Abstract:
A tool for attachment and removal of threaded components including a coupling adapted to engage the component and an arm having a first handle and a second handle displaced longitudinally by a given distance and including at least one hinge connecting the coupling to the arm or connecting the first handle to the second handle and permitting relative movement therebetween about a pivot axis substantially normal to a plane retaining the rotational axis of the coupling.

Description:
FIELD OF THE INVENTION 
     This invention deals with an improvement to a tool, in particular to that type of tool used to manually attach or remove threaded fasteners, or the like. 
     BACKGROUND OF THE INVENTION AND DESCRIPTION OF RELATED ART 
     It is common in the attachment of such threaded fasteners that the fastener must first be fitted to a structure with mating thread, then rotated without substantial torque until the fastener and structure are substantially, but not fully attached, then further rotated with a much higher degree of torque until the fastener is fully attached to the structure. A reversal of this procedure would be followed for removal of such a fastener from such a structure. 
     For example, to attach a hexagonally shaped nut with single pitch threading to a mating threaded post of a certain length which projects above a surface, one would first fit the nut over the post so as to engage the threads, then one would rotate the nut one turn for each thread of the post until the nut comes to contact the surface, then one would use a hexagonal wrench to further rotate the nut until a sufficient degree of locking pressure has been obtained between the nut and the surface. Depending on the number of threads of the post, and the fit of the mating threads, it is often preferred to use a tool adapted for fast rotation of those turns not requiring the high torque of the wrench. 
     There are a number of existing tools so adapted, including the tool depicted in FIG. 16 which is adapted for high speed rotation of a fastener, but the torque available from such a tool is insufficient to fully engage the fastener, or to disengage a fastener which had been fully engaged. Use of this tool, therefore, is only beneficial for the high speed/low torque rotations of the fastener, and one must still use the wrench to provide the high torque final rotations. 
     There are a number of other existing tools which are intended to have both of the properties of high speed/low torque and low speed/high torque application, but those are either complicated and expensive to produce, such as those that use switchable gearing, or are adapted to compromise both functions to provide service somewhat less than desired in each case, such as the tool depicted in FIG. 17 which cannot provide the torque of a standard wrench or the speed of a speed handle. 
     One existing tool which can serve both functions of high torque/low speed and high speed/low torque is depicted in FIG. 18 and is comprised of two long perpendicular bars permanently attached at their midpoints. One of the bars which is coaxial with the fitting is intended to provide a rotational support during high speed rotation, and the other bar is intended to provide a means for applying force during high torque application. The most notable disadvantage to this tool is its size and shape which render it cumbersome and expensive to inventory, ship, and store. 
     In U.S. Pat. No. 4,334,445, timewell discloses a tool which includes a fitting and a single handle, connected to an intermediary member by two hinges. This tool is claimed to be adaptable into positions which allow both high torque operation, and high speed operation. However, this invention lacks a means to support the tool with hands at two separate locations, rendering the tool difficult and awkward to operate during some applications in the high speed condition, for instance those applications where the fitting cannot firmly engage the fastener such as the way a slotted screwdriver engages a slotted screw. Also, due to the amorphous relationship between the fitting and the handle of this tool caused by the use and location of the two hinges, it is not practical to use this tool in the high speed condition for applications where, in addition to the usual tangential force, the fitting must engaged the fastener with also an axial force, such as the way a screwdriver engages a mating screw. 
     SUMMARY OF THE INVENTION 
     The object of the present invention is to avoid the foregoing disadvantages while incorporating into one individual device the most desirable features of a tool for the attachment and removal of threaded fasteners. The present invention can serve both required functions of a tool to be used for the manual attachment or removal of threaded fasteners, namely the high torque/low speed and the low torque/high speed functions, without compromising the performance of the tool in regards to either function, by being quickly and simply converted from one condition to a differing condition through the performance of only one action, and requiring no additional components. The present invention can also be configured for efficient storage, requiring no more storage space than any of the most basic tools of prior art which perform only one function. 
    
    
     DESCRIPTION OF THE DRAWINGS 
     Several conceived embodiments of the invention are depicted in the accompanying drawings. 
     FIG. 1 is a perspective view of a the first embodiment of the invention in a configuration adapted for low speed/high torque application. 
     FIG. 2 is a perspective view of the tool shown in FIG. 1 in an alternate configuration adapted for high speed/low torque application. 
     FIG. 3 is an elevational view of the tool shown in FIG. 1 in which the arm portion is shown also in phantom lines configured as depicted in FIG. 2. 
     FIG. 4 is a bottom view of the tool shown in FIG. 1. 
     FIG. 5 is an elevational view of a slight variation of the first embodiment of FIG. 1 in which the fitting is instead a common ratchet head adapted for quick exchange of variously sized common sockets. 
     FIG. 6 is a bottom view of the tool shown in FIG. 5. 
     FIG. 7 is a perspective view of the second embodiment of the invention in a configuration adapted for low speed/high torque application. 
     FIG. 8 is a perspective view of the tool shown in FIG. 7 in an alternate configuration adapted for high speed/low torque application. 
     FIG. 9 is a perspective view of the third embodiment of the invention in a configuration adapted for low speed/high torque application with two other configurations, namely the high speed/low torque configuration and a storage configuration, shown in phantom lines. 
     FIG. 10 is a perspective view of the fourth embodiment of the invention in a configuration adapted for low speed/high torque application. 
     FIG. 11 is a perspective view of the tool shown in FIG. 10 in an alternate configuration adapted for high speed/low torque application. 
     FIG. 12 is a perspective view of the tool shown in FIG. 10 in an alternate configuration adapted for storage. 
     FIG. 13 is a perspective view of the fifth embodiment of the invention in a configuration adapted for low speed/high torque application. 
     FIG. 14 is a perspective view of the tool shown in FIG. 13 in an alternate configuration adapted for high speed/low torque application. 
     FIG. 15 is a perspective view of the tool shown in FIG. PG,7 13 in an alternate configuration adapted for storage. 
     FIG. 16 depicts a tool of prior art. 
     FIG. 17 depicts a tool of prior art. 
     FIG. 18 depicts a tool of prior art. 
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     A first embodiment of the invention is depicted in FIGS. 1, 2, 3, &amp; 4. It consists of a fitting (101) and an arm (102) connected at a hinge (103). The fitting (101), commonly known as a box wrench, includes an internal hexagonally shaped feature (105) to engage the mating external hexagon of a nut or bolt head (not shown). The feature (105) has a longitudinal centerline (104), and two extensions (106) which each include a hole (115) sharing a common axis (107). Said axis (107) is perpendicular to the centerline (104) of the feature (105) to form a portion of the hinge (103). The axis (107) is separated from the centerline (104) by a certain first distance. The arm (102) includes a single extension (108) which freely fits within the extensions (106) of the fitting (101) and includes a hole (116) which is aligned coaxially with the holes (115) of the extensions (106) of the fitting (101). Adequate clearance is provided between the extensions (106) of the fitting (101) and the extension (108) of the arm (102) to allow pivoting of the arm (102) about the hinge (103) from at least the position depicted in FIG. 1 to the position depicted in FIG. 2. A cylindrical pin (113) is inserted through said three coaxial holes (115 &amp; 116) to comprise the hinge (103). The arm (102) further includes a first cylindrical handle (109) adjacent to the single extension (108). The centerline (110) of said first handle (109) being perpendicular to and coplanar with the axis (107) of the hinge (103), and coplanar with the centerline (104) of the internal hexagon feature (105). The arm (102) further includes a second cylindrical handle (111) more distant from the hinge (103) than the first handle (109). The centerline (112) of said second handle (111) being parallel to the centerline (112) of the first handle (109) and coplanar with the centerline (104) of the internal hexagon feature (105). The distance between the centerline (110) of the first handle (109) and the centerline (112) of the second handle (111) is equal to said certain first distance. The arm portion further includes a rigid connecting portion (114) between the first (109) and second (111) handles. 
     The hinge (103) is adapted to allow ninety angular degrees of pivot of the arm (102) so as to allow at least two conditions of operation. The first condition, depicted in FIGS. 1, 3, &amp; 4, is such that the centerlines (110) of the first handle (109) and the centerline (112) of the second handle (111) are perpendicular to the centerline (104) of the internal hexagon feature (105), and the second condition, depicted in FIG. 2, and depicted in phantom line in FIG. 3, is such that said handle centerlines (110 &amp; 112) are parallel to said feature centerline (104). The dimensional relationship of the feature (105), hinge (103), first handle (109), and second handle (111) is thereby such that in the condition depicted in FIG. 2, and depicted in phantom line in FIG. 3, the centerline (112) of the second handle (111) is aligned with the centerline (104) of the feature (105). 
     In the condition depicted in FIGS. 1, 3, &amp; 4, the tool is thereby adapted to provide a high mechanical advantage between a tangential force applied to the second handle (111) about the centerline (104) of the feature (105), and the torque resulting at said feature (105). This is the condition herein referred to as the high torque condition. 
     In the condition depicted in FIG. 2, and depicted in phantom line in FIG. 3, the tool is thereby adapted to provide a high speed rotation of the hexagon feature (105) by application of a tangential force to the first handle (109), about the common axis which is thereby established by the alignment of the center line (104) of the feature (105) and the centerline (112) of the second handle (111). 
     A slight variation of the first embodiment is depicted in FIGS. 5 &amp; 6 where the fitting (101) of the first embodiment has been replaced by a common ratchet head (117) for accepting common sockets (not shown). 
     A second embodiment of the invention is depicted in FIGS. 7 &amp; 8. The arm portion (124) includes two extensions (122) to form a portion of the hinge (126). Two cylindrical pins (121) are each inserted through holes (123) on each extension (122) and on each side of the fitting (118) to complete the hinge (126). The axis (119) of the hinge (126) is coplanar and perpendicular to the axis (120) of the fitting (118) and also coplanar and perpendicular to the centerline (130) of the first handle (128). Adequate clearance is provided between said two extensions (122) and said fitting (118) to allow pivoting of the arm portion (124) about the hinge (126) from the configuration depicted in FIG. 7 to the configuration depicted in FIG. 8. The centerline (129) of the second handle (127) is parallel to said centerline (130) of said first handle (128) and separated by a certain second distance. The handles (127 &amp; 128) are made unitary through the connecting portion (125) of the arm portion (124). 
     During use in the configuration depicted in FIG. 7, the first (128) and second (127) handles are oriented perpendicularly to the axis (120) of the fitting (118) so as to provide the mechanical advantage required for high torque about said axis (120) by application of a tangential force to the second handle (127) about said axis (120). 
     During use in the configuration depicted in FIG. 8, the first handle (128) is coaxial with the fitting (118), so as to provide a rotational support for the tool, and the second handle (127) is parallel to the axis (120) of the fitting (118) and separated by said certain second distance, so as to provide a mechanism by which the tool can be quickly rotated about said axis (120). 
     A third embodiment of the invention is depicted in FIG. 9. The drawing shows the tool in the configuration adapted for high torque application of a fastener (not shown), with phantom lines showing the high speed configuration and the storage configuration. In this embodiment, the holes (132) of the fitting (131) which form the portion of the hinge (136) extend fully through the fitting (131) without obstruction such that the axis (141) of said hinge (136) is perpendicular to and coplanar with the axis (133) of the fitting (131). The arm portion (135) includes three functional portions, the cylindrical pin (134) of the hinge portion (136), the first handle portion (137), and the second handle portion (138). Said cylindrical pin (134) is of length and diameter sufficient to freely engage both holes (132) of the hinge portion (136) of the fitting (131), and is attached at one end (139) to said first handle (137) whose centerline (140) is perpendicular to the axis (141) of said hinge (136), and separated from the axis (133) of the fitting (131) by a certain third distance. Said first handle (137) is of length sufficient to allow the grasp of a human hand (not shown). Said second handle (138) is more distant from the hinge (136) than the first handle (137), and is attached to said first handle (137) by a connecting portion (142). The centerline (143) of said second handle (138) is parallel to the centerline (140) of said first handle (137) and separated from said centerline (140) of said first handle (137) by said certain third distance so as to be coplanar with the axis (133) of the fitting (131). 
     During the depicted configuration, the centerline (143) of the second handle (138) is perpendicular to the axis (133) of the fitting (131) and adapted to provide the mechanical advantage required for high torque about the axis (133) of the fitting (131) by application of a tangential force to the second handle (138) about said axis (133). 
     The dimensional relationship between the arm (135) and the fitting (131) allow rotation of the arm (135) about the axis (141) of the hinge (136) to at least those two configurations depicted in phantom line, one of said two configurations being the high speed configuration, and the other being a storage configuration. 
     During use in the high speed configuration, the second handle (138) is coaxial with the fitting (131), so as to provide a rotational support for the tool. The first handle (137) is parallel to the axis (133) of the fitting (131) and the centerline (140) of said first handle (137) is separated from the axis (133) of the fitting (131) by said certain third distance, so as to provide a mechanism by which the tool can be quickly rotated about said axis (133). 
     With the arm (135) rotated about the hinge (136) one hundred and eighty angular degrees from the high speed configuration, a storage configuration is thereby established in which the tool&#39;s total length is minimized to provide a shape more compact for reduced volume during storage. 
     The arm portion (135) of this embodiment could be developed from a continuous length of cylindrical material in such a way that the cylindrical pin (134) of the hinge (136) and each of said first (137) and second (138) handles can be thereby formed from said continuous length of material, such as a length of cylindrical steel rod. 
     FIGS. 10, 11, &amp; 12 depict a fourth embodiment wherein the hinge (144) is located between the first (145) and second (146) handles, the first handle (145) thereby being unitary and coaxial with the fitting (147). The second handle (146) is adapted to pivot about the hinge (144) relative to the first handle (145) and the fitting (147). 
     During use in the configuration depicted in FIG. 10, the second handle (146) is oriented perpendicularly to the axis (148) of the fitting (147) so as to provide the mechanical advantage required for high torque about said axis (148) by application of a tangential force to the second handle (146) about said axis (148). 
     During use in the configuration depicted in FIG. 11, with the first handle (145) being a rotational support for the tool, the second handle (146) is positioned about the hinge (144) so that the centerline (140) of said second handle (146) is parallel with the axis (148) of the fitting (147), and separated by a certain fourth distance which is at least equal to the average width of the two handles (145 &amp; 146), so that said second handle (146) can provide a mechanism by which the tool can be quickly rotated about said axis (148). 
     In FIG. 12, with the second handle (146) rotated about the hinge (144) one hundred and eighty angular degrees from the configuration of FIG. 11, a storage configuration is thereby established in which the tool&#39;s total length is minimized to provide a shape more compact for reduced volume during storage. 
     FIGS. 13, 14, &amp; 15 depict a fifth embodiment, similar to the embodiment of FIGS. 10, 11, &amp; 12 wherein a second hinge (154) is located between the fitting (152) and first handle (151) in addition to the first hinge (150) which is located between the first (151) and second (153) handles. 
     During use in the configuration depicted in FIG. 13, the first (151) and second (153) handles are oriented perpendicularly to the axis (156) of the fitting (152) so as to provide the mechanical advantage required for high torque about said axis (156) by application of a tangential force to the second handle (153) about said axis (156). 
     During use in the configuration depicted in FIG. 14, with the first (151) and second (153) handles pivoted about the second hinge (154) so that the first handle (151) is coaxial with the fitting (152), said first handle (151) forms a rotational support for the tool. The centerline (155) of the second handle (153) is parallel with the axis (156) of the fitting (152), and separated by a certain fifth distance which is at least equal to the average width of the two handles (151 &amp; 153), so that said second handle (153) can provide a mechanism by which the tool can be quickly rotated about said axis (156). 
     In FIG. 15, with the second handle (153) pivoted about the first hinge (150) one hundred and eighty angular degrees from the configuration of FIG. 14, a storage configuration is thereby Established in which the tool&#39;s total length is minimized to provide a shape more compact for reduced volume during storage. The fitting (152) may be pivoted about the second hinge (154) into whichever position provides the shortest overall length of the tool.