Abstract:
A drill stem safety valve actuator that eliminates the need for a hydraulic union is provided. The actuator can include a mounting sleeve that can be affixed to the valve, that can further have a pinion gear that can rotate a ball valve. The actuator can include a rack sleeve slidably disposed on the mounting sleeve, having a rack configured to engage the pinion wherein sliding the rack sleeve linearly along the length of the mounting sleeve rotates the pinion, thus, the ball valve.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
       [0001]    This application claims priority of U.S. provisional patent application Ser. No. 62/181,022 filed Jun. 17, 2015, which is incorporated by reference into this application in its entirety. 
     
    
     TECHNICAL FIELD 
       [0002]    The present disclosure is related to the field of valve actuators, in particular, actuators for drill stem safety valves. 
       BACKGROUND 
       [0003]    Drill stem safety valves (“DSSV”) typically have two primary purposes: a) they are a safety device that can be closed to prevent mud and/or well fluid from flowing back up the interior of the drill pipe in the event of an unbalanced pressure in the mud column; and b) they can be used as a flow control device to turn on and off the flow of mud while making and breaking connections during drilling operations for top drives. When used for blow out prevention, these valves are only used during testing or in emergencies. However, in mud control, they can be operated several hundred times in the drilling of a single well. 
         [0004]    To operate a DSSV, the stem is turned ninety degrees from open to closed position and back again, by applying torque to the DSSV stem. This torque can be applied manually, or by remote actuator. For mud saving operations, remote actuation is the preferred method of applying torque to the DSSV. Remote actuators generally deliver the torque to the stem of a valve through a hexagonal or square shaft that interfaces with the matching internal profile of the stem. 
         [0005]    When the valve is used for blowout prevention, the valve can be subjected to high internal pressure which causes a significant amount of compressive load on the valve ball as it moves from open to close. This high load necessitates the application of high torque to the valve stem in order to ensure that the ball completely closes and fully stops the unwanted flow reversal. Some valves require upwards of 2000 ft-lbs to operate. A remote actuator is the most efficient method for delivering the high torque required. 
         [0006]    Actuators generally supply a fixed amount of torque, i.e. the maximum output of the actuator. The high torque delivered to valve stem can damage the internal stops for the valve stems. This damage generally leads to over travel of the ball in the open, close, or both positions. This over travel can be detrimental to the life of the valve and the safety that it is supposed to provide. For example, when the ball over travels in the open position, the flow of mud is directed off the longitudinal axis of the valve leading to accelerated wash of the valve&#39;s internal components. When the ball over travels in the close position, the valve ball may rotate to the extent that it no longer completely blocks the flow of mud, or in the case of blowout prevention: reservoir fluids. 
         [0007]    Remote actuators currently use pneumatics and/or hydraulics to create the motive force that applies torque to the actuator/DSSV interface. In most cases, a linear motion is translated to a rotational motion through the use of racks and pinions or linkages. 
         [0008]    In order to be able to deliver the torque to the DSSV stem, the actuator must be attached to the DSSV thus rotating when the DSSV is rotating. Therefore, delivery of pneumatic or hydraulic pressure to the actuator becomes problematic. The current methods of overcoming the delivery of pressure from a stationary source to a rotating actuator is through a hydraulic/pneumatic union or isolation of the actuators force generating mechanisms: typically hydraulic/pneumatic cylinders. 
         [0009]    The advantage of using hydraulic unions is that they are very compact, very efficient, and very powerful. Full hydraulic pressure can be redirected through these devices and delivered directly to the hex drive shaft either through racks and pinions or through linkages. In this mode of design, all the actuator&#39;s force generating components can be internalized within the actuator body. The internalizing of the force generating components (typically racks and pinions) allows the actuator to remain relatively small, in comparison to other styles of actuators, while still delivering comparable torque. As well, as all the force components are internalized, the possibility of damage is greatly reduced improving reliability. In addition the union can be designed to operate as a plain bearing for the rotational component, eliminating the need for costly bearings and again saving space. 
         [0010]    However, one draw back of the hydraulic union method is the design and use of small cross section hydrodynamic seals that seal oil glands between the stationary part of the actuator and the rotating part. The hydrodynamic seals provide positive sealing, due to seal compression, while the actuator remains stationary, but allow small amounts of oil to bypass when creating a dynamic seal. The bypassing oil ensures that the seal face remains lubricated, effectively creating a short journal bearing. The lubrication significantly reduces friction between the seal and the rotating member thereby extending seal life. Over time, this seepage and the combined inevitable seal wear from operation will escape to the environment, as collection and reuse methods are typically not incorporated into the actuator design. 
         [0011]    The hydraulic fluid between the seal and the rotating member is subjected to high shear rates which in turn generate heat that is difficult to dissipate due to the actuators high thermal mass and small surface area. Further, if the hydraulic pressure to function the actuator acts on the seals while the actuator is rotating, the seals increase their facial surface force and act as a brake on the rotating member. Thus, heat generation and seal wear increase significantly. 
         [0012]    In order to overcome leakage from the dynamic seals and the associated heat generation, some actuators have isolated the force generation by moving the hydraulic or pneumatic cylinders to the exterior non-rotating portion of the actuator. The external cylinders deliver a force to a moveable sleeve, isolated by bearings systems, which in turn drive linkages to create the torque at the actuator/DSSV stem interface. 
         [0013]    The isolation of the cylinders often results in a larger less rigid actuator than the hydraulic union type due to the mounting methods of the cylinders and internal clearances required between the axially shifting sleeve(s). The reduction in rigidity results in accelerated wear of the joints that connect the cylinders to the non-moving part. As well, any linkages that are used to supply torque to the interface between the actuator/DSSV often develop significant unintended clearances. The increased wear at joints of the linkages and cylinders leads to inaccurate functioning of the DSSV, i.e. the DSSV is not moved from full open to full close when the actuator is moved through its range of motion. 
         [0014]    Linkages are typically not as efficient as rack and pinion designs, and do not possess the same amount of mechanical advantage. In addition, because of their low mechanical advantage, linkages can be susceptible to moving without being actuated, as the vibration associated with drilling has been known to cause these linkages to move under their own weight and inadvertently close the valve during drilling cycles. 
         [0015]    Regardless of the actuator style, the output torque is often limited by the size of hydraulic or pneumatic cylinders that can be incorporated into the design and their respective radial offset location from the axis of the DSSV&#39;s crank center. In the case of the externally mounted cylinders, the cylinders usually have a small diameter with a thin wall in order to keep the overall actuator size to a minimum. The small thin walled cylinders have limited pressure retention, thus the output force is also limited. The union style actuators typically do not suffer from the same pressure limits to their force generation components. However, as the force generating components are internal to the small diameter bodies, the offset distance between the force generation and the crank center of rotation is severely limited. 
         [0016]    For any DSSV, the correct alignment of the ball in the open and closed position is critical to optimal valve life. Without correct alignment in the open position, the leading edge of the ball and the trailing edge of the lower seat will be exposed to abrasive mud flow, causing premature wear and potentially vortices that can accelerate erosion. The resulting deflected flow path and resulting accelerated erosion can lead to premature failure. 
         [0017]    As the alignment of the ball is critical for valve service life, most remote actuators rely on the valve&#39;s internal stops to set the alignment of the ball. Without the internal stops, most actuators would provide excess rotational motion thereby allowing the ball to over travel in both the open and close positions. 
         [0018]    Since the DSSV stem internal stops are used, the stops often get damaged (resulting in misalignment of the ball) from the high contact stresses that the actuator&#39;s output torque generates. Very few actuators have a provision for adjusting the actuators output motion limits. This adjustment would allow the actuator to correct the balls alignment within the valve without the need to perform costly repairs on the valve itself. 
         [0019]    It is, therefore, desirable to provide an for a DSSV that overcomes the shortcomings of the prior art by eliminating the need for a hydraulic union thus eliminating the leakage and seal wear problems that are associated with prior art designs. 
       SUMMARY 
       [0020]    An actuator for operating a DSSV on a drill stem that eliminates the need for a hydraulic union is provided. In some embodiments, the actuator can comprise a mounting sleeve that can be affixed to a valve by a plurality of set screws and/or by a clamp at either end of the mounting sleeve. The mounting sleeve can comprise at least one master pinion gear rotatably disposed on an outer sidewall of the mounting sleeve that can rotate a hex shaft of a ball valve drive. In some embodiments, the actuator can further comprise a rack sleeve slidably disposed circumferentially on the mounting sleeve, the rack sleeve comprising a master rack disposed thereon, the rack configured to engage the master pinion wherein sliding the rack sleeve linearly along the length of the mounting sleeve rotates the master pinion thus rotating the ball valve drive and a ball valve coupled thereto. 
         [0021]    In some embodiments, the actuator can comprise a shifting sleeve disposed circumferentially on the rack sleeve, the shifting sleeve configured to rotate about the rack sleeve and still be able to engage the rack sleeve to slide it along the length of the mounting sleeve. In some embodiments, the rack sleeve can comprise a plurality of spaced—part rollers disposed circumferentially around the diameter of the rack sleeve wherein the shifting sleeve can comprise a channel configure to receive the plurality of rollers. In this configuration, the shifting sleeve can rotate around the rack sleeve by the rollers traveling in the channel and still engage or exert force on the rack sleeve to move it slidably on the mounting sleeve, thus, rotating the master pinion. 
         [0022]    In some embodiments, the actuator can further comprise hydraulic or pneumatic piston mechanisms disposed in a shroud or structure enclosing the mounting, rack and shifting sleeves wherein the piston mechanisms can move the shifting sleeve back and forth within the shroud or structure to open or close the valve, even while the drill stem is rotating. In other embodiments, the actuator can comprise an electric screwjack or a linear actuator as means for moving the shifting sleeve back and forth within the shroud or structure. 
         [0023]    In some embodiments, the actuator can comprise a compact design wherein the hydraulic piston mechanisms can deliver motive force to the rack sleeve and the master pinion, and so can have the advantage of providing nearly as much torque as traditional hydraulic union actuators. 
         [0024]    In some embodiments, the use of a rack and pinion mechanism in the actuator can maintain a fail last position, as the pinion does not move on its own through vibration that is normally associated with drilling. 
         [0025]    In some embodiments, the actuator can allow for precise adjustment of stops to limit the wear and over travel on the valve stops, and can further allow for better alignment during actuation and prolonging valve life. 
         [0026]    Broadly stated, in some embodiments, an actuator can be provided for operating a valve disposed in a rotatable drill stem comprising a passageway therein, the drill stem defining a longitudinal axis, the valve comprising a valve mechanism configured for opening and closing the passageway, the actuator comprising: first means for attaching to the valve, the first means comprising a coupler configured for operatively coupling to the valve mechanism; second means disposed on the first means and configured for slidable movement on the first means along the longitudinal axis, the second means operatively coupled to the coupler; and third means for slidably moving the second means on the first means, the third means rotatably coupled to the first means and to the second means wherein the third means is substantially stationary when the drill stem is rotating. 
         [0027]    Broadly stated, in some embodiments, a method can be provided for operating a valve disposed in a rotatable drill stem comprising a passageway therein, the drill stem defining a longitudinal axis, the valve comprising a valve mechanism configured for opening and closing the passageway, the method comprising the steps of: providing an actuator, comprising: first means for attaching to the valve, the first means comprising a coupler configured for operatively coupling to the valve mechanism, second means disposed on the first means and configured for slidable movement on the first means along the longitudinal axis, the second means operatively coupled to the coupler, and third means for slidably moving the second means on the first means, the third means rotatably coupled to the first means and to the second means wherein the third means is substantially stationary when the drill stem is rotating; attaching the actuator to the valve; and moving the second means relative to the first means using the third means to operate the valve. 
         [0028]    Broadly stated, in some embodiments, an actuator can be provided for operating a valve disposed in a rotatable drill stem comprising a passageway therein, the drill stem defining a longitudinal axis, the valve comprising a ball valve disposed therein, the ball valve configured for opening and closing the passageway, the actuator comprising: a mounting sleeve configured for attaching to the valve, the mounting sleeve further comprising a master pinion configured for coupling to the ball valve and rotating the ball valve to open and close the passageway; a rack sleeve circumferentially disposed on the mounting sleeve and configured for slidable movement on the mounting sleeve along the longitudinal axis, the rack sleeve operatively coupled to the master pinion wherein the master pinion rotates about an axis substantially perpendicular to the longitudinal axis when the rack sleeve moves slidably on the mounting sleeve along the longitudinal axis; and shifting means for slidably moving the rack sleeve on the mounting sleeve, the shifting means rotatably coupled to the mounting sleeve and to the rack sleeve wherein the shifting means is substantially stationary when the drill stem is rotating. 
         [0029]    Broadly stated, in some embodiments, a method can be provided for operating a valve disposed in a rotatable drill stem comprising a passageway therein, the drill stem defining a longitudinal axis, the valve comprising a ball valve disposed therein, the ball valve configured for opening and closing the passageway, the method comprising the steps of: providing an actuator, comprising: a mounting sleeve configured for attaching to the valve, the mounting sleeve further comprising a master pinion configured for coupling to the ball valve and rotating the ball valve to open and close the passageway, a rack sleeve circumferentially disposed on the mounting sleeve and configured for slidable movement on the mounting sleeve along the longitudinal axis, the rack sleeve operatively coupled to the master pinion wherein the master pinion rotates about an axis substantially perpendicular to the longitudinal axis when the rack sleeve moves slidably on the mounting sleeve along the longitudinal axis, and shifting means for slidably moving the rack sleeve on the mounting sleeve, the shifting means rotatably coupled to the mounting sleeve and to the rack sleeve wherein the shifting means is substantially stationary when the drill stem is rotating; attaching the actuator to the valve; and moving the rack sleeve relative to the mounting sleeve using the shifting sleeve to rotate the ball valve. 
         [0030]    Broadly stated, in some embodiments, the master pinion can further comprise at least one gear coupled to a ball valve drive that is configured to engage the ball valve. 
         [0031]    Broadly stated, in some embodiments, the mounting sleeve can further comprise a plurality of set screws configured to engage the valve to attach the mounting sleeve thereto. 
         [0032]    Broadly stated, in some embodiments, the actuator can further comprise at least one clamp configured to clamp an end of the mounting sleeve to the valve. 
         [0033]    Broadly stated, in some embodiments, the rack sleeve can further comprise a master rack configured to engage with the master pinion. 
         [0034]    Broadly stated, in some embodiments, the shifting means can comprise: first and second end plates rotatably attached to opposing ends of the mounting sleeve; at least one shroud plate operatively connecting the first and second end plates to form at least a partially enclosed or a fully enclosured structure; a shifting sleeve disposed between the first and second end plates and circumferentially disposed on the rack sleeve, the rack and shifting sleeves, in combination, comprising means for enabling the shifting sleeve to engage the rack sleeve and to rotate relative to the rack sleeve about the longitudinal axis; and the first and second end plates and the shifting sleeve, in combination, comprising means for moving the shifting sleeve linearly back and forth between the first and second end plates thereby engaging the rack sleeve to move slidably on the mounting sleeve along the longitudinal axis. 
         [0035]    Broadly stated, in some embodiments, the enabling means can comprise: a plurality of spaced-apart rollers rotatably disposed circumferentially on an outer sidewall of the rack sleeve; and a channel disposed circumferentially on an inner sidewall of the shifting sleeve, the channel configured to receive the plurality of spaced-apart rollers. 
         [0036]    Broadly stated, in some embodiments, the moving means can comprise: at least one first displacement mechanism disposed between the first end plate and the shifting sleeve, the at least first displacement mechanism configured to urge the shifting sleeve away from the first end plate; and at least one second displacement mechanism disposed between the second end plate and the shifting sleeve, the at least second displacement mechanism configured to urge the shifting sleeve away from the second end plate. 
         [0037]    Broadly stated, in embodiments, each of the at least one first and second displacement mechanisms can comprise one or more of a group consisting of a hydraulic piston and cylinder combination, a pneumatic piston and cylinder combination, an electric screwjack and a linear actuator. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0038]      FIG. 1  is a perspective view depicting one embodiment of a drill stem safety valve actuator. 
           [0039]      FIG. 2  is a perspective view depicting the actuator of  FIG. 1  with a portion of the shifting sleeve removed to illustrate the rack and opinion mechanism. 
           [0040]      FIG. 3  is an exploded perspective view depicting the actuator of  FIG. 1 . 
           [0041]      FIG. 4  is an exploded perspective view depicting the mounting sleeve of the actuator of  FIG. 3 . 
           [0042]      FIG. 5  is an exploded perspective view depicting an end plate of the actuator of  FIG. 3 . 
           [0043]      FIG. 6A  is a cutaway perspective view depicting the end plate of  FIG. 5 . 
           [0044]      FIG. 6B  is a cutaway perspective view depicting the end plate of  FIG. 6A  with a main bearing installed. 
           [0045]      FIG. 7  is an exploded perspective view depicting the shifting sleeve of  FIG. 3 . 
           [0046]      FIG. 8  is an exploded perspective view depicting the J-Band split assembly of  FIG. 3 . 
           [0047]      FIG. 9  is a perspective cross-section view depicting the actuator of  FIG. 1  installed on a drill stem safety valve. 
       
    
    
     DETAILED DESCRIPTION OF EMBODIMENTS 
       [0048]    Referring to  FIGS. 1 to 3  and  FIG. 9 , one embodiment of actuator  10  is shown. In some embodiments, actuator  10  can comprise, broadly, mounting sleeve  12 , rack sleeve  14  and shifting sleeve  16  disposed between spaced-apart and substantially parallel end plates  18 , wherein shroud plates  22  can be attached to end plates  18  with screws  26  to provide structural rigidity to actuator and to provide an enclosure for rack sleeve  14  and shifting sleeve  16  disposed therein. Mounting sleeve  12  can define longitudinal axis  11  extending therethrough. Anchor block  58  can be attached one end plate  18  with cap screws  60  as a stop to prevent actuator  10  from rotating when the drill stem is rotating. 
         [0049]    In some embodiments, actuator  10  can comprise bearings  54  disposed between end plates  18  and mounting sleeve  12  to enable the structure of end plates  18 , shroud plates  22 , rack sleeve  14  and shifting sleeve  16  disposed therein to rotate relative to mounting sleeve about longitudinal axis  11 . In some embodiments, end plates  18  can be held in position by spiral spring retainers  24  fitted into grooves  25  disposed about the ends of mounting sleeve  12 . To affix actuator  10  to valve body  100 , J-Band assembly  20  can be installed on the ends of mounting sleeve  12  by engaging groove  13  disposed about mounting sleeve  12  and groove  15  disposed about valve body  100 , and then held in place by T-bolt clamps  21 . In some embodiments, actuator  10  can also comprise a plurality of set screws  32  threaded through mounting sleeve  12 , set screws  32  fully configured to engage valve body  100 . 
         [0050]    In some embodiments, mounting sleeve  12  can comprise one or more master pinion  28 , a gear that can couple to ball valve drive  56  that, in turn, can rotate ball valve  102  disposed in valve body  100 , as shown in  FIG. 9 . Master pinion  28  can comprise hex opening  27  for manually rotating master pinion  28  with a hex wrench. When rack sleeve  14  is circumferentially disposed on mounting sleeve  12 , master pinion  28  can be disposed in opening  35  to engage rack  36 , thus, when rack sleeve slides along mounting sleeve  12 , rack  36  can rotate master pinion  28  to rotate ball valve  102 . 
         [0051]    In some embodiments, actuator  10  can comprise shifting sleeve  16  circumferentially disposed on rack sleeve  14 . Rack sleeve  16  can comprise a plurality of spaced-apart rollers  38  disposed circumferentially on an outer sidewall thereof. Shifting sleeve  16  can comprise channel  40  disposed circumferentially on an inner sidewall thereof, channel  40  configured to receive plurality of rollers  38  wherein shifting sleeve  16  can rotate about longitudinal axis  11  relative to rack sleeve  14  and still move rack sleeve  14  along longitudinal axis  11  vis á vis channel  40  exerting force on rollers  38 . 
         [0052]    To enable movement of shifting sleeve  16  within actuator  10 , each of end plates  18  can comprise at least one fixed piston  30  extending substantially perpendicular therefrom towards the opposing end plate  18 . In some embodiments, each piston  30  can be inserted into a corresponding cylinder sleeve  62  disposed in shifting sleeve  16 . In some embodiments, each end plate  18  can comprise inlet/outlet  42  and internal passageways (as described in more detail below) to pistons  30  as means for pressurized hydraulic fluid or air enable movement of shifting sleeve  16 . By injecting pressurized fluid or air into inlet/outlet  42  of a first end plate  18 , fluid or air can pass through a passageway disposed within at least one piston  30  to enter its corresponding cylinder sleeve  62  and, thus, move shifting sleeve  16  away from said first end plate  18 . By injecting pressurized fluid or air into inlet/outlet  42  of the second end plate  18 , fluid or air can pass through a passageway disposed within at least one piston  30  to enter its corresponding cylinder sleeve  62  and, thus, move shifting sleeve  16  from second end plate  18  toward first end plate  18 . 
         [0053]    Referring to  FIG. 4 , an exploded view of one embodiment of mounting sleeve  12  is shown. In some embodiments, mounting sleeve  12  can comprise a plurality of threaded holes  33  placed circumferentially about mounting sleeve  12  in a spaced-apart configuration to received set screws  32  to enable the attachment of mounting sleeve  12  to valve body  100 , as shown in  FIG. 9 . In some embodiments, mounting sleeve  12  can comprise recessed opening  65  configured for receiving bushing  64 , which is placed between master pinion  28  and recessed opening  65 . 
         [0054]    Referring to  FIG. 5 , an exploded view of one embodiment end plate  18  is shown. In some embodiments, at least one piston  30  can be attached to end plate  18  with cap screws  70 . O-ring  29  can be disposed between at least one piston  30  and end plate  18  to provide a seal for piston passageway  52 . Each piston  30  can further comprise end seal  31  for providing a sealed slidably fitment with cylinder sleeve  62  disposed shifting sleeve  16 . In some embodiments, o-rings  44  can be disposed in opening  19  between end plate  18  and main bearing  54  to provide a seal therebetween. In some embodiments, end plate  18  can comprise set screw  66  threadably disposed in in threaded opening  67  as means to provide a stop for shifting sleeve  16  when actuator  10  is fully assembled. In some embodiments, end plate  18  can comprise groove  39  disposed therearound to receive o-ring cord  34  as means to provide a seal between end plate  18  and shroud plate  22  when installed on actuator  10 . In some embodiments, end plates  18  can comprise threaded holes  69  that can receive eyehooks (not shown) for lifting and moving actuator  10 . When eyehooks are not used or required, holes  69  can be plugged with setscrews  68 . 
         [0055]    Referring to  FIGS. 6A and 6B , cut-away views of one embodiment end plate  18  are shown,  FIG. 6A  without main bearing  54 ,  FIG. 6B  with main bearing  54 . In some embodiments, a pair of o-rings  44  can be disposed in grooves  45  to, thus, provide channel  48  when main bearing  54  is installed therein. In some embodiments, passageway  46  can provide communication between inlet/outlet  42  and channel  48 . In some embodiments, passageway  50  can provide communication between channel  48  and piston passageway  52 . Plug  51  can be installed to seal off passageway  50  in end plate  18 . Referring to  FIGS. 5, 6A and 6B , in some embodiments, one or both end plates  18  can comprise pressure relief fitting  72  (as well known to those skilled in the art) threaded into hole  73 , which can be disposed through end plate  18  and can further provide communication between atmosphere and the interior space within actuator when it is fully assembled with shroud plates  22  attached to end plates  18 . In some embodiments, seals or gaskets (as well known to those skilled in the art) can be installed between shroud plates  22  and end plates  18  to fully enclose the interior space within actuator  10 . In some embodiments, relief fitting  72  can operate to ensure that the pressure of air, gases or fluids within the interior space of actuator  10  does not exceed a predetermined level or threshold and damage internal components of actuator  10 . When the pressure of the air, gases or fluids within the interior space of actuator  10  does exceed the predetermined level or threshold, relief fitting  72  can open and provide a communication path for pressurized air, gases or fluids to exit the interior space through hole  73  to atmosphere. In some embodiments, relief fitting  72  can be selected or configured to operate anywhere within an approximate range of 10 to 15 pounds per square inch, or at some other suitable pressure as well known to those skilled in the art. 
         [0056]    Referring to  FIG. 7 , an exploded view of one embodiment of shifting sleeve  16  is shown. In some embodiments, shifting sleeve  16  can comprise cylinders  78  disposed therethrough and configured for receiving cylinder sleeves  62 . In some embodiment, cylinder sleeves  62  can further comprise wear rings  74  to provide wear protection when pistons  30  are inserted into cylinder sleeves  62 . In some embodiments, cylinder sleeves  62  can comprise ports, which can be sealed with plugs  76 . 
         [0057]    Referring to  FIG. 8 , an exploded view of J-Band assembly  20  and T-bolt clamp  21  are shown, which can be used to secure mounting sleeve  12  to valve body  100  as shown in  FIG. 9 . 
         [0058]    Referring to  FIG. 9 , actuator  10  is shown with rack sleeve  14  positioned at a most downward position wherein ball valve  102  is position in an “open” state such that there is communication between passageway  104  and passageway  106  within valve body  100 . When shifting sleeve  16  is moved upwards via injection of pressurized hydraulic fluid or air into the appropriate inlet/outlet  42 , rack sleeve  14  can move upwards from the mostward position, as shown in  FIG. 9 , to rotate master pinion  28  and, thus, ball valve drive  56  and ball valve  102  approximately 90° and, therefore, shut off communication between passageway  104  and passageway  106 . 
         [0059]    Although a few embodiments have been shown and described, it will be appreciated by those skilled in the art that various changes and modifications can be made to these embodiments without changing or departing from their scope, intent or functionality. The terms and expressions used in the preceding specification have been used herein as terms of description and not of limitation, and there is no intention in the use of such terms and expressions of excluding equivalents of the features shown and described or portions thereof, it being recognized that the invention is defined and limited only by the claims that follow.