Abstract:
A system for automatically producing formed parts from feedstock using two successive adiabatic processing stations, a first station performing adiabatic cut-off of blanks from the feedstock, and the second station performing adiabatic forming of the blanks into the formed parts. The first station operates cooperatively with a feedstock feeder assembly which feeds feedstock to the first station and also charges blanks produced at the first station into a transfer capsule of a transferer assembly. The first and second stations cooperatively operate with the blank transferer assembly which transfers in the transfer capsule blanks from the first to the second station. The second station includes means for positioning blanks relative to a forming cavity before blanks are adiabatically shaped to conform to the forming cavity and also means for ejecting formed parts from tooling that defines the forming cavity. The system includes automation means that synchronizes and sequences subassembly operations.

Description:
FIELD OF THE INVENTION 
     This invention relates to an automated, integrated, synchronized part forming system that incorporates two adiabatic processing stations which each have multiple operating stages whereby, progressively and successively, elongated feedstock is cut into blanks that are formed into parts. 
     BACKGROUND OF THE INVENTION 
     High speed impact systems for metal and plastic working, such as cut-off and forming or shaping, using the adiabatic softening phenomenon, although the subject of research and development since World War II, have proven to be difficult to achieve, control and use for mass production. 
     The energy utilized involves very high impact speeds and very short machine tool engagement times. In adiabatic forming, each part (or work piece) requires a certain amount of applied energy to be completely formed. That energy can be distributed and should never be provided by impact alone. In successful adiabatic forming, the energy delivered to a work piece is critical as no tooling can stand up to the magnitude of the shock waves created by full energy impacts. 
     It was discovered that limited forming and tool engagement time reduced the opportunity for heat to transfer into surrounding tooling. When a work piece cannot conduct heat away at the rate at which it is generated, the work piece temperature increases in a pre-determined, plastically strained zone, causing the work piece material to soften and experience decreased flow stresses, resulting in reduced energy requirements to move the material. It was found that a successful adiabatic forming operation could be achieved based on a two-part sequence of impact and immediately succeeding power stroke (or force application). In a work piece heated by impact, the heat pattern relates to the final form; some areas remain at ambient temperature while other areas may reach temperatures close to melting point. Such elevated temperatures minimize flow resistance and stresses, reduce tooling load and allow material flow into relatively small crevices. At this point, a power stroke immediately follows impact and completes a part forming operation with little resistance. Thereafter, the formed part is ejected. The adiabatic impact and power stroke part forming sequence and the part ejection from adjacent tooling are rapidly carried out. 
     An impact press device capable of providing a suitable impact for adiabatic forming is disclosed in Lindell U.S. Pat. No. 4,245,493. A tooling assembly that is suitable for use with such an impact press and that is adapted for the cut-off of elongated feedstock into blanks is disclosed in Lindell U.S. Pat. No. 4,470,330. 
     Adiabatically formed parts are desirable and even superior to parts produced by conventional forming processes because they can be rapidly produced, and are uniform and free from defects, such as burrs, work/strain hardening, pull-down and micro-cracks. 
     For use in the mass production of parts, practical automatic adiabatic forming systems are desirable and needed, but the systems must also be reliable, operable at high piece throughput speeds, and require minimum manpower. An adiabatic part forming system that is capable of converting elongated starting stock into formed parts rapidly and in an automatic manner would be very useful. Such a system would require both an adiabatic processing station for the cut-off of elongated feedstock, such as stock in the form of a bar, tube or coil, for example, into blanks, as well as an adiabatic processing station for forming of blanks into parts. Each station and the entire system would have to be capable of high throughput rates. 
     Particularly when the stations are substantially independent, such a system would require a stock feeder, an interstage blank transferer, and sychronization means. The stock feeder would have to be integrated with the first station stock cut-off device, and be adapted both for feeding and positioning of elongated stock and also for the separation and advancing of blanks. The inter-station blank transferer would have to be integrated with both the first station and the second station, and be capable of receiving blanks from a first station location, of transporting blanks from the first station to the second station, and of depositing blanks at a second station location. The synchronization means for operating the system would not only have to control the operation of the respective multiple sequential operating stages of each station, but also have to integrate operations of the stock feeder and the interstage blank transferer with the operations of first station and the second station. 
     Mere adaptations by those of ordinary skill in the art of prior art adiabatic impact devices for accomplishing adiabatic cutting or shaping of work pieces with high throughput rates may be possible, but such adaptations by themselves, even if achieved, would be inadequate without suitable peripheral equipment, such as a suitable stock feeder, a suitable interstation blank transferer and suitable automation means. A combination of suitable components is needed to achieve an automatic, integrated, adiabatic forming system capable of operating at high throughput rates. Such a system has never previously existed so far as now known. Indeed, to create such a two-station adiabatic blank cut-off and part forming system, not only must significant, nonobvious advances in adiabatic cutting and shaping stations be achieved, but also the indicated coacting peripheral required subassemblies must be invented because such subassemblies have not previously existed. 
     The present invention aims not only to achieve the components necessary for such a system, but also to achieve the combination of such components into such a system, thereby to satisfy the need for such an adiabatic forming system. To create the present system, substantial technological advances in the art have been necessary. 
     SUMMARY OF THE INVENTION 
     This invention relates to an automated, integrated, synchronized part forming system that incorporates two adiabatic processing stations that operate sequentially relative to one another. First, an adiabatic blank cut-off station progressively and successively cuts elongated feedstock into identical blanks. Next, an adiabatic part forming station progressively and successively forms the blanks into identical parts. Each station has its own multiple, sequential, cyclical operating stages. 
     The cut-off station cooperatively operates with a stock feeder subassembly. The cut-off station and the forming station cooperatively operate with an interstation blank transferer subassembly. The system includes synchronizing, sequencing and regulating automation means effective for all components. 
     The invention also relates to component subassemblies that are incorporated into the system and make possible the practical operation of the inventive system which includes the respective adiabatic forming stations, the stock feeder subassembly, the interstation blank transferer subassembly and the automation means. 
     The invention involves apparatus including the system itself, its component assemblies and subassemblies, and various combinations thereof. The invention also involves methods, including the sequential adiabatic method of part formation progressing from starting feedstock through intermediate blank to formed part. 
     The invention is not limited to the cut-off of one blank at a time from elongated feedstock. In a cut-off station two or more blanks can be concurrently cut-off. 
     Also, the invention is not limited to the forming of one part at a time from a blank. In a forming station, a double forming die or cartridge arrangement can be employed. Two forming stations that are either successively operated relative to each other in part formation or that each receive blanks from a cut-off station can be utilized. 
     The first adiabatic station in which feedstock is cut-off into blanks can advantageously incorporate two separate, independently operating, but integrated and synchronously functioning, adiabatic cut-off devices, each one of which is provided with an independent stock feeder subassembly. Similarly, the second adiabatic station in which blanks are successively formed into parts can advantageously incorporate two separate, independently operating, but integrated and synchronously functioning, adiabatic blank forming devices, each one of which is provided with a separate blank transferer subassembly. 
     Accordingly, it is an object of the present invention to provide an automated integrated, progressively operating, synchronized, two station adiabatic forming system, one station of which cuts feedstock into blanks, the other station of which shapes blanks into formed parts. 
     Another object is to provide such an automated system which operates at high work piece throughput speeds yet which operates with precision so that the system produces consistent formed parts that are free from imperfections and defects. 
     Another object is to provide such an automated system wherein each of the two stations operates mechanically and independently at high speed and progresses through multiple operating steps in a cyclical manner yet wherein both stations operate in a coordinated and synchronized manner. 
     Another object is to provide improved tooling adapted for use in a system for accomplishing adiabatic stock cut-off and adiabatic blank forming. 
     Another object is to provide an automatic system for blank cut-off and part forming which utilizes a starting feedstock having any shape or configuration including feedstock that is solid or tubular in cross-section. 
     Another object is to provide an improved stock feeder subassembly for an adiabatic processing device, such as a stock cut-off device. 
     Another object is to provide, in a stock feeder subassembly of the type indicated, the capability of carrying out step-wise successive cycles involving the advancing of an elongated feedstock into an adiabatic cut-off apparatus, the positioning and clamping of the feedstock during feedstock cut-off and blank formation, the separating of a cut-off blank from the cut-off apparatus, and, especially, the loading of the separated blank into a blank transferer subassembly, the feedstock advancing and the blank separating and loading being carried out successively in coordination with operations of an associated adiabatic cut-off device. 
     Another object is to provide an improved blank transferer subassembly that is adapted for moving a work piece from one adiabatic tooling device to another, such as from a stock cut-off device to a work piece shaping device. 
     Another object is to provide, in a blank transferer subassembly of the type indicated, the function of carrying out successive cycles involving picking up a work piece at one location at one adiabatic tooling device, transporting the work piece, and discharging the work piece at a second location at a second adiabatic tooling device, the picking up and the discharging being accomplished while maintaining the work piece in a predetermined spatial orientation. 
     Another object is to provide automation means for an adiabatic forming system that is adapted for high part throughput operating rates, that accomplishes part formation from feedstock proceeding through blank formation to formed product part, and that incorporates two successive adiabatic processing stations that each has multiple operating steps. 
     Another object is to provide, in an automation means of the type indicated, the capacity to regulate and control sequential and synchronized functioning of a series of associated peripheral assemblies that are associated with the adiabatic stations, the peripheral stations including a stock feeder means, a blank removal means, a blank transferer means, and a formed part ejection means. 
    
    
     Other objects, aims, features, purposes, advantages, and the like will become apparent to those skilled in the art from the present specification taken with the accompanying drawings and the appended claims. 
     BRIEF DESCRIPTION OF THE DRAWINGS 
     In the drawings: 
     FIG. 1A is a flow diagram illustrating a preferred process operating step sequence for forming a part from a feedstock employing the two-station adiabatic part forming system of the invention; 
     FIG. 1B is a flow diagram illustrating a preferred machine operating step sequence for executing the process step sequence of FIG. 1B; 
     FIG. 2A is a perspective environmental view of one embodiment of the inventive two-station adiabatic forming system; 
     FIG. 2B is a side elevational view of the opposite side of the adiabatic cut-off assembly from that partially shown in FIG. 2A with the hood in a fully open position; 
     FIG. 2C is a side elevational detailed view of the adiabatic forming apparatus shown in FIG. 2A; 
     FIG. 3 is a diagrammatic view in side elevation of the adiabatic cut-off assembly in a side orientation similar to that of FIG. 2B, this view showing the coacting combination of the adiabatic impact press assembly and the stock feeder assembly in functional association with the inter-station blank transferer assembly, the cut-off assembly and the transferer assembly being in the operative configuration that occurs when the forward end of a feedstock is in position to be cut-off adiabatically in the impact press assembly and thereby create a blank; 
     FIG. 4 is an enlarged, fragmentary, longitudinal, vertical sectional, detail view taken through and along the axial feedstock pathway region in the adiabatic impact press assembly, the adiabatic impact press assembly being in the operative configuration shown in FIG. 3 where the stationary and the movable die blocks of the adiabatic impact press assembly are aligned; 
     FIG. 5 is a view similar to FIG. 4, but showing the adiabatic impact press assembly at the moment after adiabatic cut-off of a blank occurs with the stationary and movable die blocks being disaligned; 
     FIG. 6 is a view similar to FIG. 5, but showing the adiabatic impact press assembly at the moment after blank separation when the stationary and movable die blocks are realigned and in the axial configuration shown in FIG. 4; 
     FIG. 7 is a view similar to FIG. 3, but illustrating the adiabatic cut-off assembly in the operative configuration where the adiabatic impact press assembly is in the configuration shown in FIG.  6  and where the static gripper of the stock feeder assembly still clamps the feedstock; 
     FIG. 8 is a view similar to FIG. 3, but illustrating the stock feeder assembly after the static gripper has released the feedstock and the second movable gripper clamps the feedstock; 
     FIG. 9 is a view similar to FIG. 3, but illustrating the stock feeder assembly after the second movable gripper has advanced the feedstock so that the feedstock&#39;s forward end is beyond the feedstock cutting plane in the impact press assembly and the cut-off blank that was produced as illustrated in FIG. 5 has been transferred into the blank-transfer capsule of the inter-station blank transferer apparatus; 
     FIG. 10 is a view similar to FIG. 3, but illustrating the stock feeder assembly after the second movable gripper has retracted the feedstock and positioned the feedstock&#39;s forward end before or at the blank cut-off position in the adiabatic impact press assembly; 
     FIG. 11 is a view similar to FIG. 3, but illustrating the stock feeder assembly after the second movable gripper has released the feedstock, and the first movable gripper has clamped and is ready to advance the feedstock to the preset feedstock cutting position shown in FIG. 3, whereby a new blank cut-off cycle of operation can begin; 
     FIGS. 12A,  12 B and  12 C each illustrate a different progressive operational stage in the operating cycle of the stock feeder assembly when this assembly is operated with two movable grippers and no fixed gripper; 
     FIG. 13 is a fragmentary perspective view of the upper portion of the stock feeder assembly showing the first and the second movable grippers; 
     FIG. 14 is a fragmentary side elevational view of the second movable gripper, some parts being broken away and some parts being shown in section; 
     FIG. 15 is a fragmentary longitudinal vertical sectional view through the second movable gripper, some parts being broken away and some parts being shown in section; 
     FIG. 16 is a fragmentary transverse vertical elevational view taken approximately along the line XVI—XVI of FIG. 15 showing the jaws of the second movable gripper; 
     FIG. 17 is a side elevational view of the cut-off assembly including the adiabatic impact press assembly and stock feeder assembly in a common housing and interconnected together by their common drive mechanism, the common housing top cover being in its fully open position and the two side covers being removed; 
     FIG. 18 is a side elevational view of the opposite side of the combined impact press assembly and stock feeder assembly (relative to FIG.  17 ), the common housing top cover being in its fully open position and two side covers being removed; 
     FIG. 19 is a horizontal sectional view through the common drive mechanism of the adiabatic cut-off assembly taken approximately along the line XIX—XIX of FIG. 17; 
     FIG. 20 is a fragmentary horizontal sectional view through the trigger assembly taken approximately along the line XX—XX of FIG. 17; 
     FIG. 21 is a fragmentary horizontal sectional view through the feed arm assembly taken approximately along the line XXI—XXI of FIG. 17; 
     FIG. 22 is a partially diagrammatic end elevational view of the inter-station blank transferer assembly in combination with the adiabatic cut-off assembly and the adiabatic forming assembly, the system being that shown in FIG. 2A with some parts being shown in section and some parts being broken away, the transfer arm and the blank transfer capsule of the transferer assembly being in functional association with the adiabatic cut-off assembly, this view showing the blank transferer assembly at the moment after a blank that has been produced in the adiabatic cut-off assembly has been transferred into the blank transfer capsule as shown in FIG. 9; 
     FIG. 23 is a view similar to FIG. 22, but illustrating the blank transferer assembly after its transfer arm has moved the associated blank transfer capsule from the adiabatic cut-off assembly to the adiabatic blank forming assembly; 
     FIG. 24 is a fragmentary, longitudinal, vertical sectional view taken through and along the axial region of the adiabatic blank forming assembly showing the blank forming assembly in association with the blank transferer assembly, the combination being shown in the operative configuration where the transfer capsule of the blank transferer assembly is about to transfer a blank held by the transfer capsule into the blank forming assembly; 
     FIG. 25 is an enlarged, fragmentary detail view of the region in the blank forming assembly where the transfer capsule and the first and the second forming capsules of the blank forming assembly associate as shown in FIG. 24; 
     FIG. 26 is a view similar to FIG. 24, but showing the adiabatic blank forming assembly at the moment after the piston of the blank transfer capsule has advanced and moved the blank from the blank transfer capsule into the first forming cartridge of the blank forming assembly; 
     FIG. 27 is an enlarged view similar to FIG. 25, but showing details of the FIG. 26 configuration in the region of the forming cartridges and the associated blank transfer capsule; 
     FIG. 28 is a view similar to FIG. 24, but showing the piston of the blank transfer capsule fully retracted back to its starting position after discharge of the blank from the capsule; 
     FIG. 29 is an enlarged view similar to FIG. 25, but showing details of the FIG. 28 configuration in the region of the forming cartridges and the associated blank receiving capsule; 
     FIG. 30 is a view similar to FIG. 24, but showing the adiabatic blank forming assembly after the blank transferer assembly has been withdrawn therefrom and the second forming cartridge is advancing axially into abutting and mating engagement with the first forming cartridge; 
     FIG. 31 is an enlarged view similar to FIG. 25, but showing the FIG. 30 configuration in the region of the first and second forming cartridges; 
     FIG. 32 is an enlarged view similar to FIG. 31, but showing the adiabatic forming assembly just after the second forming cartridge has come into full abutting and mating engagement with the first forming cartridge, and the first and second cartridges are effectively locked together, thereby defining, together with adjacent portions of the blank and adjacent portions of the ejector pin, an enclosed blank forming cavity whose configuration corresponds to the form of a part being formed from the blank; 
     FIG. 33 is an enlarged view similar to FIG. 32, but showing the ejector pin just after it has been axially advanced and abuttingly engaged with adjacent side portions of the blank whereby, in turn, the blank is axially moved to an extent such that opposed side portions of the blank are abuttingly engaged with head end portions of the forming hammer of the adiabatic forming tool assembly; 
     FIG. 34 is an enlarged view similar to FIG. 33, but showing the positions of the ejector pin, the hammer, and the blank just after the hammer has been axially advanced against the opposed resistive pressure being applied by the ejector pin against the blank to an extent sufficient to move the ejector pin back to its starting or stop position with the blank being advanced into the forming cavity; 
     FIG. 35 is a view similar to FIG. 24, but with the adiabatic impact press of the blank forming assembly advanced axially to a position where the forward end of the ram thereof is advanced to a desired spacing distance from the rearwardly projecting striking end of the hammer, this view showing the configuration just before release (or firing) of the ram by the impact press assembly; 
     FIG. 36 is a view similar to FIG. 24, but showing the ram flying out at high speed to strike the hammer and impact against the blank; 
     FIG. 37 is a view similar to FIG. 24, but showing the forming hammer after the ram has impacted thereagainst and the blank has been partially formed into a part in the forming cavity, this view showing the configuration just as the power stroke is starting to be applied against the ram; 
     FIG. 38 is a view similar to FIG. 37, but showing the configuration just after the power stroke has been fully applied to the ram so that the ram has advanced and the blank is resultingly formed and filling the forming cavity, thereby achieving a completely formed part; 
     FIG. 39 is an enlarged, fragmentary, detail view similar to FIG. 34, but showing the formed part and contiguous components of the forming assembly as viewed in FIG. 38; 
     FIG. 40 is a view similar to FIG. 38, but showing the components after their ejection immediately following part formation with the second forming cartridge retracted and separated from the first forming cartridge, the ejection pin fully advanced relative to the second forming cartridge, and the ram fully advanced relative to the first forming cartridge, so that the formed part resulting from the blank is ejected from the first and the second forming cartridges and ejected from the adiabatic forming assembly; 
     FIGS. 41A through 41E shows in vertical section five progressive and successive illustrative stages of material flow in the forming cavity proceeding from the blank to the finished formed part as such stages occur during a blank forming operation carried out in the adiabatic blank forming assembly with FIG.  41 B through FIG. 41D showing the part being formed from ram impact and with FIG. 41E showing the final part forming achieved through application of the power stroke; 
     FIGS. 42A through 42E correspond to the respective stages of FIGS. 41A through 41E and show illustratively the progressive blank forming stages apart from the forming cavity defined by the forming cartridges; 
     FIG. 43 is a diagrammatic side elevational view of the adiabatic blank forming assembly including the movable second forming cartridge, the stationary first forming cartridge, the movable impact press assembly, the drive mechanism, and the supporting frame and housing structure, the movable second forming cartridge and the movable impact press assembly being in their respective maximum open or axially spaced positions relative to the first forming cartridge, the drive mechanism including a gear train and toggle links for achieving sequencing and synchronization of adiabatic forming assembly components and operation; 
     FIG. 44 is an enlarged view showing details of the toggle link arrangement employed for reciprocating the movable second forming cartridge; 
     FIG. 45 is a view similar to FIG. 43 but showing the movable second forming cartridge and the movable impact press assembly after their respective toggle links have been advanced to a straightened configuration, thereby to place such cartridge and such impact press assembly in their respective positions of closest approach to one another and of contacting relationship with portions of the first forming cartridge; 
     FIG. 46 is a horizontal sectional view through the common drive mechanism of the adiabatic blank forming assembly taken approximately along the line XXXXVI—XXXXVI of FIG. 43; 
     FIG. 47 is a simplified diagrammatic view of a control mechanism for actuating and deactuating electromagnetically controlled pneumatic or hydraulic valves employed for operating double acting air or hydraulic cylinders utilized in apparatus of the invention; 
     FIG. 48 is a longitudinal sectional view axially taken through the pneumatic air cylinder used to translate the ejector/anvil in the forming assembly; 
     FIG. 49 is view similar to FIG. 43, but showing an alternative embodiment of a drive mechanism for the forming assembly, this alternative mechanism utilizing two cooperating servo motors; 
     FIG. 50 is a view similar to FIG. 45, but showing the drive mechanism of FIG. 49 with the toggle links moved to their straightened configuration; 
     FIG. 51 is a view similar to FIG. 43, but showing another alternative embodiment of a drive mechanism for the forming assembly, this alternative mechanism utilizing two pneumatic air or hydraulic cylinders; 
     FIG. 52 is a is a view similar to FIG. 45, but showing the drive mechanism of FIG. 51 with the toggle links moved to their straightened configuration; 
     FIG. 53 is an elevational view similar to FIG. 22, but illustrating an embodiment of the inventive apparatus where one cut-off assembly is utilized in progressive and successive combination with two forming assemblies and with two transferor assemblies, one transferor assembly being used to transfer blanks from the cut-off assembly to a first forming machine, and the second transferor assembly being used to transfer partially formed blanks from the first forming machine to a second forming machine; and 
     FIG. 54 is an elevational view similar to FIG. 22, but illustrating an embodiment of the inventive apparatus where one cut-off assembly is utilized in combination with two forming assemblies and with two transferor assemblies, the transferor assemblies here being used to transfer at least one blank from the cut-off assembly to each of the two forming assemblies in an alternative manner. 
    
    
     DETAILED DESCRIPTION 
     Referring to FIG. 1A, a flow diagram illustrating the sequence for automatic part formation from feedstock is seen that illustrates one preferred sequence of process operating steps for practicing the present invention. In a first step, an elongated feedstock is fed incrementally to, and positioned in, an adiabatic cut-off zone. In a second step, in the adiabatic cut-off zone, a prechosen increment of the feedstock at the feedstock forward end is adiabatically cut-off by an impact applied along a transverse shear plane relative to the elongated feedstock, thereby to produce a blank in less than about one millisecond. In a third step, the blank is advanced into a transfer capsule. In a fourth step the capsule holding the blank is transferred from the adiabatic cut-off zone to an adiabatic forming zone. In a fifth step, the blank is located at a forming cavity in the adiabatic forming zone. In a sixth step, forming cartridges are closed in the adiabatic forming zone. In a seventh step, the blank is adiabatically formed to conform to the cavity by a sequentially applied combination of impact immediately followed by an application of a power stroke, thereby to produce a completely formed part in milliseconds. In an eighth step, the formed part is ejected. 
     Referring to FIG. 1B, a flow diagram is shown illustrating a preferred sequence of mechanized operations that are employed in accordance with the invention to carry out the process step sequence of FIG.  1 A. First, feedstock is fed, positioned, and held in the adiabatic cut-off zone. Second, in that zone, a ram is fired, energy is applied, and a pair of initially aligned cut-off dies is disaligned, thereby to sever adiabatically a blank from the feedstock forward end. Third, the dies are realigned. Fourth, the feedstock is overadvanced, thereby to move the cut-off blank into a transfer capsule. Fifth, the capsule is transferred to an adiabatic forming zone. Sixth, in the forming zone, the blank is moved from the transfer capsule and transferred into a forming position, and the capsule is separated. Seventh, forming cartridges are engaged to define generally a forming adjacent portions of the blank. Eighth, an energy-transfer hammer is advanced and abutted against the blank adjacent the forming cavity. Ninth, a ram is fired against the hammer, the hammer is suddenly pushed against the blank, and the blank is partially formed. Tenth, power is applied against the ram, and, resultingly, the blank is formed into conforming relationship with the forming cavity, thereby producing a formed part. Eleventh, the forming cartridges are separated. Twelfth, the formed part is ejected from the forming zone. 
     The operations of FIG.  1 A and FIG. 1B are practiced in the present invention. An embodiment  99  of the inventive two station adiabatic forming system, which utilizes and performs such operations, and which includes the incorporated subassemblies, is illustrated in FIGS. 3-48. 
     (a) System  99  Operation and Subassembly Cycles of Operation 
     The present section of the specification describes system  99  operation. 
     Structural details are described in subsequent sections. 
     Referring to FIGS. 2A,  2 B and  2 C, there is seen the system  99  embodiment which comprises adiabatic cut-off assembly  100 / 101 , forming assembly  150 , transferor assembly  148 , and control station  130 . 
     Referring to FIG. 3, there is seen an illustrative diagrammatic representation in side elevation of an adiabatic cut-off assembly  100 / 101  which comprises an impact press assembly  100  in functional combination with a stock feeder assembly  101 , the combination  100 / 101  being part of a system  99 . As shown in FIG. 3, the cut-off assembly combination  100 / 101  is at one operating position or configuration that occurs in a complete cycle of automatic operation of system  99 . 
     In FIG. 3, an elongated feedstock  103 , such as a metal bar or the like, is being held by the stock feeder assembly  101  in position for a predetermined feedstock  103  forward end portion to be cut-off by the impact press assembly  100 . The impact press assembly  100 , the stock feeder assembly  101 , and the feedstock  103 , when present, are supported by a frame  104 . 
     The stock feeder assembly  101  incorporates three grippers, identified as stationary gripper  106 , first movable gripper  107 , and second movable gripper  108 . Each of the grippers  106 ,  107  and  108  is adapted to clamp and hold an adjacent portion of the elongated feedstock  103 . In the combination  100 / 101  assembly operating position shown in FIG. 3, the first movable gripper  107  clamps the feedstock  103 . The first movable gripper  107  has been advanced to a full forward position, and, when in this position, the gripper  107  has advanced the feedstock  103  to a predetermined position for cut-off by apparatus  100 . 
     FIG. 4 shows mainly details of the adiabatic impact press assembly  100 , the assembly  100  being in the operative configuration shown in FIG. 3. A further description of the assembly  100  is provided in the following section. The feedstock  103  forward end portion extends into or through the bores  112  and  113  of the die blocks  109  and  111  to the desired predetermined extent needed to place the plane of cutting desired for feedstock  103  into aligned relationship with the plane  115  defined between the die blocks  109  and  111 . In the assembly  100 , just before ram  116  impact on energy-transferring hammer  114  occurs, a cycle of operation of apparatus  100  can be considered to commence. 
     In the stock feeder assembly  101 , a change in feedstock gripping occurs just before ram  116  impact on hammer  114  occurs. The movable gripper  107  of the feeder assembly  101  releases the feedstock  103 , and the feedstock  103  is gripped by the stationary gripper  106 , there being a short dwell time interval during which the feedstock  103  is held by both such grippers  106  and  107  to avoid any shift in the position of feedstock  103 . All clamping and releasing is performed during the dwell times of the movable grippers  107  and  108 . After this change in feedstock  103  gripping has occurred, the grippers  106 ,  107 , and  108  appear as shown in FIG. 7, and this configuration is maintained during blank  119  cut-off. The operating configuration shown in FIG. 7 corresponds to the configuration shown in FIG.  6 . After blank  119  cut off, the stationary die block  109  and the movable die block  111  have their bores  112  and  113  realigned. In FIG. 7, the second movable gripper  108  has been moved and is located substantially at its rearward-most location along the path of feedstock  103  travel. 
     Immediately after the stationary gripper  106  clamps the feedstock  103 , the ram  116  is fired (released). After the ram  116  impacts against the hammer  114 , the impact is transferred to the movable die block  111 . The result is that the movable die block  111  is translated and the feedstock  103  is severed along the parting plane  115  defined by the adjacent faces of the die blocks  109  and  111 . The resulting cut-off forward end portion of the feedstock is a blank  119 . During the severing, the feedstock  103  has room to move transversely in the channels of the spacer block  117  and the guide bushing  118 . 
     In the impact press assembly  100 , before the severing, the positive die return subassembly  121  is retracted by springs, as below described. The total time period transpiring between impact and blank  119  severing is less than about one millisecond. After the blank  119  severing from the feedstock  103 , the positive die return subassembly  121  pushes the movable die block  111  back into bore alignment with the stationary die block  109 , as illustrated in FIGS. 6 and 7. The ram  116  of the adiabatic cut-off assembly  100  is retracted by the ram operating mechanism  120 , thereby effectively completing one full cycle of operation of the assembly  100 . 
     In stock feeder assembly  101 , after blank  119  cut-off, the stationary gripper  106  releases the feedstock  103 , and the second movable gripper  108  clamps the feedstock  103 , as shown in FIG.  8 . The first movable gripper  107  translates backwards to its predetermined rearward-most position. 
     The second movable gripper  108 , while clamping the feedstock  103 , now advances the feedstock  103  forwards along the feedstock pathway to a predetermined extent that is sufficient to cause the forward end of the feedstock to push the blank  119  completely out of the stationary die block  109  and also completely into a predetermined transfer position that is located in a transfer capsule  146 , as shown in the assembly  100 / 101  configuration illustratively shown in FIG.  9 . 
     Thereafter, the second movable gripper  108  retracts the so-clamped feedstock  103  backwards along the feedstock pathway to a predetermined extent that is sufficient to place the forward end of the feedstock at the parting plane  155 , as shown in FIG.  10 . In this apparatus configuration, the second movable gripper  108  is either at or near its point of rearward-most travel, depending upon apparatus adjustments. 
     Next, the first movable gripper  107  clamps the feedstock  103  and the second movable gripper  108  releases the feedstock  103 , as illustrated in FIG.  11 . The first movable gripper  107  now advances the feedstock  103  to the extent necessary to place the feedstock  103 , and the assembly  100  and assembly  101 , in the respective operating positions shown in FIG. 3, thereby completing one cycle of operation by the stock feeder assembly  101 . 
     Although in each of FIGS. 1 through 11, the components of the transferer assembly  148  identified as the transfer arm  147  and its associated transfer capsule  146  are shown in the same relative position adjacent the discharge end of apparatus  100 , those skilled in the art will appreciate that the transfer arm  147  and transfer capsule  146  need only to be in this position at some time just before a blank  119  is translated out of the apparatus  100  and into the transfer capsule  116 . 
     The die blocks  109  and  111 , and the transfer capsule  146 , are sized for use with a particular selected feedstock, as those skilled in the art will appreciate, so need to be changed when the diameter or cross sectional configuration of feedstock  103  is changed. Sometimes large size or configuration changes from one feedstock to another require a change in the jaws of the grippers  106 ,  107  and  108 . 
     In FIG. 22, the general configuration of the transferer assembly  148  is illustrated when the transfer arm  147  is located at a prechosen position  145  at the adiabatic cut-off apparatus  100  where and when the transfer capsule  146  is receiving a blank  119 , as illustrated, for example, in FIGS. 9 and 10. The transferer assembly  148  is located between the adiabatic cut-off apparatus  100 / 101  and the adiabatic forming apparatus  150 . The structure of the transferer assembly  148  is further described below. 
     When the transfer of a blank  119  into the transfer capsule  146  is completed, and the overadvanced feedstock  103  in the adiabatic cut-off apparatus  100 / 101  is being, or has been, separated from the transfer capsule  146  and relocated into a position, such as shown in FIG. 10, the transfer arm  147  pivots about the axis of shaft  151  of the transferer assembly  148  and moves the transfer capsule  146  from the position  145  to a prechosen position  155  at the adiabatic forming apparatus  150 , as illustrated in FIG.  23 . 
     When the transfer arm  147  is in the position  155 , the transfer capsule  146  is located at the adiabatic forming apparatus  150  so that the blank  119  in the transfer capsule  146  is transferable from the transfer capsule  146  into the adiabatic forming apparatus  150 . After the transfer arm  147  has moved to position  155 , the configurational interrelationship between the transferer assembly  148 , including the transfer arm  147  and the transfer capsule  146  with the blank  119 , and the adiabatic forming apparatus  150 , is as illustrated in FIG.  24 . 
     The configuration of the adiabatic forming apparatus  150 , at this point in its cycle of operation, is illustrated also in FIG.  24 . The structure of the adiabatic forming apparatus  150  is further described below. 
     When the transfer arm  147  is in the position  155 , the capsule  146  is in its desired position at the adiabatic forming apparatus  150 , as shown, for example, in FIGS. 24 and 25. The transfer capsule  146  incorporates a pneumatic or hydraulic cylinder arrangement that includes a piston  168  which is reciprocatably movable in a cylinder chamber  169   a  and  b  that is a diametrically enlarged rear region defined in a longitudinally extending cavity  166  that extends axially through the transfer capsule  146 . The piston  168  is axially connected to a shaft  167 . Responsive to fluidic (preferably pneumatic, more preferably compressed air) input through channel  171  into chamber  169   b  and applied against the rearward face of the piston  168 . As a consequence, the piston  168  and the shaft  167  are advanced in chamber  166  of capsule  146 . The forward end of the shaft  167 , which abuts against the blank  119 , pushes against and causes the blank  119  to be moved forwardly and slidably completely out of the transfer capsule  146  and into the forward end portion of the adjacent axial channel  173  of a the stationary forming cartridge  154  of the forming assembly  150 , as illustrated, for example, in FIGS. 26 and 27. 
     Preferably an end portion of the blank  119  protrudes from the channel  173 , as shown, for example, in FIGS. 26 and 27. After advancing the blank  119  into the channel  173  of the cartridge  173 , the piston  167  and the shaft  167  are fully retracted in the transfer capsule  146 , as illustrated, for example, in FIGS. 28 and 29, responsive to fluidic pressure input through channel  172  into chamber  169   a  and applied against the exposed forward face of the piston  168 . Thereafter, the transfer arm  147  pivots at shaft  151  and returns with the now empty transfer capsule  146  from the position  155  back to the position  145  at the adiabatic cut-off apparatus  100 / 101 , as shown, for example, in FIG. 22, thereby completing a cycle of operation of the transferer assembly  148 . 
     After the transfer capsule  146  has left position  155  in the adiabatic forming apparatus  150 , the movable second forming cartridge  156  of the forming assembly  150  is advanced axially towards the stationary first cartridge  154 . The forming cartridge  156  is set axially into the head of an extensible and retractable piston  157 . To achieve this advance of cartridge  156 , the piston  157  is slidably translated forwardly, as illustrated in FIGS. 30 and 31, an arrow in FIG. 31 indicating the direction of movement of piston  157 , until the forward end of the cartridge  156  is abuttingly engaged with the forward end of the cartridge  154 , as illustrated in FIG.  32 . After the cartridges  154  and  156  become engaged, they are effectively locked together. The moving mechanism employed is below described. 
     When the cartridges  154  and  156  are engaged, the walls of a forming cavity  160  are generally defined by the cartridges  154  and  156  except for the wall areas defined by the adjacent forward end portions of an ejection pin  177 , and also by the adjacent portions of the blank  119 , the latter being in opposed relationship to the former. The arrangement is such that initially a gap  178 , preferably small, exists between the ejection pin  177  and the blank  119  in the cavity  160  after the cartridges  154  and  156  are engaged and locked. 
     After the cartridges  154  and  156  are brought into engagement and locked together, the ejection pin  177  is axially advanced into contacting engagement with the adjacent portions of the blank  119 , and the blank  119  is thereby moved into contacting engagement with the adjacent forward end portions of an energy transferring hammer  174 . 
     The forming tool hammer  174  is now advanced by applying differential fluidic (preferably pneumatic) pressure into the rearward portion  173 B of the enlarged channel  173 A/ 173 B. Since the forward end of the hammer  174  has been placed in abutting engagement against the blank  119 , and since the pressure exerted by the hammer  174  against the blank  119  is chosen to be greater than the pressure exerted by the ejector pin  177  against the opposite side of the blank  119 , the blank  119  and the ejector pin  177  are both moved by the hammer  174  advance. The advance continues until the ejector pin  177  again reaches its initial abutting or seated engagement with the compartmental back wall portion provided in a rearward portion of the second cartridge  156 , as illustrated, for example, in FIGS. 35 and 36. At this point in operation, the blank  119  is preferably tight against the first cartridge  154 , the forward end of the hammer  174 , and the forward end of the ejector pin  177 . The ejector pin  177  during this phase of assembly  150  operation acts as an anvil. 
     With the adiabatic forming apparatus  150  in the configuration illustrated, for example, in FIGS. 35 and 36, the ram  178  is fired (released) by the ram operating mechanism  180 , as illustrated in FIG.  36 . The ram  178  impacts against the hammer  174 , as illustrated, for example, in FIG.  37 . At this point in operation, the blank  119  is partially formed in the cavity  160  into a part  182 , the partially formed body being designated  119 / 182  in FIG. 37 in less than about one millisecond. 
     After ram  178  impact, force is applied through and by the ram  178  against the hammer  174  by a mechanism as below described. Within milliseconds after ram  178  impact, and force application, the blank  119  fully is reshaped into conformity with the shaping cavity  160  and thereby is formed into a part  182  that fills the shaping cavity  160  as illustrated in FIGS. 38 and 39. Brief as the forming time is, the blank  119  shaping is progressive into the formed part  182  and can be considered to occur in phases after ram  178  impact. These progressive adiabatic shaping phases are illustrated successively in the sectional views FIGS. 41A through  41 E, and in FIGS. 42A through 42E. FIGS. 42A through 42E correspond to the respective FIGS. 41A through 41E. 
     It should be understood that the process of FIGS. 41B-41D takes less than about one millisecond and creates an instant heat build-up in the blank. On the other hand, the process of FIG. 41E takes a number of milliseconds depending on the RPM of the machine. The force application or power stroke forming to finalize the forming process is done when the metal is already warm or hot and is done very gently. 
     Immediately after the part  182  is thus formed, the cartridges  154  and  156  are unlocked and the second cartridge  156  is separated (retracted) from the first cartridge  154  by retracting the piston  157 , as illustrated in FIG.  40 . As the cartridges  154  and  156  separate, the ram  178  remains applied to the hammer  174 , thereby permitting the hammer  174  to act as an ejector for separating the part  182  from the cartridge  154 . Also, concurrently, as the cartridges  154  and  156  separate, the ejection pin  177  is advanced in the cartridge  156  so that the head of the ejector pin  177  is applied against the formed part  182 . Thereby, the ejector pin  177  acts as an ejector to separate the formed part  182  from the second cartridge  156 . The part  182  is thus separated from the cartridges  154  and  156  and falls into a waiting collection bin (not detailed), or the like, as desired, thereby completing a complete cycle of operation of the adiabatic forming apparatus  150 . 
     (b) Subassembly Structures 
     (1) The Stock Feeder Assembly  101   
     While various means can be utilized to operated grippers in a stock feeder assembly, the grippers  106 ,  107 , and  108  have jaws which are pneumatically operated responsive to electrical control signals. A similar jaw structure is preferably employed for each gripper. 
     The grippers  107  and  108  are slidably mounted for horizontal movements along and over respective longitudinally adjacent portions of a pair of lengthwise extending (relative to assembly  101 ), spaced, parallel rails  259  and  260  (see FIG. 13 or FIG. 14) that are associated with the top deck  222 . 
     The structure of the gripper  108  is illustrative and is seen in FIGS. 14 and 15. Gripper  108  incorporates a frame structure  380  which includes a base plate  381 , a side and end wall combination  382 , and a cap plate  383  that is equipped with a handle  384  for convenience in removal and reassembly when access to the interior of the side and end wall combination  382  is desired. The components of the frame structure are affixed together with machine screws (not shown) or the like. 
     Three pairs of aligned channels are defined in each of the opposed end walls of wall combination  382 . Through an outside pair of channels, rail  259  slidably extends and rail  260  extends through the opposite outside pair of channels so that the gripper is slidably mounted on the rails  259  and  260 . Through the medial pair of aligned channels is extended a feedstock  103 . 
     The gripper  108  utilizes a pair of jaws comprising an upper stationary jaw  386  and a lower movable jaw  387  that is vertically reciprocatable within the frame structure  380 . During the jaw  387  movements, edge wall portions thereof are guided by adjacent portions of the wall combination  382 . The upper jaw  386  is supported in, nestably received in, and held by, the frame structure  380 . The lower face of upper jaw  386  and the upper face of the lower jaw  387  are each generally flattened and normally these faces are in opposed, spaced, parallel relationship relative to each other. However, a matching groove  386 A and  387 A is defined in each of the upper and lower faces, respectively, and the grooves  386 A and  387 A are adapted to accommodate side surface portions of feedstock  103  when the feedstock  103  is extended therethrough. A plurality of coiled springs  388  extend generally vertically between the jaws  386  and  387  in opposed facial pockets (not shown). The springs  388  bias the lower and upper faces of the jaws  386  and  387  into a normally spaced relationship and the springs  388  aid in maintaining a uniform spacing between these upper and lower faces. When the jaws  386 ,  387  are in an open configuration, such as shown in FIG. 16, the jaws  386  and  387  are slidably movable relative to the feedstock  103 , or vice versa. When the jaws  386 ,  387  are placed in a closed configuration, achieved by upward movement of the lower jaw  387 , the feedstock is grasped or clamped between the jaws  386 ,  387 . 
     To achieve controllable movement of the lower jaw  387 , the central region of the lower face of the lower jaw  387  is associated with the upwardly projecting, outer end portion of a shaft  389 . The lower end portion of the shaft  389  is associated with a piston  391 . The piston  391  is reciprocatorily generally vertically movable (as shown in FIG. 15) in the longitudinally shallow chamber  392 A/ 392 B of a cylinder  393 . The upper end of the cylinder  393  is provided by a top plate  395  having a central aperture  396  through which the shaft  389  slidably extends. The lower end and side walls of the cylinder  393  are provided by a mug-like structure  394 . Sealing means, such as an o-ring  397  extending circumferentially around a groove in the piston  391 , and an o-ring  400  extending circumferentially around a groove in the aperture  396 , is provided. Access to the lower chamber portion  392 A is provided by channel  398  and access to the upper chamber portion  392 B is provided by a channel  399 . When chamber  392 A is pressurized with a compressed fluid, such as air or the like, the piston  391  and shaft  389  are elevated, raising the lower jaw  387  and achieving closure of the jaws  386 ,  387 . When chamber  392 B is similarly pressurized, the piston  391  and shaft  387  are lowered, lowering the lower jaw  387  and achieving opening of the jaws  386 ,  387 . 
     As discussed below in reference to the control system and FIG. 47, the combination of cylinder  393 , piston  391  shaft  389  and channels  398  and  399  can be regarded as a pneumatic cylinder  307 . Similarly, each of grippers  106  and  107  can be regarded as incorporating pneumatic cylinders  301  and  302 . 
     To limit movement of the gripper  108  along the rails  259  and  260 , stop blocks  361  and  362  are provided, each one being slidably movable on the rails  259  and  260 , and each one being on a different side of the gripper  108 . Each block  361  and  362  is provided with an adjustable collar  363  and  364  that is threadably engaged with its associated block and that is adapted to clamp adjustably circumferentially adjacent portions of the rails  259  and  260 . 
     The movable gripper  107  is similarly provided with stop blocks. The stationary gripper  106  has a structure like that of the movable gripper  108  except that the stationary gripper  106  is mounted in an inverted orientation and is fixed to the frame  104 . 
     As shown, for example, in FIGS. 14 and 15, to automatically operate and control the reciprocal movements of the grippers  107  and  108 , and to coordinate movements associated with the actuations of the impact press apparatus  100  and the desired progressive locations of feedstock  103  as feedstock  103  is moved in a stop and go fashion by the stock feeder assembly  101  during operation of assembly  101  and apparatus  100 , various means can be employed. Here, it is presently preferred to employ a gear train  200  that is here, as shown in FIGS. 17,  18  and  19 , illustratively but preferably comprised of five peripherally and successively inter-engaged gears  201 ,  202 ,  203 ,  204 , and  205  having horizontally spaced, parallel respective axes of rotation. Each such gear is keyed to a proximal end portion of a similar shaft  206 ,  207 ,  208 ,  209 , and  210 , respectively. Each such shaft is journaled for rotational movements along and adjacent its respective opposite end portions by a pair of bearings  211 A and  211 B,  212 A and  121 B,  213 A and  213 B,  214 A and  214 B, and  215 A and  215 B, respectively. 
     The frame  104  is provided with a pair of spaced, parallel support plates  218  and  219  that upstand from a generally horizontally oriented base plate  220  and that extend lengthwise under the top deck  222  (see, for example, FIG. 3) of the frame  104 . The plates  218  and  219  are each provided with five apertures  223  that are transversely aligned with one another in paired fashion whereby each member of the bearing pairs  211 A and  211 B,  212 A and  212 B,  213 A and  213 B,  214 A and  214 B, and  215 A and  215 B is mounted in axially aligned relationship with the other. Thus, the shafts  206 ,  207 ,  208 ,  209 , and  210  extend between the plates  218  and  219  in spaced, parallel relationship to one another and each such shaft is supported by both plates  218  and  219 . The gears  201 ,  202 .  203 ,  204 , and  205  are conveniently covered by a protective housing  224  that is conventionally mounted to plate  218  by machine screws or the like, not detailed. 
     A crank shaft assembly  226  is keyed to the distal end of shaft  206 . An electric motor  227  and associated transmission  228  (conventional assembly) is supported through the plates  218  and  219  in spaced adjacent parallel relationship to shaft  206 , and a drive crank shaft  225  on the power output shaft of the transmission  228  is connected by a drive belt  229  to the crank shaft  226  whereby the motor  227  when operating can rotatably drive the shaft  206  and thereby revolve each of the gears  201  through  205  and their associated shafts  206  through  210 . The gear  201  is identical to the gear  203  and the gear  205 , while the gears  202  and  204  are identical to each other. The rotational speed of the individual shafts  206  through  210  is thus precisely controlled by the motor  227  and the transmission  228 . Gear  203  serves as an idler gear, gears  202  and  204  each drive a crank assembly  231  and  232 , as hereinbelow described, and gear  205  drives the impact press apparatus  100 . 
     To the distal end of each of the shafts  207  and  209  is connected an adjustable crank shaft  235  and  236 , respectively. Each crank shaft  235  and  236  is eccentrically rotatably connected to a first crank arm  237  and  238 , respectively. Each terminal end of each crank arm  237  and  238  is rotabably connected to a terminal yoke of a second crank arm  240  and  241 , respectively. The initial end of each second crank arm  240  and  241  is rotatably connected to a pivot shaft  243  and  244 , respectively, that is journaled by aligned bearing pairs (not detailed) each one mounted in a different aligned aperture one in each of the plates  218  and  219 . Hence, rotation of the crank shafts  235  and  236  is translated into an oscillatory, or pivotal movement by each of the pivot shafts  243  and  244 . Each of the pivot shafts  243  and  244  is keyed to the lower end of an oscillator arm  251  and  252 , respectively, as shown in FIG. 3, for example. The upper end of each oscillator arm  251  and  252  is provided with a shallow channel  253  and  254 , respectively, that extends inwards and lengthwise into the associated oscillator arm  251  and  251 . A stub shaft  256  projecting outwardly from a downturned leg  255  of gripper  108  slidably connects with the channel  254 , and a stub shaft  257 , similar to gripper  108 , of gripper  107  slidably connects with the channel  253 . 
     Hence, as the pivot shafts  243  and  244  oscillate, the oscillator arms  253  and  254  are caused to move pivotably relative to their shafts  243  and  244 , and this pivot action moves the grippers  107  and  108  back and forth along respective portions of the rails  259  and  260 . 
     Those skilled in the art will readily appreciate that different ranges of movement and position for each movable gripper  107  and  108  are achieved by adjustments and settings of, respectively, the crank assembly  231 , comprised of crank shaft  235 , crank arm  237 , crank arm  240 , pivot shaft  243  and oscillator arm  251 , and the crank assembly  232 , comprised of crank shaft  236 , crank arm  238 , crank arm  241 , pivot shaft  244 , and oscillator arm  252 . 
     The stock feeder assembly  101  can, if desired, be operated without usage of the stationary gripper  106  as when, for example, the feedstock  103  can be advanced or retracted without slippage by using only the first movable gripper  107  and the second movable gripper  108 . In such an operating mode, the stationary gripper  106  can either be left in an open and non-gripping configuration or in an inoperative configuration during apparatus  100 / 101  operation using only the movable grippers  107  and  108  for feedstock feeding. Alternatively, the stationary gripper  106  can be separated from, or absent from, the stock feeder assembly  101 , if desired. The operating sequence in assembly  101  using just the movable grippers  107  and  108  is illustrated in FIGS. 12A,  12 B, and  12 C. These FIGS. show progressive positions of the movable grippers  107  and  108  being used without a stationary gripper  106 . Their respective gripping functions corresponds to that above described when using the stationary gripper  106 . Thus, the stock feeder can be operated with either two movable grippers or one stationary gripper and two movable grippers. 
     When using two movable grippers, with the stationary gripper  106  inactivated or absent, operation of stock feeder apparatus  100  is as follows: First movable gripper  107  clamps the feedstock  103 . Gripper  107  has been advanced to a full forward position. The gripper  107  has already advanced the feedstock  103  to a predetermined position desired for cut-off by impact press apparatus  100 . 
     After the ram  116  is fired, and the blank  119  is cut off, the first movable gripper  107  releases the feedstock  103  and the second movable gripper  108  grasps the feedstock  103 , as shown in FIG.  8 . The first movable gripper  107 , after release of the feedstock  103 , translates backwards to a predetermined rearward-most location along the pathway of feedstock  103  travel. 
     The second movable gripper  108 , while clamping the feedstock  103 , advances the feedstock  103  to a predetermined extent that is sufficient to push and move the blank  119  forwardly completely out of the stationary die block  109  and into a predetermined position which, in the system  99 , is a position in the transfer capsule  146 . 
     Thereafter, the second movable gripper  108 , while still gripping the feedstock  103 , retracts the so clamped feedstock  103 , and moves it backwards along the feedstock travel pathway to an extent sufficient to place the feedstock  103  forward end about at the parting plane  155 , as shown in FIG.  10 . At this configuration, the second movable gripper  108  is either at or near its point of rearward-most travel, depending upon apparatus adjustments. 
     The first movable gripper  107  now clamps the feedstock  103  and the second movable gripper  108  releases the feedstock  103 . The first movable gripper  107  now advances the feedstock  103  to place the forward end region of the feedstock  103  in the desired position for blank  119  cut off by impact press apparatus  100 , thus completing one cycle of operation of the grippers  107  and  108  in assembly  101 . 
     As shown by the arrows indicating directions of movable gripper  107  and  108  translation in FIGS. 12A,  12 B, and  12 C, during operation of the assembly  101 , during the sequence of stock feeder assembly  101  operation, these grippers  107  and  108  exert their respective feedstock  103  gripping functions as they move reciprocatorily along the feedstock  103  travel pathway in seemingly opposite directions relative to one another. 
     (2) The Adiabatic Impact Press Assembly  100   
     The impact press apparatus  100  is comparable to the assembly shown in Lindell U.S. Pat. No. 4,470,330 and U.S. Pat. No.  4 , 245 , 493 , the teachings of which are incorporated here by reference. However, particularly because of distinctions and improvements provided in the apparatus  100 , compared to the &#39;330 patent teachings, an abbreviated description of the structure and operation of apparatus  100  is here provided. 
     Referring to FIG. 4, the apparatus  100  is seen to incorporate a pair of die blocks  109  and  111  which have adjacent flat faces that are in planar but translatable engagement each relative to the other. Each has a bore  112  and  113 , respectively, therethrough, and these bores  112  and  113  are normally in coaxial alignment. The die blocks  109 ,  111  define along and across their adjacent faces a parting plane  115 . In operation, as above indicated, the feedstock  103  is advanced through the bores  112  and  113 . Die block  109  is stationary while die block  111  is adapted for limited movement in a direction transverse to its bore  113  and to feedstock  103 . A lower side portion of the die block  111  is associated with a head end of an energy-transferring forming hammer  114 . The hammer  114  projects outwardly and downwardly from die block  111  and the outer exposed end of the hammer  114  is adapted to be impacted by a ram  116 . 
     The apparatus  100  incorporates a ram  116  and an associated ram operating mechanism  120 . The ram  116  is vertically reciprocal and is driven by mechanical means (not shown) of the ram operating mechanism  120  as described in Lindell U.S. Pat. No. 4,470,330. 
     The apparatus  100  includes an housing  122  in which the die blocks  109  and  111  are associated and which guides and limits the movements of the die block  111 . The housing  122  herein collectively refers to components which cooperate and which are held together by screws or the like, not shown. The housing  122  includes a base plate  123  that is mounted to the frame  104 . Base plate  123  conveniently is associated with a pair of clamping blocks (not shown) that hold a stationary spacer block  117  which retains and guides the die blocks  109  and  111  in housing  122 . The housing  122  also includes a lower and an upper cap block  126 ,  127 , respectively, and an internally threaded sleeve member  129 . A cylindrical, externally threaded adjustment screw  128  threadably engages the sleeve member  129 . Screw  128  is located upstream (relative to the path of travel of feedstock  103 ) of the die blocks  109  and  111  and the spacer block  117 , and screw  128  acts to hold the blocks  109 ,  111 , and  117  in association with each other. An internally threaded split ring clamp  124  is secured against the outer end of the sleeve member  129 . Tightening of screw means (not shown) relative to clamp  124  enables the exact position of screw  128  to be maintained. A guide bushing  118  is associated with the central longitudinal region of screw  128 . The bushing  118  and the spacer block  117  are each provided with an axial channel whose diameter is larger than the diameters of the bores  112  and  113 . 
     The housing  122  is associated with a positive die return subassembly  121  that includes the upper cap block  127 . A cam guide block  133  seats against layer  132  and block  133  has a downwardly facing inclined cam surface  134 . The subassembly  121  also includes the lower cap block  126  which holds a transfer block  136  that is slidably guided therein for transverse movements relative to the bores  112  and  113 . A cam  137  is slidably guided in the housing  122  over transfer block  136  for lateral movements between a first position which is adjustable, as shown in FIG. 4, and a second position as shown in FIG.  5 . The transfer block  136  is biased by a set of springs  138  which yieldingly urge the transfer block  136  against the bottom of cam  137  and hold the cam  137  against the cam surface  134 . A small space  139  is retained between the movable die block  111  and the transfer block  136 . 
     The size of this space  139  is regulated by the extent that the cam  137  is laterally retractable from its normal rest position shown in FIG. 4 to a position such as illustrated in FIG.  5 . To enable the cam  137  to be reciprocated during operation of the apparatus  100  between a first position, as shown in FIG. 4, that permits limited movement of the die block  111 , and a second fixed position shown in FIG. 5, where the space  139  is consumed, the positive die return subassembly  121  is provided. The position of the cam  137  causes die block  111  movement to terminate and any excess energy is absorbed by the housing  122  in the region of the cam surface  134 . A shaft  141  provided which is rockable relative to the housing  122 . A crank arm (not shown) is adjustably secured to the shaft  141 . An adjustable stop (not shown) limits travel of shaft  141  in a clockwise direction, thereby limiting the amount of retraction in cam  137 . 
     The reciprocably driven ram  116  also drives a transversely extending rod (not shown) in a suitably synchronized manner. The crank arm is secured to the rod and is rocked thereby. Shaft  141  is keyed to one end of a link  142  that is hinged at its opposed end to one end of a second link  143 . The opposite end of link  143  is pivotally connected to the cam  137 . This arrangement regulates the extent of the limited movement that the die block  111  can have. The rod as driven places the cam  137  is a selected or retracted first position (see FIG. 4) and creates the space  139 . When the ram  116  is then released, the die block  111  is caused to move at high velocity relative to die block  109 . The ram  116  is conveniently retracted as soon as the die block  112  has stopped its movement. The rod is then pulled positively downwardly causing the shaft  141  to rock in a counterclockwise direction. Thus, through the links  142 ,  143 , the cam  137  is moved to the right, as illustrated in FIGS. 4 and 5, causing the transfer block  136  to move against the bias of the springs  138  and thereby restore the die block  111  to its position where bore  113  is aligned with bore  112 . Normally, the ram  16  is retracted and cocked, as suggested, for example, in FIG.  3 . 
     (3) The Transferer Assembly  148   
     The shaft  151  is here driven by a servo motor  271 . The piston  168  in transfer capsule  146  is operated by using two electromagnetic pneumatic valves  327  and  328 . The control of piston  168  and of valves  327  and  328  is described below. 
     As indicated above, operation of the transferer assembly proceeds in a discontinuous or stop-and-go manner. The transfer arm  147  swings between position  145  and position  155 , and in each position the arm  147  is stationary until operations involving the transfer capsule  146  at the outer end of the arm  147  are carried out at each of the cut-off apparatus  100 / 101  and the forming apparatus  150 . 
     The transfer arm can be variously actuated. In place of the servo motor  271  (presently preferred), a cam and linkage, or a pneumatic double acting cylinder can be used, for example. 
     The drive shaft (not shown) of the servo motor  271  and the driven shaft  151  of the arm  147  are each conveniently associated with a crank shaft (not shown), and these crank shafts are in aligned relationship with one another. Conveniently, the crank shaft on the shaft  151  has a smaller diameter than the crank shaft on the servo motor  271  drive shaft. 
     (4) The Adiabatic Forming Apparatus  150   
     The adiabatic forming apparatus  150 , as shown in FIGS. 24-46, and as above indicated, incorporates two shaping cartridges, or forming tools, identified for convenience as first cartridge  154  and second cartridge  156 . The first cartridge  154  is stationary and is mounted in an upper portion of a stationary first support leg  152  that upstands from fixed association with a base platform  153  which is part of a frame  275  (not detailed). The second cartridge  156  is translatably mounted so as to be generally coaxial with the first cartridge  154 . The second cartridge  156  is fixedly mounted in the forward head of a piston  157  which is axially reciprocatable in a horizontally oriented cylinder  158  that is defined in a stationary second support leg  159 . Leg  159  is located in laterally spaced relationship to leg  152 , and leg  159  also upstands from fixed association with the base platform  153 . Thus, the forward ends  161 ,  162 , respectively, of each of the cartridges  154  and  156  are in coaxially aligned relationship. Those skilled in the art will appreciate that the first and second cartridges  154  and  156  are selected for use with a particular blank and for forming a particular part. 
     When the piston  157  is axially advanced with the second cartridge  156 , the forward ends  161 , 162  are brought into abutting and engaged relationship with one another and define therebetween in combination with adjacent portions of a blank  119  and an ejection pin  177  a forming cavity  160  (see FIG. 22) of predetermined internal configuration. Preferably, as shown illustratively in FIG. 15, each of the forward ends  161  and  162  is provided with carbide type inserts  163 ,  164 , respectively, which, when the first and second cartridges  154  and  156  are so engaged, define enclosing wall portions of the cavity  160 . 
     The second cartridge  156  has an axially extending bore  176  therethrough and also through the carbide insert  164 . The ejection pin  177  is slidably positioned in a diametrically somewhat enlarged forward region of the bore  176 . The pin  177  is normally retracted in bore  176 , and, preferably, as shown in FIG. 31, for example, the rear end of the retracted pin in bore  176  is normally seated against a shoulder  178  provided in the bore  176 , thereby to limit rearward travel of the pin  177 . Preferably, and as shown, the edge portions of the bore  176  may protrude slightly into and form a small part of the wall surface defining the cavity  160 , and the head end of the pin  177  comprises a wall portion of the cavity  160 . 
     To achieve axial reciprocal movements of the ejection pin  177  relative to the piston  157  in the cartridge  156 , the rear face of the pin  177  is threadably associated, or the like, with the forward end of an elongated rod  184 . The rearward end of the rod  184  is associated with a fluidic (preferably pneumatic, more preferably compressed air) cylinder assembly  185  whose structure may be as detailed in FIG.  48 . Thus, referring to FIG. 48, the rearward end portion of the rod  184  extends slidably through an end opening  188  into a guidance chamber  186  defined in a cylinder  187  provided at the head end of cylinder assembly  185 . The rearward end of the rod  184  is threadably associated, or the like, with the center of the forward face of a guidance piston  189  that is adapted to slidably and axially move reciprocatingly in chamber  186 . The rearward face of the guidance piston  189  is engaged axially with the forward end portion of a shaft  191  that extends through aligned apertures  198  and  199 , respectively, defined in each of the forward end plate  196  of a cylinder  193  employed the cylinder assembly  185  and also the base plate  197  of the cylinder  187 . The rear end of the shaft  191  is engaged axially with a piston  192  that is adapted to move slidably and axially move reciprocatingly in the forward chamber  193 B of the cylinder  193  of the cylinder assembly  185 . For purposes of providing a seal between adjacent components, the piston  192  is provided with a circumferentially extending seal  194 , and the aperture in the end plate  196  of the cylinder  193  is provided with a circumferentially extending seal  266 . Pressurized fluid input through channel  267  into rearward chamber  193 A of the cylinder  193  causes the piston  192  to advance together with the shaft  191 , and pressurized fluid input through channel  268  into forward chamber  193 B causes the piston  192  to retract with the shaft  191 . Since shaft  191  is connected to rod  184 , rod  184  moves with shaft  191 , and hence the ejection pin  177  is reciprocated. 
     The first cartridge  154  has an axially extending channel  173  extending therethrough. The forward end portion of the channel  173  is preferably configured to receive slidably therein the blank  119 . The channel  173  also extends through the carbide insert  164 . A mid portion and a rearward portion of the channel  173  are enlarged diametrically. An energy-transferring elongated hammer  174  extends through the channel  173 . The hammer  174  is diametrically thickened in its mid region and there provided with outside walls that are configured to slidably engage the enlarged portions of the channel  173 . The hammer  174  is also adapted to reciprocably move in channel  173  responsive to differentially applied fluidic pressure (preferably pneumatic), as those skilled in the art will appreciate. Channel  172 , at each end of its enlarged mid-region, is provided with fluid input ports (not shown but described below). Various arrangements are possible for the hammer  174  and the channel  173 . Preferably, and as shown, the rearward end of the hammer  174  protrudes out from the rear face of the cartridge  154 . 
     The adiabatic shaping apparatus  150  is provided with a ram  178  and a functionally associated ram operating mechanism  180 . The ram  178  is axially positioned relative to the hammer  174  so as to strike the adjacent end of the hammer  174  perpendicularly when the ram  178  is released (fired) by the ram operating mechanism  180 . Structural details of the ram operating mechanism  180 , which includes a ram firing mechanism, a ram force applying mechanism, and a ram retracting mechanism, are described below. 
     To operate the adiabatic shaping apparatus  150 , a gear train  280 , as shown in FIGS. 43-46, of seven peripherally inter-engaged gears  281 ,  282 ,  283 ,  284 ,  285 ,  286 , and  287  with horizontally spaced, parallel respective axes of rotation is employed. Each of the gears  282 ,  283 ,  284 ,  285 ,  286 , and  287  is identical to the others and is keyed to one end of a shaft  292 ,  293 ,  294 ,  295 ,  296 , and  297 , respectively. Gear  181  is keyed to the output shaft  291  of a transmission  289  that is energized by an associated electric motor  290 . The rotational speed of the individual shafts  292  through  297  is thus precisely controlled by the motor  290  and the transmission  228 . The motor  290  continuously operates during the operational sequence of forming apparatus  150 . 
     Gears  283 ,  284 ,  285 , and  286  are idler gears. Gear  282  and gear  287  are each eccentrically and rotatably associated with a driven end of an eccentric crank arm  299  and  300 , respectively. The opposite driving end of each crank arm  299  and  300  is rotatably connected to a connecting pin shaft  301  and  302 , respectively. Shaft  301  joins the respective proximal ends of each of a pair of toggle links  401 ,  402  with the driving end of arm  299 . Shaft  302  joins the respective proximal ends of each of a pair of toggle links  403 ,  404  with the driving end of arm  300 . The distal end of the link  401  is pivotably associated with a spatially stationary pin shaft  406 , and the distal end of the link  404  is pivotably associated with a spatially stationary shaft  407 . The pin shafts  406  and  407  are each held by the frame  275 , and these shafts are generally aligned with the working axis of the cartridges  154  and  156 , but each shaft is outwardly spaced from the adjacent cartridge. 
     The distal end of the link  402  is pivotably joined to the outer end of a secondary link  408  by a pivot pin  409 , and the inner end of the secondary link  408  is pivotably joined to the center of the outside end of the piston  157 . The secondary link  408  is employed to compensate for the maximum kink angle of links  401  and  402 , thereby to avoid interference of links with the cylinder  158 . The distal end of the link  403  is pivotably joined to the center of the outside end of the adiabatic press assembly  165 . 
     As the gears  182  and  187  rotate, the arms  299  and  300  cause each of the respective link pairs  401 ,  402  and  403 ,  404  to move from a configuration of maximum flexure or kink, relative to their respective associated shafts  406  and  407 , such as shown in FIG. 43, to a straight configuration, such as shown in FIG.  45 . When links  401 ,  402  are in their straight configuration, the cartridges  154  and  156  are engaged and effectively locked together. When the links  403  and  404  are in their straight configuration, the ram  178  is contacting the hammer  174 , and the hammer  174  has been advanced to its location of maximum forward advance; this configuration occurs after the impact of ram  178  and power stroke against the hammer  174  have taken place and a formed part is being ejected from the first cartridge  154 . When the link pairs  401 ,  402  and  403 ,  404  are in their respective positions of maximum kink, the movable second cartridge  156  is translated to its maximum axial spacing from the stationary first cartridge  154 , while the adiabatic press assembly  165  is translated to its maximum axial spacing from protruding end of the hammer  174 . However, and as those skilled in the art will readily appreciate from the present disclosure, in operation, the apparatus  150  is preferably adjusted so that the toggle links  401 ,  402  move from a maximum kink angle to a straight configuration slightly ahead of the corresponding movements of toggle links  403 ,  404  in the cycles of assembly  150  operation. 
     During the time interval that the second cartridge  156  is axially sufficiently spaced from the stationary first cartridge  154  for the spacing between the first cartridge  154  and the second cartridge  156  to be occupied by the transfer capsule  146 , the transfer arm  147  swings the transfer capsule  146  into the position shown, for example, in FIG.  24 . The blank  119  is transferred from the transfer capsule  146  into the first cartridge  154  through actuation of the piston  167  of the transfer capsule  146 , as explained. The piston  167  is then retracted, and the transfer arm  147  moves the empty transfer capsule  146  away. Then, thereafter, as the toggle link pair  401 ,  402  moves to its straight configuration as shown in FIG. 45, for example, the second cartridge  156  is advanced into engagement with the first cartridge  154 . 
     During the time interval that the adiabatic press assembly  165  is axially sufficiently spaced from the stationary first cartridge  154 , the blank  119  is transferred into the first cartridge, the head of the hammer  174  is placed in abutting engagement with the adjacent side of the blank  119 , and the movable second cartridge  156  is brought into engagement with the first cartridge  154 . In addition, the ram  178  and the ram operating mechanism  180  are advanced with the advancing adiabatic press assembly  165  to the position of the predetermined desired striking distance between the ram  178  and the rear, protruding end of the hammer  174 . 
     Then, as the toggle link pairs  403 ,  404  continue to move to their straight configuration, the ram  178  is fired by the ram operating mechanism  180  and the ram  178  impacts against the hammer  174 . Immediately after ram  178  impact, force is applied against the ram  178  by the advancing toggle links  403 ,  404  and the advancing adiabatic press assembly  165 , and part  182  formation is completed. 
     For reasons of maintaining a short time cycle of operation, as desired, the cycle of flexure and elongation for the toggle link pairs  401 ,  402  is preferably advanced slightly over that for the toggle link pairs  403 ,  404 , as indicated above, so that when part  182  formation is complete, the toggle link pair  401 ,  402  immediately begins to kink or flex, thereby causing the second cartridge  156  to separate from the first cartridge  154  slightly before the toggle link pair  403 ,  404  has reached its straight configuration. Thus, as the toggle link pair  403 ,  404  completes its final straightening, the final straightening causes the advance of the adiabatic press assembly  165 , with the ram  178  and the ram operating mechanism  180 , to proceed, thereby permitting the ram  178  to continue advancing the hammer  174  against the part  182  and causing the hammer  174  to eject the part  182  from the first cartridge  156 , as desired. 
     The adiabatic press assembly  165  of the forming assembly  150  is provided with a cylindrical barrel  410  that is slidably mounted in a cylinder  412  defined in a stationary third support leg  411 . Leg  411  is, like leg  159 , laterally spaced from leg  152 . The axis of the press assembly is generally coaxial with that of the stationary first cartridge  154  and the second cartridge  156  so that the ram  178  of the assembly  165  is aligned with the hammer  174  and is movable towards and away therefrom linearly. 
     The structure of the adiabatic press assembly  165  is similar to that of the structure of the adiabatic press assembly  100  and the impact press of Lindell U.S. Pat. No. 4,245,493 except that, in assembly  165 , the releasing means for applying a releasing force to the locking ring  62  for triggering ram  178  release is replaced by a trigger assembly  415 . The trigger assembly  415  utilizes a spring-biased arm  416  whose driven end is keyed to a ratcheted shaft  417  and whose driven end rests against the release ring  62 . The arrangement permits the arm  416  to have its driven end rest against the release ring  62  through substantial arc, such as can occur in normal operation of the forming assembly  150  as the impact assembly is reciprocated through its distance of travel relative to the third support leg  411 . When a servo motor (not shown, but conventional and commercially available) that is associated with the ratcheted shaft  417  and that is adapted to apply a high torque force upon activation is activated, the shaft  417  is pivoted through a controlled angle. This pivot movement swings the arm  416  and causes the driven end of arm  416  to apply sufficient force to the locking ring  62  to slide this ring forward and release the ram  178 . The electrical energy for activation of this servo motor is controlled to occur when the spacing between the protruding end of the hammer  174  and the ram  178  position has reached a predetermined distance. The amount of impact force to be delivered by the ram  178  when released at the predetermined distance is preliminarily selected and set as a preliminary adjustment of the impact press assembly  165  operation. 
     In place of a gear driving arrangement as above described, various alternative arrangements can be used. One alternative arrangement is illustrated in FIGS. 49 and 50 where a pair servo motors is employed for operating a similar gear for flexing each of the toggle link pairs. 
     Another alternative arrangement is illustrated in FIGS. 51 and 52 where a pair of concurrently operating pneumatic or hydraulic cylinders are employed, one for flexing each of the toggle link pairs. Here, each cylinders push rod is utilized to pivot a lever arm, and a gear on the axis of each lever arm is utilized to turn a connected drive gear. Each drive gear is eccentrically connected to a lever arm crank that kinks and unkinks the toggle link pairs. 
     (5) The Control and Synchronizing Assembly 
     As indicated above, translation of the elongated feedstock  103  in apparatus  100 / 101  proceeds in a stop-and-go or discontinuous manner. The feedstock  103  momentarily stops translating in a single cycle of apparatus operation at each of the following times: 
     (a) Forward translation of feedstock  103  is stopped when blank  119  is being cut-off at the feedstock  103  forward end by the impact press  100 ; 
     (b) Forward translation of feedstock  103  is stopped after the cut-off blank  119  has been pushed forwards by the feedstock  103  forward end into the transfer capsule  146  and before reverse or rearwards translation of the feedstock  103  starts, and 
     (c) Rearward translation of feedstock  103  is stopped before forward translation of the feedstock  103  commences for the purpose of permitting the feedstock  103  forward end to be advanced (translated) and positioned at the impact press  100  (for a repeat of stop (a)). 
     Since the operations of adiabatic impact press assembly  100  and the stock feeder assembly  101  are driven and controlled by the common gear train  200 , the operational movements of the impact press  100 , and of the grippers  106  (if used),  107 , and  108 , are precisely synchronized so that the above indicated desired discontinuous cyclical operation is achieved. However, as those skilled in the art will readily appreciate, various apparatus parameters can be adjusted to accomplish desired changes. For example, adjustments can be made in impact press  100  operating characteristics, such as impact force, or in stock feed  101  operating characteristics, such traverse travel distance of each of the first and second movable grippers  107  and  108  in reciprocation, or the like. Such adjustments may be desirable when a feedstock or a blank to be produced is being changed. 
     As above explained, and as indicated in FIG. 47, for example, the on/off operations of the jaws of the respective grippers  106  (if used),  107  and  108  are each determined by operation of a functionally associated, conventional-type, commercially available, double-acting, pneumatic cylinder (PC). Each such PC cylinder here employed has two longitudinally adjacent chambers, and a single reciprocatable piston means located in the cylinder between the chambers. A rod or body means associated with the piston means extends generally axially in, and projects beyond one end of, the associated cylinder. Sealing means of course is included. Each chamber of each cylinder is conveniently connected with a separate conduit means for providing that chamber with a pressurized fluid (preferably compressed air). 
     Various operational control arrangements can be used. For example, each conduit means that is so associated with a different one of a cylinder&#39;s two chambers is conveniently functionally associated with a conventional, commercially available, electromagnetically actuated, double acting, pneumatic valve assembly (EPV). Two EPV valve assemblies per PC pneumatic cylinder are utilized. Each EPV valve assembly incorporates a first and a second electromagnetically actuatable valve (not detailed), and each valve is independently actuatable and controllable by an appropriate input electric signal. Both valves of each EPV valve assembly are normally (when not actuated) in a closed configuration. As indicated in FIG. 47, the movable jaw of each gripper assembly  106 ,  107 , and  108  is actuated by a different functionally associated PC cylinder assembly  301 ,  304 , and  307 , respectively. Each of the two chambers of each PC cylinder assembly  301 ,  304 , and  307  is connected via a conduit to a different EPV valve assembly, identified as EPV valves  302  and  303  for PC cylinder assembly  301 , EPV valves  305  and  306  for PC cylinder assembly  304 , and EPV valves  308  and  309  for PC cylinder assembly  307 . 
     When, for example, a first EPV valve assembly  302  is connected across a first conduit  310 , and the first conduit  310  is associated with the first chamber  301 . 1  of the cylinder of a PC pneumatic cylinder assembly  301 , and the first valve of the first EPV valve assembly  302  is electrically actuated and opened from its normally closed configuration (while the second valve of the first EPV valve assembly  302  is maintained in a closed configuration), compressed gas is delivered through the first conduit  310  and the first valve of EPV valve assembly  302  into the connected first chamber  301 . 1 . The resulting pressure in the first chamber  301 . 1  causes cylinder&#39;s piston  316  to move responsively and longitudinally in the cylinder of cylinder assembly  301 , thereby producing a first chamber  301 . 1  elongated configuration (not shown) relative to that first chamber&#39;s initial configuration. 
     Concurrently, in the second chamber  301 . 2  of the cylinder of the PC pneumatic cylinder assembly  301 , a contracted volumetric configuration (not shown) relative to that second chamber&#39;s initial configuration results because the initial pressure in the second chamber of the cylinder is concurrently reduced, thereby to permit the desired piston  316  movement, and, concurrently, to reduce the internal volume of the second chamber  301 . 2 . Such a pressure/volume reduction in the second chamber  301 . 2  is achieved by opening the second valve of the second electromagnetically actuated EPV valve assembly  303  (while maintaining the first valve of the second EPV valve assembly  303  in a closed configuration). EPV valve assembly  303  is functionally associated with the second conduit  311  that is connected to the second chamber  301 . 2  of the same cylinder of the PC cylinder assembly  301 . This second valve of EPV valve assembly  303  is associated with a vent (not shown) to the atmosphere. Opening this second valve permits gas (air) that may be under pressure in the second chamber  301 . 2  to pass out via the second conduit  311  through the open second valve and vent to the atmosphere. Preferably, the second valve of the second EPC valve assembly  303  is opened concurrently with the opening of the first valve of the first EPC valve assembly  302  so that gas (air) pressure which may exist in the second chamber  301 . 2  of the cylinder of the PC cylinder assembly  301  is released as pressure in the first conduit  310  and connected first chamber  301 . 1  increases. 
     Similarly, EPV valve assemblies  305  and  306  each connect with respective conduits  312  and  313  that in turn each connect with a different chamber  304 . 1  and  304 . 2  of the pneumatic cylinder (PC)  304 ; and EPV valve assemblies  308  and  309  each connect with respective conduits  314  and  315  that in turn each connect with a different chamber  307 . 1  and  307 . 2  of the pneumatic cylinder (PC)  307 . 
     Pneumatic cylinder  301  operates (closes or opens) the lower jaw of fixed gripper  106 , pneumatic cylinder  304  operates (closes or opens) the lower jaw of movable gripper  107 , and pneumatic cylinder  307  operates (closes or opens) the lower jaw of the movable gripper  108 . 
     In order to control and synchronize opening and closing operations of the individual electromagnetic valve assemblies  302 ,  303 ,  305 ,  306 ,  308 , and  309 , and hence operations of their associated PC cylinder assemblies  301 ,  304 , and  307 , and the opening and closing operations of the grippers  106  (if used),  107  and  108 , various arrangements can be used. A present preference is to associate the shaft of a gear, such as the shaft  207  of the gear  202  (see FIG.  19 ), with a conventional, commercially available, electromagnetic shaft rotation position sensor (SRPS)  350  which is able to (a) selectively identify, relative to a starting location for shaft  207  rotation, successive and progressive shaft  207  positions existing during every  360  degrees of shaft  207  rotation, and (b) generate electric signal outputs that are representative of shaft  207  angular positions and rotation. Since the respective electric signals produced by the shaft rotation position sensor  350  correspond to shaft  207  positions of rotation, and represent time intervals, the signals are suitable for use, during the course of a stock feeder  101  cycle of operation, in regulating the operation of the jaws of each of the grippers  106  (if used),  107  and  108 . 
     A system for achieving such control of gripper jaw activation is illustrated in the simplified schematic diagram of FIG.  47 . The output from the shaft rotation position sensor (SRPS)  350  is fed to a signal generator (SG)  351 . For example, an analog signal from sensor  350  can be converted to a digital signal, and the output signal of signal generator (SG)  351 , which is representative of the currently existing shaft  207  operative configuration, is adapted to be charged to a computer controller (C)  352  which has been programmed with shaft  207  positions that correspond to particular times and locations where activations and deactivations of the respective jaws of the grippers  106 ,  107  and  108  are desired. The controller  352  compares these programmed positions to the signals being received from the shaft rotation position sensor  350  via the signal generator  351 . When a signal from shaft rotation position sensor  350  is found by the controller  352  to correspond to a programmed position for a gripper jaw activation, then the controller  352  generates an output signal which is received by an encoder (E)  353 . A control line  371  interconnects the encoder (E)  353  with each of these six EPV valves and the servo motor  271 . 
     The encoder  253  is programmed with the unique location identification code or address for each one of the six electromagnetically actuated pneumatic valve assemblies (EPVs)  302 ,  303 ,  305 ,  306 ,  308 , and  309  and also for the servo motor (SM)  271 . When, for example, the controller  352  identifies a shaft  207  position where a particular gripper jaw is to be activated, the controller  352  sends an information signal to the encoder  353  which accepts that signal and (a) labels it with the unique location identification codes for each of the two involved electromagnetic valves to be activated is located along the control line  271 , and (b) converts it into an activation signal for use by each one of the two involved electromagnetic valves to be activated for operating the associated cylinder assembly and the jaw of the desired gripper. Thus, in the illustration, from the input signal received from the controller  352 , the encoder  353  provides signal means that is adapted to activate the first valve of the first EPV valve assembly  302 , and signal means that is adapted to activate the second valve of the second EPV valve assembly  303 . When the first valve of the first EPV valve assembly  302  is actuated, compressed air is admitted to the first chamber  301 . 1  of the PC cylinder assembly  301 , and when the second valve of the second EPV valve assembly  303  is actuated, pressurized gas (air) is released from second chamber  301 . 2  of the PC cylinder assembly  301 . Preferably such first and second valves are concurrently actuated. 
     After a given gripper jaw has been activated (closed) for the desired time interval, the termination of that time interval is identified and detected by signals received by the controller  352  from the shaft rotation position sensor  350  via the signal generator  351 , and a signal is sent by the controller  352  to the encoder  353 . After processing, that signal is effectively forwarded to the two involved EPV valve assemblies, and, upon receipt, the respective operations of these EPV valves are reversed relative to the valve actions that occurred upon initial PC cylinder assembly activation; that is, the second valve of the first electromagnetic valve assembly is energized, while the first valve of the second electromagnetic valve assembly is energized, thereby resulting in operating the lower jaw and opening the jaws of the involved gripper. The involved gripper&#39;s jaw then remains in an open configuration until a subsequent signal is received by the controller  352  from the shaft rotation position sensor  350 . That subsequent signal marks the time when that gripper&#39;s jaws are again closed, and the process operation is repeated. Thus, the operation of the jaws of the grippers  106 ,  107  and  108  is controlled. 
     After a blank  119  is cut off from the feedstock  103 , and is advanced into the transfer capsule  146 , then the transfer capsule  146  and the transfer arm  147  are ready to be moved from the position  145  at cut-off assembly  100 / 101  to the position  155  at the forming assembly  150 . To accomplish this movement, the servo motor  271  of the transferer assembly  148  is energized for the time interval needed to accomplish such arm  147  movement. This time interval is preferably predetermined or preset, but, alternatively, a microswitch (not shown) can be located at each of the positions  145  and  155  and used to de-energize the servo motor  271  upon arrival of the arm  147  at a position  155  or  145 , as those skilled in the art will readily appreciate. 
     To control the time point where activation of the servo motor  271  is to occur, which is usually the time when the blank  119  fully charged into transfer capsule  146  and the arm  147  is able to swing without interference from the feedstock  103 , various control means can be employed. One convenient and now preferred control means is to utilize the shaft position rotation position sensor SRPS  350 . When the controller C  352  receives a control signal from the shaft rotation position sensor SRPS  350  via the signal generator SG  351 , and the controller C  352  outputs a resulting signal to the encoder E  353 , an activation signal is provided for the servo-motor  271  and the arm  147  is swung as desired. 
     In FIG. 47, the subassembly comprising the shaft rotation position sensor SRPS  350 , the signal generator SG  351 , the controller C  352 , and the encoder E  253  is collectively identified for convenience in FIG. 47 as control I which is functionally associated with the cut-off assembly  100 / 101 . A corresponding subassembly comprising a shaft rotation position sensor  375 , a signal generator SG  376 , a controller C  377 , and an encoder E  378  is functionally associated with the forming assembly  150  and is collectively identified for convenience as control II in FIG.  47 . 
     In the forming assembly  150 , as indicated in FIG. 47, the pneumatic cylinder  185  has its chambers  193 A and  193 B pressurized/depressurized by two EPV valves  330  and  331 , respectively, while the chambers  173 A and  173 B used for moving the hammer  174  in the first chamber  154  assembly are pressurized/depressurized by two EPV valves  333  and  334 , respectively. The two EPV valves  327  and  328  of the transfer capsule  146  that are used for extending and retracting the shaft  167  and for supplying compressed gas or the like through channels  171  and  172 , respectively, are conveniently controlled as a part of the operations of the forming assembly  150 . 
     The SRPS sensor  375  is conveniently associated with the shaft  292  of gear  282 . After the arm  147  is in position  155  and the servo motor  271  is deenergized, the shaft rotation position sensor SRPS  375 , signals, through the signal generator  376 , the controller  377  that the transfer capsule  146  is ready to be actuated pneumatically and the controller  377  sends a signal to the encoder  378 . The encoder  378 issues addressed signals to the first valve of the EPV valve assembly  327  and to the second valve of the EPV valve assembly  328  that are associated with the transfer capsule  146 , thereby causing the shaft  167  to move the blank  119  from the transfer capsule into the first cartridge  154 . Thereafter, the sequence is reversed upon receipt and processing of another signal produced using the assembly II, and the shaft  167  is retracted into the transfer capsule  146 . 
     Next, another signal produced using the assembly II is used to actuate the servo motor  271 . Signals received from the shaft position rotation sensor  375  and processed through the signal generator  376 , the controller  377  and the encoder  378 , result, after servo motor actuation, in movement of the arm  147  from position  155  back to position  145 . 
     Thereafter, the operation of the EPV valves  330 ,  331 , and the EPV valves  333 ,  334  proceeds using signals generated by the SRPS sensor  375  as assembly  150  operation proceeds, in the same manner as above described for EPV valves  327 ,  328 . Thus, operations of the transfer capsule  146 , cylinder assembly  185 , and hammer  174  are controlled and synchronized in the forming assembly  150 . 
     A separate signal generated by the SRPS sensor  375  is initially set for actuating at the predetermined desired time the trigger assembly  415  of the press assembly  165  for release of the ram  178 . 
     Various adjustments are made to change or alter other adjustable operating variables of the assembly  150 , as those skilled in the art will appreciate. 
     In order to control and maintain a desired operating speed for the motor  290  in the cut-off assembly  100 / 101 , a conventional control loop may be employed which incorporates the motor  227 , the shaft rotation sensor  350  and a controllable rheostat (not detailed, but conventional and commercially available) that is set to feed electric line power to motor  227  at a rate controlled to maintain a nearly constant desired motor operating speed. Deviations from the desired speed produce changes in shaft  207  rotation speed that are sensed by sensor  350 . A drop in shaft  207  rotation speed below that desired causes an incremental change in the rheostat setting so that more power is fed to motor  227  causing the motor speed and the shaft rotation speed to increase up to the desired speed. A rise in shaft  207  rotation speed above that desired causes an incremental change in the rheostat setting so that less power is fed to motor  227  causing the motor speed and the shaft rotation speed to decrease down to the desired speed. 
     Similarly, a desired motor operating speed is maintained for motor  290  in the forming assembly  150  using the sensor  375 , and a controllable rheostat (not shown) in a control loop. 
     If desired a control loop to maintain the cut-off assembly  100 / 101  operating at a speed that matches the operating speed of the forming machine  150  can be employed if desired. However, by manually regulating the motor speeds of the cut off assembly  100 / 101  and the forming machine  150 , such a control loop can be avoided owing to the ability of the motor speed control loops above described to maintain accurately machine operating speed. 
     Thus, the operation, control and synchronization of the system  99  is achieved while independently maintaining the respective operations of the cut off assembly and the forming assembly. 
     It is a feature of the system  99  that the cut-off assembly  100 / 101  and the forming assembly can be used as independent and separate systems. The transferer assembly  148  and the control systems employed make such usage possible. 
     It is another feature of the system  99  that the cut-off assembly  100 / 101  can be used in various combinations with the forming assembly  150  using the transferor assembly beyond that above described and illustrated. One such combination is shown in FIG. 53 where, using two transferor assemblies, one cut-off assembly feeds blanks to a forming assembly for partial forming and then the partially formed products are fed to a second forming assembly to make parts. 
     With regard to FIG. 53, two transferor assemblies and forming stations are provided to divide the amount of forming work in half and to prepare the blank in forming station I to make it easier in forming station II to finalize the part. This may be necessary for the forming of complicated configurations or difficult materials. 
     Another such combination is shown in FIG. 54 where, using one cut-off assembly and two transferor assemblies, blanks are alternatively fed to each of two forming machines to make parts concurrently. 
     From the foregoing disclosures taken with the accompanying drawings, various modifications, embodiments, and the like will be apparent to those skilled in the art, and such are within the spirit and scope of this invention.