US2318107A - High speed punch press - Google Patents

Description

May 4, 1943. ca. B. SCHEFFEY HIGH SPEED mmcn PRESS Filed March 25, 1941 eat 1 6 Sheets-Sh May 4, 1943. s. B. SCHEFFEY HIGH SPEED PUNCH PRESS Filed March 25 1941 6 Sheets-Sheet 2 May 4,1943. 6. B. SCHEFFEY HIGH SPEED PUNCH PRESS Filed March 25, 1941 s Sheets- Sheet s May 4, 1943- (5. B. SCHEFFEY HIGH SPEED :uucn PRESS I 6 Sheets-Sheet 4 Filed March 25, 1941 M 4, 1943- G. E. S CHEFFE'Y 2,318,107

HIGH SPEED PUNCH PRE-SS Filed March 25, 1941 e Sheets-Sheet 5 May 4, 1943, I e. B. SCHEFFEY Patented May 4, 1943 UNEE ST TES ATENT F F l C E HIGH SPEED PUNCH PRESS George B. Schefiey, Reading, Pa., as'signor'to James H. Sternbergh, Reading, Pa., and himself, jointly 30 Claims.

This invention relates to high-speed machines and more particularly to punch or die presses for working on sheet strip or coiled metal. The term high speed as herein used is to be interpreted as relating to the speed at which the punch or tool actually penetrates the metal and performs the punching operation rather than the number of blanks, for example, which may be delivered per minute.

The primary purpose of the invention is to efi'ect an increased rate of production with the exceptional extension of the life of tools and dies and an improved quality of work with an expenditure of notably less power and with greater flexibility and variety of performance than is possible with present machines. And it is with respect to such machines that the invention will be hereinafter described.

One of the objects of the present invention is to provide a strong and substantial machine which will easily and rapidly perform the Work intended upon metal stock in strip or coil form either as a series of continuously repeating operations or as single operations, as desired.

A further object is to provide a practical machine of the above character which willhave an extremely high operating speed and a still higher punch action thereby to reduce the wear upon the die and punch. I

A further object is to provide a substantial automatic machine of the above character in which the actual punching operation is accomplished by a substantially instantaneous blow as distinguished from the now common relatively lowspeed, high-pressure punching operations of other presses. I

A further object is to provide a press of the last above-mentioned character in which the punch may operate against the metal substantially without entering the die at any time.

A further object is to provide a machine of the above character with improved lubricating means.

A further object is to provide a machine which may be easily and quickly set up according to the variations in material operated upon and tools employed Within a minimum time and with absolute assurance of accuracy of position.

A further object is to provide an improved machine of the above character which may be easily and quickly converted to and from single press operations or multiple series operations as desired.

A further object is to provide a practical press which will be reliable and safe in useand operation and which will be substantially automatic in its performance.

A further object is to provide a press of the above character which may be started and stopped by suitable conveniently positioned actuating members thereby increasing the safety to th operators. I

A further object is to provide a high-speed punch press which may be easily and quickly converted from one style of Work to another as far as changing of punches or dies is concerned and after such changes may be easily and quickly adjusted with respect to the thickness of the Work and the relative position of the die bed with respect to the cooperating tools.

Other objects will be in part obvious from the annexed drawings and in part hereinafter indicated inconnection therewith by the following analysis of this invention.

This invention accordingly consists in the features of construction, combination of parts, unique relation of members, and the relative proportioning and disposition thereof, all as more completely outlined herein.

To enable others skilled in the art fully 'tocomprehend the underlying features of this invention, that they may embody the same by the numerous modifications in structure and relation contemplated by the invention, drawings depicting two embodiments of the invention form a part of this disclosure, and in such drawings like characters of reference denote corresponding parts throughout the several views, in which- Figure 1 is a front elevational view of the upper part of the complete machine.

Figure 1a. is a similar view of the lower part.

Figure 2 is a side elevational view of the same machine showing the upper part disclosed in Figure 1.

Figure 2a is a similar view taken at right angles to Figure 1a and together show the complete machine.

Figure 3 is an enlarged detailed view showing the feed rollers, certain parts being in cross-sec.- tion.

Figure 4 is a detailed perspective viewof one set of feed rollers.

Figures 5 and 6 are detailed sectional views with the set of feed rollers in different positions.

Figure 7 is'a detailed View of the" wiring diapact member shown in Figure 1.

In order that a clearer perception of the pres' ent invention may be had it is to be noted that the present machine comprehends an unusually high-speed mechanism, that is, one in which the main operating shaft may efficiently turn at approximately 1000 R. P. M. with a 1" stroke or approximately 2000 R. P. M. with stroke and consequently produce a corresponding number of punchings or like operations. It is to be understood that the terms punch or punching are to be used in a broad sense, that is, denoting a tool and either an actual piercing or punching operation or a series of punches or dies operating simultaneously but in sequence upon a strip of metal as fed, for example, to provide a finished article of the desired size and shape. When used with a series of tools it is customary to include the usual punch and pilot which are here omitted for the sake of clearness.

Referring now in detail to the drawings, and more particularly to Figures 1, 1a, 2 and 2a, the entire press mechanism is for the most part enclosed in a suitable rectangular or box-like casing mounted upon a large and substantial base 2| which may be secured to a factory floor or the like in any desired manner. Outside of the base 2| and casing 20 a suitable source of power is provided such as an electric motor 22 together with transformer, speed control, etc. (not shown). These parts form no part of the present invention except insofar as they may enter into certain combinations hereinafter set forth, and

are of standard construction and need no detailed explanation or illustration.

A main power shaft 23 extends fore and aft of the casing 20 through the upper part and is driven directly and independently from the motor 22 modate the machine to variations in weight of V the punches and dies employed. Such means which may be a plate 21 or the like, also are of well known construction and further details thereof are unnecessary.

These above mentioned parts broadly indicated in Figures 2 and 2a, include the motor 22 and its V-belt 24, to drive the power shaft 23 extending forwardly through the machine, the clutch 25, the counterbalancing flywheel 26 and a suitable crosshead mechanism, as shown in Figure 1, to a front bearing 28. It is the peculiar construction and novel arrangement of the parts of this'crosshead which contribute largely to make effective the high speed of the entire machine.

As shown more clearly in Figure 1 the crosshead comprises vertical side guides 30, secured in any desired manner to the inner walls of the casing 20. These guides are preferably V-shaped in cross-section, as shown more clearly in Figure 10, and accommodate the vertically sliding portion 3| of the crosshead. This vertically sliding member 3| is generally rectangular in shape and is provided with corresponding built-up, V- shaped gibs 32, of hardened steel, sliding in the bronze grooves 30, at the sides of the casing.

The horizontal top and bottom portions, 33 and 3d, of the vertically moving crosshead member are provided with horizontal V-grooves spaced apart, vertically, one from the other, as clearly 7 shown in Figure 1, thereby to accommodate the horizontally sliding portion 35 of the crosshead which is also provided with similar V-shaped gibs 35 coacting with these upper and lower grooves 33 and 34 in the vertically sliding member 3 l.

The main driving shaft 23 passes through the horizontally sliding crosshead part 35 and is provided with suitable means such as a crank or eccentric 31, turning in antifriction bearing 40, of any suitable style, the outer periphery of which bearing is mounted in the horizontally sliding member or part 35. The lower portion of the horizontally sliding member is provided with a reinforcing hardened steel striking member or hammer 4| the lower portion of which is slightly wedge-shaped, as shown in Figure 9, thereby to cooperate with a similarly shaped upper portion 42 of the punch or die actuating hammer 43.

From the above it will be seen that as the main power or driving crank shaft 23 turns in its fore and aft bearings 44 and 45, under the action of the motor, the eccentric 31 turns withinthe roller bearing cage 40 and performs two functions. First, it moves the vertically sliding portion 3| of the crosshead in a straight up-and-down direction, as must necessarily follow by reason of the location, construction and position of the guides 30 on the inside of the casing frame 20, andthe movement of this vertically reciprocating portion of the crosshead has the well-known sine curve action, that is, maximum speed intermediate between accelerating and decelerating speeds and stops at the top and bottom of its stroke. Second, the horizontally sliding member 35 is also reciprocated relative to the vertically sliding portion 3| of the crosshead and this, its relative movement, is also confined to a straight line, from one side to the other of the vertically moving part 3|, under the action of the guides 33 and 34 in the vertically moving crosshead member 3| and its relative rate of movement also follows a sine curve but is degrees out of phase with that of the vertically moving part 3|. In other words, the horizontal movement accelerates and decelerates from and to complete stops at the ends of its horizontal reciprocation, when the part 3| moves fastest, but travels with maximum speed at the center of its stroke when part 3| is stopped at the ends of its stroke. While the member 35 travels horizontally with respect to part 3| it nevertheless has an actual circular movement, as it is carried by the eccentric 31 of the driving shaft 23. Thus the hammer 4| and the top or anvil of the punch 43 come into engagement just before the point of zero speed of the down stroke of the vertically moving member 3| and just as the horizontal member 35 is attaining its maximum speed. So the hammer 4| of the crosshead hits the anvil 42, Fig. 9, of the punch a quick, powerful, glancing blow while traveling at substantiallymaximum. horizontal speed and while the vertically moving crosshead 3| is substantially resting at the end of its down stroke and pressing the punch against the work. Thus the hammer blow adds a swift impact to the relatively slow crosshead pressure and all the moving parts cooperate, in acting upon the punch with the result that the punch is driven quickly and powerfully through its short, quick working stroke thereby effectively performing the desired action with little if any actual movement of the tool or punch 50 into the die As actual penetration of the punch into the die can be greatly reduced or entirely omitted, the wear life of the punch and die are very materially increased. The machine may be speeded up far beyond ordinary expectations because the motion of the inner crosshead 35 is timed and balanced with crosshead 3| and the adjustable balance wheel 26 is provided to compensate for different weight punches.

The more nearly the two main parts of the cross head 31 and 35 equal each other in weight the better the balancing effect obtained, together with a greater decrease in vibration when the machine is in operation.

Work feed With a punch operating mechanism such as above set forth it is of course necessary to provide means for feeding the work strip 52 relative to the punch 59 with proper timing and sequence to permit the desired result to be accomplished. There is therefore provided a main set of feed rollers shown at the right of Figure 1 and in detail in Figures 3 to 6 lying substantially immediately above and below the horizontal plane of the die 5| and to one side thereof and controlled in its operation largely by a solenoid 80. It is also desirable to provide a corresponding set of feed rollers at the opposite side (left of Figure 1) of the die 5! to receive the work strip 52 as it is fed between the punch and die 5! and, particularly, to eject the final end of the work strip after the first set of feed rollers has ceased to contact and function thereupon.

The feed rollers at the right of the machine, as I shown in Figure 4, comprehend an upper and a lower roller, 53 and 54, shown in sectional detail in Figure 3. The surfaces of these rollers are segmented (see Figures 5 and 6) in such a manner as to engage the work strip with a feeding action through a portion of their rotation only and at other times to leave the feed strip unengaged, during the actual punching operation. The relative length of the effective feeding segments can be easily and quickly adjusted by the mechanism shown in Figure 3, as will be more fully hereinafter described.

It is also necessary that the feeding operation of these feed rollers be synchronized with the reciprocation of the crosshead and that they move the work strip into the proper position to be worked upon by the punch, well before the crosshead reaches its lowermost position. The feeding may be done at any time when the solenoid 80 is not holding the rollers in operating position, even tho the machine is running. It is a feature of this press that feeding may be done early or late.

Referring again to Figure l, the work strip 52 while being punched, passes between the two feed rollers 53 and 56; thence towards the left over the die 5| supported on a die bolster 55, to the opposite side of the machine where it passes between feed rollers and 51. However, before the work strip '52 can be properly fed to the punch 55 it must first be inserted between the feed rollers and have its feed end contact a stop member 60 which is adjustable with relation to the punch and die position. When the machine is at rest the stop 60 has a position above that disclosed in the lower part of Figure 1, and with the part 60 in the normal horizontal path of travel of the work strip. Thus, with the work strip in this position, the rollers. 5354 are normally out of engagement, the upper roller being free to slide in vertical bearings 6|, under the action of coacting cam members 62 and 63, in the frame 64, which are brought into engagement by a relative sliding movement of a rod 65 acting against a compression spring 66 and under the action of a laterally movable and upwardly extending arm 61 of a bellcrank m. This bellcrank is pivoted at I j, at the right side of the roller bearing frame 64, while the opposite bellcrank arm 12 extends laterally to support, by links l3, a transverse rod or shaft 14 more clearly shown in Figure 4. The central part of this shaft is connected by means of a turnbuckle link 15 adjustably secured at its lower end to a laterally extending arm 15 pivotally mounted at 17, Figure 2a. The opposite end of this arm is moved by the action of the solenoid 80. Thus when the solenoid 8B is energized it exerts a downward pull through lever 76 and links 15 on the arm 12 and causes a corresponding turning of the bellcrank lever 10 and a lateral movement of the rod 65 towards the right thereby causing the engaging cams 62 and 63 to move the upper feed roller 53 downwardly into engagement with the lower feed roll 5d the top of which is level with the die 5 5.

Feed brake mechanism Before taking up the circuits and mechanisms actuating the solenoid, reference is again mad to Figure 1 showing a brake acting upon the work stock 52 for stopping the movement of the stock at the desired moment relative to the actuation of the crosshead and punch 55). Obviously this brake release must also be operated in synchronism with the up and down movement of the crosshead. There is, therefore, provided upon the horizontal member of the crosshead a roller bearing cage 8! suitably mounted upon a stud S2 and which cage is provided with an outer or surrounding member provided with a laterally extending arm 83 which telescopes within a recessed sleeve 84 the opposite end of which sleeve is provided with a pin 85 passing through a hole in a stud 88 adjustably mounted in one of several holes Bl upon the upper end of the vertical arm 953 of a bellcrank lever pivoted at 9|. Thus it will be seen that the horizontal crosshead member 35 is free to move up and down and laterally under the action of its driving eccentric 23 and at the same time maintain mechanical connection with the stud 86 on the bellcrank arm $51 and cause the arm to rock back and forth in synchronism with the reciprocations of the crosshead.

This bellcrank lever pivotally mounted upon a pin 91 in the side wall of the casing 2i] has its horizontal arm 92 extending outwardly through the side of the casing to connect loosely with the upper end of a spacer rod or link 93, the lower end of which link has loosely and adjustably secured thereto a laterally extending arm 94 of a bellcrank lever pivoted at 95, th lower nd or arm 94 of which constitutes a brake adapted to engage horizontally across the work strip 52 and press it against part 96 as clearly. shown in Figure 1. Now as the crosshead moves up and down the bellcrank levers 90 and 94' are rocked about their pivots to cause the brake 94'9B to alternately brake and drag upon the top surface of work strip to stop and again permit it to be movd, as by a pilot, and fed by the feed rolls. Such variations in engagement, of course, must take place in proper timing with the reciprocations of the punch 50. After the work strip has been stopped, part 96 relaxes its pressure and acts as a friction drag while punch 50' does its work.

On the side frame of the machine is a laterally extended support 97 for holding a slidingly adjustable member I00, as shown more clearly in Figure 1, thereby to permit the effective braking surface or distance between 94 and 96 to be adjusted according to the thickness of the work stock and die height. Suitable adjusting nuts I M are provided between the supports 91 for the bellcrank lever and the slide I whereby the parts may be securely locked in adjusted position.

Stop release As shown in Figure 1 and detailed in Figure 12, mounted upon the inner side of one of theouter end frame plates I02 for the feed rollers 5354 is a lever I03 pivoted at I04, the upper end of which lever is adapted to be engaged by an adjustable stud I depending from member 55, Fig. 4 while the lower end coacts with a pin I06 mounted upon a generally square or rectangular member I0'I mounted upon a transverse shaft I08. (Figure 1). This rectangular or square member I01 carries the feed stop.60 previously mentioned and by rotating the entire member I01 about its axis this stop member 60 is brought into and out of the path of travel of the work strip 52,

shown in out position in Figure 1. lDiagonally opposite the stop lip 60 there is provided a supporting leg H0 adapted to engage, when rotated downwardly, a base plate III thereby to limit the rotative movement of the member I01 in a clockwise direction. Its opposite relative movement is limited by means of a projection H2 adapted to coact with a push-button II 3 of a micro-switch I I4, the purpose of which will be presently explained.

There is another micro-switch H5 mounted upon a transverse support H6 in the frame of the machine, the actuating button II! of which is adapted to be engaged by an adjustable mechanical contact member H8 mounted upon the vertically reciprocating portion 3| of the crosshead. This micro-switch H5 is generally open and is closed when the contact member II8 reaches approximately its lowermost position, to complete the circuit through the starting switch controlling the solenoid 80 and, thru it, the operation of the feed rolls.

Assuming the parts to be substantially in the position shown in Figure 1, but with the stop lip 60 raised and in the path of travel of the stock 52, the latter is inserted laterally and towards the left between the spaced apart feed rollers 53 and 54 until it reaches this upwardly extending stop lip 60, whereupon its inward movement is arrested. At this time, the motor 22 has already been independently started and the main shaft 23 is being rotated through the belt drive as shown in Figure 2a. A foot pedal I (Figure 2a) is now depressed and motion is transmitted through turnbuckle I2I supported on pivoted arm I22 to throw in clutch 25 and start the reciprocation of the crosshead.

The stop lip 60 is provided with suitable adjusting means I23 where it may be moved relatively tangentially, to the right or left of the axis of the shaft I08 (Figure 12) about which it turns, thereby to accommodate the operation of the machine to the length of punchings to be made from the stock and the time at which the end of the strip 52 is to reach the punch 50 for the first operation.

I-Iaving'thus described the various parts, we may consider their combined action. With the crosshead 35 already in motion and with the stock 52 already in position between the feed rolls and against the stop 60, when it is desired to start production, the starting button I24, is pressed.

Then the next contact between H8 and H5 closes the latter micro-switch, energizes the solenoid 80, draws the feed rolls 53, 54, together, and simultaneously withdraws stop 60 from the path of the stock 52. This occurs just as the crosshead and the punch reach the bottom of the starting stroke. At this point, the brak 96 is off because point 82 has passed its extreme right hand position. Also, as stop 00 was withdrawn, part H2 closed micro-switch H4 and the circuit for continuous operation of the feed rolls, which will then continue in operation (by means described later) until the operator shall press the stop button.

It is to be noted, here, that the start button may be pressed at any time but the feed mechanism will not be started until the contact H8 closes the micro-switch H5 and this always will occur at exactly the predetermined and correct feed starting time which feature is novel and not to be found on other presses of this character.

Figure 13 is a diagrammatic view showing the relative timing of movement of the various parts and work stock during the operation of the machine and, as herein shown, the vertical line A indicates graphically the stroke of the vertically reciprocating portion 3| while the circle B indicates the travel or movement of the part 35 of the crosshead. During this movement of the two parts 3| and 35, the punching operation occurs at substantially the bottom of the circle B, or in the 15 to right of line A, i. e. the right half of arc C, and the 30 subtended by the are C indicates that portion of the stroke during which the punch operates upon and withdraws from the work stock. It is also approximately the part of the circle in which the starting takes place when the solenoid, micro-switches, feed rolls, and part 60 all function. The arc D, approximately indicates that portion of the operation during which the feed stroke may start and take place. If, for example, the feed of the work 52 is stopped at the end of 15 as at F, an additional fifty per cent more stroke is permitted within which to further feed the stock. In other words, the stock 52 may be stopped, even with a long pilot, at any point within 50 as indicated by the are E.

It will thus be seen that the present device permits the starter button to be pressed at any time or point in the cycle of the press, yet the feeding of the stock will not be started until its proper predetermined time, namely, at the beginning of the are C. Simultaneously with this, the linkage between stud 86 and the brake 96 engaging the work stock 52 at the extreme right of the machine (Figure 1) will have caused this brake to release. The movement of the solenoid 80, however, in moving the rod 05 towards the right causes the adjustable stop I05 to engage the upper end of the lever I 03 and swing the same relatively clockwise or toward the right thus causing the lower end of the'lever I03 to engage the afi al r stud and roller I56 and turn the square member ID! upon its; axis IIlB- thereby to bring the stop lip 60 downwardly out of the path of travel of the work stock and hold it there until the feed is stopped. As the square member It! assumes the position shown in Figure l the lug I I2 carried thereby engages the actuating button H3 of the micro-switch H4 thus causing a shorting out of micro-switch H5 and completing the circuit to hold the solenoid armature downwardly with'the feed rollers 53 and 54 in operative engagement until released by the stop button.

In other words, the micro-switch H5 is only used for feed starting purposes, that is, to complete the circuit after the starting button I24. is actuated, thereby to insure initial feeding of the stock 52 to the punch 50 at the proper time in the sequence of the other operations.

It is thus seen that a series of properly timed and coordinated actions occur and, while apparently instantaneous in operation, nevertheless each function has its proper place in a sequence to effect properly timed starting of the feeder. The sequence begins with pressing of the starter button and includes closing of micro-switch H5, energizing solenoid 80, a drawing together and subsequent engagement of the feeding rollers 53-54 with the stock, the release of the brake 96 and withdrawal of the stop lip 60 whereby the strip, or stock is subsequently fed toward the punch 55, intermittently until the entire strip has been acted upon and the final end discharged through the exit feed rollers 56-57.

Die bed adjustment As will, of course, be understood by those familiar with the subject, it is quite important that there be adjustment made in the relative position of the die bed 55 depending upon the thickness of the stock being worked and of the die and its supports. This will also necessitate an adjustment of the feed rollers 5354 not only as to their relative height with respect to the die bed 55 but also their separation relative to each other.

Thus it is necessary to first position the die bed 55 Figure la, by moving the same vertically up or down with respect to the end of the stroke of the die punch and in accordance with the thickness of'the stock upon such bed. This may be accomplished as follows: The lower part of the casing is provided with two inwardly extending arms I26 having vertical bores or sleeves acting as bearings for supporting rods I21. The lower ends of these rods are threaded and act as jack screws I23, as threaded sleeves I30 at their lower ends are turned. The upper ends of these rods support the die bed 55 as clearly shown in Figure la. The sleeves I31! surrounding the threaded lower portions I28 of these jacks are provided with worm wheels I3I which are adapted to be engaged by worms I32 and mounted upon adjacent ends of a transversely extending shaft I33 mounted in suitable bearings I34 in the side walls of the casing 20, One end of this shaft, preferably the left as shown in Fig ure 1a for convenience of operation, is provided with an actuating handle I35.

This gearing is suitably calibrated whereby one revolution of the operating handle I35 will raise or lower the die bed 55 a predetermined and known amount. It has been. found by experience that one-fifth of a turn of the handle to raise the die bed .002" is a convenient ratio of operation.

When the die bed55 is raised or lowered, suitable adjustment in the relative height of the feed roller frame shown in Figure 4, with respect to the die 5I- must also be made. the point of tangency of the lower roller 54 should be exactly level with the top surface of the die. This adjustment is preferably accomplished by loosening the two nuts I31 and moving them to raise or lower the lower feed roll 54 until its top surface is in horizontal alignment with the top of the die 5|. Then the nut I36 passing through a fixed portion of the frame I40, (see left hand side of Figure 1a,, the right; hand plate being provided with similar members, not shown) is loosened and the housing in whichis formed a slot MI is raised or lowered in order to bring the top roller 53 and the lower feed roller 54 into vertical alignment; the lower feed roller having been adjusted exactly to the level of the die 5!. This operation is performed on both adjustments, at the right and left sides of the casing.

A universal connection I42 in roller drive shaft I43 permits subsequent drive without binding.

A further adjustment of the feed rollers towards and fromeachother, at their point of tangency, to accommodate the thickness of the stock,

is performed by means of the adjusting nuts I44 at the right end of link or rod 65 between which nuts the upper end 61 of the bellcrank lever functions.

Another adjustment necessary is that for con-- trolling the amount of feed of the stock at each, punching operation. As previously stated, the

exterior surfaces" of the feed rollers 53-54 are segmental, (Figures 5 and 6) that is, one-half of each roller, for example, is of less radius than the other half and by rotating these feed roller surfaces relativeto each other, the segment, of larger diameter, can be positioned, to overlapthe m n o h o h r r011, b an s re amcurt, from a small fraction to the entire half-circumference.

By referring to Figure 3 it will be seen that to accomplish thislast adjustment it is only. nee.-

essary to loosen nut I56 which, thre adedly en gages the shaft I5I carrying this feed roller 53 thereby allowing a compression spring I52, acting againsta fixed collar; I53, to force a, cone I54 relatively towards the left, as, shownin this, view, whereupon, the surface of theupper feed roller.

53 may be rotated relative I10. that of the lower feed roller 54, as desired, to properly proportion.

or a just the extent of en a m nt of the. fee su faces. of a r diam t r with the sto k.

As stated these feed rollers 53 and 54 are about which a chain (not shown) passes to. a

corresponding sprocket upon the lower feed roll. er 51 at the opposite or left side of themachine shown in Figure 1.

both sets of feed rollers through the above described gears, chain I56 and. sprocket I62, in proper synchronism, when the clutch 25 is thrown in.

In other words,

Thus the power obtained from the main power shaft 23 of the press drives- V Lubricating system The various important moving parts of the press herein disclosed are preferably lubricated by means of a forced feed lubricating system such as shown in Figure 8. In the lower rear interior of the casing 20 a suitable reservoir I63 is provided' as well as a suitable pump I64, preferably driven by an independent; motor I65, thereby to provide a continuous stream of oil flowing over the various moving parts whether temporarily at rest or in rapid operation. Leading from the outgo side of pump I64 is a relatively large pipe I66 extending upwardly at the rear of the machine and thence forwardly across the top at I61 where it is provided with two branches I60I'I0 going to the opposite sides as well as towards the front of the press. The ends of these forwardly extending branches I68-II0 then pass downwardly at I III'I2 to supply respectively a plurality of smaller branche I'I3-II4 leading to the upper and lower parts of the vertical gibs 30 as well as to the upper central part of the transverse gibs 36 for the inner crosshead. By reference to Figures 10 and 11 these branch pipes terminate adjacent the groove I15 thereby to maintain the same properly lubricated at all times. The lower gibs of the horizontal crosshead 35 are preferably entirely immersed in a suitable tank or pan I'I6 Figure 8 adapted to catch the drip from the variou gibs thus insuring especially a proper lubrication of the lower guides for the horizontal slides. From this tank I16 the oil drains back through pipe I'II into the reservoir I63 in the bottom of the casing. The feed roller bearings may be independently lubricated in any desired manner.

Single operation It frequently becomes desirable under certain circumstances to perform a single punch or die operation upon a piece of metal at some particular point and the present machine is readily adaptable to such functions and operations, since it is only necessary to remove the feed rolls and plug I80 and use the foot pedal I20 to control the machine stroke by stroke.

Circuits In Figure 7 there is shown a wiring diagram, in simplified form and with parts similarly identified by reference numbers. The parts are positioned for single operation but on inserting the plug I80 the machine becomes ready for continuous high-speed. operation. Assume the plug I80 is connected, then the course of the current in the main control circuit is from L, through M to R and on to I24, normally open starting switch,

to H another normally open switch, thru I82, a normally closed stop switch, to L2.

For continuous operation, I80 is connected at R. and the micro switch H4, normally open, is mechanically linked to the solenoid 80.

As previously described, micro switch H5. is closed, by H8, (Figure 1), at the bottom of each stroke of the punch. Therefore, when the starting switch I24 is closed by the operator of the press, the main circuit is completed. Current then passing thru MC, closes switch MS and energizes the solenoid, 60, which operates to close I I4.

Then, switch I I5 is short circuited and itssubsequent repeated opening and closing does not interrupt the flow of current thru the solenoid which, therefore, keeps switch II4 closed and cffects continuous feeding of the press by the feed rolls in the manner previously described.

The new, short circuit is from LI thru MC and and MS to R and thru H4 and I82 to L2. To stop the crosshead the foot pedal I20 must be pressed to disengage the clutch 25. To stop the flywheel and clutch the main motor control switch must be opened.

The construction and operation of the complete machine is clear from the above explanation and accompanying drawings. It will be seen that the machine is of practical construction and substantially fool proof and automatic in its operation. It will operate at extremely high speed by reason of the novel construction of the actuating means and by reason of the high speed impact blow on the punch head driving the metal out of the work strip without necessitating the entry of the punch or tool into the die. Thus the life of the machine and particularly the die and punch is very materially increased. The machine is well adapted to accomplish among others, all of the objects and advantages herein set forth.

Without further analysis the foregoing will so fully reveal the gist of this invention that others can, by applying current knowledge, readily adapt it for various applications without omitting certain features that, from the standpoint of the prior art, fairly constitute essential characteristics of the generic or specific aspects of the invention, and thereforesuch adaptations should and are intended to be comprehended within the meaning and range of equivalency of the following claims.

I claim: a

1. In a high speed punch press of the character described, in combination, a punch and die, means for actuating said punch including a part traveling throughout its working stroke at speeds varying from zero to maximum and back to zero,-

means for causing the punch, when near the end of the stroke of said part, to be impacted, when already in contact with-the work, at a speed corresponding to the maximum speed attained by said part.

2. In a high speed press of the character described, in combination, a punch and die,means for actuating said punchincluding a part having working speed varying from zero to maximum and back to zero, and a member for causing the punch after first being pressed against the work by and when said part is near the end of its stroke, to be impacted, and driven through the work ata speed corresponding to the maximum speed attained by said part, said member and part moving at right angles to each other and having a sliding connection to engage the punch and convert its movement into movement at substantially right angles to the movement of the part.

3. In a high speed press of the character described, in combination, a punch and a die movable relative to each other, means for actuating said punch including a movable part having a working speed varying from zero to maximum and thence to zero, and means for causing the tool, when near the end of the stroke of said part and already pressing upon the work, to be driven through the work at a speed corresponding to the maximum speed attained by said part throughout said stroke, said last mentioned means including a second movable part reciprocating at right angles to said first movable part with its movement of highest speed being at the moment of rest of the first part. I

4. In a high speed press of the character described, the combination of a punch and a die, means for actuating said punch including two parts moving throughout their working strokes at speeds varying from zero to maximum and back to zero, for causing the punch, when near the end of the stroke of one part, to first press and then, by impact of the other part to act upon the work at a speed corresponding to the maximum speeds attained by the parts.

5. In a high speed press of the character described, the combination of a tool and a die, means for actuating said tool, including two parts moving throughout their working strokes at speeds varying from zero to maximum and back to zero, for causing the tool, when near the end of the stroke of one part and in substantial engagement with the work, to be impacted by the other part while moving at a speed corresponding to the maximum speed attained by either part throughout its stroke, said movements of the two parts being substantially at right angles, with the moment of highest speed of one being at the moment of rest of the other and being the moment of impact with the tool.

6. In a high speed punch press machine having a die and punch, in combination, means for reciprocating one of said parts, including a drive shaft, eccentric means driven thereby, and two reciprooable members one having an inclined impact surface and both relatively and simultaneously movable at substantially right angles under the action of said eccentric means, whereby one member is brought substantially to the end of the stroke movement of that member to carry the punch substantially into contact with the work at the same moment when the other reciprocating part is brought substantially to its highest speed to impact the punch and drive it through the work.

'7. A machine according to claim 6 in which the impacting surfaces are oppositely curved.

8. A machine according to claim 6 in which the head of the punch is rounded thereby better to receive the impacting blow struck by the member engaging the same.

9. A machine according to claim 6, in which the reciprocating members move one in a horizontal and the other in a vertical path.

10. A machine according to claim 6, in which,

the reciprocating part is travelling at substantially its highest speed when the other member is at substantially the end of its reciprocating movement.

11. A machine according to claim 6, in which the movement of that one of said members ending its stroke is in the direction of movement of the punch and in which the movement of the other member, causes the larger part of the actual punching.

12. A machine according to claim 6, in which the movement of that one of said members bringing the punch into engagement with the work is in the direction of movement of the punch.

13. In a high speed punch machine having a stationary die and reciprocal punch, in combination, means for reciprocating said punch including a drive shaft, eccentric means driven thereby, and two reciprocable crosshead members relatively movable at substantially right angles to each other under the action of said eccentric means, one of said members being partially carried and driven by the other member and having movements in a vertical direction, the ends of the vertical movement being at the momentsiof highest speed of. the relatively horizontally movablecarrier member which engages and actuates th penetration of the punch by impact. v

14 A machine as set forth in claim 13 in which thetop of the punch is rounded to more effectively receive the impact of the horizontally movable member.

15. A machine according to claim 13, having feeding means for moving a Work piece with respect to the punch, intermittently, said feeding means including two sets of feed rollers at'opposite sides of the punch and means for adjusting circumierentialiy the surface only of one feed roller relative to the other to any desired degree thereby to control the feed of the work strip one of said feed rollers being hollow and having a cone surface at one end and a cone member coincident with the axis of the roller to hold the roller in adjusted position.

16. In a high speed press machine, in combina tion, a punch and die, means for actuating said punch including a two part crosshead, each of the parts of which is reciprocated in a relatively diiTerent direction and phase whereby one brings the punch substantially into contact with the work in time "to enable the other crosshead part to actuate the punch, by impact, at the moment of the latter parts highest speed.

17; A machine according to claim 16 in which the contacting surfaces of said crosshead part and punch are curved towards each other to emphasize the impact.

18. A machine according to claim 16 including a control circuit, and means for converting the machine from continuous to single operation and vice versa as desired.

19. A machine according to claim 16, including means for feeding a work strip to the punch, means for braking and releasing the work feed, and means for determining the moment of release with respect to the position of the punch.

20. A machine according to claim 16 including of different radii coacting to efiect intermittent feed and means for adjusting the surfaces of one radius on one roller with respect to the surfaces of the other roller to regulate the extent of feed to any desired degree, one of said rollers being hollow and having a cone surface at one end and a cone member coincident with the axis of the roller to hold the roller in adjusted position.

21. A machine according to claim 16 including a pair of feed rollers one of which is hollow, means for circumferentially adjusting said hollow roller with respect to the other and means for positively setting and holding said hollow roller in position with respect to the other said last means including a cone surface at one end of said hollow roller and a cone member coincident with the axis of the roller adapted to hold the roller in adjusted position.

22. A machine according to claim 16 including a work stock feed brake, and means connecting one of the parts of the crosshead with the brake to release said brake with respect to the movement of said part.

23. A machine according to claim 16 including a work stock feed brake, and means connecting one of the parts of the crosshead with the brake to release said brake with respect to the movement of said part, and means for adjusting the time of release.

24. In a high speed machine of the character described, in combination, a tool and die, means for actuating said tool including a part traveling throughout its working stroke at speeds varying from zero to maximum and thence to zero to bring the tool substantially into contact with the work, reciprocating means for causing the tool, when near the end of the stroke of said first means, to be driven through the work by impact at a speed corresponding to the maximum speed attained by said means throughout its stroke, said last-mentioned means traveling at substantially right angles to said first-mentioned means and the movement of the tool.

25. A machine according to claim 24 including a means for positioning the machine stock at the beginning of the operation with relation to the movement of the tool whereby on release the work stock will be fed to the tool and give a perfect blank at the end of the first work stroke.

26. A machine according to claim 25 including a means for positioning the work strip at the beginning of the operation with relation to the movement of the tool, a motor drive and circuit with contacts in which the contacts are closed as a work strip is fed into engagement with the contact to start the motor and insure a perfect blank on the first complete down stroke of the tool.

27. In a high speed press of the character described, in combination a vertically moving punch, a horizontally reciprocating crosshead having an inclined part to impact the punch, a motor for the press, a control circuit, a pair of feed rollers having segmental surfaces of different radii coactnig to effect intermittent feed, and means for adjusting the surfaces of one radius on one roller with respect to the surface of the other roller to regulate the extent-of feed to any desired degree.

28. In a high speed press of the character described, in combination a vertically moving punch, a horizontally reciprocating crosshead having an inclined part to impact the punch, a motor for the press, a control circuit, a pair of feed rollers having segmental surfaces of dilferent radii, means for adjusting surfaces of one radius with respect to the other to regulate the extent of feed, means for supporting the die, and means for adjusting the die towards and from the punch, said last mentioned means including an operating handle one revolution of which is known to move the die support a predetermined known amount.

29. In a high speed press of the character described, in combination a punch, a reciprocating crosshead to impact the punch while moving at its highest speed and in a direction at substantially right angles to the movement of the punch, a motor for the press, a control circuit, a work strip, a feed brake, and means connecting one of the parts of the crosshead with the brake to release said brake with respect to the movement of said part.

30. In a high speed press of the character described, in combination a punch, a reciprocating crosshead to impact the punch while moving at its highest speed and in a direction at substantially right angles to the movement of the punch, a motor for the press, a control circuit, a work strip, a feed brake, and means connecting one of the parts of the crosshead with the brake to release said brake with respect to the movement of said part, and means for adjusting the time of release.

GEORGE B. SCHEFFEY.

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