Patent Publication Number: US-7708089-B2

Title: Breech lock stripper rubber pot mounting structure and well drilling equipment comprising same

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     This patent application is a Continuation-In-Part Application to co-pending U.S. Non-Provisional Utility patent application having Ser. No. 12/069,095, filed Feb. 7, 2008, entitled “Bearing Assembly Retaining Apparatus And Well Drilling Equipment Comprising Same”, and having a common applicant herewith. 
    
    
     FIELD OF THE DISCLOSURE 
     The disclosures made herein relate generally to equipment, systems and apparatuses relating to drilling of wells and, more particularly, to rotating control heads, rotating blowout preventors; and the like. 
     BACKGROUND 
     Oil, gas, water, geothermal wells and the like are typically drilled with a drill bit connected to a hollow drill string which is inserted into a well casing cemented in a well bore. A drilling head is attached to the well casing, wellhead or to associated blowout preventor equipment, for the purposes of sealing the interior of the well bore from the surface and facilitating forced circulation of drilling fluid through the well while drilling or diverting drilling fluids away from the well. Drilling fluids include, but are not limited to, water, steam, drilling muds, air, and other fluids (i.e., liquids, gases, etc). 
     In the forward circulation drilling technique, drilling fluid is pumped downwardly through the bore of the hollow drill string, out the bottom of the hollow drill string and then upwardly through the annulus defined by the drill string and the interior of the well casing, or well bore, and subsequently out through a side outlet above the well head. In reverse circulation, a pump impels drilling fluid through a port, down the annulus between the drill string and the well casing, or well bore, and then upwardly through the bore of the hollow drill string and out of the well. 
     Drilling heads typically include a stationary body, often referred to as a bowl, which carries a rotatable spindle, which is commonly referred to as a bearing assembly, rotated by a kelly apparatus or top drive unit. One or more seals or packing elements, often referred to as stripper packers or stripper rubber assemblies, is carried by the spindle to seal the periphery of the kelly or the drive tube or sections of the drill pipe, whichever may be passing through the spindle and the stripper rubber assembly, and thus confine or divert the core pressure in the well to prevent the drilling fluid from escaping between the rotating spindle and the drilling string. 
     As modern wells are drilled ever deeper, or into certain geological formations, very high temperatures and pressures may be encountered at the drilling head. These rigorous drilling conditions pose increased risks to rig personnel from accidental scalding, burns or contamination by steam, hot water and hot, caustic well fluids. There is a danger of serious injury to rig workers when heavy tools are used to connect a stripper rubber assembly to the drilling head. Accordingly, such a connection should be made quickly and achieve a fluid tight seal. 
     Rotation of respective rotating components of a rotating control head, rotating blowout preventor or other type of rotating control device is facilitated through a bearing assembly through which the drill string rotates relative to the stationary bowl or housing in which the bearing assembly is seated. Rotating control heads, rotating blowout preventors and other types of rotating control devices are generally referred to herein as well drilling heads. Typically, a rubber O-ring seal, or similar seal, is disposed between the stripper rubber assembly and the bearing assembly to improve the fluid-tight connection between the stripper rubber assembly and the bearing assembly. Pressure control is achieved by means of one or more stripper rubber assemblies connected to the bearing assembly and compressively engaged around the drill string. At least one stripper rubber assembly rotates with the drill string. A body of a stripper rubber assembly (i.e., a stripper rubber body) typically taper downward and include rubber or other resilient substrate so that the downhole pressure pushes up on the stripper rubber body, pressing the stripper rubber body against the drill string to achieve a fluid-tight seal. Stripper rubber assemblies often further include a metal insert that provide support for bolts or other attachment means and which also provide a support structure to minimize deformation of the rubber cause by down hole pressure forces acting on the stripper rubber body. 
     Stripper rubber assemblies are connected or adapted to equipment of the drilling head to establish and maintain a pressure control seal around the drill string (i.e., a down hole tubular). It will be understood by those skilled in the art that a variety of means are used to attach a stripper rubber assembly to associated drilling head equipment. Such attachment means include bolting from the top, bolting from the bottom, screwing the stripper rubber assembly directly onto the equipment via cooperating threaded portions on the top of the stripper rubber assembly and the bottom of the equipment, clamps and other approaches. 
     It will be understood that, depending on the particular equipment being used at a drilling head; a stripper rubber assembly at one well may be connected to equipment specific to that well while at another well a stripper rubber assembly is connected to different equipment. For example, at one well the stripper rubber assembly may be connected to the bearing assembly while at another well the stripper rubber assembly may be connected to an inner barrel or an accessory of the drilling head. Thus, the stripper rubber assembly is not unnecessarily limited to being connected to a particular component of a rotating control head, rotating blowout preventor or the like. 
     It is common practice to tighten the bolts or screws of the connection with heavy wrenches and sledge hammers. The practice of using heavy tools to tighten a bolt, for example, can result in over-tightening, to the point where the threads or the bolt head become stripped. The results of over-tightening include stripped heads, where the bolt or screw cannot be removed, or stripped threads, where the bolt or screw has no grip and the connection fails. Both results are undesirable. Even worse, vibration and other drilling stresses can cause bolts or screws to work themselves loose and fall out. If one or more falls downhole, the result can be catastrophic. The drill bit can be ruined. The entire drill string may have to tripped out, and substantial portions replaced, including the drill bit. If the well bore has been cased, the casing may be damaged and have to be repaired. 
     Drilling head assemblies periodically need to be disassembled to replace stripper rubber assemblies or other parts, lubricate moving elements and perform other recommended maintenance. In some circumstances, stripped or over tightened bolts or screws make it very difficult if not impossible to disengage the stripper rubber assembly from the drilling head assembly to perform recommended maintenance or parts replacement. 
     One prior art rotating control head configuration that is widely used rotating control heads in the oil field industry is the subject of U.S. Pat. No. 5,662,181 to John R. Williams (i.e., the Williams &#39;181 patent). The Williams &#39;181 patent relates to drilling heads and blowout preventors for oil and gas wells and more particularly, to a rotating blowout preventor mounted on the wellhead or on primary blowout preventors bolted to the wellhead, to pressure-seal the interior of the well casing and permit forced circulation of drilling fluid through the well during drilling operations. The rotating blowout preventor of the Williams &#39;181 patent includes a housing which is designed to receive a blowout preventor bearing assembly and a hydraulic cylinder-operated clamp mechanism for removably securing the bearing assembly in the housing and providing ready access to the components of the bearing assembly and dual stripper rubber assemblies provided in the bearing assembly. A conventional drilling string is inserted or “stabbed” through the blowout preventor bearing assembly, including the two base stripper rubber assemblies rotatably mounted in the blowout preventor bearing assembly, to seal the drilling string. The device is designed such that chilled water and/or antifreeze may be circulated through a top pressure seal packing box in the blowout preventor bearing assembly and lubricant is introduced into the top pressure seal packing box for lubricating top and bottom pressure seals, as well as stacked radial and thrust bearings. 
     Primary features of the rotating blowout preventor of the Williams &#39;181 patent include the circulation of chilled water and/or antifreeze into the top seal packing box and using a hydraulically-operated clamp to secure the blowout preventor bearing assembly in the stationary housing, to both cool the pressure seals and provide access to the spaced rotating stripper rubber assemblies and internal bearing assembly components, respectively. The clamp can be-utilized to facilitate rapid assembly and disassembly of the rotating blowout preventor. Another primary feature is mounting of the dual stripper rubber assemblies in the blowout preventor bearing assembly on the fixed housing to facilitate superior sealing of the stripper rubber assemblies on the kelly or drilling string during drilling or other well operations. Still another important feature is lubrication of the respective seals and bearings and offsetting well pressure on key shaft pressure seals by introducing the lubricant under pressure into the bearing assembly top pressure seal packing box. 
     Objects of a rotating blowout preventor in accordance with the Williams &#39;181 patent include a blowout preventor bearing assembly seated on a housing gasket in a fixed housing, a hydraulically-operated clamp mechanism mounted on the fixed housing and engaging the bearing assembly in mounted configuration, which housing is attached to the well casing, wellhead or primary blowout preventor, a vertical inner barrel rotatably mounted in the bearing assembly and receiving a pair of pressure-sealing stripper rubber assemblies and cooling fluid and lubricating inlet ports communicating with top pressure seals for circulating chilled water and/or antifreeze through the top seals and forcing lubricant into stacked shaft bearings and seals to exert internal pressure on the seals and especially, the lower seals. 
     Specific drawbacks of prior art rotating control head, rotating blowout preventor and/or the like (including a rotating blowout preventor/or rotating control head in accordance with the Williams &#39;181 patent) include, but are not limited to, a.) relying on or using curved clamp segments that at least partially and jointly encircle the housing and bearing assembly; b.) relying on or using clamp segments that are pivotably attached to each other for allowing engagement with and disengagement from the bearing assembly; c.) relying on or using hydraulic clamp(s); d.) relying on or using a mechanical bolt-type connection to back-up a hydraulic clamp for insuring safe operation; e.) poor sealing from environmental contamination at various interface; f.) cumbersome and ineffective stripper rubber assembly attachment; g.) lack or inadequate cooling at key heat sensitive locations of the inner barrel and/or bowl; h.) lack of real-time and/or remotely monitored data acquisition functionality (e.g., via wireless/satellite uploading of data); i.) static (e.g., non-self adjusting) barrel assembly bearing preloading; and j.) cumbersome/ineffective lubrication distribution and cooling. 
     Therefore, a rotating control head, rotating blowout preventor and/or the like that overcomes abovementioned and other known and yet to be discovered drawbacks associated with prior art oil field drilling equipment (e.g., rotating control head, rotating blowout preventor and/or the like) would be advantageous, desirable and useful. 
     SUMMARY OF THE DISCLOSURE 
     Embodiments of the present invention overcome one or more drawback of prior art rotating control head, rotating blowout preventor and/or the like. Examples of such drawbacks include, but are not limited to, a.) relying on or using curved clamp segments that at least partially and jointly encircle the housing and bearing assembly; b.) relying on or using clamp segments that are pivotably attached to each other for allowing engagement with and disengagement from the bearing assembly; c.) relying on or using hydraulic clamp(s); d.) relying on or using a mechanical bolt-type connection to back-up a hydraulic clamp for insuring safe operation; e.) poor sealing from environmental contamination at various interface; f.) cumbersome and ineffective stripper rubber assembly attachment; g.) lack or inadequate cooling at key heat sensitive locations of the inner barrel and/or bowl; h.) lack of real-time and/or remotely monitored data acquisition functionality (e.g., via wireless/satellite uploading of data); i.) static (e.g., non-self adjusting) barrel assembly bearing preloading; and j.) cumbersome/ineffective lubrication distribution and cooling. In this manner, embodiments of the present invention provide an advantageous, desirable and useful implementation of one or more aspects of a rotating control head, blowout preventor or other type of oil field equipment. 
     In one embodiment of the present invention, an upper stripper rubber canister apparatus for a well drilling head comprises a canister body and a canister body lid. The canister body includes an upper end portion, a lower end portion and a central passage extending therebetween. The central passage is configured for having a stripper rubber assembly disposed therein. The upper end portion includes a breech lock structure exposed within the central passage. The canister body lid includes an upper end portion, a lower end portion, a central passage extending between the end portions thereof, and a stripper rubber assembly mounting structure configured for allowing a stripper rubber assembly to be attached thereto. The lower end portion is configured for fitting within the central passage of the canister body at the upper end portion of the canister body. The canister body lid includes a breech lock structure integral with an exterior surface of the canister body lid adjacent the lower end portion thereof. The canister body lid breech lock structure is configured for allowing the canister body lid to be fixedly engaged with the canister body by inserting the lower end portion of the canister body lid into the canister body central passage at the upper end portion thereof and rotating the canister body lid with respect to the canister body such that at least a portion of the canister body breech lock structure become at least partially overlapped with a respective one of the canister body lid breech lock structure. 
     In another embodiment of the present invention, an upper stripper rubber canister apparatus for a well drilling head comprises a canister body and a canister body lid. The canister body includes an upper end portion, a lower end portion and a central passage extending therebetween. The central passage is configured for having a stripper rubber assembly disposed therein. The upper end portion includes a plurality of spaced apart spline members protruding therefrom within the central passage. The canister body lid includes an upper end portion, a lower end portion, a central passage extending between the end portions thereof, and a stripper rubber assembly mounting structure configured for allowing a stripper rubber assembly to be attached thereto. The lower end portion is configured for fitting within the central passage of the canister body at the upper end portion of the canister body. The canister body lid includes a plurality of spaced apart spline members protruding from an exterior surface of the canister body lid adjacent the lower end portion thereof. The canister body lid spline members are configured for being selectively and matingly engaged between the canister body spline members when the lower end portion of the canister body lid is being inserted within the canister body central passage at the upper end portion thereof and for allowing the canister body lid to be rotated with respect to the canister body after the canister body lid is sufficiently inserted within the canister body central passage at the upper end portion thereof such that at least a portion of the canister body spline members at least partially overlapped with a respective one of the canister body lid spline members to preclude unrestricted longitudinal displacement of the canister body lid with respect to the canister body in a direction opposite a lid insertion direction. 
     In another embodiment of the present invention, a well drilling head comprises a housing, a bearing assembly, a bearing assembly retaining structure, a canister body, a canister body lid and a stripper rubber assembly. The housing has a sidewall structure defining a central bore. The bearing assembly includes an outer barrel having a central bore, an inner barrel at least partially disposed within the central bore of the outer barrel and bearing units coupled between the barrels for providing concentric alignment of the barrels and allowing rotation therebetween. The bearing assembly is at least partially disposed within the central bore of the well drilling head housing. The bearing assembly retaining structure is coupled between the bearing assembly and the housing for releaseably securing the bearing assembly within the central bore of the well drilling head housing. The canister body includes an upper end portion, a lower end portion and a central passage extending therebetween. The central passage is configured for having a stripper rubber assembly disposed therein. The upper end portion includes a breech lock structure exposed within the central passage. The lower end portion of the canister body is fixedly engaged with the inner barrel of the bearing assembly. The canister body lid includes an upper end portion, a lower end portion, and a central passage extending between the end portions thereof. The lower end portion is configured for fitting within the central passage of the canister body at the upper end portion of the canister body. The canister body lid includes a breech lock structure integral with an exterior surface of the canister body lid adjacent the lower end portion thereof. The canister body lid breech lock structure is configured for allowing the canister body lid to be fixedly engaged with the canister body by inserting the lower end portion of the canister body lid into the canister body central passage at the upper end portion thereof and rotating the canister body lid with respect to the canister body such that at least a portion of the canister body breech lock structure become at least partially overlapped with a respective one of the canister body lid breech lock structure. The stripper rubber assembly is fixedly attached to the lower end portion of the canister body lid. 
     These and other objects, embodiments, advantages and/or distinctions of the present invention will become readily apparent upon further review of the following specification, associated drawings and appended claims. Furthermore, it should be understood that the inventive aspects of the present invention can be applied to rotating control heads, rotating blowout preventors and the like. Thus, in relation to describing configuration and implementation of specific aspects of the present invention, the terms rotating control head and rotating blowout preventors can be used interchangeable as both are oil well drilling equipment that provides functionality that will benefit from the present invention. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a perspective view of a rotating control head in accordance with a first embodiment of the present invention, wherein the rotating control head includes a ram-style bearing assembly retaining apparatus in accordance with the present invention. 
         FIG. 2  is a cross-sectional view taken along the line  2 - 2  in  FIG. 1 , showing the ram-style bearing assembly retaining apparatus engaged with the bearing assembly. 
         FIG. 3  is a cross-sectional view taken along the line  3 - 3  in  FIG. 1 , showing the ram-style bearing assembly retaining apparatus disengaged and the bearing assembly in a removed position with respect to a bowl of the rotating control head. 
         FIG. 4  is a perspective view of a rotating control head in accordance with a second embodiment of the present invention, wherein the rotating control head includes a ram-style bearing assembly retaining apparatus in accordance with the present invention. 
         FIG. 5  is a cross-sectional view taken along the line  5 - 5  in  FIG. 4 , showing the ram-style bearing assembly retaining apparatus engaged with the bearing assembly. 
         FIG. 6  is a perspective view of a bearing assembly of the rotating control head of  FIG. 5 . 
         FIG. 7  is a cross-sectional view taken along the line  7 - 7  in  FIG. 6 , showing a seal lubrication arrangement of the bearing assembly. 
         FIG. 8  is a cross-sectional view taken along the line  8 - 8  in  FIG. 6 , showing a bearing lubrication arrangement of the bearing assembly. 
         FIG. 9  is a detail view taken from  FIG. 8  showing specific aspects of a spring-loaded seal unit in relation to a cover plate and a top drive. 
         FIG. 10  is a partially exploded view showing the spring-loaded seal detached from the top drive. 
         FIG. 11  is a flow chart view showing a rotating control head system in accordance with an embodiment of the present invention, which includes a forced-flow seal lubrication apparatus and a forced-flow bearing lubrication apparatus. 
         FIG. 12  is a perspective view of a rotating control head in accordance with a third embodiment of the present invention, wherein the rotating control head is a high pressure rotating control head with a ram style bearing assembly retaining apparatus. 
         FIG. 13  is a cross-sectional view taken along the line  13 - 13  in  FIG. 12 . 
         FIG. 14  is a perspective view showing an embodiment of an upper stripper rubber apparatus using a bayonet style interconnection between the canister body thereof and canister body lid thereof. 
         FIG. 15  is a cross-sectional view taken along the line  15 - 15  in  FIG. 14 . 
         FIG. 16  is an exploded perspective view of the upper stripper rubber apparatus shown in  FIG. 14 . 
         FIG. 17  is a diagrammatic view of a data acquisition apparatus in accordance with an embodiment of the present invention. 
         FIG. 18  is a perspective view showing a kelly driver in accordance with an embodiment of the present invention. 
         FIG. 19  is a perspective view showing an embodiment of an upper stripper rubber apparatus using a breech lock style interconnection between the canister body thereof and canister body lid thereof. 
         FIG. 20  is a cross-sectional view taken along the line  20 - 20  in  FIG. 19 . 
         FIG. 21  is an exploded perspective view of the upper stripper rubber apparatus shown in  FIG. 19 . 
     
    
    
     DETAILED DESCRIPTION OF THE DRAWING FIGURES 
       FIGS. 1-3  show various aspects of a rotating control head  1  in accordance with a first embodiment of the present invention. The rotating control head  1  is commonly referred to as a low pressure rotating control head. As illustrated in  FIGS. 1-3 , it can be seen that an underlying distinction between a ram-style retaining apparatus in accordance with the present invention and prior art bearing assembly retaining apparatuses is that the ram-style retaining apparatus utilizes a plurality of angularly spaced apart ram assemblies  10  to retain a bearing assembly  12  in a fixed position with respect to an equipment housing. 14  (i.e., commonly referred to in the art as a bowl). An inner barrel  15  of the bearing assembly  12  is configured for having a stripper rubber assembly attached to an end portion thereof. As shown, two ram assemblies angularly spaced by approximately 180-degrees are provided for retain the bearing assembly  12  in the fixed position with respect to the equipment housing  14 . However, a ram-style retaining apparatus in accordance with the present invention is not limited to two ram assemblies. Clearly, a ram-style retaining apparatus in accordance with the present invention having more than two ram assemblies or, conceivably, only one ram assembly can be implemented. 
     Each ram assembly  10  is fixedly mounted on a respective receiver  16  of the equipment housing  14  and, as shown in  FIGS. 2 and 3 , includes a ram  18  slideably disposed within a bore  20  of the respective receiver  16 . Each ram assembly  10  includes a selective displacement means  22  coupled between a mounting plate  23  of the ram assembly  10  and the ram  18 . The mounting plate  23  is fixedly attached to the respective receiver  16 . Operation of the selective displacement means  22  allows a position of the ram  18  within the bore  20  to be selectively varied. In this manner, the selective displacement means  22  allows the ram  18  to be selectively moved between an engagement position E ( FIG. 2 ) and a disengagement position D ( FIG. 3 ). 
     As illustrated, each selective displacement means  22  includes a hand-operated crank  24 , drive axle  26  and interlock member  28 . The drive axle  26  is rotatable mounted on the respective mounting plate  23  in a manner that effectively precludes longitudinal displacement of the drive axle  26  with respect to the mounting plate  23 . The hand-operated crank  24  is fixedly attached to a first end  26   a  of the drive axle  26  such that rotation of the crank  24  causes rotation of the drive axle  26 . A second end  26   b  of the drive axle  26  is in threaded engagement with the interlock member  28 . The interlock member  28  is retained within a central bore  30  of the ram  18  in a manner that limits, if not precludes, its rotation and translation with respect to the ram  18 . Accordingly, rotation of the drive axle  26  causes a corresponding translation of the ram  18 , thereby allowing selective translation of the ram  18  between the engagement position E and a disengagement position D. 
     Referring to  FIG. 3 , the equipment housing  14  includes a central bore  32  that is configured for receiving the bearing assembly  12 . An outer barrel  33  of the bearing assembly  12  includes a circumferential recess  34  that defines an angled ram engagement face  36 . Each ram  18  includes an angled barrel engagement face  38 . An inside face  40  of the equipment housing central bore  32  and an outer face  42  of the outer barrel  33  are respectively tapered (e.g., a 2-degree taper) for providing a tapered interface between the outer barrel  33  and the equipment housing  14  when the bearing assembly  12  is seated in the equipment housing central bore  32 . A plurality of seal-receiving grooves  44  are provided in the outer face  42  of the outer barrel  33  for allowing seals (e.g., O-ring seals) to provide a respective fluid-resistant seal between the outer barrel  33  and the equipment housing  14 . In one embodiment, the tapered inside face  40  of the equipment housing central bore  32  is carried by a replaceable wear sleeve. The replaceable wear sleeve can be removed and replaces as needed for addressing wear and routine maintenance. 
     In operation, the bearing assembly  12  is lowered into the equipment housing central bore  32  of the equipment housing  14  with the rams  18  in their respective disengaged position D. Through rotation of the respective crank  24  in a first rotational direction, each ram  18  is moved from its disengaged position D to its engaged position E. In its engaged position E, the angled barrel engagement face  38  of each ram  18  is engaged with the angled ram engagement face  36  of the outer barrel  33 . Through such engagement of the angled barrel engagement face  38  of each ram  18  with the angled ram engagement face  36  of the outer barrel  33 , the outer face  42  of the outer barrel  33  is biased against the inside face  40  of the equipment housing central bore  32 . Rotation of the cranks  24  in a second rotational direction causes the rams  18  to move from their respective engaged position E to their respective disengaged position D, thereby allows the bearing assembly  12  to be removed from within the equipment housing central bore  32 . 
     Various aspects of the ram-style retaining apparatus illustrated in  FIGS. 1-3  can be altered without departing from the underlying intent and functionality of a ram-style retaining apparatus in accordance with the present invention. One example of such alteration is for the hand-operated crank  24  can be replaced with an electric, pneumatic or hydraulic motor arrangement for allowing motor-driven rotation of the drive axle  26 . Another example of such alteration is for the hand-operated crank  24  to be replaced with a non-manual device. One example of such alteration is for the hand-operated crank  24 , drive axle  26  and interlock member  28  to be replaced with a linear motion arrangement such as a hydraulic or pneumatic ram apparatus. Still another example of such alteration is for a discrete locking arrangement to be provided for securing a respective ram  18  in its engaged position to limit the potential for unintentional movement of the ram  18  toward its disengaged position. Yet another example of such alteration is for the angled ram engagement face  36  and the angled barrel engagement face  38  to be replaced with non-tapered faces (e.g., curved faces) that provide the same biasing functionality when such faces are brought into engagement with each other. And still a further example of such alteration in the optional inclusion of a means such as, for example, a pilot actuated valve circuit that prevents movement of the rams  18  from the engaged position toward the disengaged position (e.g., by preventing release and/or application of pressure to a ram cylinder or pump). 
     As can be seen, a ram-style retaining apparatus in accordance with an embodiment of the present invention offers a number of advantages over clamp-style retaining apparatuses for retaining a bearing assembly within a housing of oil field equipment. Examples of such advantages include, but are not limited to, the apparatus offering ease of engagement and disengagement, the apparatus being self-supported on the housing of the oil field equipment, and the apparatus positively biasing the bearing assembly into a seated position with respect to the housing and/or mating seal(s). 
       FIGS. 4-12  show various aspects of a rotating control head  100  in accordance with a second embodiment of the present invention. The configuration and operability of the rotating control head  100  is generally the same as the configuration and operability of the rotating control head  1  shown in  FIGS. 1-3 . Accordingly, the reader is directed to the disclosures relating to refer to  FIGS. 1-3  for details relating to the configuration and operability of the rotating control head  100 . 
     The rotating control head  100  is commonly referred to as a low pressure rotating control head. As shown, the rotating control head  100  includes a plurality of angularly spaced apart ram assemblies  110  to retain a bearing assembly  112  in a fixed position with respect to an equipment housing  114  (i.e., commonly referred to in the art as a bowl) that are substantially the same as that illustrated in  FIGS. 1-3 . The bearing assembly  112  is removably mounted within a bore  115  of the equipment housing  114 . 
     As shown in  FIG. 4 , a pressure gauge  116  can be mounted on equipment housing  114  in a manner for allowing well pressure to be monitored. It is disclosed herein that the pressure gauge  116  can be an electronic gauge having a transducer with an output interface for allowing remote electronic monitoring, recording, and/or analysis of the well pressure. 
     As Referring now to  FIGS. 4-8 , a first lubricant distribution manifold  120  and a second lubricant distribution manifold  122  can be mounted on a cover plate  124  of the bearing assembly  112 . The lubricant distribution manifolds  120 ,  122  are engaged with a top portion of an outer barrel  126  of the bearing assembly  112 . The first lubricant distribution manifold  120  is angularly spaced apart from the second lubricant distribution manifold  122  (e.g., by 180-degrees). The first lubricant distribution manifold  120  includes a first seal lubricant coupler  120   a,  a first seal lubricant passage  120   b,  a first bearing lubricant coupler  120   c  and a first bearing lubricant passage  120   d.  The second lubricant distribution manifold  122  includes a second seal lubricant coupler  122   a,  a second seal lubricant passage  122   b,  a second bearing lubricant coupler  122   c  and a second bearing lubricant passage  122   d.  The first seal lubricant coupler  120   a  is communicative with the first seal lubricant passage  120   b  for allowing the flow of seal lubricant therebetween and the first bearing lubricant coupler  120   c  is communicative with the first bearing lubricant passage  120   d  for allowing flow of bearing lubricant therebetween. The second seal lubricant coupler  122   a  is communicative with the second seal lubricant passage  122   b  for allowing the flow of seal lubricant therebetween and the second bearing lubricant coupler  122   c  is communicative with the second bearing lubricant passage  122   d  for allowing flow of bearing lubricant therebetween. Preferably, but not necessarily, the lubricant couplers  120   a,    122   a,    120   c  and  122   c  are quick disconnecting type couplers, the seal lubricant couplers  120   a,    120   c  are a first configuration (e.g., size) and the bearing lubricant couplers  122   a,    122   c  are a second configuration different than the first configuration. 
     As shown in  FIG. 7 , the first seal lubricant passage  120   b  of the first lubricant distribution manifold  120  is communicative with a first seal lubricant channel  128  within the outer barrel  126  and the second seal lubricant passage  122   b  of the second lubricant distribution manifold  122  is communicative with a first seal lubricant channel  130  within the outer barrel  126 . Similarly, as shown in  FIG. 8 , the first bearing lubricant passage  120   d  of the first lubricant distribution manifold  120  is communicative with a first bearing lubricant channel  132  within the outer barrel  126  and the second bearing lubricant passage  122   d  of the second lubricant distribution manifold  122  is communicative with a second bearing lubricant channel  134  within the outer barrel  126 . 
     The first seal lubricant channel  128  and the first bearing lubricant channel  132  extend from an upper end portion  136  of the outer barrel  126  to a lower end portion  138  of the outer barrel  126  through a key portion  140  of the outer barrel  126  ( FIG. 6 ). The key portion  140  is a raised body that intersects a circumferential ram receiving recess  133  of the outer barrel  126 . Through contact with a ram of a ram assembly, the key portion  140  provides for anti-rotation of the outer barrel  126  when mounted within the equipment housing  114  in addition to lubricant flow being routed therethrough. 
     Lubricant provided to the first seal lubricant channel  128  via the first lubricant manifold  120  serves to lubricate one or more lower seals  142  of the bearing assembly  112  and lubricant provided to the second seal lubricant channel  132  via the second lubricant manifold  122  serves to lubricate one or more upper seals  144  of the bearing assembly  112 . The seals  142 ,  144  reside within respective seal pockets  143 ,  147  and seal directly against a mating and unitary seal surface within an outer face  137  of an inner barrel  148  of the bearing assembly  112 , which is in contrast to the prior art approach of the seals engaging replaceable wear sleeves attached to the inner barrel  148 . Direct contact of the seal with the inner barrel  148  enhances sealing and heat transfer. Advantageously, the seals  142 ,  144  can be vertically adjustable for allowing a seal interface between the inner barrel  148  and the seals  142 ,  144  outer barrel  126  top be adjusted to account for wear on inner barrel seal surface. To ensure adequate delivery of lubricant, vertically spaced apart oil delivery ports  151  can be exposed within the seal pockets  143 ,  147  and/or spacers  153  with radially-extending fluid communicating passages can be provided within the apart by spacers can be provided within the seal pockets  143 ,  147  (e.g., between adjacent seals). The inner barrel  148  of the bearing assembly  112  is configured for having a stripper rubber  149  assembly attached to an end portion thereof. 
     Lubricant provided to the first bearing lubricant channel  132  via the first lubricant manifold  120  serves to lubricate a plurality of bearing units  146  rotatably disposed between the inner barrel  148  of the bearing assembly  112  and the outer barrel  126 . The bearing units  146  provide for rotation of the inner barrel  148  relative to the outer barrel  126 . Due to the first bearing lubricant channel  132  extending to the bottom portion of the outer barrel  126 , lubricant is first provided to bearing units  146  closest to the lower end portion  138  of the outer barrel  126  and lastly to the bearing units  146  closest to the upper end portion  136  of the outer barrel  126 . In this manner, the bearing units  146  exposed to a greater amount of heat from the well (i.e., the lower bearing units) are first to receive lubricant from a lubricant supply, thereby aiding in extraction of heat from such bearing units. The second bearing lubricant coupler  122   c  and the second bearing lubricant passage  122   d  serve to allow bearing lubricant to be circulated back to the lubricant supply (e.g., for cooling and/or filtration). Thus, a bearing lubricant circuit extends through the first lubricant distribution manifold  120 , through the first bearing lubricant channel  130 , through the bearing units  146  via a space between the inner barrel  148  and outer barrels  126 , through the second bearing lubricant channel  134 , and through the second lubricant distribution manifold  122 . 
     Referring to  FIGS. 5-8 , various advantageous, desirable and useful aspects of the bearing assembly  112  are shown. As shown in  FIGS. 5 and 6 , seals  150  (e.g., O-ring seals) are provided within seal grooves  152  of the outer barrel  126  for providing a sealing interface between mating portions of the outer barrel  126  and the equipment housing  114 . As shown in  FIG. 5 , cooling ribs  154  are provided on an interior face  156  of the inner barrel  148 . Preferably, but not necessarily, groups of the cooling ribs  154  are in-line with respective bearing and seal interfaces at an exterior face  158  of the inner barrel  148 , thereby enhancing cooling at such interfaces. As shown in  FIGS. 5 ,  7  and  8 , a washer-type spring  160  (e.g., a Bellville spring) is engaged between the vertically spaced apart bearings  146  for actively maintaining preloading of such bearings. As best shown in  FIGS. 5-8 , an exterior face  162  of the outer barrel  126  is tapered (e.g., a 2-4 degree draft). The tapered exterior face  162  engages a mating tapered face  164  ( FIG. 5 ) of the equipment housing  114 , thereby providing a self-alignment and tight interface fit between the outer barrel  126  and the equipment housing  114 . 
     Referring now to  FIGS. 6 ,  8 ,  9 , and  10 , bearing assembly  112  includes a spring-loaded seal unit  166  disposed between a cover plate  168  and a top drive  169 . The cover plate  168  is fixedly attached to the outer barrel  126  and the top drive  169  is fixedly attached to the inner barrel  148 . In one embodiment, as shown, the spring-loaded seal unit  166  is mounted within a circumferential channel  167  (i.e., a groove) of the top drive  169  and is fixedly attached of the top drive  169  with a plurality of threaded fasteners  170 . As best shown in  FIG. 9 , the spring-loaded seal unit  166  includes a seal body  171  having a sealing lip  172  that engages a seal interface surface  174  of the cover plate  168 . As shown, the seal interface surface  174  is a surface of a hardened seal body that is an integral component of the cover plate  168 . Alternatively, the seal interface surface  174  can be a non-hardened surface of the cover plate  168  or a surface of a hardened insert within the cover plate  168 . Preferably, but not necessarily, the top drive  169  includes a seal shroud  177  that serves to protect the sealing lip  172 . 
     As best shown in  FIG. 9 , an inner sealing member  176  (e.g., an O-ring) is engaged between an inner face  178  of the spring-loaded seal unit  166  and the top drive  169 . An outer sealing member  180  (e.g., an O-ring) is engaged between an outer face  182  of the spring-loaded seal unit  166  and the top drive  169 . In this manner, a fluid-resistant seal and/or contaminant-resistant seal is provided between the spring-loaded seal unit  166  and the cover plate  168  as well as between the spring-loaded seal unit  166  and the top drive  169 . 
     As best shown in  FIGS. 9 and 10 , the seal body  171  is mounted on the top drive  169  through a plurality of compression springs  184 . Each one of the springs  184  has one of the threaded fasteners  170  extending therethrough. In this manner, the top drive  169  is one example of a seal carrying structure. It is disclosed herein that the a spring-loaded seal unit  166  can be carried by any number of different types and configurations of well drilling head components that suitably serve as a seal carrying structure. An ancillary structural component that is in combination with the top dive, inner barrel or the like is another example of a seal carrying structure. 
     In operation, the springs  184  exert a preload force on the seal body  171  when the sealing lip  172  of the seal body  171  is brought into contact with the cover plate  168 . In one embodiment, the seal body  171  is made from a material whereby the entire seal body  171  offers limited resilient (i.e., flexibility) such that sealing is provided via the seal body floating on the springs  184  as opposed to the sealing lip  172  deflecting under force associated with the preload force exerted by the springs  184 . Accordingly, a stiffness characteristic of the seal body  171  is such that application of force on the sealing lip  72  results in negligible deformation of the sealing lip and displacement of the entire seal body  171  with respect to the channel  167 . 
     As shown in  FIGS. 6-8 , it is disclosed herein that an inner barrel in accordance with the present invention may include one or more ancillary discrete components engaged with an outer barrel body. Examples of such ancillary discrete components include, but are not limited to, cover plates (e.g., cover plate  168 ), spacers (e.g., spacer  173 ) and the like. 
       FIG. 11  is a flow chart view that shows a rotating control head system  200  in accordance with an embodiment of the present invention. The rotating control head system  200  includes rotating control head  205  with integrated forced-flow seal lubrication apparatus  210  and integrated forced-flow bearing lubrication apparatus  215 . The forced-flow seal lubrication apparatus  210  facilitates delivery of seal lubricant to various seals of a bearing assembly  220  of the rotating control head  205 . The forced-flow bearing lubrication apparatus  215  facilitates circulation of bearing lubricant through various bearings of the bearing assembly  220  of the rotating control head  205  and cooling of the circulated bearing lubricant. 
     The forced-flow seal lubrication apparatus  210  includes a seal lubricant pump  212 , a seal lubricant reservoir  213 , and seal lubrication components  214 . The seal lubricant pump  212  extracts lubricant from the seal lubricant reservoir  213 , and provides such extracted lubricant to one or more seals of the bearing assembly  220  through the seal lubrication components  214 . In one embodiment, the rotating control head  205  is embodied by the rotating control head  100  shown in  FIG. 4 . In such an embodiment, the seal lubrication components  214  are comprised by various components of the rotating control head  100 , which include the first seal lubricant coupler  120   a , the second seal lubricant coupler  122   a , the first seal lubricant passage  120   b , the second seal lubricant passage  122   b , the first seal lubricant channel  128  and the second seal lubricant channel  130 . Accordingly, in such an embodiment, seal lubricant is routed to the respective seals through the respective seal lubricant coupler ( 120   a ,  122   a ), through the respective seal lubricant passage ( 120   b ,  122   b ), and to one or more seals through the respective seal lubricant channel ( 128 ,  130 ). 
     The forced-flow bearing lubrication apparatus  215  includes a bearing lubricant pump  225 , a lubricant reservoir  226 , bearing lubricant components  230 , a bearing lubricant heat exchanger  235 , a coolant pump  240 , and a coolant radiator  245 . A bearing lubrication flow circuit is defined by bearing lubricant flowing from lubricant reservoir  226  via the bearing lubricant pump  225 , which resides within the lubricant reservoir  226 , through the bearing lubricant components  230 , through a lubricate core portion  227  of the bearing lubricant heat exchanger  235 , and back into the bearing lubricant reservoir  226 . A coolant flow circuit is defined by coolant flowing from the coolant pump  240 , through a coolant core portion  229  of the bearing lubricant heat exchanger  235  to the coolant radiator  245 . The lubricate core and coolant core portions ( 227 ,  229 ) of the bearing lubricant heat exchanger  235  allow for the independent flow of lubricant and coolant and for heat from the coolant to be transferred to the coolant. Accordingly, the bearing lubricant heat exchanger  235  is preferably, but not necessarily, a liquid-to-liquid heat exchanger. The coolant radiator  245  is preferably, but not necessarily, of the liquid-to-air type. 
     The bearing lubricant pump  225  provides bearing lubricant to the bearing lubricant components  230 , with such bearing lubricant being routed back to the lubricant pump  225  through the lubricate core portion  227  of the bearing lubricant heat exchanger  235 . The coolant pump  240  provides coolant to the coolant radiator  245  through the coolant core portion  229 . In one embodiment, the rotating control head  205  is embodied by the rotating control head  100  shown in  FIG. 4 . In such an embodiment, the bearing lubrication components  230  are comprised by various components of the rotating control head  100 , which include the first bearing lubricant coupler  120   c,  the second bearing lubricant coupler  122   c,  the first bearing lubricant passage  120   d , the second bearing lubricant passage  122   d,  the first bearing lubricant channel  132  and the second bearing lubricant channel  134 . Accordingly, in such an embodiment, bearing lubricant is routed to the respective bearings through the respective bearing lubricant coupler ( 120   c,    122   c ), through the respective bearing lubricant passage ( 120   d,    122   d ), and to one or more bearings through the respective bearing lubricant channel ( 132 ,  134 ). 
     It is disclosed herein that the seal lubricant  212 , the seal lubricant reservoir  213 , the bearing lubricant pump  225 , the coolant pump  240  and the coolant reservoir  245  can be mounted on the equipment body  114  of the rotating control head  100 . In such an embodiment, elongated hoses or pipes extend between the bearing lubricant heat exchanger  235  and the coolant radiator  245 . Alternatively, the coolant pump  240 , lubricant pump  225  and/or the heat exchanger  235  can be remotely located from the rotating control head  100 . 
     Turning now to a brief discussion on high pressure rotating control heads in accordance with embodiments of the present invention, such a high pressure rotating control head  300  is shown in  FIGS. 12 and 13 . The high pressure rotating control head  300  comprises an upper stripper rubber apparatus  302  mounted on the low pressure rotating control head  100  of  FIGS. 4-12  in a manner whereby the upper stripper rubber apparatus  302  is mounted in place of the top drive  169 . A canister body  304  of the upper stripper rubber apparatus  302  carries the spring-loaded seal unit  166 . The spring-loaded seal unit  166  is engaged between the canister body  304  and the cover plate  168  in the same manner is it is between the top drive  169  and cover plate  168  in the low pressure rotating control head  100 . The canister body  304  is attached to the outer barrel  126  in a manner whereby rotation of the canister body  304  with respect to the outer barrel  126  is substantially precluded and whereby vertical displacement during use is substantially precluded. 
     A top driver cover  306  (i.e., also referred to herein as a canister body lid) of the upper stripper rubber apparatus  302  is configured for having a stripper rubber assembly  307  operably and fixedly attached thereto. In this manner, the high pressure rotating control head  300  is configured for having spaced apart stripper rubber assemblies (i.e.,stripper rubber assemblies  145 ,  307 ) attached thereto. A first one of such spaced apart stripper rubber assemblies (i.e., stripper rubber assembly  145 ) is fixedly attached to an end portion of the inner barrel  148  and a second one of such spaced apart stripper rubber assemblies (i.e., stripper rubber assembly  307 ) is fixedly attached to the top driver cover  306 . 
     The top driver cover  306  can be engaged with the canister body  304  through any number of different types of interconnection approaches. Mechanical fasteners such as screws, pins and the like are an example of such possible interconnection approaches. The objective of such interconnection is to secure the top driver cover  306  and canister body  304  to each other in a manner than precludes relative rotation and vertical separation therebetween. 
     A bayonet style interconnection is a preferred embodiment for interconnecting a top driver cover and a canister body.  FIGS. 14-16  show an embodiment of the upper stripper rubber apparatus  350  including a canister body  354 , a canister body lid  356  (i.e., top driver cover) and a kelly driver  357 . The upper stripper rubber apparatus  350  includes a bayonet style interconnection between the canister body lid  356  and the canister body  354 . The upper stripper rubber apparatus  350  shown in  FIGS. 14-16  and the upper stripper rubber apparatus  302  shown in  FIGS. 12 and 13  are interchangeable with respect to a given high pressure rotating control head. 
     Still referring to  FIGS. 14-16 , the canister body lid  356  includes one or more bayonet interconnect structures  358  and the canister body  354  includes one or more mating bayonet style interconnect structures  360 . Each bayonet connector structure  358 ,  360  includes an engagement groove  362  having a closed end portion  364  and an open end portion  366 . An elongated edge portion  368  of the engagement groove  362  is defined by an elongated raised rib member  370  extending at least partially along the engagement groove  362 . A space  372  at least as long as one of the canister body lid bayonet connector structures  358  is provided between adjacent ones of the canister body bayonet connector structures  360  and a space  372  at least as long as one of the canister body bayonet connector structures  360  is provided between adjacent ones of the canister body lid bayonet connector structures  358 . Preferably, but not necessarily, all of the canister body lid bayonet connector structures  358  are substantially the same length and all of the canister body bayonet connector structures  360  are substantially the same length. 
     Accordingly, the engagement groove  362  of each canister body bayonet connector structure  360  and the rib member  370  of each canister body lid bayonet connector structure  358  are jointly configured for allowing the rib member  370  of each canister body lid bayonet connector structure  358  to be slideably received within the engagement groove  362  of a respective one of the canister body bayonet connector structures  360  through relative rotation between the canister body  354  and the canister body lid  356  when the canister body  354  and the canister body lid  356  are in a mated orientation such that the rib member  370  of each canister body lid bayonet connector structure  358  is aligned with the engagement groove  362  of the respective one of the canister body bayonet connector structures  360 . Similarly, the engagement groove  362  of each one of the canister body lid bayonet connector structures  358  and the rib member  370  of each one of the canister body bayonet connector structures  360  are jointly configured for allowing the rib member  370  of each canister body bayonet connector structures  360  to be slideably received within the engagement groove  362  of a respective one of the canister body lid bayonet connector structures  358  through relative rotation between the canister body  354  and the canister body lid  356  when the canister body  354  and the canister body lid  356  are in the mated orientation. 
     The bayonet interconnect structures are engage by vertically lowering the top driver cover  306  into place on the canister body  304  with the rib members  370  and spaces  372  aligned accordingly, and then rotating the top driver cover  306  a fraction of a turn with respect to the canister body  304  for securing the top driver cover  306  to the canister body  304 . Preferably, the direction of locking rotation of the top driver cover  306  with respect to the canister body  304  is the same direction as the kelly rotational direction, thereby ensuring that the top driver cover  306  remains in an interconnected orientation with respect to the canister body  304  during operation of the rotating control head and key driver. Optionally, one or more locking devices can be engaged between the canister body  356  and the canister body lid  356  for maintaining the canister body  354  and the canister body lid  356  in an interlocked configuration. 
     As shown in  FIG. 14 , a means is provided for securing the canister body  354  and the canister body lid  356  in a manner that limits rotational displacement of the canister body  354  with respect to the canister body lid  356 . As shown, a notch  374  is provided in a flange portion  376  of the canister body lid  356  and a threaded hole  378  is provided in a top edge of the canister body  354 . When the canister body lid bayonet connector structures  358  are engaged with the canister body bayonet connector structures  360 , the notch  374  is aligned with the threaded hole  378 . Thus, a threaded fastener (e.g., a shoulder bolt) can be can be threaded into the threaded hole  378  to limit (e.g., entirely preclude) rotational displacement of the canister body  354  with respect to the canister body lid  356  in a manner such that rotational torque applied to the canister body lid  356  is transferred to the canister body  354 . It is disclosed herein that a plurality of notches  374  and corresponding threaded holes  378  can be provides, as needed to carry a given torque loading. 
     A breech lock style interconnection is another preferred embodiment for interconnecting a top driver cover (i.e., canister body lid) and a canister body.  FIGS. 19-21  show an embodiment of an upper stripper rubber apparatus  450 , which uses a breech lock style interconnection for interconnecting canister body and a canister body lid. The upper stripper rubber apparatus  450  includes a canister body  454 , a canister body lid  456  (i.e., top driver cover) and a kelly driver  457 . The canister body lid  456  includes a stripper rubber mounting structure (not specifically shown) configured for allowing a stripper rubber assembly (e.g., the stripper rubber assembly  459  shown in  FIGS. 20 and 21 ) to be attached to a lower end portion of the canister body lid  456 . As will be discussed below in greater detail, the upper stripper rubber apparatus  450  includes a breech lock style interconnection between the canister body lid  456  and the canister body  454 , which facilitates fixedly attach the canister body lid  456  to the canister body  454 . It is disclosed herein that the upper stripper rubber apparatus  450  shown in  FIGS. 19-21  and the upper stripper rubber apparatus  302  shown in  FIGS. 12 and 13  are interchangeable with respect to a given high pressure rotating control head. 
     As best shown in  FIGS. 20 and 21 , the canister body lid  456  includes a plurality of spaced apart spline members  458  (i.e., canister body lid spline members) and the canister body  454  includes a plurality of mating spaced apart spline members  460  (i.e., canister body spline members). The spline members  458 ,  460  are examples of breech lock structures in accordance with the disclosures made herein. The canister body lid spline members  458  are configured for being selectively and matingly engaged between the canister body spline members  460  when a lower end portion  461  of the canister body lid  456  is being inserted within a central passage  463  of the canister body at an upper end portion  465  thereof. The canister body lid spline members  458  are further configured for allowing the canister body lid  456  to be rotated with respect to the canister body  454  after the canister body lid  456  is sufficiently inserted within the canister body central passage  463  at the upper end portion  465  such that at least a portion of the canister body spline members  460  at least partially overlapped with respective ones of the canister body lid spline members  458  to preclude unrestricted longitudinal displacement of the canister body lid  456  with respect to the canister body  454  in a direction opposite a lid insertion direction. In the overlapped position, interference (over-under interference) between the spline members  458 ,  460  precludes such unrestricted longitudinal displacement of the canister body lid  456  with respect to the canister body  454 . 
     Preferably, but not necessarily, all of the spline members  458 , 460  have a common width and are spaced apart by a common amount. In this manner, there is not a mandated orientation (i.e., clocking) of the canister body lid  456  with respect to the canister body  454  when aligning the spine members  458  between spline members  460 . The canister body lid  456  includes a flange  467  adjacent the upper end portion  465  thereof. The flange  467  extends outwardly with respect to an exterior surface  469  of the canister body lid  456  in a manner whereby the flange  467  engages a top edge  471  of the canister body  454  to limit an insertion depth of the canister body lid  456  with respect to the canister body  454  (i.e., the flange  467  abuts the upper edge portion  465  to limit insertion depth). 
     The upper stripper rubber apparatus  450  includes a means for securing the canister body  454  and the canister body lid  456  in a manner that limits rotational displacement of the canister body  454  with respect to the canister body lid  456 . As shown in  FIGS. 19 and 21 , one embodiment of such a means includes a key-receiving recess  472  is exposed at the upper edge portion  465  of the canister body  454  and the canister body lid  456  includes a key-receiving recess  474  extending through the flange  467 . The key-receiving recesses  472 ,  474  are respectively positioned to be aligned when the spline members  458 ,  460  are in the overlapped orientation thereby allowing a key  476  to be positioned within the key receiving recesses  472 ,  474  to preclude unrestricted rotational displacement between the canister body  454  and the canister body lid  456 . The key includes a passage extending therethough for allowing a fastener (e.g., a screw) to be engaged with a mating structure of the canister body  454  (e.g., threaded hole at the base of the key-receiving recess  472 ). 
     It is disclosed herein that a key is one example of a device for defined as a securing the canister body  454  and the canister body lid  456  in a manner that limits rotational displacement of the canister body  454  with respect to the canister body lid  456 . It is further disclosed herein that embodiments of the present invention are not limited to a particular means for securing the canister body  454  and the canister body lid  456  in a manner that limits rotational displacement of the canister body  454  with respect to the canister body lid  456 . For example, the canister body  454  and/or the canister body lid  456  can include an integral (e.g., cast in or unitarily machined) anti-rotation member that carry torque loads exerted between the load canister body  454  and the canister body lid  456 . Thus, one or more removable retention members (e.g., threaded fasteners) can be used to preclude unintentional rotation of the canister body  454  with respect to the canister body lid  456  (i.e., limit relative rotation but not carry loads exerted on the canister body  454  by the canister body lid  456 . 
     One or more seal grooves  477  are provided in the canister body lid  456  for forming a sealed interface between the canister body  454  and the canister body lid  456 . Alternatively or additionally, one or more seal grooves can be provided in the canister body  454 . 
     Turning now to data acquisition, it is disclosed herein that respective portions of a data acquisition apparatus can be integrated into a rotating control head in accordance with an embodiment of the present invention. Such data acquisition is valuable in assessing operation of the rotating control head. More specifically, such a data acquisition apparatus facilitates monitoring, capturing, analysing and/or transmitting of data relating to rotating head operation. Examples of rotating head operation include, but are not limited to, well pressure, time in use, max pressure seen, number of drill string pipes installed, amount of downtime for a given reference time, number of bearing assembly rotations, number of critical conditions experienced, and the like. Acquired data is preferably sent from the data acquisition apparatus to a data management system (e.g., a computer having network access) via a wireless manner. 
     As shown in  FIG. 17 , in one embodiment, a data acquisition apparatus. 400  in accordance with the present invention includes sensor devices  405 , (e.g., transducers, probes, thermal couples, etc), a transmitter  410 , a receiver  415 , and a data acquisition system  420 . The data acquisition apparatus  400  is coupled to a rotating control head (e.g., the rotating control head  100  disclosed herein) through the sensor devices  405 . Operational information of the rotating control head is gathered by the sensor devices  405  and is transmitted to the data acquisition system  420  via the transmitter  410  and the receiver  415 . The transmitter  410  and the receiver  415  can be any type of units suitably configured for transmitting signal over wire, wirelessly, over a computer network, via satellites, etc. The data acquisition system  420  is configured for storing, monitoring and/or analyzing information received from the sensor devices  405 . Thus, such information can be stored, monitored and/or analyzed at a remote location from the rotating control head. 
     Turning now to a discussion of related equipment used with rotating control heads in accordance with the present invention, a kelly driver is oil field equipment that facilitates applying a rotational torque to a segment of drill string pipe.  FIG. 18  shows and embodiment of a kelly driver  500  in accordance with an embodiment of the present invention. The kelly driver  500  includes hinged split bushings  505 , a top ring  510 , and connection pins  515 . The split bushings  505  each include spaced apart hinge members  520 . The spaced apart hinge members  520  are configured for and orientated for being aligned and interlocked with connection pins  512 . In this manner, the hinge members  520  can be readily and rapidly engaged with and removed from the associated drill string pipe. 
     In the preceding detailed description, reference has been made to the accompanying drawings that form a part hereof, and in which are shown by way of illustration specific embodiments in which the present invention may be practiced. These embodiments, and certain variants thereof, have been described in sufficient detail to enable those skilled in the art to practice embodiments of the present invention. It is to be understood that other suitable embodiments may be utilized and that logical, mechanical, chemical and electrical changes may be made without departing from the spirit or scope of such inventive disclosures. To avoid unnecessary detail, the description omits certain information known to those skilled in the art. The preceding detailed description is, therefore, not intended to be limited to the specific forms set forth herein, but on the contrary, it is intended to cover such alternatives, modifications, and equivalents, as can be reasonably included within the spirit and scope of the appended claims.