a weld gun apparatus 10 according to the present invention bonds a workpiece , such as work elements 12 and 14 , with pressure applied by first and second electrodes 16 , 18 contacting and loading opposite sides 20 , 22 of the workpiece during a welding operation . a pair of tongs 24 , 26 position the first and second electrodes 16 , 18 with respect to the workpiece 12 , 14 to contact and load opposite sides 20 , 22 of the workpiece 12 , 14 while the tongs 24 , 26 rotate with respect to one another about a pivot axis , such as pivot pin 28 . the weld gun apparatus 10 according to the present invention centers the pair of tongs 24 , 26 relative to a predetermined planar position for the welding operation to be conducted on the workpiece . the tongs 24 , 26 when placed in an open position with respect to the predetermined planar position , permit the workpiece elements 12 , 14 to be inserted , properly positioned and clamped , if necessary . the weld gun apparatus 10 ensures alignment of the welding electrodes at the desired position for welding the workpiece and compression of the work elements 12 , 14 together required for welding . after welding , the weld gun apparatus 10 ensures separation of the electrodes from the workpiece to allow removal of the welded workpiece and installation of new work elements for welding . the electrodes 16 , 18 carried by opposing ends of the pair of tongs 24 , 26 approach the predefined welding position relatively precisely while allowing for a small deflection , or self adjustment , to compensate for variations in work element dimensions as well as to reduce , or preferably eliminate deformation of the work elements 12 , 14 , in those cases when the work elements are slightly out of the predefined welding plane . in operation , the pair of tongs 24 , 26 are initially in the position as illustrated in fig2 with the electrodes 16 , 18 spaced from the work elements 12 , 14 being inserted into the workstation for welding . appropriate stop limits ( not shown ) may be provided for limiting rotational movement toward the fully open position for each of the pair of tongs 24 , 26 as shown in fig2 . means 30 is provided for driving the pair of tongs 24 , 26 with respect to the pivot axis to move the electrodes 16 , 18 toward and away from one another to contact and load opposite sides 20 , 22 of the work elements 12 , 14 during the welding operation . the driving means 30 can include a pressure actuated means 32 for moving the electrodes 16 , 18 , such as a pneumatic or hydraulic cylinder 34 and associated plunger 36 . after pressure is supplied into the pneumatic or hydraulic cylinder 34 , the plunger 36 is pushed outward with respect to the pneumatic or hydraulic cylinder 34 which may result in one or both tongs rotating about pivot pin 28 . the driving means 30 can also include electric means , such as an electric reversible servo - motor for moving the electrodes 16 , 18 . the counterbalance mechanism compensates for the weight of the weld gun and for inertia to greatly reduce the potential for damage to the product to be welded . the pneumatic cylinder 34 and plunger 36 then load the opposite sides 20 , 22 of the work elements 12 , 14 by compressing the work elements between the first and second electrodes 16 , 18 with sufficient pressure or force during the application of electric current therethrough to complete the welding operation . the welding operation is accomplished by heating the workpiece with electric current passing through the first and second electrodes 16 , 18 and through the work elements 12 , 14 producing a weld cross - section which is generally circular . with the welding gun apparatus 10 now in the position as illustrated in fig1 the pair of tongs 24 , 26 are in a closed position during the welding operation . after welding is completed , pressure is supplied to the pneumatic or hydraulic cylinder 34 to draw the plunger 36 into the cylinder 34 . in the case of an electric servo - motor , power is applied to the motor to reverse the rotation of the motor and drive the electrodes 16 , 18 away from one another . by way of example and not limitation , the tongs 24 , 26 separate from the workpiece generally simultaneously since the weld gun apparatus is in a balanced condition about pivot pin 28 when in or immediately adjacent the closed welding position . one of the tongs , such as tong 26 may travel about pivot pin 28 further than the other tong until the tong reaches a rotational limit , placing the weld gun apparatus 10 generally in the open position shown in fig2 . it is believed that the tong connected to the counterbalancing means 38 will preferably be the tong that travels a shorter rotational distance between open and closed positions . the tongs 24 , 26 may be moved to an intermediate open position ( not shown ) to allow movement of the weld gun apparatus along the joint of the workpiece formed by the work elements 12 , 14 for performing multiple welds before opening the tongs 24 , 26 to the fully open position of fig2 for removal of the finished , welded workpiece and insertion of new work elements 12 , 14 to be welded . means 38 is provided for counterbalancing the effective weight or mass and moment force of the weld gun , including tongs 24 , 26 , electrodes , 16 , 18 and driving means 30 with respect to the pivot pin 28 . the counterbalancing means 38 is disposed with respect to the pivot axis , such as pivot pin 28 , for balancing the tongs 24 , 26 , electrodes 16 , 18 and driving means 30 with respect to the pivot axis when in , or immediately adjacent to , the closed or welding position . preferably , the counterbalancing means 38 includes a torsion spring 40 positioned about the pivot axis and operably connected to one of the pair of tongs 24 , 26 at one end of the spring . as best seen in fig1 and 3 , the torsion spring 40 is enclosed within a housing 42 having a generally cylindrical wall 44 with gear teeth 46 formed around at least a portion of the external periphery thereof . the gear teeth 46 preferably extend around the entire external periphery of the cylindrical wall 44 of the housing 42 . in addition , the gear teeth 46 preferably take the form of zero - backlash teeth for engagement with a driving gear 48 , such as a worm gear , which may take the form of a double enveloping worm gear and gear teeth combination . preferably , the gear teeth 46 and driving gear 48 have zero backlash and are self - locking in either rotational direction . the housing 42 has at least one radially extending end wall 50 with an aperture 52 formed therein for rotatably receiving a portion of the pivot pin 28 so that the pivot pin 28 can rotate independently of the housing 42 . within the housing 42 , a spring seat 54 is formed for engaging and anchoring one end 56 of the torsion spring 40 . the spring seat 54 may take the form of an axially extending protrusion from the radially extending end wall 50 adjacent the inner surface of the cylindrical wall 44 of housing 42 as best seen in fig1 and 3 . the opposite end 58 of the torsion spring 40 is engaged within an axially extending slot 60 formed in an outer end of the pivot pin 28 engaged within the housing 42 . the pivot pin 28 is connected to one of the pair of tongs , such as tong 24 by suitable means , such as connection pin 62 . the connection pin 62 couples the pivot pin 28 and tong 24 to one another so that the biasing action of the torsion spring 40 acting on pivot pin 28 results in balancing rotational forces acting on the tong 24 including the rotational force imparted by gravitation forces acting on the effective weight or mass of the actuating means 32 and connected tong 26 . the other tong 26 is rotatably connected about pivot pin 28 . pivot pin 28 is supported through one or more apertures 64 formed in a support bracket 66 for supporting the weld gun apparatus 10 in any desired position and orientation . the driving gear 48 is rotatably supported by a gear housing 68 connected to the support bracket 66 . means 70 is provided for adjusting the balancing or biasing force of the torsion spring 40 . the adjusting means 70 can be manually actuated , or automated if desired . as shown in fig1 the adjusting means 70 can include an outwardly extending end of the shaft fixedly connected to the driving gear 48 having a hex head 72 , or other suitable member 72 capable of being driven , such as a spline , slot , socket , or the like . the member 72 is fixedly connected to the driving gear 48 allowing rotation of the worm gear with a manual wrench , power driven socket or other suitable driver . rotation of the driving gear 48 by engagement with the hex head 72 causes corresponding rotation in the housing 42 through meshing engagement of the gear teeth 46 formed on the external periphery of the housing 42 with the driving gear 48 . the one end 56 of the torsion spring 40 engaged with spring seat 54 formed with or connected to the housing 42 causes a corresponding change in torsional biasing force depending on the direction of rotation of the housing 42 . as shown in fig1 rotation of the housing 42 in the clockwise direction increases the torsional biasing force , while rotation of the housing 42 in the counter - clockwise direction causes a reduction in the torsional biasing force of torsion spring 40 . if required , the torsion spring 40 can be positioned in housing 42 with a counter - clockwise spiral orientation , rather than the clockwise spiral orientation as shown in fig1 and 2 . depending on the placement , either clockwise or counterclockwise , of the torsion spring 40 in the housing , the torsional biasing force can be increased by rotation in a first direction and can be decreased by rotation in an opposite second direction . means 74 for insulating is provided to electrically isolate the pair of tongs 24 , 26 from one another and to isolate the pair of tongs 24 , 26 from the pivot pin 28 , counterbalancing means 38 and support bracket 66 . in operation , the torsion spring 40 counterbalances the distributed weight of the pair of tongs 24 , 26 and driving means 30 with respect to pivot pin 28 when in the closed position as illustrated in fig1 . this counterbalancing prevents undue force or impact of the electrodes 16 , 18 with the opposite sides 20 , 22 of the work elements 12 and 14 while moving to the closed position of fig1 from the open position of fig2 . once the torsion spring 40 biasing force is set to the appropriate amount in order to accomplish counterbalancing when in the closed position as illustrated in fig1 no further adjustment of the torsion spring 40 should be necessary . currently , high carbon content steel torsion springs 40 are being tested in order to determine the expected lifetime between failure , and to determine the desirability of using non - magnetic and / or non - electro - conductive torsion springs made of composite material , such as a carbon plastic fiber or fiber - glass . while the invention has been described in connection with what is presently considered to be the most practical and preferred embodiment , it is to be understood that the invention is not to be limited to the disclosed embodiments but , on the contrary , is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims , which scope is to be accorded the broadest interpretation so as to encompass all such modifications and equivalent structures as is permitted under the law .