text: the description of implementations below is presented for purposes of illustration . it is not exhaustive and does not limit the claimed invention to the precise forms disclosed . modifications and variations are possible in light of the description below , or may be acquired from practicing the invention . the claims and their equivalents define the scope of the invention . as illustrated in fig1 - 4 , an apparatus 100 for spinning a tubular is provided . the apparatus 100 may include a frame 102 , a center roller assembly 104 , a first adjustable roller assembly 106 , and a second adjustable roller assembly 108 . in particular , fig1 is a perspective view of one example of an implementation of the apparatus 100 in accordance with present invention . as shown , the frame 102 may include a substantially v - shaped construction having a central region 110 , and a first arm 112 and second arm 114 outwardly extending in angular opposition from the central region 110 . each arm 112 , 114 carries a rail system 116 , 118 . the first arm 112 and second arm 114 define a well 120 therebetween . the center roller assembly 104 may be coupled to the central region 110 proximate the well 120 . each adjustable roller assembly 106 , 108 is coupled to a motor carriage 122 , 124 . each motor carriage 122 , 124 is slidably coupled to the rail system 116 , 118 of each arm 112 , 114 , such that the adjustable roller assemblies 106 , 108 may be linearly translated along the rail systems 116 , 118 towards and , alternately , away from the center roller assembly 104 in a fixed angular orientation relative to the center roller assembly 104 , as depicted by arrows 123 . each carriage 122 , 124 is translated along the rail system 116 , 118 by a hydraulic cylinder 126 coupled between the carriage 122 , 124 at one end 128 , and a pin assembly 132 coupled to the frame 102 at an opposite end 130 . each roller assembly 104 , 106 , 108 includes a drive roller 134 , 136 , 138 directly driven by motors 144 , 146 , 148 , respectively . fig2 is a perspective view of the apparatus 100 illustrating how an adjustable roller system 106 is detachably coupled to the frame 102 at the pin assembly 132 ( fig1 ) of each arm 112 , 114 . as shown , each pin assembly 132 includes a coupling pin 202 that is received by a pair of sleeves 204 coupled to a distal end of the motor carriage 122 . the sleeves 204 are configured such that an end 130 of the hydraulic cylinder 126 may be disposed in corresponding alignment between them . as specifically shown , the motor carriage 122 may be coupled to the frame 102 by inserting the coupling pin 202 through a pair of orifices 206 formed at a distal end of the arm 112 . the sleeves 204 and end 130 of the cylinder may be disposed between and positioned in alignment with the orifices 206 such that the coupling pin 202 may pass and extend therethrough . once the coupling pin 202 is installed through the orifices 206 , the pin 202 may be secured to the frame 102 by a dowel pin 208 , for example , that may be inserted into a pin hole 210 located and a bottom end of the pin 202 . in the alternative , the motor carriage 122 , and thus the roller assembly 106 , may be disassembled from the frame 102 by first removing the dowel pin 208 from the coupling pin 202 , and then removing the coupling pin 202 from the orifices 206 . once the coupling pin 202 is removed from the orifices 206 , the motor carriage 122 may be removed from the rail system 116 . in this way , the roller assembly 106 may be disassembled from the frame 102 for maintenance , repair and replacement . further , the rollers assemblies 106 , 108 may be removed from the apparatus 100 without having to disassemble the frame 102 . fig3 is a perspective view illustrating the apparatus 100 engaged with a tubular 302 or pipe . to engage the tubular 302 , the adjustable roller assemblies 106 , 108 are initially translated to an open or extended position ( not shown ). the apparatus 100 is then brought into close proximity to the tubular 302 such that the tubular 302 is positioned in the well 120 , between the roller assemblies 104 , 106 , 108 . the hydraulic cylinders 126 are actuated to bring the adjustable roller assemblies 106 , 108 into contact with the tubular 302 . thereafter , the cylinders 126 continue to linearly extend to pull the apparatus 100 toward the tubular 302 until all three roller assemblies 104 , 106 , 108 are in contact with the tubular 302 , as shown in fig3 . fig4 is a top view of the apparatus 100 engaged with the tubular 302 . as shown , the adjustable roller assemblies 106 , 108 may be translated linearly towards and , alternatively , away from the center roller assembly 104 to accommodate tubulars of varying dimensions . for example , the adjustable roller assemblies 106 , 108 may be self - adjusted to accommodate tubulars with diametrical dimensions between approximately 2 % and 13 % inches . in accordance with the present invention , the drive rollers 134 , 136 , 138 of the adjustable roller assemblies 106 , 108 will always engage the tubular 302 , regardless of its size , at a set contact angle of , for example , 120 ° relative to the x - axis ( 30 ° relative to the drive roller of the center roller assembly 104 ). thus , the rollers may maintain a three - point contact of 120 °, as shown at points 402 , 404 , 406 , to reduce triangulation of the tubular 302 as it is being spinned by the rollers 134 , 136 , 138 . an additional benefit of engaging a tubular 302 at the same angle , for example 120 °, regardless of tube size , is that it enables the apparatus to engage the tubular with equal spinning loads at each contact point 402 , 404 , 406 . moreover , the translating adjustable rollers of the present invention provide a mechanical advantage over rollers that pivot into engagement with the tubular because rollers that pivot into engagement require more torque to keep the rollers engaged with the tubular due to the moment arm . in another implementation of the invention , the design of drive rollers 134 , 136 , 138 of the present invention can be modified to allow the spinner to have a dual function and operate as a clamping device . as will be illustrated in more detail below , in connection with fig5 - 11 , the drive rollers 134 , 136 , 138 can be replaced with driver roller assembly 500 , which is a driver roller having internal gear mechanisms . by adding internal gear mechanisms to the drive roller , the drive roller assembly 500 is able to apply additional torque on the tubulars , and thus , allow the spinner apparatus 100 to also operate as a clamping mechanism . fig5 is a front perspective view of one example of an implementation of a drive roller assembly 500 having internal gear mechanisms , and fig6 is a top view of the drive roller assembly 500 of fig5 . the drive roller assembly 500 can be used interchangeably with drive rollers 134 , 136 , 138 ( fig1 ). as illustrated in fig5 & amp ; 6 , each drive roller assembly 500 includes a driver roller 502 enclosing the internal gears that allow the driver rollers 502 to apply additional torque on the tubulars . housed within the driver roller 502 is a roller insert 504 that secures a modified sun gear 506 . the modified sun gear 506 includes an opening 508 for receiving the drive shaft of a gear motor from 144 , 146 , 148 ( fig1 ) to rotate the driver roller assembly 500 . the modified sun gear 506 includes ridges 510 within the opening for engaging the drive shaft of the gear motor 144 , 146 , 148 ( fig1 ), which provides for rotation of the drive roller 506 . the outer surface of the drive roller 506 may be smooth to minimize the damage done to the tubular pipe when acting as a spinner or casing joint when acting as a clamping device . fig7 is an exploded view of the drive roller 500 assembly of fig5 . as shown in fig7 , the drive roller assembly 500 includes , from top to bottom : ( i ) a roller insert 504 ; ( ii ) a modified sun gear 506 ; ( iii ) a sun gear insert 712 ; ( iv ) a planet carrier assembly 714 ; ( v ) a high load thrust bearing 716 ; ( vi ) a drive roller 502 ; ( vii ) a high - load ball bearing 718 and ( viii ) a tapered roller 720 . as illustrated in fig7 , the modified sun gear 506 has external teeth 722 on the lower portion of the modified sun gear 506 for securely fitting in , and engaging , the planet carrier assembly 714 . the lower portion of the modified sun gear 506 is positioned in an opening in the center of the planet carrier assembly 714 . the modified sun gear 506 further includes a sun gear insert 712 that press fits into the bottom of the modified sun gear 506 , which may be inserted in the modified sun gear 506 before inserting the modified sun gear 506 into the planet carrier assembly 714 . the planet carrier assembly 714 includes an upper plate 724 and a lower plate 726 and three planet gears 728 positioned there between , about the circumference of the plates 724 and 726 equidistant from one another . the upper plate 724 has a central opening for receiving the lower portion of the modified sun gear 506 . the teeth 722 on the lower portion of the modified sun gear 506 engage the teeth on the three planet gears 728 when positioned within the central opening of the upper plate 724 of the planet carrier assembly 714 . the driver roller 502 is a hollow tube having a cavity that houses the planet carrier assembly 714 , the modified sun gear 506 , the high load thrust bearing 716 , a high - load ball bearing 718 and a high - load tapered roller 720 . the planet carrier assembly 714 and the modified sun gear 506 sit atop the high load thrust bearing 716 , a high - load ball bearing 718 and a high - load tapered roller 720 within the cavity of the driver roller 502 . a ring gear 730 is located in the inner radius of the drive roller 506 . the ring gear 730 includes cut teeth or cogs that engage the cut teeth of the three planet gears 728 of the planet carrier assembly 714 . fig8 is a cross - section view of the drive roller assembly of fig6 , taken along lines a - a . fig8 best illustrates the assembly , engagement and the coupling of the various components of the drive roller assembly 500 . as illustrated , the a roller insert 504 maintains the higher portion of the modified sun gear 506 within the planet carrier assembly 714 atop the high load thrust bearing 716 , the high - load ball bearing 718 and the tapered roller bearing 720 . the teeth of the lower portion of the modified sun gear 506 engage the teeth of the planet rollers 728 in the planet carrier assembly 714 . the teeth of the planet gears 728 in the planet carrier assembly 714 thereby engage in the teeth of the ring gear 730 of the driver roller 502 , when assembled . thus , in operation , the rotation of the modified sun gear 506 ( driven by the drive shaft of the motor ) allows the rotation of the planet gears 728 in the planet carrier assembly 714 which in turn , rotates the driver roller 502 through engagement with the ring gear 730 . this 3 : 1 gear ratio then provides three times ( 3 ×) the torque at one - third the speed . fig9 is a top perspective view of the planet carrier assembly 714 of the drive roller assembly 500 of fig5 . as shown in fig9 , the planet carrier assembly 714 includes an upper plate 724 and a lower plate 726 , with three planet gears 728 positioned between the upper and lower plates . the planet gears 728 are positioned equidistant from one another spaced about the circumference of the plate 724 and 726 and positioned such that the teeth of the planet gears 728 extend out past the outer circumference of the plates 724 and 726 for engagement with the ring gear 730 of the drive roller 502 . the upper plate 724 has a central opening for receiving the lower portion of the modified sun gear 506 . the planet gears 728 rotate about dowel pins 932 that run from the upper plate 724 to the lower plate 726 and through the center of each planet gear 728 . the three planet gears 728 are arranged to interact with both the ring gear 730 of the drive roller 502 and the modified sun gear 506 at the same time . fig9 and 10 also illustrate the use of a machine key 715 positioned in grooves 960 ( fig1 ) that extend on the sides of the central opening of the lower plate 726 . the machine key is engaged by the shaft ( not shown ) on the apparatus or spinner 100 that holds the drive roller assemblies 500 on the spinner 100 . the engagement of the machine key by the shaft prevents the movement of the upper and lower plates 724 and 726 of the planet carrier assembly 714 , while still allowing the planet gears 728 to rotate about the dowel pins 932 . the machine key 715 is used to transmit the torque from the shaft to the planet carrier gear 714 . fig1 is a top view of the planet carrier assembly 714 of fig9 . fig1 best illustrates the equal size and spacing of the three planet gears 728 about the planet carrier assembly 714 . the planet gears 728 rotate about the dowel pins 932 running from the upper plate 724 through the center of the planet gears 728 to the lower plate 726 . the dowel pins 932 are secured on the upper and lower plates 724 and 726 by retaining rings 936 . fig1 illustrates the teeth 940 of the planet gears 728 extending outward past the upper and lower plates 724 and 726 for engagement with the ring gear 730 of the driver roller 502 and extending within the opening of the upper plate 724 for engagement with the teeth 722 on the lower portion of the modified sun gear 506 when inserted into the center of the planet carrier assembly 714 . the concentricity of the planet gear 728 spacing with the modified sun gear 502 and ring gear 730 allows the torque to carry through a straight line thus , eliminating the need to redirect the power or relocate other components . fig1 is an exploded view of the planet carrier assembly 714 of fig9 . as illustrated in fig1 , the planet carrier assembly 714 includes , from top to bottom , the following components : ( i ) retaining rings 936 ; ( ii ) an upper plate 724 ; ( iii ) high - load thrust bearings 942 ; bearing sleeves 944 ; ( iv ) planet gears 728 ; ( v ) additional high - load thrust bearings 942 ; ( vi ) a machine key 715 ; ( vii ) a lower plate 726 ; ( viii ) dowel pins 932 and ( ix ) additional retaining rings 936 . the three planet gears 728 are held between the upper lower and plates 724 and 726 of the planet carrier assembly 714 by dowel pins 932 and bearing sleeves 944 that run through the center openings in the planet gears 728 . the dowel pins 932 and bearing sleeves 944 allow the planet gears 728 to rotate above their center axis . the planet gears 728 are spaced about from the upper and lower plates 724 and 726 to allow for the planet gears 728 to spin freely between the plates by high - load thrust bearings 942 positioned above and below the planet gears 728 around the dowel pins 932 . both the upper and lower plates 724 and 726 have internal recesses 955 for receiving the bearings 942 and maintaining space between the planet gears 728 and the upper and lower plates 724 and 726 . the dowel pins 932 run through the openings in the upper and lower plates 724 and 726 and extend into outer recesses 950 in both the upper and lower plates 724 and 726 that allow the dowel pins 932 to be secured to the upper and lower plates 724 and 726 with retaining rings 936 positioned within the outer recesses of the upper and lower plates 724 and 726 . fig1 is a cross - section view of the planet carrier assembly 714 of fig1 taken along line a - a . fig1 best illustrates how the dowel pins 932 and bearing sleeves 944 extend through the center of the planet gears 728 and through openings on the upper and lower plates 724 and 726 . the outer recesses 950 of the upper and lower plates 724 and 726 to allow for retaining rings 936 to be positioned below ( or countersunk below ) the outer surfaces of the plates 724 and 726 . inner recesses 955 receiving the high - load thrust bearings 942 and provide space between the planet gears 728 and upper and lower plates 724 and 726 to allow the planet gears 728 to freely spin between the upper and lower plates 724 and 726 . in operation , each gear motor 144 , 146 , 148 ( fig1 ) drives the modified sun gear 506 , which rotates the set of three planet gears 728 on a stationary planet carrier assembly 714 . the three planet gears then engage and rotate the ring gear 730 of the driver roller 502 . the rotation of the modified sun gear 506 and planet carrier assembly 714 rotates the drive roller 502 . by using this internal gear system , a gear ratio of 3 : 1 is delivered , thus providing three times the torque at one - third the speed . incorporating this internal gear systems into the drive roller assemblies 500 delivers higher torque that permits the spinner / apparatus 100 to not only allow the rollers to make up drill pipe , but also to clamp casing joints . by being able to operate as both a drill spinner and clamping device , the vertical footprint of the apparatus is minimized as is the need to incorporate a taller external gear box to apply higher torque . in general , terms such as “ coupled to ,” and “ configured for coupling to ,” and “ secured to ,” and “ configured for securing to ” and “ in communication with ” ( for example , a first component is “ coupled to ” or “ is configured for coupling to ” or is “ configured for securing to ” or is “ in communication with ” a second component ) are used herein to indicate a structural , functional , mechanical , electrical , signal , optical , magnetic , electromagnetic , ionic or fluidic relationship between two or more components or elements . as such , the fact that one component is said to be in communication with a second component is not intended to exclude the possibility that additional components may be present between , and / or operatively associated or engaged with , the first and second components . the foregoing description of implementations has been presented for purposes of illustration and description . it is not exhaustive and does not limit the claimed inventions to the precise form disclosed . modifications and variations are possible in light of the above description or may be acquired from practicing the invention . the claims and their equivalents define the scope of the invention .