Patent Publication Number: US-10766128-B2

Title: Power tool drive mechanism

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
     This is a continuation application of U.S. application Ser. No. 14/444,982 filed Jul. 28, 2014, which claims the benefit of the entire disclosures of which are incorporated herein by reference. 
    
    
     FIELD OF THE INVENTION 
     The present invention relates to a power tool drive mechanism. 
     BACKGROUND OF THE INVENTION 
     Fastening tools, such as nailers, are used in the construction trades. However, many fastening tools which are available are insufficient in design, expensive to manufacture, heavy, not energy efficient, lack power, have dimensions which are inconveniently large and cause operators difficulties when in use. Further, many available fastening tools do not adequately guard the moving parts of a nailer driving mechanism from damage. 
     Many fastening tools which are available are inconveniently bulky and have systems for driving a fastener which have dimensions that require the fastening tool to be larger than desired. For example, drive systems having a motor which turns a rotor can require clutches, transmissions, control systems and kinetic parts which increase stack up and limit the ability of a power tool to be reduced in size while retaining sufficient power to achieve a desired performance. 
     There is a strong need for a fastening tool having an improved motor and drive mechanism. 
     SUMMARY OF THE INVENTION 
     In an embodiment, a power tool can have an electric motor having a rotor which has a rotor shaft. The rotor shaft can be coupled to a flywheel which can have a potion which is cantilevered over at least a portion of the rotor. The flywheel can also have a contact surface adapted to impart energy from the flywheel when contacted by a moveable member. The overlapping portion can be adapted to rotate radially about at least a portion of the motor. The power tool can have a motor which has an inner rotor, or a motor which has an outer rotor. The flywheel can have a portion which is cantilevered over at least a portion of said rotor. 
     In an embodiment, a power tool can have an electric motor having a motor housing and a rotor having a rotor shaft. The rotor shaft can be coupled to a flywheel which can have a potion which is cantilevered over at least a portion of the motor housing. The flywheel can also have a contact surface adapted to impart energy from the flywheel when contacted by a moveable member. The overlapping portion can be adapted to rotate radially about at least a portion of the motor housing. The power tool can have a motor which has an inner rotor, or a motor which has an outer rotor. 
     The power tool can have an overlapping portion which supports a flywheel ring which can have a contact surface. Optionally, the contact surface can have a geared portion. The contact surface can optionally have at least one grooved portion. The contact surface can optionally have at least one toothed portion. 
     In an embodiment, the power tool can have a flywheel ring and a rotor shaft which rotate in a ratio in a range of 0.5:1.5 to 1.5:0.5; such as in a range of 1:1.5 to 1.5:1. In an embodiment, the power tool can have a flywheel ring and a rotor shaft which rotate in a ratio of about 1:1. In an embodiment, the power tool can have a flywheel ring and a rotor shaft which rotate in a ratio of 1:1. The power tool can also have a flywheel ring which rotates at a speed in a range of from about 2500 rpm to about 20000 rpm. The power tool can also have a flywheel ring which rotates at a speed in a range of from about 5600 rpm to about 10000 rpm. In another embodiment, the power tool can have a flywheel ring which has a contact surface which has a speed in a range of from about 20 ft/s to about 200 ft/s. In yet another embodiment, the power tool can have a flywheel ring which has an inertia in a range of from about 10 J(kg*m{circumflex over ( )}2) to about 500 J(kg*m{circumflex over ( )}2). 
     In an embodiment, the power tool can have a flywheel ring which rotates in a plane parallel to a driver profile centerline plane. The power tool can also have a moveable member which is a driver blade which has a driving action which is energized by a transfer of energy from contact of the driver blade with the flywheel. The power tool can also have a moveable member which is a driver profile which has a driving action which is energized by a transfer of energy from contact of the driver profile with the flywheel. 
     The power tool can be a cordless power tool. The power tool can be a cordless nailer and can be adapted to drive a nail. The power tool can also be driven by a power cord, or be pneumatic or receive power from another source. 
     In an embodiment, a fastening device can have a motor having a cantilevered flywheel. The cantilevered flywheel can have a contact surface adapted for frictional contact with a driving member adapted to drive a fastener. The fastening device can have a motor which has an inner rotor, or a motor which has an outer rotor. The motor can be a brushed motor or a brushless motor. The motor can be an inner rotor motor which can be a brushed motor or an outer rotor motor which can be a brushed motor. The motor can be an inner rotor motor which can be a brushless motor or an outer rotor motor which can be a brushless motor. 
     In an embodiment, the fastening device can also have a cupped flywheel. The cupped flywheel can have a flywheel ring. In an embodiment, at least a portion of the cupped flywheel can be cantilevered over at least a portion of said motor and/or motor housing. The cupped flywheel can have a contact surface. The cupped flywheel can have a geared flywheel ring. 
     In an embodiment, the cupped flywheel can have a mass in a range of from about 1 oz to about 20 oz. In another embodiment, the fastening device can have a cantilevered flywheel which can have a diameter in a range of from about 0.75 to about 12 inches. The cantilevered flywheel can be adapted to rotate at an angular velocity of from about 500 rads/s to about 1500 rads/s. The cantilevered flywheel can be adapted to have a flywheel energy in a range of from about 10 j to about 1500 j. 
     In an embodiment, the fastening device can have a driving member which is driven with a driving force of from about 2 j to about 1000 j. In another embodiment, the fastening device can have a driving member which is driven at a speed of from about 10 ft/s to about 300 ft/s. The fastening device can have a driving member which is a driver blade. The fastening device can have a driving member which is a driver profile. 
     The fastening device can have a direct drive mechanism. In an embodiment, the direct drive mechanism can have a cantilevered flywheel. In another aspect, the fastening device can have a drive mechanism which is clutch-free. 
     The fastening device can be a nailer and can be adapted to drive a fastener which is a nail. 
     In an embodiment, a power tool can have a motor having a rotor and a flywheel adapted for turning by the rotor. The flywheel can have a flywheel portion which is positioned radially over at least a portion of the motor. In an embodiment, the flywheel portion can be at least a part of a flywheel ring, or can be a flywheel ring. In an embodiment, the flywheel portion can be at least a part of a flywheel body, or a flywheel body. In an embodiment, the flywheel portion can be at least a part of a cupped flywheel, or a cupped flywheel. 
     In an embodiment, the power tool can have a flywheel which is a cupped flywheel. The flywheel body can have a flywheel inner circumference which is configured radially about at least a portion of the motor. In another embodiment, the power tool can have a flywheel which is a cupped flywheel and which has a flywheel ring having at least a part which positioned radially over at least a portion of the motor. 
     In an embodiment, the power tool can have a motor housing which houses at least a portion of the motor and a flywheel portion which is positioned radially over at least a portion of the motor housing. 
     In an embodiment, the power tool can have a flywheel adapted for clutch-free turning by the motor. In another embodiment, the power tool can have a flywheel adapted for transmission-free turning by the motor. In yet another embodiment, the power tool can have a flywheel which can be adapted for turning by the rotor in a ratio of 1 turn of the flywheel to 1 turn of the rotor. In even another embodiment, the power tool can have a flywheel which can be adapted for turning by the rotor in a ratio of 1.5 turn of the flywheel to 1 turn of the rotor to 1.0 turn of the flywheel to 1.5 turn of the rotor. 
     In an embodiment, the power tool can be a fastening device. In another embodiment, the power tool can be a fastening device adapted to drive a nail into a workpiece. 
     In an embodiment, a power tool can have a motor having a rotor axis and a flywheel adapted for turning by the motor. The flywheel can have a flywheel portion coaxial to the rotor axis and which is at least in part located over at least a portion of the motor. The power tool can have a flywheel body having a flywheel body portion which radially surrounds at least a portion of the motor. The power tool can have a cupped flywheel having a cupped flywheel portion which radially surrounds at least a portion of the motor. The power tool can have a cupped flywheel having a flywheel ring and in which a portion of the flywheel ring is adapted to rotate coaxial to the rotor axis. The power tool can have a flywheel portion which has a flywheel contact surface which is adapted to rotate coaxial to the rotor axis. In an embodiment, the flywheel contact surface which can be adapted to have a velocity of at least 10 ft/s and in which the flywheel contact surface can be adapted to revolve coaxially about the rotor axis. 
     In an embodiment, the power tool can have a flywheel portion which is a cantilevered portion. The power tool can have a flywheel portion which is cantilevered over at least a portion of the motor. The flywheel portion which is cantilevered over at least a portion of the motor can have a contact surface. 
     In another embodiment, the power tool can have a flywheel portion which is cantilevered over at least a portion of the motor and can have a geared flywheel ring. In yet another embodiment, the power tool can have a motor housing which houses at least a portion of the motor and in which the flywheel has a flywheel inner circumference which is configured radially about at least a portion of the motor and which has a flywheel motor clearance of greater than 0.02 mm. 
     The power tool can be a fastening device. 
     In addition to the disclosure of articles, apparatus and devices herein, this disclosure encompasses a variety of method of use and construction of the disclosed embodiment. For example, a method for driving a fastener, can have the steps of: providing a motor and a cantilevered flywheel adapted to be turned by the motor; providing a driving member adapted to drive a fastener into a workpiece; providing a fastener to be driven; configuring the cantilevered flywheel such that at least a portion of the cantilevered flywheel can be reversibly contacted with a portion of the driving member; operating the cantilevered flywheel at an inertia of from about 2 j to about 500 j; causing the driving member to reversibly contact at least a portion of the cantilevered flywheel; imparting a driving force in a range of from about 1 j to about 475 j to the driving member from the cantilevered flywheel; and driving the fastener into the workpiece. The motor which is provided can have an inner rotor or an outer rotor. Additionally, the motor provided can be a brushed motor or a brushless motor. 
     In an embodiment, the method of driving a fastener can also have the step of operating the cantilevered flywheel at a speed in a range of from about 2500 rpm to about 20000 rpm. In an embodiment, the method of driving a fastener can also have the step of operating the cantilevered flywheel at an angular velocity in a range of from about 250 rads/s to about 2000 rads/s. 
     In another embodiment, the method of driving a fastener can also have the steps of providing a fastener which is a nail; and driving the nail into the workpiece. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The present invention in its several aspects and embodiments solves the problems discussed above and significantly advances the technology of fastening tools. The present invention can become more fully understood from the detailed description and the accompanying drawings, wherein: 
         FIG. 1  is a knob-side side view of an exemplary nailer having a fixed nosepiece assembly and a magazine; 
         FIG. 2  is a nail-side view of an exemplary nailer having the fixed nosepiece assembly and the magazine; 
         FIG. 3  is a detailed view of the fixed nosepiece with a nosepiece insert and a mating nose end of the magazine; 
         FIG. 4  is a perspective view of the latched nosepiece assembly of the nailer having a latch mechanism; 
         FIG. 5  is a side sectional view of the latched nosepiece assembly; 
         FIG. 6  is a perspective view illustrating the alignment of the nailer, magazine and nails; 
         FIG. 7  is a perspective view of a cupped flywheel positioned for assembly onto an inner rotor motor; 
         FIG. 8  is a side view of the cupped flywheel positioned for assembly onto the inner rotor motor; 
         FIG. 9  is a front view of the cupped flywheel; 
         FIG. 10A  a side view of a drive mechanism having the cupped flywheel which is frictionally engaged with a driver profile; 
         FIG. 10B  is a cross-sectional view of the drive mechanism having the cupped flywheel which is frictionally engaged with the driver profile; 
         FIG. 11  is a perspective view of the drive mechanism having the cupped flywheel and the driver which is in a resting state; 
         FIG. 12A  is a perspective view of the drive mechanism having the cupped flywheel and the driver which is in an engaged state; 
         FIG. 12B  is a perspective view of the drive mechanism having the cupped flywheel and the driver which is in an engaged state showing an embodiment in which a flywheel ring centerline plane in coplanar with a driver centerline plane; 
         FIG. 13  is a perspective view of a drive mechanism having the cupped flywheel and the driver which is in a driven state; 
         FIG. 14  is a side view of a partial drive assembly having the cupped flywheel; 
         FIG. 15  is a top view of the partial drive assembly having the cupped flywheel; 
         FIG. 16A  is a perspective view of the drive assembly having the cupped flywheel shown in conjunction with a magazine for nails; 
         FIG. 16B  is a sectional view of the drive assembly having the cupped flywheel taken along the longitudinal centerline plane of the rotor shaft; 
         FIG. 17  is a sectional view of the drive assembly having the cupped flywheel taken along the longitudinal centerline plan of the driver profile; 
         FIG. 18A  is a perspective view of the cupped flywheel; 
         FIG. 18B  is a view of the cupped flywheel having a number of flywheel openings in a flywheel face; 
         FIG. 18C  is a view of the cupped flywheel having a number of flywheel slots in a flywheel body; 
         FIG. 18D  is a view of the cupped flywheel having a number of flywheel slots in the flywheel body and the flywheel face; 
         FIG. 18E  is a view of the cupped flywheel having a number of flywheel round openings in the flywheel body and the flywheel face; 
         FIG. 18F  is a view of the cupped flywheel having a mesh flywheel body and a mesh flywheel face; 
         FIG. 18G  is a view of a cantilevered flywheel ring supported by a number of flywheel struts; 
         FIG. 19A  is a perspective view of the cupped flywheel having dimensioning; 
         FIG. 19B  is an example of the cupped flywheel having a narrow cup and wide flywheel ring; 
         FIG. 20  is an embodiment of a cupped flywheel roller drive mechanism; 
         FIG. 21  is an embodiment of the cupped flywheel having a flywheel ring having axial gears; 
         FIG. 22  is an embodiment of the cupped flywheel having a flywheel ring grinder portion; 
         FIG. 23  is an embodiment of the cupped flywheel having a flywheel ring saw portion; and 
         FIG. 24  is an embodiment of the cupped flywheel having a flywheel ring fan portion. 
     
    
    
     Throughout this specification and figures like reference numbers identify like elements. 
     DETAILED DESCRIPTION OF THE INVENTION 
     The disclosed fastening tool can have of a wide variety of designs and can be powered by a number of power sources. For example, power sources for the fastening tool can be manual, pneumatic, electric, battery, combustion, solar or use other (or multiple) sources of energy, such as battery and electric powered. The fastening can be cordless or can have a power cord. In an embodiment, the fasten can have both a cordless mode and a mode in which a power cord is used. 
     In an embodiment, the power tool can be driven by an inner rotor motor  500  and a flywheel  700  which can be a cantilevered flywheel  899 , such as a cupped flywheel  702  (e.g.  FIG. 7 ). The inner rotor motor  500  can be a brushed motor  501 , a brushless motor, or of another type. The inner rotor motor  500  can be in instant start motor and can drive an instant start flywheel and/or fastening device driver. 
     The disclosed use of the cantilevered flywheel  899 , such as the cupped flywheel  702  achieve numerous benefits, such as allowing brushed motors to be used, significant reductions in manufacturing cost, smaller and lighter power tools. In embodiments, the inner rotor motor  500  with the flywheel  700  can drive a clutch-free (clutchless) and/or transmission-free direct drive mechanism. The inner rotor motor  500  with the cantilevered flywheel  899  achieves an efficient direct drive system for a flywheel to drive action in a power tool and/or fastening device. 
     The power tool drive mechanism disclosed herein can be used with a broad variety of fastening tools, including but not limited to, nailers, drivers, riveters, screw guns and staplers. Fasteners which can be used with the magazine  100  (e.g.  FIG. 1 ) can be in non-limiting example, roofing nails, finishing nails, duplex nails, brads, staples, tacks, masonry nails, screws and positive placement/metal connector nails, rivets and dowels. 
     In an embodiment in which the fastening tool is a nailer. Additional areas of applicability of the present invention can become apparent from the detailed description provided herein. The detailed description and specific examples herein are not intended to limit the scope of the invention. This disclosure and the claims of this application are to be broadly construed. 
       FIG. 1  is a side view of an exemplary nailer having a magazine viewed from the knob-side  90  (e.g.,  FIG. 1  and  FIG. 3 ) and showing the pusher assembly knob  140 . The embodiment of  FIG. 1  shows a magazine  100  which is constructed according to the principles of the present invention is shown in operative association with a nailer  1 . In this example,  FIG. 1 &#39;s nailer  1  is a cordless nailer. However, the nailer can be of a different type and/or a power source which is not cordless. 
     Nailer  1  has a housing  4  and a motor having an inner rotor, herein as “inner rotor motor  500 ”, (e.g.  FIG. 7 ) which can be covered by the housing  4 . In the embodiment of  FIG. 1 , the inner rotor motor  500  drives a nail driving mechanism for driving nails which are fed from the magazine  100 . The terms “driving” and “firing” are used synonymously herein regarding the action of driving or fastening a fastener (e.g. a nail) into a workpiece. A handle  6  extends from housing  4  to a base portion  8  having a battery pack  10 . Battery pack  10  is configured to engage a base portion  8  of handle  6  and provides power to the motor such that nailer  1  can drive one or more nails which are fed from the magazine  100 . 
     Nailer  1  has a nosepiece assembly  12  which is coupled to housing  4 . The nosepiece can be of a variety of embodiments. In a non-limiting example, the nosepiece assembly  12  can be a fixed nosepiece assembly  300  (e.g.  FIG. 1 ), or a latched nosepiece assembly  13  (e.g.  FIG. 4 ). 
     The magazine  100  can optionally be coupled to housing  4  by coupling member  89 . The magazine  100  has a nose portion  103  which can be proximate to the fixed nosepiece assembly  300 . The magazine  100  can engage the fixed nosepiece assembly  300  at a nose portion  103  of the magazine  100  which has a nose end  102 . In an embodiment, the fixed nosepiece assembly  300  can fit with the magazine  100  by a magazine interface  380 . In an embodiment, the magazine screw  337  can be screwed to couple the fixed nosepiece assembly  300  to the magazine  100 , or unscrewed to decouple the magazine  100  from the fixed nosepiece assembly  300 . 
     The magazine  100  can be coupled to a base portion  8  of a handle  6  at a base portion  104  of magazine  100  by base coupling member  88 . The base portion  104  of magazine  100  is proximate to a base end  105 . The magazine can have a magazine body  106  with an upper magazine  107  and a lower magazine  109 . An upper magazine edge  108  is proximate to and can be attached to housing  4 . The lower magazine  109  can have a lower magazine edge  101 . 
     The magazine  100  can include a nail track  111  sized to accept a plurality of nails  55  therein (e.g.  FIG. 5 ). The nails can be guided by a feature of the upper magazine  107  which guides at least one end of a nail, such as a nail head. The lower magazine  109  can guide a portion of a nail, such as a nail tip supported by a lower liner  95 . The plurality of nails  55  can be moved through the magazine  100  towards nosepiece assembly  12  by a force imparted by contact from the pusher assembly  110 . 
       FIG. 1  illustrates an example embodiment of the fixed nosepiece assembly  300  which has an upper contact trip  310  and a lower contact trip  320 . The lower contact trip  320  can be guided and/or supported by a lower contact trip support  325 . The fixed nosepiece assembly  300  can have a nose  332  which can have a nose tip  333 . When the nose  332  is pressed against a workpiece, the lower contact trip  320  and the upper contact trip  310  can be moved toward the housing  4  which can compress a contact trip spring  330 . A depth adjustment wheel  340  can be moved to affect the position of a depth adjustment rod  350 . In an embodiment, the depth adjustment wheel  340  can be a thumbwheel. The position of the depth adjustment rod also affects the distance between nose tip  333  and insert tip  355  (e.g.  FIG. 3 ). A detail of a nosepiece insert  410  can be found in  FIG. 3 . 
     The magazine  100  can hold a plurality of nails  55  ( FIG. 6 ) therein. A broad variety of fasteners usable with nailers can be used with the magazine  100 . In an embodiment, collated nails can be inserted into the magazine  100  for fastening. 
       FIG. 2  is a side view of exemplary nailer  1  having a magazine  100  and is viewed from a nail-side  58 . Allen wrench  600  is illustrated as reversibly secured to the magazine  100 . 
       FIG. 3  is a detailed view of a fixed nosepiece with a nosepiece insert and a mating nose end of a magazine.  FIG. 3  is a detailed view of the nosepiece assembly  300  from the channel side  412  which mates with the nose end  102  of the magazine  100 . 
       FIG. 3  detail A illustrates a detail of the nosepiece insert  410  from the channel side  412 . The nosepiece insert  410  has the rear mount screw hole  417  for the nail guide insert screw  421 . Nosepiece insert  410  can also have a blade guide  415  and nail stop  420 . The driver blade  54  can extend from the drive mechanism into channel  52 . Nosepiece insert  410  can be fit to nosepiece assembly  300  and can have an interface seat  425 . Nosepiece insert  410  can also have a nosepiece insert screw hole  422  and a magazine screw hole  336 . Optionally, insert screw  401  for mounting the nosepiece insert  410  to the fixed nosepiece assembly  300  can be a rear mounted screw or a front mounted screw. Optionally, one or more prongs  437  respectively having a screw hole  336  for the magazine screw  337  can be used. In an embodiment, a nail channel  352  can be formed when the nosepiece insert  410  is mated with the nose end  102  of the magazine  100 . 
       FIG. 3  detail B is a front detail of the face of the nose end  102  having nose end front side  360 . The nose end  102  can have a nose end front face  359  which fits with channel side  412 . The nose end  102  can have a nail track exit  353 . For example, a loaded nail  53  is illustrated exiting nail track exit  353 .  FIG. 3  detail B also illustrates a screw hole  357  for magazine screw  337 . In an embodiment, nosepiece insert  410  ( FIG. 3 ) having nose  400  with insert tip  355  is inserted into the fixed nosepiece assembly  300 . 
       FIG. 4  is a side view of another embodiment of exemplary nailer  1  viewed from the knob-side  90 . In this embodiment, the nosepiece assembly  12  is a latched nosepiece assembly  13  having a latch mechanism  14 . Also in this embodiment, the magazine  100  is coupled to the housing  4  and coupled to the base  8  of the handle  6  by bracket  11 . 
       FIG. 5  is a side sectional view of the latched nosepiece assembly  13  having a nail stop bridge  83 . In an example embodiment, channel  52  can be formed from two or more pieces, e.g. nose cover  34  and at least one of groove  50  and nosepiece  28  (and/or nail stop bridge  83 ). Nosepiece  28  has a groove  50  formed therein which cooperates with the nose cover  34  (when the nose cover  34  is in its locked position). The locking of nose cover  34  against groove  50  can form an upper portion of channel  52 . The driver blade  54  can extend from the drive mechanism into channel  52 . The driver blade  54  can engage the head of the loaded nail  53  to drive loaded nail  53 . Cam  56  prevents escape of driver blade  54  from the nosepiece  28 . The nail stop bridge  83  that bridges the channel  52  engages each nail of the plurality of nails  55  as they are pushed by the pusher  112  along the nail track  111  of the magazine  100  and into channel  52 . The tips of the plurality of nails  55  can be supported by the lower liner  95 , or a lower support. 
       FIG. 6  illustrates the nail stop  420 , the nail stop centerline  427 , a longitudinal centerline  927  of the magazine  100 , a longitudinal centerline  1027  of the nail track  111 , a longitudinal centerline  1127  of the plurality of nails  55  and a longitudinal centerline  1227  of the nailer  1 .  FIG. 6  illustrates that in an embodiment having fixed nosepiece  300  having nosepiece insert  410  can be mated with the nose end  102  channel centerline  429  can be collinear with nail  1  centerline  1029 . Like reference numbers in  FIG. 1  identify like elements in  FIG. 6 . In an embodiment, the magazine  100  can have its longitudinal centerline  927  offset from a longitudinal centerline  1227  of nailer  1  by an angle G. Angle G can be 14 degrees. In an embodiment, nail stop centerline  427  can be collinear with a longitudinal centerline  927  of the magazine  100 . Additionally, in an embodiment, longitudinal centerline  927  of the magazine  100  can be collinear with a longitudinal centerline  1027  of the nail track  111 , as well as collinear with a nail stop centerline  427 . Longitudinal centerline  1127  of the plurality of nails  55  can be collinear with nail stop centerline  427 . Nail stop centerline  427  can be offset as shown in  FIG. 6  at an angle G measured from nailer  1  channel centerline  429 . In an embodiment, angle G aligns the longitudinal centerline  1027  of the nail track  111  with the centerline  1127  of the plurality of nails  55  and also nail stop centerline  427 . 
       FIG. 7  is a perspective view of the cupped flywheel positioned for assembly onto an inner rotor motor  500 .  FIG. 7  illustrates the inner rotor motor  500  having a motor housing  510  and a first housing bearing  520  which bears a rotor shaft  550  driven by an inner rotor  540  ( FIG. 10A ). In an embodiment, the motor used can alternatively be a frameless motor which does not include a motor housing, or which can have only a partial motor housing which covers part of a longitudinal length of the motor.  FIG. 7  also illustrates a flywheel  700  which is a cantilevered flywheel  899  and which in the embodiment of  FIG. 7  is the cupped flywheel  702 . The cupped flywheel  702  is shown in a disassembled state and in coaxial alignment with a rotor centerline  1400 . The cupped flywheel  702  is shown in an assembled state, for example in  FIGS. 10A and 10B . In an embodiment, the cupped flywheel  702  can have a flywheel body  710  and at least one of a flywheel opening  720  and/or a plurality of flywheel openings  720 . Herein, both a single flywheel opening and a number of flywheel openings are designated by the reference numeral “ 720 ”. There is no limitation at to the number flywheel openings which can be used. Such openings achieve a reduction and/or tailoring of the mass of the flywheel to meet structural, inertial and power consumption specifications. In an embodiment, the cupped flywheel  702  can have a flywheel ring  750  which can be a geared flywheel ring  760 . Optionally, the cupped flywheel  702  can have a flywheel bearing  770  which interfaces with the rotor shaft  550 . 
       FIG. 8  is a side view of the cupped flywheel positioned for assembly onto the inner rotor motor  500 . As illustrated in  FIG. 8 , the cupped flywheel can be positioned such that a flywheel axial centerline  1410  is collinear with a rotor centerline  1400 . In an embodiment, the cupped flywheel  702  can be frictionally attached to the rotor shaft  550  by means of fitting the flywheel bearing  770  onto a portion of the rotor shaft  550 . In other embodiments, the cupped flywheel  702  can be affixed to the rotor shaft  550  by other means, such as using a lock and key configuration, using a “D” shaped shaft portion mated with a “D” shaped portion of the flywheel bearing  770 , using fasteners such a screw, a linchpin, a bolt, a wed, or any other means which attached the cupped flywheel  702  to the rotor shaft  550 . In an embodiment, the inner rotor  540  and/or the rotor shaft  550  and the cupped flywheel  702  and/or the flywheel bearing  770  can be manufactured as one piece, or multiple pieces. 
       FIG. 9  is a front view of the cupped flywheel  702  having a number of the flywheel opening  720 . The flywheel ring  750  is shown extending radially away from the center of the cupped flywheel  702  and the flywheel bearing  770 . There is no limitation to the number of flywheel rings which can be used. Optionally, one or more flywheel rings can be located along the length of the cupped flywheel  702 . Each flywheel ring can have a contact surface to impart energy to a moveable member. Multiple flywheel rings can power multiple members, or the same member. 
       FIG. 10A  is a side view of a drive mechanism having the cupped flywheel  702  which is frictionally engaged with a driver profile  610 . In  FIG. 10A , the mating of the flywheel ring  750  with the driver profile  610  is shown. There is no limitation as to the means by which the flywheel  700  imparts energy to the driver  600 , driver profile  610  and/or driver blade  54 . In the example of  FIG. 10A , the flywheel ring  750  is a geared flywheel ring  760  having a first gear groove  783  and a second gear groove  787  which is shown in frictional contact with driver profile  610  and more specifically a first profile tooth  611  and a second profile tooth  613 . By this frictional contact, at least a portion of the rotational energy developed in the cupped flywheel  702  is imparted to the driver profile  610  propelling the driver profile through a driving action to cause the driver blade  54  born by the driver profile  610  to drive a nail  53 . 
       FIG. 10B  is a cross-sectional view of a drive mechanism having the cupped flywheel  702  which is frictionally engaged with the driver profile  610 . In  FIG. 10B , the cross-sectional view illustrates the cantilevered nature of the flywheel ring  750  over at least a portion of the inner rotor motor  500 . In an embodiment, the flywheel ring  750  can be cantilevered over the entirety of the inner rotor motor  500 , or any portion of the inner rotor motor  500 . In the embodiment of  FIG. 10B , the cup shape of the cupped flywheel  702  when coupled to the rotor shaft  550  as illustrated in  FIG. 10B  configures the flywheel ring  750  radially and in a cantilevered configuration about at least a portion of inner rotor motor  500  and/or motor housing  510  and/or rotor  540 . The flywheel ring  750  can be positioned along the rotor centerline  1400  at a position at which the flywheel ring  750  is positioned such that a portion of each of the motor housing  510 , the stator  530 , the inner rotor  540  and the rotor shaft  550  is radially within a flywheel ring inner circumference  707 . The flywheel ring inner circumference  707  can have a diameter which optionally is the same or different from the flywheel inner diameter  706 . The flywheel ring inner circumference  707  can be separated from the motor housing  510  by a flywheel motor clearance  701 . There is no limitation as to the dimension of the flywheel motor clearance  701 . The clearance  701  can be in a range of from less than a millimeter to one foot or more, such as 0.02 mm, 0.05 mm, 1 mm, 2 mm, 3 mm, 4 mm, 5 mm, 7.5 mm, 10 mm, 15 mm or 25 mm, or greater. For example, in an embodiment of a power tool the clearance can be in a range of from 0.02 mm to 10 mm can be used. In another non-limiting example for larger industrial equipment a clearance of 5 mm to 25 mm or greater, can be used. 
     In the example embodiment of  FIG. 10B , the flywheel ring inner circumference  707  can be the same as a flywheel inner circumference  709 . The flywheel inner circumference  709  can be the same or different from the flywheel ring inner circumference  707 . The flywheel inner circumference  709  can have any dimension which is separated from the motor housing  510  by a clearance. The flywheel inner circumference  709  can be at least in part over at least a portion of the inner rotor motor  500  and/or the motor housing  510 . The flywheel inner circumference  709  can at least in part radially encompass at least a part of inner rotor motor  500  and/or the motor housing  510 . 
     The driving action of the driver profile  610  can be used to drive a fastener, such as a nail  53 , into a workpiece.  FIGS. 11, 12, 12B and 13  disclose a selection of steps taking from a driving action of the driver profile  610 . The driver profile  610  can be driven by a frictional contact with the flywheel  700  which can be the cantilevered flywheel  899 . In an embodiment, the driver profile  610  can have a driver blade  54  which can be propelled to physically contact the fastener such that the fastener is driven into a workpiece. In an embodiment, the fastener can be a nail  53 . The driving action of the driver profile  610  can begin when the driver profile  610  makes contact with the flywheel  700  which can be a cantilevered flywheel  899 , such as the cupped flywheel  702 . Upon contact by the driver profile  610  with the flywheel  700 , the driver profile  610  can be propelled toward the nosepiece  12  and a fastener such as a nail  53  positioned in the nosepiece  12  for driving into a work piece. The driver profile  610  and/or the driver blade  54  can physically contact the fastener such that the fastener is driven into a workpiece. After the fastener is driven into the workpiece, the driver profile  610  can return to its resting position. In an embodiment, the driver profile  610  can be driven by means of frictional contact by the flywheel  750  of the cupped flywheel  702 . 
       FIG. 11  is a side view of a drive mechanism having the cupped flywheel  702  and a driver profile  610  which is in a resting state. In  FIG. 11 , the driver profile  610  has a portion proximate to but not touching the flywheel ring  750  of the cupped flywheel  702 . In  FIG. 11 , the driver blade  54  is shown extending from its seating in the driver profile  610  to the latched nosepiece assembly  13  and its parts, such as the nosepiece  28 . The flywheel  700  can rotate at a speed and an angular velocity. 
     Numeric values and ranges herein, unless otherwise stated, are intended to have associated with them a tolerance and to account for variances of design and manufacturing. Thus, a number is intended to include values “about” that number. For example, a value X is also intended to be understood as “about X”. Likewise, a range of Y-Z, is also intended to be understood as within a range of from “about Y-about Z”. Unless otherwise stated, significant digits disclosed for a number are not intended to make the number an exact limiting value. Variance and tolerance is inherent in mechanical design and the numbers disclosed herein are intended to be construed to allow for such factors (in non-limiting e.g., ±10 percent of a given value). Likewise, the claims are to be broadly construed in their recitations of numbers and ranges. 
     In the embodiment of  FIG. 11 , the cantilevered flywheel  899  is shown to be the cupped flywheel  702 . There is no limitation regarding the diameter or dimensions of any of the various embodiments of the flywheel  700  disclosed herein, such as the cantilevered flywheel  899  which can be the cupped flywheel  702 , or other type of cantilevered flywheel having at least a portion projecting over at least a portion of the inner rotor motor  500 . In other example embodiments, the flywheel  700  can have a number of flywheel struts  713  ( FIG. 18G ), or flywheel  700  can have a flywheel mesh structure  740  ( FIG. 18F ), or other structure. Any of the flywheels disclosed herein can have a diameter from small to quite large, such as in a range of from less than 0.5 inches to greater than 24 inches. For example cupped flywheel  702  can have a portion, such as a flywheel body portion  710  and/or a flywheel outer diameter  704  ( FIG. 19A ) having a diameter which can be 0.05 in, 1.0 in, 1.5 in, 2.0 in, 3.0 in, 4.0 in, 5.0 in, 6.0 in, 7.0 in, 8.0 in, 9.0 in, 10.0 in, 11.0 in, 12.0 in, 12.6 in, 15 in, 18 in, 24 in. The flywheel ring  750  can also have an outer diameter  751  which can be 0.05 in, 1.0 in, 1.5 in, 2.0 in, 3.0 in, 4.0 in, 5.0 in, 6.0 in, 7.0 in, 8.0 in, 9.0 in, 10.0 in, 11.0 in, 12.0 in, 12.6 in, 15 in, 18 in, 24 in. Additionally, there is no limitation to the structural supports for the flywheel ring  750 . 
     There is no limitation to the speed at which any of the many types and variations of flywheels operate. For example, any of the flywheels disclosed herein can be operated at any rotational speed in the range of from 2500 rpm to 20000 rpm, or greater. In an embodiment, cupped flywheel  702  can be operated at a rotational speed of from less than 2500 rpm to 20000 rpm, or greater. For example, cupped flywheel  702  can be operated at a rotational speed of 1000 rpm, 2500 rpm, 5000 rpm, 5600 rpm, 7500 rpm, 8000 rpm, 9000 rpm, 10000 rpm, 12000 rpm, 12500 rpm, 13000 rpm, 14000 rpm, 15000 rpm, 17500 rpm, 18000 rpm, 20000 rpm, 25000 rpm, 30000 rpm, 32000 rpm, or greater. 
     There is also no limitation to the angular velocity at which any of the many types and variations of flywheels operate. For example, any of the flywheels disclosed herein can be operated at any rotational speed in the range of from 250 rads/s to 3000 rads/s, or greater. In an embodiment, the cupped flywheel  702  can be operated at a rotational speed of from less than 250 rads/s to 3000 rads/s, or greater. For example, the cupped flywheel  702  can be operated at a rotational speed of 200 rads/s, 300 rads/s, 400 rads/s, 500 rads/s, 600 rads/s, 700 rads/s, 800 rads/s, 900 rads/s, 1000 rads/s, 1200 rads/s, 13000 rads/s, 1400 rads/s, 1500 rads/s, 1600 rads/s, 1750 rads/s, 2000 rads/s, 2200 rads/s, 2500 rads/s, 3000 rads/s, or greater. 
     There is also no limitation to the velocity of a flywheel portion and/or a portion of the contact surface  715  at which any of the many types and variations of flywheels operate. For example, any of the flywheels disclosed herein can be operated such that the velocity of a flywheel portion and/or a portion of contact surface  715  is in a range of from less than 5 ft/s to 400 ft/s, or greater. For example cupped flywheel  702  can be operated such that velocity of a flywheel portion and/or a portion of contact surface  715  is 2.5 ft/s, 5 ft/s, 7.5 ft/s, 9 ft/s, 10 ft/s, 15 ft/s, 20 ft/s, 25 ft/s, 30 ft/s, 50 ft/s, 75 ft/s, 90 ft/s, 100 ft/s, 125 ft/s, 150 ft/s, 175 ft/s, 190 ft/s, 200 ft/s, 250 ft/s, 300 ft/s, 350 ft/s, 400 ft/s, or greater. 
     There is no limitation to the mass which any of the many types and variations of flywheels disclosed herein can have. For example, any of the flywheels disclosed herein can have a mass in a range of from less than 1 oz to greater than 50 oz. For example the cupped flywheel  702  can have a mass of less than 0.5 oz, 1.0 oz, 0.75 oz, 1 oz, 2 oz, 3 oz, 4 oz, 5 oz, 7.5 oz, 9 oz, 10 oz, 12 oz, 14 16 oz, 18 oz, 20 oz, 25 oz, 30 oz, 40 oz, 50 oz, or greater. In another example, the cupped flywheel  702  can have a mass of less than 10 g, 25 g, 28 g, 50 g, 75 g, 100 g, 150 g, 200 g, 250 g, 300 g, 500 g, 750 g, 900 g, 1000 g, 1250 g, 1500 g, 2000 g, or greater. 
     There is no limitation to the inertia of any of the many types and variations of flywheels. For example, any of the flywheels disclosed herein can be operated to have any inertia in the range of from less than 10 J(kg*m{circumflex over ( )}2) to 500 J(kg*m{circumflex over ( )}2), or greater. For example cupped flywheel  702  can have an inertia of less than 5 J(kg*m{circumflex over ( )}2), 7.5 J(kg*m{circumflex over ( )}2), 10 J(kg*m{circumflex over ( )}2), 25 J(kg*m{circumflex over ( )}2), 50 J(kg*m{circumflex over ( )}2), 75 J(kg*m{circumflex over ( )}2), 90 J(kg*m{circumflex over ( )}2), 100 J(kg*m{circumflex over ( )}2), 150 J(kg*m{circumflex over ( )}2), J(kg*m{circumflex over ( )}2), 200 J(kg*m{circumflex over ( )}2), 250 J(kg*m{circumflex over ( )}2), 300 J(kg*m{circumflex over ( )}2), 350 J(kg*m{circumflex over ( )}2), 400 J(kg*m{circumflex over ( )}2), 450 J(kg*m{circumflex over ( )}2), 500 J(kg*m{circumflex over ( )}2), 600 J(kg*m{circumflex over ( )}2), or greater. 
     There is also no limitation regarding the flywheel energy which any of the many types and variations of flywheels can possess. For example, any of the flywheels disclosed herein can have a flywheel energy of any value in the range of from less than 10 j to 1500 j, or greater. For example cupped flywheel  702  can have a flywheel energy of less than 5 j, 10 j, 20 j, 50 j, 100 j, 150 j, 200 j, 250 j, 300 j, 350 j, 400 j, 450 j, 500 j, 550 j, 600 j, 650 j, 700 j, 750 j, 800 j, 900 j, 1000 j, 1100 j, 1250 j, 1500 j, 2000 j, or greater. 
       FIG. 12A  is a side view of a drive mechanism having the cupped flywheel  702  and a driver profile  610  which is in an engaged state. In  FIG. 12A , the driving process is shown at a point of the sequence in which the driver profile  610  is frictionally engaged with the cupped flywheel  702 . At this stage the cupped flywheel  702  will impart energy to the driver profile  610  which bears the driver blade  54 . This energy will propel the driver profile toward the nosepiece  12 , which in the example of  FIG. 12A  is the latched nosepiece  13 . 
     There is no limitation to the driving force which can be imparted to the driver profile  610  and/or the driver blade  54 . For example, any of the flywheels disclosed herein can impart a driving force in a range of from less than 2 j to 1000 j, or greater. For example cupped flywheel  702  can impart a driving force to the driver profile  610  and/or the driver blade  54  of less than 1 j, 2 j, 4 j, 8 j, 10 j, 15 j, 20 j, 25 j, 50 j, 75 j, 90 j, 100 j, 125 j, 150 j, 175 j, 200 j, 250 j, 300 j, 350 j, 400 j, 500 j, 1000 j, 15000 j, or greater. 
     There is no limitation to the torque generated by the inner rotor motor  500 . For example, any of the flywheels disclosed herein can be driven by the inner rotor motor  500  which can generate a torque in the range of from less than 0.005 Nm to 10 Nm, or greater. For example, the inner rotor motor  500  can generate any torque in the range of from less than 0.005 Nm, 0.01 Nm, 0.05 Nm, 0.075 Nm, 0.09 Nm, 0.1 Nm, 1.5 Nm, 2 Nm, 2.5 Nm, 3 Nm, 3.5 Nm, 4 Nm, 4.5 Nm, 5 Nm, 6 Nm, 7 Nm, 10 Nm, or greater. 
     There is no limitation to the velocity of the driver profile  610  at which any of the many types and variations of flywheels operate. For example, any of the driver profile  610  disclosed herein can be operated at any velocity in the range of from less than 10 ft/s to 400 ft/s, or greater. For a power tool and/or fastening device having the cupped flywheel  702  can have the driver profile  610  which can have a velocity of for example, 2.5 ft/s, 5 ft/s, 7.5 ft/s, 9 ft/s, 15 ft/s, 20 ft/s, 25 ft/s, 30 ft/s, 50 ft/s, 75 ft/s, 90 ft/s, 100 ft/s, 125 ft/s, 150 ft/s, 175 ft/s, 190 ft/s, 200 ft/s, 250 ft/s, 300 ft/s, 350 ft/s, 400 ft/s, or greater. 
       FIG. 12B  is a side view of a drive mechanism having the cupped flywheel and a driver which are in an engaged state and shows an embodiment in which the flywheel ring centerline plane  1600  is coplanar with the driver centerline plane  1500 .  FIG. 12B  provides a detailed illustration of the geometry of the example embodiment disclosed in  FIG. 12A . In an embodiment, a cantilevered flywheel member such as the flywheel ring  750  can be positioned along its rotational plane to have a flywheel ring center line plane  1600  coplanar to a driver centerline plane  1500 . There is no limitation to the geometries and configurations which can be used to coordinate a portion of the flywheel  700  to contact the driver profile  610 . In the embodiment shown in  FIG. 12A , the cupped flywheel  702  has a cantilevered position of a portion of cupped flywheel body  710  and flywheel ring  750  such that they are projected over at least a portion of the inner rotor motor  500 . 
     In the example of  FIG. 12B , the alignment of the flywheel ring center line plane  1600  coplanar to the driver centerline plane  1500  can further be positioned coplanar to a plane extending from the channel centerline  429  shown in  FIG. 6 . In the embodiment of  FIG. 12B , the radial centerline  1602  of the flywheel ring  750 , the driver profile centerline  1502 , driver blade centerline  1554  and the channel centerline  429  can be coplanar. 
     In an embodiment, the radial centerline  1602  of the flywheel ring  750  and the centerline of the driver profile centerline  1502  can be parallel. In an embodiment, the radial centerline  1602  of the flywheel ring  750  and the centerline of the channel centerline  429  can be parallel. In an embodiment, the driver profile centerline  1502  and the channel centerline  429  can be parallel. In an embodiment, the driver profile centerline  1502  and the driver blade centerline  1554  can be parallel. In an embodiment, the driver profile centerline  1502  and driver blade centerline  1554  can be collinear. In an embodiment, the driver profile centerline  1502 , the driver blade centerline  1554  and the channel centerline  429  can be collinear. 
     There is no limitation to the geometries that can be used regarding the coordination of the components of the drive mechanism disclosed herein. In another embodiment, the driver blade centerline  1554  can be coplanar with the flywheel ring centerline plane  1600 . This allows for many configurations of the driver blade  54  and flywheel  700  to achieve a successful driving of the driver blade  54 . In another embodiment, the driver profile centerline  1502  can be coplanar with the flywheel ring center line plane  1600 . Many configurations of the driver profile  610  and flywheel  700  can achieve a successful driving of the driver profile  610 . In another embodiment, the channel centerline  429  can be coplanar with the flywheel ring center line plane  1600 . Many configurations of the channel  52  and flywheel  700  can achieve a successful driving of a nail  53 . 
     While the embodiment of  FIG. 12B  shows the radial centerline  1602  of the flywheel ring  750  and the driver profile centerline  1502  in a coplanar arrangement, arrangements which are not coplanar can also be used. For example, configurations can be used in which the driver blade centerline  1554  is not coplanar with the radial centerline  1602  of the flywheel ring  750 . In other examples, configurations can be used in which the radial centerline  1602  of the flywheel ring  750  and the channel centerline  429  are not coplanar. In another embodiment, the driver blade centerline  1554  is not collinear with the driver profile centerline  1502 . 
     There is also no limitation to an angle of contact which generates friction and/or otherwise transfers energy between the flywheel  700  and the driver profile  610  and/or driver blade  54 .  FIG. 12B  illustrates a tangential contact between a portion of the driver profile  610  and the flywheel ring  750 . Any angle sufficient to allow a transfer of energy from the flywheel  700  to the driver profile  610  and/or directly to the driver blade  54  can be used. For example, a contact between the flywheel  700  can be configured such that the flywheel ring centerline plane  1600  intersects the driver centerline plane  1500  at an angle, such as at an angle less than 90°, or less than 67°, or less than 45°, or less than 34°, or less than 25°, or less than 18°, or less than 15°, or less than 10°, or less than 5°, or less than 3°. 
       FIG. 13  is a side view of a drive mechanism having the cupped flywheel and a driver profile  610  which has progressed in its driving action to a position striking a fastener.  FIG. 13  illustrates the driver profile  610  at a position in which is still engaged with the flywheel ring  750 , yet is near the end of its driving motion which terminates when the driver profiles motion toward the nosepiece assembly  12  ceases and the motion of profile  610  toward the nosepiece  12  stops and/or when recoil begins of the driver profile  610  back toward its original configuration as show in  FIG. 11 . Arrow  2000  indicates the direction of motion of the driver profile  610  during a driving action. 
       FIG. 14  is a side view of a drive assembly having the cupped flywheel  702 .  FIG. 14  shows an example embodiment of a nailer drive mechanism at the state in which the driver profile  610  has initially and tangentially made frictional contact with the flywheel ring  750 . This is a position analogous to that depicted in  FIG. 12 .  FIG. 14  illustrates an embodiment of the driver assembly  800  including an activation mechanism  820  which has an activation member  830  which by its movement can impart a force along the engagement axis  1800  (also illustrated in  FIG. 12B  as a +y and −y axis) which causes the driver profile  610  to come into frictional contact with flywheel  700  to effect a driving motion of driver profile  610 . The engagement movement of activation member  830  is reversible and illustrated by a double pointed engagement movement arrow  835 .  FIG. 14  also illustrates an embodiment of a driver profile return mechanism  1700  which absorbs recoil energy and guides the driver profile  610  back to its resting state, prior to another driving action. 
       FIG. 15  is a top view of a partial drive assembly having the cupped flywheel.  FIG. 15  shows the driver profile  610  at a resting state.  FIG. 15  also illustrates the parallel and/or coplanar configuration of driver profile centerline  1502 , the flywheel ring centerline plane  1600  and the driver blade centerline  1554 . 
       FIG. 16A  is a perspective view of a drive assembly having the cupped flywheel  702  shown in conjunction with the magazine  100  feeding the plurality of nails  55 .  FIG. 16A  illustrates a driver assembly  800  in conjunction with the driver profile  610  and cantilevered drive  1900 . The cantilevered drive can have an inner rotor motor  500  and the cupped flywheel  702 , as well as a geared flywheel ring  760  which can frictionally engage the driver profile  610  when activated by the activation mechanism  820 . In this example embodiment, the power tool is a nailer  1  having the latched nosepiece assembly  13  and a magazine  100  feeding a plurality of nails  55 . 
       FIG. 16B  is a sectional view of the drive assembly shown in  FIG. 16  having the cupped flywheel sectioned along the longitudinal centerline plane of the rotor shaft.  FIG. 16  illustrates a cross section of the activation mechanism  820  and driver profile  610  bearing driver blade  54 . In this embodiment, the driver profile  610  is engaged by the flywheel ring  750 . The cupped flywheel  702 , the flywheel ring  750 , the inner rotor motor  500 , the rotor shaft  550  and flywheel bearing  770  are shown in cross section.  FIG. 16B  also illustrates a bearing support ring  920  which in the cross section is shown as a ring of extra material having a thickness provided to strengthen the transition of shape (the approximate 90 degree angle) between the flywheel bearing  770  longitudinal axis and the plane of the flywheel face  703 . The bearing support ring  920  can be of a single body construction strengthening the transition of material between the bearing  770  and flywheel face  703 . 
       FIG. 17  is a sectional view of a drive assembly having the cupped flywheel  702  taken along the driver centerline plane  1500  of the driver profile.  FIG. 17  is a sectional view of the driver assembly  800  example of  FIG. 16A , which in  FIG. 17  is shown in a cross sectional view taken along the flywheel ring centerline plane  1600 . In the example of  FIG. 17 , the driver centerline plane  1500  and the flywheel ring centerline plane  1600  are shown in a coplanar configuration.  FIG. 17  illustrates an example of the alignment of the flywheel ring  750 , the driver profile  610  and the driver blade  54  in conjunction with the activation mechanism  820 . The stator  530  and inner rotor  540  of inner rotor motor  500  are shown in cross section. 
       FIGS. 18A-G  show a variety of embodiments of cantilevered flywheel designs. There is no limitation to the design of the cantilevered flywheels or regarding the means of supporting such flywheels or transferring their energy to a moveable member, such as the driver profile  610 . The various cantilevered flywheel designs can have contact surface  715 , as shown in non-limiting example in  FIGS. 18A, 20, 21, 22 and 23 . The contact surface  715  can be any portion of the flywheel which contacts another member and which imparts energy to another member. 
     The contact surface  715  in its many types and variations can impart energy to the driver profile  610  and/or driver blade  54 . The interface between the contact surface  715  and the driver profile  610  and/or driver blade  54  can have a breadth of variety. For example, the interface can produce a frictional contact (e.g.  FIG. 20 ) or a geared contact (e.g.  FIGS. 10A, 10B and 21 ). The shape of the contact surface  715  can range from flat or flattened, to rough or patterned, to having large gearing. The shape of the contact surface in an axial direction along the −x to +x axis ( FIG. 12B ) can be any shape in the range of concave to convex. Additionally, the contact surface  715  can have a surface which is sinusoidal, grooved, adapted for a lock and key interface, pitted, nubbed, having depressions, having projections, or any of a variety of topography which can adapt the contact surface  715  to impart energy to another object and/or item, such as the driver profile  610  and/or driver blade  54 , or moveable member, gear or other member. 
       FIG. 18A  is a perspective view of the cupped flywheel  702  having the geared flywheel ring  760 . In the example of  FIG. 18A , the contact surface  715  is shown as a geared surface of the geared flywheel ring  760 . In the example of  FIG. 20 , the contact surface  715  is a flattened surface which can cause another member to rotate or otherwise move. In the example of  FIG. 22 , the contact surface  715  is a grinding surface of a flywheel ring grinder portion which can remove material from another article. In the example of  FIG. 23 , the contact surface  715  is a saw tooth portion of flywheel ring saw portion  767 . In the many and varied embodiments, the contact surface  715  can be in a position cantilevered to rotate radially about at least a portion of the motor housing  510  and inner rotor motor  500 . 
       FIG. 18B  is a view of the cupped flywheel having a number of flywheel openings in the flywheel face. In the example of  FIG. 18B , a number of a flywheel openings  720  are present and pass through the flywheel face  703 . There is no limitation regarding the shape of the openings which are used with the cupped flywheel  702 . If the flywheel cup material is sufficiently thick, grooves or other features which can reduce the weight of the cupped flywheel  702  can be used whether or not an opening is created in any portion of the cupped flywheel  702 . 
       FIG. 18C  is a view of the cupped flywheel  702  having a number of flywheel slots in a flywheel body  710 . The cupped flywheel can have a flywheel slot  725  or a number of flywheel slots. Herein, a number of flywheel slots are also collectively referenced by the numeral  725 .  FIG. 18C  shows the cupped flywheel  702  which has the number of flywheel slots  725  present in the flywheel body  710 . The number of the flywheel slots  725  can reduce the weight of the flywheel  700 , achieve a desired rotation balance of the flywheel, achieve inertial specifications of the flywheel  700  and meet performance specifications for the flywheel  700 . The number of flywheel slots  725  in the cupped flywheel  702  can be used to achieve design benefits, such as weight control and improved performance, analogous to those achieved by using a number of the flywheel openings  720 , or openings of other shapes. 
       FIG. 18D  is a view of the cupped flywheel  702  having the number of slots  725  present in the flywheel body  710  as well as present in the flywheel face  703 . 
       FIG. 18E  is a view of the cupped flywheel having a number of flywheel round openings in a flywheel body  710  and flywheel face  703 . In the example of  FIG. 18E , the cupped flywheel  702  has a number of a flywheel round openings  730  present in the flywheel body  710 , as well as present in the flywheel face  703 . While  FIG. 18E  illustrates an example having a round opening, there is no limitation regarding the shape of the openings that can be used with any variety of the flywheel  700  disclosed herein. For example, openings can be round, oval, oblong, irregular, slots, decoratively shaped, patterned, or any desired shape and/or pattern. 
       FIG. 18F  is a view of the cupped flywheel having a mesh flywheel body and mesh flywheel face. There is no limitation as to the nature of the material which supports the contact surface  715  and imparts energy and/or rotational motion from the inner rotor motor  500 . Any material which supports the contact surface in a cantilevered position about at least a portion of the inner rotor motor  500  and/or the motor housing  510  can be used.  FIG. 18F  illustrates an example embodiment in which a flywheel mesh structure  740  is used to support the flywheel ring  750  having a contact surface  715  which is a geared surface. 
     This disclosure is not limited to a cup-shaped flywheel. The flywheel  700  can be any type of flywheel which supports the contact surface  715  in a cantilevered position about at least a portion of the inner rotor motor  500  and/or the motor housing  510 . 
       FIG. 18G  is a view of a cantilevered flywheel ring supported by a number of flywheel struts  713 . In the example shown in  FIG. 18G , the contact surface  715  is the surface of the geared flywheel ring  760 . In this embodiment, the geared flywheel ring  760  is supported by a number of flywheel struts  713 . In this example, the number of flywheel struts  713  can be coupled to flywheel bearing  770  which can be driven by the rotor shaft  550 . 
     There is no limitation regarding the relative geometries of the features of the cupped flywheel  702 .  FIG. 19A  is a perspective view of the cupped flywheel having dimensions. The example embodiment of  FIG. 19  illustrates the flywheel  700  which is the cupped flywheel  702  having a flywheel outer diameter  704  and a flywheel inner diameter  706 . The cupped flywheel  702  is born by the flywheel bearing  770  having a flywheel bearing length  772  and a flywheel bearing thickness  815 . In an embodiment, a bearing support ring  920  having a bearing support ring width  926  of material can be used to transition the flywheel face  703  material and the flywheel bearing  770  between a bearing support ring outer diameter  811  (also shown as support outer diameter  922 ) and the flywheel inner diameter  706 . As shown in  FIG. 19A , the bearing support ring  920  and the flywheel bearing  770  can be supported by material at an interfacing portion which can be of one body in construction and which can extend between the bearing support ring inner diameter  924  and bearing support ring outer diameter  811 . The flywheel bearing  770  can be coupled to rotor shaft  550  at an interface between flywheel bearing inner diameter  813  and rotor shaft  550  having a rotor outer diameter  552 . The cupped flywheel  702  can have a flywheel body outside diameter  708  from which a flywheel ring can extend radially in a direction away from the rotor shaft  550  and have a flywheel ring height  752  as measured in  FIG. 19A  between the flywheel outer diameter  704  and the flywheel body outside diameter  708 . The flywheel ring  750  can also have an outer diameter  751 . 
     The cupped flywheel  702  can have a flywheel length  711  which in projection can be composed of a flywheel ring length  754 , a flywheel body length  712  of flywheel body  710  and a flywheel bearing length  772 . A flywheel cup length  714  can have a length which in its projection can be composed of the flywheel ring length  754  and the flywheel body length  712 . Optionally, the flywheel bearing can be flat with the flywheel face  703 , not have a projection and not contribute to the flywheel length  711 . In other embodiments, the flywheel bearing is not used and has no contribution to the flywheel length  711 . 
       FIG. 19A  illustrates the cupped flywheel  702  having the flywheel ring  750  which has the contact surface  715  which is grooved and/or geared forming the geared flywheel ring  760 . There is no limitation to the type of gearing, grooving or surface characteristics of the contact surface  715 . In the embodiment of  FIG. 19A , the geared flywheel ring  760  has flywheel ring length  754  and a number of gear teeth. As shown in  FIG. 19A , the geared flywheel ring  760  has a first gear tooth  781  having first gear tooth width  791 , a second gear tooth  785  having second gear tooth width  795 , and a third gear tooth  789  having third gear tooth width  799 . The first gear tooth  781  can be separated from the second gear tooth  785  by a first gear groove  783  having first gear groove width  792 . The second gear tooth  785  can be separated from the third gear tooth  789  by a second gear groove  787  having second gear groove width  797 . 
       FIG. 19B  is an example of cupped flywheel having a narrow cup and wide flywheel ring.  FIG. 19B  is an example of another dimensional configuration of the cupped flywheel  702  having the flywheel ring  750 . In the embodiment of  19 B the flywheel body outside diameter  708  is less than that of the embodiment illustrated in  FIG. 19A  and the flywheel ring height  752  is greater than that of the embodiment illustrated in  FIG. 19A . Any dimension of the flywheel  700  and the cupped flywheel  702  can be set to meet any design specifications. 
     The application and use of a flywheel  700  which is a cantilevered flywheel  899 , such as cupped flywheel  702  is not limited by this disclosure. In addition to a nailer  1 , the cantilevered flywheel  899  which can be driven by an inner rotor motor  500  can be used with any power tool which can receive power from a flywheel directly or by means of a mechanism receiving power from the cantilevered flywheel  899 .  FIGS. 20 and 21  show examples to drive mechanisms which can use the cantilevered flywheel  899 .  FIGS. 22, 23 and 24  show examples types of power tool applications which can use the cantilevered flywheel  899 . Power tools which can use the technology of this disclosure include but are not limited to fastening tools, material removal tools, grinders, sanders, polishers, cutting tools, saws, weed cutters, blowers and any power tool having a motor, such as in non-limiting example an inner rotor motor, whether brushed or brushless. 
       FIG. 20  is an embodiment of the cupped flywheel roller drive mechanism. In the example of  FIG. 20 , the flywheel ring  750  is a flywheel ring having flattened contact surface  761  having the contact surface  715  which is flattened in shape and which drives a first drive wheel  897  which drives a second drive wheel  898 . 
       FIG. 21  is an embodiment of the cupped flywheel  702  having a flywheel ring  750  having axial gears. In the example of  FIG. 21 , the flywheel ring  750  is a flywheel ring having axial gears  763  which drives a gear  779 . 
       FIG. 22  is an embodiment of the cupped flywheel  702  having the flywheel ring  750  which has a flywheel ring grinder portion  765 . 
       FIG. 23  is an embodiment of the cupped flywheel  702  having the flywheel ring  750  which has a flywheel ring saw portion  767 . 
     The cantilevered flywheel  899  can be used in any appliance which can receive power from a flywheel.  FIG. 24  is an embodiment of the cupped flywheel  702  having the flywheel ring  750  which has a flywheel ring fan portion  769 . The cantilever flywheel  899  can also be used in appliances such as fans, humidifiers, computers, printers, devices with brushed inner rotor motors, devices with brushless inner rotor motors and devices with motors having outer rotors. The cantilever flywheel  899  can also be used in automobiles, trains, planes and other vehicles. The cantilever flywheel  899  can be used in any device having an inner rotor motor. 
     The scope of this disclosure is to be broadly construed. It is intended that this disclosure disclose equivalents, means, systems and methods to achieve the devices, activities and mechanical actions disclosed herein. For each mechanical element or mechanism disclosed, it is intended that this disclosure also encompass in its disclosure and teach equivalents, means, systems and methods for practicing the many aspects, mechanisms and devices disclosed herein. Additionally, this disclosure regards a motor having a cantilevered flywheel and its many aspects, features, elements uses and applications. Such a device can be dynamic in its use an operation, this disclosure is intended to encompass the equivalents, means, systems and methods of the use of the tool and its many aspects consistent with the description and spirit of the operations and functions disclosed herein. The claims of this application are likewise to be broadly construed. 
     The description of the inventions herein in their many embodiments is merely exemplary in nature and, thus, variations that do not depart from the gist of the invention are intended to be within the scope of the invention. Such variations are not to be regarded as a departure from the spirit and scope of the invention.