drive interior volume  318  form a fourth variable volume  326 . The fourth variable volume  326  may expand when fluid enters the second drive port  320  thereby extending the second rack  324  from the second drive chamber  316 , or the fourth variable volume  326  may contract when fluid exits the second drive port  320  thereby retracting the second rack  324  into the second drive chamber  316 . 
     The rotation powered vehicle  298  of  FIG. 38  may also include a first volume of fluid  328  which may be partially disposed within either the first variable volume  292  or the second variable volume  304 . The embodiment may also include a second volume of fluid  330  which may be partially disposed within either the third variable volume  314  or the fourth variable volume  326 . 
     The rotation powered vehicle  298  of  FIG. 38  may also include a first gear  332  which is coupled to a first ratchet  334 . The first ratchet  334  may be configured to engage the first gear  332  and rotate with the first gear  332  if the first gear  332  is rotating in the first angular direction. The first ratchet  334  may also be configured not to engage the first gear  332  when the first gear  332  rotates in the second angular direction. The rotation powered vehicle  298  may also include a second gear  336  which is coupled to a second ratchet  338 . The second ratchet  338  may be configured to engage the second gear  336  and rotate with the second gear  336  if the second gear  336  is rotating in the first angular direction. The second ratchet  338  may also be configured not to engage the second gear  336  when the second gear  336  rotates in the second angular direction. 
     The rotation powered vehicle  298  may also include a front axle  240  which is pivotally secured to the chassis  280  and which allows for the steering of the rotation powered vehicle  278 . The rotation powered vehicle  298  may also include a drive axle  342  which is may be coupled to the first gear  332  by a first chain  346 . The drive axle  342  may also be coupled to the second gear  336  by a second chain  348 . 
       FIGS. 43-46  depict the rotation powered vehicle  278  undergoing a first half power cycle.  FIG. 43  depicts the platform  282  being rotated in the first angular direction by the application of a force  325  to the platform  282 . The rotation of the platform  282  in the first angular direction collapses the first variable volume  292  and transfers a portion of the first volume of fluid  328  to the second variable volume  304  which expands the second variable volume  304  and extends the first rack  302  from the first drive chamber  294 . This process is shown in  FIG. 44  which depicts the first pressure chamber  284 , the first pressure piston  290 , the first drive chamber  294 , the first drive piston  300 , the first volume of fluid  328 , the first variable volume  292 , and the second variable volume  304 .  FIG. 44  depicts a force indicated by arrow  350  moving the first pressure piston  290  into the first pressure interior volume  288  thereby collapsing the first variable volume  292 . This forces a portion of the first volume of fluid  328  into the second variable volume  304  which expands and extends the first drive piston  300  and the first rack  302  out of the first drive interior volume  296  as indicated by arrow  343 . 
       FIG. 44  also depicts a pressure chamber diameter  352  and a drive chamber diameter  354 . It is the relationship between these two diameters that will determine the relative motion of the first pressure piston  290  with respect to the motion of the first drive piston  300 . For example if the diameters are circular and the radius of the first pressure chamber  284  is r 1  and the radius of the first drive chamber  284  is r 2  then by equating volumes in the two chambers one gets the following equation: 
     
       
         
           
             
               
                 
                   
                     L 
                     ⁢ 
                     
                         
                     
                     ⁢ 
                     2 
                   
                   = 
                   
                     L 
                     ⁢ 
                     
                         
                     
                     ⁢ 
                     1 
                     * 
                     
                       
                         r 
                         ⁢ 
                         
                             
                         
                         ⁢ 
                         
                           1 
                           2 
                         
                       
                       
                         r 
                         ⁢ 
                         
                             
                         
                         ⁢ 
                         
                           2 
                           2 
                         
                       
                     
                   
                 
               
               
                 
                   ( 
                   1 
                   ) 
                 
               
             
           
         
       
     
     where L 1  is the distance the first pressure piston  290  travels and L 2  is the distance the first drive piston t 300  ravels. So if r 1  is 3″ and r 2  is 1″, the L 2  is 9 times L 1 , that is for every inch that the first pressure piston  290  moves the first drive piston  300  will move 9 inches. Similarly, the ratio between the two diameters can be used to act as a force limiter or a force multiplier. By equating pressures in the two chambers: 
     
       
         
           
             
               
                 
                   
                     F 
                     ⁢ 
                     
                         
                     
                     ⁢ 
                     2 
                   
                   = 
                   
                     F 
                     ⁢ 
                     
                         
                     
                     ⁢ 
                     1 
                     * 
                     
                       
                         r 
                         ⁢ 
                         
                             
                         
                         ⁢ 
                         
                           2 
                           2 
                         
                       
                       
                         r 
                         ⁢ 
                         
                             
                         
                         ⁢ 
                         
                           1 
                           2 
                         
                       
                     
                   
                 
               
               
                 
                   ( 
                   2 
                   ) 
                 
               
             
           
         
       
     
     where F 1  is the force on the first pressure piston  290  and F 2  is the resultant force on the first drive piston  300 . So if r 1  is 3″ and r 2  is 1″, the F 2  is 1/9 the value of F 1 . 
     Returning to the first half power cycle,  FIG. 45  shows the first rack  302  extending from the first drive chamber  294  as indicated by arrow  353 . Simultaneously, the second rack  324  retracts into the second drive chamber  316  as indicated by arrow  355 .  FIG. 46  depicts the first rack  302  operatively engaged with the first gear  332 . As the first rack  302  extends from the first drive chamber  294 , the first rack  302  turns the first gear  332  in the first angular direction. As the first gear  332  rotates in the first angular direction it rotates the first ratchet  334  in the first angular direction which in turn rotates the drive axle  342  in the first angular direction thereby translating the rotation powered vehicle  278  in the first linear direction. 
       FIG. 41  shows a linkage  356  which is pivotally secured between the first rack  302  and the second rack  324 . The linkage  356  acts to retract the second rack  324  into the second drive chamber  316  as the first rack  302  extends from the first drive chamber  294 . In turn the linkage  356  acts to retract the first rack  302  into the first drive chamber  294  as the second rack  324  extends from the second drive chamber  316 . 
       FIGS. 47 and 48  depict a second half cycle of the rotation powered vehicle  278  of  FIG. 38 .  FIG. 47  depicts the platform  282  being rotated in the second angular direction by a force  325 . The rotation of the platform  282  in the second angular direction collapses the third variable volume  314  and transfers a portion of the second volume of fluid  330  to the fourth variable volume  326  which expands the fourth variable volume  326  and extends the second rack  324  from the second drive chamber as shown in  FIG. 48 . As the second rack  324  extends from the second drive chamber  316  as indicated by arrow  359 , the second rack  324  turns the second gear  336  in the first angular direction. Simultaneously, the first rack  302  retracts into the first drive chamber  294  as indicated by arrow  357 . As the second gear  336  rotates in the first angular direction it rotates the second ratchet  338  in the first angular direction which in turn rotates the drive axle  342  in the first angular direction thereby translating the rotation powered vehicle  278  in the first linear direction. 
       FIG. 49  depicts an alternate drive embodiment for the rotation powered vehicle  278  of  FIG. 38 .  FIG. 49  depicts the same elements depicted in  FIG. 44  with the addition of a first flexible bladder  358  disposed within the first variable volume  292  and in fluid communication with the first pressure port  286 , and a second flexible bladder  360  disposed within the second variable volume  304  and in fluid communication with the first drive port  298 . 
       FIG. 50  is a flowchart which depicts the method described above for carrying out a power cycle of the rotation powered device of  FIG. 38 . Boxes  362 - 392  depict the method steps first half power cycle and boxes  394 - 424  depict the method steps for the second half power cycle. 
       FIGS. 51-54  depict another embodiment of a rotation powered vehicle  426 . All of the previous rotation powered vehicle embodiments have employed hydraulic power to carry out a power cycle. The rotation powered vehicle embodiment  426  of  FIG. 51  uses mechanical drive mechanisms in order to convert the rotational motion of the platform into translational motion of the rotation powered vehicle  426 . 
     The rotation powered vehicle embodiment  426  of  FIG. 51  may include a chassis  430  and a rigid platform  428  which is pivotally secured to the chassis  430  by a platform pivot section  437 . The rotation powered vehicle embodiment  426  may also include a first linkage  432  which is pivotally secured to the platform  428  at a first pivot point  434  on the first linkage  432 . The first linkage  432  may also include a first linkage slot  444 . A first coupler link  446  may be pivotally secured to the chassis  430  and pivotally secured to a second pivot point  442  on the first linkage  438 . A first rack  448  may be slidably disposed along the chassis  430 , and the first rack  448  may include a first rack pin  449  which may be engaged with the first linkage slot  444 . 
     A first gear  450  may be disposed on a gear axle  477  and may be operatively coupled to the first rack  448 . A first ratchet  452  may in turn be coupled to the first gear  450 . The first ratchet  452  may be configured such that it engages with and rotates with the first gear  450  if the first gear  450  rotates in the first angular direction. The first ratchet  452  may also be configured such that it does not engage the first gear  450  if the first gear  450  rotates in the second angular direction. 
     The rotation powered vehicle embodiment  426  may also include a second linkage  454  which is pivotally secured to the platform  428  at a third pivot point  456  on the second linkage  454 . The second linkage  454  may also include a second linkage slot  460 . A second coupler link  462  may be pivotally secured to the chassis  430  and pivotally secured to a fourth pivot point  458  on the second linkage  454 . A second rack  464  may be slidably disposed along the chassis  430 , and the second rack  464  may include a second rack pin  472  which may be engaged with the second linkage slot  460 . 
     A second gear  466  may be disposed on the gear axle  477  and may be operatively coupled to the second rack  464 . A second ratchet  468  may in turn be coupled to the second gear  466 . The second ratchet  468  may be configured such that it engages with and rotates with the second gear  466  if the second gear  466  rotates in the first angular direction. The second ratchet  468  may also be configured such that it does not engage the second gear  466  if the second gear  466  rotates in the second angular direction. 
     The rotation powered vehicle embodiment may also include a front axle  473  which is pivotally secured to the chassis  430  and which allows for the steering of the rotation powered vehicle  426 . The embodiment may also include a drive axle  474  which is secured to the first gear  450  by a first chain  475 , and which is secured to the second gear  466  by a second chain  476 . 
       FIGS. 55-57  depict a first half power cycle of the rotation powered vehicle  426  of  FIG. 51 .  FIG. 56  depicts a rotation of the platform  426  in the first angular direction about the platform pivot section  437  by the application of a force  469 . This rotates the first linkage  432  in the second angular direction (as indicated by arrow  463 ) which in turn translates the first rack  448  (as indicated by arrow  467 ) over the first gear  450  as shown in  FIG. 58 . Simultaneously, the second linkage  454  rotates in the first angular direction as indicated by arrow  465  and moves the second rack  464  as indicated by arrow  471 . As the first gear  450  rotates in the first angular direction it engages the first ratchet  452  which also rotates in the first angular direction. The rotation of the first ratchet  452  in the first angular direction in turn rotates the drive axle  474  in the first angular direction. This results in the translation of the rotation powered vehicle  426  in the first linear direction.  FIGS. 59 and 60  depict how the first rack  448  may be slidably disposed along a section of the chassis  430 , as first rack pins  449  are inserted into a chassis slot  470 . 
       FIGS. 61 and 62  depict a second half power cycle of the rotation powered vehicle  426 .  FIG. 61  depicts a rotation of the platform  428  in the second angular direction about the platform pivot point  437  by the application of a force  469 . This rotates the second linkage  454  in the second angular direction (as indicated by arrow  465 ) which in turn translates the second rack  464  (as indicated by arrow  471 ) over the second gear  466  as shown in  FIG. 62 . Simultaneously, the first linkage  432  rotates in the first angular direction (as indicated by arrow  463 ) and causes the first rack  448  to move as indicated by arrow  467  in  FIG. 62 . As the second gear  466  rotates in the first angular direction it engages the second ratchet  468  which also rotates in the second angular direction. The rotation of the second ratchet  468  in the first angular direction in turn rotates the drive axle  474  in the second angular direction. This results in the translation of the rotation powered vehicle  426  in the first linear direction. Other embodiments of the rotation powered vehicle described above may include embodiments which are configured such that the first linkage  432  and the second linkage  454  rotate in the same direction during a given half power cycle. 
       FIG. 63  is a flowchart which depicts the method described above for carrying out a power cycle of the rotation powered vehicle  426 . Boxes  480 - 504  depict the method steps first half power cycle and boxes  506 - 530  depict the method steps for the second half power cycle. 
     Having now described various embodiments of the invention in detail as required by the patent statutes, those skilled in the art will recognize modifications and substitutions to the specific embodiments disclosed herein. Such modifications are within the scope and intent of the present invention as defined in the following claims.