Patent Publication Number: US-11041362-B2

Title: Production tubing flow diversion valve

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application is a continuation application that claims priority from U.S. patent application Ser. No. 15/755,003, filed Feb. 23, 2018, which is a National Stage Entry of PCT/US2016/047758, filed Aug. 19, 2016; which itself claims priority from U.S. provisional application No. 62/208,915, filed Aug. 24, 2015. The entireties of U.S. Ser. No. 15/755,003, PCT/US2016/047758 and U.S. 62/208,915 are incorporated herein by reference. 
    
    
     FIELD OF THE INVENTION 
     The present invention relates to a flow diversion apparatus. In particular, the invention relates, but is not limited, to a flow diversion valve for use with one or more submersible pumps in hydrocarbon producing wells to enable fluid within tubing positioned above the pumps to flow into the tubing annulus when pump operation ceases or there is a backflow of fluid down through the tubing. 
     BACKGROUND TO THE INVENTION 
     Reference to background art herein is not to be construed as an admission that such art constitutes common general knowledge. 
     In the extraction of hydrocarbon resources from beneath the earth&#39;s surface it is often necessary to overcome a low or negative pressure differential between the pressure of the hydrocarbon fluids in the reservoir pores and the hydrostatic head of that fluid in wells penetrating the reservoir from the surface. This is often achieved using a submersible pump that adds energy to a fluid to increase its flow rate and static pressure. Typical submersible pumps either employ downhole motors, such as electrical submersible pumps, or alternatively surface motors, such as reciprocating pumps and rotary progressive cavity pumps (PCP). Reciprocating and rotary pump types are activated by a rod string that is installed inside the production tubing. 
     In some embodiments, the pump is directly in line with the production tubing. When the pump shuts down, either planned or unplanned, fluid may flow back down the tubing and into the outflow port of the pump. This may occur until the level of fluid in the tubing equals that in the tubing annulus surrounding the tubing. In other situations, the pressure within the tube may increase, pushing fluid back down the tubing and into the pump. Whatever the cause, a reverse flow of fluid into the pump can cause mechanical damage. For example, the fluid may possibly cause spinning of the pump in reverse. The downward flow through the pump will also bring any solids entrained in the fluid back into the pump. Should this occur, the solids settle and pack in impellers and bearings and become impregnated in exposed elastomers, causing damage to the pump on later restarting, or cause the pump to seize completely if the torque required to turn the solids-laden pump exceeds the torque capacity of the drive motor. Also, at times, the tubing string or the pump can pack off or plug after a shut down. This may prevent flow back down the tubing. If the tubing does not drain, the operator may then have to bail out the production fluid before pulling the pump and tubing. Bailing involves running a bailer on a wireline repeatedly down into the tubing, taking time. This downtime can result in lost production and increased expenses for workmen and materials. Preventing solids from falling back into the pump is therefore desirable to prolong pump run life and reduce frequency of costly workovers. 
     One prior art approach is described in U.S. Pat. No. 6,289,990 awarded to D. B. Dillon et al, entitled “Production Tubing Shunt Valve”, which describes apparatus and methods for preventing solids from falling back into electrical submersible pumps. However, the apparatus claimed does not include a passageway for a rod string through the centre of the Production Tubing Shunt Valve needed to operate and protect the progressive cavity pumps. 
     Another prior art approach is described in U.S. Pat. No. 8,545,190 awarded to Lawrence Osborne, which describes a shunt valve device that can be used with progressive cavity pumps, but which does not incorporate means for disassembly of the valve to replace damaged or worn parts and thus has a limited run life. Moreover, with ready means for disassembly, typically the potential for the valve to fail during use, particularly due to the torque induced along a flow string, is increased. 
     OBJECT OF THE INVENTION 
     It is an aim of this invention to provide a flow diversion (valve) apparatus which overcomes or ameliorate one or more of the disadvantages or problems described above, or which at least provides a useful alternative. 
     By way of example only, one objective of the present invention is to prevent or divert the buildup of solids in downhole submersible pumps, including progressive cavity pumps. Alternatively, or additionally, an objective of the present invention is to provide a flow diversion valve that can be fully cleaned, inspected and redressed between workovers to replace worn seals, fatigued closure mechanisms and corroded or eroded parts, and which is fluidly connected to the submersible pump, wherein the flow diversion valve automatically diverts hydrocarbons or other fluids and any entrained solids present in the production string above the pump away from the submersible pump outlet when pump operation is shutdown. 
     A further potential objective for the flow diversion valve actuator mechanism is to be resistant to abrasion by solids entrained in the fluid, reduce permanent pressure loss resulting from upward flow of the fluid past the actuator and include a means to enable the actuator mechanism to be retrieved using conventional fishing equipment should the rod string passing through the actuator become parted from the flow diversion valve. 
     Yet another potential objective is to provide a valve shuttle, actuator, etc., within the flow diversion valve contained within a multi-part housing. 
     Other preferred objects of the present invention are apparent from the following description. 
     SUMMARY OF INVENTION 
     A flow diversion valve comprising: 
     a valve body including an upper housing releasably connected to a lower housing, the upper housing and lower housing being configured to accommodate a rotating rod therethrough; 
     a shuttle positioned within the valve body, the shuttle being configured to move to cover one or more spill ports of the valve body; and 
     a releasable locking member, 
     wherein the releasable locking member is positioned between the upper housing and the lower housing to assist in preventing relative movement therebetween. 
     Preferably, the upper housing is threadingly connected to the lower housing. Normally, the upper housing is threadingly connected to the lower housing with the handedness of the threads being in the same direction as a torque generated by a pump. Typically, the upper housing is threadingly connected to the lower housing with a left-handed thread. 
     Preferably, the releasable locking member is releasably connected to the valve body. Typically, the releasable locking member assists in preventing the upper housing disengaging from the lower housing. Normally, the releasable locking member assists in preventing the upper housing sliding along the lower housing. Typically, the releasable locking member assists in preventing the lower housing moving in a downward direction. 
     Preferably, the releasable locking member includes a locking body. Preferably, the locking body has an aperture therein. Typically, the locking body includes two apertures extending therethough. Typically, the locking body is configured to be received into a locking aperture of the valve body. Normally, the locking aperture of the valve body is at least located in the lower housing. Preferably, the locking aperture extends between the lower housing to the upper housing. Typically, the locking aperture includes a threaded portion. Preferably, the threaded portion is located in the upper housing and/or the lower housing. In a further form, the locking body is in the form of a screw. In another form, the locking body forms a toggle clamp and/or a latch. 
     Preferably, detaching the upper housing from the lower housing allows access to valve components such as the shuttle, the spring and/or various seats and seals. This access allows, for example, the valve components to be cleaned, inspected and redressed. It also allows replacement of, for instance, worn, fatigued, corroded and/or eroded components as will be described below. 
     Preferably, the valve body is manufactured from heat, pressure and corrosion resistant alloys, such as stainless steel. Typically, the valve body is manufactured from high tensile steel. Preferably, the high tensile steel includes chromium-molybdenum (chromoly) steel. Normally, the valve body is manufactured from higher tensile material compared to the metallurgy of the production tubing adjacent thereto. Typically, the valve body material may be coated. Typically, the valve body can be made from combinations of the above. In a further form, preferably the valve body includes non-ferritic material. 
     Normally, the upper housing and the lower housing each include an aperture therethrough to accommodate the rotating rod. Typically, the apertures share the same longitudinal axis. 
     Preferably, the valve body includes one or more threaded connections that are configured to connect to production tubing. Normally, the one or more threaded connections include two threaded connections that are respectively located on the ends of the upper housing and the lower housing. Typically, the one or more threaded connections extend around an outside surface of the lower housing. Normally, the one or more threaded connections extend around an inside surface of the upper housing. Preferably, the one or more threaded connections are tapered. Normally, a torque ring is included between the production tubing and the one or more threaded connections. Typically, the torque ring is situated adjacent an end of the production tubing and next to the one or more threaded connections. Preferably, the torque ring is resiliently flexible. Preferably, the torque ring includes plastic. Preferably, the plastic is in the form of rubber. 
     Preferably, opening and/or closing of the one or more spill ports is controlled by movement of the shuttle and/or the actuator. Typically, the shuttle is a cylindrical shape body substantially matching the radius of the interior of the valve body. Normally, the upper end of the shuttle has one or more seats that correspond with one or more seats on the bottom of the actuator. Typically, a first seat is located on a first face (upper surface) of the shuttle and is for sealing against a first seat closure on a lower end of an actuator. Preferably, in response to the first seat closure of the actuator sealing against the first seat of the shuttle, fluid flow is directed out of the one or more spill ports. 
     Normally, a valve shuttle seat is located on the valve body. Typically, the valve shuttle seat is located on the upper housing. Preferably, a second seat is located on the shuttle for engaging the valve shuttle seat. Normally, the second seat is on an upper portion of the shuttle. Typically, in response to the second seat of the shuttle sealing against the valve shuttle seat, fluid flow is directed upwards along the flow diversion valve. Preferably, the aperture of the upper housing tapers inward from the top of the upper housing towards the valve shuttle seat. 
     Normally, the shuttle is biased by a spring that assists in moving the shuttle to cover the one or more spill ports of the valve body. Preferably, the spring is located substantially between a shuttle spring end and a valve body support. Normally, the valve body support is located beneath the second seat of the shuttle. Typically, the valve body support is in the form of a ledge. Preferably, the valve body support supports a bottom surface of the spring. Preferably, the valve body support does not support an internal surface of the spring. Preferably, the ledge is substantially L-shaped and is open to the apertures extending through the upper housing and/or lower housing such that the spring is not supported on the internal surface. 
     Normally, a valve center line is shared by the longitudinal axis of the apertures extending through the upper housing and lower housing, as well as the valve body, the shuttle, and/or the actuator. 
     Typically, the actuator has a bore for accepting the rotatable rod therethrough. Preferably, the actuator is for translating along the rotatable rod. Preferably, the rotatable rod is connected and supplies rotational power to a rotor in a submersible pump positioned beneath the flow diversion valve. 
     Preferably, the actuator includes a non-metallic sleeve. Preferably, the non-metallic sleeve is located on an inner portion of the actuator. Preferably, the non-metallic sleeve includes plastic. Preferably, the non-metallic sleeve includes a thermoplastic. Preferably, the thermoplastic includes poly ether ether ketone (PEEK). Preferably, in a further embodiment, the inner sleeve includes ceramic. 
     Preferably, the actuator includes an upper shell that is connected to a lower shell. Preferably, the upper shell is threadingly connected to the lower shell. Preferably, the non-metallic sleeve is located between the upper shell and the lower shell. Preferably, the non-metallic sleeve is situated inside the upper shell and the lower shell such that it is configured to slide over the rotating rod. 
     Preferably, the actuator includes a first conical shaped end and a second conical shaped end. Typically, the first conical shaped end is located on a lower portion of the actuator and the second conical shaped end is located on an upper portion of the actuator. Preferably, the first conical shaped end is tapered at a different angle to the second conical shaped end. Normally, the taper of the first conical shaped end is more inclined than the taper of the second conical shaped end. Preferably, the first conical shaped end includes the first seat closure. 
     Preferably, the actuator includes a ferromagnetic component. Preferably, the ferromagnetic component is a permanent magnet. Preferably, the ferromagnetic component is in the form of a ring. Preferably, the ring is magnetic. 
     Preferably, a spring is fitted on a top portion of the actuator. Preferably, the spring fitted on the top portion of the actuator acts as a shock absorber. Preferably, the spring fitted on the top portion of the actuator is configured to be positioned over the rotating rod. Preferably, in response to the actuator moving up and the spring impacting with a portion of the production string, the spring absorbs and dampen the shock impulse, thereby extending run life of the actuator and rod string. 
     Typically, in response to an upward flow moving through valve body, the spring extends the shuttle upward to cover the one or more spill ports. Preferably, in response to the upward flow moving through valve body, the actuator moves along the rotating rod above the valve body. That is, preferably the actuator is configured to leave the valve body in response to a sufficient upward flow moving through valve body. Preferably, the aperture extending through the upper housing is wider than the actuator to allow the actuator to move therethrough. 
     Preferably, in the event that pump operation is shutdown, the actuator slides down over the rotatable rod until it contacts the shuttle by means of the first seat closure. Preferably, in response to the first seat closure of the actuator sealing against the shuttle, the weight of fluid above the actuator then pushes the shuttle down, thereby exposing the one or more spill ports in the valve body. Preferably, in response to exposing the one or more spill ports in the valve body, there is a flow of fluid, and any entrained solids, out of the one or more spill ports away from a pump and into the well annulus. 
     Preferably, the rotating rod includes a coupling. Preferably, the coupling is located above the valve body. Preferably, the coupling includes a plastic covering. Preferably, the coupling includes an inner metal body with a thread. Preferably, the thread of the coupling is configured to be connected to pipe of the rotating rod adjacent thereto. Preferably, the coupling assists in stopping the actuator contacting an inner wall of the production tubing. 
     In a further form, the invention resides in a flow diversion valve comprising: 
     a valve body including an upper housing releasably connected to a lower housing, the upper housing and lower housing being configured to receive a rotating rod therethrough; and 
     a shuttle positioned within the valve body, the shuttle being configured to move to cover one or more spill ports of the valve body, 
     wherein the upper housing is threadingly connected to the lower housing with a left-handed thread. 
     Preferably, the flow diversion valve is as described herein. 
     In a further form, the invention resides in a flow management system, the system including: 
     production tubing having a rotating rod therein; 
     a flow diversion valve connected to the production tubing, the flow diversion valve comprising:
         a valve body including an upper housing releasably connected to a lower housing, the upper housing and lower housing being configured to receive the rotating rod therethrough;   a shuttle positioned within the valve body, the shuttle being configured to move to cover one or more spill ports of the valve body; and   a releasable locking member,   wherein the releasable locking member is positioned between the upper housing and the lower housing to assist in preventing relative movement therebetween; and       

     a pump connected to the flow diversion valve. 
     Preferably, the flow diversion valve is as described herein. 
     Preferably, production tubing includes a reinforced tube. Preferably, the reinforced tube connects directly to the flow diversion valve. Typically, the reinforced tube is in the form of a blast joint. Preferably, the reinforced tube includes a greater wall thickness relative to standard tubing used in the production tubing. Normally, the inner diameter of the reinforced tube substantially matches the inner diameter of standard tubing used in the production string. 
     Preferably, the pump is in the form of a progressive cavity pump. Preferably, the pump is configured to be submerged. 
     In a further form, the invention resides in a flow management system, the system including: 
     production tubing having a rotating rod therein; and 
     a flow diversion valve connected to the production tubing, the flow diversion valve comprising:
         a valve body including an upper housing releasably connected to a lower housing, the upper housing and lower housing being configured to receive a rotating rod therethrough;   a shuttle positioned within the valve body, the shuttle being configured to move to cover one or more spill ports of the valve body,   wherein the upper housing is threadingly connected to the lower housing with the handedness of the threads being in the same direction as a torque generated by a pump that is connected to the flow diversion valve.       

     Preferably, the handedness of the threads is a left-handed thread. 
     Preferably, the flow management system is as described herein. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The accompanying drawings, which are incorporated in and constitute a part of the specification, illustrate preferred embodiments of the disclosure. These drawings, together with the summary of the disclosure given above and the detailed description of the preferred embodiments given below, serve to explain the principles of the disclosure. By way of example only, preferred embodiments of the disclosure will be described more fully hereinafter with reference to the accompanying figures. 
         FIG. 1  is a schematic diagram of a flow diversion valve in a flow management system, according to an embodiment of the invention. 
         FIG. 2A  is a diagram of the flow management system associated with  FIG. 1  showing the (submersible) pump and a flow diversion valve connected to production tubing, according to an embodiment of the invention. 
         FIG. 2B  is a diagram of a flow management system, according to a further embodiment of the invention. 
         FIG. 3A  is a cross-sectional view of the flow diversion valve of  FIG. 2A , according to an embodiment of the invention, in a first configuration. 
         FIG. 3B  is a cross-sectional view of the flow diversion valve of  FIG. 2A , according to an embodiment of the invention, in a second configuration. 
         FIG. 3C  illustrates a cross-sectional view of a locking member, according to an embodiment of the invention. 
         FIG. 3D  illustrates an exterior view of a valve body in  FIGS. 3A and 3B  showing multiple spill ports and the spill ports closed by the positioning of a valve shuttle, according to an embodiment of the invention. 
         FIG. 4  is a cross-sectional view of a seal of the flow management system, according to an embodiment of the invention. 
         FIG. 5  is a cross-sectional view of an actuator, according to an embodiment of the invention. 
         FIG. 6  is a cross-sectional view of an actuator with a ferrite core, according to a further embodiment of the invention. 
         FIG. 7  is a cross-sectional view of an actuator with a ferrite core and spring shock absorber, according to a further embodiment of the invention. 
         FIG. 8A  is a cross-sectional view of the flow diversion valve of  FIG. 2B , according to an embodiment of the invention, in a first configuration. 
         FIG. 8B  illustrates a cross-sectional view of a locking member, according to a further embodiment of the invention. 
         FIG. 8C  illustrates an exterior view of a valve body in  FIG. 8A  showing multiple spill ports and the spill ports closed by the positioning of a valve shuttle, according to a further embodiment of the invention. 
     
    
    
     DETAILED DESCRIPTION OF THE DISCLOSURE 
     The disclosure provided in the following pages describes examples of some embodiments of the disclosure. The designs, figures, and description are non-limiting examples of certain embodiments of the disclosure. For example, other embodiments of the disclosed device may or may not include the features described herein. Moreover, disclosed advantages and benefits may apply to only certain embodiments of the disclosure and should not be used to limit the disclosure. 
     To the extent parts, components and functions of the described disclosure exchange fluids, the associated interconnections and couplings may be direct or indirect unless explicitly described as being limited to one or the other. Notably, indirectly connected parts, components and functions may have interposed devices and/or functions known to persons of ordinary skill in the art 
       FIG. 1  shows a schematic diagram of a flow management system  100 , according to an embodiment of the invention, with a pump  104  connected to a flow diversion valve  108 . The flow diversion valve  108  (hereinafter termed “diversion valve”) is interconnected with the pump  104  via a pump outlet  106 . The pump  104  is in the form of a progressive cavity pump (PCP) and includes a pump inlet  102 . The diversion valve  108  includes a valve outlet  110  and a valve spill port  112 . In various embodiments, the inlets, outlets and ports are one or more of a fitting, flange, pipe, or similar fluid conveyance. In the preferred embodiment, the pump  104  is located below the diversion valve  108 . 
       FIG. 2A  shows a section of a typical well  200 A. A flow management system  100 A in the well  200 A includes a diversion valve  108 A interposed between the pump  104  and production tubing  204 . In some embodiments, a casing  208  surrounds one or more joints of the production tubing  204 , diversion valve  108 A, and pump  104 . Here, an annulus  206  is formed between the production tubing  204  and the casing  208 . A production flow is indicated by an arrow  102   a  while a backflow is indicated by an arrow  202 . The diversion valve  108 A of this disclosure serves to isolate backflows from one or more valves, portions of a valve, and the pump  104 . 
       FIG. 2B  shows a further well  200 B. Similar to  FIG. 2A ,  FIG. 2B  shows a flow management system  100 B with a diversion valve  108 B interposed between the pump  104  and production tubing  204 . In comparison to the flow management system  100 A, the flow management system  100 B includes production tubing  204  having a blast joint  205  above the diversion valve  108 B. The blast joint  205  is discussed further below along with differences between the diversion valves  108 A,  108 B. 
       FIGS. 3A to 3D  show an embodiment of the diversion valve  108 A in the form of diversion valve  300 A. The diversion valve  300 A includes a valve body  324  comprising an upper housing  302  and a lower housing  303 . The upper and lower housings  302 ,  303  of the diversion valve  300 A are connected with threads  304  shown in  FIGS. 3A and 3B . The threads  304  in this embodiment are left-handed threads. This use of screw threads with left-handedness assists in preventing the threads  304  from backing off as a consequence of torque induced through the diversion valve  300 A by the operation of the pump  104 . 
     Separate threads exist on the connection  321  at top of upper housing  302 . These threads can be of a female configuration on the interior surface of connection  321 . These threads at the top of the upper housing  302  are compatible with the threads of the production tubing  204 . As shown in  FIGS. 3A and 3B , the connection between the production tubing  204  and upper housing  302  includes a torque ring  322 . The torque ring  322  is situated adjacent an end of the production tubing  204  and next to the threads on the interior surface of the connection  321 . The torque ring  322  is made from a rubber and assists in, amongst other things, increasing torsion capacity of the connection  321 . 
     The threads  320  at the bottom of the lower housing  303  may be compatible with threads located at the top of the pump  104  assembly (see  FIG. 2A ). It will be appreciated that the threads will be of the same spacing and one thread segment will be of a female connection and the other segment will be of a male connection. This compatibility will eliminate the need for any special crossover pup joints above or below the diversion valve  300 A, thereby simplifying installation and reducing costs. Furthermore, as appreciated from above, the connection between the lower housing  303  and pump  104  may also include a torque ring  322 . 
     The valve body  324 , accommodates components including a shuttle  337 , an actuator  383 , and a closing spring  312 . In a further embodiment, the diversion valve  300 A may include a shock absorbing spring (not shown) connected to the upper side of the actuator  383 . It will be recalled that the actuator  383  can traverse up the rotatable rod  382 , which is typically polished, under the influence of upward fluid flow  390 . 
     Turning to  FIG. 3C , the diversion valve  300 A includes a releasable locking member in the form of anti-rotation screws  305 A. The anti-rotation screws  305 A include an aperture in the form of a socket that receives a rotating tool (e.g. a hex key). The anti-rotation screws  305 A respectively engage a locking aperture in the form of groove  306 A in the lower housing  303 . The combination of the anti-rotation screws  305 A and groove  306 A prevent the threads  304  from backing off as a consequence of torque induced through the diversion valve  300 A by the operation of the pump  104  located below the diversion valve  300 A. See  FIG. 2A . In other embodiments, the valve body  324  may have a clam shell like construction wherein one side of the upper and lower housing  302 ,  303  of the valve body  324  is connected by a hinge like device and the other side detachably closed by an anti-rotation screw  305 A, horizontal latch device, etc. The valve body  324  may also comprise more than two detachable sections. 
     Whenever the pump  104  and other equipment above it is retrieved from the well  200 A, the upper housing  302  can be separated from the lower housing  303  by first removing the anti-rotation screws  305 A and then unscrewing threads  304 . The connecting surfaces of the upper and lower housing  302 ,  303  may contain seals and seats holding the seals in position. Suitable seal materials can include silicone rubber, elastomers, thermoplastic elastomers, and metals that are soft in comparison to the valve body  324 , the selection depending, among other things, on the valve application. In an embodiment, the seals are made from ultra-high molecular weight polyethylene. 
     On separation of the two housings  302 ,  303  the shuttle  337  and closing spring  312  can be removed, dismantled, cleaned and inspected, with any worn, fatigued, corroded or eroded parts replaced. The diversion valve  300 A can then be reassembled and re-used, thereby extending run life of the diversion valve  300 A. This use of threads  304  and anti-rotation screws  305 A eliminates the need to instead weld the upper housing  302  to the lower housing  303 , which makes it impossible to subsequently dismantle and redress the device, preventing re-use if any of the internal parts are damaged. 
     The valve body  324  has a central chamber  323 A. There is also a rotatable rod  382  that extends from the surface down the inside of the production tubing  204 . The rotatable rod  382  passes through the central chamber  323 A of the diversion valve  300 A. The shuttle  337  is positioned within the valve body  324 . The shuttle  337  includes an upper section  340 , a centre sleeve  342  and a lower section  341 . As shown in one figuration of  FIG. 3A , the upper section  340  blocks the spill ports  316 . The upper section  340  would be in this position when the fluid flow is upward fluid flow  390 . 
     Upper and lower seals  314 ,  330  are fitted circumferentially to the centre sleeve  342  of the shuttle  337 . In one embodiment, the seals have a curved cross-section such as a circular cross-section. In another embodiment, the seals have a rectangular cross-section (as shown in  FIG. 3A ). 
     In some embodiments, one or more seals  314 ,  330  have a structure  400  similar to that shown in  FIG. 4 . Here, a seal body  402  such as a polymeric body, has inner and outer lip seals  406 ,  404  and substantially envelops a charge O-ring or energizing spring  408  such as a silicon rubber ring, or metal spring. In various embodiments, the seals  314 ,  330  are made from one or more of a rubber, plastic, metal, or another suitable material known to persons of ordinary skill in the art. For example, seal materials include silicone rubber, elastomers, thermoplastic elastomers, and metals that are soft in comparison to the valve body  324 , the selection depending on, among other things, the valve application. In an embodiment, the seals are made from ultra-high molecular weight polyethylene. 
     The shuttle and actuator  337 ,  383 , have through-holes  356 ,  357  (i.e. a bore). The rotatable rod  382  pass through the through-holes  356 ,  357 . As outlined above, there is typically a chrome-plated or similar polished surface included on the rotatable rod  382 . A purpose of the chrome-plated polished rod is to limit the friction acting on the through hole  357  of the actuator inner sleeve  388 , as it traverses along the rotatable rod  382 . 
     A first face of the valve shuttle in the form of a first seat  368  is for sealing against a first (conical) actuator sealing face  367  of the actuator  383 . In an embodiment, the first seat  368  is near an upper end of the upper section  340  of the shuttle  337  and the first actuator sealing face  367  is near a lower end of the actuator  383 . In some embodiments, the first seat  368  is about radially oriented with respect to the valve body centre line  301 . In various embodiments, the shuttle sealing face (i.e. first seat  368 ) is integral with or coupled to the shuttle  337 . And, in various embodiments, the actuator sealing face  367  (i.e. the actuator sealing face) is integral with or coupled to the actuator  383 . 
     The design of actuator  383  may have a conical or tapered lower section to reduce permanent pressure loss resulting from upward flow of fluid around it. Furthermore, the upper section or surface of the actuator  383  is conical to reduce erosion of the actuator  383  by particle impingement of any solids entrained in back flowing fluid. In a preferred embodiment, the apex angles of the upper and lower conical sections are different. 
     In the embodiment shown in  FIGS. 3A and 3B , the actuator  383  has a conical actuator sealing face  367  to reduce permanent pressure loss resulting from upward flow of fluid around it. The upper surface of the actuator  383  also has a conical shape. In further embodiments, the taper of the upper surface of the actuator  383  may be shallower, relative to the conical sealing face  367 , and have a greater length to reduce turbulence in the upward flow. 
     The actuator  383  may further comprise threaded components. This is shown in the further embodiment of actuator  500  in  FIG. 5 . The upper and lower threaded components (or shells) are shown as items  501  and  502 . See also  FIGS. 6 and 7 . The threaded components allow the actuator  383 ,  500 ,  600 ,  700  to be disassembled. As discussed below, a ferrite material may be placed within the interior of the actuator  383 ,  500 ,  600 ,  700 . This ferro-magnetic material may facilitate recovery of the actuator in the event that the rotatable rod  382  breaks. 
     A second face (or portion) in the form of second seat  317 , on the upper section  340  of shuttle  337 , is for sealing against a face of the valve body  324  above the spill ports  316 . The face of the valve body  324  is in the form of valve shuttle seat  318 . In an embodiment, the valve shuttle seat  318  is near an upper section of the upper housing  302  of valve body  324 . In some embodiments, the valve shuttle seat  318  is about radially oriented with respect to the valve body centreline  301 . In various embodiments, the second seat  317  of the shuttle  337  is integral with or coupled to the shuttle  337 . And, in various embodiments, the valve shuttle seat  318  is integral with or coupled to the valve body  324 . 
     As indicated above, radially arranged and located on the upper housing  302  of valve body  324  are one or more spill ports  316 . Each spill port  316  extends between inner and outer walls  371 ,  372  of the valve body  324 . The inner wall  371  of the valve body  324  tapers inwardly towards the valve shuttle seat  318 . 
     Inducing upward movement of the shuttle  337  is the closing spring  312 . In various embodiments, the closing spring  312  is seated about radially oriented with respect to the valve body centreline  301  and is seated on a valve body support  313 . In the embodiment shown in  FIGS. 3A and 3B , an upper end of the closing spring  315  presses against an underside of a lower section  341  of the shuttle  337 . This lower section  341  is known as the shuttle spring end. 
     It will be appreciated that it will be important for the area or diameter of the annulus  323  be as wide as feasible to facilitate production flow. 
     In the embodiments shown, the spring  312  is positioned in close proximity to the interior wall of the valve body  324 . In further embodiments, an outer edge of the cylindrical coil spring  312  may be in contact with the interior surface. The spring  312  is not positioned or supported with an interior partition. This configuration is utilized in part to maximize the radial space or annulus,  323 , and through-hole  356  between the rotatable rod  382  and the interior of the valve wall. 
     Similarly, the shuttle  337  is constructed so the seat of the widely positioned spring  312  (having a wide radius) and shuttle spring end lower section  341 , also having a maximum radius, meet at or proximate to their interior edges  315 A. This meeting of components having wide radii provides maximum diameter to the annulus containing fluid. In further embodiments, the outer surface of the shuttle  337  may be in contact with at least a portion of the valve body  324  interior surface. The outer surface of the shuttle  337  and spring  312  may be coated with a non-friction, high temperature resistant substance such as Molykote available from Dow Corning. This is a bonding, dry-film lubricant typically containing MoS 2  graphite or PTFE. 
     The resulting widened space within the valve body  324  can decrease the flow resistance for the pump  104 , thereby increasing the pump life. It also decreases the erosion potential of solids-laden fluid through the diversion valve  300 A, thereby minimizing wear of the components of the diversion valve  300 A. 
     Operation of the diversion valve  300 A includes rotation of the rotatable rod  382  which is normally the means of operating the pump  104 . In normal operation, forces on the shuttle  337  and actuator  383  determine their position. When the pump  104  is lifting fluid within the tubing and within a designed flow-rate range, the shuttle  337  rises to its uppermost position  394  under the influence of the closing spring  312  and the rising fluid lifts the actuator  383  free of the shuttle  337  to a higher position  384  on the rotatable rod  382 . Notably, in its uppermost position, the shuttle  337  blocks the spill ports  316  when the second seat  317  seals with the valve shuttle seat  318 . Furthermore, the actuator  383  typically leaves the valve body  324  under the influence of the lifting fluid. This is shown in  FIG. 3A . In addition, the actuator  383  may be stopped along the rotatable rod  382 , above the valve body  324 , with the coupling  210 . The coupling  210  includes an inner metal body with a thread that connects the rotatable rod  382  with additional rods extending from the surface. An outer plastic covering with centralizing vanes, which maybe spiral, also surrounds the inner metal body of the coupling  210 . 
     It will be appreciated that the fluids and any entrained solids discharged from the pump  104  flows through the bore of the diversion valve lower housing  303  and shuttle  337  which is blocking the spill ports  316 . The fluids emerge through the aperture at the top of the upper housing  302  and continue up into the production tubing above. 
     When the pump  104  ceases to lift fluid at a sufficient rate, as with back-flow  391 , the actuator  383  falls to contact the shuttle  337 . This causes the actuator sealing face  367  to seal with the first seat  368  of the shuttle  337 . Further, if the force P 22  resulting from the pressure above the first seat  368  overcomes the force of the closing spring  312  and the force resulting from the pressure below the actuator  383 , the shuttle  337  is pushed down to position  396  and the spill port(s)  316  are unblocked allowing fluid in the tubing above the diversion valve  300 A to spill outside the diversion valve  300 A, for example into annulus  206  between the production tubing  204  and the casing  208 . 
     It will be appreciated that the interior radius of the upper housing  371  may be larger than the internal radius of the housing including the cylindrical shape of the shuttle  337 . Further the external radius of the shuttle  337  is greater than the radius of the actuator sealing face  367  of the actuator  383 . This size differentiation results in the configuration of the actuator  383  seating against the first seat  368  of the shuttle  337  and allows the spill ports  316  to open. 
     From the above, it can be seen that insufficient fluid flow, no fluid flow, or reverse fluid flow causes the diversion valve  300 A and the pump  104  to be removed from the fluid circuit and/or isolated from the fluid column above the shuttle  337 . A benefit of this isolation is protection of the diversion valve  300 A and the pump  104 . One protection afforded is protection of the diversion valve  300 A and pump  104  components from solids, normally rising with the fluid but now moving toward the diversion valve  300 A and the pump  104 , that might otherwise foul or block one or both of the diversion valve  300 A or pump  104 . Blocking the flow path around the shuttle  337  and opening the spill ports  316  removes these solids outside the diversion valve  300 A. 
       FIG. 3D  illustrates an exterior view of the diversion valve  300 A. Shown are the screw threads  320  connecting the diversion valve  300 A to the pump  104 . Also shown are the spill ports  316  and the upper section  340  of the shuttle  337 . Also shown are the anti-rotation screws  305 A. 
       FIG. 5  shows one embodiment of the actuator  500  comprising an upper metal shell  501  and a lower metal shell  502  encapsulating a non-metallic inner sleeve  503 . The metal shells  501 ,  502  are treated using processes such as electroless nickel plating or quench polish quench (QPQ) liquid nitriding to confer improved corrosion and surface hardness. The improved surface hardness boosts abrasion resistance from impingement of solids entrained in the fluids passing around the actuator  500  (or  383 ). The use of a non-metallic material for the inner sleeve  503  ensures the actuator  500  will not seize on the rotatable rod  382 . For downhole applications thermoplastics such as polyether ether ketone (PEEK), or ceramics, are ideally suited for non-metallic parts as they are mechanically and chemically stable at prevailing in-situ conditions, and can be used with injection moulds. The actuator  500  is assembled by sandwiching the sleeve  503  between the upper and lower metal shells  501 ,  502  and screwing these two parts together. The advantage of this split shell design is that it enables the inner sleeve  503  to be fabricated in a separate injection mould or machined from raw stock materials, greatly simplifying overall construction of the actuator  500 , and enables parts to be independently replaced if worn or damaged, rather than having to replace the entire assembly, thereby reducing costs. The shape of the actuator  500  is depicted in a cross sectional view. The shape can be described as a double conical shape or cross sectionally as a rhomboid, being a parallelogram in which adjacent sides are of unequal lengths and angles are not right angles. 
     In the eventuality that the rotatable rod  382  parts, twists, deforms or separates below the diversion valve  300 A, the rotatable rod  382  above the break is pulled from the well, causing the actuator  383  to rest against the shuttle  337 . The oblique positioning of the actuator within the valve body  324  greatly hinders recovery of the remaining section of the rotating rod in the well that is attached to the rotor located in the pump  104 . 
       FIG. 6  shows an alternative actuator  600  embodiment which also encompasses an upper and lower metal shell  601 ,  602 , an inner non-metallic sleeve  603  and also includes a magnetic ring  604 . This ring  604  is made from a ferromagnetic material, such as alnico or samarium cobalt, that can be suitably plated or coated (examples: nickel plated, epoxy coated, parylene coated) to confer additional corrosion resistance. 
     Using the magnetic properties of the magnetic ring  604 , the actuator  600  can then be retrieved using a skirted and bar fishing magnet that can be deployed on slickline inside the production tubing. The strong magnetic attraction between the bar magnet and the ferromagnetic ring  604  in the actuator  600  overcomes gravitational pull and viscous drag on the actuator  600 , enabling it to be retrieved to the surface. 
     Successful retrieval of the actuator  600  then provides access for standard fishing equipment to retrieve the remaining part of the rotatable rod  382  left in the well that will be attached to the PCP rotor located inside pump  104 . The PCP rotor can then be re-deployed on a new rotatable rod  382 , thereby avoiding a costly well workover, involving mobilisation of a drilling or workover rig, to retrieve the production tubing  204  and pump  104 . 
       FIG. 7  shows yet another embodiment of an actuator  700  that has a spring shock absorber  705  on top. Actuator  700  encompasses an upper and lower metal shell  701 ,  702 , an inner non-metallic sleeve  703  and also includes a magnetic ring  704 . This is positioned over the rotatable rod  382  that passes through the centre of the actuator  700  and flow diversion valve  300 A. The rotatable rod  382  comprises multiple individual rods (including the polished rod) that are screwed together with the coupling  210 , which has a larger diameter than the rod body. When the actuator  700  moves up the rotatable rod  382  under the action of flow moving around it, there is potential for the actuator  700  to impact the rod coupling  210 , imparting a high impulse force, otherwise known as shock load. Repeated impacts can obviously lead to mechanical fatigue of either the actuator  700 , rod coupling  210 , or both. The purpose of the spring shock absorber  705  is to absorb and dampen the shock impulse, thereby extending run life of the actuator  700  and rotatable rod  382 . 
     The actuator embodiments shown in  FIG. 5 ,  FIG. 6  and  FIG. 7  may have rhomboid geometries top and bottom. This tapered profile has the benefit of limiting extent of turbulent eddies created in the fluid as it flows through the annular restriction around the actuator, thereby reducing energy dissipation. This will in turn reduce permanent pressure loss, also referred to as irreversible pressure loss. The tapered geometries of the upper and lower metal shells will therefore also provide the additional benefit of limiting impact on head efficiency created by the pump  104 . 
     It should be evident to those skilled in the art that the designs shown in actuator embodiments  FIG. 5 ,  FIG. 6  and  FIG. 7  can be combined to provide an actuator than has a top shock absorber but no internal ferromagnetic ring 
       FIGS. 8A to 8C  show an embodiment of the diversion valve  108 B in the form of diversion valve  300 B. The diversion valve  300 B is substantially the same as diversion valve  300 A and, therefore, like numbering has been used. However, the diversions valve  300 B includes the following notable differences. 
     As further shown in  FIG. 8B , the diversion valve  300 B includes a locking member having a locking body  305 B that is substantially rectangular. The locking body  305 B includes two apertures therethrough. A locking aperture  306 B in the form of two threaded holes is located in the lower housing  303 . The locking aperture  306 B extends outward to form a ledge in the lower housing  303 . The locking body  305 B is received between the ledge and the upper housing  302 . Two fasteners  307 B extend through the two apertures of the locking body  305 B and are connected to the two threaded holes to releasably connect the locking member to the valve body  324 . Multiple locking members are equally spaced around the valve body  324 . In a preferred embodiment four locking members are incorporated. When the locking members are in place, they assist in preventing the threads  304  from backing off as a consequence of torque induced through the flow diversion valve  300 B during assembly of the flow diversion valve  300 B with the pump  104  and the production tubing  204 , during operation of the pump  104  and during removal of the flow diversion valve  300 B from between the pump  104  and production tubing  204 . 
     In comparison to the flow management system  100 A, the production tubing  204  of the flow management system  1008 , above the diversion valve  300 B, includes a blast joint  205 . The blast joint  205  has an inner diameter that is the same as the standard tubing used in the production tubing  204  thereabove. However, the blast joint includes a greater wall thickness relative to standard tubing. In this regard, the production tubing is a reinforced tube that connects directly to the diversion valve  300 B. The blast joint  205 , by virtue of having a greater wall thickness, can withstand greater wear caused by any potential rubbing between the actuator  383  and the inner wall of the blast joint  205 . 
     As can be appreciated from  FIGS. 8A and 8C , with the use of the shuttle  337  and actuator  383 , the opening and closing of the spill ports  316  in the diversion valve  300 B is the same as diversion valve  300 A. 
     This specification is to be construed as illustrative only and is for the purpose of teaching those skilled in the art the manner of carrying out the disclosure. It is to be understood that the forms of the disclosure herein shown and described are to be taken as the presently preferred embodiments. As already stated, various changes may be made in the shape, size and arrangement of components or adjustments made in the steps of the method without departing from the scope of this disclosure. For example, equivalent elements may be substituted for those illustrated and described herein and certain features of the disclosure maybe utilized independently of the use of other features, all as would be apparent to one skilled in the art after having the benefit of this description of the disclosure. 
     While specific embodiments have been illustrated and described, numerous modifications are possible without departing from the spirit of the disclosure, and the scope of protection is only limited by the scope of the accompanying claims. 
     This specification is to be construed as illustrative only and is for the purpose of teaching those skilled in the art the manner of carrying out the invention. It is to be understood that the forms of the invention herein shown and described are to be taken as the presently preferred embodiments. As already stated, various changes may be made in the shape, size and arrangement of components or adjustments made in the steps of the method without departing from the scope of this invention. For example, equivalent elements may be substituted for those illustrated and described herein and certain features of the invention maybe utilized independently of the use of other features, all as would be apparent to one skilled in the art after having the benefit of this description of the invention. 
     While specific embodiments have been illustrated and described, numerous modifications are possible without departing from the spirit of the invention, and the scope of protection is only limited by the scope of the accompanying claims. 
     In this specification, adjectives such as first and second, left and right, top and bottom, and the like may be used solely to distinguish one element or action from another element or action without necessarily requiring or implying any actual such relationship or order. Where the context permits, reference to an integer or a component or step (or the like) is not to be interpreted as being limited to only one of that integer, component, or step, but rather could be one or more of that integer, component, or step etc. 
     In this specification, the terms ‘comprises’, ‘comprising’, ‘includes’, ‘including’, or similar terms are intended to mean a non-exclusive inclusion, such that a method, system or apparatus that comprises a list of elements does not include those elements solely, but may well include other elements not listed.