Abstract:
A roll-type straightening and feed mechanism includes opposing sets of straightening rolls adapted to straighten coil stock as it travels therebetween, opposing feed rolls adapted to grip the coil stock therebetween to advance the straightened coil stock to a using station, and operators connected to simultaneously separate the straightening rolls and the feed rolls and release the coil stock therebetween, and to simultaneously reset the straightening rolls and the feed roll and re-grip the coil stock for advancing straightened stock.

Description:
CROSS-REFERENCES TO RELATED APPLICATIONS 
     none. 
     REFERENCE TO MICROFICHE APPENDIX 
     not applicable. 
     STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT 
     not applicable. 
     BACKGROUND OF THE INVENTION 
     1. Field of Invention 
     The present invention relates generally to apparatus for straightening coil stock, and then feeding the straightened coil stock to a using station. 
     More particularly, the invention relates to apparatus provided with both straightening and feed rolls that are adapted to simultaneously engage the coil stock during material demand by the using station, and to simultaneously release the coil stock in the absence of material demand from the using station, and which, while suitable for other uses, is particularly useful in intermittently feeding coil stock to a punch press for ease of final positioning of the stock in the press. 
     2. Description of Prior Art 
     A conventional punch press line adapted to punch parts from coiled strip stock includes a reel that holds the coiled stock, a stock straightening mechanism that straightens the stock as it is drawn off the reel, and a feed mechanism that draws the stock from the straightener and feeds the straightened stock to the punch press. 
     A conventional coil stock feed mechanism includes a set of power-rotated feed rollers between which the strip stock is gripped, to pull the stock from the straightener and feed the stock to the punch press. For use with a punch press, the feed rolls are operative to alternately advance the stock in a selected length increment to the press, and then release the stock during the each punch cycle of the press. 
     A conventional coil stock straightening mechanism includes two sets of rollers between which the stock travels in a wave such that the stock cyclically flexes in alternating directions as it travels therethrough. 
     Precision stamping of strip stock requires the stock to be precisely positioned in the punch press during each punch cycle. This precision positioning is typically accomplished by punching a pilot hole in the stock at a first station, and actuating a tapered pilot pin at a second station through a pilot hole that was punched at the first station during a preceding press cycle for final positioning of the stock at the second station prior to punching of the desired part. During each cycle, the stock is feed into the punch press approximately one to two thousandths (0.001-0.002) inch short of the desired position by the feed mechanism, the feed mechanism releases the stock, and the tapered pilot pin draws the stock the additional 0.001-0.002 inch into the desired final position. After the desired part has been punched, the pilot pin is withdrawn, and the feed mechanism re-engages the stock to feed stock for the next cycle. Thus, operation of the feed mechanism is controlled in cyclic synchronization with the pilot pin operation of the punch press, or some other type of position control associated with the cyclic operation of the press. 
     Traditionally, the straightener and feed mechanisms are provided in separate units, with a loop of the coil stock therebetween. This loop of stock accommodates the difference in feed characteristics of the continuously acting straightener and the intermittently pulling feed mechanism. One such conventional arrangement is generally shown in Waddington U.S. Pat. No. 5,150,022. 
     In certain instances, the straightener and feed mechanisms have been combined into a single unit. This provides advantages including the elimination of the loop of material and an associated reduction of floor space requirements. The combined unit also simplifies set-up and control of the entire straightening and feeding process because the straightened material moves directly from the straightening rolls into the feed rolls and then into the die area of the punch press. 
     However, prior combined roll-type straightener and feed mechanisms present certain difficulties as regards the final positioning of the stock in the punch press. With the elimination of the loop of material, the integrated straightening mechanism resists movement of the stock into its final position as a result of the continuous tension applied to the stock by the straightener rolls. As a result, the pilot mechanism in the punch press must be adapted to overcome this tension as it pulls the stock into final position. Consequently, presses set-up for use with a combined straightener and feed mechanism typically experience wear of the pilot pin at an increased rate distortion of the material being fed, and are subject to loss in final positioning accuracy at a faster rate as compared with presses that are fed by a conventional feed mechanism that is separated from the straightening mechanism. Another drawback of prior combined straightening and feed mechanisms is that they are subject to loss in roll position and overall feed length accuracy. 
     Thus, it is apparent that there is a need for a combined straightening and feed mechanism that provides the benefits, but eliminates the above-identified disadvantages associated with prior combined straightening and feed mechanisms. 
     SUMMARY OF THE INVENTION 
     The general aim of the present invention is to provide new and improved combined feed and straightening apparatus adapted to feed precisely controlled length increments of coiled strip stock to a punch press in synchronization with the final positioning control system of the press, and which eliminates the continuously acting straightening roller tension on the stock of prior apparatus of the same general type. 
     A detailed objective is to achieve the foregoing by providing feed rollers and straightening rollers that simultaneously engage the strip material for straightening and advancing a length of stock to the punch press during a material demand cycle, and that simultaneously release the material at the end of each material demand cycle for final positioning in the press. 
     These and other objectives and advantages of the invention will become more apparent from the following detailed description when taken in conjunction with the accompanying drawings. 
     Briefly, a combined coil stock feed and straightening device includes a pair of feed rollers located on opposite sides of a feed path along which the strip stock is guided, and two sets of straightening rollers upstream of the feed rollers on opposite sides of the feed path. 
     Incremental movement of the coil stock through the device is accomplished by power rotating the feed rollers while the strip material is clamped therebetween, and stopping and separating the feed rollers to stop further powered movement of the strip material during operation of the punch press. The straightening rollers are adapted to separate from the coil stock simultaneously with the feed rollers for ease of final positioning of the stock in the press. 
     In preferred embodiments, one of the feed rollers is rotated on a fixed axis in relation to the feed path, and the other feed roller is moveable toward and away from the fixed feed roller between a material gripping position and a material release position. Similarly, one of the sets of straightening rollers rotate on fixed axes in relation to the feed path, and the other set is movable toward and away from the fixed set for movement between a material engaging-straightening position and a material release position. 
     A pair of operators, responsive to fluidic control signals, effect synchronized movement of the movable feed roller and the movable set of straightening rollers between said positions, and associated pilot release valves are operable to supply the fluidic control signals in response to material demand signals from the punch press. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a left side cross-sectional view taken substantially through the center of a combined coil stock straightening and feed apparatus incorporating the unique aspects of the present invention, the apparatus being shown in its material gripping condition, for straightening and feeding coil stock to a using station. 
     FIG. 2 is a view similar to FIG. 1, but with the apparatus shown in its material release condition. 
     FIG. 3 is a top view taken substantially along the line  3 — 3  of FIG.  6 . 
     FIG. 4 is a top view taken substantially along the line  4 — 4  of FIG. 6, with certain parts broken away and shown in cross-section, and with the apparatus shown in its material gripping condition. 
     FIG. 5 is a top view with certain parts broken away and shown in cross-section, and with the apparatus shown in its material release condition. 
     FIG. 6 is a left side view showing certain gear-drive and other internal components in dashed lines. 
     FIG. 7 is a right side view taken substantially along the line  7 — 7  of FIG. 3, with the apparatus shown in its material gripping condition. 
     FIG. 8 is a view similar to FIG. 7, but with the apparatus shown in its material release condition. 
     FIG. 9 is a view taken substantially along the line  9 — 9  of FIG.  3 . 
     FIG. 10 is a downstream end view, with certain parts broken away and shown in cross-section. 
     FIG. 11 is a schematic representation of certain fluidic and electrical components of the apparatus of FIG.  1  and showing said components in a material-feed condition. 
     FIG. 12 is a schematic representation similar to FIG. 11 but showing said components in a material-release condition. 
    
    
     While the invention is susceptible of various modifications and alternative constructions, a certain illustrated embodiment has been shown in the drawings and will be described below in detail. It should be understood, however, that there is no intention to limit the invention to the specific form disclosed, but on the contrary, the intention is to cover all modifications, alternative constructions, and equivalents falling within the spirit and scope of the invention. 
     Reference numerals shown in the drawings correspond to the following items: 
       10 —combined straightening and feed device 
       12 —upstream end of device  10   
       14 —downstream end of device  10   
       16 —strip stock 
       18 —lower drive feed roller 
       18   a —bearings supporting lower drive feed roller 
       18   b —rotational axis of lower drive feed roller 
       20 —upper pinch feed roller 
       20   a —bearings supporting upper drive feed roller 
       20   b —rotational axis of upper drive feed roller in material gripping condition 
       20   b ′—rotational axis of upper drive feed roller in material release condition 
       22 —rotary drive unit 
       24 —output shaft of drive unit 
       26 —fixed straightening rollers 
       26   a —bearings supporting fixed straightening rollers 
       26   b —rotational axes of fixed straightening rollers 
       28 —movable straightening rollers 
       28   a —bearings supporting movable straightening rollers 
       28   b —rotational axes of movable straightening rollers 
       30 —casing/rigid frame structure 
       32 —fixed side supports 
       34 —drive belt 
       36 —pulley on lower drive unit 
       38 —pulley on drive unit output shaft 
       40 —bracket 
       40   a —bearings supporting bracket 
       40   b —rotational axes of bracket 
       42 —sidewalls of bracket 
       44 —connecting member 
       46 —tail section 
       46   a —hole in tail section 
       48 —gear of lower feed roll 
       50 —gear of upper feed roll 
       52 —idler gear 
       54 —idler gear 
       56 —spring assembly 
       56   a —adjustable spring retainer 
       56   b —lock nut 
       58 —actuator 
       60 —piston 
       62 —piston bore 
       64 —air chamber 
       66 —piston seal 
       68 —piston rod 
       70 —rod seal 
       72 —pin 
       74 —radius profile 
       76 —rubber stop 
       78 —actuator cap 
       80 —rubber stop 
       84 —gear 
       86 —gear 
       88 —gears 
       90 —gears 
       92 —platen 
       92   a —bearings supporting platen 
       92   b —pivoting axis of platen 
       92   c —bracket 
       94 —entrance guide roller 
       94   a —adjustable edge guides 
       96 —actuator 
       97 —actuator cap 
       98 —springs 
       98   a —counterbore 
       100 —cam 
       102 —wear plate 
       104 —piston 
       106 —piston bore 
       108 —piston seal 
       110 —piston rod 
       112 —rack 
       114   a —gear 
       114   b —gear 
       114   c —gear 
       116 —drive shaft 
       118 —air chamber 
       120 —rubber stop 
       122 —rubber stop 
       124 —air pilot valve 
       126 —air pilot valve 
       128 —control unit module 
       130 —air pressure supply 
       132 —control signals from punch press 
     A—A—feed path of strip stock  16   
     DETAILED DESCRIPTION OF THE INVENTION 
     For purposes of illustration, the present invention is shown in the drawings as a combined material feed and straightening device  10  (FIG. 1) adapted to incrementally feed precise lengths of straightened continuous strip material  16  along a feed path A—A from a supply coil to a punch press in synchronization with the final positioning arrangement of the press. 
     Briefly, the device  10  includes a casing or rigid frame structure generally indicated as  30  having fixed side supports generally indicated as  32  that extend lengthwise between upstream and downstream ends  12  and  14  on each side of the feed path A—A; a pair of feed rollers  18  and  20  operatively coupled to a rotary drive unit  22  for advancing the strip material  16  along the feed path; and two sets of straightening rollers  26  and  28  adapted to effect straightening of the material as it travels through the device. 
     The feed rollers  18  and  20  are located on opposite sides of the feed path A—A proximate the downstream end  14 , are mounted for rotation about parallel axes  18   b  and  20   b  extending transversely to the feed path, and comprise (i) a lower drive feed roller  18  mounted in fixed relation to the casing  30 , and (ii) an upper pinch feed roller  20  operably connected to a pneumatic operator  58  for movement between (a) a material gripping position (as shown in FIG. 1) cooperative with the lower drive feed roller for gripping the strip material  16  therebetween and advancing the material toward the punch press in response to a control or feedback signal from the press during a material demand cycle, and (b) a material release position (as shown in FIG. 2) spaced from the strip material in response to a second signal from the press indicating the end of the material demand cycle. 
     The straightening rollers  26  and  28  are located on opposite sides of the feed path A—A upstream of the feed rollers  18  and  20 , are mounted for rotation about axes  26   b  and  28   b  parallel to the feed rollers, and comprise (i) a lower set of straightening rollers  26  mounted in fixed relation to the casing  30 , and (ii) an upper set of straightening rollers  28  operably connected to a second pneumatic operator  96  for synchronized movement with the upper feed roller  20  between (a) a material engaging position (FIG. 1) cooperative with the lower straightening rollers for straightening the strip material  16  prior to reaching the feed rollers during the material demand cycles of the punch press, and (b) a material release position (FIG. 2) spaced from the strip material between the material demand cycles. 
     In the embodiment shown, the lower drive feed roller  18  is journaled between the side supports  32  of the casing  30  in bearings  18   a  (FIG. 3) for rotation about axis  18   b  below the feed path A—A. The output shaft  24  of drive unit  22  is coupled for rotation of the lower feed roller such as with gears or a chain, and in the embodiment shown through a drive belt  34  connected between pulleys  36  and  38  provided at the ends thereof (see FIGS.  5  and  7 ). Suitable drive units include, but are not limited to brushless AC servomotors and stepper motors, such as provided with a resolver adapted to provide a closed-loop roller position feedback signal for use by the system controller. 
     The upper pinch feed roller  20  is journaled in bearings  20   a  (FIG. 3) between laterally spaced side walls  42  of a bracket  40  for rotation about axis  20   b  above the feed path, and is journaled with respect to the casing  30  for limited pivoting toward and away from the lower feed roller. In this instance, the bracket is journal mounted between the side supports  32  about an axis  40   b  above the feed path A—A and parallel to but spaced transversely of the axes  18   b  and  20   b  for swinging between (i) a lower position (FIG.  1 )in which the upper feed roller is in gripping engagement with the strip material  16  located in the feed path, and (ii) a raised position (FIG. 2) in which the upper feed roller is spaced from the strip material in the feed path. The bracket shown includes a generally horizontal upper section  44  connecting the side walls  42 , and a generally vertical tail section  46  depending therebetween at a position below the lower drive feed roller  18 . 
     The upper feed roller  20  is rotationally coupled to the lower feed roller  18  by gears  48  and  50  connected through idler gears  52  and  54  that are rotatably supported on idler shafts carried by the casing  30  (see FIGS. 3,  4  and  6 ). The gears  48 ,  50 ,  52  and  54  are provided with the same pitch diameter so that the feed rollers rotate at the same speed but in opposite angular directions as indicated. Thus, when the upper feed roller is in its material gripping position (FIG.  1 ), the drive unit  22  power rotates both feed rollers for advancing a length of the strip material  16  passing therebetween toward the punch press. Advantageously, idler gear  54  rotates about the journal mounting axis  40   b  such that, as the bracket pivots about the same axis  40   b , the gear  50  connected to upper feed roller rotates about the center of, and rolls along the idler gear  54  to maintain full engagement therebetween. 
     As shown in FIG. 1, the upper feed roller  20  is spring biased into its material gripping position by spring  56 , and pneumatically actuated to the material release position (FIG. 2) by pneumatic actuator  58 . To that end, spring  56  is grounded to the casing  30  and positioned to engage the bracket  40  oppositely of the journal mounting axis  40   b  with respect to the pinch roller axis  20   b  to continuously bias the bracket toward its lower position, and the actuator  58  is connected to the tail section  46  of the bracket oppositely of the journal mounting axis  40   b  with respect to the feed path A—A for rotation of the bracket from its lower position to its upper position in contravention to the resilient biasing force of the spring. An adjustable spring retainer  56   a  threaded through the casing  30  and locked into position with a threaded nut  56   b , permits manual adjustment of the spring-bias gripping force between the feed rollers. 
     The linear pneumatic actuator  58  includes a piston  60  slidably located in a piston bore  62  defined within the casing  30  and pneumatically responsive for linear movement therein to pressure in air chamber  64  defined in the piston bore; a piston seal  66  positioned to establish a sliding, sealing engagement between the piston and the piston bore; and a piston rod  68  that extends through a rod seal  70  and that is operatively connected at its free end to the tail section  46  of the bracket  40 . In this instance, the piston rod extends slidably through a hole  46   a  in the tail section of the bracket, and a pin  72  located in a cross-hole in the piston rod maintains the piston rod in position therein. A radius-profile  74  formed in the tail section provides a relatively low-friction, automatically centering interface with the outer cylindrical profile of the pin. For actuation stability, the actuator is aligned with the lateral center of the bracket for connection to the center of the tail section (see FIG.  3 ). 
     With this arrangement, as air pressure is supplied to chamber  64 , the piston  60  strokes in a direction away from the tail section  46  (to the left as shown in FIGS.  1  and  2 ), and the pin  72  engages and draws the tail section  46  with the piston, pivoting the bracket  40  toward its raised position (clockwise as shown in FIGS. 1 and 2) and the upper feed roller  20  toward its material release position, until a rubber stop  76  engages against the actuator cap  78  (FIG.  2 ). 
     As air pressure is relieved from the chamber  64 , the bias force of spring  56  rotates the bracket  40  towards it lower position (counter-clockwise as shown) and the upper feed roller  20  toward the lower feed roller  18  and into gripping engagement with the strip material  16  therebetween. As the bracket rotates, the tail section acts against the pin  72  to return the piston to its extended position (FIG.  1 ). A second rubber stop  80  is optionally provided in the actuator chamber  64  to cushion the return stroke of the piston, and to reduce the volume of the chamber without affecting the pressure responsive area of the piston for relatively short actuator response time characteristics. 
     The lower straightening rollers  26  are journaled between the side supports  32  of the casing  30  in bearings  26   a  (FIG. 3) for rotation about axes  26   b  below the feed path A—A. The lower straightening rollers are rotated by the drive unit  22  through a gear train comprising a gear  84  that is connected for rotation with the lower feed roller  18  and that drives gears  86   a  and  86   b , the latter of which is connected via a common shaft to gear  86   c  which, in turn, drives idler gears  88  journaled in the side supports  32  on idler shafts and gears  90  connected to ends of the lower straightening rollers engaging the idler gears (see FIGS. 3,  6  and  8 ). 
     The upper straightening rollers  28  are journaled in a platen  92  for free rotation about axes  28   b  (see FIGS.  1  and  9 ), and are journaled for limited pivoting with respect to the casing  30  toward and away from the lower straightening rollers. In this instance, the straightening rollers  28  are journaled on pins  28   a  connected to the sides of a bracket  92   c  carried by the platen, and the platen is pivotally mounted between the side supports  32  for pivoting about an axis  92   b  parallel to the feed path A—A proximate the upstream end thereof for swinging between (i) a lower position (FIG.  1 )in which the upper straightening rollers are in straightening engagement with the strip material  16  located in the feed path, and (ii) a raised position (FIG.  2 )in which the upper rollers are spaced from the strip material in the feed path. The axes  28   b  of the upper straightening rollers may be fixed in the platen  92 , or the bracket  92   c  may be adapted for adjustment of the axes  28   b  such as disclosed in further detail in patent, U.S. Pat. No. 4,594,872 which is incorporated herein by reference. An entrance guide roller  94  provided upstream of the straightening rollers includes adjustable edge guides  94   a  (FIG. 3) to position the strip material  16  laterally between the side supports  32  as it feeds into the device  10 . 
     The upper straightening rollers  28  are spring biased into their material release position, and pneumatically actuated to their material engaging-straightening position by a second pneumatic actuator  96 . In this instance, a pair of laterally spaced springs  98  (see FIGS. 1 and 4) are positioned for acting between the casing  30  and the downstream end of the platen  92  to continuously bias the platen upwardly toward its raised position against a cam  100 , and the actuator  96  is connected for actuation of the cam  100  (i) to effect movement of the platen from its raised position to its lower position in contravention to the resilient biasing force of the springs  98 , and (ii) to permit rotation of the platen from its lower position to its raised position from the biasing action of the springs  98 . 
     The cam  100  is carried by a drive shaft  116  that is journal mounted for pivoting about axis  116   b  above the downstream end of the platen  92  between first and second positions associated with the raised and lowered positions of the platen. The cam includes an operative surface portion that is off-set below axis  116   b  and that is positioned to slidably act against a hardened wear-plate  102  carried at the downstream end of the platen  92  such that pivoting of the cam about axis  116   b  causes the contact between the cam and the wear plate to lower and raise as shown in FIGS. 1 and 2, respectively. In the embodiment shown, the opposite end of the cam is threaded into a spacer  100   a  that is connected to the end of the shaft  116  with a pin  100   b  extending therethrough. 
     The second pneumatic actuator  96  is constructed similar to actuator  58 , and includes a pneumatically actuated piston  104  slidably located in a piston bore  106  defined within the casing  30  for linear movement between retracted and extended positions as shown in FIGS. 4 and 5, respectively, a low friction piston seal  108  positioned to establish a sliding, sealing engagement between the piston and the piston bore, and a piston rod  110  extending from the piston for linear movement therewith. 
     In this instance, the piston rod  110  is coupled to a gear-toothed rack  112  for linear reciprocating movement as shown in FIGS. 7 and 8, and the rack drivingly engages a set of gears  114   a-c  to translate the linear piston motion into rotary motion. The upper gear  114   c  rotates about axis  116   b  and is connected to the cam  100  through the drive shaft  116 . 
     With this arrangement, as air pressure is supplied to the chamber  118 , the piston  104  strokes in the direction away from the rack  112  (to the left as shown in FIGS.  7  and  8 ), the rack moves with the piston and rotates the gears  114   a-c , rotating the cam  100  toward its lowered position, until the rubber stop  120  engages against the actuator cap  97  as shown in FIG.  7 . As the cam pivots downwardly, it acts against the upwardly biased wear plate  102  to drive the platen  92  downwardly to its lower position and the upper straightening rollers  28  to their material engaging-straightening position (FIG.  1 ). 
     As air pressure is relieved from the chamber  118 , the bias force of springs  98  simultaneously raises the platen  92 , and acting through the wear plate  102 , rotate the cam  100  to their raised position (FIG.  2 ), and returns the piston  104  to its extended position (FIG.  8 ). A second rubber stop  122  is optionally provided to cushion the return stroke of the piston, and to reduce the volume of the chamber without affecting the pressure responsive area of the piston for relatively short actuator response time characteristics. 
     Synchronized pneumatic signals are provided to the actuators  58  and  96 , to effect synchronized operation of the feed roller  20  and the straightening rollers  28 , via synchronized operation of solenoid operated air pilot valves  124  and  126  that are pneumatically coupled to the actuators and electrically connected to receive control signals from a control unit  128 . 
     As shown in the schematic in FIG. 11, the pilot valve  124  is spring biased to a normally open position to vent chamber  64  of actuator  58  to atmosphere, and the pilot valve  126  is spring-biased to a normally closed position to establish fluid communication between chamber  118  of actuator  96  and a fluid pressure supply  130 . Thus, absent an energizing control signal to the pilot valves  124  and  126 , the spring  56  biases the feed roller  20  to its material gripping position, and the actuator  96  drives the cam  100  to its lower position and the upper straightening rollers  28  to their material straightening position, such that the device  10  is operative to simultaneously straighten the coil stock  16  and feed the straightened material to the punch press. 
     When the pilot valves  124  and  126  are energized, the valve  124  closes to establish communication between the chamber  64  and the pressure source  130 , and the valve  126  opens to vent the chamber  118  to atmosphere. As discussed above, pressure to the chamber  64  causes the upper feed roller  20  to swing to its material release position, and the absence of pressure in chamber  118  allows the platen springs  98  to bias the upper straightening rollers  28  upwardly to their material release position. 
     Thus, simultaneously energizing and de-energizing the solenoid operated pilot valves  124  and  126  results in synchronized actuation of the feed rollers and the straightening rollers between their material engaging-gripping positions and material release positions. 
     An automatic control system operatively coupled between the combined material feed and straightening device  10  and the punch press is adapted to synchronize the feed and straightener operations of the device  10  with the material demand cycles of the punch press. Preferably, the control system includes a closed-loop, electronic control module  128  that is adapted to control the feed and straightening functions of a conventional material feed device, but modified to accomplish the feed and straightening synchronization functions of the present invention. Thus, the controller can be programmed with an integral or remote data entry keypad and associated programmable control module. The controller will be typically adapted for manual, single cycle, and automatic operating modes. And the controller can be provided with adjustable ramping speed and suitable fault diagnostics, as well as job memory, full batch and cumulative/cyclic counting functions. 
     To accomplish synchronized operation between the device  10  and the punch press, the controller receives signals  132  from the punch press indicating the start and end of the material demand cycles, and provides appropriate control signals to the pilot valves  124  and  126  in accordance herewith. In the embodiment described, when the controller receives a signal from the punch press indicating the start of a material demand cycle, the controller provides signals to simultaneously de-energize the solenoids of the pilot air valves such that the feed roller  20  and straightening rollers  28  simultaneously move to their material gripping-feeding and straightening positions, whereupon the power-rotated feed rollers draw the strip material through the straightening rollers, and advance the straightened stock toward the punch press. When the controller receives a signal from the press indicating a sufficient length of material has been provided and thus the demand for material has ended, the controller initiates signals to energize the pilot valves, whereupon the upper feed roller and the upper straightening rollers actuate to their material release positions and free the strip for final position in the press. Upon receiving the next material demand signal from the press, the controller simultaneously de-energized the pilot valves, and the upper feed roller and straightening rollers return to their material gripping-feeding and straightening positions without any loss in material roll position. This activity cycle is repeated for each operating cycle of the punch press. 
     Those skilled in the art will recognize that alternate arrangements are suitable for use in the invention hereof. For example, but without limitation, alternate arrangements will include the use of hydraulics to actuate the operators, dual-acting actuators rather than spring-biased actuators, and alternate biasing arrangements such as air springs. These and additional equivalents and alternate arrangements will fall within the scope of the present invention. 
     From the foregoing, it will be apparent that the present invention brings to the art a new and improved apparatus adapted to simultaneously straightening and feed strip material to a punch press or other using station. More particularly, the device is uniquely adapted to simultaneously release both the feed pressure and the straightening pressure on the strip material during a portion of each press cycle for ease of final positioning in the press, or for other using station purposes, and to simultaneously reset and regrip the strip material, to reapply the feed pressure and straightening pressure to the material for advancing and simultaneously straightening the next length of stock to the press.