the present invention is directed to an externally powered core catcher and valve mechanism adapted to cut cores in unconsolidated and loose formations in a manner such that the core , when cut , is stratigraphically undisturbed . the externally powered core catcher and valve assembly is designed to be utilized in conjunction with a conventional core barrel in a fashion described in greater detail below . the valve assembly of the invention is externally actuated and is thus not dependent on any type of co - action with the core . unconsolidated formations of the type targeted by the present invention are usually encountered in marine drilling operations . fig1 illustrates a typical semi - submersible drilling platform 1 from which distends a casing string 4 to a conventional blow - out preventer 6 . in fig1 drill string 8 continues below the blow - out preventer 6 through the seabed 5 to the formation of interest , with the coring apparatus referenced at 10 . fig2 a - 2b illustrate a cross - section of one embodiment of the core catcher and valve assembly 10 of the present invention as it may be connected to the inner barrel of a conventional coring tool ( not shown ). the inner barrel and bearing assembly illustrated in fig2 includes a safety joint pin 17 through which is disposed a bore 16 to allow for fluid flow in a generally conventional fashion . at its lower end , safety joint 17 is threadedly coupled in co - rotatable relation to safety joint box 11 which in turn is threadedly coupled at its lower end to a bit sub 27 . the integrity of the seal between joint 17 and safety joint box 11 is preserved by an o - ring 13 . bit sub 27 is coupled to a conventional coring bit 92 . to maintain a relatively stationary orientation in the wellbore 9 , bit sub 27 may be provided with stabilizers 15 as illustrated in fig2 b . a core catcher is shown at 86 in fig2 b . in the embodiment illustrated in fig2 a - 2b , a bearing assembly 14 is concentrically disposed within and rotationally and longitudinally fixed to box 11 . assembly 14 includes a bearing retainer 21 which is rotatably journalled to bearing assembly 14 by means of conventional ball bearings 23 . ball bearings 23 are disposed within a bearing race 24 defined in corresponding adjacent portions of retainer 21 . thus , bearing retainer 21 is longitudinally fixed with respect to box 11 while being rotatably secured thereto . in actual drilling operations , box 11 and joint pin 17 are actuated by tension applied to the kelly ( not shown ) at the drilling plalform 1 . during such operations , bearing retainer 21 remains stationary , thereby allowing other elements depending therefrom to also remain rotationally stationary with respect to safety joint box 11 . at its lower end , bearing retainer 21 is coupled to a bearing shaft 42 which is situated rotationally independent of safety joint box 11 . at its lower portion , shaft 42 is threadedly coupled to an inner barrel 44 which in turn is threadedly connected to an inner barrel sub 43 . ( see fig2 - 3 ) inner barrel sub 43 is threadedly connected to a mandrel 46 . the relative positions of the shaft 42 , inner barrel 44 , inner barrel sub 43 , and mandrel 46 are illustrated at fig3 a - 4a . shaft 42 is provided with an inner bore 22 which at its lowermost portion threadedly receives a retainer 60 . retainer 60 defines a restricted diameter bore 57 and a valve seat 43 to accommodate a pressure relief valve ball 84 . referring to fig3 a - 3b , an annular piston 47 is slidably disposed about mandrel 46 above a set of disc springs 50 . piston 47 is threadedly coupled to a spring housing tube 51 and the combination is axially moveable between an upper and a lower orientation along mandrel 46 . annular piston 47 is preferably separated from disc springs 50 by a spacer 49 which is used to &# 34 ; tune &# 34 ; the exact and desired preload of disc springs 50 as will be further described herein . disc springs 50 are supported at their lower extent by a split ring 52 and split ring retainer 53 as illustrated . split ring 52 has an outside diameter slightly smaller than the inside diameter of spring housing 51 so as to provide for slidable cooperation there between referring to fig3 - 5 , annular piston 47 is provided with a series of fluid portals 48 which define a series of fluid inlets 45 and a series of fluid outlets 88 . fluid inlets 45 are adapted to receive well fluid discharged around mandrel 46 in the annulus 7 defined between mandrel 46 and bit sub 11 . well fluid flowing through this annulus 7 must now through there inlets 45 since mandrel 46 defines a close tolerance fit within the interior of said bit sub 11 as illustrated in fig2 . annular piston 47 is moveable between an upper and a lower position as influenced by the upward bias of springs 50 and the influence of well fluid pressure which exerts a downward pressure thereon . annular piston 47 is normally biased in an upper or &# 34 ; closed &# 34 ; position as illustrated in fig4 but may be locked in a lower second or &# 34 ; open &# 34 ; position as illustrated in fig3 . springs 50 are circumferentially disposed about mandrel 46 in a stacked array as illustrated . in a preferred embodiment , dire springs area type manufactured by key bellvilles under the tradename &# 34 ; bellville springs &# 34 ;. due to the relatively narrow cross section of springs 50 , the flat load and the setting load of springs 50 will ordinarily differ . in a preferred embodiment , springs 50 create a flat load of 8 , 000 lbs . and a setting load of 7 , 500 lbs . these loads may be slightly varied or &# 34 ; tuned &# 34 ; by the varying longitudinal length of spacer 49 . it is possible to accurately evaluate the setting and release pressure of springs 50 from manufacturing specifications and tolerances . with exception to modification available through spacer 49 , it is economically desirable that each valve assembly be substantially identical in construction . not all well sites , however , are provided with similar well fluid pumping capacities . it may therefore be desirable to include means to vary or modify the amount of pump pressure necessary to overcome the upward bias of springs 50 in order to move piston 47 downwardly to a &# 34 ; release &# 34 ; position as further discussed herein . in a preferred embodiment , inlets 45 are designed to accommodate such flexibility . inlets 45 are preferably provided with a threaded opening 45a as illustrated in 3a and 4a . openings 45a are receivable to one or more threaded plugs 21 as illustrated in fig5 . the insertion of plugs 21 enables the downward movement of piston 47 with a decreased amount of fluid flow than would be the case absent the insertion of such plugs . depending on the pump facilities available at a given well site , it may be desirable to use one or a number of such plugs 21 in order to achieve an optimum release pressure . an actuator sub 96 is circumferentially disposed about mandrel 46 in spaced relation below split ring 52 and is threadedly connected to housing 51 . in such a fashion , actuator sub 96 is similarly movable between an upper and a lower position as will be further described . at its upper extent , actuator sub 98 describes an inner diameter significantly larger than the outer diameter of mandrel 46 . the difference in the diameter of actuator sub 96 and mandrel 46 defines an annulus 93 which accommodates the movement of a lock ring 54 as will be further described below . a series of setting portals 90 are formed at the lowermost portion of annulus 91 in order to allow external access to lock ring 54 . in a preferred embodiment , it has been found desirable to include a minimum of five to six setting portals 90 equally spaced about the circumference of actuator sub 96 . to enable ready access to lock ring 54 , portals 90 are preferably one quarter of an inch or greater in diameter , though this size is dependent on the given application . portals are preferably threaded and receive standard alien screws 90a as illustrated in fig6 a . lock ring 54 is circumferentially disposed about mandrel 46 and is accommodated in a groove or channel designated 34 . the depth of channel 34 is preferably no more than one - half the thickness of lock ring 54 . in such a fashion lock ring 54 when situated in said channel 34 defines a shoulder 55 as illustrated in fig6 a - 6b . shoulder 55 fits into a corresponding groove 61 formed in the interior of actuator sub 96 as illustrated , and when thus fitted serves to prevent the upward movement of actuator sub 96 . in such fashion , lock ring 54 serves to hold or lock actuator sub 96 in a lower or cocked position . lock ring 54 preferably comprises a conventional c - ring formed of a highly resilient steel alloy . lock ring 54 is normally outwardly biased about mandrel 46 as illustrated in fig6 b . in this orientation , shoulder 55 is not held within groove 61 on actuator sub 96 . this orientation will be referred to herein as the &# 34 ; unlocked &# 34 ; position and is shown in fig4 . in this position , actuator sub 96 is situated in an &# 34 ; upper &# 34 ; position . conversely , the &# 34 ; locked &# 34 ; position occurs when lock ring 54 is held in lock channel 34 by the cooperation of shoulder 55 and groove 61 as previously described . the &# 34 ; locked &# 34 ; position is illustrated in fig3 . in the &# 34 ; locked &# 34 ; position , actuator sub 96 is situated in a lower or &# 34 ; open &# 34 ; position . at its lower end , actuator sub 96 defines an inside diameter closely matched to the outside diameter of mandrel 46 . this close tolerance fit serves to effect a metal - to - metal seal between the two members , which seal is enhanced by a conventional o - ring 32 . at its lowermost extent , actuator sub 96 defines a pair of actuator arms 91 which , in a preferred embodiment , are diametrically opposed as illustrated in fig8 . actuator arms 91 are slidably disposed in specially configured slots 88 , formed in mandrel 46 . ( see fig8 .) arms 91 are also provided with a pair of keyways 74 disposed in an orientation generally normal to the axis of the workstring 8 . keyways 74 accommodate two ball keys 76 in a manner which will be described in greater detail below . as illustrated in fig7 and 8 , actuator arms 91 are preferably l - shaped at their lowermost extremity at is lower end , mandrel 46 defines two &# 34 ; windows &# 34 ; which are formed by machining two parallel cuts in mandrel 46 through to bore 3 . the resulting configuration may alternatively be described as a &# 34 ; web &# 34 ; structure or housing . this web structure or housing accommodates a ball closure valve as will be further described below . immediately above and below the web structure , mandrel 48 describes corresponding connection rings 46a and 46b for use in securing upper and lower valve seats , 99a and 99b , respectively . in a preferred embodiment , connection rings define a larger outside diameter than the mandrel body 46 . lower ring 46b also serves as a stop to upward movement by actuator sub 96 . this stop is created by the physical interaction between the l - shaped bottom portion of actuator arm 91 and the larger diameter of lower ring 46b as illustrated in fig7 . with specific reference to fig3 c and 7 - 8 , the ball close valve assembly comprises a modified spheroid or ball 80 having an outside diameter slightly smaller than the outside diameter of rings 46a and 46b , yet larger than seats 99a and 99b . in a preferred embodiment , ball 80 includes a bore 72 disposed therethrough of a diameter the same or substantially the same diameter as the bore 3 formed through mandrel 46 . ball 80 also includes two flattened portions or pivot planes 83 which are formed coplanar to each other and are disposed parallel to the major axis defined through bore 72 . pivot planes 83 are provided with two diametrically opposed pivot sockets 82b as illustrated . in a preferred embodiment , pivot sockets 82b are both centered with respect to pivot planes 83 . pivot sockets 82b define a pivot axis normal to the axis formed through bore 72 and accommodate pivot pins 82 which are disposed through apertures 8a formed in mandrel 46 . ball 80 is thus able to pivot about pivot sockets 82b between an &# 34 ; open &# 34 ; orientation , in which case ball bore 72 aligns with the axis of the workstring 8 , and a &# 34 ; closed &# 34 ; position in which case the axis of bore 72 is rotated to a position normal to the axis of the workstring 8 . the relative position of ball 80 in an &# 34 ; open &# 34 ; and &# 34 ; closed &# 34 ; position may be seen by comparing fig3 b and 4b . pivot planes 83 are provided with retention sockets 76a sufficient to retain ball keys 76 . it is envisioned that keys 76 comprise conventional ball bearings of a size complementary to keyways 74 . keys 76 may be seemed in retention sockets 76a by a suitable fixative , e . g ., epoxy . alternatively , keys 76 may be welded in place . in a preferred embodiment , sockets 76a are of a depth sufficient to allow the protrusion of approximately one - half of each ball key 76 so as to provide for a slidable , contacting interaction between key 76 and keyways 74 . referring to fig3 b and 4b , keys 76 are eccentrically situated on pivot planes 83 such that they are held within keyways 74 when the actuator sub 96 moves between a &# 34 ; locked &# 34 ; and an &# 34 ; unlocked &# 34 ; position . ball 80 is seated with respect to mandrel 46 and actuator sub 96 via an upper and a lower bearing seat , 99a and 99b , respectively . seats 99a and 99b are ring - shaped in configuration and preferably include beveled contract areas 103 so as to accommodate the curvature of ball 80 . seats 99a and 99b are fixed within mandrel 46 via set screws 84 which are threadedly disposed through rings 46a and 46b and are received in corresponding apertures formed in seats 99a and 99b as illustrated in fig8 . in order to reduce frictional wear on ball 80 , seats 99a and 99b are preferably formed of a softer material , e . g ., a brass or bronze alloy . an alternate embodiment of the ball closure mechanism of the present invention may be seen by reference to fig9 - 16 . referring specifically to fig9 - 10 , dowels or pins 76a may be substituted for bore keys 76 to create a more robust pivot mechanism , where one end of pins 76a are receivable in apertures 110 formed in arms 91 . in this embodiment the travel formerly provided by the eccentric shape of keyway 74 is now provided by a crescent shaped track 114 formed on the pivot plane 83 of ball 80 , which track 114 accommodates the free end of pin 76a . also in this embodiment , the outward distortion of arms 91 is further prevented by replacing slots 88 with an aperture 121 formed in mandrel 46 as illustrated . to further prevent distortion and / or radial spreading of arms 91 , a reinforcing ring 97 may affixed about actuation sub 96 . ( see . fig1 ). as in prior embodiments , upper seat 99b is secured with screws 84 as illustrated in fig1 - 11 . the operation of the apparatus of the present invention may be described as follows by reference to the drawings and especially fig3 and 4 . preliminary to running the tool downhole , ball 80 must be moved and locked in an &# 34 ; open &# 34 ; position as previously described . in the &# 34 ; open &# 34 ; orientation , the axis of bore 72 is aligned with the axis of bore 3 so as to allow the upward progression of a core within the tool . in this position , springs 50 are compressed and actuator sub 96 is moved to a lower or cocked position with respect to mandrel 46 . actuator sub 96 is initially moved downwardly with respect to mandrel 46 by use of a hydraulic press ( not shown ) which in one form consists of a cylindrical tube sized to accommodate the tool and apply a sufficient axial force to compress springs 50 . when disc springs 50 have been compressed to a position where the groove 61 of actuator sub 96 is situated below locking ring 54 , ring 54 is deformed into groove 34 by threading allen screws 90a into portals 90 . the threading of screws 90a in this fashion serves to physically compress ring 54 . when ring 54 has been compressed in this manner , actuator sub 96 is allowed to slide upwardly along mandrel 46 until shoulder 55 locks into groove 61 . in such a fashion , ring 54 is maintained in a compressed position and actuator sub 96 is locked in a lower position . when the valve assembly has been &# 34 ; locked &# 34 ;, ball 80 is positioned in an &# 34 ; open &# 34 ; orientation as illustrated in fig3 a and 3b . the relative movement of ball 80 with respect to sub 96 is accomplished by the travel of keys 76 in keyways 74 so as to urge harmonious interaction therebetween . when the tool has been thusly prepared , it is then secured to a conventional coring assembly by threading the mandrel 46 onto the inner barrel 44 via inner barrel sub 43 . the entire assembly is then lowered into the wellbore until contact is made with the bottom of the hole . once contact is made , drilling fluid is pumped through the drill string 8 between the inner barrel and the outer barrel core assembly past the inside diameter of the core bit 92 . the drilling assembly is then rotated and weight is placed on the drill string 8 to penetrate the formation . the rotation of drill bit 92 results in the formation of core sample which feeds up into the inner barrel of the coring assembly . it is possible at the surface to determine when the core barrel is filled by noting the marked decrease in drilling penetration which occurs at this time . when the inner barrel has thus been filled , fluid pressure is increased on the coring assembly . this pressure increase is detectable on the rig floor and is thus available as an indicator , sometimes referred to as a &# 34 ; tattletale ,&# 34 ; that the ball has closed . the amount of this fluid pressure increase is determined by the load created by springs 50 and the use of plugs 21 or the like as previously described . this increase in pressure creates a downward force against annular piston 47 through fluid portals 48 . once a sufficient downward force is established on annular piston 47 , piston 47 is moved downwardly , thus allowing the expansion of lock ring 54 which no longer retained by the superimposition of actuator 96 moves out of channel 34 . when ring 54 has thus expanded to a non - compressed position , fluid flow through portals 48 is decreased or stopped , thus allowing the rapid , upward movement of actuator sub 96 as induced by disc springs 50 . this upward movement quickly pivots ball 80 approximately 90 degrees , thus severing the core and sealing the core inside the bore tube . the tool and core can then be retrieved to the surface . an alternate embodiment of the &# 34 ; tattletale &# 34 ; feature of the invention is illustrated in fig1 and 14 - 16 . this embodiment mat be desirable is some instances where modern gauge packages do not adequately enable an accurate means to detect the actuation of ball valve 80 by a slight pressure increase induced by the closure of ball 80 in the prior embodiment . in this alternate embodiment , when ball 80 is situated in an &# 34 ; open &# 34 ; or cocked position , fluid is compelled to pass through one or more flow restrictions 102 . restrictions 102 form a close tolerance , metal to metal seal with the inner portion of the outer barrel core assembly . the combination serves to significantly narrow the passageway for well fluid pumped downwardly into annulus 107 , and results in a high pressure reading on the rig floor . by reference to fig1 - 11 , this embodiment provides a pressure plug 123 to prevent a pressure lack between annular 107 and bore 3 , which plug 123 defining a small bore 125 to allow for fluid communication therebetween . when , however , piston 47 is moved downwardly as a result of the movement of ball to a &# 34 ; closed &# 34 ; position , as discussed above , restrictions 102 are moved out of contacting relation with the inner portion of bit sub 27 , thereby opening annular fluid passageway 107 . fluid pressure detectable on the rig floor now drops to close to zero , and is therefore more easily detectable by even improperly calibrated equipment . although particular detailed embodiments of the apparatus and method have been described herein , it should be understood that the invention is not restricted to the details of the preferred embodiment . many changes in design , composition , configuration and dimensions are possible without departing from the spirit and scope of the instant invention .