US3353417A - High speed double blow header - Google Patents

Description

Nov. 21, 1967 NEBENDORF ET AL HIGH SPEED DOUBLE BLOW HEADER 4 Shee ts-Sheet 1 Filed March 29, 1965 ,'I,\ u n 1,1111% 'IIIIIIIIIIII/ IZ-INVENTOR: W 16i; I

H. NEBENDORF ET AL 3,353,417

HIGH SPEED DOUBLE BLOW HEADER Nov. 21, 1967 4 Sheets-Sheet 2 Filed March 29, 1965 INVENTORS Nov. 21, 1967 H. NEBENDORF ET AL 3,353,417

HIGH SPEED DOUBLE BLOW HE'ADER 4 Sheets-Sheet '5 Filed March 29, 1965 INVENTORS Nov. 21, 1967 H- NE BENDORF ET AL 3,353,411

HIGH SPEED DOUBLE BLOW HEADER Filed March 29, 1965 4 Sheets-Sheet 4 INVENTORS Z United States Patent Ofitice 3,353,417 Patented Nov. 21, 1967 many Filed Mar. 29, 1965, Ser. No. 443,385 Claims priority, applicatgtgnggsermany, Oct. 8, 1964,

2 Claims. (2174-53 The present invention relates to high speed double blow headers. Double blow headers are known which have a bed frame disclosed in Patent No. 3,031,698. The bed frame carries a reciprocating header slide, or gate, driven by a crank-shaft on the frame, which gate carries a shiftable punch carrier operated at half crankshaft speed, so that on one advance stroke of the gate a first punch or tool engages a blank held by transfer fingers in alignment with a die, pushes the blank into the die and upsets the blank, and on the next advance stroke the punch carrier has shifted and so presents a second punch or tool to the work now recessed in the same die. After the second blow the blank is ejected from the die and the transfer fingers bring a new blank into a projected position in front of the die.

In these headers, the main or driving crankshaft turns continuously, as does the half speed cam shaft. This means that the gate, carrying the punches or tools is ever moving except at the very end of its stroke. The punch carrier, however, must remain motionless relative to the gate during the final portion of each advance stroke of the gate, while a punch is upsetting a blank in the die. The problem is one of moving the punch carrier mounted on the gate so as to shift the carrier between its two alternative positions at the correct time, and of positively maintaining the carrier in its operating position during the final portion of each advance stroke of the gate.

Reliance on a combination of positive stops for the punch carrier coupled with spring over-travel accommodation devices is unsatisfactory, particularly at high speed operation, because of flutter, bounce, pounding and general unreliability or inconsistency in operation. All of these occurrences can result in misalignment of the punches or tools with the work or die, and thus break or injure expensive tool parts.

The speed of operation of the machine, and the durability of the parts in service, also depend upon the necessary rates of acceleration and deceleration, and upon the mass of the parts which must be so accelerated and decelerated, since excessive loads on the driving and bearing parts cause excessive wear or breakage, and also interfere with the desired accuracy of timing and positioning, because of compression and stretch of the parts.

Accuracy is combined with maximum speed of operation in a double blow header by mounting on the reciprocating slide or gate a shiftable punch carrier, and an oscillating, positive motion cam means for shifting the carrier while controlling its acceleration and deceleration, and yet positively holding the carrier in its two operating positions. The cam means is oscillated by connections driven by the crankshaft, and the motion imparted to such connections by the reciprocation of the gate relative to the frame is accommodated by relatively small movement of the cam means on the gate in either direction, without corresponding movement of the punch carrier after it has moved the cam means on the gate to either of its two operating positions. In this manner the critical part of the movement of each of the parts on the gate is minimized, thereby minimizing the necessary rate of acceleration and deceleration and permitting the punch carrier to be moved to, and positively held in, each of its operating positions with maximum speed of operation followed by accuracy of positioning. This arrangement also minimizes the mass of the parts which must be carried on the reciprocating gate, thereby further contributing to speed and reliability of operation.

The positive motion cam means carried by the reciprocating gate is oscillated by a second positive motion cam means on the frame, the latter cam means being driven by a continuously rotating half speed shaft geared to the crankshaft. This arrangement takes advantage of all of the advantages of the oscillating positive motion cam means carried on the gate and, at the same time, permits the second cam means on the frame to be contoured to give the optimum rate of acceleration and deceleration in each direction. It is necessary for the first punch to be shifted into, and held in alignment with, the die at a point substantially before the end of the first stroke of the gate so that the punch may engage a new blank held in transfer fingers, push the blank down into the die and finally upset the projecting end of the blank. However, the shifting movement to bring the second punch into alignment with the die can start at a point wherein the gate is much closer to the face of the die and such shifting motion can continue through the remainder of the first retracting stroke and the greater portion of the second advancing stroke, since the blank now remains seated and retracted in the die. Similarly, the carrier can start the shifting movement to bring the firts punch back into alignment with the die at a point very close to the face of the die after the second blow but must complete this shifting movement at a point wherein the gate is spaced much farther back from the die on the next advance stroke so as to allow the necessary travel to push the next new blank into the die. Any extra dwell of either punch which may be required by a long punch or by a knock-out operation working on a long blank, in either the first or the second punch can be accommodated, all while maintaining optimum rates of acceleration and deceleration at all other points in the cycle.

The motion of the cam means on the frame is transmitted to the oscillating cam means on the reciprocating gate by a connecting rod having ball and socket or universal joint connections permitting the reciprocation of the gate during the transmission of the oscillating motion between the two cam means. The use of a connecting rod for coupling the two cam means eliminates sliding connections between the parts. Such sliding connections are subject to inaccuracy from manufacturing tolerances and wear, and also from springing or yielding underacceleration and deceleration loads.

It is one object of the present invention to provide a high speed double blow header, wherein very precise end positions of the first and second punches or tools, determined by cams, are obtained forcibly and play-free without any particular abutments, to reduce thereby the reciprocating masses, in order to obtain an appreciable increase of the number of revolutions of the shaft, to avoid wear and to obtain, nevertheless, advantageous extended resting periods during the blow header operation.

It is another object of the present invention to provide a high speed double blow header, wherein the axle of the shiftable punch carrier is operated by means of a directly forced cam drive.

It is still another object of the present invention to provide a high speed double blow header, wherein the swinging axle of the pair of angular arms carrying follower-rollers constitutes simultaneously the swinging axis of the shiftable punch carrier formed as swinging wing.

By this arrangement a precise transmission of the cam strokes is transmitted directly to the shiftable punch carrier, without loss and free of error. The transmission of the driving rotary forces is thereby favorable and reliable as well as easily obtained in exact synchronism. No wear occurs during long time operation, and thus an adjustment is intentionally omitted. The exact forced operation makes possible in an advantageous manner, during the press operation longer resting periods for the purpose of an equalized forming of the work piece.

In order to advantageously leave the shiftable punch carrier in one end position appreciably longer than in the other end position, cams are required which are disposed symmetrically. A forced roller guide is obtained, in accordance with the present invention, such, that the paths of the cams disposed in adjacent planes are formed of the same size, as well as set off relative to each other in relation to a symmetry plane with its equally formed control profiles, so that the follower-roller sitting on the angular pair of arms is engaged at each point of the cam position free of play.

A simple structure of reliable operation is obtained, in accordance with the present invention, such, that the cams coordinated to the pair of angular arms sit on a profiled shaft, which is driven by means of a pair of bevelled gears immovably mounted on the machine frame, and one of the bevelled gears is mounted displaceably on the profile key shaft.

The same arrangement lends itself also for a linearly moveable punch or tool carrier, without causing disadvantageous effects. In accordance with the present invention, for this purpose, a slide-like guided tool carrier is pivotally connected with one of the arms by means of a slide mounted in the punch or tool carrier.

With these and other objects in view, which will become apparent in the following detailed description, the present invention will be clearly understood in connection with the accompanying drawings, in which:

FIG. 1 is a longitudinal section of the device designed in accordance with the present invention with the swinging tool carrier;

FIG. 2 is an end view of the control drive seen in the direction of the arrow X of FIG. 1;

FIG. 3 is an elevation of one of the cams;

FIG. 4 is a perspective front elevation of the drive shownin FIG. 2;

FIG. 5 is a longitudinal section of the device with a slide-like displaceable tool carrier;

FIG. 6 is an elevation of the control drive seen in the direction of the arrow Y of FIG. 5; and

FIG. 7 is a perspective view of the control drive disclosed in FIG. 6.

Referring now to the drawings, and in particular to the embodiment disclosed in FIGS. 1-4, a press slide 1 is guided in a machine frame (not shown), which press slide 1 is driven to perform a reciprocating movement by a connecting rod 2, substantially as disclosed in Patent No. 1,918,910 to Hilgeland.

A punch or tool carrier 3, reciprocating within the cycle is mounted crosswise at the end face of the press slide 1, which tool carrier 3 carries the tools and dies 4 and 5.

Thus the punch transfer mechanism comprises a bevel gear 16 on the half-speed, or secondary shaft 16 driving a mating bevel gear on the hollow shaft 15 which rotates. In the hollow shaft 15' is mounted a female spline. A second shaft 14 aligned with the hollow shaft 15 is carried in bearings on the slide 1 of the header. At one end of the shaft 14, a male spline engages the aforementioned female spline. At the other end of the shaft 14 are mounted a pair of complementary earns 11 and 12 which are keyed to and driven by the shaft 14. The cams 11 and 12 provide motion to the punch carrier plate 3 and to substantially define the end points of its travel. The cam shaft 14 makes one complete turn in the exact same time interval required for the header slide on which it is mounted to make two complete reciprocating strokes.

The tool carrier 3 is swingably mounted with an axle 6. A pair of angular arms is keyed to the axle 6, the arms 7 and 8 of the pair being disposed in opposite directions and in series relative to the longitudinal direction of the swinging axle 6 in adjacent planes. They consitiute a double lever operating like a seesaw.

Each of the arms 7 and 8 is equipped at its end with cam- follower rollers 9 and 10, respectively. The swinging axle 6 of the angular pair of arms 8 and 9 carrying the cam- follower rollers 9 and 10 is simultaneously the swinging axis of the tool carrier 3 on which the tools 4 and 5 are mounted. The roller 10 engages a cam 11, while the roller 9 engages a second cam 12.

The two cams 11 and 12 cooperating with the rollers 9 and 10 are disposed in parallel planes and are mounted on a common hub 13, which is keyed to the shaft 14 mounted below the press slide 1.

The shaft 14 is driven by means of bevelled gears 15 and 16 mounted for rotation in a machine frame (not shown). The earns 11 and 12 are set off relative to each other, so that upon reaching the highest point of the cam 11 by the roller 10, the roller 9 has reached about the lowermost point of the cam 12.

By this arrangement a completely forced and tolerancefree engagement of the rollers 9 and 10 on the cams 11 and 12 is brought about, and whereby a satisfactory end position of the tool carrier 3 is obtained.

Referring now again to the drawings, and in particular to FIGS. 57, which disclose a second embodiment of the present invention, a tool carrier 17 guided along a straight line slide-like in the press slide 1 is provided, which tool carrier 17 carries the tools 4' and 5'.

Here again a swinging axle 6 is provided similarly to the arrangement in the first embodiment and forms the swinging axis for the arms, the arms 7' and 8 are keyed in series arrangement in the same manner as disclosed in connection with the first embodiment. The arms 7 and 8' are equipped again with rollers 9 and 10'. The roller 9' engages a cam 12 and the roller 10' engages a cam 11'. Both earns 11' and 12' are keyed to a common hub 13', which is keyed to the profiled splined shaft 14' in the same manner as disclosed in connection with the first described embodiment.

Contrary to the embodiment disclosed in FIGS. 1-4, the arm 7' is, however, pivotally conected with the longitudinally displaceable tool carrier 17, and in particular by means of a pin 19 which is mounted on a slide 19' guided in a slot 18 of the tool carrier 17. The pin 19 is pivotally connected with the arm 7'.

Thus, in the second embodiment two earns 11' and 12' are again provided which are disposed in series and each of which engages a roller 9 and 10', respectively, which are rotatably mounted on the arms 7' and 8' swingable about the swinging axle 6.

For assuring the end positions of the tool carrier 17, a locking device 20 is also provided in both embodiments of the present invention, which locking device slidingly locks the tool carrier 3.

While we have disclosed two embodiments of the present invention, it is to be understood that these embodiments are given by example only and not in a limiting sense, the scope of the present invention being determined by the objects and the claims.

We claim:

1. In a header,

a press slide mounted for reciprocating movement,

a punch carrier,

means mounting said punch carrier on said press slide for angular oscillating motion between two alternative work positions,

first cam means rotatably mounted on said press slide and having lift portions and dwell portions,

a first follower on said punch carrier and constantly in engagement with said first cam means,

second cam means rotatably mounted on said press I slide and having lift portions and dwell portions,

a second follower on said punch carrier and constantly in engagement with said second cam means,

a shaft rotatably mounted below said press slide and rotating in timed relation to the reciprocation of said press slide,

said first cam means and said second cam means continuously rotated by said shaft and shifting said punch carrier during their rotation between said two alternative work positions by direct engagement with said first and second followers, respectively,

an axle fixed to said punch carrier,

said followers comprising oppositely disposed arms secured to said axle,

each of said arms carrying a follower roller, and

said first and second cam means rotating in parallel planes perpendicularly to the axis of said shaft and spaced apart at a distance equal to the distance of said arms along the axis of said shaft.

2. In a header,

a press slide mounted for reciprocating movement,

a punch carrier,

means mounting said punch carrier on said press slide for linear reciprocating movement between two alternative work positions,

first cam means rotatably mounted on said press slide and having lift portions and dwell portions,

a first follower on said punch carrier and constantly in engagement with said first cam means,

second cam means mounted on said press slide and having lift portions and dwell portions,

a second follower on said punch carrier and constantly in engagement with said second cam means,

a shaft rotatably mounted below said press slide and rotating in timed relation to the reciprocation of said press slide,

said first cam means and said second cam means continuously rotated by said shaft and reciprocating said punch carrier during their rotation between said two alternative work positions by direct engagement with said first and second followers, respective,

an axle pivotally mounted in said press slide,

said followers comprising oppositely disposed arms secured to said axle,

each of said arms carrying a follower roller,

said first and second cam means rotating in parallel planes perpendicular to the axis of said shaft and spaced apart at a distance equal to the distance of said arms along the axis of said shaft,

said punch carrier having a slot,

a slide guided in said slot for lateral movement in said punch carrier, and

a pin pivotally connected with said slide and pivotally connected with one of said arms.

References Cited UNITED STATES PATENTS 651,828 6/1900 Copland 74-54 1,918,910 7/ 1933 Hilgeland. 2,427,395 9/ 1947 Kellogg 7454 X 2,599,053 6/1952 Friedman 1012.5 2,830,456 4/ 1958 Stafford 74--53 MILTON KAUFMAN, Primary Examiner.

D. H. THIEL, Assistant Examiner.

Claims (1)

1. 2. IN A HEADER; A PRESS SLIDE MOUNTED FOR RECIPROCATING MOVEMENT, A PUNCH CARRIER, MEANS MOUNTING SAID PUNCH CARRIER ON SAID PRESS SLIDE FOR LINEAR RECIPROCATING MOVEMENT BETWEEN TWO ALTERNATIVE WORK POSITIONS, FIRST CAM MEANS ROTATABLY MOUNTED ON SAID PRESS SLIDE AND HAVING LIFT PORTIONS AND DWELL PORTIONS, A FIRST FOLLOWER ON SAID PUNCH CARRIER AND CONSTANTLY IN ENGAGEMENT WITH SAID FIRST CAM MEANS, SECOND CAM MEANS MOUNTED ON SAID PRESS SLIDE AND HAVING LIFT PORTIONS AND DWELL PORTIONS, A SECOND FOLLOWER ON SAID PUNCH CARRIER AND CONSTANTLY IN ENGAGEMENT WITH SAID SECOND CAM MEANS, A SHAFT ROTATABLY MOUNTED BELOW SAID PRESS SLIDE AND ROTATING IN TIMED RELATION TO THE RECIPROCATION OF SAID PRESS SLIDE, SAID FIRST CAM MEANS AND SAID SECOND CAM MEANS CONTINOUSLY ROTATED BY SAID SHAFT AND RECIPROCATING SAID PUNCH CARRIER DURING THEIR ROTATION BETWEEN SAID TWO ALTERNATIVE WORK POSITIONS BY DIRECT ENGAGEMENT WITH SAID FIRST AND SECOND FOLLOWERS, RESPECTIVE, AN AXLE PIVOTALLY MOUNTED IN SAID PRESS SLIDE, SAID FOLLOWERS COMPRISING OPPOSITELY DISPOSED ARMS SECURED TO SAID AXLE, EACH OF SAID ARMS CARRYING A FOLLOWER ROLLER, SAID FIRST AND SECOND CAM MEANS ROTATING IN PARALLEL PLANES PERPENDICULAR TO THE AXIS OF SAID SHAFT AND SPACED APART AT A DISTANCE EQUAL TO THE DISTANCE OF SAID ARMS ALONG THE AXIS OF SAID SHAFT,

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