Patent Publication Number: US-7222557-B2

Title: Ratcheting tool driver

Description:
BACKGROUND OF THE INVENTION 
   The present invention relates to drivers for interchangeable driver bits and, in particular, to drivers of the ratcheting type. 
   Ratcheting drivers are well known, as are drivers with interchangeable bits. Conventional ratchet mechanisms for ratcheting screwdrivers, for example, have pawls that extend in the axial direction (defined by the screwdriver shaft) and that have narrow extensions engageable with teeth of a gear provided on the shaft. The pawls are pushed into and out of engagement with the gear by a control member that is usually slidable in the axial direction. Such ratchet mechanisms occupy a significant proportion of the overall length of the screwdriver. 
   One type of ratcheting driver for interchangeable bits is disclosed in U.S. Pat. No. 4,777,852. This patent discloses a ratcheting arrangement wherein a ratchet body is press-fitted into a recess in one end of a handle and a cap telescopes over the body for rotation with respect thereto. The force transmission from the cap to the pawl assembly is indirect and involves a multi-part assembly. 
   SUMMARY OF THE INVENTION 
   The present invention recognizes and addresses considerations of prior art constructions and methods. In an embodiment of the present invention a ratcheting tool driver comprises a hand-actuatable body having a first axial bore, an end face transverse to said first axial bore, a first chamber recessed from and opening into said end face and said first axial bore and a second chamber recessed from and opening into said end face and said first axial bore, said second chamber being located on an opposite side of said first axial bore from said first chamber. A socket ring disposed in, and rotatable about an axis of, the first axial bore, the socket ring defining teeth about an outer circumference thereof and defining a second axial bore that receives a tool shank in rotational driving engagement therein. A first pawl having at least one pawl tooth is disposed in the first chamber so that the first pawl is slidable transversely to the first axial bore between a first pawl first position in which the at least one first pawl tooth engages the socket ring teeth so that the first pawl blocks relative rotation between the body and the socket ring in a first rotational direction, and a first pawl second position in which the at least one first pawl tooth is disengaged from the socket ring teeth. A second pawl having at least one pawl tooth is disposed in the second chamber so that the second pawl is slidable transversely to the first axial bore between a second pawl first position in which the at least one second pawl tooth engages the socket ring teeth so that the second pawl blocks relative rotation between the body and the socket ring in a second rotational direction opposite the first rotational direction, and a second pawl second position in which the at least one second pawl tooth is disengaged from the socket ring teeth. 
   A cover is rotatably received on the hand-actuatable body and comprises an end wall defining a bore therethrough and a generally cylindrical side wall coupled to the end wall that defines a first ramped cam area and a second ramped cam area, the first and second ramped cam areas defining a plurality of cavities therein such that an end of the first and the second pawls engage the respective ramped first and second cam areas. The cover is disposed on the body so that the cover is rotatable about the body between a first position in which the first cam area engages the first pawl so that the first pawl is in the first pawl first position, and the second cam area engages the second pawl so that the second pawl is in the second pawl first position, a second position in which the first cam area engages the first pawl so that the first pawl is in the first pawl first position, and the second cam area engages the second pawl so that the second pawl is in the second pawl second position, and a third position in which the first cam area engages the first pawl so that the first pawl is in the first pawl second position, and the second cam area engages the second pawl so that the second pawl is in the second pawl first position. 
   A metal clip is received in the first and second cam areas and is shaped to abut the walls of the plurality of cavities formed in each cam area such that an end of the first and the second pawls engage the metal clip within respective ramped first and second cam areas. 
   A first spring is disposed between a wall of said first recessed chamber and said first pawl so that said first spring biases said first pawl at least one pawl tooth towards said socket ring teeth. Additionally, a second spring is disposed between a wall of said second recessed chamber and said second pawl so that said second spring biases said second pawl at least one pawl tooth towards said socket ring teeth. 
   The cover is secured to the hand-actuatable body by a snap ring received in a first annular groove formed in an outer circumference of said body and a second annular groove formed in the cover side wall inner circumference. 
   The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate one or more embodiments of the invention and, together with the description, serve to explain the principles of the invention. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
     A full and enabling disclosure of the present invention, including the best mode thereof, directed to one of ordinary skill in the art, is set forth in the specification, which makes reference to the appended drawings, in which: 
       FIG. 1  is an exploded view of a ratcheting tool in accordance with an embodiment of the present invention; 
       FIG. 2A  is a top view of a ratcheting body in accordance with an embodiment of the present invention; 
       FIG. 2B  is a perspective view of the ratcheting body as in  FIG. 2A ; 
       FIG. 3A  is a top view of the ratcheting body as in  FIG. 2A , including a ratchet ring and pawls; 
       FIG. 3B  is a perspective view of the ratcheting body as in  FIG. 3A ; 
       FIG. 4A  is a bottom view of a cover in accordance with an embodiment of the present invention; 
       FIG. 4B  is a perspective view of the cover as in  FIG. 4A ; 
       FIG. 4C  is a perspective view of the cover as in  FIG. 4B ; 
       FIG. 5A  is a top view of the ratcheting tool as in  FIG. 1 , the cover shown in phantom; 
       FIG. 5B  is a partial perspective view of the ratcheting tool as in  FIG. 1 , the cover shown in phantom; 
       FIG. 6A  is a side view of the socket ring and pawls of  FIGS. 3A and 3B  shown in a first position; 
       FIG. 6B  is a top view of the cover of  FIG. 1  shown in a position corresponding to the first position as in  FIG. 6A ; 
       FIG. 6C  is a side view of the socket ring and pawls of  FIG. 6A  shown in a second position; 
       FIG. 6D  is a top view of the cover of  FIG. 6B  shown in a position corresponding to the second position as in  FIG. 6A ; 
       FIG. 6E  is a side view of the socket ring and pawls of  FIG. 6A  shown in a third position; 
       FIG. 6F  is a top view of the cover of  FIG. 6B  shown in a position corresponding to the third position as in  FIG. 6E ; 
       FIG. 7  is a perspective view of a ratcheting tool in accordance with an embodiment of the present invention; 
       FIG. 8  is an exploded perspective view of the ratcheting tool if  FIG. 7 ; 
       FIG. 9  is a cut away view of the ratcheting tool of  FIG. 7 ; 
       FIG. 10  is a cut away view of the ratcheting tool of  FIG. 7  with the cover shown in a first position; 
       FIG. 11  is a cut away view of the ratcheting tool of  FIG. 7  with the cover shown in a second position; and 
       FIG. 12  is a cut away view of the ratcheting tool of  FIG. 7  with the cover shown in a third position. 
   

   Repeat use of reference characters in the present specification and drawings is intended to represent same or analogous features or elements of the invention. 
   DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS 
   Reference will now be made in detail to presently preferred embodiments of the invention, one or more examples of which are illustrated in the accompanying drawings. Each example is provided by way of explanation of the invention, not limitation of the invention. In fact, it will be apparent to those skilled in the art that modifications and variations can be made in the present invention without departing from the scope and spirit thereof. For instance, features illustrated or described as part of one embodiment may be used on another embodiment to yield a still further embodiment. Thus, it is intended that the present invention covers such modifications and variations as come within the scope of the appended claims and their equivalents. 
     FIG. 1  shows a ratcheting driver, in this instance a screwdriver,  10  in accordance with an embodiment of the present invention. Driver  10  includes a handle  12 , a body  14 , pawls  16  and  18 , a socket ring  20 , and a cover  22 . Handle  12  is generally cylindrical in shape and includes a first end  24  and a second end  26 . The exterior shape of handle  12  may vary as desired, and the handle may be formed from any suitable material including, but not limited to, wood, metal or metal alloy, ceramic, rubber or a polymer. Handle  12  may be knurled and/or may include a polymer or rubber coating around its periphery to increase the effectiveness of a user&#39;s grasp. Handle  12  may also include polymer inserts at angular positions of the handle to provide gripping portions for the user to securely grip the handle and apply adequate torque on a work piece. First end  24  defines an axial bore  28  of a size and shape to receive body  14 , as further described below. 
   Body  14  comprises a shaped shank portion  30  and a generally cylindrical ratcheting body  32 . Shaped shank portion  30  may be, for example cylindrical, octagonal, pentagonal, triangular, square, or any other polygonal shape or other shape that rotationally secures the body and the handle, and in one preferred embodiment, shaped shank portion  30  is hexagonal and contains one or more ribs or splines  34  on an end thereof that are received in respective corresponding grooves  36  formed in recess  28 . Splines  34 , grooves  36  and recess  28  together rotationally lock handle  12  to body  14 . Other methods may be implemented to rotationally lock handle  12  to body  14 . For example, body  14  may be press fit into handle  12 , or shank portion  30  may contain axial splines (not shown) that mate with corresponding axial grooves (not shown) formed on the inner diameter of bore  28  to thereby rotationally lock handle  12  to body  14 . Additionally, adhesive may also be used intermediate handle  12  and shank portion  30  to fixedly secure the handle to the body portion. In another embodiment of the body  14  shown in  FIGS. 2B–5B , shaped shank portion  30  is generally cylindrical in shape and has opposite flat sides  31  that are received in corresponding flats in bore  28 . The handle and the shaped shank portion can be press-fitted together or adhesive may be used to axially retain the handle to the shank portion. 
   Body  14  may be formed from any suitable material such as stainless steel, alloys or other metals and, in a preferred embodiment, is formed from zinc alloy. Shank portion  30  and generally cylindrical ratcheting body  32  define an axial bore  38  ( FIG. 2A ) adapted to receive socket ring  20 . Referring to  FIGS. 2A and 2B , a front face  40  of generally cylindrical ratcheting body  32  also defines two blind axial bores  42  and  44  that receive respective sets of springs  46  and  48  ( FIG. 1 ). Other detent means may be used instead of a spring, for example spring/pin set, a spring-loaded lever or ball, a clip spring, a nylon spring, or a self contained spring and plunger unit. 
   Referring to  FIGS. 2A–5B , generally cylindrical ratcheting body  32  defines two recessed openings  50  and  52  through its outer circumference that are recessed from and open into ratcheting body front face  40  and that receive portion of pawls  16  and  18 , respectively. Pawls  16  and  18  are rotatably mounted on a pin  54  ( FIGS. 3A and 3B ) that is received and fixed in two holes  56  and  58  ( FIGS. 2B and 3B ). Because recessed openings  50  and  52  open into front face  40 , pawls  16  and  18  may be placed into the ratcheting body during the driver&#39;s manufacture through the open front face. 
   Returning again to  FIG. 1 , pawls  16  and  18  are generally rectangular but may be formed in any suitable shape. Pawl ends  60  and  62  define pins  64  and  66 , and pawl ends  68  and  70  define respective sets of teeth  72  and  74  that interact with socket ring teeth  76  formed on socket ring  20 . Teeth  72  and  74  may be defined on an arc having a radius so that at least some of the teeth on the pawls engage with the teeth on the socket ring, or in the embodiment shown in  FIG. 1 , the teeth are generally defined over a linear surface so that most of the teeth on the pawl engage the teeth on the socket ring. The sides of pawl ends  68  and  70  proximate the socket ring bore  86  are curved to provide clearance around the socket ring. The curvature allows teeth  72  and  74  to align with socket ring teeth  76 . 
   Still referring to  FIG. 1 , bores  78  and  80  formed in pawls  16  and  18 , respectively, receive pin  54  so that the pawls are rotationally fixed about the pin in a manner that allows pawl ends  68  and  70  to be biased toward socket ring  20 . Each of pins  64  and  66  receive respective wheels  82  and  84 . Wheels  82  and  84  engage cover  22  during the operation of driver  10 , as explained in detail below. 
   Socket ring  20  is generally cylindrical in shape with an axial bore  86  ( FIG. 3B ) formed in one end. Axial bore  86  is circular in cross-section at a first end  88  and polygonal in cross-section at a second end  90  ( FIG. 1 ) to receive a polygonal-shaped tool shaft. It should be understood that axial bore  86  may be configured in any suitable shape, for example in an oval, square, rectangular or TORX cross-section, to receive and rotationally lock a suitable tool shaft to socket ring  20 . Socket ring teeth  76  are shaped to match pawl teeth  72  and  74 . Socket ring first end  88  ( FIG. 5B ) extends through a hole  92  in cover  22  when the cover is secured to the generally cylindrical ratchet body  32 . 
   The number of teeth on socket ring  20  may increase or decrease depending on the desired rotational resolution and torque loading requirements. Rotational resolution as used herein refers to the amount of angular rotation of the driver handle necessary to result in one revolution of the tool shaft. That is, a larger number of teeth on the socket ring and pawl results in a higher rotational resolution and thus a greater angular rotation of the driver handle to result in one revolution of the tool shaft. Torque loading, however, is lowered in that the increased number of teeth results in smaller teeth that are more susceptible to slippage. The opposite is true for a lower number of teeth. That is, when the number of teeth is reduced and tooth size is increased, torque loading increases since the pawl teeth are less likely to slip over the socket ring teeth. However, larger teeth result in lower resolution. Therefore, the driver&#39;s use will determine the proper balance between rotational resolution and torque loading and, in turn, the number of teeth and tooth size. Tooth size, shape and density are uniform on both the socket ring and the pawl so that the pawl teeth mesh with the socket ring teeth. 
   Referring to  FIGS. 4A–4C , cover  22  is generally cylindrical in shape and includes two outwardly extending knurled thumb grip portions  94  and  96 . A cam surface, designated generally as  98 , is formed on an inner circumference of cover  22  between thumb grip portions  94  and  96 . Cam surface  98  has one protruding portion  100  and two recessed portions  102  and  104 . Depending on the cover&#39;s rotational position with respect to the body, cam surface  98  will bias one or both of pawls  16  and  18  out of engagement with socket ring teeth  76  through wheels  82  and  84 . When wheels  82  and/or  84  are received in certain portions of respective cam recessed portions  102  and  104 , springs  46  and/or  48  ( FIG. 1 ) bias the pawl(s) so that pawl teeth  72  and/or  74  engage socket ring teeth  76 . Through-hole  92  in cover  22 , centered about a longitudinal axis  106  ( FIG. 1 ), receives axial extending portion  88  of socket ring  20  ( FIG. 5B ). 
   As shown in  FIGS. 4B and 4C , each recessed portion  102  and  104  respectively defines three arcuate recesses  102   a ,  102   b ,  102   c  and  104   a ,  104   b , and  104   c  each being recessed from protruding portion  100 . Specifically arcuate recesses  102   a  and  104   a  are stepped down an equal distance from portion  100  and recesses  102   b ,  102   c ,  104   b  and  104   c  are stepped down from recesses  102   a  and  104   a  an equal distance. Thus, recesses  102   b ,  102   c ,  104   b  and  104   c  are located at the same level. The arcuate recesses are adapted to receive wheels  82  and  84  and allow the cover to remain locked in a predetermined position without accidental movement. Thus, a predetermined torque applied to cover  22  is necessary to move the wheel(s) out of one arcuate recess and into an adjacent arcuate recess. The slope of the arcuate recesses and the spring rate of the springs define the amount of torque necessary to move cover  22  relative to ratcheting body  32 . 
   Referring to  FIGS. 2B to 5B , an annular flange  108  formed on the inner circumference of cover  22  ( FIGS. 4A–4C ) is received in a recess  110  formed on the outer circumference of ratcheting body  32  ( FIG. 2B ), thereby securing the cover to ratcheting body in the axial direction. A discontinuous flange, as shown in  FIGS. 4A–4C , allows cover  22  to be placed on ratcheting body  32  while allowing for limited relative rotation of the two components. Other methods for attachment are conceivable. For example, a flange (not shown) can be formed on the outer circumference of ratchet body  32  and a lip (not shown) formed on an inner circumference of the cover. When the cover is pushed onto the ratcheting body, the lip deflects outward over the flange and positions itself behind the flange, thereby retaining the cover on the ratchet body. In one preferred embodiment, a snap ring (not shown) is received in opposing grooves formed in the inner circumference of cover  22  and in the outer circumference of ratchet body  32 . Thus, as the cover is pressed onto the body, the snap ring deflects radially inward until the grooves align at which point the snap ring occupies a portion of each groove axially retaining the cover on the ratchet body. 
   In operation, and referring to  FIGS. 6A–6F , driver  10  applies torque to a tool shaft when a user turns handle  12  in a first direction and/or an opposite second direction. Driver  10  may also ratchet with respect to the tool shaft in either direction, depending on the position of cover  22  with respect to body  14 .  FIGS. 6A and 6B  respectively show socket ring  20  and cover  22  positioned so that arcuate recess  104   a  cams wheel  84  downward against the upward bias of spring  48  ( FIG. 1 ). In this position, pawl teeth  74  are lifted away from socket ring teeth  76 . Wheel  82 , however, is received in arcuate recess  102   c  so that spring  46  ( FIG. 1 ) biases pawl teeth  72  into engagement with socket ring teeth  76 . Thus, when a user applies torque to handle  12  in the counterclockwise direction (from the perspective shown in  FIG. 6B ) while the socket ring is rotationally fixed to a work piece, socket ring teeth  76  apply a force vector to the pawl, through the pawl teeth in a direction between pin  54  and the socket ring. The pawl thus tends to pivot about pin  54  so that the teeth are driven further into engagement with the socket ring teeth. Thus, torque is applied to the work piece in the counterclockwise direction from body  14  through the pawl and the socket ring. 
   If, however, the user rotates handle  12  in the clockwise direction when socket ring  20  is rotationally fixed to the work piece, the reaction force between the pawl teeth and the socket ring teeth causes pawl  18  to pivot about pin  54  and push against the bias of spring  46 . This compresses spring  46 , and pawl teeth  72  eventually ride over socket ring teeth  76 . Spring  46  then causes pawl teeth  72  to pivot back into the next set of socket ring teeth. The ratcheting process repeats as the operator continues to rotate handle  12  in the counterclockwise direction. 
     FIGS. 6C and 6D  show cover  22  rotated in the clockwise direction from its position in  FIGS. 6A and 6B . As cover  22  is rotated, wheel  82  rides through the arcuate recesses in recessed cam portion  102  from arcuate recesses  102   c  to arcuate recess  102   a . Likewise, wheel  84  moves from arcuate recess  104   a  to arcuate recess  104   c . In this position, the end of pawl  18  is biased downward against the upward bias of spring  46  while pawl teeth  74  are biased into operative engagement with socket ring teeth  76 . Thus, when a user applies torque to handle  12  in the clockwise direction ( FIG. 6C ) while socket ring  20  is rotationally fixed to a work piece, socket ring teeth  76  apply a force vector to the pawl, through the pawl teeth in a direction between pin  54  and the socket ring. The pawl thus tends to pivot about pin  54  so that the teeth are driven further into engagement with the socket ring teeth. As a result, torque is applied to the work piece in the counterclockwise direction from body  14  through the pawl and the socket ring. If, however, the user rotates handle  12  in the clockwise direction, and socket ring  20  is rotationally fixed to the work piece, the force vector against pawl teeth  74  causes pawl  16  to pivot about pin  54  against the bias of spring  48 . This compresses spring  48 , and pawl teeth  74  eventually ride over socket ring teeth  76 . Spring  48  once again biases the pawl end upward, thereby forcing pawl teeth  74  back into the next set of socket ring teeth. This ratcheting process repeats as the operator continues to rotate handle  12  in the clockwise direction. 
   Finally, referring to  FIGS. 6E and 6F , cover  22  is shown rotated to a position where wheels  82  and  84  are received in arcuate recesses  104   b  and  102   b , respectively. In this configuration, springs  46  and  48  bias the pawl ends upward causing both sets of pawl teeth  74  and  72  to engage socket ring teeth  76 . Consequently, socket ring  20  is rotationally fixed to handle  12  in both the clockwise and counterclockwise directions, and driver  10  applies torque to the work piece in both directions, similarly to a conventional screwdriver. 
     FIGS. 7 and 12  illustrate another embodiment of a ratcheting driver  210  of the present invention. Referring in particular to  FIGS. 7 ,  8  and  9 , driver  210  includes a handle  212 , a body  214 , pawls  216  and  218 , a socket ring  220 , and a cover  222 . Handle  212  is generally cylindrical in shape and includes a first end  224  and a second end  226 . First end  224  defines an axial bore  228  formed therein of a size and shape to receive body  214 . The exterior shape of handle  212  may vary as desired, and the handle may be formed from any suitable material including, but not limited to, wood, metal or metal alloy, ceramic, rubber or a polymer. Handle  212  may be knurled and/or may include a polymer or rubber coating around its periphery to increase the effectiveness of a user&#39;s grasp. 
   Body  214  comprises a cylindrical shank portion  230  and a ratcheting body  232 . Shank portion  230  may contain one or more flat portions  234  that are received between respective corresponding radial ribs  236  to thereby rotationally lock handle  212  to body  214 . Other methods may be implemented to rotationally lock handle  212  to shank portion  230 . For example, body  214  may be press fit into handle  212 , or shank portion  230  may contain ribs or splines (not shown) that mate with corresponding ribs or splines formed on the inner diameter of bore  228  to thereby rotationally lock handle  212  to shank  230 . Handle  212  may be axially locked to body  214  through frictional force, adhesive, or as shown in  FIG. 8 , by a flange (not shown) formed on the inner diameter of handle bore  228  and a recess  238  formed in shank portion  230 . A cap  240  is press-fitted in handle end  226  to close off the end of the handle. 
   Ratcheting body  232  may be formed from any suitable material such as stainless steel, alloys or other metals polymers or ceramics and, in a preferred embodiment, is formed from zinc alloy. Ratcheting body  232  defines an axial bore  242  formed therein and adapted to receive socket ring  220 . A front face  244  defines two recessed chambers  246  and  248  that are recessed from and open into ratchet body front face  244  and receive pawls  216  and  218 , respectively ( FIG. 10 ). Because the chambers open into the front face, pawls  216  and  218  may be placed during the driver&#39;s manufacture through the open front face  244 . Chambers  246  and  248  are closed at one transverse end  250  and  252  but open at the other ( FIG. 10 ). Chambers  246  and  248  are generally rectangular in shape but may also be formed in other shapes corresponding to the shape of pawls  216  and  218 . 
   Referring to  FIG. 10 , pawls  216  and  218  are generally rectangular but may be formed in any suitable shape. Pawl ends  254  and  256  form notches  258  and  260 , and arches  262  and  264  formed on the pawls&#39; inner sides  266  and  268  have first ends that define respective sets of teeth  270  and  272  that correspond in shape and size to teeth  274  formed on the outer periphery of socket ring  220 . Teeth  270  and  272  are defined on an arc having a radius that corresponds to the radius of the socket ring  220  so that the teeth on the pawls fit snugly with the teeth on the socket ring. It should be understood that the teeth on the pawl may instead be formed over an arc having a radius that is slightly larger than the radius of the socket ring teeth. 
   Blind bores  276  and  278  formed in pawls  216  and  218 , respectively, receive springs  280  and  282  that bias pawls  216  and  218  in the outward direction from recesses  246  and  248  so that pawl teeth  270  and  272  are biased toward socket ring teeth  274 . Each of notches  258  and  260  defines a stopper face  284  and a slider face  286 . Stopper face  284  and slider face  286  engage cover  222  during the operation of driver  210 , as explained in detail below. 
   Referring to  FIGS. 8 and 10 , socket ring  220  is generally cylindrical in shape with an axial bore  288  ( FIG. 10 ) formed in one end. Axial bore  288  may be polygonal in cross-section to receive a polygonal-shaped tool shaft. It should be understood that axial bore  288  may be configured in any suitable shape, for example in an oval, square, rectangular, circle or TORX cross-section, to receive and rotationally lock a suitable tool shaft to socket ring  220 . Socket ring teeth  274  are shaped to match pawl teeth  270  and  272 . An annular end portion  290  extends through a hole  292  in cover  222  when cover  222  is secured to the ratchet body  232  by a snap ring  293  received in a groove  294  formed in ratchet body  232  ( FIGS. 8 and 9 ). 
   The number of teeth on socket ring  220  may increase or decrease depending on the desired rotational resolution and torque loading requirements. That is, a larger number of teeth on the socket ring and pawl results in higher rotational resolution. Torque loading, however, is lowered in that the increased number of teeth results in smaller teeth that are more susceptible to slippage or shearing. The opposite is true for a lower number of teeth. That is, when the number of teeth is reduced and tooth size is increased, torque loading increases since the pawl teeth are less likely to slip over the socket ring teeth. However, larger teeth result in lower resolution. Therefore, the driver&#39;s use will determine the proper balance between rotational resolution and torque loading and, in turn, the number of teeth and tooth size. Tooth size, shape and density are uniform on both the socket ring and the pawls so that the pawl teeth mesh with the socket ring teeth. 
   Referring to  FIG. 10 , cover  222  is generally cylindrical in shape and includes two recessed areas  296  and  298  that are mirror images of each other and that receive a metal clip  300 . Clip  300  snugly fits into the recesses and is shaped to match the contour of the recessed areas. Thus, depending on the cover&#39;s rotational position with respect to the ratchet body, the recessed areas respectively engage pawl ends  254  and  256 . That is, when pawl ends  254  and/or  256  move through its respective recessed areas, springs  280  and  282  can bias the pawls so that pawl teeth  270  and/or  272  engage socket ring teeth  274 . Through-hole  292  in cover  222  ( FIG. 9 ), centered about a longitudinal axis  302  ( FIG. 9 ), receives axial extending portion  290  of socket ring  220  ( FIG. 9 ). Ratchet body  232  also has two stop faces  304  and  306  ( FIG. 10 ) that engage stops  308  and  310  formed in cover  222  to prevent the cover from over rotating with respect to ratchet body  232 . 
   In operation, driver  210  applies torque to a tool shaft when a user turns handle  212  in a first direction and/or an opposite second direction. Driver  210  may also ratchet with respect to the tool shaft in either direction, depending on the position of cover  222  with respect to ratchet body  232 .  FIG. 10  shows cover  222  positioned so that ramped cavities  312  and  314  align with and receive pawl ends  254  and  256 , respectively. In this position, springs  280  and  282  bias pawls  216  and  218  upward so that pawl end  254  and  256  are received in cavities  312  and  314 . The spring bias causes sliding portions  286  to engage with metal clip  300 . Thus, when a user applies torque to handle  212  in the clockwise direction (with respect to  FIG. 10 ) while the socket ring is rotationally fixed to a workpiece, socket ring teeth  274  apply a counterclockwise reaction force to pawl teeth  272 . This wedges pawl  218  between the socket ring and the back surface of pawl chamber  248 , and torque is thereby applied to the workpiece in the clockwise direction from body  214  through the pawl and the socket ring. The same holds true when the handle is turned in the counterclockwise direction while the socket ring is rotationally fixed to a workpiece. That is, the socket ring teeth  274  apply a clockwise reaction force to pawl teeth  272  causing pawl  216  to wedge between the socket ring and the back surface of pawl chamber  246 , and torque is thereby applied to the workpiece in the counterclockwise direction. 
   Referring to  FIG. 11 , cover  222  is shown positioned such that ramped cavity  316  receives pawl end  254  and ramped cavity  322  cams pawl end  256  downward. That is, because ramped cavity  316  receives pawl end  254 , spring  280  biases pawl  216  upward such that pawl teeth  270  engage socket ring teeth  274 . Likewise, because ramped cavity  322  cams pawl end  256  downward against the upward bias of spring  282 , pawl teeth  272  disengage from socket ring teeth  274 . As a result, when a user applies torque to handle  212  in the counterclockwise direction (from the perspective shown in  FIG. 11 ) while the socket ring is rotationally fixed to a work piece, socket ring teeth  274  apply a clockwise reaction force to pawl teeth  270  thereby wedging pawl  216  between the socket ring and the back surface of pawl chamber  246 . As a result, torque is thereby applied to the work piece in the counterclockwise direction from handle  212  through the ratchet body, the pawl and the socket ring. 
   If, however, the user rotates handle  212  in the clockwise direction when socket ring  220  is rotationally fixed to the work piece, the reaction force causes pawl  216  to push against the bias of spring  280 . This compresses spring  280 , and pawl teeth  270  eventually ride over socket ring teeth  274 . Spring  280  then pushes pawl  216  upward, forcing pawl teeth  270  back into the next set of socket ring teeth. The ratcheting process repeats as the operator continues to rotate handle  212  in the clockwise direction. 
   Referring to  FIG. 12 , cover  222  is shown rotated counterclockwise to a predetermined position where pawl end  254  is received in ramped cavity  320  and pawl end  256  is received in ramped cavity  318 . That is, because ramped cavity  320  receives pawl end  254 , the walls of ramped cavity  320  bias pawl  216  downward such that pawl teeth  270  disengage from socket ring teeth  274 . Contrary to pawl  216 , because ramped cavity  322  allows pawl end  256  to move upward from the bias of spring  282 , pawl teeth  272  engage socket ring teeth  274 . As a result, when a user applies torque to handle  212  in the clockwise direction (from the perspective shown in  FIG. 12 ) while the socket ring is rotationally fixed to a work piece, socket ring teeth  274  apply a counterclockwise reaction force to pawl teeth  272  thereby wedging pawl  218  between the socket ring and the back surface of pawl chamber  248 . As a result, torque is thereby applied to the work piece in the clockwise direction from handle  212  through the ratchet body, the pawl and the socket ring. 
   If, however, the user rotates handle  212  in the counterclockwise direction when socket ring  220  is rotationally fixed to the work piece, the reaction force causes pawl  218  to push against the bias of spring  282 . This compresses spring  282 , and pawl teeth  272  eventually ride over socket ring teeth  274 . Spring  282  then pushes pawl  218  upward, forcing pawl teeth  272  back into the next set of socket ring teeth. The ratcheting process repeats as the operator continues to rotate handle  212  in the counterclockwise direction. 
   Cover  222  is retained in each rotational position by the reaction forces exerted by the springs between the pawl ends and the ramped cavities. That is, the geometry of the ramped cavities  312 ,  314 ,  316 ,  318 ,  320  and  322  determines the amount of rotational torque necessary to move cover  222  with respect to ratcheting body  232 . The steeper the ramped cavities the higher the torque necessary to rotate the cover. Additionally, the amount of torque may also be affected by the spring rate of springs  280  and  282 . The higher the rate, the greater the torque necessary to move the cover relative to the ratcheting body. 
   While one or more preferred embodiments of the invention have been described above, it should be understood that any and all equivalent realizations of the present invention are included within the scope and spirit thereof. The embodiments depicted are presented by way of example only and are not intended as limitations upon the present invention. Thus, it should be understood by those of ordinary skill in this art that the present invention is not limited to these embodiments since modifications can be made. Therefore, it is contemplated that any and all such embodiments are included in the present invention as may fall within the scope and spirit thereof.