Patent Publication Number: US-11649899-B2

Title: Ball valve

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application is a continuation application of, and claims the benefit of priority to, U.S. patent application Ser. No. 15/349,183 filed on Nov. 11, 2016, issued as U.S. Pat. No. 11,131,404 on Sep. 28, 2021, which claims the benefit of U.S. Provisional Application entitled “Ball Valve,” which was filed on Nov. 16, 2015, and assigned Ser. No. 62/255,849, the contents of which applications are herein incorporated by reference in their entirety. 
    
    
     FIELD OF THE DISCLOSURE 
     The present disclosure generally relates to flow control assemblies for fluid systems, and more particularly, to ball valve assemblies for fluid systems. 
     BACKGROUND OF THE DISCLOSURE 
     Ball valves can be used in applications that require the transmission of fluids. Ball valves can be one-quarter turn valves used in on-off applications, but can also be used to modulate flow. Ball valves can be unidirectional (flow in one direction) or bidirectional (flow in either direction). Two common types of ball valves are floating ball valves and trunnion ball valves. Ball valves can utilize different seat styles. Two common types of seats that are used in ball valves are crush seats and deflecting seats. 
     In general, crush seats can be designed with the intent that the initial preload on the seats will be significant enough to yield the seat material and form the seat to the ball. Essentially, the ball crushes the seats during assembly. After the seats are crushed, the seats generally do not return to their initial geometry, but a certain amount of contact stress can remain between the ball and the seat, thus generating a seal. 
     A second seat style is a deflecting seat. In general, deflecting seats can be designed to act like a spring. When preload is applied to a deflecting seat, the seat can deflect away from the load. Some material yield can still occur at the point of contact between the ball and the seat, but the yield can be less significant and more localized than on a crush seat. Additionally, as this yield (and any subsequent creep) occurs, the seat can maintain a load on the ball by continuing to spring back into the ball as the seat tries to return to its original un-deflected geometry. 
     Floating ball valves can be fabricated with a certain amount of preload in the seats. This preload can be used to first enact a seal between the ball and the upstream and downstream seats. As the difference in pressure between upstream and downstream increases, so does the load on the ball, thus forcing the ball downstream and enhancing the downstream seal. A floating ball valve can have a primary seal on the downstream seat and may not have a secondary seal. In general and depending on the preload applied during assembly, a floating ball valve may seal on the upstream seat as well. 
     Determining the appropriate seat preload on a floating ball valve can generally pose some challenges. Some seats should be loaded only enough to generate a seal at very low pressures. The ball can then be free to float downstream to increase sealing load at higher pressures. However, if seat load is too low, the valve may not be forgiving enough to seal in some applications. Additionally, if the seat load is too low, the market perception can be that the valve may not seal. If the seat load is too high, the ball may not be able to float downstream, resulting in an upstream and a downstream seal. In general, this can be undesirable in some existing floating ball valve designs because it can result in pressure trapped inside the cavity of the valve. The ball floating towards the downstream seat, and losing its seal on the upstream seat, can be the mechanism used to prevent trapping cavity pressure in a floating ball valve. Moreover, if the seat load is too high, an additional disadvantage is that the stem torque may increase, thereby causing the valve to be difficult to operate. 
     In general, trunnion ball valves can hold the ball rigidly along the axis of the stem (some deflection can still occur) via the stem and a second bearing surface, or shaft, on the bottom of the ball (the trunnion). These bearing surfaces may be integral to, or separate from the ball. The seats on a trunnion ball valve can be allowed to move along the central axis of the valve and can be positively displaced (e.g., spring loaded) towards the ball. The seats may, or may not, be installed in seat carriers that can also move along the central axis of the valve. As the difference in pressure between upstream and downstream increases, the upstream seat can apply an increasing load against the ball, thus enhancing the seal. In contrast to a floating ball valve, a trunnion ball valve generally has a primary seal on the upstream seat and can provide a secondary seal on the downstream seat. 
     With respect to thermoplastic ball valve seat sealing, some conventional thermoplastic ball valves are of a floating ball design, though there are some plastic trunnion ball valves. Conventional plastic ball valves (whether they employ a floating or a trunnion mount ball) can be built with adjustable seal retainers. The adjustable seal retainer can allow the preload on the seats (e.g., the load that exists in a static condition, prior to loading from differential pressure) to be adjusted (e.g., increased) in the field to attempt to create a seal between the ball and the seat. While some plastic ball valves can have one seal retainer (with the opposite end of the valve body having a fixed seat location—this end of the valve can be referred to as the closed or blocked end), some designs offer an adjustable seal retainer on both ends of the valve.  FIG.  1    shows a view of a conventional floating ball valve with a single adjustable seal retainer. 
     Conventional adjustable seal retainers have been used for several reasons (e.g., manufacturing costs/tolerances; thermal expansion/contraction of valves; low stem torque expectations; seat creep and sealing window; deflection of valves due to mechanical loading; small seat sealing window). Regarding small seat sealing windows, it is noted that some conventional thermoplastic ball valves on the market utilize a crush seat. This type of seat can have a relatively small seal tolerance. There may be little adjustment between the point where a seal is generated, and the point at which stem torque becomes objectionable. Additionally, some crush seats may suffer from creep over time. 
     Some adjustable seal retainers can create challenges. These challenges can include: (i) balls forced off of stem center, and/or (ii) difficulty to establish correct seal retainer position. For example and with respect to balls forced off of stem center, when conventional adjustable seal retainers are used, they can be used on one end of the valve (e.g., with the other end being the blocked or closed end of the valve body). As a result, there may be one seal retainer location (and therefore one seat load) that allows for the center-line of the ball to correspond with the center-line of the stem. If the seal retainer is adjusted to a position other than this one location, the ball can be effectively pushed to a position that is off center from the stem center-line. This can result in the ball camming in relation to the stem bore when the valve is being rotated. When the ball cams, it can result in increased stem torque and backlash or slight reverse rotation in the handle. Some disadvantages of such backlash in the handle can result in poor user experiences. For example, if the ball is in a closed position and backlash in the handle occurs, the valve can lose the seal between the ball and the seat. If the ball is in an open position and backlash in the handle occurs, there may not be a correct or fully aligned flow path through the ball. 
     Regarding the difficulty to establish correct seal retainer position, it is noted that determining the appropriate seal retainer position (and therefore seat load) on a conventional valve with an adjustable seal retainer can be difficult both for the valve manufacturer and for an end user rebuilding the valve. One indicator of seat load can be the stem torque. However, adjusting the seal retainer to achieve a specific seat load and confirming via stem torque can be difficult and can require a trial and error approach. Additionally, each time stem torque is checked the valve may first be rotated several times in order to break the edge of the newly compressed seat. This can further add to the difficulty of achieving consistent seat load in the factory and in the field. Some conventional valves with two adjustable seal retainers (instead of one) can be even more difficult to adjust correctly. 
     With respect to ball valve lockout mechanisms, it is noted that the occasional need to lock a ball valve in position is a relatively new practice in the plastic valve market. This locking capability can be used to attempt to keep a valve from being operated for commercial or for safety reasons. Commercial reasons may include maintaining a set process or preventing theft. Safety reasons can be “lock-out/tag-out” of a closed valve in order to allow maintenance to be safely performed on equipment downstream from the closed and locked valve. 
     Having a method to lock a valve in position (e.g., fully closed) can be common with metal valves. One locking mechanism on metal ball valves is a simple slide lock (see  FIGS.  7 - 11   ). One disadvantage of this style lock is that it may be overcome by removing the nut that retains the handle (at which point the handle, slide plate, and lock can be removed). Some locking mechanisms that attempt to overcome this weakness have been manufactured for use on metal ball valves, but they can add cost to the valve ( FIGS.  4 - 6  and  11    show some of these commercially available lock-outs). Some methods of locking a plastic valve in position have been brought to market. These methods can range from overly complicated, to overly cumbersome, to both. Some of these methods can include: (i) trigger style lockout (see  FIG.  2   ); and (ii) handle enclosure lockout (see  FIGS.  3 A- 3 B ). 
     With respect to trigger style lockouts, it is noted that a common lock out conventionally available on plastic ball valves can be a trigger style lock out. This lockout can employ a trigger on the handle of the valve and an engagement method between the trigger and the body of the valve. The trigger can employ a through hole for engagement by a padlock or hasp, thus allowing for a means of lockout (e.g., when a padlock or hasp is installed, the trigger may not be pulled). Some disadvantages of this design are that it may be cumbersome to operate and that similar to the metal slide plate, removal of the handle can allow the lock to be overcome. 
     With respect to the handle enclosure lockout, it is noted that the enclosure style lock-out can include the use of a housing, separate from the valve itself that wraps around the top, bottom and sides of the handle and can be locked close. This lockout generally works by preventing access to the valve handle. However, this lockout sometimes can be overcome by squeezing the lockout hard enough to deflect it into the handle (thus engaging the handle). Additionally, this lockout can sometimes be overcome by removing the handle. 
     An interest exists for improved ball valve assemblies and related methods of use. Some conventional assemblies/systems in this general field are described and disclosed in U.S. Pat. Nos. 5,323,805; 4,023,773; 6,695,285; 6,217,002; 4,411,407 and 3,380,708. These and other inefficiencies and opportunities for improvement are addressed and/or overcome by the assemblies, systems and methods of the present disclosure. 
     SUMMARY OF THE DISCLOSURE 
     The present disclosure provides for improved flow control assemblies for fluid systems. More particularly, the present disclosure provides for advantageous ball valve assemblies for fluid systems. 
     In exemplary embodiments, the present disclosure provides for improved ball valve assemblies and related features, systems and methods of use. Exemplary ball valve assemblies of the present disclosure offer many advantages over conventional assemblies including, without limitation, advantages in the sealing mechanisms of the ball valve assemblies, and advantages with the user interfaces of the ball valve assemblies (e.g., advantages with the lockout mechanisms). 
     Additional advantageous features, functions and applications of the disclosed assemblies, systems and methods of the present disclosure will be apparent from the description which follows, particularly when read in conjunction with the appended figures. References listed in this disclosure are hereby incorporated by reference in their entireties. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       Features and aspects of embodiments are described below with reference to the accompanying drawings, in which elements are not necessarily depicted to scale. 
       Exemplary embodiments of the present disclosure are further described with reference to the appended figures. It is to be noted that the various features, steps and combinations of features/steps described below and illustrated in the figures can be arranged and organized differently to result in embodiments which are still within the scope of the present disclosure. To assist those of ordinary skill in the art in making and using the disclosed assemblies, systems and methods, reference is made to the appended figures, wherein: 
         FIG.  1    is a cross-sectional side view of a conventional ball valve assembly; 
         FIGS.  2 - 11    depict some conventional lockout mechanisms for valves; 
         FIG.  12    is an exploded side view of a ball valve assembly according to an exemplary embodiment of the present disclosure, prior to assembly; 
         FIG.  13    is an exploded side perspective view of the ball valve assembly of  FIG.  12   ; 
         FIGS.  14  and  14 A  are side perspective views of the ball valve assembly of  FIG.  12   , after assembly; 
         FIG.  15    is a top view of the ball valve assembly of  FIG.  14   ; 
         FIGS.  16 ,  16 A and  16 B  are cross-sectional views of the ball valve assembly taken along the line A-A of  FIG.  15   ; 
         FIG.  17    is a side view of the ball valve assembly of  FIG.  14   ; 
         FIG.  18    is a bottom view of the ball valve assembly of  FIG.  14   ; 
         FIG.  19    is another top view of the ball valve assembly of  FIG.  12   ; 
         FIGS.  20 A and  20 B  are cross-sectional views of the ball valve assembly of  FIG.  19   ; 
         FIG.  21    is a front side view of an exemplary body member of the assembly of  FIG.  12   ; 
         FIGS.  22 - 23    are side perspective views of the body member of  FIG.  21   ; 
         FIG.  24    is a side view of the body member of  FIG.  21   ; 
         FIG.  25    is a side perspective view of the body member of  FIG.  21   ; 
         FIG.  26    is a side view of the body member of  FIG.  21   ; 
         FIG.  27    is a top view of the body member of  FIG.  21   ; 
         FIG.  28    is a side view of an exemplary first seat carrier of the assembly of  FIG.  12   ; 
         FIG.  29    is a side perspective view of the first seat carrier of  FIG.  28   ; 
         FIG.  30    is a side view of the first seat carrier of  FIG.  28   ; 
         FIG.  31    is a side perspective view of the first seat carrier of  FIG.  28   ; 
         FIG.  32    is a side view of the first seat carrier of  FIG.  28   ; 
         FIG.  33    is a side view of an exemplary second seat carrier of the assembly of  FIG.  12   ; 
         FIG.  34    is a side perspective view of the second seat carrier of  FIG.  33   ; 
         FIG.  35    is a side view of the second seat carrier of  FIG.  33   ; 
         FIG.  36    is a side perspective view of the second seat carrier of  FIG.  33   ; 
         FIG.  37    is a side view of the second seat carrier of  FIG.  33   ; 
         FIG.  38    is a side view of an exemplary seal retainer of the assembly of  FIG.  12   ; 
         FIG.  39    is a side perspective view of the seal retainer of  FIG.  38   ; 
         FIG.  40    is a side view of the seal retainer of  FIG.  38   ; 
         FIG.  41    is a side perspective view of the seal retainer of  FIG.  38   ; 
         FIG.  42    is a side view of the seal retainer of  FIG.  38   ; 
         FIG.  43    is a side view of an exemplary lock plate of the assembly of  FIG.  12   ; 
         FIG.  44    is a top view of the lock plate of  FIG.  43   ; 
         FIG.  45    is a bottom view of the lock plate of  FIG.  43   ; 
         FIG.  46    is a bottom perspective view of the lock plate of  FIG.  43   ; 
         FIG.  47    is a top perspective view of the lock plate of  FIG.  43   ; 
         FIG.  48    is a bottom perspective view of an exemplary handle of the assembly of  FIG.  12   ; 
         FIG.  49    is a cross-sectional side view of another exemplary ball valve assembly of the present disclosure; 
         FIG.  50    is a side view of another exemplary second seat carrier; 
         FIG.  51    is a side perspective view of the second seat carrier of  FIG.  50   ; 
         FIG.  52    is a side view of the second seat carrier of  FIG.  50   ; 
         FIG.  53    is a side perspective view of the second seat carrier of  FIG.  50   ; 
         FIG.  54    is a side view of the second seat carrier of  FIG.  50   ; 
         FIG.  55    is a side view of another exemplary seal retainer; 
         FIG.  56    is a side perspective view of the seal retainer of  FIG.  55   ; 
         FIG.  57    is a side view of the seal retainer of  FIG.  55   ; 
         FIG.  58    is a side perspective view of the seal retainer of  FIG.  55   ; 
         FIG.  59    is a side view of the seal retainer of  FIG.  55   ; 
         FIG.  60    is a cross-sectional side view of another exemplary ball valve assembly of the present disclosure; 
         FIG.  61    is a cross-sectional side view of another exemplary ball valve assembly of the present disclosure; and 
         FIG.  62    is a cross-sectional side view of another exemplary ball valve assembly of the present disclosure. 
     
    
    
     DETAILED DESCRIPTION OF DISCLOSURE 
     The exemplary embodiments disclosed herein are illustrative of advantageous ball valve assemblies, and systems of the present disclosure and methods/techniques thereof. It should be understood, however, that the disclosed embodiments are merely exemplary of the present disclosure, which may be embodied in various forms. Therefore, details disclosed herein with reference to exemplary ball valve assemblies/fabrication methods and associated processes/techniques of assembly and use are not to be interpreted as limiting, but merely as the basis for teaching one skilled in the art how to make and use the advantageous ball valve assemblies/systems of the present disclosure. 
     The present disclosure provides for improved flow control assemblies for fluid systems. More particularly, the present disclosure provides for advantageous ball valve assemblies for fluid systems. 
     In exemplary embodiments, the present disclosure provides for improved ball valve assemblies and related features, systems and methods of use. Exemplary ball valve assemblies of the present disclosure offer many advantages over conventional assemblies including, without limitation, advantages in the sealing mechanisms of the ball valve assemblies, and advantages with the user interfaces of the ball valve assemblies (e.g., advantages with the lockout mechanisms). 
     Referring now to the drawings, like parts are marked throughout the specification and drawings with the same reference numerals, respectively. Drawing figures are not necessarily to scale and in certain views, parts may have been exaggerated for purposes of clarity. 
     Referring now to  FIGS.  12 - 20 B , there is illustrated a ball valve assembly  10  according to exemplary embodiments of the present disclosure. Exemplary ball valve assembly  10  can include body member  12 , ball member  16 , stem member  20 , first seat member  30 , second seat member  32 , first seat carrier  40 , second seat carrier  42 , seal retainer  50 , first end connector  60 , second end connector  62 , first assembly fastener member  70  and second assembly fastener member  72 . Exemplary assembly  10  also includes lock plate  80  and handle  90 . In general, assembled ball valve assembly  10  can be utilized in fluid systems as a flow control assembly. Exemplary ball valve assembly  10  takes the form of a true union assembly  10 , although the present disclosure is not limited thereto. Rather, assembly  10  can take a variety of forms (e.g., unibody, etc.). 
     As discussed further below, exemplary ball valve assembly  10  offers many advantages over conventional assemblies including, without limitation, advantages in the sealing mechanisms of assembly  10 , and advantages with the user interfaces of the assembly  10  (e.g., advantages with the lockout mechanisms associated with lock plate  80 ). In particular and without limitation, it is noted that first seat carrier  40 , second seat carrier  42 , the sealing mechanisms associated with carriers  40 ,  42 , and lock plate  80  are advantageous components/features that contribute to some of the benefits of assembly  10  over conventional assemblies. 
     In certain embodiments and as shown in  FIGS.  12 ,  13  and  21 - 27   , the body member  12  can be the largest component of assembly  10 , and is the component configured to retain system pressure of assembly  10 . In an exemplary form, the body member  12  includes two cylinders  11 ,  13 . The larger cylinder  11  defines the main body bore  14  and provides a location/housing for the ball member  16 , seats  30 ,  32 , seat carriers  40 ,  42  and seal retainer  50 . Cylinder  11  of body member  12  extends from a first end  7  to a second end  9 . 
     The second, smaller cylinder  13  is the neck of the body  12  and defines a neck bore  15  for the stem  20  and stem seals. In an exemplary embodiment, the body  12  has an integral mounting pad  17  at the bottom of cylinder  11  of the body  12 . This pad  17  can be utilized for mounting the assembly  10  to a panel or the like. Exemplary body  12  also has a mounting flange  18  on top of and extending from the cylindrical neck  13  of the body  12 . This flange  18  can be used for mounting actuators on non-handle operated assemblies  10 . This mounting flange  18  can also be utilized in conjunction with the lock plate  80  to provide position indication, and can provide the ability to lock the assembly  10  (e.g., ball  16 ) in position, as discussed further below. 
     Exemplary stem member  20  is a substantially cylindrical component that provides an interface between the outside of the body member  12  and the ball member  16 . In an embodiment and as shown in  FIG.  16   , the stem member  20  has one or more O-ring grooves  21  (e.g., two O-ring grooves  21 ). When installed in the body member  12 , gasketing material  28  (e.g., O-rings) positioned within these O-ring grooves  21  provide a seal between the stem member  20  and the neck  13  of the body  12  (e.g., a piston seal and/or a face seal and/or a shoulder seal). Exemplary engagement between the ball  16  and stem  20  is slotted or the like, although the present disclosure is not limited thereto. It is noted that such ball  16  and stem  20  engagement could be a suitable geometry/engagement that allows the ball  16  to shift downstream under load. 
     When the ball  16  is positioned in the closed position as shown in  FIG.  20 A , the floating ball valve assembly  10  is configured to seal by allowing the ball  16  (and seats  30 ,  32  and carriers  40 ,  42 ) to float or move downstream (e.g., in the direction of Arrow A in  FIG.  20 A ) due to the load applied via upstream pressure (e.g., in reaction to an upstream load or applied pressure). 
     Similarly, when the ball  16  is positioned in the closed position as shown in  FIG.  20 B , the floating ball valve assembly  10  is configured to seal by allowing the ball  16  (and seats  30 ,  32  and carriers  40 ,  42 ) to float or move downstream (e.g., in the direction of Arrow B in  FIG.  20 B ) due to the load applied via upstream pressure (e.g., in reaction to an upstream load or applied pressure). 
     The ball  16  is positioned inside body  12 , and is engaged by seats  30 ,  32  and is engaged by the stem  20 . The engagement between the ball  16  and the seats  30 ,  32  can facilitate that the ball  16  remains in line with the central longitudinal axis AX of the body bore  14  of valve body  12  ( FIG.  21   ). 
     The engagement between the ball  16  and stem  20  can define the rotational position of the ball  16  in relation to the center point of the ball  16 . The engagement between the ball  16  and the stem  20  can also facilitate that the ball  16  is centered on the central stem axis C ( FIG.  21   ) of the neck bore  15  of valve body  12  (e.g., axis C of stem  20  positioned in bore  15 ) when the ball  16  is in the open position ( FIG.  16   ), and that the ball  16  can float or move along central longitudinal axis AX when the ball  16  is in the closed position ( FIGS.  20 A and  20 B ). Exemplary central stem axis C of neck bore is transverse or perpendicular to central longitudinal axis AX of body bore  14 . 
     As shown in  FIGS.  12 ,  13  and  16   , the exemplary engagement between the stem  20  and the ball  16  is via a female slot  5  on the outside diameter of the ball  16  (e.g., on top of ball  16 ). This slot  5  can be perpendicular to the bore  4  of the ball  16 . The slot  5  can be engaged via a male protrusion  31  on the stem  20 . As shown in  FIG.  16   , when the ball  16  is in the open position, the engagement between the sidewalls of the slot  5  and the protrusion  31  on the stem  20  can force the ball  16  to be centered on the stem axis C (e.g., ball  16  will not substantially move along axis AX in such position). As shown in  FIGS.  20 A and  20 B , when the ball  16  is in the closed position, the ball  16  can be free to float or move along the longitudinal axis AX of the valve body  12  (e.g., with slot  5  moving relative to protrusion  31 — FIG.  13   ). 
     The first and second seat members  30 ,  32  of assembly  10  are configured to create a seal between the ball  16  and the seat carriers  40 ,  42 . In exemplary embodiments, each seat  30 ,  32  is substantially cylindrical/circular with a through hole, and defines a substantially diamond-shaped cross-sectional profile revolved about a center axis, although the present disclosure is not limited thereto. Rather, it is noted that each seat  30 ,  32  can take a variety of shapes, forms and/or designs. In general, each exemplary seat  30 ,  32  is designed to deflect under load and return substantially to its original geometry when the load is removed. 
     As shown in  FIGS.  16  and  28 - 32   , exemplary first seat carrier  40  is substantially cylindrical with a through hole, and extends from an outer end  34  to an inner end  36 . First seat carrier  40  is configured and dimensioned to house and retain the first seat member  30 , and provides a seal to the body member  12 . For example and as shown in  FIGS.  16  and  31  and  32   , first seat carrier  40  can include an inner wall  37  configured to house, engage and/or abut against the outer end of seat  30  to house and retain the first seat member  30  within carrier  40 . Exemplary body  12  includes inner wall  2  (e.g., angled or spherical inner wall  2 ) configured to house, engage and/or abut against the outer end  34  (e.g., angled or spherical outer end  34 ) of carrier  40  to house and retain the carrier  40  within body  12  ( FIGS.  16 ,  26  and  28   ). 
     In an embodiment and as depicted in  FIGS.  16  and  28   , the first seat carrier  40  is sealed on its outside diameter (“OD”) or outer surface  38  via gasketing material  28  (e.g., O-ring  28 ) positioned within a groove  22  of outer surface  38  of carrier  40 , with the O-ring  28  in groove  22  providing a piston seal against the inner diameter (“ID”) or inner surface  3  of bore  14  of the body member  12 . 
     It is noted that the first seat carrier  40  can also utilize a face seal or some other sealing mechanism or combination of sealing mechanisms to provide a seal against the body  12 . Such seal could be separate from, or integral to first seat carrier  40 . For example, such seal could be integral to body  12  or some other component of assembly  10 . 
     In exemplary embodiments and as dictated by differential pressure, the first seat carrier  40  and seat  30  floats or moves downstream, in the direction of Arrow A in  FIG.  20 A , when the ball  16  of valve assembly  10  is closed (when the direction of Arrow A in  FIG.  20 A  represents the flow direction).  FIG.  20 A  depicts the ball  16  of valve assembly  10  in the closed position. As such, when the ball  16  is in the closed position and the direction of Arrow A represents the flow direction, the first seat carrier  40 , seat  30  and ball  16  are free to float or move along the longitudinal axis AX of the valve body  12  in the direction of Arrow A. 
     In other embodiments and as dictated by differential pressure, the first seat carrier  40  and seat  30  floats or moves downstream, in the direction of Arrow B in  FIG.  20 B , when the ball  16  of valve assembly  10  is closed (when the direction of Arrow B in  FIG.  20 B  represents the flow direction).  FIG.  20 B  depicts the ball  16  of valve assembly  10  in the closed position. As such, when the ball  16  is in the closed position and the direction of Arrow B represents the flow direction, the first seat carrier  40 , seat  30  and ball  16  are free to float or move along the longitudinal axis AX of the valve body  12  in the direction of Arrow B. 
     As shown in  FIGS.  16  and  33 - 37   , exemplary second seat carrier  42  is substantially cylindrical with a through hole, and extends from an outer end  39  to an inner end  41 . Second seat carrier  42  is configured and dimensioned to house and retain the second seat member  32 , and provides a seal to the body member  12 , and also provides a seal to the seal retainer  50  (thus preventing bypass between the body  12  and the seal retainer  50 ). For example and as shown in  FIGS.  16  and  34 - 35   , second seat carrier  42  can include an inner wall  43  configured to house, engage and/or abut against the outer end of seat  32  to house and retain the second seat member  32  within carrier  42 . As discussed further below, exemplary seal retainer  50  includes inner wall  52  (e.g., planar inner wall  52 ) configured to house, engage and/or abut against the outer end  39  (e.g., planar outer end  39 ) of carrier  42  to house and retain the carrier  42  within seal retainer  50  ( FIGS.  16 ,  33  and  40   ). 
     In an embodiment and as depicted in  FIGS.  16  and  33   , the second seat carrier  42  is sealed on its OD or outer surface  44  via gasketing material  28  (e.g., O-rings  28 ) positioned within grooves  23 ,  24  of outer surface  44  of carrier  42 , with the O-ring  28  in groove  23  providing a piston seal against the ID or inner surface  3  of bore  14  of the body member  12 , and with the O-ring  28  in groove  24  providing a piston seal against the ID or inner surface  53  of the seal retainer  50 . 
     It is noted that the example embodiment has two O-rings  28  on second seat carrier  42  in order to prevent bypass between body  12  and seal retainer  50 . However, this could be sealed via other methods. It is also noted that the second seat carrier  42  can also utilize a face seal or some other sealing mechanism or combination of sealing mechanisms to provide a seal against the body  12  and/or retainer  50 . Such seals could be separate from, or integral to second seat carrier  42 . Such seals could be integral to body  12  or to retainer  50  of assembly  10 . 
     In exemplary embodiments and as dictated by differential pressure, the second seat carrier  42  and seat  32  floats or moves downstream, in the direction of Arrow A in  FIG.  20 A , when ball  16  of the valve assembly  10  is closed (when the direction of Arrow A in  FIG.  20 A  represents the flow direction). Again,  FIG.  20 A  depicts the ball  16  of valve assembly  10  in the closed position. As such, when the ball  16  is in the closed position and the direction of Arrow A represents the flow direction, the second seat carrier  42 , seat  32  and ball  16  are free to float or move along the axis AX of the valve body  12  in the direction of Arrow A. 
     In other embodiments and as dictated by differential pressure, the second seat carrier  42  and seat  32  floats or moves downstream, in the direction of Arrow B in  FIG.  20 B , when the ball  16  of valve assembly  10  is closed (when the direction of Arrow B in  FIG.  20 B  represents the flow direction). As such, when the ball  16  is in the closed position and the direction of Arrow B represents the flow direction, the second seat carrier  42 , seat  32  and ball  16  are free to float or move along the axis AX of the valve body  12  in the direction of Arrow B. 
     In certain embodiments and as shown in  FIGS.  16  and  38 - 42   , seal retainer  50  is substantially circular/cylindrical with a through hole, and extends from an outer end  45  to an inner end  47 . Exemplary seal retainer  50  is configured to mount to the second end  9  of the body  12  and to retain the internal components (e.g., ball  16 , carriers  40 ,  42 , seats  30 ,  32 ) within bore  14  of body  12  of the valve assembly  10 . 
     As noted, seal retainer  50  includes inner wall or counter-bore  52  configured to house, engage and/or abut against the outer end  39  of carrier  42  to house and retain at least a portion of the carrier  42  within seal retainer  50 . Second seat carrier  42  provides a seal to the seal retainer  50  via gasketing material  28  in groove  24 , thus preventing bypass between the body  12  and the seal retainer  50  (e.g., with O-ring  28  in groove  24  providing a piston seal against inner surface  53  of seal retainer  50 ). 
     As discussed further below and as shown in  FIGS.  12 ,  13 ,  16  and  41   , an engagement surface  63  of end connector  62  engages abutment surface  51  of seal retainer  50 , with gasketing material  28  (e.g., O-ring  28 ) positioned within groove  26  of abutment surface  51  of seal retainer  50 , and with the O-ring  28  in groove  26  providing a face seal of engagement surface  63  of end connector  62  against abutment surface  51  of seal retainer  50 . 
     In an embodiment and as depicted in  FIGS.  16  and  25   , the inner surface  3  of second end  9  of body  12  includes threads  8  that extend from the second end  9  to an abutment wall  46  of body  12  positioned a distance from second end  9 . 
     As shown in  FIGS.  16  and  38   , exemplary seal retainer  50  is threaded with threads  48  on its OD or outer surface  54 , with the threads  48  of seal retainer  50  configured to engage threads  8  of body  12  until inner end  47  of seal retainer  50  abuts or engages the abutment wall  46  of body  12 . 
     In certain embodiments, the depth the seal retainer  50  is driven to or positioned within second end  9  and relative to the body member  12  dictates how much preload is applied to the seats  30 ,  32 . In an embodiment, the inner end  47  of seal retainer  50  is driven/mounted/threaded to a hard stop against abutment wall  46  of body  12  (e.g., via engagement of threads  8 ,  48 ), and may not require adjustment. 
     While exemplary seal retainer  50  is shown as threaded with threads  48 , it is noted that retainer  50  could have a suitable geometry without threads that engages body  12  and that can retain load (e.g., including retainer  50  welded to or integrally formed with body  12 ). For example, if retainer  50  is integrally formed with body  12 , the ball  16 , stem  20 , seat carriers  40 ,  42  and seats  30 ,  32  can be assembled together, and then body  12  with integral retainer  50  can be formed around such fabrication of ball  16 , stem  20 , seat carriers  40 ,  42  and seats  30 ,  32  assembled together. 
     It is also noted that seal retainer  50  could also not include threads and be retained by a fastener  72  (or  70 ) or the like. 
     In other embodiments, seal retainer  50  could also be positioned on first end  7  of body  12 . In such cases where assembly  10  includes retainers  50  on both sides  7 ,  9  of body  12 , then first seat carrier  40  and first end  7  of body  12  could be configured, dimensioned and adapted to operate and function similarly to second seat carrier  42  and similarly to second end  9  of body  12 . 
     It is noted that the example embodiment provides that the seal retainer  50  can be driven to a hard stop against abutment wall  46 , however, it is noted that retainer  50  could remain adjustable. For example, if retainer  50  is desired to be adjustable, retainer  50  could be driven or moved to a predefined location or position along threads  8  between second end  9  and wall  46 , or it could be further tightened against wall  46  to create appropriate/desired seat load on seats  30 ,  32 . 
     As discussed further below and as shown in  FIGS.  12 ,  13 ,  14 A,  16 ,  27  and  43 - 47   , exemplary lock plate  80  is configured to couple the handle  90  to the stem  20 , to provide stops at the full open and the full closed positions, and to provide a means of locking the valve assembly  10  (e.g., ball  16 ) in position. In an exemplary embodiment, the lock plate  80  includes windows  83  therethrough (e.g., two windows  83  positioned 180° apart on plate  80 ) configured to indicate valve assembly  10  (e.g., ball  16 ) position (e.g., Open or Closed). It is noted that lock plate  80  can be used on other valve types, and it may not be exclusive to floating ball valves. 
     As shown in  FIGS.  12 ,  13 ,  16  and  48   , exemplary handle  90  is configured to provide a means of operating the valve assembly  10  (e.g., operating/moving ball  16 ). In an embodiment, the handle  90  includes a socket  91  that is designed to engage the protrusion  85  of lock plate  80 . Exemplary handle can take the form of a “T” design or shape, although the present disclosure is not limited thereto. Rather, handle  90  can take a variety of shapes/forms (e.g., lever design or other shapes/styles). In alternate embodiments, it is noted that the handle  90  can engage the stem  20  directly (e.g., and not via plate  80 ). 
     In other embodiments, it is noted that handle  90  and lock plate  80  can be integral with one another (e.g., as an integrally formed or molded one-piece component that includes handle  90  and plate  80 ). Exemplary one-piece handle  90  and plate  80  can be configured to couple to stem  20  (e.g., via socket  84 , as discussed further below). 
     As depicted in  FIGS.  12 ,  13  and  16   , exemplary end connectors  60 ,  62  are configured to provide a means of connecting the valve assembly  10  to a pipe line or the like. End connectors  60 ,  62  can provide socket (for solvent welding or socket fusion) or threaded connections. Exemplary end connectors  60 ,  62  are substantially circular/cylindrical with a through hole. 
     As shown in  FIGS.  12 ,  13  and  16   , the engagement surfaces  61 ,  63  of the end connectors  60 ,  62  are configured to engage a face seal on the body member  12  and seal retainer  50 , respectively, to generate a seal between the end connector  60  and first end  7  of body  12 , and between the end connector  62  and seal retainer  50 . More particularly and in certain embodiments, engagement surface  61  of end connector  60  engages outer surface  6  of first end  7  of body  12  ( FIG.  22   ), with an O-ring  28  positioned within groove  25  of outer surface  6  of first end  7  of body  12  ( FIG.  16   ), with the O-ring  28  in groove  25  providing a face seal of engagement surface  61  against outer surface  6  of first end  7  of body  12  ( FIGS.  12  and  16   ). 
     Similarly, engagement surface  63  of end connector  62  engages abutment surface  51  of seal retainer  50 , with an O-ring  28  positioned within groove  26  of abutment surface  51  of seal retainer  50 , with the O-ring  28  in groove  26  providing a face seal of engagement surface  63  against abutment surface  51  of seal retainer  50 . 
     As shown in  FIGS.  12 ,  13  and  16   , exemplary assembly fasteners  70 ,  72  are configured to retain the end connectors  60 ,  62  on the body  12  of the valve assembly  10 . Assembly fasteners  70 ,  72  can be substantially circular/cylindrical with a through hole. 
     As depicted in  FIG.  13   , each exemplary assembly fastener  70 ,  72  has an internal thread  71  that engages an external thread  55  on the body  12 . As each assembly fastener  70 ,  72  is tightened onto the body  12  of valve assembly  10 , assembly fasteners  70 ,  72  engage the shoulder surfaces  65 ,  67  on the OD of end connectors  60 ,  62 , respectively ( FIG.  12   ), and this engagement forces the end connector  60  against the face seal of outer surface  6  of first end  7  of body  12 , and forces the end connector  62  against the face seal of abutment surface  51  of seal retainer  50  (and against second end  9 ). 
     Exemplary valve assembly  10  is a floating ball valve assembly  10 . However, instead of utilizing seats that are fixed in relation to the seal retainer and the valve body, the exemplary assembly  10  advantageously utilizes seats  30 ,  32  that are installed in seat carriers  40 ,  42 . 
     The seat carriers  40 ,  42  (and seats  30 ,  32 ) are allowed to float, move or translate along the horizontal axis AX of the valve assembly  10 . As noted, carriers  40 ,  42  are sealed within the valve assembly  10  via piston seals between the OD of the seat carriers  40 ,  42  and the ID of the valve body  12  and seal retainer  50 . 
     When the valve assembly  10  (e.g., ball  16 ) is closed, the initial seal is generated via preload on the seats  30 ,  32  established at assembly. As the differential pressure acts on the pressure area of the ball  16 , the ball  16  is forced to float or move downstream (e.g., along axis AX in the direction A in  FIG.  20 A , or direction B in  FIG.  20 B ) and the ball  16  applies additional load on the downstream seat (e.g.,  30  or  32 ), thus increasing the contact stress on the downstream seat and improving the seal between the ball  16  and the downstream seat. 
     The differential pressure acting on the ball  16  is the difference in pressure between the upstream and the downstream. The area on the ball  16  on which the differential pressure acts is the projected area inside the seal between the ball  16  and the respective seat  30 ,  32 . The projected area can be adjusted in the design by adjusting the seal location between the ball  16  and the respective seat  30 ,  32 . 
     One advantageous improvement of assembly  10  can be realized at the upstream seat (e.g.,  30  or  32 ) and seat carrier (e.g.,  40  or  42 ). In some conventional floating ball valves, sometimes as the ball floats downstream it can move away from the upstream seat and, at some level of differential pressure, the seal between the upstream seat and the ball can be lost. 
     By utilizing a floating seat carrier (e.g.,  40 ,  42 ) on the upstream seat (e.g.,  30  or  32 ), the upstream seat carrier and the upstream seat are allowed to float or move downstream (e.g., along axis AX in the direction A in  FIG.  20 A , or direction B in  FIG.  20 B ) along with the ball  16 , thus allowing assembly  10  to retain both a downstream and an upstream seal (e.g., effectively a primary and a secondary seal). 
     The upstream seat carrier (e.g.,  40  or  42 ) is motivated to float or move downstream due to differential pressure acting on the pressure area of the seat carrier. The differential pressure acting on the upstream seat carrier is the difference in pressure between the upstream and the central cavity of the valve body  12 . In the event of a failure to seal at the downstream seat (e.g., seat  30  or  32 ), this differential pressure is equal to the difference in pressure between the upstream cavity and the downstream. The upstream pressure area of the seat carrier can be defined as the difference in the projected area of the body ID or seal retainer ID and the projected area inside the seal between the ball  16  and the seat (the ball pressure area). 
     It is noted that seat carriers  40 ,  42  can be designed such that each provides two different pressure areas (e.g., the pressure area on the first end  7  side of the carrier  40  could be different than the pressure area on the valve cavity side of the carrier  40 ; the pressure area on the second end  9  side of the carrier  42  could be different than the pressure area on the valve cavity side of the carrier  42 ). 
     In addition to applying load to (and thereby improving) the upstream seal, the load created by the upstream seat carrier (e.g.,  40  or  42 ) is transferred into the ball  16 , thus further increasing the load on the downstream seat (e.g., seat  30  or  32 ), and thereby further improving the downstream seal. This additional load is above and beyond what is achievable with existing floating ball valves. This additional load can be especially beneficial at low (e.g., less than 2 psi) line pressures where the force applied to the differential area of the ball  16  (and thereby to the downstream seat) is relatively small. 
     In some embodiments, as the differential pressure acts on the pressure area of the ball  16 , the ball  16  is forced to float or move downstream (e.g., direction A in  FIG.  20 A , or direction B in  FIG.  20 B ) and apply additional load on the extreme downstream seat (e.g., seat  32  for direction A, or seat  30  for direction B), thus increasing the contact stress on the extreme downstream seat and improving the seal between the ball  16  and the extreme downstream seat  30  or  32 . 
     Thus and in certain embodiments, when the ball member  16  is rotated to a fully closed position and when the downstream direction is configured to flow from the first end  7  to the second end  9  of the body member  12  (e.g., direction of arrow A in  FIG.  20 A ), then: (i) the ball member  16  is configured to move along the central longitudinal axis AX in the downstream direction and apply a downstream load against the second seat  32  in reaction to the upstream load or applied pressure, with the downstream load increasing sealing contact stress between the ball member  16  and the second seat  32 , and (ii) the first seat carrier  40  and the first seat  30  are configured to move along the central longitudinal axis AX in the downstream direction and apply an additional downstream load against the ball member  16  in reaction to the upstream load or applied pressure, the additional downstream load increasing sealing contact stress between the ball member  16  and the first seat  30  and between the ball member  16  and the second seat  32 . 
     Similarly, when the ball member  16  is rotated to a fully closed position and when the downstream direction is configured to flow from the second end  9  to the first end  7  of the body member  16  (e.g., direction of arrow B in  FIG.  20 B ), then: (i) the ball member  16  is configured to move along the central longitudinal axis AX in the downstream direction and apply a downstream load against the first seat  30  in reaction to the upstream load or applied pressure, the downstream load increasing sealing contact stress between the ball member  16  and the first seat  30 , and (ii) the second seat carrier  42  and the second seat  32  are configured to move along the central longitudinal axis AX in the downstream direction and apply an additional downstream load against the ball member  16  in reaction to the upstream load or applied pressure, the additional downstream load increasing sealing contact stress between the ball member  16  and the second seat  32  and between the ball member  16  and the first seat  30 . 
     Due to the additional load that the seat carriers  40 ,  42  can apply to the downstream seal, the required preload on the seats  30 ,  32  is reduced. Since the preload on the seats  30 ,  32  is reduced, the tendency for the seats  30 ,  32  to creep over time is minimized or eliminated. This can be especially realized on valve assemblies utilizing deflecting seats instead of crush seats. By minimizing seat  30 ,  32  creep, the need to adjust the seal retainer  50  is also minimized or eliminated. This allows the valve assembly  10  to be designed such that the seal retainer  50  can be installed against a hard stop (e.g., wall  46 ), or is installed to a set position (e.g., along threads  8 ). This can significantly improve manufacturability and serviceability of the valve assembly  10 . 
     Moreover, since the preload on the seats  30 ,  32  can be reduced, this thereby reduces stem torque, which thereby facilitates easier and more user-friendly operation of assembly  10 . 
     Additionally, with the seal retainer  50  designed to be located at a single position (e.g., non-adjustable), the valve assembly  10  can be designed to have the ball  16  centered in relation to the stem  20  (e.g., axis C) when in the open position ( FIG.  16   ). This allows the valve assembly  10  to operate more smoothly and substantially eliminates the “camming” action that can result from a ball  16  that is forced off-center. This effect can be further enhanced by designing the seat carriers  40 ,  42  such that, when the valve  10  is open, they do not apply additional load to the ball  16 . 
     In addition to the significant benefits that the floating seat carriers  40 ,  42  provide for maintaining and improving upstream and downstream seals, the floating seat carriers  40 ,  42  also provide for a means of relieving cavity pressure. In a closed valve with both upstream and downstream seals, cavity pressure can potentially increase to a level greater than upstream or downstream pressure. There can be several causes for this phenomenon, but some common causes are temperature changes and chemical reactions inside the valve cavity. When cavity pressure increases, it is important that the valve assembly  10  have a means of relieving this pressure past the seats  30 ,  32 . If the valve remains sealed at the upstream and downstream seats  30 ,  32 , and does not relieve the pressure, there is the potential for the cavity pressure to cause the valve  10  to suffer catastrophic failure. By utilizing floating seat carriers  40 ,  42 , an increase in cavity pressure changes the loading on the upstream seat carrier (and, therefore, the upstream seat). By manipulating the pressure areas on the seat carrier  40 ,  42 , the valve  10  can be designed to relieve body cavity pressure upstream when cavity pressure is equal to, greater than, or even less than upstream line pressure. 
     Exemplary ball valve assembly  10  also offers several improvements to the user interface. One notable improvement can result from the addition of the lock plate  80 . Exemplary lock plate  80  is configured to provide a means of locking the valve assembly  10  (e.g., ball  16 ) in position. Lock plate  80  can also be configured to provide a means of indicating the position of the ball  16  of valve assembly  10  (e.g., Open or Closed). Lock plate can also be configured to provide a means of coupling the handle  90  to the stem  20 . 
     In exemplary embodiments and as shown in  FIGS.  14 A and  44 - 47   , the lock plate  80  is configured to provide a means of locking the ball  16  of valve assembly  10  via holes  82  (e.g., four holes  82 ) therethrough. Holes  82  can run parallel (or other suitable direction) to the axis C of the stem  20 . 
     As the valve assembly  10  is rotated to a fully open position ( FIGS.  15  and  16   ) or fully closed position ( FIGS.  19  and  20 A / 20 B), these holes  82  are configured to align with a respective hole or aperture  19  in the top flange  18  of the valve body  12  ( FIGS.  14 A,  19  and  27   ). When in these positions (e.g., fully open or fully closed) and as shown in  FIG.  14 A , a padlock or hasp  64  can be installed through the aligned holes  82  of lock plate  80  and the holes  19  of body  12  to prevent the lock plate  80  from rotating. Since the lock plate  80  engages the stem  20  (which engages the ball  16 ), the lock plate  80  can effectively lock the ball  16  of valve assembly  10  in position. The fit or engagement between the lock plate  80  and the stem  20 , and the fit or engagement between the lock plate  80  and stem bore  15  of the body  12  can be tight enough to prevent the lock plate  80  from being removed when a lock or hasp  64  is installed. When no lock  64  is installed, the lock plate  80  can be pulled directly away from the top of the valve body  12 , with a minimum of rotation, in order to be removed. When a lock/hasp  64  is installed, the lock/hasp  64  acts as a hinge, forcing the lock plate  80  to attempt to rotate, and thus preventing removal of the lock plate  80  thereby preventing operation of the valve assembly  10 . 
     Holes  82  can be provided on plate  80  in an industry standard bolt pattern, or other suitable bolt patterns or the like. Holes  82  can take a variety of suitable shapes/forms (e.g., round, oblong, square, etc.). Holes  82  can be provided in various different/differing sizes to accommodate different lock  64  sizes/shapes. Plate  80  can include multiple hole  82  locations for locking the valve  10  (e.g., ball  16 ) in intermediate positions (e.g., between fully open and fully closed). In some embodiments, plate  80 /holes  82  could be configured to only lock in one position (e.g., only fully closed or only fully open). 
     In other embodiments, it is noted that lock  64  could be mounted through a hole in the neck  13  of body  12 , thereby engaging the stem  20 , handle  90  and/or an alternate piece/component, thereby preventing rotation of the stem  20 /ball  16 . 
     As depicted in  FIGS.  15 ,  19  and  44 - 47   , exemplary lock plate  80  can provide a means of position indication of ball  16  by means of the two slots or windows  83  that are positioned therethrough in the face portion of lock plate  80 . When the ball  16  of valve assembly  10  is in the fully open position ( FIG.  15   ) or the fully closed position ( FIG.  19   ), these windows  83  expose text  27  or the like that is on the mounting flange  18  of the valve body  12  ( FIGS.  15 ,  19  and  27   ). This text  27  can indicate that the valve assembly  10  is “Open” or “Closed.” This feature can be especially valuable on valve assemblies  10  that have had the handle  90  removed, as the handle  90  can be used to indicate valve position. Text  27  or other indicators (e.g., position indication markings) can provide degrees, percent open, or other variant between open and closed. Windows  83  can be fully cut out of plate  80  (e.g., windows  83  could have three or less sides, instead of four sides). 
     As shown in  FIGS.  16 ,  46  and  48   , the lock plate  80  can be configured to provide a means of coupling the handle  90  to the stem  20  via a female socket  84  on the bottom of the plate  80  which couples to stem  20  (e.g., via a snap-fit connection), and via the engagement protrusion  85  on top of the plate  80  which couples to socket  91  of handle  90  (e.g., via a snap-fit connection). 
     In certain embodiments and as depicted in  FIGS.  45 - 46   , the bottom surface of plate  80  (e.g., the external surface of female socket  84 ) can include an abutment protrusion  86  (e.g., an abutment protrusion  86  that encompasses or extends a 90° quadrant around socket  84 ). Exemplary abutment protrusion extends from a first end  87  to a second end  89 . 
     As depicted in  FIG.  27   , the engagement protrusion  86  can be configured to engage and/or be positioned within a mating groove  29  or the like in mounting flange  18  proximal to bore  15  (e.g., with the groove  29  in flange  18  encompassing or extending 180° in flange  18 ). Exemplary groove extends from a first wall  73  to a second wall  75 . 
     When protrusion  86  is positioned in groove  29  (e.g., when plate  80  is mounted to flange  18  of body  12 ), the plate  80  (and handle  90 , stem  20  and ball  16 ) can be rotated (e.g., 90°) from a first position where the first end  87  of protrusion  86  abuts against first wall  73  of groove  29  (e.g., a fully closed position for ball  16 ) to a second position where the second end  89  of protrusion  86  abuts against second wall  75  of groove  29  (e.g., a fully open position for ball  16 ). As such, protrusion  86  of plate  80  and groove  29  of flange  18  advantageously provide hard stops at the full open and the full closed positions of ball  16 . 
     In other embodiments, it is noted that lock plate  80  could be integrated to handle  90 . In other embodiments, there could be other combinations of engaging geometries or the like between plate  80  and handle  90 . 
     It is noted that having a component (e.g., plate  80 ), separate from the handle  90  and stem  20 , to couple the handle  90  and stem  20  can be advantageous for several reasons. For example, such a coupling between the handle  90  and stem  20  is desirable in that some end users may remove handles  90  from valves  10  that are not locked in position in order to deter operation of the valve  10 . This can be common of locations with potential for public access as well as applications where valve operation is undesirable, but does not create a safety hazard. Among end users who remove handles from valves, roughly half prefer for the stem to be exposed (allowing for relatively easy valve operation with a wrench) and the other half prefer for the stem to be recessed inside the valve (thus making operation with a wrench more difficult). By utilizing a lock plate  80  with an integral coupling, both preferences can be served (e.g., the former can remove just the handle  90 , the latter can remove the handle  90  and lock plate  80 ). 
     Another reason such coupling between the handle  90  and stem  20  is desirable is to allow for actuators to be mounted directly to the mounting flange  18  on the valve body  12 . Some standards for stem engagement (that some actuators are designed around) were written with the intent that the valve stem would be manufactured from metal. As such, attempting to mate directly to the actuator with a plastic stem may result in a stem too weak to handle the applied load. By recessing the stem  20 , a metal coupling can be made to adapt the plastic stem (and its larger cross section) to the relatively small bore of the actuator. Since exemplary stem  20  is recessed, the bulk of the coupling can fit inside of the stem bore  15  of the body  12  (on top of and around the stem  20 ), thus allowing a standard actuator to be mounted directly to the valve body  12 . 
     Another reason such a coupling between the handle  90  and stem  20  is desirable is to simplify valve assembly. During assembly, the stem  20  can be inserted into the main bore  14  of the valve body  12 , then rotated and pressed into the stem bore  15 . As the stem  20  length increases relative to the bore  14  of the body  12 , this operation becomes more difficult and the likelihood of damaging a seal in the process is increased. Using a coupling (e.g., plate  80 ) between the stem  20  and the handle  90  allows the stem  20  length to be minimized. 
     The exemplary ball valve assembly  10  provides many advantages. One advantage includes improved sealing due to increased load area for differential pressure to act on. Another advantage includes the upstream seal provides a secondary seal if the downstream seal becomes damaged. 
     Another advantage includes the exemplary seat carriers  40 ,  42  are “self-centering”—e.g., the ball  16  and seats  30 ,  32  return to naturally centered position when the ball  16  is in the closed position. Another advantage includes, in some embodiments, driving the seal retainer  50  to a hard stop simplifies manufacturing as well as rebuilding in the field. Another advantage includes the deflecting seats  30 ,  32  allow for considerably larger manufacturing windows than crush seats used on some plastic valves. 
     Another advantage includes the configuration/design of assembly  10  does not trap cavity pressure. This is a result of floating seat carriers  40 ,  42  being forced away from the ball  16  when cavity pressure exists, and seats  30 ,  32  being designed to deflect off the ball  16  under differential load created by cavity pressure. 
     Another advantage includes the exemplary lockout (e.g., plate  80 ) cannot be removed from the valve assembly  10  (without destruction) when the valve assembly  10  is locked-out. Another advantage includes the exemplary removable lockout  80  allows exposed or recessed flats for customers who remove the handle  90  as a deterrent to valve assembly  10  operation. Another advantage includes the exemplary recessed stem  20  and bolt pattern flange  18  allow for a direct mount of an actuator to valve assembly  10  (e.g., with use of intermediate coupling). Another advantage includes the windows  83  in the lock plate  80  provide clear indication of valve position (e.g., via text  27 ), even when the handle  90  is removed. 
     In other embodiments, first seat carrier  40  and/or second seat carrier  42  can be a spring-loaded carrier  40 ,  42 .  FIG.  49    depicts second seat carrier  142  being a spring-loaded carrier  142 , via spring  33  positioned between carrier  142  and seal retainer  150 . For example, such springs  33  can be metallic, plastic or rubber (e.g., O-ring). Such springs  33  can be wetted or non-wetted. Such springs  33  can be integral to seat carrier  40 ,  42  and/or  142  (e.g., thereby providing a flexing carrier  40 ,  42  and/or  142 ). In some embodiments, a spring  33  can be positioned between the first seat carrier  40  and the body member  12  (and/or with spring  33  positioned between carrier  142  and seal retainer  150 ). 
     The compression generated on the spring(s)  33  during fabrication of the ball valve assembly  10  can perform several functions. For example, such compression can be used to generate pre-load on the seats ( 30 ,  32 ) to create an initial seal with ball member  16 , and/or it can assist in motivating the upstream seat carrier ( 40 ,  42 ) to move downstream when the ball member  16  is closed, and/or it can be used to enhance the centering of the ball member  16  within the valve assembly  10  in the open position. The valve assembly  10  and spring(s)  33  can be sized such that the spring(s)  33  are substantially fully compressed during assembly, or such that they are allowed to compress further during operation of the valve assembly  10 . 
       FIG.  49    also shows seal retainer  150  including groove  35  for gasketing material  28  to form an alternative seal with seat carrier  142 . 
     As shown in  FIGS.  49 - 54   , exemplary second seat carrier  142  is substantially cylindrical with a through hole, and extends from an outer end  139  to an inner end  141 . Second seat carrier  142  is configured to house and retain the second seat member  32 , and provides a seal to the body member  12 , and also provides a seal to the seal retainer  150  (thus preventing bypass between the body  12  and the seal retainer  150 ). Second seat carrier  142  includes an inner wall  143  configured to house, engage and/or abut against the outer end of seat  32  to house and retain the second seat member  32  within carrier  142 . 
     Second seat carrier  142  is sealed on its OD or outer surface  144  via gasketing material  28  (e.g., O-rings  28 ) positioned within groove  123 , with the O-ring  28  providing a piston seal against the ID or inner surface  3  of body  12 , as similarly discussed above in connection with carrier  42 . 
     As similarly discussed above and as dictated by differential pressure, second seat carrier  142  floats or moves downstream, in the direction of Arrow A in  FIG.  20 A , when ball  16  of the valve assembly  10  is closed (when the direction of Arrow A in  FIG.  20 A  represents the flow direction). In other embodiments and as dictated by differential pressure, second seat carrier  142  floats or moves downstream, in the direction of Arrow B in  FIG.  20 B , when the ball  16  of valve assembly  10  is closed (when the direction of Arrow B in  FIG.  20 B  represents the flow direction). 
     As shown in  FIGS.  49  and  55 - 59   , seal retainer  150  is substantially circular/cylindrical with a through hole, and extends from an outer end  145  to an inner end  147 . Exemplary seal retainer  150  is configured to mount to the second end  9  of the body  12  and to retain the internal components (e.g., ball  16 , carrier  142 , seat  32 ) within bore  14  of body  12 , as similarly discussed above in connection with retainer  50 . 
     Seal retainer  150  includes inner wall  152  configured to house, engage and/or abut against the outer end  139  of carrier  142  to house and retain at least a portion of the carrier  142  within seal retainer  150 . Seal retainer  150  provides a seal to the carrier  142  via gasketing material  28  in groove  35  of retainer  150 , thus preventing bypass between the body  12  and the seal retainer  150  (e.g., with O-ring  28  in groove  35  providing a piston seal against outer end  139  of carrier  142 ). 
     As similarly discussed above, an engagement surface  63  of end connector  62  engages abutment surface  151  of seal retainer  150 , with gasketing material  28  positioned within groove  126  of abutment surface  151  of seal retainer  150 , and with the O-ring  28  in groove  126  providing a face seal of engagement surface  63  of end connector  62  against abutment surface  151  of seal retainer  150 . 
     Exemplary seal retainer  150  is threaded with threads  148  on its OD or outer surface  154 , with the threads  148  of seal retainer  150  configured to engage threads  8  of body  12  (e.g., until inner end  147  of seal retainer  150  abuts or engages the abutment wall  46  of body  12 ). 
     It is noted that the example embodiment provides that the seal retainer  150  can be driven to a hard stop against abutment wall  46 , however, it is noted that retainer  150  could remain adjustable. For example, if retainer  150  is desired to be adjustable, retainer  150  could be driven to a predefined location or position along threads  8  between second end  9  and wall  46 , or it could be further tightened against wall  46  to create appropriate/desired seat load on seats  30 ,  32 . 
     As noted above, a spring  33  can be positioned between carrier  142  and seal retainer  150  (e.g., positioned between wall  178  of carrier  142  and inner end  147  of retainer  150 ). As such, spring  33  can thereby provide a flexing carrier  142 . 
       FIG.  49    also shows seat  30  not including seat carrier  40 . Therefore and in some embodiments without seat carrier  40 , seat  30  is not configured to float. 
       FIG.  60    shows assembly  10  with seat  30  not including seat carrier  40  (e.g., seat  30  is not configured to float/move), and assembly  10  includes seat  32  and seat carrier  42 . In other embodiments, it is noted that seat carrier  40  could take the form/shape of seat carrier  42  or  142  (and include retainer  50 ,  150 ), and seat  32  could or could not include carrier  42 ,  142  and retainer  50 ,  150  (e.g., seat  32  may or not be configured to float). 
     In some embodiments, assembly  10  may include seat carrier  40 , and may not include seat carrier  42 . In other embodiments, assembly  10  may include seat carrier  42 , and may not include seat carrier  40 . 
       FIG.  61    shows seat  30  not including seat carrier  40 .  FIG.  61    also shows seal retainer  150 ′ including groove  35  for gasketing material  28  to form a seal with seat carrier  142 ′.  FIG.  61    depicts seal retainer  150 ′ being an adjustable seal retainer  150 ′ (e.g., via threading  148 ′ on seal retainer  150 ′ and threading  8  on body  12 ). As shown in  FIG.  61   , there may not be a spring  33  or the like positioned between retainer  150 ′ and carrier  142 ′. 
       FIG.  62    depicts second seat carrier  142  being an O-ring-loaded carrier  142 , via O-ring  133  positioned between retainer  150  and carrier  142 . O-ring  133  is configured and dimensioned to function as a spring to act on seat carrier  142 , as similarly discussed above in connection with spring  33 . 
     In certain embodiments, first seat carrier  40  and/or second seat carrier  42  can be integral to seat  30 ,  32 . For example, first seat carrier  40  can be integral with seat  30 , thereby providing an oversized seat  30  having a seal on its OD (or elsewhere). Such oversized seats  30  (or  32 ) can have a spring as well (e.g., integral or non-integral spring). 
     In other embodiments, first seat carrier  40  and/or second seat carrier  42  can be configured and dimensioned to spring to relieve pressure, and/or to maintain seat load. Such features may be especially useful with crush seats. 
     In certain embodiments, first seat carrier  40  and/or second seat carrier  42  could have two different seal diameters that could be loaded via compressible fluid. The volume of compressible fluid may be trapped between seals and create a cushion effect that forces seat carrier  40 ,  42  towards (or away from) ball  16 . Carriers  40  and  42  could also be loaded via non-compressible fluid with a port through body  12  or elsewhere. 
     In exemplary embodiments, the present disclosure provides for a ball valve assembly including floating (pressure energized) or moving seat carriers  40 ,  42 ,  142  with a floating/moving ball  16 . The present disclosure also provides for a ball valve assembly  10  including spring loaded seat carriers  40 ,  42 ,  142  with a non-wetted spring and floating ball  16 . 
     The present disclosure also provides for a ball valve assembly including a seat carrier  40 ,  42 ,  142  with compressed fluid cushion. The present disclosure also provides for a ball valve assembly including a floating ball valve with seat carriers  40 ,  42 ,  142  externally loaded by non-compressible fluid. 
     The present disclosure also provides for a ball valve assembly including seat carriers  40 ,  42 ,  142  that deflect to relieve cavity pressure. The present disclosure also provides for a ball valve assembly including a lock-out plate  80  used as a coupling. 
     The present disclosure also provides for a ball valve assembly including a lock plate  80  with integral coupling and stops for full open and full closed positions. The present disclosure also provides for a ball valve assembly including a lock plate  80  that allows for valve operation without a handle  90 . The present disclosure also provides for a ball valve assembly including a lock-out plate  80  with windows  83  to indicate open, closed, or intermediate positions. 
     The present disclosure also provides for a ball valve assembly including differentiated snap fits between the handle  90  and lock plate  80  and between the lock plate  80  and stem  20  to ensure that the lock plate  80  stays on the valve when the handle  90  is removed. The present disclosure also provides for a ball valve assembly including a valve with a single floating seat ring  40  or  42 ,  142 . The present disclosure also provides for a ball valve assembly including a self-centering ball  16 , seat  30 ,  32 , and seat carrier  40 ,  42 ,  142  design. 
     The present disclosure also provides for a ball valve assembly including the floating seat ring  40 ,  42 ,  142  that allows the upstream seat to move downstream with the ball  16  at shutoff so that the seat remains in contact with ball  16 . The present disclosure also provides for a ball valve assembly including a seat carrier  40 ,  42 ,  142  and seat  30 ,  32  manufactured as one piece. 
     The present disclosure also provides for a ball valve assembly including seat carriers  40 ,  42 ,  142  that result in lower operating torque as once the ball  16  of the assembly is opened, the ball  16  is not fighting with mechanically loaded seats  30 ,  32  due to a reduced pre-load requirement. 
     Although the assemblies, systems and methods of the present disclosure have been described with reference to exemplary embodiments thereof, the present disclosure is not limited to such exemplary embodiments and/or implementations. Rather, the systems, assemblies and methods of the present disclosure are susceptible to many implementations and applications, as will be readily apparent to persons skilled in the art from the disclosure hereof. The present disclosure expressly encompasses such modifications, enhancements and/or variations of the disclosed embodiments. Since many changes could be made in the above construction and many widely different embodiments of this disclosure could be made without departing from the scope thereof, it is intended that all matter contained in the drawings and specification shall be interpreted as illustrative and not in a limiting sense. Additional modifications, changes, and substitutions are intended in the foregoing disclosure.