US3126150A

US3126150A - Punch cams

Info

Publication number: US3126150A
Authority: US
Priority date: 1961-12-20
Publication date: 1964-03-24
Anticipated expiration: 1981-03-24

Description

March 1964 G. E. LYONS ETAL HIGH-SPEED PUNCHING MECHANISM Filed Dec. 20, 1961 FIG. 20

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INTERPOSER 13 INTERPOSER 14 PUNCH CAMS 2&5 &PUNCH DRIVE PLATE8 PUNCH CAMS 3&4 &PUNCH DRIVE PLATE9 PUNCH RESTORE CAMS PUNCH RESTORE BAIL? ACFNT United States Patent 3,126,150 HIGH-SJIEED PUNCHING MECHANISM George E. Lyons, Hyde Park, and Raymond A. Barbeau,

Poughkeepsie, N.Y., assignors to International Business Machines Corporation, New York, N.Y., a corporation of New York Filed Dec. 20, 1961, Ser. No. 160,778 Claims. (Cl. 234-115) This invention relates to punching mechanisms and, more particularly, to very high-speed punching mechanisms.

With the ever increasing speed of modern data processing systems, the problems of converting output data to a usable form are becoming more and more acute. Particularly troublesome is the great disparity in speed between the electronic data outputs and the mechanical devices which transform these data outputs to physical manifestations on record members.

In the conversion of electronically derived information to punched tape or cards, the limiting factor is often the s eed of the punch mechanism. Generally, in the prior art, mechanical punches have operated on the principle of driving each punch through a complex linkage from a driving means. In such a mechanism, the entire linkage connected to an individual punch executes one complete cycle for each actuation of the punch; thus, limiting the speed of the punch to the rate at which the entire linkage is driven and restored. This principle of operation has proven satisfactory so long as the punches were allowed to operate at moderate speeds. For example, certain paper tape and card perforating devices of the prior art have operated in the range of to 60 cycles or punches per second. This operating range permitted the use of spring restoring elements and conventional bearings. However, when attempts were made to operate these punches at the desired higher rates of speed, neither the spring restoration elements nor the hearings were able to withstand prolonged use. Moreover, at these high speeds, harmonic vibrations were encountered in the spring restoration elements which made their use impractical. Noisy operation was another undesirable aspect which resulted from this mode of operation.

The present invention is primarily intended for use in high speed tape preparation devices which may operate at speeds of 300 cycles per second or higher. The principle of operation disclosed, however, is equally applicable to slow speed devices.

The principal object of the invention is, therefore, to provide a punching mechanism that is capable of operation at extremely high speeds.

An additional object is to provide a punching mechanism capable of the high speed referred to, characterized by a linear positive drive of the punch on both the punching and restoring strokes.

A further object of the invention is to provide extremely simple actuating and restoring mechanisms for the punches.

Another object of the invention is to provide a punching mechanism that operates with a minimum amount of noise.

Another object of the invention is to eliminate the problem of harmonic vibrations that is sometimes encountered in punching mechanisms.

In accordance with the foregoing objects this invention provides a pair of punch drive plates driven by a cam shaft, a punch restore bail also driven by the cam shaft, a plurality of punches, and a dual set of interposers, each of which is selectively insertable between chosen ones of the punches and the punch drive plates. Each punch drive plate is actuated once during a single revolution of the cam shaft thereby actuating any punches under which ice interposers have been inserted. After each actuation the punches are positively restored by the action of the punch restore bail. Thus, the punches may be actuated at double the frequency of the cam shaft without the attendant disadvantages of the use of complex mechanisms.

The foregoing and other objects, featuresand advantages of the invention will be apparent from the following more particular description of a preferred embodiment of the invention, as illustrated in the accompanying drawmgs.

In the drawings:

FIG. 1 is a perspective view of the punching mechanism with a portion of the punch restore bail broken away.

FIG. 2a is a sectional end view of the punching mechanism shown in FIG. 1 and taken along the line 2a2a.

FIG. 2b and 2c are partial sectional views of FIG. 2a at different times in a punch cycle.

FIG. 3 is a timing chart which shows the relative movements of the major elements employed in the punching mechanism.

Referring now to FIG. 1 of the accompanying drawing, the punching mechanism is provided with a shaft 1 which is coupled to any suitable driving means, such as a motor, and is driven at high speed, for example, r.p.m. Mounted rigidly on shaft 1 are

single lobe cams

2, 3, 4, and 5 and double-lobe cam 6.

Cams

2 and 5 are aligned as are

cams

3 and 4 but the aligned high lobes of

cams

2 and 5 are displaced by from the aligned high lobes of

cams

3 and 4. A punch dn've plate 9 is upwardly disposed from and rides on

cams

3 and 4; a punch drive plate 8 is similarly disposed with respect to

cams

2 and 5. For each 180 of rotation of cam shaft 1, one of the punch drive plates is moved upwardly by its associated cam drivers. In one complete revolution of shaft 1, both

drive plates

8 and 9 receive successive actuations.

A punch restore bail 7 encircles the complete punch mechanism and in addition to other functions, acts as a frame therefor. Shaft 1 extends through a pair of elongated holes 30 (only one is shown) in punch restore bail 7. Since shaft 1 is positionally fixed, its relationship with holes 30 acts to constrain the bail 7 to linear up and down travel. Both

punch drive plates

8 and 9 extend at either extremity through rectangular slots 17 (only one shown) in restore bail 7. Slots 17 act to constrain the travel of punch drive plates 55 and 9 to linear up and down motion. As either

punch drive plate

8 or 9 is driven upwardly by its respective cam drivers, the portion thereof which extends through slots 17 contacts the upper extremities of the slots and impels the entire restore bail 7 in an upward direction.

Projecting through the upper comb-like portion 18 of punch restore bail 7 and stripper plate 20 (shown in FIG. 2a) are a plurality of punches 15 having enlarged bases 16 and upper cutting surfaces 12. An oppositely disposed pair of

interposers

13 and 14 support the base 16 of each punch 15 when the punches are in their nonpunch or home position. Although only two sets of interposers are shown in FIG. 1, it should be understood that each punch has associated therewith an identical pair of opositely disposed interposers.

Punch drive plates

8 and 9 provide the driving force to move the punches 15 from their home position to a punch position; however, a selected punch will not be propelled upwardly unless one of its

interposers

13 or 14 is inserted over the actuated punch drive plate.

In their withdrawn position (FIG. 2a)

interposers

13 and 14 are supported by

rest plates

10 and 11. The exterior mountings for

rest plates

10 and 11 have been omitted to simplify the drawings. Both

rest plates

10 and 11 remain stationary throughout the complete oper- :2 ation of the punch mechanism. Also, at no time are the interposers completely withdrawn from beneath the bases 16 of punches 15.

Each interposer is separately inserted and withdrawn by an actuating means. Any well known variety may be used, but for illustrative purposes, one such actuating means is shown in FIG. 2a. When interposer 14 is in the withdrawn position, electromagnet 24 is energized and electromagnet 22 is die-energized. When the insertion of interposer 14 is desired, energization is switched from electromagnet 24 to electromagnet 22. Electromagnet 22 thereby attracts arm 23 which pivots about pin 25 and inserts interposer 14 over drive plate 9. One such actuating means is provided for each interposer.

Punches which are to be actuated by punch drive plate -9 have their corresponding interposers 14 placed in position over drive plate 9 while it is in its unactuated or down position. Likewise, punches which are to be actuated by punch drive plate 8 have their interposers inserted while it is in its down position. In this manner, as the interposers inserted on the previous punch cycle are operated by one-punch drive plate, the interposers for the punches to be actuated during the next punch cycle are being inserted over the other punch drive plate. As either punch drive plate is upwardly actuated by its respective cam drivers, any interposers in place over the plate are caused to travel in an upward direction, this motion also being imparted to the corresponding punches. When the actuated drive plate reaches the limit of its upward travel, the cutting surfaces 12 of the selected punches extend into the orifice in die 21 thereby resulting in the perforation of any record member which may pass between die 21 and stripper plate 20.

With reference now back to FIG. 1, each high lobe of cam 6 is displaced 90 from the high lobes of cams 2-5 and 34 respectively. In addition, the exterior curvature of cam 6 is complementary to the combined curvatures of cams 25 and 3-4. Associated with cam 6 is an upwardly disposed follower section 19 of punch restore bail 7. As previously stated, punch restore bail 7 is actuated upwardly by the interaction of the

punch drive plates

8 or 9 and the upper portions of slots 17. Punch restore bail 7 is so constructed that during its upward actuation, its follower portion 19 is firmly held against cam 6. As soon as the high lobes of the pair of positive driving cams begin to retreat from their uppermost position, cam 6, because of its complementary curvature, positively pushes follower portion 19 in a downward direction. This achieves a threefold purpose: The upper portions of slots 17 push down on and thereby act to restore the actuated punch drive plate; during the restorative action, the particular punch drive plate being restored is firmly held against its driving cams; and any punches actuated by the drive plate are withdrawn from the record member nad returned to their home position by the downward force exerted on their base portions 16 by the teeth of comb-like section 18 of restore bail 7.

The result of this operation is that there is a positive driving cam both during the actuation and restoration of the punches and punch drive plates. This configuration prevents excessive noise, provides a positive driving and restoration force for both the punches and the punch drive plates, and eliminates the need for spring biasing.

Referring now to FIGS. 2a, 2b, 2c and 3, a complete cycle of operation of the punching mechanism will be described. FIG. 3 is a timing chart which shows a single cycle of operation of cam shaft 1. The base line of each of the separate cam curves is assumed to be the low dwell of the

punch cams

2 and 5. In the particular example shown, punch 15 isactuated twice during the cycle along with its

respective interposers

13 and 14. It should be recognized, however, that this is merely exemplary and that either one or the other or neither of the interposers, could be actuated, depending upon the desired perforation of the record member. Moreover, although the operation of only one of the punches is described, the other punches in the mechanism are actuated in a similar manner, according to the data to be perforated.

Initially, or at 0 (FIGS. 2a and 3), it is assumed that the high lobes of

cams

2 and 5 are at their extreme upward position and that interposer 13 was not inserted during the last half of the previous cycle. Thus, though punch drive plate 8 is actuated, punch base 16 remains resting on

interposers

13 and 14 and cutting portion 12 is not extended. The high lobes of

cams

3 and 4 are at their extreme downward position. Since punch 15 is to be actuated twice during this cycle, interposer 14 must next be inserted between punch drive plate 9 and punch base 16. This is accomplished during the interval t which is the time during which punch

cams

3 and 4 are at their low dwell and punch drive plate 9 is in its unactuated position. The insertion of interposer 14 is accomplished by switching energization from electromagnet 24 to electromagnet 22 thereby resulting in an attraction of arm 23 to electromagnet 22. As arm 22 pivots about point 25, interposer 14 is inserted over punch drive plate 9.

As the high lobes of

cams

2 and 5 continue to rotate, they cease being the positive driving power within the mechanism and a high lobe of punch restore cam 6 assumes control. The interaction of follower portion 19 of punch restore bail 7 with the controlling high lobe of cam 6 forces the restore bail 7 downward causing the restoration of previously actuated punch drive plate 8 and any punches (other than punch 15) which were actuated during the previous half cycle. When the controlling high lobe of cam 6 reaches its lowermost orientation, the punch mechanism is fully restored with all punches and drive plates in their unactuated positions.

Shortly, after the restoration of the punch mechanism,

punch cams

3 and 4 acting upon punch drive plate 9 assume positive driving control. Because interposer 14 is now in position over punch drive plate 9, it, as well as punch 15 and punch restore bail 7, is carried upward as plate 9 is actuated by

cams

3 and 4. When the high lobes of

cams

3 and 4 reach their uppermost orientation (FIG. 2b) at cutter portion 12 of punch 15 extends into the orifice in die 21, thereby perforating any record member between stripper plate 20 and die 21.

During interval t which is when

cams

2 and 5 are at low dwell and drive plate 8 is unactuated, interposer 13 is inserted between punch drive plate 8 and punch base 16. This is accomplished in a similar manner and with a similar mechanism (not shown) to that utilized for interposer 14.

Shortly after punch 15 perforates the record member, the positive driving force Within the mechanism again switches and a high lobe of cam 6 assumes control from

punch cams

3 and 4. This action results in a complete restoration of the punch mechanism to its non-punch state as previously described. At any time after the punch has perforated the record member, interposer 14 may either be withdrawn or left in place dependent upon the desired punching scheme in the next punch cycle.

After the restoration of the mechanism by punch restore cam 6 and punch restore bail 7,

punch cams

2 and 5 assume positive driving control of the mechanism and cause the actuation of punch 15 through the upward movement of punch drive plate 8 and interposer 13 (FIG. 20). This completes a single revolution of cam shaft 1.

In this preferred embodiment, the timing of the insertion of the interposers has been described with respect to punch operation at less than maximum speeds. If maximum speed operation is desired, the amount of time available for insertion of the interposers can be increased by energizing the insertion electromagnet as soon as the punch drive plate has begun to rise on the cycle just previous to that in which interposer insertion thereover is desired. In this manner, the interposer will be blocked by the drive plate until it returns to its unactuated position. The interposer then slides in over the drive plate and under the punch and is fully inserted.

While the invention has been particularly shown and described with reference to a preferred embodiment thereof, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention.

We claim:

1. A punch mechanism comprising:

a set of punches movable between punch and nonpunch positions;

a pair of single element multiple punch drivers, slidably disposed to move between punch and non-punch positions each driver being capable of moving all of said punches;

multilobe cyclic cam means for alternatively reciprocating said drivers during a single cycle;

and a plurality of interposer means insertable between chosen ones of the punches of said set and said moved one of said drivers to transmit said driver movement to said chosen punches causin said chosen punches to be extended to the punch position.

2. The invention set forth in claim 1 further comprising means actuated by said cam means for restoring said chosen punches to the non-punch position after each driver movement.

3. A cyclic punch mechanism comprising:

a pair of single element multiple punch drivers slidably disposed to move between punch and non-punch positions;

cyclic cam means for actuating said drivers successively in a cycle to the punch position;

a plurality of punches;

a plurality of first interposer means adapted to be inserted during a first portion of said cycle between chosen ones of said punches and one of said drivers to transmit the movement of said one driver to said chosen punches;

a plurality of second interposer means adapted to be inserted during a second portion of said cycle between chosen ones of said punches and the other driver to transmit the movement of said other driver to said chosen punches;

and restoring means driven by said cam means for moving said chosen punches and the actuated driver to the non-punch position after each portion of said cycle.

4. A cyclic punch mechanism comprising:

a pair of single element multiple punch drivers linearly movable between punch and non-punch positions;

cyclic cam means for actuating each of said drivers successively in a cycle to the punch position;

a plurality of punches;

a plurality of first interposer means adapted to be inserted during a first portion of said cycle between and in engagement with chosen ones of said punches and one of said drivers to transmit the movement of said one driver to said chosen punches;

a plurality of second interposer means adapted to be inserted during a second portion of said cycle between and in engagement with chosen ones of said punches and the other driver to transmit the movement of said other driver to said chosen punches;

and restoring means linearly driven by said cam means for moving said chosen punches and the actuated driver to the non-punch position after each portion of said cycle.

5. In a high speed punching mechanism:

a cyclically rotatable shaft;

first and second cam means mounted on said shaft;

a pair of movable punch drive plates displaced succes sively from a non-punch position to a punch position by said first cam means during a cycle of said shaft;

a plurality of movable punches;

a plurality of interposers positionable between said drive plates and selected ones of said punches to transmit drive plate displacement to said selected punches;

and a restore bail engaging and operated by said second cam means after each successive displacement for restoring said selected punches and the displaced drive plate.

6. In a high speed punching device:

a rotatable cam shaft having first and second cam means mounted thereon, said first and second cam means having complementary cam surfaces;

first and second punch drive plates successively driven to a punch position by said first cam means during a revolution of said shaft;

a plurality of punches movable between punch and nonpunch positions;

a plurality of interposers positionable between said punch drive plates and selected punches for transmitting to said selected punches the movement to the punch position of each said plate;

and restore means operated to a punch position coincidentally with said punch drive plates and operated to a non-punch position by said second cam means, said restore means positioned about said punches and punch drive plates and embracing the punches so that upon operation by said second cam means said restoring means returns said punches and punch drive plates to the non-punch position.

7. In a high speed punching device:

a rotatable shaft having mounted thereon first cam means having a single lobe, second cam means having a single lobe diametrically opposed to the lobe on said first cam means and a double lobe cam complementary to a combination of said first and second cam means;

first and second punch drive plates successively driven from a non-punch position to a punch position by said first and second cam means respectively;

a plurality of punches movable between punch and nonpunch positions;

a plurality of interposers positionable between said punch drive plates and selected ones of said punches for transmitting to said selected punches the movement to the punch position of each said plate;

and restoring means actuated to a punch position by said punch drive plates and returned to a non-punch position by said double lobe cam, said restore means embracing said punches and said punch drive plates so that upon activation by said double lobe cam said restore means returns said punches and punch drive plates to the non-punch position.

8. The device as described in claim 7 wherein said restore means comprises a movable single element bail hav- 9. In a high speed punching device:

a plurality of punches movable between punch and nonpunch position;

a pair of interposers for each punch, the interposers of each pair being respectively related to said punch drive plates and positionable between the corresponding punch and the respective drive plates, for transmitting to said punch the movement to the punch position of the respective drive plate;

and restoring means moved to a punch position by each of said punch drive plates and returned to a nonpunch position by said double lobe cam, said restoring means embracing said punches and said punch drive plates so that upon restoration by said double lobe cam, said restoring means returns the moved 5 ones of said punches and punch drive plates to the non-punch position. 10. The device as claimed in claim 9 wherein said restore means comprises a movable bail which includes a toothed portion through which said punches extend, slotted 10 portions through which said punch drive plates pass, and a follower portion in contact with said double lobe cam.

References Cited in the file of this patent UNITED STATES PATENTS

Claims

1. A PUNCH MECHANISM COMPRISING: A SET OF PUNCHES MOVABLE BETWEEN PUNCH AND NONPUNCH POSITIONS; A PAIR OF SINGLE ELEMENT MULTIPLE PUNCH DRIVERS, SLIDABLY DISPOSED TO MOVE BETWEEN PUNCH AND NON-PUNCH POSITIONS EACH DRIVER BEING CAPABLE OF MOVING ALL OF SAID PUNCHES; MULTILOBE CYCLIC CAM MEANS FOR ALTERNATIVELY RECIPROCATING SAID DRIVERS DURING A SINGLE CYCLE; AND A PLURALITY OF INTERPOSER MEANS INSERTABLE BETWEEN CHOSEN ONES OF THE PUNCHES OF SAID SET AND SAID MOVED ONE OF SAID DRIVERS TO TRANSMIT SAID DRIVER MOVEMENT TO SAID CHOSEN PUNCHES CAUSING SAID CHOSEN PUNCHES TO BE EXTENDED TO THE PUNCH POSITION.