Abstract:
A ball valve and ball valve actuator including a unique valve stem seal and mounting connection between the ball valve and actuator. The stem seal design reduces leakage issues and significantly lengthens the life span of the ball valve and actuator and the mounting connection between the actuator. The ball valve maintains the centrality of the valve stem in connection with the actuator pinion and minimizes torque and shear forces transferred to the valve stem and hence the stem seal itself.

Description:
FIELD OF THE INVENTION 
     The present invention relates to a ball valve and ball valve actuator and more specifically to a unique valve stem seal and mounting connection between the ball valve and actuator. The stem seal design reduces leakage issues and significantly lengthens the life span of the ball valve and actuator and the mounting connection between the actuator. The ball valve maintains the centrality of the valve stem in connection with the actuator pinion and minimizes torque and shear forces transferred to the valve stem and hence the stem seal itself permitting use of smaller electric actuators then known conventionally to operate the ball valve. 
     BACKGROUND OF THE INVENTION 
     Many industrial processes include liquid, semi-liquid and gas distribution systems which require automation of ball valves in the distribution pipelines of the industrial processes. Examples of such processes are food processing, chemical manufacturing and PET blow molding operations. In such processes very specific quantities of liquid product must be delivered, combined, dispensed and/or regulated in some manner by the automated ball valves so as to produce a desired final product or application. In many instances the ball valves are controlled or actuated for example by pneumatic actuators, which in turn are controlled via a computer system which controls and monitors the industrial process or application. 
     The actuators open, close and in general operate the ball valves to regulate the flow of product in any manner as directed by the computer system. There are many commercially available actuator systems to open and close ball valves including for example pneumatic double acting load cylinders with a rack and spur gear operating the valve stem of an attached ball valve. In such a pneumatic system, air pressure is controlled by a solenoid valve that drives the load cylinder which moves the rack and turns the spur gear which in turn rotates to the stem of the ball valve. This known arrangement allows the valve to be opened or closed in response to directed air pressure pulses. 
     Industry standards exist for the mounting and connection of such actuators to known ball valve designs. These standards ensure that there is some consistency across the industry, however the standards do not optimize the manufacturing and operating characteristics necessary to produce ball valves and actuators with a long lifespan. Even under the industry standards a ball valve and actuator combination may be merely a manual ball valve which has the handle removed and is bolted to the actuator so that the valve stem is fitted into a pinion in the actuator which turns the valve stem and hence the ball in the valve. 
     Ball valves are generally provided with a valve bonnet which houses the valve stem and is usually an integral part of the valve body. The valve bonnet extends perpendicularly upwards relative to the flow passage through the valve, and has a flange which, under the industry standards, is provided with four (4) bolt holes by which the flange is connected to the bottom of the actuator housing. The industry standards require four vertical bolts, one bolt at each corner of the flange on the bonnet which connect into threaded holes in the bottom of the actuator housing. These bolts are generally aligned in parallel with the valve stem and are subject to a significant amount of reaction torque and shear stress that occurs between the actuator and valve from internal seals and packings as well as the additive effects of forces created by fluid dynamics acting on the ball valve. Also, the axial length of the bonnet and the valve stem of the known ball valves defines a substantial distance between the actuator and the ball valve which can accentuate the torque and shear forces and so apply tremendous stress on these bolts over time. 
     Even before failure, any loosening of the standard valve and actuator connection due to such torque and shear forces causes misalignment between the valve stem and the rotation axis of the actuator. At the very least such a loss of centrality, or axial misalignment between the rotation axis of the valve stem and that of the actuator can place significant pressure and force on the valve seal accelerating wear and causing external leaks. In the worst case scenario, the valve stem seals can fail altogether and/or the valve body separates from the actuator. These conventional type of connections between the valve body and the actuator can survive only a certain number of cycles before failure or maintenance which of course affects not only the efficiencies and costs relating to the ball valve and actuator but which shuts down the entire process in which these devices are used. 
     OBJECTS AND SUMMARY OF THE INVENTION 
     The present invention obviates the short comings and disadvantages of the described prior structures and arrangements. In particular, one aspect of the present invention is directed to an improved valve stem seal which significantly increases the ability of the stem seal to resist leakage over its lifetime and the number of cycles applied to the valve by the actuator. 
     Another aspect of the invention provides a secure and integral connection between the ball valve body and the actuator body so that the torque and shear forces applied between the actuator and the ball valve body during operation do not allow for relative motion between the two elements and thereby prevent misalignment of the stem shaft with the actuator pinion that would otherwise compromise the stem seal. 
     It is a still further object of the present invention to provide a cost-efficient bar stock ball valve provided with an integral mounting track for connecting to a mounting pad of the actuator. 
     It is yet another object of the present invention to provide a maintenance free ball valve stem seal that does not use a threaded packing nut that can come loose or fail during the course of the operative lifetime and a high number of cycles of the ball valve. By eliminating the threaded packing nut there is no chance or risk of improper manual adjustment either during assembly, installation or maintenance. 
     It is another still further object of the present invention to significantly reduce the shear and torque forces between the actuator and ball valve body which correspondingly loosen the connection therebetween and compromise the integrity of the connection between the actuator and the ball valve stem and thus the accurate actuation of the ball valve by the actuator. 
     The present invention utilizes a compression spring in combination with an external O-ring to reduce the amount of friction wear as well as to compensate for any wear of the external O-ring resulting from cycling of the ball valve. Also, the present invention includes a precise, dimensionally controlled mounting device for ensuring that the ball valve body is accurately and securely affixed to the actuator body in a manner which reduces the torque and sheer forces between these two elements. The reduction of such detrimental forces ensures that the centrality of the actuator pinion and valve stem is maintained so as to provide a highly accurate actuation of the ball valve via the actuator throughout a significantly increased lifetime of the valve and actuator. 
     The present invention also relates to a ball valve comprising a valve body defining a fluid passageway extending between a fluid inlet and a fluid outlet, two opposing ball seats located within the fluid passageway for rotatably retaining a ball in the valve body and a valve stem connected to the ball and extending through a valve stem bore in the valve wall to rotate the ball between the ball seats, and a valve stem seal comprising, an external O-ring having an inner diameter an outer diameter and an outer surface, a spring for axially compressing the external O-ring; and wherein the spring maintains a preload force on the external O-ring to ensure the inner diameter of the external O-ring remains in contact with the valve stem around its full circumference. 
     The present invention further relates to a method of connecting a ball valve to an actuator comprising the steps of providing a valve body defining a fluid passageway extending between a fluid inlet and a fluid outlet, locating a ball seat within the fluid passageway for rotatably retaining a ball in the valve body and extending a valve stem connected to the ball through a valve stem bore in the valve wall to rotate the ball in the ball seat according to an actuation force provided by an actuator, and forming the valve stem bore extending through a valve bonnet on the valve body and machining an external surface of the valve bonnet as a curved concave surface for receiving a mating connection mechanism of the actuator. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a perspective view of the ball valve  1  body and actuator  3 ; 
         FIG. 2  is a side elevation view of the ball valve  1  and actuator  3  together; 
         FIG. 3A  is a cross-sectional view of the interior of the ball valve and the valve stem and stem seal mechanism attached to the actuator; 
         FIG. 3B  is a cross-sectional side view of the external O-ring; 
         FIG. 4  is a cross-sectional side view of the valve body and stem seal components; 
         FIG. 5  is a perspective view of the valve body, valve bonnet and valve stem as well as the valve stem seal mechanism; 
         FIG. 6  is a perspective view of the mounting pad of the actuator; 
         FIG. 7A  is a partial cross-sectional view of the ball valve and seal mechanism; 
         FIG. 7B  is a cross-sectional view of the ball valve and seal system as connected with the actuator and mounting pad; 
         FIG. 8  is an elevational cross-section of the ball valve and seal system driven by an electric actuator and worm gear; and 
         FIG. 9  transmission from the motor to the valve stem. 
     
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     Initially observing  FIGS. 1-3  the present invention is embodied in a ball valve  1  connected to a ball valve actuator  3 . The ball valve  1  is contained by a valve body  5  having an inlet  7  and an outlet  9  at opposing ends of the valve body  5  which define a passageway  10  therebetween along an axis A. As is well known, during use a fluid passes through the passageway  10  from the inlet  7  to the outlet  9  and the fluid flow is controlled by the orientation of the ball  6  inside the ball valve  1  which moves between an open position and a closed position to control the fluid flow through the passageway  10 . The inner surface of the inlet  7  and outlet  9  is generally provided with a threaded connection in order to connect to the threads on an external surface of a pipe (not shown) connected to the inlet  7  and to the outlet  9  at either side of the valve body  5 . As the general structure and operation of such ball valves  1  and fittings are well known in the art, no further discussion is provided with respect to the same. 
     The ball valve body  5  of the present invention is generally fabricated from bar stock for purposes of cost efficiency, although other methods of fabrication such as cast and molded valve bodies may also be used in this invention. The bar stock body may also have its axis A and hence passageway  10  as defined between the inlet  7  and outlet  9  formed eccentrically relative to the centerline C of the barstock, for example as described in U.S. Pat. No. 7,025,330 to Masse, and as shown in  FIG. 2 . The eccentric machining of the inlet  7  and outlet  9  of the ball valve  1  relative to the centerline C of the bar stock valve body  5  ensures that there is an abundance of material on one side of the bar stock valve body  5  than the other to facilitate the machining requirements for the valve bonnet  13  and the mounting track  15 . The valve bonnet  13  and mounting track  15  are necessary for attaching and securing the valve body  5  and the actuator  3  together as described in detail below. 
     Turning to  FIG. 3A , a cross-sectional view of the interior of the ball valve  1  shows the ball seat  11  supporting the ball  6  which controls the flow of fluid through the ball valve  1 . A valve stem  17  is connected to the ball  6  and extends upwardly perpendicularly relative to the axis A upwards and through the valve bonnet  13  and into a connection with the pinion  19  of the valve actuator  3 . A critical part of the present invention is that both alone, and working together, the valve stem seal  12  arrangement and mounting structure described in greater detail below maintain the valve stem  17  in perfect axial alignment, i.e., centrality, with the pinion  19  and the pinion axis P. The centrality is highly important because any axial misalignment or radial displacement between the pinion  19  and the valve stem  17  increases the torque and shear forces on the valve stem  17  and the valve stem seal  12  which can lead to premature leakage and failure of the ball valve  1  and actuator  3 . 
     The valve stem seal components of the present invention provide improved integrity to the valve stem seal  12  by the use of a lower stem seal  20 , an internal O-ring  31  and an external O-ring  33 . The lower stem seal  20  is made of a durable material such as reinforced Teflon® and is positioned in a step formed on the lower most edge of the inner wall  14  of the valve bonnet  13  so as to form an initial static seal between the valve stem  17  and any fluid in the ball valve  1 . Next, the valve stem  17  is provided at an intermediate location inside the valve bonnet  13  with a circumferential radial groove  32  into which the internal O-ring  31  is fit. The internal O-ring  31  is the main dynamic seal between the inner wall  14  of the valve bonnet  13  and the valve stem  17  for preventing fluid and pressure leakage from within the ball valve  1  up between the valve stem  17  and the inner wall  14  of the bonnet  13  especially in the circumstance where some axial misalignment of the valve stem  17  occurs. Another function of the internal O-ring  31  is to inhibit media-borne contamination from leaking up through the valve stem  17  and valve bonnet  13  and detrimentally affecting the spring compensated external O-ring  33  discussed below. 
     The external O-ring  33  provides both a secondary static and dynamic seal at the uppermost edge of the inner wall  14  of the valve bonnet  13  between the valve bonnet  13  and the valve stem  17 . As a dynamic seal the external O-ring  33  prevents leakage when the valve is actuated, i.e., when the valve stem  17  is being rotated in the bonnet  13 , and also as a static seal to prevent leakage when the valve stem  17  is stationary. An upper groove  34  is circumferentially formed in the topmost edge of the inner wall  14  of the valve bonnet  13  and the external O-ring  33  is fit into the upper groove  34 . The external O-ring  33  is sized so as to have a cross-sectional diameter d and a radial diameter D which can be compressed into the upper groove  34  and elastically seals the entire radial distance between the bonnet and the valve stem  17 . An important feature of this invention, the cross-sectional diameter d of the external O-ring  33  shown in  FIG. 3B  is also great enough to extend the upper most surface portion of the external O-ring  33  above a top surface  16  of the valve bonnet  13  and so provide a desired set off S of an O-ring follower  35  from the top surface  16  of the valve bonnet  13  as explained below. 
     Another important aspect of the present invention, the external O-ring  33  is biasly or spring compensated, i.e., held in position by an axially directed compression spring  37  to make up for extreme cycling and radial wear of this O-ring  33  as the valve stem  17  is turned or actuated over time. As can be appreciated, as the valve stem  17  is cycled over the lifetime of the valve, friction wears the inner most surface portion or inner diameter (“I.D.”), of the external O-ring  33 . As is well known in conventional valves, as the wear occurs on the I.D. of the external O-ring  33  the inner diameter of the external O-ring  33  is increased to a point where the I.D. as defined by the inner most surface portion of the O-ring no longer contacts or abuts the surface of the valve stem  17 . This creates a radial gap between the external O-ring  33  and the valve stem  17  that significantly increases the chances of fluid leaking through this external O-ring seal  33 . This is especially true in the case of highly pressurized fluid systems which maintain a high continuous pressure force on the seals and exploit any weakening of the seals towards failure. The axial bias or spring compensation force exerted on the external O-ring is intended to counteract the increasing I.D. by maintaining a biasing force on the top surface of the external O-ring  33  which compresses the flexible elastic material comprising the external O-ring  33  and maintains contact between the I.D. of the external O-ring and the valve stem  17 . 
     A biasing mechanism such as a compression spring, for example, a Belleville spring  37  is positioned axially adjacent, as shown in  FIG. 4  and axially above, the external O-ring  33  seal to provide a downward axial force on the external O-ring  33 . The biasing mechanism could also be an elastically deformable O-ring, was her(s), coil spring or other compressible biasing mechanism but by way of example the biasing mechanism is exemplified by the Belleville compression spring  37 . The O-ring follower  35  is placed between the spring and the external O-ring  33  so that through the O-ring follower  35  the spring  37  places an axial force around the top exposed circumference of the external O-ring  33  and forces the elastically deformable O-ring to expand radially inwardly, i.e., so that any wear of the I.D. of the external O-ring  33  is compensated for by this radial inward expansion. The force applied by the spring  37  is directed to expand the O-ring  33  radially inwardly because the vertical and horizontal faces of the upper groove  34  confine the O-ring from expanding the outer diameter (O.D.) as the external O-ring  33  radially outward, or axially downwardly respectively. Thus, the Belleville spring  37 , provides a constant axial pressure force on the external O-ring  33  so that as the inner radial surface of the external O-ring  33  wears, the entire inner radial surface I.D. of the O-ring  33  is maintained in contact with the circumferential outer surface of the valve stem  17  and so maintains the valve stem seal  12 . 
     Due to the dimensions of the external O-ring  33  extending above the top surface  16  of the bonnet, the bottom surface of the O-ring follower  35  is spaced the desired set-off S from the top surface  16  of the valve bonnet  13 . As the inner diameter of the external O-ring  33  wears and the Belleville spring  37  maintains a constant axial force or pressure on the O-ring follower  35  and hence the external O-ring  33 , the top most surface of the external O-ring  33  is forced farther axially downward and maintains a decreasing set-off until the O-ring wears to the extent that the bottom surface of the O-ring follower  35  contacts the top surface  16  of the valve bonnet  13 . The desired set-off S is generally based on the size of the valve and the external O-ring  33 . In a large valve with a correspondingly larger external O-ring  33  the set-off S would of course be greater than in a smaller valve. It has been found that a preferred initial set-off of the O-ring follower is approximately 5-30% and more preferably about 10-20% of the diameter d of the O-ring  33 . For example where the diameter of the O-ring is 0.139″, 0.1×0.139=0.0139″ would be an appropriate set-off S. 
     The constant axial force provided by the Belleville spring  37  is important because it maintains the same axial force on the O-ring  33  no matter to what extent the O-ring  33  wears and reduces the set-off S. At least until sometime after the O-ring follower  35  bottoms out on the top surface  16  of the bonnet  13 , no manual intervention such as maintenance or tightening of a packing nut is necessary to maintain the seal. This provides a substantially longer lifetime to the external O-ring  33  and the seal provided thereby with the valve stem  17 . 
     The O-ring follower  35  placed between the biasing mechanism or Belleville spring  37  and the external O-ring  33  also reduces the overall circumferential wear on the diameter d of the external O-ring  33  because the O-ring follower  35  is radially fixed, i.e., cannot rotate, because of a pair of axially downwardly depending legs  30  from the O-ring follower  35  which fit into detents  57  in the valve bonnet  13  which thereby maintains the O-ring follower  35  in a specifically aligned radial position as shown in  FIG. 5 . This directly prevents any axial wear on the external O-ring  33  caused by any circumferential rotational movement of the Belleville spring  37  relative to the external O-ring  33 . 
     Returning to  FIG. 4 , on top of, or axially above the Belleville spring  37  is a spring follower  39  for securing the spring  37  or other biasing mechanism relative to the valve stem  17 . The spring follower  39  is provided with a notch  40  on an innermost edge for partially receiving a retaining ring  41  for securing the follower to the valve stem  17 . Once assembled, the notch  40  in the spring follower  39  also prohibits the retaining ring  41  from being removed or accidentally released from its secured position by confining the outer diameter of the retaining ring  41  and locking it into the retaining ring groove  42  machined into the valve stem. The retaining ring  41  is in turn secured in place inside a retaining groove  42 , or alternatively under a circumferential lip  58 , around the valve stem  17  itself. The retaining ring  41  may be for instance a snap or split ring which has a diameter smaller than the outer diameter of the valve stem  17  or smaller than the circumferential lip  58  and thus snaps into the retaining groove  42  or under the lip  58  on the valve stem  17 . The Belleville spring  37  forces the spring follower  39  axially upwards against the retaining ring  41  in the retaining groove  42  so as to maintain the retaining ring  41  and the spring follower  39  substantially axially immovable relative to the valve stem  17 . 
     The spring follower  39  in turn maintains the Belleville spring  37  in a compressed position between the spring follower  39  and the O-ring follower  35  so that the spring  37  can only expand axially downwardly towards the valve bonnet  13  and so force compression to maintain the I.D. of the external O-ring  33 . With this arrangement, no conventional valve stem packing nut is necessary in order to maintain the stem seal components in relative connection on the valve stem  17 . The valve stem seal  12  maintains its integrity without any adjustment or maintenance or any pre-load of the seal mechanism, the pre-load is in general fixed and dependent upon the retaining ring  41  and the size, type and spring constant of the spring  37  or other biasing mechanism utilized in the device. This structure further eliminates any danger of over, or under-tightening such as known with a packing nut which can result in premature stem seal leaks. 
     In another embodiment of the present invention disclosed in  FIGS. 5-8 , a unique mounting system for connecting the valve body  5  to the actuator  3  is shown and described. Observing  FIG. 5 , the valve body  5  as described above is generally machined from bar stock and is formed having the mounting track  15  consisting of two parallel tracks  15  machined across a top side  51  of the valve body  5  parallel to the axis A. These tracks  15  are essentially channels and form an area of low relief on each side of the valve bonnet  13  and which define therebetween an area of high relief on which the valve bonnet  13  is formed. The tracks  15  on either side of the bonnet  13  are each defined by a floor  45  extending along the length of the valve body  5  and an inner sidewall  47  leading upwards from the floor  45  to the top of the area of high relief  49 . The inner sidewall  47  and floor  45  do not have to extend the length of the valve body  5 , but for purposes of machining may be more economically formed in this manner. 
     The valve bonnet  13  is set, affixed or formed by machining atop the area of high relief  49  and provided with a radial, circumferentially extending bonnet channel  55  around and defining the outermost circumferential surface of the bonnet. The bonnet channel  55  has a curved, concave cross-section extending between a top and a bottom edge of the valve bonnet  13  and, as will be explained in further detail below, the bonnet channel  55  facilitates the secure axial retention of the valve body  5  against the actuator  3 . Interrupting the outermost circumferential surface of the bonnet as well as the bonnet channel  55  are the pair of detents  57  previously described for receiving the legs  30  of the O-ring follower  35 , although only one detent  57  and leg  30  may be necessary, two are discussed for purposes of clarity. As explained previously in regards to the valve stem seal  12 , the detents  57  in the valve bonnet  13  receive the depending legs  30  from the external O-ring  33  follower to keep the external O-ring  33  follower from radially rotating. It is also important to note that these detents  57  are opposingly formed on either side of the valve bonnet  13  and are oriented essentially parallel with the axis P but at an approximately 45 degree angle relative to a plane defined by the axis A and axis P. This 45 degree offset ensures that the detents  57  and depending legs  30  do not interfere with the rest of the mounting structure as described below. 
     As shown in  FIGS. 6-8 , the actuator  3  is provided with a mounting pad  21  for integrally connecting with the top side  51  of the valve body  51  the valve bonnet  13  and hence the opposing tracks  15  formed in the top side  51  of the valve body  5 . Observing  FIG. 6 , the mounting pad  21  includes a plurality of feet  23 , in the case of the present embodiment four (4) feet  23  disposed in a square configuration, although other arrangements are possible, are used to engage the tracks  15  in the valve body  5  although another number of feet  23  could be used as well. The feet  23  which depend from the bottom of the mounting pad  21  define each corner of the square configuration and are spaced apart from one another the same distance as the width of the area of high relief  49  between the opposing tracks  15  on the valve body  5 . In this manner, when the actuator  3  is connected with the valve body  5 , two parallel adjacent feet  23  of the mounting pad  21  fit into and along each of the tracks  15  on the valve body  5  and the inner sidewall  47  of each channel bears directly on the side of the feet  23  and maintains the valve body  5  and the actuator  3  fixed in the desired relative radial positioning. With the four (4) feet  23  defining each corner of the mounting pad  21  as shown in the present embodiment, the valve body  5  may be mounted to the actuator  3  and vice versa in different radial positions, i.e., the radial alignment of the valve body  5  and the actuator  3  can be varied by 90 degrees so that a range of connection arrangements and alignments are possible. 
     With the valve body  5  brought into contact with the mounting pad  21  on the actuator  3  as in  FIG. 7A , the valve seal  12  and valve bonnet  13  enter into a receiving orifice  53  centered between the four feet  23  of the mounting pad  21  and a portion of the valve stem  17  extends upwards above the bonnet  13  and into the actuator  3 . The radial fit between the bonnet  13  and actuator orifice  53  is controlled such that only minimal clearance is allowed providing for precise centrality and axial alignment between the two elements. The tight control of the tolerances of the bonnet  13  and orifice  53  ensures that the valve stem  17  is in precise connection and axial alignment with the pinion  19  located inside of the actuator  3 . The valve stem  17  and pinion  19  are non-rotatably connected together so when necessary they may rotate together about the valve stem  17  axis P to turn the ball  6  of the ball valve  1  to a desired position. Because the mounting pad  21  and feet  23  are engaged in the opposing tracks  15  on the valve body  5  no relative radial rotation of the actuator  3  and the valve body  5  can occur, only the matter of axially affixing and securing the valve body  5  and the actuator  3  remains. 
     The curved, concave cross-section defining the bonnet channel  55  on the outer circumferential surface of the valve bonnet  13  passes into the receiving orifice  53  and the bonnet channel  55  is brought into axial alignment with at least one, and preferably two horizontally extending clamp screws  25  rotatably supported in the mounting pad  21  of the actuator  3 . As seen in  FIG. 7B , each of the clamp screws  25  are provided through the mounting pad  21  in a receiving passage  26  along an axis Z perpendicular to the axial alignment of the valve stem  17  and pinion  19 . The receiving passages  26  accepting the clamp screws  25  are spaced a desired distance on each side of the receiving orifice  53 , however they are spaced so the receiving passages  26  at least partially intersect with, and an outer surface of the clamp screw  25  also intersects with and enters inside the radius of the opening defined by the receiving orifice  53 . Because of this spacing and intersection, a portion of the outer surface of each clamp screw  25  comes into contact with and interferes with the curved, concave surface on the outer surface of the bonnet  13 . 
     By way of further explanation, with the valve bonnet inserted inside the receiving orifice  53  of the mounting pad  21  as the clamp screws  25  are tightened, they extend farther into the receiving orifice  53  and due to the tangential nature of the alignment between the axes Z and the bonnet  13  the clamp screws  25  begin to engage tangentially with the curved, concave surface  55  of the bonnet  13 . As the screws are turned farther into the receiving passages  26  and into greater contact with the bonnet channel  55 , the curved, concave bonnet channel  55  by its very nature aligns and centers itself with the similarly curved outer circumference of the clamp screws  25 . In other words the concave curve defining the bonnet channel  55  mates in a natural corresponding curved fashion with the clamp screw  25  and thereby pulls the valve body  5  into close integral contact with the actuator  3 . The curved concave bonnet channel  55  and clamp screw  25  act as a cam means which when the clamp screws  25  extend tangentially into relative contact with the bonnet channel  55  pulls the bonnet and hence the valve body  5  axially vertically upwards and into even tighter, more direct contact, with the mounting pad  21  of the actuator  3 . Thus, this clamp screw  25  and bonnet channel  55  arrangement ensures a relative and secure axial connection between the valve actuator  3  and the valve body  5 . 
     In this structure and arrangement with the axial relationship between the actuator  3  and valve body  5  secured by the clamping screws  25 , and the radial relationship confined by the mating feet  23  of the mounting pad and mounting track  15 , any relative torque occurring between the actuator  3  and the valve body  5  is absorbed independently of the clamp screws  25  through the feet  23  on the four (4) corners of the mounting pad  21  that straddles the area of high relief  49  on the valve body  5 . Such torque forces are essentially absorbed by the side of the feet  23  within the channel bearing against the respective opposing inner sidewalls of the opposing tracks  15  on the top side  51  of the valve body  5 . The absorption of these torque forces by this integrated structure ensures that the torque forces are not transferred to the pinion  19  and valve stem  17  of the actuator  3  and ball valve  1 . Thus, the centrality, or axial alignment of the pinion  19  and valve stem  17 , as well as the connection therebetween, remains unaffected and secure, eliminating any risk of the valve loosening while in service. 
     In a further embodiment of the present invention seen in  FIGS. 8 and 9  the mounting system as described above facilitates use of the ball valve in conjunction with an electric drive motor for actuating the ball valve  1  instead of a hydraulic or pneumatic drive as previously discussed. The use of an electric motor driven actuator is preferred in certain cases where a pneumatic or hydraulic power source is not available, or where a smaller space requires a valve and actuator smaller than known electric actuators. It is to be appreciated that with the mounting and valve packing arrangement as described above, the torque from conventional valve necessary to actuate these ball valves, i.e., open and close the ball valves is significantly reduced. This torque reduction permits a significant reduction in the necessary size of the electric motor and permits a more compact arrangement of drive components for actuating the ball valve  1 . 
     The electric actuator  60  of this embodiment includes a specific worm drive transmission arrangement which is an important aspect of the present invention resulting from the reduction in torque necessary to actuate the valve as described above. The smaller amount of necessary torque permits use of a smaller electric motor  61  and a more compact drive train arrangement with more space efficient components, i.e., a spur and worm gear to turn the ball valve can be utilized, thereby reducing the overall space and energy requirements for each respective sized ball valve. 
     The electric drive of this embodiment as seen in  FIG. 8  includes the electric motor  61  having an electrical connection  62  for receiving power. In general, the motor  61  drives a reduction ratio transmission as shown. (Although other types of reduction transmissions are certainly possible.) Positional/rotation sensors  63  for indicating the relative position of actuator pinion  19  and hence the open and closed state of the ball valve  1  are located axially above the worm gear  65 . Substantially different from the conventionally known electric actuators, the present actuator uses a 50:1 ratio reduction worm gear reduction ratio transmission including a worm  64  for driving the worm gear  65  which in turn rotates the actuator pinion  19  and the ball  6  of the ball valve  1 . 
     The motor  61  produces an output drive which turns a series of spur gears  67  to drive the worm  64  as seen in  FIG. 9 . The worm  64  thus drives the main worm gear  65  which drives the actuator pinion  19  for rotating the ball valve  1 . The worm  64  may not necessarily be the most efficient power transfer in a reduction ratio transmission, however worm gears have the additional advantage of being relatively compact. The reduction in torque necessary to actuate the ball valve  1  disclosed herein as facilitated by the new mounting connection between the valve and actuator makes it feasible to use the worm  64  with a smaller electric motor  61  then is generally used while still taking advantage of the compact size of the worm  64  to reduce the overall size of the actuator itself. This important aspect of the present invention thus has the goal of fabricating a relatively smaller drive and connection components for the necessary sized ball valve  1  which are not only more efficient in terms of power use, but can be fit into smaller more compact areas, products and processes. 
     Since certain changes may be made in the above described invention, without departing from the spirit and scope of the invention herein involved, it is intended that all of the subject matter of the above description or shown in the accompanying drawings shall be interpreted merely as examples illustrating the inventive concept herein and shall not be construed as limiting the invention.