with reference to fig1 and 2 of the drawings , a power tool constructed in accordance with the teachings of the present invention is generally indicated by reference numeral 10 . as those skilled in the art will appreciate , the preferred embodiment of the present invention may be either a cord or cordless ( battery operated ) device , such as a portable screwdriver or drill . in the particular embodiment illustrated , the power tool 10 is a cordless drill having a housing 12 , a motor assembly 14 , a multi - speed transmission assembly 16 , a clutch mechanism 18 , an output spindle assembly 20 , a chuck 22 , a trigger assembly 24 and a battery pack 26 . those skilled in the art will understand that several of the components of the power tool 10 , such as the chuck 22 , the trigger assembly 24 and the battery pack 26 , are conventional in nature and therefore need not be discussed in significant detail in the present application . reference may be made to a variety of publications for a more complete understanding of the conventional features of the power tool 10 . one example of such publications is u . s . pat . no . 5 , 897 , 454 issued apr . 27 , 1999 , the disclosure of which is hereby incorporated by reference as if fully set forth herein . the housing 12 includes a pair of mating handle shells 34 that cooperate to define a handle portion 36 and a drive train or body portion 38 . the trigger assembly 24 and the battery pack 26 are mechanically coupled to the handle portion 36 and electrically coupled to the motor assembly 14 in a conventional manner that is not specifically shown but which is readily the capabilities of one having an ordinary level of skill in the art . the body portion 38 includes a motor cavity 40 and a transmission cavity 42 . the motor assembly 14 is housed in the motor cavity 40 and includes a rotatable output shaft 44 , which extends into the transmission cavity 42 . a motor pinion 46 having a plurality of gear teeth 48 is coupled for rotation with the output shaft 44 . the trigger assembly and battery pack 26 cooperate to selectively provide electric power to the motor assembly 14 in a manner that is generally well known in the art so as to permit the user of the power tool 10 to control the speed and direction with which the output shaft 44 rotates . the transmission assembly 16 is housed in the transmission cavity 42 and includes a speed selector mechanism 60 . the transmission assembly 16 receives a rotary input from the motor pinion 46 and converts that input to a relatively lower speed , higher torque output that is transmitted to the shaft 62 of the output spindle assembly 20 . the transmission assembly 16 includes a plurality of reduction elements that are selectively engaged by the speed selector mechanism 60 to provide a plurality of speed ratios . each of the speed ratios multiplies the speed and torque of the drive input in a predetermined manner , permitting the output speed and torque of the transmission assembly 16 to be varied in a desired manner between a relatively low speed , high torque output and a relatively high speed , low torque output . rotary power output from the transmission assembly 16 is transmitted to the output spindle assembly , to which the chuck 22 is coupled for rotation , to permit torque to be transmitted to a tool bit ( not shown ). the clutch mechanism 18 is coupled to the transmission assembly and is operable for limiting the magnitude of the torque associated with the output of the transmission assembly 16 to a predetermined , selectable torque limit . with additional reference to fig3 the transmission assembly 16 is illustrated to further include a gear case 100 that houses a three - stage , two - speed gear train 102 . with additional reference to fig4 the gear case 100 is shaped in a generally hollow cylindrical manner and includes a fastening tab 104 and a clip aperture 106 on each of its lateral sides , a pair of guide rails 108 and a guide tab 110 that is located on its top surface , and a central cavity 112 that extends longitudinally through the gear case 100 . each fastening tab 104 terminates at its outward face at a coupling recess 114 that extends in a direction that is generally transverse to the central cavity 112 . the coupling recess 114 is preferably arcuately shaped , and in the particular embodiment illustrated , is illustrated to be generally u - shaped . each clip aperture 106 extends through the wall 116 of the gear case 100 along the longitudinal axis 118 of the central cavity 112 and intersects the central cavity 112 . the guide rails 108 positioned rearwardly of the guide tab 110 and are spaced laterally apart from one another . the guide rails 108 and the guide tab 110 will be discussed in further detail , below . the gear train 102 is illustrated to be a planetary type gear train , having a first planetary gear set 120 , a second planetary gear set 122 and a third planetary gear set 124 . in the example provided , each of the first , second and third gear sets 120 , 122 and 124 are operable in an active mode , wherein the gear set performs a speed reduction and torque multiplication operation , while the second planetary gear set 122 is also operable in an inactive mode , wherein it provides a rotary output having a speed and torque that is about equal to that which is input to it . the first planetary gear set 120 includes first ring gear 130 , a first set of planet gears 132 and a first reduction carrier 134 . the first ring gear 130 is an annular structure , having a plurality of gear teeth 130 a that are formed about its interior diameter and a plurality of gear case engagement teeth 130 b that are formed onto its outer perimeter . with additional reference to fig5 the first ring gear 130 is disposed within the central cavity 112 of the gear case 100 such that the gear case engagement teeth 130 b engage mating teeth 130 c formed on the inner surface of the gear case 100 to inhibit relative rotation between the first ring gear 130 and the gear case 100 . as the gear case engagement teeth 130 b terminate prior to the rear face 130 d of the first ring gear 130 , forward movement of the first ring gear 130 is halted by interference between the mating teeth 130 c that are formed on the inner surface of the gear case 100 and the portion of the first ring gear 130 that is disposed rearwardly of the gear case engagement teeth 130 b . the first reduction carrier 134 includes a body 134 a , which is formed in the shape of a flat cylinder and a plurality of cylindrical pins 134 b that extend from the rearward face of the body 134 a , and a plurality of 134 c a plurality of gear teeth 134 c are formed into the outer perimeter of the body 134 a and are sized to engage the gear teeth 152 a of the second ring gear 152 . with reference to fig7 the profile of the gear teeth 134 c of the body 134 a is illustrated in greater detail . as shown , each tooth 134 c terminates at a gradual radius 190 at the forward face of the body 134 a but terminates abruptly at the rearward face of the body 134 a . a radius 192 is also formed on the valleys 194 between the gear teeth 134 c . the first set of planet gears 132 includes a plurality of planet gears 132 a , each of which being generally cylindrical in shape and having a plurality of gear teeth 132 b formed onto its outer perimeter and a pin aperture ( not specifically shown ) formed through its center . each planet gear 132 a is rotatably supported on an associated one of the pins 132 b of the first reduction carrier 134 and is positioned to be in meshing engagement with the gear teeth of the first ring gear 130 . a first annular thrust washer 140 is fitted to the end of the gear case 100 proximate the motor assembly 14 and prevents the planet gears 132 from moving rearwardly and disengaging the pins 134 b of the first reduction carrier 134 . a raised portion 142 is formed onto the front and rear faces of each planet gear 132 to inhibit the gear teeth 132 b of the planet gears 132 from rubbing on the first reduction carrier 134 and the first thrust washer 140 . the teeth 46 a of the motor pinion 46 are also meshingly engaged with the teeth 132 b of the planet gears 132 and as such , the motor pinion 46 serves as the first sun gear for the first planetary gear set 120 . the second planetary gear set 122 is disposed within the central cavity 112 forward of the first planetary gear set 120 and includes a second sun gear 150 , a second ring gear 152 , a second reduction carrier 154 and a second set of planet gears 156 . the second sun gear 150 is fixed for rotation with the first reduction carrier 134 and includes a plurality of gear teeth 150 a that extend forwardly from the flat , cylindrical portion of the first reduction carrier 134 . the second ring gear 152 is an annular structure having a plurality of gear teeth 152 a formed about its interior diameter , an annular clip groove 158 formed into its outer perimeter and a plurality of gear case engagement teeth 160 that are formed onto its outer perimeter . the gear teeth 152 a may be heavily chamfered at the rear face 152 b of the second ring gear 152 but terminate abruptly its front face . more preferably , a heavy radius 170 is formed onto the rear face 152 b and the sides of each of the gear teeth 152 a as illustrated in fig6 with the heavy radius 170 being employed rather than the heavy chamfer as the heavy radius 170 on the gear teeth 152 a provides for better engagement between the second ring gear 152 and the second reduction carrier 154 , as will be described in more detail , below . in the example illustrated , the clip groove 158 is a rectangular slot having a pair of sidewalls 174 . the clip groove 158 will be discussed in further detail , below . the second ring gear 152 is movably disposed within the central cavity 112 of the gear case 100 between a first position as shown in fig6 wherein the gear case engagement teeth 160 engage mating teeth 180 formed on the inner surface of the gear case 100 to inhibit relative rotation between the second ring gear 152 and the gear case 100 , and a second position as shown in fig5 wherein the gear case engagement teeth 160 are axially spaced apart from the mating teeth 180 to thereby permit relative rotation between the second ring gear 152 and the gear case 100 . the second reduction carrier 154 includes a body 154 a , which is formed in the shape of a flat cylinder , and plurality of pins 154 b that extend from the rearward face of the body 154 a . referring back to fig3 and 5 , the second set of planet gears 156 is shown to include a plurality of planet gears 156 a , each of which being generally cylindrical in shape and having a plurality of gear teeth 156 b and a pin aperture ( not specifically shown ) in its center . each planet gear 156 a is supported for rotation on an associated one of the pins 154 b of the second reduction carrier 154 and is positioned such that the gear teeth 156 b are in meshing engagement with gear teeth 152 a of the second ring gear 152 . the third planetary gear set 124 is disposed on the side of the second planetary gear set 122 opposite the first planetary gear set 120 . like the second planetary gear set 122 , the third planetary gear set 124 includes a third sun gear 200 , a third ring gear 202 , a third reduction carrier 204 and a third set of planet gears 206 . the third sun gear 200 is fixed for rotation with the body 154 a of the second reduction carrier 154 and includes a plurality of gear teeth 200 a that extend forwardly from the body 154 a . an annular second thrust washer 210 is disposed between the second ring gear 152 and the third ring gear 202 and operates to limit the forward movement of the second ring gear 152 and the rearward movement of the third ring gear 202 and the third set of planet gears 206 . the second thrust washer 210 , which includes an aperture 212 through which the third sun gear 200 extends , engages the inner surface of the gear case 100 . the third ring gear 202 is an annular structure having a plurality of gear teeth 202 a formed about its interior diameter and an outer radial flange 220 that forms its outer perimeter . a clutch face 222 is formed into the forward surface of the outer radial flange 220 . in the particular embodiment illustrated , the clutch face 222 is shown to have an arcuate cross - sectional profile and is further defined by a plurality of peaks 224 and valleys 226 that are arranged relative to one another to form a series of ramps that are defined by an angle of about 18 °. those skilled in the art will understand , however , that clutch faces of other configurations , such as those having a sinusoidal shape , may also be employed . those skilled in the art will also understand that while the clutch face 222 is shown to be unitarily formed with the third ring gear 202 , multi - component configurations may also be employed . such multi - component configurations include , for example , an annular clutch face ring ( not shown ) having a rearward facing first side for engaging the third ring gear 202 and a forward facing second side that forms the clutch face 222 . configuration in this latter manner may be advantageous , for example , when it is necessary for the clutch face 222 to have properties or characteristics ( e . g ., lubricity , hardness , toughness , surface finish ) that are different from the properties or characteristics of the third ring gear 202 . the third reduction carrier 204 includes a body 204 a , which is formed in the shape of a flat cylinder , and a plurality of cylindrical pins 204 b , which extend from the rearward face of the body 204 a , and a coupling portion 204 c that extends from the forward face of the body 204 a . rotary power transmitted to the third reduction carrier 204 is transmitted through the coupling portion 204 c to a coupling member 230 that engages the shaft 62 of the output spindle assembly 20 . those skilled in the art will understand that various other coupling devices and methods may be utilized to couple the third reduction carrier 204 to the output spindle assembly 20 , such as a direct coupling of the shaft 62 of the output spindle assembly 20 to the body 204 a of the third reduction carrier 204 . the third set of planet gears 206 includes a plurality of planet gears 206 a , each of which being generally cylindrical in shape and having a plurality of gear teeth 206 b formed onto its outer perimeter and a pin aperture ( not specifically shown ) formed through its center . each planet gear 206 a is rotatably supported on an associated one of the pins 204 b of the third reduction carrier 204 and is positioned to be in meshing engagement with the gear teeth 202 a of the third ring gear 202 . the speed selector mechanism 60 is illustrated to include a slider body 240 and a clip structure 242 . the slider body 240 is an elongated structure that is configured to be housed between the handle shells 34 and selectively slid along the top of the gear case 100 . the slider body 240 includes an attachment groove 246 , which permits the clip structure 242 to be attached to the slider body 240 , and a selector tab 248 , which is configured to receive an input from the user of the power tool 10 to switch the second planetary gear set 122 between the active and inactive modes . with additional reference to fig9 and 10 , a slot 250 is formed into the underside of the slider body 240 and is sized to engage the guide tab 110 that extends from the top surface of the gear case 100 . the guide rails 108 are spaced laterally apart to receive the slider body 240 . the guide tab 110 and the guide rails 108 cooperate with the sides of the slot 250 and the sides of the attachment groove 246 , respectively , to guide the slider body 240 as the slider body 240 is moved in an axial direction along the top surface of the gear case 100 . returning to fig3 the clip structure 242 is a wire that is formed to include a circular body portion 256 and a pair of end tabs 258 that extend inwardly from the body portion 256 . the body portion 256 is fixedly coupled to an attachment tab 260 , which is illustrated to be a pair of trunnions that extend downwardly from the slider body 240 . the body portion 256 is sized to fit over the outer circumference of the gear case 100 and preferably includes a rotation - inhibiting element 262 to inhibit the clip structure 242 from rotating relative to the attachment tab 260 . in the embodiment provided , the rotation - inhibiting element 262 is illustrated to include a plurality of bends , such as m -, n -, s -, or z - shaped bends , that are formed into the wire and which are molded into or abut the underside of the slider body 240 . each of the end tabs 258 extends through an associated one of the clip apertures 106 in the sides of the gear case 100 and engages the annular clip groove 158 that is formed into the perimeter of the second ring gear 152 . the wire that forms the clip structure 242 is somewhat smaller in diameter than the width of the clip groove 158 . alternatively , the rotation - inhibiting element 262 may include a plurality of tabs that are formed from bends in the body portion 256 of the wire , wherein each tab is defined by a circumferentially extending segment that is offset radially outwardly from the remainder of the body portion 256 . each of the tabs is configured to be received in a corresponding aperture formed into the slider body 240 such that the front and rear faces of each tab engage the sides of the apertures in the slider body 240 . the tabs , being confined within an associated aperture in the slider body 240 , inhibit relative movement between the slider body 240 and the body portion 256 of the clip structure 242 . sliding movement of the slider body 240 relative to the gear case 100 is operable for transmitting a force through the end tabs 258 of the clip structure 242 and to the second ring gear 152 which may be used to move the second ring gear 152 between the first and second positions . when the second ring gear 152 is positioned in the first position as illustrated in fig6 the engagement teeth 160 of the second ring gear 152 are engaged to the mating engagement teeth 180 of the gear case 100 and the gear teeth 152 a of the second ring gear 152 are engaged to only the gear teeth 156 b of the planet gears 156 a of the second planet gear set 156 , thereby permitting the second planetary gear set 122 to operate in the active mode . when the second ring gear 152 is positioned in the second position as illustrated in fig5 the engagement teeth 160 of the second ring gear 152 are not engaged to the mating engagement teeth 180 of the gear case 100 and the gear teeth 152 a of the second ring gear 152 are engaged to both the gear teeth 156 b of the planet gears 156 a of the second planet gear set 156 and the gear teeth 134 c of the first reduction carrier 134 , thereby permitting the second planetary gear set 122 to operate in the inactive mode . in fig3 the clutch mechanism 18 is illustrated to include a clutch sleeve 300 , a clutch member 302 , a plurality of balls 304 , a clutch plate 306 , a spring 308 , an adjustment collar 310 , a detent mechanism 312 and a clutch cover 314 . with additional reference to fig4 the clutch sleeve 300 is illustrated to include a wall member 320 , which defines a hollow cavity or bore 322 that extends along the longitudinal axis of the clutch sleeve 300 , a base portion 324 and a nose portion 326 that extends forwardly from the base portion 324 . the rearward end of the bore 322 is sized to receive a forward portion of the gear case 100 , the third ring gear 202 and the third reduction carrier 204 , while the forward portion of the bore 322 is sized somewhat smaller so as to receive the coupling member 230 and the shaft 62 of the output spindle assembly 20 . the nose portion 326 , which is somewhat smaller in diameter than the base portion 324 , is generally cylindrical , having a helical thread form 330 that wraps around its perimeter . the base portion 324 includes a pair of outboard tabs 334 , which are formed on the lateral sides of the base portion 324 , a plurality of leg apertures 336 , which extend generally perpendicular to the longitudinal axis of the bore 322 , and a detent aperture 338 for receiving the detent mechanism 312 . each outboard tab 334 is configured to receive an associated one of the fastening tabs 104 and includes a pin aperture 340 . in the particular embodiment illustrated , each outboard tab 334 is defined by an outer lateral wall 342 , a lower wall 344 , and an upper wall 346 , through which the pin aperture 340 extends . with additional reference to fig1 , a cylindrical locking pin 350 is fitted through the pin aperture 340 in each outboard tab 334 and the coupling recess 114 in the associated fastening tab 104 and thereby fixedly but removably couples the clutch sleeve 300 to the gear case 100 . the locking pins 350 are highly advantageous in that they eliminate the need for threaded fasteners , fastening tools and the use of bosses in the gear case 100 and the clutch sleeve 300 that are configured for receiving a conventional threaded fastener . the leg apertures 336 are circumferentially spaced about the nose portion 326 and extend through the base portion 324 and intersect the rearward portion of the bore 322 . the detent aperture 338 extends through the base portion 324 between the clutch cover 314 and the gear case 100 and is sized to receive a portion of the detent mechanism 312 . in fig3 and 13 , the clutch plate 306 is illustrated to be a unitarily formed structure that includes a washer - like annular plate member 360 and a plurality of leg members 362 that are coupled to and circumferentially spaced about the annular plate member 360 . the leg members 362 have a generally circular cross - section and extend generally perpendicularly from the plate member 360 . the end of the each leg member 362 opposite the plate member 360 terminates in a spherical recess 364 that is configured to receive one of the balls 304 , which are illustrated to be hardened bearing balls . the clutch plate 306 is disposed over the nose portion 326 of the clutch sleeve 300 and moved axially rearward to push the leg members 362 through the leg apertures 336 in the base portion 324 , as well as to bring each of the balls 304 into contact with the clutch face 222 and an associated one of the spherical recesses 364 . in an alternate embodiment illustrated in fig1 , the clutch plate 306 ′ is illustrated to be similar to the clutch plate 306 , except that the ends of the leg members 362 ′ opposite the annular plate member 360 terminate at a spherical protrusion 370 , rather than a spherical recess . configuration in this manner is advantageous in that it eliminates the balls 304 from the clutch mechanism 18 . returning to fig3 and with additional reference to fig1 , the spring 308 is illustrated to be a conventional compression spring having ground ends . the spring 308 is disposed over the nose portion 326 of the clutch sleeve 300 between the plate member 360 of the clutch plate 306 and the adjustment collar 310 . the adjustment collar 310 is an annular structure that is illustrated to include an internal annular flange 380 , a threaded portion 382 and an engagement portion 384 . the internal annular flange 380 extends around the inner circumference of the adjustment collar 310 and sized somewhat smaller in diameter than the spring 308 but larger than the nose portion 326 of the clutch sleeve 300 . the threaded portion 382 intersects the internal annular flange 380 and is sized to threadably engage the thread form 330 that is formed on the outer diameter of the nose portion 326 . the engagement portion 384 is configured to permit the adjustment collar 310 to be rotatably coupled to the clutch cover 314 and well as to move axially within the clutch cover 314 . in the example provided , the engagement portion 384 includes a plurality of engagement teeth 384 a that are formed about the outer perimeter of the adjustment collar 310 . the engagement teeth 384 a will be described in further detail , below . a wire clip 400 is coupled to the nose portion 326 to inhibit the removal of the adjustment collar 310 from the thread form 330 . the wire clip 400 is formed in u - shape , having a base 402 that is disposed between a pair of spaced apart legs 404 . each of the legs 404 extends in a generally perpendicular direction away from the base 402 . with the clutch plate 306 and spring 308 fitted over the nose portion 326 and the adjustment collar 310 engaged to the thread form 330 , the wire clip 400 is fitted over the nose portion 326 generally perpendicular to the longitudinal axis of the clutch sleeve 300 such that legs 404 are engaged to leg apertures 408 in the clutch sleeve 300 and the base 402 is disposed in a shallow u - shaped recess 410 that is situated on the top surface of the nose portion 326 as best shown in fig4 . engagement of the wire clip 400 into the leg apertures 408 and recess 410 operatively locks the wire clip 400 to the nose portion 326 and thereby creates a positive stop that is configured to prevent the adjustment collar 310 from being threaded out of engagement with the thread form 330 that is formed onto the nose portion 326 . the clutch cover 314 is constructed in the form of a hollow sleeve that shrouds the clutch plate 306 , the spring 308 , the nose portion 326 and the wire clip 400 . the clutch cover 314 extends forwardly of the base portion 324 and includes a gripping surface 420 that is formed on its outer perimeter . the gripping surface 420 is contoured to permit the user of the power tool 10 to rotate the clutch cover 314 about the longitudinal axis of the power tool 10 to adjust the setting of the clutch mechanism 18 as will be discussed in greater detail , below . a plurality of mating engagement teeth 422 are formed onto the inner diameter of the clutch cover 314 which are sized to engage the engagement teeth 384 a of the adjustment collar 310 . the mating engagement teeth 422 are relatively longer than the engagement teeth 384 a and as such , permit the engagement teeth 384 a to axially slide along the mating engagement teeth 422 along the longitudinal axis of the power tool 10 when the clutch cover 314 is rotated . in the example provided , the detent mechanism 312 is illustrated to include a detent spring 430 , a plunger 432 and a detent ring 434 . the detent spring 430 and plunger 432 are housed in the detent aperture 338 that is formed through the base portion 324 of the clutch sleeve 300 . the detent spring 430 , which is illustrated to be a conventional compression spring , abuts the gear case 100 on a first side and a flattened end of the plunger 432 on the opposite side , thereby biasing the plunger 432 in a direction outwardly from the base portion 324 . the plunger 432 includes a contact end 440 , which is defined by a spherical radius in the example illustrated , and which is biased forwardly by the detent spring 430 into contact with the detent ring 434 . in the particular embodiment provided , the detent ring 434 is integrally formed with the clutch cover 314 and includes a plurality of circumferentially spaced recesses or detents 442 that are sized to engage the contact end 440 of the plunger 432 . each of the detents 442 is illustrated to be defined by a spherical radius that conforms to the contact end 440 . a setting indicator 450 ( fig2 ) may be employed to indicate the position of the adjustment collar 310 relative to the clutch sleeve 300 . in the example provided , the setting indicator 450 includes an arrow 452 that is formed into the handle shells 34 and a scale 454 that is marked into the circumference of the clutch cover 314 . rotation of the clutch cover 314 relative to the clutch sleeve 300 causes the adjustment collar 310 to rotate in an equivalent manner to thereby alter the amount by which the spring 308 is compressed . interaction between the contact end 440 of the plunger 432 and the detents 442 in the detent ring 434 provide the user of the power tool 10 with feedback as to the setting of the clutch mechanism 18 , as well as inhibit the clutch cover 314 from inadvertently rotating out of the position to which it has been set . the spring 308 exerts a compression force onto the annular flange 380 of the adjustment collar 310 and the plate member 360 of the clutch plate 306 , driving the leg members 362 of the clutch plate 306 rearwardly and biasing the balls 304 into engagement with the clutch face 222 . the balls 304 exert a counter torque onto the clutch face 222 that tends to inhibit rotation of the third ring gear 202 relative to the clutch sleeve 300 . when the power tool 10 is operated and the torque that is exerted through the gear teeth 202 a of the third ring gear 202 exceeds the counter torque , the peaks 224 of the clutch face 222 ride over the balls 304 to enable the third ring gear 202 to rotate relative to the third reduction carrier 204 and greatly reduce the torque that is applied to the output spindle assembly 20 . while the invention has been described in the specification and illustrated in the drawings with reference to a preferred embodiment , it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention as defined in the claims . in addition , many modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from the essential scope thereof . therefore , it is intended that the invention not be limited to the particular embodiment illustrated by the drawings and described in the specification as the best mode presently contemplated for carrying out this invention , but that the invention will include any embodiments falling within the foregoing description .