Patent Publication Number: US-11649678-B1

Title: Piston motor system

Description:
TECHNICAL FIELD 
     The present disclosure relates to the field of oil and gas drilling, and more particularly relates to a piston motor system for drilling an oil or gas well. 
     BACKGROUND 
     Conventional oil or gas well drilling methods, especially for horizontal wells and directional wells, include the use of a mud motor powering a drill bit to generate a high amount of torque and rotations per minute (RPM) during a drilling operation. Depending on the type of drilling operation, different configurations of mud motors, drill bits, etc. may be used according to drilling requirements. A drilling system must be able to endure a high amount of stress caused by the large amount of force required for drilling, and efficiently maintain a consistent power output throughout the drilling operation. In many configurations, drilling fluid may be pumped through the drilling pipes, out of the drill bit, and back to the surface to simultaneously power the mud motor, cool the drill bit, and remove debris from the wellbore. 
     Because of the large amount of torque and RPM required to drill oil or gas wells, conventional drilling methods include many different points of failure. For example, without limitation, indicators of downhole mud motor failure may include frequent stalling, high surface pressure or pressure fluctuation, etc. and may result in a loss in rate of penetration (ROP) or complete system failure. As a key component of horizontal and directional drilling, there is a need for improvements of the mud motor to avoid system failure and increase efficiency of drilling operations. 
     Therefore, a heretofore unaddressed need exists in the art to address the aforementioned deficiencies and inadequacies. 
     SUMMARY 
     In one embodiment, a motor system for drilling an oil or gas well is described. The motor system includes: a cylindrical body; a converter configured to convert a two-directional rotation into a one-directional rotation; a rotatable shaft configured to be (a) disposed inside of the cylindrical body, (b) rotatable in both a counterclockwise direction and a clockwise direction, and (c) coupled to a drill bit through the converter; a driving piston configured to be coupled to the rotatable shaft and configured to divide the cylindrical body into a first chamber and a second chamber; and a flow piston configured to change flow direction of a fluid within the cylindrical body to drive the driving piston, wherein the driving piston is configured to be driven by the fluid via a pressure difference to move in a forward direction and in a reverse direction. 
     In another embodiment the flow piston is configured to be in a first position and a second position. 
     In another embodiment when the flow piston is in the first position, the fluid in the first chamber is of a higher pressure than the fluid in the second chamber so that the driving piston is to move in the forward direction. 
     In another embodiment when the flow piston is in the second position, the fluid in the second chamber is of a higher pressure than the fluid in the first chamber so that the driving piston is to move in the reverse direction opposite to the forward direction. 
     In another embodiment, the motor system further includes a control cylinder, wherein movement of the flow piston between the first position and the second position is controlled via the control cylinder. 
     In another embodiment the control cylinder comprises a control cylinder body, a control cylinder piston, and a control cylinder shaft; the control cylinder body is divided into a first control cylinder chamber and a second control cylinder chamber via the control cylinder piston; the control cylinder piston is coupled to a first end of the control cylinder shaft; and a second end of the control cylinder shaft is coupled to the flow piston. 
     In another embodiment the flow piston is configured to be in the first position when the control cylinder piston is in a first control position; and the flow piston is configured to be in the second position when the control cylinder piston is in a second control position. 
     In another embodiment, the motor system further includes forward triggers disposed on a forward end of the cylindrical body and rear triggers disposed on a rear end of the cylindrical body, wherein the forward triggers are configured to be activated by the driving piston and cause the control cylinder piston to move from the first control position to the second control position; and the rear triggers are configured to be activated by the driving piston and cause the control cylinder piston to move from the second control position to the first control position. 
     In another embodiment, the motor system further includes a first normally-closed valve and a second normally-closed valve; wherein the first normally-closed valve and the second normally-closed valve are configured to open in response to activation of the forward triggers, thus allowing the fluid to flow into the first control cylinder chamber and out of the second control cylinder chamber; the first normally-closed valve and the second normally-closed valve are configured to open in response to activation of the rear triggers, thus allowing the fluid to flow out of the first control cylinder chamber and into the second control cylinder chamber; and the first normally-closed valve and the second normally-closed valve are configured to close after movement of the control cylinder piston either from the first control position to the second control position or from the second control position to the first control position is complete. 
     In another embodiment the cylindrical body further comprises an inlet opening and an outlet opening; fluid is input into the cylindrical body via the inlet opening; and fluid is output from the cylindrical body via the outlet opening. 
     In another embodiment the cylindrical body further comprises a first transfer opening and a second transfer opening; the flow piston further comprises a transfer chamber; the first transfer opening is disposed on the first chamber; the second transfer opening is disposed on the second chamber; and the first transfer opening is connected to the second transfer opening via a transfer pipe. 
     In another embodiment when the flow piston is in the first position, fluid flows into the first chamber via the inlet opening; and the transfer chamber connects the first transfer opening and the outlet opening such that fluid from the second chamber flows out of the second transfer opening, through the transfer pipe, through the first transfer opening, through the transfer chamber, and through the outlet opening. 
     In another embodiment when the flow piston is in the second position, the transfer chamber connects the first transfer opening and the inlet opening such that fluid from the inlet opening flows into the transfer chamber, through the first transfer opening, through the transfer pipe, through the second transfer opening, and into the second chamber; and fluid flows out of the first chamber via the outlet opening. 
     In another embodiment the cylindrical body comprises a plurality of transfer pipes and a plurality of outlet pipes; the outlet pipes are configured to connect the outlet opening to an output; and the outlet pipes and the transfer pipes are alternatingly arranged along a periphery of the cylindrical body. 
     In another embodiment the flow piston further comprises an inner passage; and when the flow piston is in the first position, fluid flows from the inlet opening, through the inner passage, and into the first chamber. 
     The motor system of claim  1 , further comprising one or more support rods configured to prevent torsion of the driving piston. 
     In another embodiment, the motor system further includes a first input normally-closed valve, a second input normally-closed valve, a first output normally-closed valve, and a second output normally-closed valve; wherein the first input normally-closed valve and the first output normally-closed valve are configured to open in response to activation of the forward triggers thus allowing the fluid to flow into the first control cylinder chamber and out of the second control cylinder chamber; the second input normally-closed valve and the second output normally-closed valve are configured to open in response to activation of the rear triggers thus allowing the fluid to flow into the second control cylinder chamber and out of the first control cylinder chamber; and the first input normally-closed valve, the second input normally-closed valve, the first output normally-closed, and the second output normally-closed valve are configured to close after movement of the control cylinder piston either from the first control position to the second control position or from the second control position to the first control position is complete. 
     In another embodiment the outlet pipes are configured to transfer the fluid to a cavity of the convertor and then to the drill bit. 
     In another embodiment the fluid may be water, oil, or gas. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The accompanying drawings illustrate one or more embodiments of the present disclosure and, together with the written description, serve to explain the principles of the present disclosure, wherein: 
         FIGS.  1 A- 1 H  illustrate a fluid flow sequence of an exemplary piston motor system, wherein  FIG.  1 A  shows an initial flow sequence for a flow piston in a first position, 
         FIG.  1 B  shows an intermediate flow sequence for a flow piston in a first position,  FIG.  1 C  shows a flow sequence immediately before triggering a flow piston to move to a second position,  FIG.  1 D  shows a flow sequence after triggering two normally-closed valves to open for a flow piston in a first position,  FIG.  1 E  shows an initial flow sequence for a flow piston in a second position,  FIG.  1 F  shows an intermediate flow sequence for a flow piston in a second position,  FIG.  1 G  shows a flow sequence immediately before triggering a flow piston to move to a first position, and  FIG.  1 H  shows a flow sequence after triggering two normally-closed valves to be open for a flow piston in a second position, in accordance with an embodiment of the present disclosure; 
         FIGS.  2 A- 2 B  illustrate an exemplary drill bit connector, wherein  FIG.  2 A  shows a top perspective view of an exemplary drill bit connector and  FIG.  2 B  shows a bottom perspective view of an exemplary drill bit connector, in accordance with an embodiment of the present disclosure; 
         FIGS.  3 A- 3 B  illustrate an exemplary 2-to-1 rotation converter, wherein  FIG.  3 A  shows a perspective view of an exemplary 2-to-1 rotation converter and  FIG.  3 B  shows an exploded view of an exemplary 2-to-1 rotation converter, in accordance with an embodiment of the present disclosure; 
         FIGS.  4 A- 4 B  illustrate an exemplary output cap, wherein  FIG.  4 A  shows a perspective view of an exemplary output cap and  FIG.  4 B  shows a top view of an exemplary output cap, in accordance with an embodiment of the present disclosure; 
         FIG.  5    illustrates an exemplary rotation shaft and support rods, in accordance with an embodiment of the present disclosure; 
         FIG.  6    illustrates an exemplary driving piston, in accordance with an embodiment of the present disclosure; 
         FIGS.  7 A- 7 B  illustrate an exemplary cylindrical body, wherein  FIG.  7 A  shows a perspective cross-sectional view of an exemplary cylindrical body and  FIG.  7 B  shows a top view of an exemplary cylindrical body, in accordance with an embodiment of the present disclosure; 
         FIGS.  8 A- 8 B  illustrate an exemplary flow piston, wherein  FIG.  8 A  shows a top perspective view of an exemplary flow piston and  FIG.  8 B  shows a bottom perspective view of an exemplary flow piston, in accordance with an embodiment of the present disclosure; 
         FIG.  9    illustrates an exemplary shaft connector, in accordance with an embodiment of the present disclosure; 
         FIGS.  10 A- 10 B  illustrate an exemplary input cap, wherein  FIG.  10 A  shows a perspective view of an exemplary input cap and  FIG.  10 B  shows a top view of an exemplary input cap, in accordance with an embodiment of the present disclosure; 
         FIGS.  11 A- 11 C  illustrate an exemplary control cylinder, wherein  FIG.  11 A  shows a front perspective view of an exemplary control cylinder,  FIG.  11 B  shows a rear perspective view of an exemplary control cylinder, and  FIG.  11 C  shows a right cross-sectional view of an exemplary control cylinder in accordance with an embodiment of the present disclosure; 
         FIGS.  12 A- 12 B  illustrate an exemplary cylinder switch system, wherein  FIG.  12 A  shows a section of an exemplary cylinder switch system integrated with an output cap and  FIG.  12 B  shows a section of an exemplary cylinder switch system integrated with an input cap, in accordance with an embodiment of the present disclosure; 
         FIGS.  13 A- 13 B  illustrate an incorporated exemplary cylinder switch system, wherein  FIG.  13 A  shows a section integrated with an output cap and  FIG.  13 B  shows a section integrated with an input cap, in accordance with an embodiment of the present disclosure; 
         FIG.  14    illustrates a cross-sectional view of a single-shaft piston motor system, in accordance with an embodiment of the present disclosure; 
         FIG.  15    illustrates a cross-sectional view of a double-shaft piston motor, in accordance with an embodiment of the present disclosure; 
         FIGS.  16 A- 16 B  illustrate an exemplary rotation output for a double-shaft piston motor, wherein  FIG.  16 A  shows a first view of a rotation output for a double-shaft piston motor, and  FIG.  16 B  shows a second view of a rotation output for a double-shaft piston motor, in accordance with an embodiment of the present disclosure; 
         FIG.  17    illustrates an operating environment of a piston motor system, in accordance with an embodiment of the present disclosure; 
         FIGS.  18 A- 18 B  illustrate a fluid flow sequence of a second embodiment of an exemplary piston motor system, wherein  FIG.  18 A  shows an exemplary flow piston moving from a first position to a second position and  FIG.  18 B  shows an exemplary flow piston moving from a second position to a first position, in accordance with an embodiment of the present disclosure; and 
         FIG.  19    illustrates a fluid flow sequence of a third embodiment of an exemplary piston motor system, in accordance with an embodiment of the present disclosure. 
     
    
    
     DETAILED DESCRIPTION 
     The present disclosure will now be described more fully hereinafter with reference to the accompanying drawings, in which exemplary embodiments of the present disclosure are shown. The present disclosure may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure is thorough and complete, and will fully convey the scope of the present disclosure to those skilled in the art. Like reference numerals refer to like elements throughout. 
     The terms used in this specification generally have their ordinary meanings in the art, within the context of the present disclosure, and in the specific context where each term is used. Certain terms that are used to describe the present disclosure are discussed below, or elsewhere in the specification, to provide additional guidance to the practitioner regarding the description of the present disclosure. For convenience, certain terms may be highlighted, for example using italics and/or quotation marks. The use of highlighting and/or capital letters has no influence on the scope and meaning of a term; the scope and meaning of a term are the same, in the same context, whether or not it is highlighted and/or in capital letters. It is appreciated that the same thing can be said in more than one way. Consequently, alternative language and synonyms may be used for any one or more of the terms discussed herein, nor is any special significance to be placed upon whether or not a term is elaborated or discussed herein. Synonyms for certain terms are provided. A recital of one or more synonyms does not exclude the use of other synonyms. The use of examples anywhere in this specification, including examples of any terms discussed herein, is illustrative only and in no way limits the scope and meaning of the present disclosure or of any exemplified term. Likewise, the present disclosure is not limited to various embodiments given in this specification. 
     It is understood that when an element is referred to as being “on” another element, it can be directly on the other element or intervening elements may be present therebetween. In contrast, when an element is referred to as being “directly on” another element, there are no intervening elements present. As used herein, the term “and/or” includes any and all combinations of one or more of the associated listed items. 
     It is understood that, although the terms Firstly, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by these terms. These terms are only used to distinguish one element, component, region, layer or section from another element, component, region, layer or section. Thus, a first element, component, region, layer or section discussed below can be termed a second element, component, region, layer or section without departing from the teachings of the present disclosure. 
     It is understood that when an element is referred to as being “on”, “attached” to, “connected” to, “coupled” with, “contacting”, etc., another element, it can be directly on, attached to, connected to, coupled with or contacting the other element or intervening elements may also be present. In contrast, when an element is referred to as being, for example, “directly on”, “directly attached” to, “directly connected” to, “directly coupled” with or “directly contacting” another element, there are no intervening elements present. It is also appreciated by those of skill in the art that references to a structure or feature that is disposed “adjacent” to another feature may have portions that overlap or underlie the adjacent feature. 
     The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the present disclosure. As used herein, the singular forms “a”, “an”, and “the” are intended to include the multiple forms as well, unless the context clearly indicates otherwise. It is further understood that the terms “comprises” and/or “comprising”, or “includes” and/or “including” or “has” and/or “having” when used in this specification specify the presence of stated features, regions, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, regions, integers, steps, operations, elements, components, and/or groups thereof. 
     Furthermore, relative terms, such as “lower” or “bottom” and “upper” or “top”, may be used herein to describe one element&#39;s relationship to another element as illustrated in the figures. It is understood that relative terms are intended to encompass different orientations of the device in addition to the orientation shown in the figures. For example, if the device in one of the figures is turned over, elements described as being on the “lower” side of other elements will then be oriented on the “upper” sides of the other elements. The exemplary term “lower” can, therefore, encompass both an orientation of lower and upper, depending on the particular orientation of the figure. Similarly, for the terms “horizontal”, “oblique” or “vertical”, in the absence of other clearly defined references, these terms are all relative to the ground. Similarly, if the device in one of the figures is turned over, elements described as “below” or “beneath” other elements will then be oriented “above” the other elements. The exemplary terms “below” or “beneath” can, therefore, encompass both an orientation of above and below. 
     Unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which the present disclosure belongs. It is further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and the present disclosure, and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein. 
     As used herein, the terms “comprise” or “comprising”, “include” or “including”, “carry” or “carrying”, “has/have” or “having”, “contain” or “containing”, “involve” or “involving” and the like are to be understood to be open-ended, i.e., to mean including but not limited to. 
     As used herein, the phrase “at least one of A, B, and C” should be construed to mean a logical (A or B or C), using a non-exclusive logical OR. It should be understood that one or more steps within a method may be executed in different order (or concurrently) without altering the principles of the present disclosure. 
     Embodiments of the present disclosure are illustrated in detail hereinafter with reference to accompanying drawings. It should be understood that specific embodiments described herein are merely intended to explain the present disclosure, but not intended to limit the present disclosure. 
     In order to further elaborate the technical means adopted by the present disclosure and its effect, the technical scheme of the present disclosure is further illustrated in connection with the drawings and through specific mode of execution, but the present disclosure is not limited to the scope of the implementation examples. 
     The present disclosure relates to the field of oil and gas drilling, and more particularly relates to a piston motor system for drilling an oil or gas well. 
       FIGS.  1 A- 1 H  illustrate a fluid flow sequence of an exemplary piston motor system, wherein  FIG.  1 A  shows an initial flow sequence for a flow piston in a first position,  FIG.  1 B  shows an intermediate flow sequence for a flow piston in a first position,  FIG.  1 C  shows a flow sequence immediately before triggering a flow piston to move to a second position,  FIG.  1 D  shows a flow sequence after triggering two normally-closed valves to be open for a flow piston in a first position,  FIG.  1 E  shows an initial flow sequence for a flow piston in a second position,  FIG.  1 F  shows an intermediate flow sequence for a flow piston in a second position,  FIG.  1 G  shows a flow sequence immediately before triggering a flow piston to move to a first position, and  FIG.  1 H  shows a flow sequence after triggering two normally-closed valves to be open for a flow piston in a second position, in accordance with an embodiment of the present disclosure. 
     For the purpose of illustrating the flow sequence of the present invention, with reference to  FIGS.  1 A- 1 H , a system diagram of piston motor  100  is described herein. It should be noted that the system diagram of piston motor  100  is for illustrative purposes only, and does not limit piston motor  100  to the particular embodiment shown. 
     Piston motor  100  is configured to utilize pressurized fluid from input  102  to move driving piston  164  in a first direction towards rotation output  122  (hereinafter a forward direction) and a second direction towards flow piston  112  (hereinafter a reverse direction). In the present embodiment, fluid may be, for example, without limitation, water, oil, gas, etc. When driving piston  164  moves in a forward direction, rotation shaft  168 , coupled to rotation output  122 , rotates clockwise. When driving piston  164  moves in a reverse direction, rotation shaft  168  rotates counterclockwise. In another embodiment, the rotation direction of rotation shaft  168  may be reversed relative to the direction of driving piston  164 . Namely, when driving piston  164  moves in a forward direction, rotation shaft  168  may rotate counterclockwise, and when driving piston  164  moves in a reverse direction, rotation shaft  168  may rotate clockwise. 
     A 2-to-1 rotation converter (not shown, to be described with reference to  FIGS.  3 A- 3 B ) may be used between rotation shaft  168  and rotation output  122  such that rotation output  122  is in a single rotation direction. For example, while rotation shaft  168  rotates in a clockwise direction and a counterclockwise direction, rotation output  122  may only rotate in a clockwise direction or only rotate in a counterclockwise direction as the 2-to-1 rotation converter converts the two rotation directions of rotation shaft  168  into a single rotation direction of rotation output  122 . 
     Piston motor  100  comprises first chamber  160  and second chamber  166  separated via driving piston  164 . Flow piston  112  may be used to control the flow of fluid within piston motor  100 . When flow piston  112  is in a first position (as shown in  FIGS.  1 A- 1 D ), a pressurized fluid from input  102  flows into first chamber  160  such that the fluid pressure in first chamber  160  is higher than the fluid pressure in second chamber  166 . Thus, driving piston  164  moves in the forward direction and rotation shaft  168  rotates clockwise. When flow piston  112  in a second position (as shown in  FIGS.  1 E- 1 H ), a pressurized fluid from input  102  flows into second chamber  166  such that the fluid pressure in second chamber  166  is higher than the fluid pressure in first chamber  160 . Thus, driving piston  164  moves in the reverse direction and rotation shaft  168  rotates counterclockwise. 
     An exemplary initial flow sequence of piston motor  100  is shown with reference to  FIG.  1 A . A pressurized fluid from input  102  flows through first inlet pipe  104  to first inlet opening  106  and also through second inlet pipe  152  to second inlet opening  150  of input cap  142 , through inner passage  146 , and into first chamber  160 . Thus, the fluid in first chamber  160  is high pressure in comparison to the fluid in second chamber  166  and causes driving piston  164  to move in the forward direction. As driving piston  164  moves in the forward direction, a portion of the fluid in second chamber  166  flows to output  124 . The flow path of fluid from second chamber  166  to output  124  is as follows: fluid exits second chamber  166  via second transfer opening  120  and flows through transfer pipes  116  and into first transfer opening  110  of annular transfer chamber  108 . Flow piston  112  directs fluid from first transfer opening  110  to first outlet opening  114  and second outlet opening  156  via annular transfer chamber  108 , where annular transfer chamber  108  is a sealed off portion of first chamber  160 . Thus, fluid from first transfer opening  110  flows through annular transfer chamber  108  and out of first outlet opening  114  and second outlet opening  156 . Fluid from first outlet opening  114  flows through first outlet pipe  118  to output  124 , and fluid from second outlet opening  156  flows through second outlet pipe  162  to output  124 . The exact structure of flow piston  112  will be described below with reference to  FIGS.  8 A- 8 B . 
     Driving piston  164  moves in a forward direction from the position shown in FIG.  1 A to the position shown in  FIG.  1 B  (intermediate flow sequence) and then to the position shown in  FIG.  1 C , before flow piston  112  moves into a second position. While driving piston  164  moves in the forward direction, first chamber  160  becomes larger as second chamber  166  becomes smaller, relative to the position of driving piston  164 . 
     With reference to  FIG.  1 D , for driving piston  164  to switch from moving in the forward direction to moving in the reverse direction, driving piston  164  reaches a first end of rotation shaft  168  adjacent to rotation output  122  and activates forward triggers (not shown) at a forward end of second chamber  166 . In the present embodiment, the forward triggers hydraulically communicate with first normally-closed valve  126  and second normally-closed valve  148 . However, different communication means may be used between the forward triggers, first normally-closed valve  126 , and second normally-closed valve  148 . For example, without limitation, mechanical compression, electronic signaling, pneumatic signaling, etc. may be used after the forward triggers are activated by driving piston  164  to cause first normally-closed valve  126  and second normally-closed valve  148  to open. Alternatively, first normally-closed valve  126  and second normally-closed valve  148  may open according to a pre-set schedule without the need for the forward triggers, or may be opened remotely. 
     After driving piston  164  reaches the forward end of rotation shaft  168  adjacent to output cap  170  as shown in  FIG.  1 C , flow piston  112  is triggered to move from the first position to the second position. Control cylinder piston  138  is directly coupled to flow piston  112  via control cylinder shaft  140 . Thus, similar to flow piston  112 , control cylinder piston  138  is configured to be in a first position and a second position. When flow piston  112  is in the first position, control cylinder piston  138  is also in the first position. Similarly, when flow piston  112  is in the second position, control cylinder piston  138  is also in the second position. 
     The flow path of fluid after the forward triggers are activated by driving piston  164  is shown in  FIG.  1 D . Control cylinder  134  includes control cylinder chamber  136 , where control cylinder chamber  136  is divided into first control cylinder chamber  130  and second control cylinder chamber  132  via control cylinder piston  138 . After the forward triggers are activated, first normally-closed valve  126  and second normally-closed valve  148  are opened until the triggering process stops, allowing fluid to flow into and out of control cylinder  134  and causing control cylinder piston  138  to move from the first position to the second position. Specifically, fluid from input  102  flows into control cylinder  134  via first control cylinder pipe  128  and into first control cylinder chamber  130 . Thus, fluid in first control cylinder chamber  130  is higher pressure than fluid in second control cylinder chamber  132 , and control cylinder piston  138  moves from the first position to the second position. Because control cylinder piston  138  is coupled to flow piston  112  via control cylinder shaft  140 , the movement of control cylinder piston  138  from the first position to the second position is translated to flow piston  112 , causing flow piston  112  to also move from the first position to the second position. Fluid from second control cylinder chamber  132  is output via second control cylinder pipe  144 . Fluid from second control cylinder pipe  144  flows through control cylinder opening  154 , through annular transfer chamber  108 , through second outlet opening  156 , to second outlet pipe  162 , and to output  124 . Similarly, fluid from second control cylinder pipe  144  flows through control cylinder opening  154 , through annular transfer chamber  108 , through first outlet opening  114 , to first outlet pipe  118 , and to output  124 . It should be noted that flow piston  112  is of a cylindrical shape, and thus comprises a single annular transfer chamber  108 . Thus, while flow piston  112  is in the first position, fluid from first transfer opening  110  may flow through both first outlet opening  114  and second outlet opening  156 , while fluid from control cylinder opening  154  may flow through both first outlet opening  114  and second outlet opening  156 . 
     Flow piston  112  in the second position after the activation of the forward triggers is shown in  FIG.  1 E . Because flow piston  112  is in the second position, the flow pathways within piston motor  100  have changed such that input  102  is connected to second chamber  166  and first chamber  160  is connected to output  124 . 
     The flow path of fluid when flow piston  112  is in the second position is as follows: 
     Fluid from input  102  flows through inlet pipe  104  and into annular transfer chamber  108  via first inlet opening  106 . While in the second position, annular transfer chamber  108 , sealed off from first chamber  160 , connects first inlet opening  106  and first transfer opening  110 . Thus, fluid from first inlet opening  106  flows through annular transfer chamber  108  and out of first transfer opening  110 . Fluid from first transfer opening  110  flows through transfer pipes  116  and into second transfer opening  120 . Thus, input  102  is connected to second chamber  166  and second chamber  166  to be of higher pressure than first chamber  160  causing driving piston  164  to move in the reverse direction. As driving piston  164  moves in the reverse direction, fluid from first chamber  160  flows to output  124 . Fluid in first chamber  160  flows through first outlet opening  114 , through first outlet pipe  118 , and to output  124 . Similarly, fluid in first chamber  160  may also flow through second outlet opening  156 , through second outlet pipe  162 , and to output  124 . 
     As flow piston  112  is in the second position, driving piston  164  moves in the reverse direction to an intermediate position, as shown in  FIG.  1 F , and reaches the reverse end of rotation shaft  168  adjacent to shaft holder  158 , as shown in  FIG.  1 G . Rear triggers (not shown) are then activated by driving piston  164  and causes flow piston  112  to move from the second position to the first position by the opening of first normally-closed valve  126  and second normally-closed valve  148 . 
     As depicted in  FIG.  1 H , the flow path for moving the flow piston from the second position to the first position is shown. As second normally-closed valve  148  is open, fluid flows from input  102  to second control cylinder chamber  132 . Specifically, fluid from input  102  flows through first inlet pipe  104  into first inlet opening  106  and also through second inlet pipe  152  into second inlet opening  150 , and into annular transfer chamber  108 . Annular transfer chamber  108  connects first inlet opening  106  and second inlet opening  150  with control cylinder opening  154 . Thus, fluid from first inlet opening  106  and second inlet opening  150  flows into control cylinder opening  154  via annular transfer chamber  108 . Fluid from control cylinder opening  154  flows through second control cylinder pipe  144  into second control cylinder chamber  132 , causing second control cylinder chamber  132  to be higher pressure than first control cylinder chamber  130 . As a result, control cylinder piston  138  moves into the first position along with flow piston  112 . 
     As control cylinder piston  138  moves into the first position, fluid from first control cylinder chamber  130  is expelled to output  124 . Specifically, fluid from first control cylinder chamber  130  flows out first cylinder pipe  128  as first normally-closed valve  126  is open. Fluid from first cylinder pipe  128  flows into first chamber  160 , through inner passage  146  and out first outlet opening  114  into first outlet pipe  118  and to output  124 . Similarly, fluid may also flow through inner passage  146 , through second outlet opening  156 , through second outlet pipe  162 , and to output  124 . As a result, piston motor  100  returns to the configuration shown in  FIG.  1 A  and first normally-closed valve  126  and second normally-closed valve  148  are closed. Piston motor  100  continues cycling between the configurations shown in  FIGS.  1 A- 1 H  such that rotation is output via rotation output  122 . 
     It should be noted that the switching of flow piston  112  occurs approximately instantaneously such that rotation output  122  rotates with a constant torque. The switching shown in  FIGS.  1 D and  1 H  results in little to no loss in overall torque. Additionally, first normally-closed valve  126  and second normally-closed valve  148  are open only during the activation of the forward triggers and activation of the rear triggers, and remain closed prior to and immediately after the forward triggers and rear triggers are activated. 
     Rotation shaft  168  may include one or more male spirals and driving piston  164  may include one or more female spirals configured to be coupled to the one or more male spirals of rotation shaft  168 . In the preferred embodiment, rotation shaft  168  includes 5 male spirals and driving piston  164  includes 5 female spirals. However, as will be appreciated by one skilled in the art, a greater or lesser number of spirals may be used for each of rotation shaft  168  and driving piston  164 . 
       FIGS.  2 A- 2 B  illustrate an exemplary drill bit connector, wherein  FIG.  2 A  shows a top perspective view of an exemplary drill bit connector and  FIG.  2 B  shows a bottom perspective view of an exemplary drill bit connector, in accordance with an embodiment of the present disclosure. With reference to  FIG.  2   , drill bit connector  200  comprises hex opening  202 , bearing outer body  204 , inner body  206 , drill bit threading  208 , outlet openings  210 , cylindrical body threading  212 , and bearing needles  214 . Drill bit connector  200  is configured to be coupled to a conventional oil and gas well drill bit via drill bit threading  208 . Thus, the output rotation from the piston motor system of the present embodiment, for example, without limitation, may be used to power the conventional oil and gas well drill bit during drilling operations. While inner body  206  is configured to rotate, bearing outer body  204  is configured to remain static and may be coupled to cylindrical body  700  (to be described with reference to  FIGS.  7 A- 7 B ) via cylindrical body threading  212 . While the present embodiment utilizes threading as a coupling means, alternative coupling means may also be used to connect drill bit connector  200  to a conventional oil drill bit and cylindrical body  700 . For example, without limitation, adhesive, channels, fasteners, rivets, etc. may be used as the coupling means. 
     Inner body  206  is separated from bearing outer body  204  via bearing needles  214 , thus enabling inner body  206  to smoothly rotate while bearing outer body  204  remains static. Bearing needles  214  are of a cylindrical structure in the present embodiment. However, bearing needles  214  may alternatively be ball-shaped. Inner body  206  may be coupled to 2-to-1 rotation converter  300  (to be described with reference to  FIGS.  3 A- 3 B ) via hex opening  202 . Thus, rotation from 2-to-1 rotation converter  300  may be transferred to drill bit connector  200 , and subsequently to the conventional oil and gas well drill bit. Fluid output from single shaft piston motor  1400  (to be described with reference to  FIG.  14   ) flows through outlet openings  210  and through the conventional oil and gas well drill bit coupled to the bit connector. Conventional oil and gas well drill bits are typically hollow, allowing for fluid to flow through conventional oil and gas well drill bits to increase penetration rate and dislodge cuttings while simultaneously cooling and cleaning the drill bit. As will be appreciated by one skilled in the art, outlet openings  210  may be of various shapes and sizes and are not necessarily of the shape and size as shown in  FIGS.  2 A- 2 B . For example, without limitation, outlet openings  210  may be circular, rectangular, mesh, etc. 
       FIGS.  3 A- 3 B  illustrate an exemplary 2-to-1 rotation converter, wherein  FIG.  3 A  shows a perspective view of an exemplary 2-to-1 rotation converter and  FIG.  3 B  shows an exploded view of an exemplary 2-to-1 rotation converter, in accordance with an embodiment of the present disclosure. 2-to-1 rotation converter  300  comprises hex shaft  302 , following ring gear  304 , pinion gears  306 , gear rods  308 , hex mover  310 , driving ring gear  312 , and gear holder  314 . 
     2-to-1 rotation converter  300  in the present embodiment is a rotation converter to convert an alternative clockwise-counterclockwise rotation to only clockwise or counterclockwise rotation. Namely, 2-to-1 rotation converter  300  is attached to rotation shaft  500  (to be described with reference to  FIG.  5   ) which provides two rotation directions, and 2-to-1 rotation converter  300  outputs a single rotation direction via hex shaft  302 . Gear holder  314  is configured to house the remaining components of 2-to-1 rotation converter  300 . 
     Hex shaft  302  comprises output hex  328  and input hex  332  separated by gear contact  330 . Output hex  328  is configured to be coupled to hex opening  202  of drill bit connector  200 . Ring gear contact  330  is a section of hex shaft  302  with a smooth outer surface such that hex shaft  302  may rotate independently from following ring gear  304 . Input hex  332  may be coupled to hex mover  310  such that hex shaft  302  rotates according to hex mover  310 . 
     Gear rods  308  are equally distributed in four directions along hex mover  310 , where gear rods  308  provide support for pinion gears  306 . Gear rods  308  are coupled to gear holder  314  and are separated from hex mover  310  such that rotation of hex mover  310  does not affect gear rods  308 . While the present embodiment includes four gear rods  308  and four pinion gears  306 , as will be appreciated by one skilled in the art, a different number of gear rods  308  and pinion gears  306  may be utilized in 2-to-1 rotation converter  300 . Rotation shaft  500  is coupled to driving ring gear  312  such that driving ring gear  312  rotates in the same direction as rotation shaft  500 . For example, without limitation, when rotation shaft  500  rotates in a clockwise direction, driving ring gear  312  rotates in a clockwise direction. Similarly, when rotation shaft  500  rotates in a counterclockwise direction, driving ring gear  312  rotates in a counterclockwise direction. 
     Driving ring gear  312  and following ring gear  304  are configured to be parallel with each other and to be connected by pinion gears  306  as shown in  FIG.  3 B . Gear teeth in opinion gears  306  are in contact with driving gear outer teeth  326  and following gear outer teeth  318 . Thus, driving gear outer teeth  326  face following gear outer teeth  318  but are not in direct contact with each other. Driving ring gear  312  rotates pinion gears  306  and pinion gears  306  rotate following ring gear  304 . 
     The configuration of driving ring gear  312 , following ring gear  304 , and pinion gears  306  ensures an opposite rotation direction of driving ring gear  312  and following ring gear  304 . The contact points of driving ring gear  312  and pinion gears  306  and contact points of following ring gear  304  and pinon gears  306  are on opposite sides of each of pinion gears  306 . When driving ring gear  312  rotates in a clockwise direction, pinion gears  306  are driven to rotate in the same tangential direction as driving ring gear  312  at the contact points of driving ring gear  312  and pinion gears  306 . Pinion gears  306  rotate following ring gear  304  in a tangential direction opposite to driving ring gears  312  at the contact points of driving ring gear  312  and pinon gears  306 . Thus, following ring gear  304  rotates counterclockwise. Similarly, when driving ring gear  312  rotates in a counterclockwise direction, following ring gear  304  is driven by driving ring gear  312  to rotate clockwise through opinion gears  306 . 
     Depending on the direction of rotation of the rotation input to 2-to-1 rotation converter  300 , following ring gear  304  or driving ring gear  312  may be engaged with hex mover  310  via hex mover following teeth  320  and hex mover driving teeth  322 , respectively. Specifically, hex mover following teeth  320  may be engaged with following gear inner teeth  316  when the input direction is counterclockwise, and hex mover driving teeth  322  may be engaged with driving gear inner teeth  324  when the input direction is clockwise. The structure of following gear inner teeth  316  and hex mover following teeth  320  are complementary and are configured to be engaged when following ring gear  304  rotates in a clockwise direction but disengaged when following ring gear  304  rotates in a counterclockwise direction. Similarly, the structure of driving gear inner teeth  324  and hex mover driving teeth  322  are complementary and are configured to be engaged when driving ring gear  312  rotates in a clockwise direction but disengaged when driving ring gear  312  rotates in a counterclockwise direction. 
     Thus, rotation is transferred throughout 2-to-1 rotation converter  300  as follows: rotation is input from rotation shaft  500  coupled to driving ring gear  312 . Driving ring gear  312  rotates pinion gears  306 . Pinion gears  306  rotate following ring gear  304 . When rotation shaft  500  rotates in clockwise direction  334 , hex mover  310  disengages with following ring gear  304  and engages with driving ring gear  312 , and hex mover  310  rotates with driving ring gear  312  together in clockwise direction  334 . When rotation shaft  500  switches from the clockwise rotation direction to the counterclockwise rotation direction, hex mover  310  is pushed away from driving ring gear  312  to following ring gear  304  via the driving gear inner teeth  324  and hex mover driving teeth  322 . Thus, hex mover  310  disengages with driving ring gear  312  and engages with following ring gear  304  via following gear inner teeth  316  and hex mover following teeth  320 . Subsequently, hex mover  310  and following ring gear  304  rotate together. Since rotate shaft  500  rotates in the counterclockwise direction, driving ring gear  312  rotates in the counterclockwise direction, following ring gear  304  rotates in clockwise direction  334 , and hex mover  310  also rotates in clockwise direction  334 . Hex mover  310  rotates hex shaft  302 . Hex mover  310  and hex shaft  302  are configured to always rotate in the same direction of rotation. 
       FIGS.  4 A- 4 B  illustrate an exemplary output cap, wherein  FIG.  4 A  shows a perspective view of an exemplary output cap and  FIG.  4 B  shows a top view of an exemplary output cap, in accordance with an embodiment of the present disclosure. Output cap  400  includes shaft opening  402 , support rod openings  404 , valve channel  406 , pipe caps  408 , and valve openings  410 . 
     Output cap  400  is configured to control fluid flow within single shaft piston motor  1400 , specifically within the pipes of cylindrical body  700  at an output end. Fluid flow within cylindrical body  700  will be described in greater detail below with reference to  FIG.  7   . To control fluid flow, output cap  400  includes pipe caps  408  evenly distributed in 6 directions. Pipe caps  408  may be coupled to several inner pipes of cylindrical body  700  such that fluid from the inner flows to the second chamber of cylindrical body  700 . Pipe caps  408  may include means for sealing the inner pipes (e.g., transfer pipes  116  described in  FIG.  1   ) of cylindrical body  700 , such as, without limitation, rubber seals, gaskets, etc. In contrast, outlet gaps  412 , evenly distributed between pipe caps  408 , are configured to allow fluid from inner pipes (e.g., transfer pipes  116  described in  FIG.  1   ) of cylindrical body  700  to flow to the outlet of single shaft rotation motor  1400 . 
     Support rod openings  404  are configured to accept support rods  506 , and shaft opening  402  is configured to accept rotation shaft  500 , to be described with reference to  FIG.  5    below. Similar to pipe caps  408 , means for sealing may be used for support rod openings  404  and shaft opening  402  to prevent fluid from flowing out of support rod openings  404  and shaft opening  402 . Valve channel  406  and valve openings  410  are configured to provide a mounting means for first forward valve  1202  and second forward valve  1220 , to be described with reference to  FIG.  12 A  below. 
       FIG.  5    illustrates an exemplary rotation shaft and support rods, in accordance with an embodiment of the present disclosure. Support rods  506  are configured to fasten output cap  400  to shaft connector  900 , and thus to input cap  1000 , where output cap  400  and input cap  1000  are each coupled to cylindrical body  700 , and additionally prevent torsion of driving piston  600  (to be described with reference to  FIG.  6   ). Two support rods  506  are shown in the present embodiment. However, as will be appreciated by one skilled in the art, a greater or lesser number of support rods may be used in the present embodiment depending on the specific application of single shaft piston motor  1400 . Support rods  506  may pass through output cap  400  such that output cap threading  514  is exposed above support rod openings  604 . A nut (not shown) may be threaded onto output cap threading  514  such that a portion of support rods  506  may be secured in place. Similarly, shaft connector threading  516  may be used to secure a portion of support rods  506  into support rod openings  902  of shaft connector  900  (to be described with reference to  FIG.  9   ). 
     Rotation shaft  500  is configured to rotate in response to driving piston  600  (to be described with reference to  FIG.  6   ) and provides a rotation input to 2-to-1 rotation converter  300  via shaft head  502 . Shaft head  502  includes head hex  508 , head body  510 , and head lip  512 . Head hex  508  is configured to be coupled to driving ring gear  312  of 2-to-1 rotation converter  300 . Head body  510  is a smooth, intermediate portion of shaft head  502  between head hex  508  and head lip  512  configured to pass through shaft opening  402  of output cap  400 . Head lip  512  is a portion of shaft head  502  and may secure rotation shaft  500  in place against a surface of output cap  400 . A sealing means, such as, without limitation, a gasket, rubber seal, etc., with a means of reducing friction may be used on one or more of head body and head lip to prevent or minimize fluid from leaking through shaft opening  402  of output cap  400  while allowing for free rotation of rotation shaft  500  with low friction. Shaft body  504  is an elongated shaft configured to rotate as driving piston  600  slides along the length of rotation shaft  500 . Thus, shaft body  504  may be matched with shaft opening  602  of driving piston and, in the present embodiment, is a 5 spiral shaft with a star-shaped cross section. However, different configurations of rotation shaft  500  may be used in the present embodiment. For example, without limitation, shaft body  504  may include a greater or lesser number of spirals and thus have a different shaped cross section than shown in  FIGS.  5  and  6   , and accordingly a differently shaped shaft opening  602  of driving piston  600  may be used according to the shape of shaft body  504 . 
       FIG.  6    illustrates an exemplary driving piston, in accordance with an embodiment of the present disclosure. Driving piston  600  is configured to slide along rotation shaft  500  within cylindrical body  700  according to fluid pressure at either side of driving piston  600 . Thus, driving piston  600  may rotate rotation shaft  500  and generate a rotation output for single shaft piston motor  1400 . For example, without limitation, with driving piston  600  moving in a forward direction, rotation shaft  500  may rotate in a clockwise direction. In contrast, with driving piston  600  moving in a reverse direction, rotation shaft  500  may rotate in a counterclockwise direction. Driving piston  600  may include a sealing means at shaft opening  602  and support rod openings  604  such as, without limitation, gaskets, rubber seals, etc. Additionally, driving piston  600  may be of various widths and is not limited to the width shown in  FIG.  6   . 
       FIGS.  7 A- 7 B  illustrate an exemplary cylindrical body, wherein  FIG.  7 A  shows a perspective cross-sectional view of an exemplary cylindrical body and  FIG.  7 B  shows a top view of an exemplary cylindrical body, in accordance with an embodiment of the present disclosure. Cylindrical body  700  includes rotation converter channels  702 , pipe cap openings  704 , second transfer openings  706 , transfer pipes  708 , first outlet openings  710 , first transfer openings  712 , inner cavity  714 , rotation output threading  716 , second outlet openings  718 , input threading  720 , and outlet pipes  722 . In the present embodiment, the cylindrical body may be, for example, without limitation, of a pipe shape, with a circular-outer cross-section, and a large ratio of length to diameter (or size). However, as will be appreciated by one skilled in the art, the outer cross-section of the cylindrical body may be other shapes, such as hexagonal, rectangular with rounded corners, slot-shaped, irregularly-shaped, etc. 
     Cylindrical body  700  is configured to house the remaining components of single shaft piston motor  1400  and is adapted for optimal fluid flow within inner cavity  714  and through transfer pipes  708  and outlet pipes  722 . Inner cavity  714  is an inner portion of cylindrical body  700  and is surrounded by evenly distributed transfer pipes  708  and outlet pipes  722  (as shown in  FIG.  7 B ). Inner cavity  714  is separated into a first chamber and a second chamber by flow piston  600 , where fluid is moved into and out of the first chamber and the second chamber via transfer pipes  708  and outlet pipes  722 . It should be noted that as driving piston  600  slides along rotation shaft  500  within inner cavity  714  of cylindrical body  700 , the sizes of the first chamber and the second chamber are variable relative to each other. For example, without limitation, when driving piston  600  moves in a forward direction, the second chamber decreases in volume while the first chamber increases in volume, and when driving piston  600  moves in a reverse direction, the second chamber increases in volume while the first chamber decreases in volume. Additionally, while transfer pipes  708  and outlet pipes  722  are integrated into cylindrical body  700  in the present embodiment, as will be appreciated by one skilled in the art, external pipes may be used instead of or in combination with transfer pipes  708  and outlet pipes  722  to transfer fluid within cylindrical body  700 . For example, without limitation, an embodiment of the present invention utilizing external piping is shown with reference to  FIGS.  1 A- 1 H . 
     Cylindrical body  700  may be threaded onto a fluid input (e.g., regular drilling pipe) via input threading  720 . The input may provide pressurized fluid to cylindrical body  700 , thus enabling single shaft piston motor  1400  to convert energy from the pressurized fluid to rotation output via driving piston  600  and rotation shaft  500 . Depending on the mode of single shaft piston motor  1400 , the pressurized fluid may be input to either the first chamber or the second chamber. When input in the first chamber, the pressurized fluid causes driving piston  600  to move in the forward direction towards the rotation output. When input in the second chamber, the pressurized fluid causes driving piston  600  to move in the reverse direction towards the fluid input. The inner pipes of cylindrical body  700  enable fluid to be transferred between the first chamber and the second chamber, and similarly from each of the chambers to the output end of cylindrical body  700  opposite the fluid input. 
     When single shaft piston motor is in the first mode, fluid from the input flows directly into the first chamber, moving driving piston  600  in the forward direction and causing fluid in the second chamber to flow through second transfer openings  706  into transfer pipes  708 , out of first transfer openings  712 , through first outlet openings  710 , through outlet pipes  722 , through second outlet openings  718 , and out the outlet side of cylindrical body  700 . Thus, fluid is input to the first chamber, driving piston moves in the forward direction, and fluid flow out from the second chamber. 
     When single shaft piston motor is in the second mode, fluid from the input flows through first transfer openings  712 , through transfer pipes  708 , and out of second transfer openings  706  into the second chamber. Thus, driving piston moves in the reverse direction, fluid from first chamber flows through first outlet openings  710 , through outlet pipes  722 , and out second outlet openings  718  to the output end of cylindrical body  700 . 
     Fluid is controlled within cylindrical body  700  via flow piston  800  (to be described with reference to  FIGS.  8 A- 8 B ), control cylinder  1100  (to be described with reference to  FIGS.  11 A- 11 B ), and a cylinder switch system (to be described with reference to  FIGS.  12 A- 12 B ). An overview of the flow sequence within single shaft piston motor  1400  was described above with reference to  FIGS.  1 A- 1 H . 
     In the present embodiment, cylindrical body  700  includes six transfer pipes  708  and six outlet pipes  722 , where transfer pipes  708  and outlet pipes  722  are alternately distributed within cylindrical body  700 . Namely, outlet pipes  722  are configured to transfer fluid from the first chamber and the second chamber to the output via first outlet openings  710  and second outlet openings  718 , and transfer pipes  708  are configured to transfer fluid between the first chamber and the second chamber via second transfer openings  706  and first transfer opening  712 . The flow mechanisms of outlet pipes  722  and the transfer pipes  708  are shown with reference to  FIGS.  1 A- 1 H . It should be noted that the position of flow piston  800  (to be described with reference to  FIGS.  8 A- 8 B ) determines how fluid flows within cylindrical body  700 . 
     At the output end of cylindrical body  700 , rotation converter channels  702  are configured to mount 2-to-1 rotation converter  300 , and rotation output threading  716  is configured to be threaded with cylindrical body threading  212  of drill bit connector  200 . Thus, 2-to-1 rotation converter  300  and drill bit connector  200  are mountable to cylindrical body  700 . 
       FIGS.  8 A- 8 B  illustrate an exemplary flow piston, wherein  FIG.  8 A  shows a top perspective view of an exemplary flow piston and  FIG.  8 B  shows a bottom perspective view of an exemplary flow piston, in accordance with an embodiment of the present disclosure. Flow piston  800  includes inner passage  802 , annular transfer chamber  804 , trigger passage  806 , flow piston support  808 , and shaft connector  810 . 
     Flow piston  800  is configured to be in a first position and a second position within cylindrical body  700 . For example, without limitation, when flow piston  800  is in the first position, driving piston  600  moves in the forward direction as fluid pressure in the first chamber of cylindrical body  700  is greater than fluid pressure in the second chamber. When flow piston  800  is in the second position, driving piston  600  moves in the reverse direction as fluid pressure in the second chamber of cylindrical body  700  is greater than fluid pressure in the first chamber. 
     Inner passage  802  is an inner cavity of flow piston  800 , and is configured to allow for fluid to flow from the input to the first chamber when driving piston  800  is in the first position. 
     Annular transfer chamber  804  is an intermediate chamber along a periphery of flow piston  800 , and is formed with cylindrical body  700 . Annular transfer chamber  804  is configured to allow for transfer of fluid from the second chamber to the output when flow piston  800  is in the first position, and configured to allow for transfer of fluid from the input to the second chamber when flow piston  800  is in the second position. 
     Trigger passage  806  are pass-through channels for rear triggers  1210  (to be described with reference to  FIGS.  12 A- 12 B ). 
     Flow piston support  808  is a supporting beam perpendicular to an opening of inner passage  802  and includes shaft connector  810  as a mounting location for flow piston connector  1102  of control cylinder  1100  (to be described with reference to  FIG.  11   ). In combination with control cylinder  1100 , forward triggers  1208 , and rear triggers  1210 , flow piston is configured to move between the first position and the second position. 
       FIG.  9    illustrates an exemplary shaft connector, in accordance with an embodiment of the present disclosure. Shaft connector  900  includes support rod openings  902  and rotation shaft opening  904 . 
     Shaft connector  900  is configured to support support rods  506  via support rod openings  902  and rotation shaft  500  via rotation shaft opening  904 . Shaft connector  900  is configured to be mounted within inner passage  802  of flow piston  800  and on input cap  1000  via shaft connector recess  1012  (to be described with reference to  FIGS.  10 A- 10 B ). 
       FIGS.  10 A- 10 B  illustrate an exemplary input cap, wherein  FIG.  10 A  shows a perspective view of an exemplary input cap and  FIG.  10 B  shows a top view of an exemplary input cap, in accordance with an embodiment of the present disclosure. Input cap  1000  includes inner pipe caps  1002 , cylinder pipe openings  1004 ,  1010 , and  1018 , valve openings  1006 , inlet openings  1008 , shaft connector recesses  1012 , shaft connector bolt openings  1014 , and cylinder opening  1016 . 
     Input cap  1000 , in combination with flow piston  800 , is configured to control fluid input of single shaft piston motor  1400 . Fluid from the input of single shaft piston motor  1400  flows into inlet openings  1008  and, depending on the position of flow piston  800 , flows into either first chamber or second chamber of cylindrical body  700 . When flow piston  800  is in the second position, inlet openings  1008  of input cap  1000  and first transfer openings  712  of cylindrical body  700  are sealed within annular transfer chamber  804  of flow piston  800 ; thus, inlet openings  1008  are connected to first transfer openings  712  and fluid from the input flows through inlet openings  1008 , through first transfer openings  712 , and into the second chamber of cylindrical body  700 . 
     When flow piston  800  is in the first position, fluid from the input flows through inlet openings  1008 , through inner passage  802  of flow piston  800 , and into the first chamber of cylindrical body  700 . 
     Input cap  1000  further includes mounting means for the cylinder switch system (to be further described with reference to  FIGS.  12 A- 12 B  and  FIGS.  13 A- 13 B ). The mounting means includes, for example, without limitation, cylinder pipe openings  1004 ,  1010 , and  1018 , valve openings  1006 , inlet openings  1008 , and cylinder openings  1016 . The mounting means are generally openings in input cap  1000  configured to support the cylinder switch system. 
       FIGS.  11 A- 11 C  illustrate an exemplary control cylinder, wherein  FIG.  11 A  shows a front perspective view of an exemplary control cylinder,  FIG.  11 B  shows a rear perspective view of an exemplary control cylinder, and  FIG.  11 C  shows a right cross-sectional view of an exemplary control cylinder in accordance with an embodiment of the present disclosure. Control cylinder  1100  includes flow piston connector  1102 , first control cylinder opening  1104 , second control cylinder opening  1106 , first cylinder chamber  1108 , control cylinder piston  1110 , second cylinder chamber  1112 , control cylinder shaft  1114 , and control cylinder cap  1116 . 
     Control cylinder  1100  is configured to move flow piston  800  between the first position and the second position via control cylinder shaft  1114  and flow piston connector  1102 . Flow piston connector  1102  may be coupled to flow piston support  808  via a coupling means, such as, without limitation, a screw, fastener, adhesive, bracket, etc. As shown in  FIG.  11 C , flow piston  800  is in a first position and corresponds to the first position of flow piston  800 . In the first position, first cylinder chamber  1108  is of a smaller volume when compared to second cylinder chamber  1112 . In contrast, when in the second position, control cylinder piston  1110  may be adjacent to second control cylinder opening  1106  such that flow piston  800  is in the second position. In the present embodiment, movement of control cylinder piston  1110  is powered by fluid pressure. Namely, when control cylinder piston  1110  is to move from the first position to the second position, pressurized fluid may enter control cylinder  1100  via first control cylinder opening  1104 . Thus, first cylinder chamber  1108  has a higher pressure than second cylinder chamber  1112  and control cylinder piston  1110  moves toward second control cylinder opening  1106  such that control cylinder piston  1110  is in the second position. 
     Conversely, when control cylinder piston  1110  is in the second position and is to move into the first position, pressurized fluid enters control cylinder  1100  via second control cylinder opening  1106 ; causing second cylinder chamber  1112  to be of a higher pressure than first cylinder chamber  1108 . Thus, control cylinder piston  1110  moves towards first control cylinder opening  1104  such that control cylinder piston  1110  is in the first position. 
     Control cylinder cap  1116  may seal an end of control cylinder  1100 , and is configured to be threaded onto both the end of control cylinder  1100  and into control cylinder opening  1016  of input cap  1000 . 
       FIGS.  12 A- 12 B  illustrate an exemplary cylinder switch system, wherein  FIG.  12 A  shows a section of an exemplary cylinder switch system integrated with an output cap and  FIG.  12 B  shows a section of an exemplary cylinder switch system integrated with an input cap, in accordance with an embodiment of the present disclosure The cylinder switch system includes first forward valve  1202 , first cylinder pipe  1204 , second cylinder pipe  1206 , forward triggers  1208 , rear triggers  1210 , third cylinder pipe  1212 , fourth cylinder pipe  1214 , first rear valve  1216 , second rear valve  1218 , and second forward valve  1220 . The first forward valve  1202 , second forward valve  1220 , first rear valve  1216 , and second rear valve  1218  are normally-closed valves. In the present disclosure, normally-closed valves may be valves that are only open during triggering, and remain closed prior to and after being triggered to open. 
     The combination of the triggers (including forward triggers  1208  and rear triggers  1210 ), control cylinder pipes (including first cylinder pipe  1204 , second cylinder pipe  12016 , third cylinder pipe  1212 , and fourth cylinder pipe  1214 ), and valves (including first forward valve  1202 , first rear valve  1216 , second rear valve  1218 , and second forward valve  1220 ) of the cylinder switch system are configured to control the position of control cylinder  1100 . 
     Forward triggers  1208  and rear triggers  1210  are configured to be pressed by driving piston  600 . When control cylinder  1100  is in the first position, driving piston  600  moves in the forward direction and activates forward triggers  1208 . When forward triggers  1208  are activated, the valves of the control switch system are configured to move control cylinder  1100  from the first position to the second position such that driving piston  600  moves in the reverse direction. Specifically, when forward triggers  1208  are activated, first forward valve  1202  is closed while second forward valve  1220  is opened. Thus, fluid flows through first cylinder pipe  1204 , through second forward valve  1220 , through second cylinder pipe  1206 , and into first control cylinder opening  1104  of control cylinder  1100 . Simultaneously, in response to activation of forward triggers  1208 , first rear valve  1216  is closed while second rear valve  1218  is opened. Thus, fluid is output from control cylinder  1100  via second control cylinder opening  1106 , flows through fourth cylinder pipe  1214 , through second rear valve  1218 , and through third cylinder pipe  1212 . 
     It should be noted that control cylinder pipes  1204 ,  1206 , and  1212  pass through outlet pipes  722  of cylindrical body  700 . For example, without limitation, third cylinder pipe  1212  may output fluid into an outlet pipes of cylindrical body  700 . 
     When control cylinder  1100  is in the second position, driving piston  600  moves in the reverse direction and activates rear triggers  1210 . When rear triggers  1210  are activated, the valves of the control switch system are configured to move control cylinder  1100  from the second position to the first position such that driving piston  600  moves in the forward direction. Specifically, when rear triggers  1210  are activated, first rear valve  1216  is opened while second rear valve  1218  is closed. Thus, fluid flows into first rear valve  1216 , through fourth cylinder pipe  1214 , and into second control cylinder opening  1106  of control cylinder  1100 . Simultaneously, in response to activation of rear triggers  1210 , first forward valve  1202  is opened and second forward valve  1220  is closed. Thus, fluid flows out of first control cylinder opening  1104  of control cylinder  1100 , through second cylinder pipe  1206 , and out of first forward valve  1202  to the output of single shaft piston motor  1400 . As such, control cylinder  1100  is successfully transitioned from the second position to the first position, causing driving piston  600  to move in the forward direction. 
       FIGS.  13 A- 13 B  illustrate an incorporated exemplary cylinder switch system, wherein  FIG.  13 A  shows a section integrated with an output cap and  FIG.  13 B  shows a section integrated with an input cap, in accordance with an embodiment of the present disclosure. As shown, the cylinder switch system (described with reference to  FIGS.  12 A- 12 B ) is integrated with output cap  400  of  FIGS.  4 A- 4 B  and input cap  1000  of  FIGS.  10 A- 10 B . 
     With reference to  FIG.  13 A , first forward valve  1202  and second forward valve  1220  are securely seated into valve channel  406 , while first cylinder pipe  1204  and second cylinder pipe  1206  are configured to pass through outlet gaps  412  of output cap  400 . Thus, the portion of the cylinder switch system as shown in  FIG.  13 A  is incorporated into an output cap for single shaft piston motor  1400 . 
     With reference to  FIG.  13 B , first rear valve  1216  and second rear valve  1218  are configured to pass through valve openings  1006  of input cap  1000 , while cylinder  1100  is configured to pass through cylinder opening  1016 . Additionally, first cylinder pipe  1204  and second cylinder pipe  1206  are configured to pass through cylinder pipe opening  1010  and cylinder pipe opening  1018 , respectively. Third cylinder pipe  1212  is similarly configured to pass through cylinder pipe opening  1004 . Thus, the portion of the cylinder switch system as shown in  FIG.  13 A  is incorporated into an input cap for single shaft piston motor  1400 . 
       FIG.  14    illustrates a cross-sectional view of a single-shaft piston motor, in accordance with an embodiment of the present disclosure. Single shaft piston motor  1400  encompasses a combination of one or more components described with reference to  FIGS.  2 A- 13 B  above. In particular, the one or more components of  FIGS.  2 A- 13 B  may be coupled together to form single shaft piston motor  1400 . It should be appreciated that single shaft piston motor  1400  is not limited to including the one or more components of  FIGS.  2 A- 13 B , and may include additional or fewer components than those listed above. 
     Single shaft piston motor  1400  may include cylindrical body  700  to house the remaining components of single shaft piston motor  1400 , where cylindrical body  700  may be secured to drill bit connector  200  through rotation output threading  716 , and to a fluid input of single shaft piston motor  1400  through input threading  720 . 
     Drill bit connector  200  may be coupled to an output of 2-to-1 rotation converter  300 . 2-to-1 rotation converter  300  may be coupled, at its input, to rotation shaft  500 . Rotation shaft  500  may pass through output cap  400 , while output cap  400  is secured to support rods  506 . Driving piston  600  may be slidably connected to rotation shaft  500 . Rotation shaft  500  may be coupled at its rear end to shaft connector  900 . At an input portion of cylindrical body  700 , the control means, including but not limited to flow piston  800 , input cap  1000 , and control piston  1100  may be mounted to cylindrical body  700 . Specifically, control cylinder may pass through input cap  1000  and may be coupled to flow piston  800 . 
     Single shaft piston motor  1400  may include various elements not mentioned in  FIGS.  2 A- 13 B  but are nonetheless incorporated into the present invention. For example, without limitation, output cap bearings  1402  and shaft connector bearings  1404  may be used between rotation shaft  500  and output cap  400 , and between rotation shaft  500  and shaft connector  900 , respectively, to facilitate the rotation of rotation shaft  500 . In another example, various screws, nuts, bolts, and other such fastening means may be used within single shaft piston motor  1400  to enable the coupling of the one or more components to each other. 
       FIG.  15    illustrates a cross-sectional view of a double-shaft piston motor, in accordance with an embodiment of the present disclosure. The present invention is not limited to single shaft piston motor  1400 , and may include, for example, without limitation, double shaft piston motor  1500 . Double shaft piston motor  1500  may be of a similar structure to single shaft piston motor  1400 , except adapted to include first rotation shaft  1504  and second rotation shaft  1506 . Additionally, double shaft piston motor  1500  may include a different means for converting rotation from first rotation shaft  1504  and second rotation shaft  1506  to rotation output  1502 . The specific structure of rotation output  1502  is described below, with reference to  FIGS.  16 A- 16 B . 
       FIGS.  16 A- 16 B  illustrate an exemplary rotation output for a double-shaft piston motor, wherein  FIG.  16 A  shows a first view of a rotation output for a double-shaft piston motor, and  FIG.  16 B  shows a second view of a rotation output for a double-shaft piston motor, in accordance with an embodiment of the present disclosure. Rotation output  1502  includes, for example, without limitation, outer thread  1602 , outer gear  1604 , first inner gear  1606 , first hex mover  1608 , springs  1610 , bearing needles  1612 , outer cylinder  1614 , inner cylinder  1616 , inner threading  1618 , second inner gear  1620 , second hex mover  1622 , and bearing outer body  1624 . 
     Rotation output  1502  is configured to convert the rotation of first rotation shaft  1504  and second rotation shaft  1506  into a single output rotation direction to power, for example, an oil and gas well drill bit (e.g., drill bit  1720  in  FIG.  17   ). The spiral configuration of first rotation shaft  1504  and second rotation shaft  1506  are in opposite directions such that, as the driving piston moves forward and backward along the lengths of first rotation shaft  1504  and second rotation shaft  1506 , first rotation shaft  1504  and second rotation shaft  1506  rotate in opposite directions. Output ends of first rotation shaft  1504  and second rotation shaft  1506  include first hex mover  1608  and second hex mover  1622 , respectively, where first hex mover  1608  is matched with first inner gear  1606  and second hex mover  1622  is matched with second inner gear  1620 . The rotation direction of the respective rotation shaft determines an engaged state or a disengaged state of the hex movers in relation to the inner gears. In the present embodiment, the hex movers are in an engaged state when the attached rotation shaft rotates in a clockwise direction. 
     For example, without limitation, the movement of the driving piston in the forward direction causes first rotation shaft  1504  to rotate in a clockwise direction and second rotation shaft  1506  to rotate in a counterclockwise direction. Thus, first hex mover  1608  and first inner gear  1606  are in an engaged state, while second hex mover  1622  and second inner gear  1620  are in a disengaged state. While in the engaged state, first hex mover  1608  is configured to rotate first inner gear  1606 . In contrast while in the disengaged state, the rotation of second hex mover  1622  is not transferred to second inner gear  1620 , and second inner gear  1620  rotates independently from rotation shaft  1506 . Thus, rotation from first rotation shaft  1504  is transferred to outer gear  1604  via first inner gear  1606 . In the present configuration, second inner gear  1620  freely rotates with outer gear  1604 , and rotation is not transferred from second rotation shaft  1506  to rotation output  1502 . It should be noted that the teeth of first inner gear  1606  and second inner gear  1620  are engaged with the teeth of outer gear  1604 , but are not engaged with each other. 
     When the driving piston moves in the reverse direction, first rotation shaft  1504  rotates in a counterclockwise direction and second rotation shaft  1506  rotates in a clockwise direction. Thus, second hex mover  1622  and second inner gear  1620  are in an engaged state, and rotation is transferred from second rotation shaft  1506  to rotation output  1502 , while rotation is not transferred from first rotation shaft  1504  to rotation output  1502 . 
     Each of rotation shafts  1504  and  1506  may include springs  1610  configured to apply compression to first hex mover  1608  and second hex mover  1622 , to help engagement of hex movers and inner gears but still allow disengagement. When drilling piston is switching from forward movement to reverse movement, the structure of first hex mover  1608  and first inner gear  1606  forces first hex mover  1608  to move away from first inner gear  1606 , while spring  1610  pushes second hex mover  1622  to engage with second inner gear  1620 . In contrast when drilling piston is switching from reverse movement to forward movement, the structure of second hex mover  1622  and second inner gear  1620  forces second hex mover  1622  to move away from second inner gear  1620 , while spring  1610  pushes first hex mover  1608  to engage with first inner gear  1606 . Thus, only when rotation shaft rotates clockwise, its hex mover and inner gear engages with each other and inner gear rotates clockwise, to rotate outer gear  1604  clockwise. 
     Outer gear  1604  is coupled to outer cylinder  1614 , and outer cylinder  1614  is coupled to inner cylinder  1616  such that the rotation from the rotation shafts is transferred to outer gear  1604 , and rotation from outer gear  1604  is transferred from outer cylinder  1614  to inner cylinder  1616 . Rotation output  1502  may also include bearings  1612  between outer gear  1604  and outer casing  1628  to facilitate the rotation of outer gear  1604 . Inner cylinder  1616  may include inner threading  1618 , where an output attachment may be threaded. In the present embodiment, the output attachment may be, for example, without limitation, a drill bit. However, as will be appreciated by one skilled in the art, other output attachments may also be used. 
     While the present invention may include embodiments such as single shaft piston motor  1400  and double shaft piston motor  1500 , alternative embodiments are also within the scope of the present invention, and embodiments with a greater number of rotation shafts may be used. With an even number of rotation shafts (e.g., 4, 6, 8, etc.), functionality may be similar to that of double shaft piston motor  1500 , wherein half of the rotation shafts may be in an engaged state while the other half of the rotation shafts may be in the disengaged state. 
       FIG.  17    illustrates an operating environment of a piston motor system, in accordance with an embodiment of the present disclosure. 
     Well drilling system  1700  includes, for example, without limitation, drilling derrick  1702 , drilling mud pump  1704 , drilling mud container  1706 , control system  1712 , wellbore walls  1714 , drilling pipe  1716 , piston motor  1718 , drill bit  1720 , and blowout preventer  1722 . 
     Well drilling system  1700  may be used to efficiently drill beneath ground surface  1708  and through subsurface rocks  1710 . Drilling derrick  1702  may be used as a support structure for system  1700 , and allows for new sections of drill pipe  1716  to be added to system  1700  as drilling progresses. Different types of drilling derricks may be used depending on the specific application, such as single, double, triple, quadric, conventional, slant, etc. Further, drill piston motor  1718  may be coupled to any suitable drill bit known in the art, such as, without limitation, roller cone bits, mill tooth bits, insert drilling bits, diamond drilling bits, Polycrystalline Diamond Compact bits, thermally stable polycrystalline bits, etc. Sections of wellbore walls  1714  and drill pipe  1716  may be added to system  1700  during drilling operation. Drilling pipe  1716  may provide fluid to piston motor  1718  via drilling mud pump  1704 , where fluid may pass through piston motor  1718  and drill bit  1720  and be discarded to the surface via a space between drilling pipe  1716  and wellbore walls  1714 . The fluid may be recycled to drilling mud container  1706  as an input to drilling mud pump  1704 . 
     Control system  1712  may be any type of drilling control system known in the art, and may communicate with drilling mud pump  1704 , drilling derrick  1702 , and blowout preventer  1722  via wired or wireless connection. In one embodiment, control system  1712  may be integrated with drilling mud pump  1704  as a single entity. Control system  1712  may also communicate with piston motor  1718  to determine a status of the drilling operation and provide for failure detection of well drilling system  1700 . For example, without limitation, a decrease in torque or rate of penetration (ROP) of the drilling system may be indicative of an error within the system, and control system  1712  may be used to automatically or manually pause the drilling operation such that diagnostic procedures may be completed. 
       FIGS.  18 A- 18 B  illustrate a fluid flow sequence of a second embodiment of an exemplary piston motor system, wherein  FIG.  18 A  shows an exemplary flow piston moving from a first position to a second position and  FIG.  18 B  shows an exemplary flow piston moving from a second position to a first position, in accordance with an embodiment of the present disclosure. Secondary piston motor  1800  is substantially similar to piston motor  100 , albeit a change in the control system for flow piston  112 . In the present embodiment, secondary piston motor  1800  includes first input valve  1802 , cylinder inlet pipe  1804 , second input valve  1806 , first cylinder chamber  1808 , first output valve  1810 , control cylinder piston  1812 , second cylinder chamber  1814 , second output valve  1816 , control cylinder shaft  1818 , and cylinder outlet pipe  1820 . The first input valve  1802 , second input valve  1806 , first output valve  1810 , and second output valve  1816  are normally-closed valves. 
     Control of flow piston  112  in the present invention may be achieved through various different means, and results in flow piston  112  moving between the first and second positions and thus control the direction of movement of driving piston  164 . While the present embodiment illustrates a fluid-powered control system (as shown with reference to  FIGS.  1 A- 1 H  and  FIGS.  18 A- 18 B ), alternative control means may be used, such as, without limitation, mechanical motor control, control through the use of electrical signaling, pneumatic control, etc.  FIGS.  18 A- 18 B  illustrate an exemplary alternative fluid control means for the present invention. 
     After driving piston  164  reaches a forward end of piston motor  1800  and activates forward triggers (not shown), flow piston  112  is configured to move from a first position to a second position via the control system. Activation of the forward triggers causes second input valve  1806  to open causing fluid to flow from input  102  into second cylinder chamber  1814  via cylinder inlet pipe  1804 . Thus, pressure in second cylinder chamber  1814  is of a higher pressure than the pressure in first cylinder chamber  1808 , causing control cylinder piston  1814  (and thus flow piston  112  via control cylinder shaft  1818 ) to move from the first position to the second position. Simultaneously, first output valve  1810  is opened in response to activation of the forward triggers, and fluid in first cylinder chamber  1808  is forced through cylinder outlet pipe  1820  to output  124 . 
     As shown in  FIG.  18 B , after driving piston  164  reaches a rear end of piston motor  1800  and activates rear triggers (not shown), flow piston  112  is configured to move from a second position to a first position via the control system. Activation of the rear triggers causes first input valve  1802  to open, causing fluid to flow from input  102  into first cylinder chamber  1808  via cylinder inlet pipe  1804 . Thus, pressure in first cylinder chamber  1808  is of a higher pressure than pressure in second cylinder chamber  1814 , causing control cylinder piston  1812  (and thus flow piston  112  via control cylinder shaft  1818 ) to move from the second position to the first position. Simultaneously, second output valve  1816  is opened in response to activation of the rear triggers, and fluid in second cylinder chamber  1814  is forced through cylinder outlet pipe  1820  to output  124 . 
       FIG.  19    illustrates a fluid flow sequence of a third embodiment of an exemplary piston motor system, in accordance with an embodiment of the present disclosure. 
     Piston motor system  1900  includes, for example, without limitation, battery  1902 , switch  1904 , wiring  1906 , motor  1908 , and motor shaft  1910 . 
     In piston motor system  1900 , flow piston  112  moves between the first position and the second position via motor  1908 . Motor  1908  is preferably a direct current (DC) motor, but may be any suitable motor known in the art, such as, without limitation, an alternating current (AC) motor, direct drive, linear motor, etc. Motor  1908  may be coupled to battery  1902  via wiring  1906 , where battery  1902  is configured to power motor  1908 . In the present embodiment, switch  1904  may be used to control motor  1908 , and cause motor shaft  1910  to move flow piston  112  between the first position and the second position. For example, without limitation, when driving piston reaches a forward end of piston motor  1900 , forward triggers (not shown) are triggered and signal switch  1904  to activate, causing motor  1908  to move flow piston  112  from the first position to the second position via motor shaft  1910 . Similarly, when driving piston reaches a rear end of piston motor  1900 , rear triggers (not shown) are triggered and signal switch  1904  to activate, causing motor  1908  to move flow piston  112  from the second position to the first position via motor shaft  1910 . Switch  1904  may communicate with forward triggers and rear triggers via wireless or wired connection. 
     Torque (τ) of the motor results from the pressure difference on the two sides of driving piston (ΔP), the piston diameter (D), the driving shaft stage length (length for 360° rotation; L), and the driving shaft diameter (d). With ignoring friction between driving piston and chamber wall and friction between driving piston and ration shaft, the torque of the piston motor of the present disclosure may be calculated according to: 
     
       
         
           
             
               
                 
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     For example, without limitation, pump pressure may be 8 MPa and generates a 5 MPa pressure difference on the two sides of the driving piston, the driving shaft stage length is 600 mm, driving piston diameter is 100 mm, and driving shaft diameter is 30 mm, the torque is about 3400 N·m (˜2500 ft-lb). The pressure difference is mainly controlled by pump pressure as well as friction between the fluid and the drilling pipe, friction between the driving piston and chamber wall, and hydrostatic pressure difference between the drilling pipe inside and the drilling pipe-wellbore annular space. In a preferred embodiment, the pump pressure may be 1 MPa-10 MPa, even higher. 
     The rotation rate (ROP) may depend on the flow rate (R), the piston diameter (D), the driving shaft stage length (L), and the driving shaft diameter (d). The rotation rate of the piston motor of the present disclosure may be calculated according to: 
     
       
         
           
             
               
                 
                   
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                         L 
                       
                     
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     For example, without limitation, flow rate may be 500 liter/minute (131 gallons per minute), the driving shaft stage length is 300 mm, driving piston diameter is 100 mm, and driving shaft diameter is 30 mm, resulting in a rotation rate of approximately 230 rpm. The flow rate may be mainly controlled by the pump rate, and in a preferred embodiment, may be up to 500 gpm (gallons per minute). 
     The foregoing description of the present disclosure, along with its associated embodiments, has been presented for purposes of illustration only. It is not exhaustive and does not limit the present disclosure to the precise form disclosed. Those skilled in the art will appreciate from the foregoing description that modifications and variations are possible considering the said teachings or may be acquired from practicing the disclosed embodiments. 
     Likewise, the steps described need not be performed in the same sequence discussed or with the same degree of separation. Various steps may be omitted, repeated, combined, or divided, as necessary to achieve the same or similar objectives or enhancements. Accordingly, the present disclosure is not limited to the said-described embodiments, but instead is defined by the appended claims considering their full scope of equivalents.