Abstract:
This invention relates to bi-directional ratcheting socket wrenches having two modes of operation that can be used independently or simultaneously and having only one ratchet mechanism. This invention can rotate a work piece by being rotated around the socket axis as is common to socket wrenches, the handle can be rotated around its axis or the two motions can be combined as one fluid motion. This can be accomplished in either direction of rotation while permitting the ability to reposition the wrench and/or the handle. Again, this is achieved using a single ratchet mechanism. This invention also provides a means to lock the handle in position relative to the wrench itself, a means to sufficiently retain the handle without impeding handle rotation, a means to mount the handle on a bearing and a means to provide alternative embodiments of the wrench to further increase its usefulness in confined areas.

Description:
FIELD OF INVENTION 
   The present invention relates to a socket wrench and its preferred embodiments having two modes of operation that can be employed independently or simultaneously, having a lockable handle and having a single ratchet mechanism. 
   BACKGROUND OF THE INVENTION 
   Considerable effort has been spent trying to perfect a socket wrench having two modes of operation that can be used independently or simultaneously. Some factors that have greatly limited the success of these efforts are ratchet mechanism location, the type of ratchet mechanism used and handle mounting and retention. 
   The prior art of Singleton (U.S. Pat. No. 4,907,476) is an example of ratchet mechanism location effecting handle and ratchet mechanism operation. In that prior art, the ratchet mechanism is in the head, allowing the wrench to be rotated and repositioned as is a common socket wrench, but the t-handle can only be rotated in one direction and not repositioned. This is due to the fact that the ratchet mechanism in the head only allows rotation in one direction relative to the head. When the t-handle is turned, the ratchet pawls disengage to allow rotation relative to the head but when attempting to reposition the t-handle in the other direction, the ratchet pawls now engage, blocking rotation. This also means that when using the socket wrench in the common manner, anytime the socket rotates relative to the head (i.e. repositioning), it causes the t-handle to rotate again. Several prior art attempts have been made to improve this situation by adding a second ratchet mechanism, including Gegg (U.S. Pat. Nos. 3,952,617 and 5,201,255) and Scott (U.S. Pat. No. 4,474,089). This resulted in wrenches of great complexity and a high number of custom parts that can have a detrimental impact on assembly and production. Further, the prior art of Cockman, Jr. (U.S. Pat. No. 4,406,184) teaches that by locating a single ratchet mechanism in the handle, completely disconnected from the head, two modes of operation can be achieved simultaneously, making a second ratchet mechanism unnecessary. 
   While Cockman, Jr. (U.S. Pat. No. 4,406,184) taught ratchet mechanism location, its efforts to provide sufficient means to retain the handle had questionable results at best. A handle that is required to move along the longitudinal axis of the socket wrench to lock, it seems, could just as easily become unlocked when the forces applied to the handle are not completely perpendicular to the handle. This situation may cause the handle to suddenly come unlocked, the handle retaining screw to impact the side of its slot, subjecting it to considerable side loads, and more likely than not causing eventual failure of the handle retaining screw. 
   It is apparent that some have tried to overcome these obstacles by what amounts to interconnecting a right-angle driver extension to a type of ratcheting screwdriver. Again, handle retention becomes a significant problem. The methods employed to retain a screwdriver handle are designed to deal with rather small rotational forces and quickly fail when placed under heavy side loading. It would appear that some have tried to downplay the issue. Prior art Huang (U.S. Pat. No. 7,069,818), Gegg (U.S. Pat. No. 5,201,255), Scott (U.S. Pat. No. 4,474,089) and Cockman, Jr. (U.S. Pat. No. 4,406,184), to name a few, all lack, in this writers opinion, a quickly discernable, proven method of handle retention that is capable of withstanding the loads encountered when using a socket wrench in the described manners. 
   Another problem with the ratcheting screwdriver solution is the selection of ratchet mechanisms. Typically, a socket wrench contains a ratchet mechanism able to endure greater loads than any found in a ratcheting screwdriver. The ratchet mechanisms typically found in socket wrenches also have a greater number of teeth meaning that the socket wrench can be rotated and repositioned in as little as six to nine degrees of movement. A typical ratcheting screwdriver may require eighteen degrees of movement to be repositioned. This situation becomes apparent in prior art Huang (U.S. Pat. No. 7,069,818), forcing the use of gear reduction in the head to compensate for this predicament. 
   Another problem to consider is deflection and/or bending. When side loading the handle, if the load is conveyed directly to the drive shaft or some type of coupling device, there is a great possibility that the shaft or coupler will become jammed, distorted or bent, leaving the tool inoperable. Obviously, a socket wrench of the type described, needs some form of structure to withstand the loads encountered in everyday use. 
   Prior art Cockman, Jr. (U.S. Pat. No. 4,406,184) also taught the use of a means to lock the handle in position relative to the wrench itself. Because the handle and the ring gear for the ratchet mechanism rotate as one, when the tool is rotated around the axis of the socket to input torque in common fashion, the ratchet mechanism pawl engages the ring gear causing the handle to rotate in the opposite direction of the tool itself. Under relatively light loads this tendency can be opposed manually simply by the user holding the handle in position but under heavier loads there is a need to mechanically hold the handle in position. Again, a handle that is able to move along the axis of the wrench, it seems, could easily become disengaged from the desired setting, having a severe impact on tool function. 
   SUMMARY OF THE INVENTION 
   Thus, the invention is a ratcheting socket driver capable of two modes of socket rotation that can be used independently of one another or simultaneously. The first mode of socket rotation is to rotate the entire tool around the working axis of the socket, as is common to most socket wrenches, and then to reposition the tool back to a certain point, repeating the process as necessary to progress the work piece. The second mode of socket rotation is to rotate the handle of the tool around the longitudinal axis of the tool, similar to using a screwdriver, and then to reposition the handle back to a certain point, again repeating this process as necessary. Either of these two modes of operation can be used one at a time or combined in any ratio to progress the work piece. 
   The invention also includes a movable handle-locking device. 
   The invention also includes a hub assembly for the purpose of allowing the handle to be rotatably mounted to the body of the tool. 
   In another preferred embodiment, the hub assembly would include a bearing for the purpose of reducing friction and drag. 
   In another preferred embodiment, the invention also includes a bevel gear set with a ratio of greater than 1:1. This means the handle to socket ratio could be increased to gain a mechanical advantage. 
   In another preferred embodiment, the invention includes an articulated head and drive shaft. This means the head could be rotated somewhat off axis along a plane. 
   In another preferred embodiment, the invention includes a head having its axis offset from that of the handle. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
       FIG. 1  is a full isometric view of socket wrench  10  with handle  25  locked. 
       FIG. 2  is an exploded isometric view of socket wrench  10  and its parts. 
       FIG. 3  is a top view of socket wrench  10  with handle  25  locked. 
       FIG. 4  is a sectional view of socket wrench  10  per section lines  4 - 4  of  FIG. 3 . 
       FIG. 5  is a full isometric view of socket wrench  10  with handle  25  unlocked and integral head  17  and body  20 . 
       FIG. 6  is a sectional view of socket wrench  10  per section lines  6 - 6  of  FIG. 5 . 
       FIG. 7  is a section of the anterior portion of handle  25  per section line  7 - 7  of  FIG. 5  with ratchet assembly  35  installed. 
       FIG. 8  is a section of the anterior portion of handle  25  per section line  7 - 7  of  FIG. 5  with exploded view of ratchet assembly  35 . 
       FIG. 9  is a posterior end view of lock collar  22  with 6-point lock cavity. 
       FIG. 10  is a posterior end view of lock collar  22  with 12-point lock cavity. 
       FIG. 11  is a sectional view of lock collar  22  per section line  11 - 11  of  FIG. 9 . 
       FIG. 12  is a sectional view of lock collar  22  per section line  12 - 12  of  FIG. 10 . 
       FIG. 13  is an exploded view of hub-retainer assembly and its parts. 
   

   DETAILED DESCRIPTION 
   Drawings and descriptions combine to refer to socket wrench  10  ( FIG. 1 ) that is the invention. Anterior refers to end nearest the right-hand margin as drawn. Posterior refers to the distal end. 
   Three of the main parts of socket wrench  10  are body  20  ( FIGS. 2 and 4 ), head  17  and handle  25 . Head  17  is either permanently mounted in a fixed position to the anterior end of body  20  (FIGS.  1 , 2 , 3  and  4 ) or is an integral part of body  20  ( FIGS. 5 and 6 ). Handle  25  is rotatably mounted to the posterior end of body  20 . 
   Body  20 , is an elongated tube, having a hollow, circular interior section running through its length, open at both ends. Posterior end of body  20  has as some of its exterior portions, a threaded segment corresponding to lock nut  30  and a grooved keyway corresponding to inside tab washer  29 . The anterior end has as some of its portions, an enlarged circular opening that forms a cavity corresponding to the hub of second miter gear  15 . Body  20  also has as one of its integral parts lock collar chassis  19 . As drawn, lock collar chassis  19  is hexagon-shaped but could be any shape that prevents lock collar  22  from rotating around the longitudinal axis of body  20 . Lock collar chassis  19  is positioned near the mid-point along the length of body  20 . The narrowest width of lock collar chassis  19  is greater than the outside diameter of the posterior portions of body  20 . Lock collar chassis  19  has two semi-circular detents on one of its sides in correspondence with ball detent assembly  21 . Body  20  also has as one of its integral parts lock collar stop  18  conjoined to the anterior end of lock collar chassis  19 . Lock collar stop  18  has a diameter equal to and/or somewhat greater than the width of lock collar chassis  19 . Where the diameter of lock collar stop  18  is greater than the width of lock collar chassis  19 , lock collar stop  18  forms a shoulder, thus limiting the forward travel of lock collar  22  along lock collar chassis  19 . 
   The interior portions of head  17  are formed by two interconnected, asymmetrical cylindrical cavities at right angles to one another. The smaller posterior cavity is formed to correspond to the anterior end of body  20 . The larger cavity is formed to enclose drive collar  11 , first miter gear  13 , second miter gear  15  and centering stud  14 . In proximity to the upper rim of the larger cavity is formed an annular groove corresponding to inside snap ring  12 . A portion of the upper posterior side of the larger cavity is removed, to form a flattened segment, to allow for proper installation and function of inside snap ring  12 . A centering hole is formed on the bottom, interior face of the larger cavity corresponding to centering stud  14 . 
   Handle  25  is cylindrical, with rounded sides and asymmetrical circular openings at each end, with hollowed interior portions. The hollowed interior portions of handle  25  vary in diameter to form shoulders to support hub  27  and ring gear  33 . The largest cavity corresponding to ring gear  33  also has two or more semi-circular grooves formed into its walls corresponding to anti-rotation pins  34 . The grooves are formed in straight lines parallel to the longitudinal axis of handle  25 . The grooves are formed to a depth of one-half the diameter of anti-rotation pins  34 . The ring gear cavity also has an annular groove formed into its walls corresponding to spiral snap ring  36 . 
   As drawn, handle key  24  is hexagon-shaped, identical in size and shape to lock collar chassis  19 , and is an integral part of handle  25 . Handle key  24  has a circular opening at its anterior end forming a cavity that interconnects with the hollowed interior portions of handle  25 . 
   Lock collar  22  is cylindrical, with rounded sides and asymmetrical openings at each end, with hollowed interior portions. The posterior end has a circular opening forming a cylindrical interior cavity. The anterior end has a hexagon-shaped opening forming a hexagonal interior cavity that interconnects with the posterior end cylindrical cavity. The shape and size of the hexagonal cavity directly corresponds to the shape and size of the exterior portions of lock collar chassis  19 . Ball detent assembly  21  is installed to correspond to detents on lock collar chassis  19 . Lock collar  22  provides a means to, when desired, rigidly connect handle  25  to body  20  to prevent handle  25  from rotating around the longitudinal axis of body  20 . In another preferred embodiment ( FIG. 10 ,  12 ), lock collar  22  would have a third, double-hexagon-shaped, interior cavity formed to correspond to handle key  24 . The cavity, being similar to the interior portions of a common twelve-point socket, allows for twelve possible handle-locking positions rather than six possible handle locking positions of the previous embodiment ( FIGS. 9 ,  11 ). 
   Thrust washer  23  is a standard friction reducing, flat type washer commonly known and is installed to prevent deterioration of parts through normal use. 
   Hub  27  is cylindrical, with rounded sides, an annular, posterior flange and symmetrical circular openings at each end to form hollowed, circular interior portions. Hub  27  provides a means to transfer loads from handle  25  to body  20  and, through bearing washer  28  and tab washer  29 , to lock nut  30 . In another preferred embodiment, the hollowed, circular interior portions are enlarged to accept a corresponding bearing assembly insert. The bearing assembly insert is installed to reduce unnecessary friction and part deterioration. 
   Bearing washer  28  is similar to a standard flat type washer. It has a center hole with at least two additional, smaller holes formed through its flange. The smaller holes are formed symmetrically spaced around the circumference of the center hole. The diameter of the smaller holes through the flange is somewhat greater than the thickness of bearing washer  28 . A single ball bearing, also with a diameter greater than the thickness of bearing washer  28  and corresponding to that of the smaller hole, is installed into each of the smaller holes. When hub  27  rotates, the ball bearings are rolled between hub  27  and inside tab washer  29  and rotate bearing washer  28  as necessary, keeping equal spacing between the ball bearings. Bearing washer  28  allows hub  27  and handle  25  to rotate around body  20  while inside tab washer  29  and most importantly lock nut  30  remain stationary relative to body  20 . 
   Inside tab washer  29  is a standard internal key type flat washer as is commonly known. 
   Lock nut  30  is a standard rotation-resistant type threaded fastener as is commonly known. 
   Drive shaft  31  is an elongated rod, with rounded sides and fixtures formed at each end. The anterior end of drive shaft  31  forms a spindle corresponding to the hub of second miter gear  15  and with a threaded circular cavity corresponding to second miter gear retainer  16 . At the posterior end, drive shaft  31  forms a square drive receiver corresponding to the drive stem portion of ratchet mechanism  35 . 
   Ring gear  33  is cylindrical, with rounded sides and symmetrical openings at each end, and with hollowed, circular interior portions. As is common of inside type ring gears found in many socket wrenches, the interior portions of ring gear  33  have a certain number of teeth of a particular size and shape. The size, shape and number of teeth of ring gear  33  correspond to the particular chosen ratchet mechanism. The exterior portions of ring gear  33  have two or more semi-circular grooves formed into its sides corresponding to anti-rotation pins  34 . The grooves are formed in straight lines parallel to the longitudinal axis of ring gear  33  and are formed to a depth of one-half the diameter of anti-rotation pins  34 . The posterior opening has an annular recess corresponding to posterior flange portion of ratchet mechanism  35 . 
   Ratchet mechanism  35  is a standard, bi-directional torque transfer type of assembly as is found in many socket wrenches. 
   Drive collar  11  is circular, with rounded sides, a flat bottom end, and a socket drive stem formed at the top end. The circular portion has two round segments, top and bottom, with the bottom segment having a somewhat smaller diameter and an annular groove corresponding to inside snap ring  12 . The bottom end of drive collar  11  has a hexagon-shaped interior cavity corresponding to the hub of first miter gear  13 . The cavity has a threaded hole centered within it corresponding to centering stud  14 . 
   First miter gear  13  is a standard beveled type cog as is commonly known. The exterior portions include a hexagon-shaped hub, with six flat sides and a hollow interior, formed to correspond to the interior portions of the hexagon-shaped cavity in the bottom end of drive collar  11 . The shape of the hub prevents rotation of first miter gear  13  relative to drive collar  11 . 
   Second miter gear  15  is a standard beveled type cog as is commonly known. The exterior portions include a circular hub, with rounded sides and a hollow interior, corresponding to the spindle of drive shaft  31 . 
   Centering stud  14  is a solid hexagonal rod, with six flat sides and fixtures formed at each end. The top end has a rounded, threaded portion and the bottom end has a semi-circular portion corresponding to the centering hole on the bottom, interior face of head  17 . 
   Ball detent assembly  21  is a standard spring loaded ball assembly as is commonly known and is used in conjunction with detents on lock collar chassis  19  to retain lock collar  22  in desired locked or unlocked position. 
   In another preferred embodiment (not drawn), body  20  and drive shaft  31  are articulated in proximity to head  17 , permitting head  17  a limited degree of movement, up or down, off the longitudinal axis of body  20 . This form of articulation is common to a certain type of socket wrench and is sometimes referred to as a flexible head or swivel head socket wrench. 
   In another preferred embodiment (not drawn), the longitudinal axis of handle  25  is not aligned with head  17  in the previous manner, but is offset a certain amount forming a curved portion of body  20 . Drive shaft  31  could be formed using an assembly of tightly wound wire strands (i.e. wire rope) or by using a chain-link type of assembly. This form of misaligning the handle is common to a certain type of socket wrench and is sometimes referred to as offset-handle socket wrenches. 
   In another preferred embodiment (not drawn), first miter gear  13  has a greater number of teeth than second miter gear  15 , giving handle  25  a gear ratio of greater than 1:1 over the drive collar assembly. When handle  25  is rotated to effect rotation of the work piece, this increased ratio allows greater torque output than possible in the previous embodiment. This form of gear reduction is sometimes referred to as a torque multiplier. 
   To assemble, the anterior end of body  20  is permanently attached in a fixed position to head  17 . This step is not necessary when head  17  and body  20  are integral ( FIG. 5 ,  6 ). Lock collar  22  is mounted over the posterior end of body  20  and is installed onto lock collar chassis  19  with ball detent assembly  21  aligned with the detents on lock collar chassis  19 . Thrust washer  23  is mounted over the posterior end of body  20  and installed against lock collar chassis  19 . Handle  25  is mounted over the posterior end of body  20  and installed against thrust washer  23 . Hub  27  is mounted through the posterior opening of handle  25 , over the posterior end of body  20  and installed against the shoulder formed on the interior of handle  25 . Bearing washer  28  is mounted, with ball bearings in place, through the posterior opening of handle  25 , over the posterior end of body  20 , and installed against hub  27 . Inside tab washer  29 , with tab aligned to keyway, is mounted, through the posterior opening of handle  25 , over the posterior end of body  20 , and installed against bearing washer  28 . Lock nut  30  is mounted through the posterior opening of handle  25 , and installed onto threaded portion of body  20 , and is tightened as necessary. Drive shaft  31  is installed through the posterior opening of handle  25  and into the posterior opening of body  20 , and is positioned so that the anterior end spindle extends into head  17 . Second miter gear  15  is installed through the larger cavity of head  17 , mated to the spindle on the anterior end of drive shaft  31  and retainer screw  16  is installed. Ratchet mechanism  35  is installed into ring gear  33  and retained with snap ring  32  to form a ratchet assembly. The ratchet assembly is installed into posterior opening of handle  25  and ratchet mechanism  35  drive stem is mated to the receiver of drive shaft  31 . With the semi-circular grooves of ring gear  33  aligned with the semi-circular grooves of handle  25 , anti-rotation pins  34  are installed into the cavities formed at the grooves. Spiral snap ring  36  is installed into annular groove within posterior opening of handle  25 . First miter gear  13  hub is installed into the cavity at the bottom end of drive collar  11  and centering stud  14  is installed to form a drive collar assembly. Inside snap ring  12  is installed into annular groove in drive collar  11  and drive collar assembly is rotatably installed into the larger cavity of head  17  and retained by inside snap ring  12 . 
   To operate socket wrench  10 , choose either right-hand (clockwise) or left-hand (counter-clockwise) work-piece rotation using the ratchet mechanism  35  selector switch at the posterior end of handle  25  ( FIG. 7 ). Next, chose handle  25  either locked, unable to rotate around the longitudinal axis of body  20 , or unlocked with handle  25  able to rotate relative to body  20 . Locking handle  25  allows higher torque input by mechanically opposing rotation of handle  25 . To lock handle  25 , lock collar  22  is moved toward the posterior detent while rotating handle  25  to align handle key  24  with lock collar  22  and lock collar chassis  19 . When alignment is achieved, lock collar  22  engages handle key  24  while still engaged to lock collar chassis  19 , locking handle  25  in position relative to body  20  and ball detent assembly  21  engages posterior detent. 
   With the selector switch in the right-hand rotation position and handle  25  locked, socket wrench  10  functions in the same manner as many common socket wrenches. By rotating socket wrench  10  in a right-hand direction around the rotational axis of the work-piece, in the common manner, torque is conveyed from body  20  and lock collar  22  through handle  25  to ring gear  33 . Ring gear  33  is engaged by ratchet mechanism  35  pawls and torque is conveyed through ratchet mechanism  35  to drive shaft  31 . Drive shaft  31  conveys this torque through second miter gear  15  to first miter gear  13 . First miter gear  13 , being mounted in a fixed position to drive collar  11 , conveys this torque through the drive collar assembly to the work-piece, thus causing the work-piece to rotate in the right-hand direction. No parts rotate relative to body  20 , head  17  and handle  25 . 
   Rotating socket wrench  10  in the opposite direction, in the common manner, the pawl of ratchet mechanism  35 , as intended, is disengaged from ring gear  33 . This permits ratchet mechanism  35 , drive shaft  31 , second miter gear  15 , drive collar assembly and work-piece to rotate relative to body  20 , head  17  and handle  25  and socket wrench  10  can be repositioned without rotating the work-piece. Change the ratchet mechanism  35  selector switch to the left-hand setting and socket wench  10  functions in the same manner by rotating work-piece and being repositioned in the opposite direction of right-hand setting. 
   To unlock handle  25 , lock collar  22  is moved forward to disengage handle key  24  and posterior detent and to engage anterior detent. Handle  25  unlocked, socket wrench  10  is nonetheless functional than previously described except that handle  25  rotation is opposed manually by user rather than mechanically by lock collar  22 . 
   A work piece can also be rotated using only handle  25 . With handle  25  unlocked and ratchet mechanism  35  selector switch set for right-hand rotation, applying rotational force in the right-hand direction to handle  25  causes handle  25  and ring gear  33  to rotate. Ring gear  33  engages ratchet mechanism  35  pawl and conveys this torque through ratchet mechanism  35  to drive shaft  31 . Drive shaft  31  conveys this torque through second miter gear  15  to first miter gear  13 . First miter gear  13 , being mounted in a fixed position to drive collar  11 , conveys this torque through the drive collar  11  to the work-piece, thus causing the work-piece to rotate in the right-hand direction. Applying rotational force to handle  25  in the opposite direction, torque is transferred from handle  25  to ring gear  33 . The pawls of ratchet mechanism  35 , as intended, disengage ring gear  33  to permit handle  25  to be repositioned without rotating the work-piece. 
   Finally, the previously described manners of operation may be employed simultaneously where socket wrench  10  and handle  25  are both rotated at the same time to effect work-piece rotation. This function also allows simultaneous repositioning of both socket wrench  10  and handle  25 . Using socket wrench  10  in this manner greatly increases the efficiency of the tool and provides a more ergonomic motion for the user.