Abstract:
A wrench ( 10 ) with torque augmenter is provided which includes a linkage assembly ( 38 ) to join a drive input ( 46 ) with an output wrench socket ( 90 ). The linkage assembly ( 38 ) consists of a drive link ( 40 ) extending from the input socket ( 46 ) and coacting with a conversion link ( 42 ) extending to a ratchet ( 88 ) disposed about the output socket ( 90 ) of the wrench. Rotation of the drive link ( 40 ) pivots the conversion link ( 42 ) to transfer torque from the input to the output socket ( 90 ). A pawl ( 76 ) on the driven link ( 42 ) is provided to coact with the ratchet ( 88 ) which encircles the output socket ( 90 ). A guide ( 36 ) is disposed at the interior of the housing ( 12 ) for the wrench to coact with the linkage assembly ( 38 ) and maintain proper alignment during a torque operation, such that stress and force are substantially reduced or dissipated, if not eliminated, during the operation. Another embodiment ( 310 ) of the wrench includes a pair of sockets ( 312,314 ) interconnected with a drive link assembly ( 316 ) to which a pair of springs ( 348,350 ) are operatively associated. This embodiment ( 310 ) is for use with an impact type wrench ( 380 ) and automatically recycles itself for a subsequent torque operation during the intermittent lulls of the torque cycle of the impact wrench. Other embodiments ( 600,700,800 ) of the hand wrench are constructed with internal self-contained hydraulic systems ( 664 ) to provide torque augmentation.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     This application is a 35 U.S.C. 371 application of PCT/US98/23425 filed Nov. 4, 1998 and a continuation-in-part of U.S. application Ser. No. 08/976,814 filed Nov. 24, 1997, which is a continuation-in-part of U.S. application Ser. No. 08/965,546 filed Nov. 6, 1997, U.S. Pat. No. 5,953,966. The disclosure of U.S. application Ser. Nos. 08/976,814 and 08/965,546, are hereby incorporated by reference. 
    
    
     BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The present invention relates to torquing apparatus and in particular, to hand operated apparatus adapted to transmit and/or augment torque from an input through to an output of the apparatus. Additionally, the invention relates to a device which is especially adaptable for use with pulsating torque apparatus such as impact tools or other external torque providing apparatus. 
     2. Description of the Related Art 
     Wrenches are among the most useful hand tools and their design often have conflicting objects. The primary purpose of a wrench is to apply torque to a nut or other fastening device to seat or unseat the device in threaded engagement with a mating object. In order to apply large amounts of torque, wrenches normally have to be either very large in size or use auxiliary mechanisms such as hydraulic or mechanical apparatus to increase the torque provided by the wrench. This tends to make the wrench bulky and large and limit its effectiveness for normal everyday use where the object is to provide a wrench that is relatively small, can fit into tight places and is easy and convenient to use. Examples of torque augmenting devices are known and disclosed in the prior art as follows: 
     
       
         
               
               
             
           
               
                   
               
               
                 U.S. Pat. No. 
                 Inventor(s) 
               
               
                   
               
             
             
               
                 1,522,839 
                 Rogers 
               
               
                 2,204,800 
                 Freeborn 
               
               
                 2,235,192 
                 Bailey 
               
               
                 2,238,125 
                 Murray 
               
               
                 2,292,079 
                 Joyce 
               
               
                 2,296,532 
                 Mekeel, Jr. 
               
               
                 2,653,489 
                 Charpentier 
               
               
                 2,655,015 
                 Linder 
               
               
                 2,742,797 
                 Perham 
               
               
                 2,783,657 
                 Kohlhagen 
               
               
                 2,882,757 
                 Edsall 
               
               
                 3,363,482 
                 Case 
               
               
                 3,364,794 
                 Ishoika 
               
               
                 3,722,325 
                 Rogers 
               
               
                 4,041,835 
                 Isler 
               
               
                   
               
             
          
         
       
     
     For example, U.S. Pat. No. 2,296,532 to Mekeel. Jr. discloses a torque control transmission having a reaction brake which includes a ratchet wheel and latch, and a reversing brake with oppositely facing ratchet wheel and latch. Connector arms support the latches and are pivotally operated by a lever. 
     U.S. Pat. No. 2,783,657 to Kohlhaaen discloses a constant torque drive having a plurality of gears arranged between a pair of plates, and a pawl pivotally mounted on one of the gears and urged by a spring into operative engagement with a disc-shaped head of a stud to lock the gears against counterclockwise rotation, but permit their rotation in a clockwise direction. The gears are supported by an arm which is connected to a spring to urge the arm in a certain direction. 
     U.S. Pat. No. 3,364,794 to Ishoika discloses a spring torque converter having a plurality of rocking levers, pairs of which are connected with links for coaction with the drive shaft and driven shaft to apply torque. Another embodiment discloses a plurality of crank pins, and a helical spring having one end attached to the respective crank pin and another end attached to an anchoring pin on a carrier portion of the device. 
     The remaining patents also disclose other torquing devices. 
     There are also the instances where a wrench is required for use in a torque operation under water. Sometimes, the torquing operation occurs at substantial depths for prolonged period of time. The operation may occur over a substantially large area requiring the user of the wrench to move to the different cites that the torquing operation is to occur. In those instances, with devices requiring hydraulic lines, the amount of pressure necessary to be increased at the surface to convey the pressure through the line must be carefully monitored and controlled. 
     In addition, the hydraulic line snaking downward through the water to the torque wrench is cumbersome and with increased length difficult to move about a large area under water. There is also the possibility of entanglement of the hydraulic line and where ruptures occur, a substantial amount of hydraulic fluid could be caused to be leaked into the water thereby fouling the environment in violation of federal and state statutes. 
     OBJECTS AND SUMMARY OF THE INVENTION 
     The present invention provides a simple, efficient and light weight wrench with torque augmenting means, consisting of a socket wrench which utilizes a rachet arrangement and which includes additional features within the handle of the wrench that enable an auxiliary unit to be connected to the wrench to augment the torque provided by the wrench when situations requiring high torque are encountered. The wrench apparatus is constructed in a manner to facilitate effective coaction of the various components without placing undue stress on the housing and handle of the wrench which enables the wrench to be relatively small for the job it can perform and relatively light and easy to use. 
     In another embodiment of the invention, the wrench apparatus has two power delivery sockets or driving sockets, one at either end and is relatively symmetrical. The driving sockets can be used for related sizes of nuts that would be used with the device, or for dissimilar shaped fasteners of comparable size. A central driven aperture disposed between the two power delivery sockets has opposed driving fingers extending toward either end of the device to coact with driven arms in the same manner as the single driven aperture hand wrench previously discussed. Spring means are incorporated within the housing to return a middle link, known as the MISSING LINK™, which has opposed driving fingers to an initial position to enhance coaction between the device and an external periodic type of power delivery apparatus, such as an impact wrench. 
     In a further embodiment of the present invention, the apparatus is constructed with an internal hydraulic assembly connected to a reservoir external to the apparatus for applying torque to a drive output of the wrench. 
     In still another embodiment of the present invention the wrench is provided with an internal hydraulic assembly, including the hydraulic reservoir, so that the wrench is completely self-contained for applying torque to a drive output. 
     It is an object of the present invention to provide an augmenter which can be used in confined spaces, and has an envelope sized approximately the same as a standard wrench socket to fit in an area between adjacent nuts. 
     It is another object of the present invention to provide a hand wrench augmenter which can operate as a hand wrench or as a plain wrench without any force augmentation. 
     It is another object of the present invention to provide a hand wrench having means to enable additional torque to be transmitted to the hand wrench, which in turn is converted to torque at the wrench engaging portion of the apparatus to augment the total torque that can be exerted by the wrench. 
     It is another object to the present invention to provide a hand wrench with torque augmenting means which can function either as a hand wrench or as a high torque tightening apparatus of limited travel independently of each other. 
     It is another object of the present invention to provide a hand wrench augmenter which can be augmented in multiple positions and from either side. 
     It is an object of the present invention to provide a hand wrench which is adapted for use with a separate input drive to transmit torque to an output drive such as a socket. 
     It is another object of the present invention to provide a hand wrench which is of simple construction, easy to maintain and repair, and adapted to receive differently sized input drives to transmit torque to the output drive. 
     It is another object of the present invention to provide a hand wrench constructed with linkage to transmit and convert the torque at the input receptacle to the output drive. 
     It is another object of the present invention to provide a hand wrench which is operable without external gears or hydraulics. 
     It is another object of the present invention to provide a hand wrench constructed with a housing in which a guide means is disposed to substantially reduce, if not eliminate, forces at an interior portion of the housing and the linkage within the housing, such that the structural integrity of the housing is maintained. 
     It is another object of the present invention to provide a hand wrench constructed with a housing having side walls arranged to absorb the force of the internal linkage during an operation of the apparatus. 
     It is another object of the present invention to provide a hand wrench having a housing in which a biasing means is arranged to automatically urge the linkage to reset for a subsequent torque transmission/augmenting operation. 
     It is another object of the present invention to provide a hand wrench having a pair of sockets of different sizes at opposed ends of the hand wrench. 
     It is another object of the present invention to provide a hand wrench adapted to coact with the drive member of an external torquing member such as an impact wrench. 
     It is another object of the present invention to provide a wrench with a linkage assembly constructed and arranged to interconnect a pair of drive socket assemblies for coaction therewith during a torquing operation. 
     It is another object of the present invention to provide a wrench with a housing sealed for containing lubricating means therein for elements of the wrench. 
     It is another object of the present invention to provide a wrench containing linkage means adapted to coact with a repetitive external torque source, to enable coaction between the internal linkage of the wrench and the external pulsating impact torque source. 
     It is another object of the present invention to provide a wrench with an internal linkage assembly adapted for use with compression springs or leaf springs to initialize the wrench during repetitive cycles. 
     It is another object of the present invention to provide a wrench with an augmenting means constructed and arranged within a housing of the wrench to automatically reset for a torque augmenting cycle during a lull in operation of a coacting impact wrench. 
     It is another object of the present invention to provide a wrench having a torque augmenting means adapted to coact with an intermittent cycle of an impact wrench. 
     It is another object of the present invention to provide a wrench adapted to coact with an external source of cyclic torque. 
     It is another object of the present invention to provide a wrench which is relatively lightweight, relatively durable, and of simplified construction. 
     It is another object of the present invention to provide a wrench constructed to minimize the size of the driving sockets of the apparatus to enable the apparatus to be positioned in areas not easily accessible by an external pulsating torque source. 
     It is another object of the present invention to provide a wrench relatively inexpensive to fabricate, and which can be produced in a wide range of sizes to fit fasteners of relatively small sizes up to relatively large sizes exceeding 6″ in diameter. 
     It is another object of the present invention to provide a wrench having a torque augmenting means operated hydraulically. 
     It is another object of the present invention to provide a wrench having a hydraulic assembly incorporated therein which is adapted for connection to an external hydraulic source and pump. 
     It is another object of the present invention to provide a wrench having a torque augmenting means with a built-in hydraulic assembly, including a hydraulic reservoir. 
     It is another object of the present invention to provide a wrench having a hydraulic torque augmenting means incorporated therein for the wrench to be completely self-contained. 
     It is another object of the present invention to provide a wrench having a torque augmenting means hydraulically operated and including a pressure gauge as part of the wrench. 
     It is another object of the present invention to provide a wrench having a hydraulic torque augmenting means which is adapted to receive a hand ratchet or an impact wrench to drive the wrench. 
     It is another object of the present invention to provide a wrench having a self-contained torque augmenting means which is hermetically sealed for use under water. 
     It is another object of the present invention to provide a wrench having a hydraulic torque augmenting means of which a cylinder, piston and reservoir for the hydraulics are constructed as an assembled unit for the wrench. 
     It is another object of the present invention to provide a wrench having a hydraulic torque augmenting means and a pressure gauge therefor, which pressure gauge swivels for orientation to facilitate reading of the gauge during torquing operations. 
     It is another object of the present invention to provide a wrench having at least one adjustable friction control member to engage an output ratchet of the wrench to prevent the ratchet from slipping during the initial tightening of the ratchet. 
     It is another object of the present invention to provide a wrench constructed with input and output drives adapted to be mated with other wrench drives so that the wrenches can be ganged. 
     It is another object of the present invention to provide a wrench having an internal hydraulic assembly with a valve to vent air into the system so that the wrench can be used with an impact wrench or hand wrench. 
     It is another object of the present invention to provide a wrench having internal elements adapted to be adjusted for a speed versus torque relationship for the wrench. 
     It is another object of the present invention to provide a wrench having a torque augmenting means wherein the input drive and output drive are arranged along a center line for the wrench. 
     It is another object of the present invention to provide a wrench having an internal hydraulic torque assembly connected to a quick disconnect valve coupling at an exterior of the wrench for coupling to a hydraulic source. 
     It is another object of the present invention to provide a wrench having an internal hydraulic torque augmenting means having a pressure assembly with a pressure relief valve to prevent the wrench from over-torquing. 
     It is another object of the present invention to provide a wrench having an internal hydraulic torque augmenting means which is actuated upon circular motion conducive to that used with a ratchet to provide torque output. 
     It is another object of the present invention to provide a wrench having a self-contained hydraulic torquing assembly which permits the user to operate the wrench independent of external systems. 
     It is another object of the present invention to provide a wrench having a dual-pawl assembly where the pawls are at different pitches with respect to a ratchet for the wrench so that at least one tooth of one of the pawls is engaged with the ratchet at all times. 
     It is another object of the present invention to provide a reaction arm removably mountable to a drive input for the wrench and adjustable for positioning the wrench for a torque operation. It is another object of the present invention to provide a reaction arm rotatable with respect to the wrench for use with a slugging wrench for a torque operation. 
     It is another object of the present invention to have a reaction arm which is height adjustable with respect to an exterior surface of the wrench to provide an impact zone at varying distances from the exterior surface. 
     It is another object of the present invention to provide a wrench having a cylinder disposed therein for support and operation of a piston-spring assembly for providing torque for the wrench. 
     It is another object of the present invention to provide a wrench which is adapted to provide a torque output either in a 2:1 ratio or, where hydraulics are used, in another ratio of force multiplied by distance. 
     It is another object of the present invention to provide a wrench for a torque operation which is adapted for use with an impact wrench and recoils during a torquing operation upon the recoil or slip of the impact wrench. 
     It is another object of the present invention to provide a wrench for a torque operation which has an internal hydraulic assembly for connection with a hydraulic contact wrench and constructed to recoil (or slip) in conjunction with the slip of the contact wrench. 
     It is another object of the present invention to provide a wrench for torquing operations which when operated hydraulically bypasses the manual drive input to actuate the drive output for the wrench. 
     It is another object of the present invention to provide a dual-pawl assembly for coaction with a ratchet at the drive output for the wrench, each one of the pawls having teeth constructed and arranged for engagement with the ratchet teeth at a predetermined interval during the torquing operation. 
     It is another object of the present invention to provide guide means consisting of bar elements disposed along a top and bottom of the housing for the wrench to provide structural support for the housing and movement of elements at an interior of the housing. 
     It is another object of the present invention to provide a wrench having a torque augmenting means which includes drag means for the ratchet of the wrench to restrict movement of the ratchet during initial stages of a torque operation. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     For a more complete understanding of the present invention, reference may be had to the following detailed description of the preferred embodiments taken in conjunction with the accompanying drawings, of which: 
     FIG. 1 is a perspective view showing a hand wrench with torque augmenting means according to the present invention; 
     FIG. 2 is a top perspective view showing internal elements of the hand wrench; 
     FIG. 3 is a top plan view showing the hand wrench at rest for a torque operation; 
     FIG. 4 is a top plan view of elements shown in the view of FIG. 3 coacting for a torque conversion stroke; 
     FIG. 5 is a top plan view of the hand wrench of FIG. 4 completing the stroke; 
     FIG. 6 is a top plan view showing elements of another embodiment of the hand wrench according to the present invention; 
     FIG. 7 is a top plan view showing elements of still another embodiment of the hand wrench according to the present invention; 
     FIG. 8 is a top view of another embodiment of the invention having driven apertures on each end of the device and being relatively symmetrical in nature, with a drive aperture centrally located; 
     FIG. 9 is a side view taken along line  9 — 9  of FIG. 8; 
     FIG. 10 is a view taken along line  10 — 10  of FIG. 9; 
     FIG. 11 is another embodiment of the invention similar to the view shown in FIG. 10; 
     FIG. 12 is a cross-sectional view of an impact wrench known in the art; 
     FIG. 13 is a view of another embodiment of the present invention similar to the view shown in FIG. 10; 
     FIG. 14 is a top plan view showing an interior of another embodiment of the hand wrench according to the present invention; 
     FIG. 15 is a top plan view showing an interior of still another embodiment of the hand wrench according to the present invention; 
     FIG. 16 is a top plan view of the embodiment shown in FIG. 15 upon conclusion of a torque stroke of the present invention; 
     FIG. 17 is a top plan view of a cover for a casing for the embodiments shown in FIGS. 14-16; and 
     FIG. 18 is a partial top view of a dual-pawl and ratchet assembly for the wrench according to the present invention. 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     Referring to FIGS. 1 and 2, a hand wrench having torque augmenting means of the present invention is shown generally at  10 . The augmenter  10  is constructed to receive an external drive input A and transmit or augment the torque from the input A to an output B, such as a hex-sided stud or bolt. 
     The augmenter  10  consists of a housing  12  which is constructed from a pair of halves  14 , 16 . The halves  14 , 16  can be held together by conventional mechanical fasteners such as screws, or with a friction fit. Each one of the halves  14 , 16  is provided with a continuous side wall  18 , 20  in which a corresponding detent or cutout  22 , 24  is formed. When the halves  14 , 16  are brought together to form the housing  12 , they also provide a handle for the wrench, and the cutouts  22 , 24  formed in the respective side walls  18 , 20  are aligned in registration with each other to provide a space S at which force can be exerted to part the halves  14 , 16 . 
     The half  14  has an exterior surface  26  upon which printed indicia can be displayed. The indicia can be instructions for operating the tool, logos, safety notices, etc. The half  16  has an exterior surface also for printed indicia which is not shown due to the perspective of the drawing Figures. 
     The half  14  is constructed with a small aperture  28  at one end thereof, the aperture  28  extending from the surface  26  completely through the half  14 . An opposite end of the half  14  is formed with a larger aperture  30  which similarly extends from the surface  26  completely through the half  14 . 
     Referring also to FIGS. 2 and 3, additional elements of the augmenter  10  are also disclosed. 
     The half  16  includes an interior floor  32  from which the continuous side wall  20  extends upward therefrom. The side wall  20  is provided with an inner surface  34 . An arcuate guide bar  36  extends upward from the floor  32 . The guide bar  36  extends across the floor  32  such that each one of the opposed ends of the guide bar  36  is connected to a corresponding portion of the inner surface  34  of the continuous side wall  20  at opposite sides of the floor  32 . 
     In FIG. 3, the augmenter  10  of the present invention is shown at rest ready to commence a torque operation. The elements of the augmenter  10  which enable the transmission and augmenting of torque are as follows. 
     A linkage assembly shown generally at  38  is constructed and arranged for operation when the halves  14 , 16  are joined together. The linkage assembly  38  includes a drive finger  40  and a driven arm  42 . 
     The drive finger  40  has a first end from which an upstanding cylindrical portion  44  extends. The cylindrical portion  44  extends through both halves  14 , 16  when joined together. The drive finger  40  rotates about the cylindrical portion  44 . The cylindrical portion  44  is provided with a hex or other multi-sided aperture  46  (FIG. 2) extending completely therethrough. The aperture  46  is adapted to act as an engaging receptacle for a multi-sided male drive member A. The aperture  46  is constructed and arranged in the drive finger  40  to be in registration with the aperture  28  of the half  14 . The half  16  is similarly provided with an aperture which is in registration with the aperture  28  of the half  14 , such that when the halves  14 , 16  are joined to each other with the linkage assembly  38  disposed therebetween, the multi-sided aperture  46  of the drive plate  40  is accessible at the smaller aperture  28  of the half  14  or at the corresponding aperture (not shown) in the other half  16 . This permits the user to extend the drive input A completely through the housing  12 , or to enable access to the engaging receptacle from either side of the housing. Therefore, the receptacle will always be accessible even if necessary to turn the augmenter  10  over for an operation. 
     The drive finger  40  is constructed with a side wall generally shown at  48  which substantially conforms to the tapered shape of the inner surface  34  of the side wall  20  of the half  16 . As shown in FIG. 3, an arcuate portion of the side wall  48  is constructed to rest against and be received by the complimentary tapered inner surface  34 . This permits the drive finger  40  to pivot in position and rest against the side wall  20 . However, as will be discussed hereinafter, the drive finger  40  does not exert a pressure load against the side wall  20  which would be sufficient to weaken the side wall  20 . 
     The opposite, free end of the drive finger  40  is formed with an oblong-shaped aperture  50  extending completely therethrough. A longitudinal axis of the oblong-shaped aperture  50  bisects a central axis of the multi-sided aperture  46 . 
     The driven arm  42  includes at one end a pin  52  extending therefrom. The pin  52  is constructed and arranged to be in registration with and received by the oblong-shaped aperture  50  of the drive finger  40 . The pin  52  is similarly oblong-shaped and is of a height that preferably is at least equal to the depth of the oblong-shaped aperture  50 , and does not exceed the greatest height of the driven arm  42 . The pin  52  is rotatably mounted to the driven arm  42 . Alternatively, the pin  52  may be circularly shaped and fixed to the driven arm  42 . 
     The driven arm  42  widens as it extends to assume a circular shape. As also shown in the perspective view of FIG. 2, a larger, circular shaped portion of the driven arm  42  is shown generally at  54 . 
     The driven arm  42  is provided with side walls  56  and  57  which are shaped to engage along their entire length or to engage substantially along their entire length the inner surface of the continuous wall  20  of the housing when the driven arm is at the end of its travel. This tends to distribute the forces produced by the side wall of the driven arm  42  along the entire housing, minimizing the stress at any one point. 
     The shape of the side wall  56  permits the driven arm  42  to pivot freely within the half  16  when the driven arm  42  coacts with the drive finger  40 . 
     An arcuate boss  62  or ridge extends upward from the driven arm  42  to coact with the drive finger  40 . The height of the boss  62  substantially corresponds to the thickness of the drive finger  40  for a purpose to be described with reference to FIGS. 4 and 5. 
     Grooves  58  and  60  respectively are machined in the driven arm leaving ridges  62  and  66 , and  64  and  67  respectively. The grooves  58  and  60  are adapted to mate with a pair of arcuate ridges. The arcuate ridge on the floor of the top plate is not shown. The arcuate ridge on the bottom half being designated as  36 . The coaction of the grooves  60  on the driven arm with the arcuate ridge  36  on the back half of the housing provides a guide for movement of the driven arm and also provides for structural support of the driven arm as it is moved by the drive finger. The top of the ridges  62  and  66  on the front side and  64  and  67  on the rear extend to the inner surface of the housing when the halves  14 , 16  are assembled. 
     As shown more particularly in FIG. 2, the arcuate guide bar  36  is sized and shaped to be received in the groove  60 , while another arcuate guide bar (not shown due to the perspective view of the Figures) of half  14  is received in the groove  58 . This construction permits the driven arm  42  to ride along the arcuate guide bar  36  and the prescribed angle of arc of the guide bar  36 . The driven arm  42  widens generally at  66  into a circular portion having an aperture  68  extending completely therethrough and in registration with the large aperture  30  of the plate  14  and the aperture  27  of the plate  16 . The circular portion  66  of the driven arm  42  is formed with a recess  70  in communication with the aperture  68 . A pair of bores  72 , 74  are formed in the circular portion  66  of the driven arm  42  and open into the recess  70 . 
     A pawl  76  is disposed in the recess  70 . The pawl  76  is formed with a pair of bores  78 , 80 , each of which is in registration with a corresponding one of the bores  72 , 74  of the driven arm  42 . Springs  82 , 84  are disposed in the recess  70 , each one having its opposed ends terminating in a corresponding one of the bores  72 , 78  and  74 , 80 , respectively. The springs  82 , 84  resiliently bias the pawl  76  to float in the recess  70  so that inclined teeth  77  of the pawl  76  are urged to engage corresponding inclined teeth  86  of a ratchet  88  disposed in the large aperture  30 . 
     The ratchet  88  fits in a stepped portion of the aperture  68 . The aperture  68  has a larger diameter and a smaller diameter. The larger diameter will accommodate the teeth of the rachet and the small diameter will support the teeth and enclose the entire ratchet mechanism. 
     The ratchet  88  is circular in shape and is received in the large circular end  54  of the driven plate  42  to surround a hex socket  90 . The ratchet  88  is connected to and preferably an integral part of the hex socket  90 . 
     A circular shaped wear collar  92  is constructed and arranged to extend around the hex socket  90  above the ratchet teeth  86 . The wear collar  92  is made from bronze or other soft alloy to reduce friction during a torque operation when the halves  14 , 16  are joined to form the housing  12 . 
     The starting position of the torquing operation is shown for example in FIGS. 1 and 3. First, the housing  12  of the augmenter  10  is grasped and the large hex will be engaged with the item to be tightened such as the output shaft B. The handle of the wrench  12  is then manually turned much as a standard socket head wrench until the output shaft is tight and further movement of the handle manually is no longer possible. If augmented torque is required, then an augmenting drive shaft A is entered into the augmenting receptacle aperture  46 . The input shaft A can then be rotated. This can either be a long lever, or it can be a power type of unit. However, even a twelve inch (12″) additional lever rotating the augmenting receptacle will be sufficient to produce substantial augmenting torque, since the lever can be substantially longer than the length of the handle. Additionally, since the handle must be located in a fixed position in a specific location with respect to the output shaft to be tightened, there may not be sufficient room to obtain proper purchase for rotating the handle of the augmenter, whereas an auxiliary lever or rotating bar can extend to an area of greater freedom when using the augmenting feature. 
     The input A is turned as indicated by the arrow  94  shown in FIG.  4 . The rotation is in, for example, a counter clockwise direction. Accordingly, the drive finger  40  is also urged to pivot in a counter clockwise direction. The driven arm  42  is urged to move in a direction of arrow  96 , while the pin  52  moves along the oblong-shaped aperture  50  of the drive finger  40 . 
     The arcuate guide bar  36  extending upward from the bottom  32  of the plate  16  provides a stress point for the drive finger  40  and the driven arm  42 . That is, as the finger and arm  40 , 42  respectively, are pivoted, there is a tendency for the finger  40  and arm  42  to be forced away from each other which would, but for presence of the guide bar  36 , cause a detrimental amount of force to be incurred by the continuous side wall  20  of the plate  16 . The guide bar  36  restricts the “parting” of the linkage assembly  38  and channels the stress and forces which occur during the torque operation to a more central location of the plate  16 . Such forces are disbursed so that the structural integrity of the halves  14 , 16 , and therefore the housing  12 , is not compromised. 
     As the linkage assembly  38  is pivoted, the inclined teeth  77  of the pawl  76  engage the corresponding inclined teeth  86  of the ratchet  88 . This motion forces the hex socket  90  to pivot as indicated by arrow  98  in FIG. 5 to tighten down the bolt B. 
     The springs  82 , 84  as shown in FIGS. 4-5, bias the pawl  76  toward the ratchet  88  for engagement of the teeth  77 , 86 . The motion of the linkage assembly  38  is therefore imported to the hex socket  90  to allow effective motion only in the direction as indicated by the arrow  98 . 
     When the “throw” of the linkage assembly  38  is complete, as shown in FIG. 5, the input A is moved in the opposite direction, i.e. clockwise, to return the linkage assembly  38  for another torque operation. This movement permits the inclined teeth  77  of the pawl  76  to ride over the inclined teeth  86  of the ratchet so that the mechanism can be reset as in FIG. 3 for another torque cycle. 
     Another embodiment of an augmenter  110  constructed in accordance with the present invention is illustrated at FIG.  6 . Elements illustrated in FIG. 6 which correspond to elements described above with respect to FIGS. 1-5 have been designated by corresponding reference numerals increased by 100. The embodiment of FIG. 6 is designed for use in a manner similar to that shown with respect to the embodiment of FIGS. 1-5, unless otherwise stated. 
     Referring now to FIG. 6, an additional biasing element  93  is shown. The biasing element  93  can be an extension spring, as shown in FIG. 6, or a torsion spring. In the example shown, the extension spring  93  has one end  95  connected to the driven arm  142 , and an opposite end  97  connected to the continuous side wall  120  of the plate  116 . The spring  93  inherently biases the linkage assembly  138  in a direction of arrow  99  to facilitate the return of the linkage assembly  138  to the starting position after the “throw” of the linkage assembly  138  is complete. 
     The construction and coaction of the drive finger  140  and the driven arm  142  of the linkage assembly  138  is such that a pair of springs  93  can be employed. That is, in addition to the spring  93 , another spring (not shown), or a plurality of springs can be attached to the driven arm  142  at an opposite side to which the spring  93  is attached, and then to a corresponding portion of the side wall  120  to facilitate movement of the linkage assembly  138  in either direction. 
     The augmenter  110  is not limited to having only an extension spring such as that shown in FIG.  6 . The device can be constructed with a combination of extension springs and torsion springs to operate as the biasing element  93 . 
     It is preferred to mount the biasing element  93  as shown, as this position is proximate to the region of pivotal coaction between the drive finger  140  and the driven arm  142 , thereby most effectively using the biasing force of the spring  93 . 
     Another embodiment of an augmenter  210  constructed in accordance with the present invention is illustrated at FIG.  7 . Elements illustrated in FIG  7 . which correspond to elements described above with respect FIGS. 1-5 have been designated by corresponding reference numerals increased by  200 . The embodiment of FIG. 7 is designed for use in a manner similar to that shown with respect to the embodiment of FIGS. 1-5, unless otherwise stated. 
     In FIG. 7, a drive finger  211  has a first end from which a cylindrical portion  244  extends. The cylindrical portion  244  is provided with a hex or other multi-sided aperture extending completely therethrough. The half  216  is similarly provided with an aperture which is in registration with the aperture  246  of the half  214 , such that when the halves  214 ,  216  are mated, the multi-sided aperture  246  of the drive finger  211  is accessible from an exterior of the half  214 . This permits the user to extend the drive input A completely through the housing regardless of the length of the input A. The drive finger  211  is constructed with a side wall generally shown at  13  which substantially conforms to the shape of the upstanding side wall  220  of the half  216 . 
     As shown in FIG. 7, a side wall  215  of the drive finger  211  is constructed to rest against the complimentary shaped side wall  220  extending from the half  216 . This permits the drive finger  211  to pivot in position and rest against an inner surface  234  of the side wall  220 . 
     An opposite end of the drive finger  211  is formed with a rack of teeth shown generally at  217 . The rack  217  extends completely along this end of the drive finger  211  and is of a particular thickness and pitch for coaction with other elements of this embodiment as discussed below. 
     A transfer gear  219  is disposed for pivotal movement between the halves  214 ,  216 . The transfer gear  219  is mounted to the half  216  by a pin  21 . A plurality of teeth  223  extend along a peripheral edge of the gear  219 , which teeth  223  are constructed and arranged for releasable mating engagement and contact between corresponding teeth  217  on the drive finger  211 . During a torque operation, at least three or four, and preferably five of the teeth  217 , 223  on the drive finger  211  and the transfer gear  219 , respectively, are in contact to provide strength and stability during the torque operation. 
     The driven arm  255  in FIG. 7 is provided with a rack of teeth  27  extending along a peripheral edge of a portion thereof. The pitch of the teeth on the rack  27  of the driven arm  255  is equal to the pitch on the teeth  217  on the drive fingers  211 . The rack of teeth  27  is of a thickness and pitch to facilitate releasable mating contact with the teeth  223  of the transfer gear  219 . At least three or four, and preferably five teeth of the transfer gear  219  and driven arm  225  mesh during a torque operation to facilitate strength and stability of the device during the operation. 
     Springs (not shown) can also be used with the embodiment of FIG. 7 to bias the drive finger  211  and driven arm  225  to their selective positions. 
     The embodiment of FIG. 7 operates as follows. 
     The drive input A is inserted into the aperture  246  and turned in the direction of arrow  294 . The drive finger  211  is moved in a counter-clockwise direction with the teeth  217  thereof in engagement with the teeth  223  of the transfer gear  219 . The transfer gear  219  in turn rotates in a clockwise direction as shown by the arrow  229 . This motion of the transfer gear  219  causes the driven arm  255  to move in a clockwise direction as indicated by the arrow  298  to impart a rotational movement to the teeth  286  of the ratchet  288 . The hex socket  290  is also moved in a clockwise direction to turn the bolt or stud being tensioned. When the hex socket  290  has been turned down on the bolt or stud through a complete “throw” of the turning operation, the device is returned by the user in an opposite direction for the driven arm  255  to ride over the teeth  286  to prepare for a subsequent torquing operation during which the teeth  286  of the ratchet  288  are engaged to subsequently cause the hex socket  290  to tighten down the bolt. 
     The height of drive finger  211  and driven arm  255 , in combination with locking means (not shown) for the housing function as a guide for  211 , 225 . 
     The construction of the teeth used for the drive plate  211 , transfer gear  219  and driven arm  255 , are selected for gear backlash to be within tolerable limits so that slippage is reduced as much as possible upon reversal of the gear rotation. 
     As shown in FIGS. 1-5, the wrench with augmenting device can be used as a simple hand wrench tool to either tighten or loosen nuts to another fastener. The socket of the wrench is fitted over the item to be loosened or tightened in the same manner that a ratchet type socket wrench would be fitted over any standard item to be wrenched. Note that nesting sockets (not shown but well known in the art) could be used to modify the size of the engaging socket in order to give the tool a wider range of operative use. The tool also has a relatively narrow rim between the socket and the outer edge of the tool surrounding the socket. This enables the tool to be placed into relatively narrow areas which is often the case with bolting circles and other areas which provide limited access for the worker. The tool is then operated as a standard ratchet socket wrench. The handle is rotated about the socket to loosen or tighten the item that is to be wrenched. In an instance where a high torque is necessary; either to “break” or dislodge a nut or other fastener which tends to become frozen in place, or to “snug up” the item to be tightened when it is no longer possible to easily move the handle of the wrench, then the augmenting feature of the wrench is employed. A mating drive fits into the drive socket or receptacle in the bottom of the handle. This drive implement can be a relatively long bar or it can be connected to the output drive of a mechanical or pneumatic device. The auxiliary drive member is then actuated to rotate the driven socket in the handle, which actuates the linkage in the handle of the wrench to rotate the socket through a limited angle as discussed. This limited angle will be sufficient to tighten or loosen the item that is being acted upon by the wrench. If it turns out that the linkage in the handle of the wrench has “stopped out” or run its full travel without reaching the desired level of torque being applied by the actuating socket of the wrench then the auxiliary torque apparatus can be reversed. The rachet feature of the wrench, will allow the linkage within the handle to return to the initial position. The auxiliary torque apparatus does not have to be removed from the drive socket at the bottom of the handle, but merely rotated in a direction opposite to the force applying direction because the ratchet feature will allow the linkage within the handle to return to its initial position. 
     The wrench of course can be used to tighten or loosen, merely by turning the wrench over, and using one face for turning in a clockwise direction and the other face for turning in a counter clock-wise direction. As shown in FIGS. 2-5, the front and back halves of the housing have ridges which coact with and guide the grooves in the driven arm of the linkage over a relatively wide area. Additionally, the sides of the driven arm are shaped to conform with or abut the interior side walls of the linkage along a long length of the driven arm. This will tend to dissipate the force that will be applied to the housing by the linkage when the linkage is “stopped out” at the end of its travel. Similarly, the pin arrangement and slotted drive finger allow for relatively wide contact surfaces to minimize wear. The ridges or raised portions on the driven arm which surround the rachet at the lower end which form the groove for the ridges from the housing act as a stiffening member when the pieces are assembled to provide strength for the handle making the tool relatively rugged but still operable. 
     The ratchet and socket arrangement is relatively simple and reliable, and the wear features of the construction insure not only that the life of the tool will be relatively long, but its operation will be relatively easy. 
     Shown in FIG. 6 are a variety of springs which can also be used to bias the driven arm of the apparatus. The springs can be compression springs or torsion springs. 
     As shown in FIG. 7, the apparatus can also be built in a variety of ways such as by use of an idler gear between two gear racks, which replaces the linkage. 
     Referring to FIGS. 8-10, there is shown another embodiment of the invention at  310  having a symmetrical arrangement in which a pair of drive sockets  312 , 314  are provided, each driven from a link  316  connected to the driven middle socket  318 . The drive sockets  312 , 314  and link  316 , as well as other elements of this embodiment discussed below, are disposed in a housing  320  for the augmenter  310  consisting of releasably engagable halves  322 , 324 . The same form of linkage shown in FIGS. 2-6 is present in the augmenter  310 , with the oval pin  326  rising in slot  328  in the driven arm  330  of region A, and oval pin  332  rising in slot  334  from the driven arm  336  in region B. A similarly constructed ratchet and pawl arrangement  338 , 340  is used with respect to each of the drive sockets  312 , 314  at each end of the wrench. Driving the driven aperture  342  of the socket  318  will cause rotation of the link  316  with the opposing driven arms  330 , 336 . The drive fingers  344 , 346  rotate the driven arms  330 , 336  to rotate the adjacent ratchet assemblies  338 , 340  until the driven arms  330 , 336  abut a respective opposed side of the housing  320  along the length of the arms  330 , 336 . 
     The driven or middle link  316  has torsion springs  348 , 350  on either side attached to the adjacent wall of the housing. The springs  348 , 350  each slide as the middle link is rotated, and tend to urge the middle link  316  into the initial position as shown in the drawing. 
     The various guides, slots and grooves that are shown in FIGS. 1-7 on the front and back walls of the housing, and on the driven arms of the apparatus can also be included in the structure of the embodiment shown in FIGS. 8-10, and the embodiment shown in FIGS. 11 and 13. 
     While the augmenter  310  is shown having parallel sides and is relatively symmetrical, these dimensions will vary depending upon the size of the drive sockets  312 , 314  at either end of the device and the intended use of the tool. 
     If, for example, it is desired to have a longer throw for each cycle of the augmenter  310 , then the central portion of the tool between the drive sockets  312 , 314  can be widened as shown and discussed with respect to FIG.  13 . This will provide a longer distance for the driven arms  330 , 336  to travel and therefore, increase the angle for each cycle. 
     Additionally, the size of the drive sockets can vary from less than an inch to more than 9 inches to accommodate nuts which fasten to studs of 6″ or more in length. 
     The system is well suited for use with external torquing devices, such as a commonly available impact wrench  380  shown in FIG.  12 . This impact wrench  380  has a transmitting end  382  which is driven by a slide collar  384 , that will oscillate back and forth, to engage and disengage the finger  386  extending from the collar to ride on camming surface  388  connected to the transmitting end  382 . When the torque exerted by a motor  390  is sufficiently high to cause the torque level adjusting spring  392  to retract, the engaging finger  386  will ride up the cam surface  388  to a point such that the spring  392  is compressed sufficiently to enable the finger  386  to disengage from the camming surface  388  and allow the device to rotate internally without externally rotating the transmitting end of the device. 
     By inserting the transmitting end of the impact wrench into the driven socket  318  at the middle of the augmenter  310 , the drive link  316  will rotate the drive fingers  344 , 346 . 
     The housing halves  322 , 324  are joined together as shown in FIG. 9. A gasket  366  is interposed between the halves to seal a lubricant, such as grease for the elements, within the augmenter  310 . The gasket can be formed by filling corresponding grooves in the mating surfaces of the housing with a substance that will cure to form a gasket. 
     There is a coaction between the internal spring of the impact wrench which causes the periodic application of torque, and the internal springs  348 , 350  connected to the link  316 . The impact wrench produces an increase in torque and rotation until disengagement occurs between the drive finger and the camming surface. During movement of the impact wrench, the driven or middle link  316  of the augmenter  310  will move from the initial position as shown in FIG. 10 to a position at the opposite end of its travel against the other wall. When the spring of the impact wrench causes disengagement, the torque asserted is suddenly substantially reduced and the spring arrangement  348 , 350  of the augmenter will then cause the middle link  316  to rotate to the initial position shown in FIG. 10, bringing each one of the driven arms  330 , 336  up flush against a respective side of the inner wall  364  of the housing. 
     As the collar of the impact wrench  352  rotates in the direction of the arrows surrounding middle aperture  342 , or in a counter-clockwise direction, the driven arm will rotate in the clockwise direction to rotate the driven socket  318  until the opposite side of the driven arm abuts the inner wall  364  of the housing. 
     To use the augmenter  310  to remove a fastener, the augmenter is turned over so that the angles are reversed and the direction of the impact wrench is also reversed. 
     As shown in FIGS. 9 and 10, the elements for the augmenter  310  are symmetrical about the central transverse axis  362 . Regions A and B of the augmenter  310  at opposed sides of the axis  362  include elements which function in a symmetrical manner of operation. This provides for even torque augmentation during cycling and recycling, and relatively equal amounts of stress and wear upon the operable elements of the device. 
     FIG. 11 shows another embodiment of the augmenter invention shown generally at  410 , in which a middle link  416  has two ears  466 , 468 , which are used to connect compression springs  470 , 472 , respectively, to the sidewall  464  of the housing. The compression springs  470 , 472  function in the same manner as the torsion springs  348 , 350  shown in FIG. 10, i.e. the function to position the middle link  416  to one extreme position to urge the driven arms  444 , 446  abutted against the wall  464 . 
     FIG. 13 shows still another embodiment of the augmenter invention according to the present invention which is shown generally at  510 . In this embodiment, a sidewall  568  of the augmenter  510  is bowed or widened at opposed sides shown generally at  570 , 572 , with the apex of each widened portion occurring at approximately the transverse axis  562  of the housing for the augmenter  510 . As with the embodiments in FIGS. 8-11, elements of this embodiment of the augmenter  510  are symmetrical at opposed sides of the axis  562 . The widening of the sidewall  568  of the housing provides for an increased throw of the central link  516  so that the respective driven arms  530 , 536  will proceed along the direction of the arrows  574 , 576 , respectively, wherein the arms  530 , 536  abut a corresponding region of the sidewall  568 . Because the arms  530 , 536  have to travel further for abutment with the sidewall  568 , there is an increase in throw over that which is provided with the embodiments at FIGS. 8-11. 
     Accordingly, from the above description, the mechanical advantage that is imparted by means of the augmenter wrench can be varied depending upon the relative lengths of the driven arms and the drive fingers engaging the driven arms. An equal length of the driven arms in relation to the drive fingers will produce a neutral mechanical advantage. A positive mechanical advantage will result if the lever arm of the drive finger is longer than the lever arm of the driven arm and vice versa, if it is shorter. In the Figures, the drive finger is shown shorter than the driven arm thereby reducing the torque provided to the drive sockets below the torque provided to the middle driven socket. 
     The device of the present invention not only can act as an effective tool for manually tightening a fastener up to a certain extent, but the device offers significant advantages when working with an impact tool in confined spaces or spaces having relatively low clearance. The device is relatively narrow at the drive socket to fit over a bolt, or for a socket to be placed within the drive aperture to engage a nut. When the impact tool engaged with the augmenter relaxes, or there is a lull in the torque cycle, the internal springs of the augmenter will force the driven arm to the extreme initial position and the cycle will repeat itself. The combination of the impact tool and the augmenting wrench will continue to cycle until the torque necessary to rotate the driven arm is greater than the torque that is exerted by the impact wrench. In effect, the device dead ends when the pressure of the spring on the drive collar will be insufficient to rotate the driven arm of the augmenter. 
     A drive arm is mounted for coaction with the ratchet and has a somewhat triangular shape extending toward a more central portion of the housing. 
     The distance between the drive socket and the driven aperture affords clearance so that an impact tool such as shown in FIG. 12, can be applied to the augmenter at a substantial offset distance from the fastener acted upon. 
     A continuous gasket extends along the surface area of each one of the halves where the halves contact each other to form the housing. The elements described with respect to FIGS. 8-11 are bathed in grease to provide lubrication and cooling during the highly repetitious movement of the elements when being driven by the impact wrench. 
     The movement of the impact wrench in the drive receptacle causes each one of the sockets to move in an opposite direction in the ratio of the lever arms. That is, the sockets will rotate at the opposite ratio of the mechanical advantage. 
     In FIG. 14, another embodiment of a wrench having torque augmenting means is shown generally at  600 . The housing  602  for the wrench is formed of two halves  604 , 606  (see also FIG. 17) for the bottom and top, respectively, which are held together with case screws positioned at  608 - 614 . For reference purposes, a front end  616  of the wrench includes a ratchet  618  with teeth  620  and a pawl  622  with corresponding engaging teeth  624  mounted for coaction with each other. The pawl  622  is biased for coaction with the ratchet  68  by a spring  626 . The pawl  622  and spring  626  are supported on a drive or lever arm  628  formed with a recess  630  to receive the pawl  622  and spring  626 . The pawl and spring are adapted for coaction with the ratchet  618  during a torque operation. A drive or torque output  632  for this embodiment can be either a male drive element or a female drive element such as a socket. 
     The housing  602  is provided with at least one, and in a preferred construction, a pair of threaded bores  634 , 636  in each of which is inserted a corresponding pair of friction control screws  638 , 640  of this drag means for providing “drag” upon the ratchet  618 . The friction control screws  638 , 640  of this drag means prevent the ratchet  618  from losing the initial torque obtained at the very beginning of a torque operation. 
     A drive or power input  642  is disposed substantially at a center of the housing  602 . The drive input  642  is adapted to receive a male member, or can be fitted with an adapter to extend therefrom and receive the female drive member such as a socket. 
     A linking means  644  such as a reaction arm having three lobes  644 A-C or ears is mounted to a circular bushing  645  supported at the drive input. The linking arm  644  turns at the bushing  645  in conjunction with movement of the drive input  642 . A bottom floor  646  of the housing  602  is constructed and arranged to provide for movement of the linking arm  644  within the casing  602 . 
     The drive output  632  and the drive input  642  are accessible from either side of the casing  602 . 
     A connecting means such as a first pin  648 A connects the first lobe  644 A or transmission lobe of the linking arm  644  with the lever arm  628 . A second pin  648 B connects the second ear  644 B or return lobe of the linking arm  644  to a compression spring  650  mounted in a receptacle  651  at an end  652  of the housing  602  substantially opposed to the end  616  of the housing in which the torque output  632  is arranged. The compression spring  650  includes a mounting plate  654  having an aperture  656  therethrough which is constructed and arranged to receive the second pin  648 B and permit the second pin  648 B to move during pivoting of the linking arm  644 . A support stud  658  extends from the mounting plate  654  and is attached to an end of the compression spring  650 . The opposite end of the compression spring, as mentioned above, is mounted at an interior of the housing  602  in the receptacle  651  as shown generally at  660 . The compression spring  650  forces the linking arm  644  in the direction of arrow  662 . 
     A third connecting means such as pin  648 C connects a third one of the lobes  644 C or power lobe of the linking arm  644  to piston means  664  or a plunger which extends into a cylinder  666  in the housing  602 . A seal  668  extends around a head  670  of the piston  664 . 
     A chamber  672  for the cylinder  666  is in communication with a passageway  674  leading to an inlet  675  which can be connected to a valve  676  or other hydraulic source/device external to the housing  602  for the wrench  600 . 
     Slots  643 A-C are provided for corresponding pins  648 A-C to move therein during pivotal movement of the linking arm  644 . 
     The arcuate guide bar  36 , and ridges  62 , 66  and  64 , 67 , and grooves  58 , 60  of FIGS. 2 and 3 can also be included in the embodiment shown in FIGS. 14-18, but are not shown in FIGS. 14-18 for purposes of clarity. These elements function similar to that disclosed and described with respect to FIGS. 2 and 3. 
     In operation, the wrench  600  is used by inserting a drive member into the power input  642  and torquing the input to pivot the linking arm  644  in a clockwise direction. Referring also to FIG. 15, this motion will accordingly force the drive arm  628  in a clockwise direction thereby providing the torque and permitting the teeth  624  of the pawl  622  to engage the ratchet teeth  620  and retain the next advanced position with respect to the ratchet  618 . 
     Alternatively, if an impact wrench  380 , such as that shown in FIG. 12, is inserted into the power input  642  for the wrench  600  of the present invention, the repetitive cycling of the impact wrench  380  will provide the necessary torquing strokes. The spring  650  will force the linking arm  644  in a counter clockwise direction upon termination of each stroke during the lull or slip of the impact wrench  380 . 
     The power input  642  can be bypassed in those instances where a hydraulic line is connected to the valve  676  of the wrench  600 , thereby employing the piston  664  to force the linking arm  644  in a clockwise direction against the spring  650 . After completion of the stroke of the linking arm  644 , the brief interval of slip permits the spring  650  to bias the linking arm  644  in a counter clockwise direction to reset for a subsequent torquing stroke. 
     Torque output for the wrench shown in FIG. 14 is determined by the ratio of the distances D 1  and D 2 . The 2:1 ratio corresponds to the distance indicated at D 1  with respect to the distance at D 2 , thereby providing the 2:1 ratio for torque input to torque output. 
     In FIGS. 15 and 16, another embodiment of the wrench shown in FIG. 14 is disclosed. In this embodiment, the elements are referred to by numbers increased by  100  so that the wrench is shown generally at  700 . All of the elements operate substantially the same as those disclosed in FIG. 14, unless otherwise stated. A cylinder  766  for the piston  764  is modified to receive and retain the spring  750 . In this manner of construction, the spring  750 , piston  764  and cylinder  766  are assembled as a unit in the housing  702  for the wrench  700 . 
     The torque output provided by the wrench as shown in FIG. 15 is obtained from the formula, torque output=(F 1 ×D 1 )÷(F 2 ×D 2 ) where: 
     F 1  is the force applied at the piston  764 ; 
     D 1  is the distance traveled by the piston  764 ; 
     F 2  is the force applied to the reaction arm  744 ; and 
     D 2  is the distance that the drive arm  728  travels. 
     In FIG. 15, the compression spring  750  is mounted at one end in the cylinder  766  at  760 . An opposite end of the spring is received in a sleeve  780  or a collar which extends to the mounting plate  754  through which the second pin  748 B is disposed. The construction of the spring  750  and piston  764  arranged in the same cylinder  766  provides for more stable torquing and recoiling operations, and a reduction in vibration under extreme pressures. FIGS. 15 and 16 show the beginning (FIG. 15) position of the wrench  700  according to the present invention as it proceeds through a first stroke (FIG. 16) just prior to the subsequent slip that would occur if used with an impact wrench (FIG.  12 ), or the return of a hand operated device at the power input  742  for another subsequent stroke of torquing force. 
     Referring to FIG. 16 in conjunction with FIG. 15, there is shown movement of the piston  764  in the direction of arrow  782  to force the linking arm  744  in the direction of arrow  784 . As the linking arm turns clockwise all the way to the stops  786 , 788 , the sleeve  780  is forced in the direction of the arrow  790  so that the spring  750  is compressed in the cylinder  766 . 
     During the pivoting of linking arm  744 , it can be seen that the drive arm  728  is pivoted in the direction of the arrow  792  until the drive arm  728  contacts the stop  786  in the housing  702 . As the drive arm  728  turns, the teeth  724  of the pawl  722  are biased into engagement with the teeth  720  of the ratchet  718  to provide for a torque stroke at the drive output  732 . Accordingly, the drive output  732  turns in the direction of the arrow  794 . 
     FIG. 17 shows a cover  706  or the other half of the housing  702  for the wrench  700  shown in FIGS. 15 and 16. This cover  706  can also be used with the embodiment shown in FIG. 14. A legend or table of the relationship of the PSI and TORQUE (foot lbs.) is shown generally at  796  and is provided on the cover for purposes of cross-referencing during the torque operation. A broken line  798  indicates the position of a gasket used when the halves of the housing are joined together. 
     FIG. 18 shows a dual-pawl assembly for another embodiment of the present invention. In this arrangement, pawls  822 A, 822 B are of similar construction and have corresponding teeth  824 A, 824 B. The pawls are disposed in respective recesses  830 A, 830 B of the drive arm  828 . The pawls  822 A,B include springs  826 A,B to be biased with respect to the ratchet teeth  820 . It is preferred that when the teeth  824 B of, for example, the pawl  822 B have engaged the corresponding teeth  820  of the ratchet  828 , the teeth  824 A of the pawl  822 A are no more than half way into engagement with corresponding teeth  820  of the ratchet  818 . With this arrangement, as the torquing continues, and the pawls teeth  824 B are extracted, the other pawls teeth  824 A move into close engagement with the ratchet teeth  820  to prevent any loss of torque already obtained. In all other aspects, the elements and operations thereof are the same as those shown with respect to FIGS. 14-16. 
     It will be understood that the embodiments described herein are merely exemplary and that a person skilled in the art may make many variations and modifications without departing from the spirit and scope of the invention. All such modifications and variations are intended to be included within the scope of the invention as defined in the appended claims.