Abstract:
A mechanical device comprising, a gear rack having a first point and a second point; at least one piston attached either to said first point or said second point; said piston having an exterior surface and an interior surface; wherein said exterior surface is facing away from said gear rack and wherein said gear rack is attached to said interior surface; said gear rack being gyratingly coupled with an actuator shaft; wherein said gear rack is capable of moving in a substantially linear direction due to a force being applied to said exterior surface or said interior surface; and wherein said actuator shaft rotating due to the said motion of said gear rack; in another embodiment, at least one piston having an interior surface and an exterior surface; said inner side pivotingly mated with a connecting rod; said connecting rod having an opposing point B which is rotationally fastened to a counterbalance; said counterbalance rotating about an actuating shaft; a cylinder chamber having with a top breach housing said at least one piston; a pull shaft pivotingly connected to said exterior surface with pivoting joint and to a gear rack with a second pivoting joint; said pull shaft reciprocly advancing within said top breach; said reciprocation causing said gear rack to similarly reciprocate causing rotation of an input shaft; wherein said input shaft is mated with said gear rack through a one way gear box; and an accelerating spark plug, disposed in the body of said cylinder chamber for igniting combustible materials introduced into said cylinder chamber.

Description:
CLAIM OF PRIORITY 
       [0001]    This application claims priority of a U.S. patent application Ser. No. 13/626,950 filed on Sep. 26, 2012, the contents of which are fully incorporated herein by reference. This application is also claiming priority of an earlier filed provisional application 61/977,554 filed on Apr. 9, 2014, the contents of which are fully incorporated herein by reference, and for which this application services as the utility substitute. 
     
    
     FIELD OF THE INVENTION 
       [0002]    The present invention relates to piston engines, and various alternatives of such engines designed to improve efficiency and performance. 
       BACKGROUND OF THE INVENTION 
       [0003]    The use of piston engines is well known and spans over a century. Such engines come in various configurations and alignments. However, all such engines have a common feature of alternating pistons that are connected to a rotating crankshaft. The rotation of the crankshaft produces rotational power that is later translated through a series of gears, usually referred to as a transmission device, to the wheels or other moving parts of a machine that is using such a motor as a source of power. 
         [0004]    All existing embodiments are suffering from a common shortcoming in that the rotation of the crankshaft necessarily contains dead zones, or zones of now power, where the rotational force of the piston is wasted until the crankshaft turns over into a force producing position. The present invention aims to eliminate and solve this problem by connecting pistons to a gear rack that is always moving linearly, thereby not wasting any cycles on rotation. While the present invention also contains a crankshaft like device, it is used only for the initial startup, to eliminate vibration and to prevent the cylinder head from slamming into the cylinder chamber. 
         [0005]    Furthermore, it will be shown that the device embodied in the present invention has a plurality of different applications, such as a water propulsion engine. The reciprocating gear rack of the present invention can be retrofitted using a conventional piston on one and another piston on the other end or to a water piston of the water propulsion device. 
         [0006]    Various implements are known in the art, but fail to address all of the problems solved by the invention described herein. One embodiment of this invention is illustrated in the accompanying drawings and will be described in more detail herein below. 
       SUMMARY OF THE INVENTION 
       [0007]    It is therefore an object of the present invention to provide a hydraulic motor capable of using high-pressure or low-pressure fluids such as water, wherein the power of water pressure is applied to effectuate a number of different applications such as rotating a brush using a mechanism that produces alternating flows of water. 
         [0008]    It is a further object of the present invention to provide an apparatus wherein water from a conventional faucet or tap is carried through flexible tubing to an hydraulic actuator which alternates the flow of water through the device using a system of valves which open and close, which flow of water causes a brush to rotate. 
         [0009]    It is a further object of the present invention to provide an apparatus wherein a supply of water is carried to a hydraulic rotary actuator wherein a system of opening and closing valves causes water flow to alternate between two available paths, causing alternating hydraulic pressure which may be applied for cleaning, as well as a variety of other uses. 
         [0010]    Yet another object of the present invention is provide a more efficient use of reciprocating piston motion. 
         [0011]    Still another object of the present invention is to provide a continuously operating water propulsion device. 
         [0012]    It is still another object of the present invention is to provide a smaller, more efficient engine, that produces the same or greater degree of output as a conventional internal combustion engine using conventional rotational elements. 
         [0000]    These and other features of the invention can be further understood by reference to the following drawings. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0013]      FIG. 1  shows a bottom schematic view of the hydraulic motor according to an embodiment of the present invention that will rotate a brush. 
           [0014]      FIG. 2  shows a bottom schematic view of the hydraulic motor according to an embodiment of the present invention that will rotate a brush. 
           [0015]      FIG. 3  shows a bottom schematic view of the hydraulic motor according to an embodiment of the present invention that will rotate a brush. 
           [0016]      FIG. 4  shows a bottom schematic view of the hydraulic motor according to an embodiment of the present invention that will rotate a brush 
           [0017]      FIG. 5  shows an elevated schematic view of the brush rotated by the hydraulic motor, from the side according to an embodiment of the present invention that will rotate said brush. 
           [0018]      FIG. 6  shows an elevated schematic view of the brush rotated by the hydraulic motor, from the other side according to an embodiment of the present invention that will rotate said brush. 
           [0019]      FIG. 7  shows an elevated schematic view of the top of the hydraulic motor according to an embodiment of the present invention that will rotate a brush. 
           [0020]      FIG. 8  shows an elevated schematic view of the side of a one-way gear box, which may be attached to the hydraulic rotary actuator of the hydraulic motor of the present invention to convert the alternating flow of water, which causes an alternating rotation of a shaft, to a one-way continuous rotation, producing an embodiment of the present invention suitable for many different applications. 
           [0021]      FIG. 9  demonstrates an elevated schematic view of the side of the handle and soap dispenser of the hydraulic motor according to an embodiment of the present invention which will rotate a brush. 
           [0022]      FIG. 10  shows a bottom schematic view of the hydraulic motor according to an alternate embodiment of the present invention, using a different arrangement of parts to rotate a brush. 
           [0023]      FIG. 11 . shows the back of the gear rack and piston mechanism that comprises the assembly of the present invention. 
           [0024]      FIG. 12 . is a perspective view of another embodiment of the present invention, showing the counterweight component of the assembly. 
           [0025]      FIG. 13 . is a top view of an embodiment of the present invention. 
           [0026]      FIG. 14  is a side view of an embodiment of the present invention. 
           [0027]      FIG. 15  is a perspective view of an embodiment for several cylinders connected in line to one 
           [0028]      FIG. 16  is a two sided diagram of the one way gear box. 
           [0029]      FIG. 17  is a cross sectional diagram of another embodiment of the present invention. 
           [0030]      FIG. 18  is a cross sectional diagram of yet another embodiment of the present invention. 
       
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS 
       [0031]    The preferred embodiments of the present invention will now be described with reference to the drawings. Identical elements in the various figures are identified with the same reference numerals. 
         [0032]    Reference will now be made in detail to embodiment of the present invention. Such embodiments are provided by way of explanation of the present invention, which is not intended to be limited thereto. In fact, those of ordinary skill in the art may appreciate upon reading the present specification and viewing the present drawings that various modifications and variations can be made thereto. 
         [0033]    Now referring to the drawings,  FIG. 1  shows the hydraulic motor  21  of the present invention. Water under ordinary tap pressure is admitted through a port  4  to entry line  20  and through second port  4  to integrating valve  22 . Water is then admitted through valve  18  into a chamber inside cylinder  3 . Water then fills the chamber inside cylinder  3 , which puts pressure upon and compresses spring  19 . The piston  1  is pushed to the right by the pressure of water filling the chamber inside of cylinder  3 , teeth inside the gear rack  2  engage with teeth arranged along the outside of gear  7 , turning said gear  7 . Rotation of gear  7  turns shaft  6  which is removably attached to brush  9 , thus rotating brush  9 . 
         [0034]    Piston  1  moves to the right until the pressure of water is balanced by the tension on the spring  19 . At this point Spring  19  pushes the valve trigger  11 , which opens valve  22 . This causes water to fill the right side of the chamber inside cylinder  3 . Water pressure in the chamber inside cylinder  3  pushes piston  1  to the left, putting pressure on spring  19  and causing the engaged teeth of gear  7  to turn in the opposite direction, causing shaft  6  and brush  9  to rotate until the piston  1  reaches the point where water pressure is balanced by the tension put on spring  19 . At this point, valve  22  opens and the other valve closes, causing the left side of the chamber inside cylinder  3  to begin filling with water again, starting the sequence over again. This sequence repeats until the user stops the flow of water into the system. 
         [0035]    The foregoing figures may be further understood by reference to the following list of parts shown by name and reference number:
       Piston  1     Gear Rack  2     Cylinder  3     Port  4     Bearing  5     Shaft  6     Gear  7     Piston Seal  8     Cover Brush  9     Brush  10     Valve Trigger  11     Valve Exit Line  12     End Cap  13     Plug Seals  14     Hydraulic Rotary Actuator  15     Water Line to Cylinder  16     Connector  17     Valve Plug  18     Spring  19     Entry Line to Valve  20     Extension Pipe  21     Integrating Valve  22     Valve Connection Screw  23     Soap Dispenser  24     Support for Piston  25     Direction of Piston  26     Retaining Screw for Spring  27     Bolt with hole in center to accommodate piston trigger  28     Hollow chamber for Valve trigger  29         
 
         [0065]      FIG. 2  shows the further progression of fluid through the hydraulic motor, causing movement of fluid filling the left chamber of cylinder  3 , pushing the piston  1  in the direction shown by the arrow  26  to the right. 
         [0066]      FIG. 3  shows the further progression of fluid through the hydraulic motor, filling the right side of the chamber of cylinder  3 , pushing piston  1  in the direction shown by the arrow  26 , to the left. 
         [0067]      FIG. 4  shows the further progression of fluid through the hydraulic motor, further filling the right side of the chamber of cylinder  3 , pushing piston  1  in the direction shown by the arrow  26 , to the left. 
         [0068]      FIG. 5  shows the exterior parts of the hydraulic motor, illustrating the port  4 , the shaft  6 , the cover brush  9  the brush  10 , the valve exit line  12 , the end cap  13 , the water line to the cylinder  16 , the entry line to valve  20 , the extension pipe  21  and the integrating valve  22 . 
         [0069]      FIG. 6  shows the exterior parts of the hydraulic motor from the other side, illustrating the cylinder  3 , the port  4 , the shaft  6  the cover brush  9 , the brush  10 , the valve exit line  12 , the hydraulic rotary actuator  15 , the water line to the cylinder  16 , the entry line to valve  20 , the extension pipe  21 , the integrating valve  22  and the valve connection screws  23 . 
         [0070]      FIG. 7  shows the exterior parts of the hydraulic motor from the top, illustrating the cylinder  3 , the port  4 , the shaft  6 , the cover brush  9 , the brush  10 , the hydraulic rotary actuator  15 , the water line to the cylinder  16 , the entry line to valve  20 , the extension pipe  21 , the integrating valve  22  and the valve connection screws  23 . 
         [0071]      FIG. 8  shows a one-way gearbox, which may be attached to the hydraulic motor of the present invention to the shaft  1  shown in  FIG. 1 . The one-way gearbox will allow the shaft to rotate in only one direction, enabling the present invention to be applied to a wide variety of applications. A one-way gear or gear clutch  101  is mounted on the shaft, and will clutch when motion goes to the right. A second one-way gear or gear clutch  102  is mounted on the shaft and will clutch when motion goes to the left. The body  103  of the one-way gearbox contains the gears, the shaft and the bearings. The bearing  104  will reduce friction and prevent oil from leaking from the one-way gearbox. The gear  105  is attached to the shaft. The bearing  106  is mounted on the shaft to reduce friction. The gear  105  and the bearing  106  are mounted on the shaft  107 . A shaft  108  connects to the hydraulic rotary actuator  15  shown in  FIG. 1 . A shaft  109  connects to a variety of other embodiments including a gearbox speed increaser, generator, washing machine or a variety of other applications. The body of the gear box  103  is attached to the hydraulic rotary actuator  15  shown in  FIG. 1  at seven connection points  110 . 
         [0072]    The action of the one-way gear box is described in  FIG. 8  by the clutch A which controls two gears, and will allow the first gear  101  and second gear  105  to rotate to the right or to the left, but gear  101  will clutch when it goes right, releasing the shaft. Clutch B controls three gears: the first gear  102  may rotate to the left or to the right, the second gear  105  may rotate to the left or to the right and the third gear  105  may rotate to the left or to the right, but gear  102  will clutch when it goes to the left, releasing the shaft. 
         [0073]      FIG. 9  shows the extension pipe  21 . 
         [0074]      FIG. 10  shows the progression of fluid through another embodiment of the hydraulic motor using the same parts in a slightly different arrangement, with the fluid filling the entry line to valve  20 , the water line to cylinder  16 , through port  4 , causing movement of fluid filling the left chamber of cylinder  3 , pushing the piston  1  in the direction shown by the arrow  26 , to the right. 
         [0075]    The details of the mechanical device, that is comprised most basically of the gear rack  2  and the piston  1 , are further described  FIGS. 11-14 . Shown in  FIG. 11  are the gear rack  2 , the first point  200 , the second point  205 , the piston  1 , the exterior surface  210 , the interior surface  215 , the gear shaft  222 , the gear rack connector pin  230 , the connecting rod  235 , the point A  240 , the point B  245 , the input shaft  250 , the counterweight  255 , the first point of the counterweight  260 , the second point of the counterweight  265 , the one way gear transmission  270 . The gear rack  2 , is shown having the first point  200  and the second point  205 . The points  200  and  205  serve as mounting points for the piston  1 . The present invention may have at least one more pistons  1  mounted on the gear rack  2 . 
         [0076]    Still referring to  FIG. 11 , the piston  1  has the exterior surface  210  and the interior surface  215 . In an embodiment using hydraulic fluid, as in  FIGS. 1-10 , the exterior surface would come into contact with liquid, such as water. For combustion engines, the exterior surface  210  would come into contact with combustible fuels secreted into a cylinder and would create pressure necessary to achieve the proper oxygen to fuel mixture. Such piston  1  would also serve push out combustion vapors after the burn was achieved. The piston seal  8  slides along the cylinder wall, as shown in the cylinder  3  in  FIG. 1 , and prevents any access liquids or vapors from escaping into the cylinder cavity  29  ( FIG. 1 ) or out of a cylinder and into the engine bay holding such a combustion engine. The interior surface  215  is mounted onto first or second points  200  or  205  of the gear rack  2 . The interior surface  215  may be disposed at a 90 degree angle  275  ( FIG. 12 ), or at any other angle with respect to the plane of the gear rack  2 . The interior surface  215  and the exterior surface  210  are preferably parallel to each other or oriented at a slight angle with respect to each other. 
         [0077]    As would be appreciated by one skilled in the art, and demonstrated in  FIGS. 11-14 , the gear rack  2  replaces the connector rod of a conventional engine. In the present invention, all of the pressure applied to the exterior surface  210  by the force of the combustion is translated into linear motion  273  or  273  of the gear rack  2 . Unlike existing engines, where the actual linear force ranges between approximately 25% to 75%, with the rest of the force being dissipated by friction and with compressing the crankshaft in a sideways or oscillating direction, the present invention uses close to 100% of the linear force to produce the actual and direct driving force, as illustrated in items 272 and 273, to actually drive the actuator shaft  220 . 
         [0078]    As shown in  FIGS. 1-10 , and again in  FIGS. 11-14 , the gear rack  2  is gyraticly coupled with an actuator shaft  220 . This connection can be direct, as illustrated in  FIGS. 1-4 , or through the one way gear transmission  270 , as shown in  FIG. 8  and  FIGS. 11-14 . The gyratic coupling means that the gear rack  2  and actuator shaft  220 , or the gear rack  2  and the connector gear  226  are in constant contact with one another. The contact may be variably engaged in other embodiments, such as with a transmission having a neutral position. As the gear rack undergoes linear motions  272  or  273 , it forces the gear shaft  222 , or more directly, the connector gear  226  to rotate or to rock from side to side, thus providing driving force to whatever the actuator shaft  220  is connected to, such as vehicle or locomotive wheels, or action ends of mechanized tools. The engagement between the gear rack  2  and the connector gear  226 , or any gears shown in the figures, can also be achieved using rollers, belts or chains. The gear rack  2  can be which can be positioned in a horizontal, vertical, or at any other angle with respect to the horizon, 
         [0079]    In some embodiments, such as the hydraulic embodiment shown in  FIGS. 1-4 , the linear force  272  or  273  is offset by the constant presence of liquid inside the cylinder  3 . This counteracting force uses the momentum of the piston to push the piston back into position for the next load of fuel. When an engine is disabled, the counteracting force of such a liquid also prevents the piston  1  from damaging the cylinder chamber by slowing the linear motion of the piston  1 . However, in combustion engines, such as petrol/gasoline, diesel or steam engines, the liquid fuel or steam is injected into the cylinder only if the engine is running. Once the engine is stopped, no additional fuel is fed into the cylinder chamber. Even though the engine has been stopped the piston  1  would still be in motion through inertia and would invariably slam into a wall or cap of a cylinder and damage it. To avoid this problem, and to foster a more balanced operational rhythm of an engine disclosed in the present invention, a connecting rod  235  and a counterweight  255  may used to control the linear motion of the gear rack  2 , as described in  FIG. 13 . The connecting rod  235  is required to prevent cylinder damage in internal combustion engines, while the counterweight  255  is present to promote balance and reduce vibration and also combines with the connecting rod  235  to prevent cylinder damage. 
         [0080]    To further on the embodiment shown in  FIG. 13 , shown are the gear rack  2 , the first point  200 , the second point  205 , the piston  1 , the interior surface  215 , the actuator shaft  220 , the gear shaft  222 , the connector gear  226 , the gear rack connector pin  230 , a second gear rack connector pin  232 , the connecting rod  235 , the point A  240 , the point B  245 , the input shaft  250 , the counterweight  255 , the first point of the counterweight  260 , the second point of the counterweight  265 , the one way gear transmission  270 , the orientation angle  275 . The embodiment shown in  FIGS. 11 ,  13 , and  14  is best suited for use with combustion engines for reasons described above. The connector pin  230  is mounted on the gear rack  2 . The gear rack connector pin  230  is mounted near the end of the gear rack  2 , either at the first point  200  or the second point  205 , but may be mounted at any point along the gear rack  2 . To increase the travel distance of the piston  1 , a longer connecting rod  235  or a larger, heavier counterweight  255  may be used. The connector pin  230  serves as a mounting point and the pivot for the point B  245  of the connecting rod  235 . The point A  240  is connected to the second connector pin  232 , which connects the connecting rod  235  to the counterweight  255 . The counterweight contains an input shaft  250 . The input shaft  250  can be connected to a starter device (not shown) which can spin the counterweight while being assisted by an external power source, such as manual crank or a battery. When the engine is operating, the connecting rod  235 , assisted by the counterweight  255 , will use the momentum of the piston  1  to move the piston back into the firing position. Meaning, if the piston  1  is moving in the direction  272 , the connecting rod  235 , or the connecting rod  235  and the counterweight  255 , will move the piston back in the opposite direction  273 , to expel remaining fumes or to receive the next load of fuel. When the operation of the engine is stopped, the piston  1  will travel in a substantially linear direction until reaching the end of the connecting rod  235 , at which point travel will stop or go in reverse, instead of proceeding further and slamming into the cap of the cylinder or the cylinder wall. An end cap  13  and a cylinder is shown in  FIG. 2 . To balance the force of the piston  1 , a counterweight  255  may be added to the point A  240  and would pivot about the input shaft  250 . The points A and B,  240  and  245  respectively, are interchangeable. 
         [0081]      FIGS. 12 and 14  demonstrate the gear rack  2 , the first point  200 , the second point  205 , the piston  1 , the exterior surface  210 , the interior surface  215 , the actuator shaft  220 , the gear shaft  222 , the drive gears  223  and  224 , the connecting gear  226  which achieves coupling or engagement of the gear rack connector pin  230 , a second connector pin  232 , the input shaft  250 , the counterweight  255 , the one way gear transmission  270 , and the orientation angle  275 .  FIGS. 12 and 14  illustrate the operation of the one way transmission  270 , as was also described in  FIG. 8 .  FIG. 12 . demonstrates the one way gear transmission  270  in an embodiment not having a connecting rod  235 , while  FIG. 14  illustrates the same concept with a device having a connecting rod  235 , along with a counterbalance  255 . A variety of transmission devices may be employed in place of the gear transmission  270 . 
         [0082]    Still referring to  FIGS. 12 and 14 , the one way gear box contains the connecting gear  226 . This gear is gyratingly coupled with the gear rack  2 . As the connecting gear  226  moves along the gear rack  2 , it turns the gear shaft  222 , which in turn rotates the sprocket  228 ,  FIG. 11  and  FIG. 16 . The sprocket drives a chain over a second sprocket  231 , as shown in  FIG. 16 . The sprocket  231  that is not connected to the gear shaft  222  contains a clutch. The gear  224  also contains a clutch that operates in the opposite direction from the clutch on the sprocket  231 . The sprocket  231  and the drive gear  224  mounted on the actuating shaft  220  will be clutching in opposite directions. Thus while the drive gear  223  rotates either to the right or the left, the clutch at the bottom always rotates in one direction driven interchangeably by the lower sprocket or the lower gear  224 . 
         [0083]    When considering  FIGS. 11-14  one skilled in the art will appreciate that an engine comprising one gear rack  2  and piston  1  combination, can be connected with at least one additional gear rack  2 , as shown in  FIG. 15 . The additional gear rack  2  being exactly the same or substantially similar to other gear racks  2  in this particular engine. Each such gear rack may have a one way gear transmission  270  that is gyratingly coupled with an actuating shaft  220 . To work in concert with one another, the gear transmissions  270  can be sharing the same actuating shaft  220 . This combination of gear racks  2  and piston  1  assemblies can be positioned to move inversely with respect to one another, so as to prevent resonance and reduce vibration of an engine disclosed in the present invention. The input shaft  250  may be coming from a conventional starter device, which is powered by the engine&#39;s battery, to begin, and continue the operation of such engine. The gear racks  2  may be substantially straight or curved. The present invention may serve as the engine for the actuating shaft  220  in hydraulic devices as described in  FIGS. 1-10 . The gear rack  2  and piston  1  combination would also effectively replace connecting rods and piston assembly found in gasoline and diesel engines (internal combustion engine), and in most steam engines (external combustion engine). The actuator shaft  220  would replace a standard crank shaft, and the one way gear transmission would function as an analogous transmission found coupled to existing external or internal combustion engines. 
         [0084]      FIG. 16  is a detailed diagram of the gear transmission  270 . Shown is the connector gear  226 , which engages with the gear rack  2  for rotational or gyrational movement. The gear shaft  222 , which connects the connector gear  226  with the upper drive wheel and a second upper drive wheel. In the figure the upper drive wheel is shown as a sprocket  228  and the second upper drive wheel is shown as the drive gear  223 . The teeth of the drive gear  223  are engaged with the teeth of the second lower drive wheel, which is shown as the lower drive wheel  224 . The actuating shaft  220  connects the lower drive wheel, which is again shown as the lower sprocket  231 , with the second lower drive wheel that is shown as the drive gear  224 . The looped strip of material links the upper drive wheel with the lower drive wheel. In  FIG. 16  this is shown in form of a roller chain  227  looping over the upper sprocket  228  and lower sprocket  231 . Either or both of the lower sprocket  231  and the lower drive wheel  224  contain clutch mechanisms which are opposite of each other. For the purpose of this invention, clutching also means ratcheting. 
         [0085]    The two clutch gears  231  and  224  are opposites of each other, meaning, when the connector gear  226  is rotating in a clockwise direction, the sprocket  228  and the drive gear  223  are spinning in the clockwise direction. The drive gear  224  always moves in the opposite direction of the drive gear  223 , while the sprocket  231  is always spinning in the same direction as sprocket  228 . Thus, if the desired rotation of the actuating shaft  220  is clockwise, then in the present scenario the sprocket  231  will drive the actuating shaft  220 , while the drive gear  224  will be spinning freely or clutching. Once the motion of the gear rack  2  reverses and the connecting gear is rotating in the counterclockwise direction, with the sprockets  228  and  231  and drive gear  223  all rotating counterclockwise, the drive gear  224  is now rotating clockwise and thus driving the actuating shaft  220  in the same clockwise direction. The sprocket  231 , while still spinning is actually clutching and not supplying any drive force to the actuating shaft  220 , until the rotation of the drive gear  226  is once again clockwise, at which point the process would repeat itself. Thus, while the motion of the gear rack  2  is reciprocating, the direction of the rotation of the actuating shaft  220  is always the same. The direction of rotation of the actuating shaft  220  can be reversed by reversing the drive direction of the clutch wheels  231  and  224 . The upper sprocket  228  and the lower sprocket  231  can be replaced with rollers and gears, while a fabric, polymer, rubber or steel ribbon can be used instead of the roller chain  227 . The drive gears  223  and  224  can be replaced rollers or wheels, having high friction rolling surfaces. The location of the upper and lower drive wheels  228  and  231  and the location of the second upper and lower drive wheels  223  and  224  can be reversed along their respective shafts  222  and  220 . 
         [0086]      FIG. 17  demonstrates an alternative embodiment of the present invention. Shown are the gear rack  2 , the first point  200 , the second point  205 , the piston  1 , the exterior surface  210 , the interior surface  215 , the actuator shaft  220 , the gear shaft  222 , the connector gear  223 , the gear rack connector pin  230 , the connecting rod  235 , the input shaft  250 , the counterweight  255 , the one way gear box  270 , the orientation angle  275 . Also shown are a pulling shaft  300 , joint A  310  and joint B  320 , cylinder chamber  330 , the top breech  340 , the ring gasket  350 , and the spark plug  360 . The appeal of this embodiment is that the piston  1  is being pulled by the pulling shaft  300 , rather than driven forward by the gear rack  2 . The advantage of pulling versus pushing is that a driving force tends to be more blunt and weathering on the components being driven whereas a pulling force is gentler. Additionally, this embodiment integrates the engine block architecture known in prior art with the novelty of the present invention. 
         [0087]    In the embodiment disclosed in  FIG. 17  is launched by manually rotating the input shaft  250 . This is usually accomplished with battery power. The rotating input shaft  250  spins the counterweight  255 , which in this case can be a component the conventional crank shaft. The counterweight  255  is connected to the connecting rod  235  with a connector pin  230 . The connecting rod  235  is pivotingly connected to the inner surface  215 . As the piston  1  moves forward, it begins exerting lateral pressure on the pulling shaft  300  which communicates this pressure to the gear rack  2  and to the gearbox  270 . As the counterweight  255  completes a rotation arc of 360°, it draws the piston  1  away from the top breech  340 , thereby vacating the interior space of the cylinder chamber  330 . The cylinder chamber  330  now fills with a combustible solution through cam openings (not shown). The piston  1  then begins to glide toward the top breech  340  compressing the fuel mixture. The spark plug  360  then ignites the fuel mixture using electric current derived from battery or alternator or any other means known in the art, causing the piston assembly comprising elements  1  and  235  to once again move away from the breech  340 . The process then repeats itself continuously until the device is shut off. Once battery power initiates the first spin of the input shaft  250 , the gear rack  2  and the one way gear box  270  take over driving the piston  1 , with the spark plug  360  providing the accelerating force of this embodiment. The actuator shaft  220  provides the rotational output that is necessary to provide driving force to the device or machine that is utilizing this present invention as a source of power, which may be a vehicle, lawn equipment, a power tool a gas generator, or any other machine that utilizes internal combustion engines. 
         [0088]    The pulling shaft  300  may be pivotately connected to the gear rack  1  at point  205  and pivotately connected to the exterior surface  210 , such that the pulling shaft  300  rocks back and forth as piston  1  closes in and recedes within the cylinder chamber  330 . 
         [0089]      FIG. 18  is a demonstration of an application of the present invention where the gear box  270  has been replaced by an inner chamber  390  disposed within an outer chamber  380 . Liquid, preferably water, is introduced through the inlet  410  and expelled through the outlet  420 . The precise location of the inlet  410  and outlet  420  is not dispositive to enablement. 
         [0090]    Water is introduced into the inner chamber  390  through flaps  370 C while the water piston  1 B is moving in the direction  430 , against the inner face  390 A. The initial motion is produced by battery power rotating the counterweight  255 , which exerts a lateral pressure on the pull shaft  300 . During this time valves or flaps  370 A and E are closed and the channel  400  between these valves is dry. The cavity of the inner chamber  390  fills up with water against the inner face  390 A until the point where the counterweight rotates through  3600  and begins to pull the piston  1  in the direction  440 . At the same time, the cylinder chamber  330  fills up with combustible materials through cam openings (not shown) and is ignited by the spark plug  360  producing force against the exterior surface  210  which drives the piston  1  in direction  440 . 
         [0091]    While the water piston  1 B is traveling in the direction  440  the cavity of the inner chamber  390  empties through valves  370 D through channel  400  and out of the outlet  420 . At the same time the cavity of the inner chamber  390  against the outer face  3901  begins to fill up with water through valve  370 A and  370 E. During this time valves  370 C and  370 B are closed. On the return trip in the direction  430 , the outer face  390  B of the piston  1 B pushes the water out through valve  370 B and out of the outlet  420 , while valves  370 E,  370 D and  370 A are closed and only  370 C open and introducing water against inner face  390 A. 
         [0092]    As demonstrated in  FIG. 18 , there is always flow of liquid from the inlet  410  to the outlet  420 . Furthermore, since the water is being forced out of the inner chamber  390 , into the narrow channel  400  through the valves  370 D or  370 B, it exits the outlet  420  with a certain force, which is at least a match to the suction force produced at the inlet  410 . As a result, what is shown is a propulsion mechanism that can be used in a liquid medium to propel a machine, such as a vessel, in the direction opposite the force of propulsion. It can be further appreciated by the one skilled in the art that the flow of liquid can be reversed, with outlet  420  forming an inlet and inlet  410  functioning as an outlet. The reversal is accomplished through sequencing of open and shut actions of the valves  370 A-E. The valves  370  A-E may be controlled with the force of the flow of water that is induced by the lateral movement of the water piston  1 B, or externally through a use of a solenoid (not shown). 
         [0093]    In  FIGS. 17 and 18  the pull shaft  300  travels through a hermetic ring or seal  350  in the top breach  340 . In  FIG. 18  there is an additional opening  352  for the pull shaft  300 . The opening is sealed with an additional hermetic ring or seal  351 . 
         [0094]    Although this invention has been described with a certain degree of particularity, it is to be understood that the present disclosure has been made only by way of illustration and that numerous changes in the details of construction and arrangement of parts may be resorted to without departing from the spirit and the scope of the invention.