US3035762A - Tape perforating apparatus - Google Patents

Description

y 22, 1962 J. H. DRlLLlCK 3,035,762

TAPE PERFORATING APPARATUS Filed Nov. 17, 1959 6 Sheets-Sheet 1 INVENTOR. JACOB H. DRILLICK May 22, 1962 J. H. DRlLLlCK 3,035,752

TAPE PERFORATING APPARATUS Filed Nov. 17, 1959 6 Sheets-Sheet 2 INVENTOR. JACOB H. DRILLICK Attorney May 22, 1962 .1. H. DRlLLlCK TAPE PERFORATING APPARATUS 6 Sheets-Sheet 3 Filed Nov. 17, 1959 INVENTOR. JACOB H. DRlLLICK W Attorney May 22, 1962 J. H. DRlLLlCK 3,035,762

TAPE PERFORATING APPARATUS Filed Nov. 17, 1959 6 Sheets-Sheet 4 INVENTOR. JACOB H. DRILLICK I Attorney y 1952 J. H. DRILLICK 3,035,762

- TAPE PERFORATING APPARATUS Filed Nov. 1'7, 1959 6 Sheets-Sheet 5 n u .i 1 1 ii I! H 1! 1| ll H.051!

INVENTOR. JACOB H. DRILLICK Attorney May 22, 1962 J. H. DRlLLlCK 3,035,762

TAPE PERFORATING APPARATUS Filed Nov. 17, 1959 6 Sheets-Sheet 6 UC ..'|HIHHHWI m MIN JACOB H. DRILL! CK Attorney United States Patent M 3,035,762 TAPE PERFORATING APPARATUS Jacob H. Drilliclr, Los Angeles, Calif., assignor to Telecomputing Corporation, North Hollywood, Calif., a corporation of California Filed Nov. 17, 195?, Ser. No. 853,575 10 Claims. (Cl. 234-115) This invention relates to apparatus for perforating tape in accordance with coded electric signals to produce a code pattern of perforations in the tape.

In conventional tape perforating machines employing reciprocating punches the reception of signals for each code character results in two operations on the punches. First, the proper punches are selected or conditioned to be actuated, and then they are actuated to perforate the tape. In a common arrangement, the punch members are cyclically conditioned by an intermediate mechanism called an interposer. This is in turn powered by a cyclically operable reciprocating drive mechanism.

Such an arrangement has, heretofore, employed multiple elements in both the interposer mechanism and the cyclical drive mechanism, both having relatively high masses and complex motions. To overcome the inertia of these elements it is necessary to operate at an undesirably low punching speed. The present invention provides a high speed tape perforator and has only one eccentric and one cam-generated motion in its simplified drive mechanism. A unitary interposer mechanism is employed, as contrasted with the multiple element interposers of prior inventions. This reduction in both mass and numer of moving parts obviates this difliculty and results in high punching speed and long life. Other improvements, such as a novel anti-bounce mechanism associated with the interposer geometry, prevent interposer bounce or malfunction and makes possible higher interposer velocities.

The principal object of the present invention is to provide an improved perforating mechanism in which the control and actuating instrumentalities are designed to require only one eccentric and one cam-generated motion to the end that higher speeds and more reliable operation are obtainable.

Another object of the present invention resides in the provision of an improved unitary interposer means for conditioning the punch elements. Due to this provision, a more rapid operation of the punch member is possible.

A still further object of the invention is to provide a punch selecting and controlling device, wherein a magnetically actuated armature trips the interposer arm and thereby conditions the punch element and thereafter the interposer drives the punch element with a simple harmonic motion.

These and other objects of the invention will become more readily apparent from the following description and accompanying drawings, which disclose, by way of example, the principle of the invention and the best mode, which has been contemplated, of applying that principle.

FIGURE 1 is a multiple section view of the tape perforating apparatus of the present invention showing the principal elements thereof.

FiGURE 2 is a plan view of the apparatus of FIGURE 1 shown partially in section.

FiGURE 3 is an exploded view of the punch magnet interposer mechanism, illustrating the co-action of the principal parts thereof.

FIGURE 4 is a cross-section of the main drive shaft taken on line A-A of FIGURE 2.

FIGURE 5 is a cross-section of the eccentric cam mechanism taken on line 3-13 of FIGURE 2.

FIGURE 6 is a diagrammatic view of the interpose 3,035,762 Patented May 22, 19-62 mechanism illustrating the unlatched condition of the interposer.

FIGURE 7 is a diagrammatic view of the interposer mechanism in the latched condition.

FIGURE 8 is a diagrammatic view of the interposer mechanism showing the interposer driving the punch element upward.

FIGURE 9 is a fragmentary elevation view of the punch and die mechanism, partially in section, taken on line CC of FIGURE 1, illustrating their relationship with the interposers and the punch elements.

FiC-URE 10 is a fragmentary elevational View, partially in section, showing the jamb-rack feed mechanism.

FIGURE 11 is a fragmentary plan view, partially in section, of the feed mechanism, the section being taken along line DD of FIGURE 10.

lnterposer Mechanism Looking now at FIGURE 1 there is shown a side frame 1 which is spaced apart from, and in parallel relationship with, a similar frame by spacer rods 2, 3, 4 and 5. These spacer rods are fastened to the side frames by means of screws 6, 7, 8 and 9. A main drive shaft 10 is located in perpendicular relationship with side frame 1 and carries thereon various cams of which cam 11 is typical. These cams will be more fully described hereinafter. Link 12 for bellcrank 16 is driven from drive shaft 16 via eccentric cam ring 13 thereby providing a reciprocating motion to shaft 14 which is carried on one end of th link 12 and is attached thereto by collar 15. Bellcrank i6 is pivo-tally mounted on shaft 17 which is in turn fastened by any suitable means to side frame 1. Interposer shaft 18 is mounted on bellcrank 16 which turns on shaft 17 carried by hearing (shown in FIGURE 9). Interposer shaft 18 carries thereon a plurality of interposers of which 19, 20 and 21 are typical. The lower end portion of the interposers are guided by lower interposer comb plate 22 and guide plate 23. Plate 22 is spaced apart from guide plate 23 by spacer 31 and is attached thereto by fastener 32 (as shown in FIGURE 3). A plurality of interposer anti-bounce springs of which 24 and 25 are typical are located adjacent to the lower ends of the interposers. When an interposer is not engaging its associated punch elements, the lower end of the interposer rests on the upper surface of the anti-bounce spring.

e relationship of the interposer 19 to anti-bounce spring 24 is also shown in FIGURES 68. The anti-bounce springs 24, '25, etc. are attached to guide plate 23 by means of screws 26 and 27, which mate with threaded holes in guide plate 23.

Each interposer has an outwardly extending arm having a hook portion thereon to which is attached an interposer tension spring such as shown at 28 and 29. Located directly above the hook portion of the interposer arm is a latch portion which may be positioned in latching relationship with a magnet actuator assembly the structure of which will be described more fully hereinafter.

Main Drive Assembly stalled roll pin 35 so that cam 11 will turn with drive shaft 10. In. other instances an eccentric cam ring 13 rides upon cam 36 as shown in FIGURE 5. The eccentric cam ring 13 which rides on cam 36 is retained thereon by means of washer 37 and retaining ring 38. The cam 36 is attached to the main drive shaft 10 by means of roll pin 39 which passes through hole 40 in a manner similar to that shown in FIGURE 4.

The main drive shaft 10 turns through one revolution Main drive shaft extends through bearing 42 and carries main drive pulley 44. An extension of main drive shaft 10 through pulley 44 carries a single revolution clutch 45, and is retained thereon by collar 62, which may be of any well known standard construction. Main drive pulley 44 is to be driven from a continuously running drive motor of any standard well known construction.

Upon actuation of clutch 45, shaft 10 and collar 62 will be caused to rotate through a single revolution and stop while drive pulley 44 continues to rotate.

Bearing 41 is carried in side plate 46 and is attached thereto by swaging or any other convenient means. Intermediate of bearing 41 and bushing 42 are carried the various operating cams which rotate with main drive shaft 10. Each of these cams performs a specific function and a staggered relationship of the cam lobes determines the sequence of each function. Cam 47 serves to drive the tape feed mechanism. Eccentric cam ring 13 operates link 12 for powering bellcrank 16. Timing cam 48 actuates switch assembly 55, via cam follower 51 and link 56, for timing the clutch and interposer mag- 3 net signals. Timing cam 49 actuates the electrical switch assembly 57 via link 58 for producing timing signals as required in the control of the clutch and interposer magnets. Cam 50 actuates switch assembly 59 via cam follower 53 and link 60 for generating interlock signals.

The various timing intervals occurring through the per-- forator cycle are under the control of the electrical signals generated by means of switch assemblies 55, 57 and 59.

Magnet Actuator Assembly The magnet actuator assembly is shown in FIGURES 1, 2 and 3. Looking now at FIGURE 3, there is shown an exploded view of the magnet actuator, interposer and punch element assembly. The interposers 19, 20, 21,

etc., are under the control of a magnetic latching means comprising a magnetic pole piece 66 which is common to four separate magnet coils, of which 68 is typical. Associated with each magnet coil 68 is a magnet armature 69 biased by an armature spring 70. The armature spring 70 is attached to armature support 71. The armature 'latch' 30 engages the related interposer 19 when the armature magnet coil 68 is unenergized and Will trip the interposer 19 to be urged downward by tension spring 28 upon being energized.

Coil 72 is similar to coil 68, there being four coils in all, arranged on a common single pole piece 66. The upper two coils are arranged in staggered relationship with the lower two coils. A similar magnet actuator assembly comprising four coils and four armatures is 'lo- 65 cated in opposition to the above-described assembly. Interposer 20, for example, would engage an associated armature latch in this opposing assembly.

Interposer 21 will engage the latch carried by armature 75 of the first described assembly. In this way, every 7 other interposer engages an armature latch associated 'with one of the magnets on the common pole piece assembly. This arrangement provides a simple and compact arrangement which may be readily and inexpensively assembled.

Looking now at FIGURES 6, 7 and 8, there is shown, diagrammatically, the operation of the interposer and magnet actuator mechanism illustrating both the actuated and the reset conditions thereof. FIGURE 6 illustrates the reset condition which exist at the beginning of the perforating cycle. The reset or latched condition of the armature 69A and the latch 30A is shown in solid outline. In this condition, the latch portion of interposer 19 rests on latch 30A, and the uppermost portion of this interposer will not engage punch element 76. The initial relationships of cam 11, cam follower 80, and eccentric cam ring 13, with respect to the starting position of the main drive shaft 10 are also shown in FIGURE 6. The perforating cycle commences by selectively energizing various combinations of the magnet coils thereby actuating the armatures and unlatching the interposers. Upon being actuated, armature 69 and latch 30 will move away from engagement with interposer 19 in a direction shown in phantom outline and by arrow 83.

When the related magnetic coil is energized magnet armature 69 will move armature latch 30 away from interposer 19 causing the latter to be rotated about interposer shaft 18 under the influence of tension spring 28 which normally causes interposer 19 to be urged against armature latch 39. Shaft 14 and collar 15 are coupled to link 12 which provides a reciprocating motion to shaft 14. Rotation of interposer 19 by tension spring 28 will cause the uppermost portion of the interposer to engage punch element 76 as shown in FIGURE 7.

At the beginning of the punch cycle, interposer 19 rests on anti-bounce spring 24 as shown in FiG-URE 6. As the interposer is unlatched to permit its engagement with punch element 76, the lower end portion of interposer 19 moves out of its abutting engagement with anti-bounce spring 24. Anti-bounce spring 24 then moves upward to an edgewise engagement with the lower portion of interposer 19 as shown in FIGURE 7. This prevents the impact of the upper portion of the interposer 19, when striking punch element 76, from bouncing the interposer back into its disengaged condition. Such an inadvertent return of the interposer to its original condition is obviated by the restraint of spring 24 in engaging the side portion of the lower end of the interposer rather than engaging the bottom portion. As the interposer is driven upward during the latter part of the punching cycle, as shown in FIGURE 8, the interposer is moved towards disengagement from the anti-bounce spring 24.

The maximum upward excursion of interposer 19 and punch 76 is shown in FIGURE 8.

Concurrent with the upward motion of punch element 76, cam 11 will drive cam follower 8! in a direction outward from main drive shaft 10. Cam follower is carried on shaft 79 which is fixedly attached to link 78. The lower end of link 78 is pivotally mounted on shaft 77; thus its upper end will move in the direction of arrow 183 when cam follower 80 is displaced by the lobe of cam 11. The upper end of link 78 carries shaft 81 which in turn reciprocally drives switch link 82 which actuates a related timing switch assembly.

The successive positions of link 78 and its related parts are shown, relative to the concurrent positions of the interposer and punch element, in FIGURES 7 and 8.

When interposer 19 is moved into engagement with punch element 76, as is shown in FIGURE 7, upward motion of interposer shaft 18 will lift punch element 76 upward and into engagement with the die block. The upward motion of shaft 18 is derived from reciprocating link 12 via bellcrank 16 which is mounted on shaft 17 for arcuate movement about the center line of bearings 139 and 140. The beginning condition of this upward motion is shown by the broken outline in FIGURE 7; the intermediate condition of this upward motion is shown in solid outline.

The position of interposer 19, relative to armature latch 3b, is restored to its original relationship when bellcrank 16 moves from the position shown in solid outline in F16- URE 8 to the position shown in dotted outline. During this time, the canted or beveled upper edge of the arm portion of interposer 19 will move through an upward, slightiy arcuate, path in sliding engagement with latch 36A causing it to be initially deflected in the direction of arrow 33 (as shown in FEGURE 6). Thereafter, latch 33A will move, under the biasing action of spring 70 (as shown in FIGURE 3), into latched engagement with the latch portion of the interposer arm, thus resulting in the original or reset condition of the interposer 19. The

upward motion of interposer 19 will cause its extreme lower end to disengage from anti-bounce spring 24 in the manner shown in FIGURE 8; at the conclusion of its downward movement, the bottom end of interposer 19 will come to rest on the upper surface of anti-bounce spring 24.

As can be seen, only the magnet armature 69 and the interposer 19 are required to be acted upon to effect a change from the normal condition to the active punch condition.

Upon momentary energization of magnetic coil 63, as shown in FIGURE 3, the related magnetic armature 69 is displaced to unlatch or release the engaged interposer and permit it to be angularly displaced under influence of tension spring 28 thereby positioning the upper end of interposer 19 in the path of the lower or free end of the related punclmelement 76.

It should be mentioned at this time that the shaft 18 is not constantly reciprocated but is operated in a cyclical or stop-start manner under the control of the single revolution clutch 45 and that the selected armature latch, or latches, are actuated to unlatch the desired interposers prior to the tirne the reciprocating drive action commences. Thus, upon unlatching of a selected interposer, and movement of shaft 18, the related punch eiement is forced upwardly thereby causing the tape interposed between the die aperture and die block to be perforated.

Due to the close spacing of the parts, the magnetic assemblies and interposers are alternately arranged with the related hook portions and magnets placed in staggered relationship as shown in FIGURE 3 with the spring restrained arm of the interposers being alternately reversed to provide an extremely compact arrangement of magnets and interposers.

Every other interposer has its anti-bounce spring in reversed relationship to the adjacent anti-bounce springs to correspond to the alternating arrangement of interposers and magnet assemblies. The anti-bounce springs may conveniently comprise two comb-like rows of fiat leaf springs joined at one end and free at their opposite ends. It is hese free ends which cyclically engage the bottom and the sides of the lower end portions of the related interposers to prevent bouncing of the interposers and thereby inadvertently relatch them prior to the completion of the punch cycle. The steps of the cyclic operation of the anti-bounce mechanism is shown in FIG- URES 6, 7 and 8.

Punch and Die Mechanism Looking now at FIGURE 9, there is shown the relationship of the punch elements 76, and 90-86, the die block 98, the interposers 19--21, 99--1Z'3, and 135 and the punch reset mechanism as described hereinafter. The punch and die mechanism is supported between side plate 1 and side plate '46 which are in turn separated by bottom plate 196 and top plate 124. The die block 98 is attached to top plate 124 on only one side and is aligned by means of dowel pin 116 thereby leaving an open passage 115 through which the tape to be perforated may be inserted. In the embodiment shown, there are eight punch apertures 126133 in the die block 93 for receiving punch elements 76 and 9896, plus an extra aperture 134 for receiving the feed punch 97. Fastener 117 attaches side plate 46 to the bottom plate 106. Fastener 117 mates with not 114 carried by side plate 46. Similarly, fastener 119 attaches bottom plate 106 to side plate 1 and is held by nut 120. The alignment of the punch elements with respect to the punch apertures is maintained by having them guided for rectilinear translation by the relative position of guide plate 107 with respect to top plate 124. Guide plate 107 is supported by plates 112 and 113. Dowel pin 116, in addition to aligning the die block 98, also attaches plate 112 to top plate 124. Guide plate 107 is held in positicn between plates 112 and 113 by fasteners 108 and we. Fastener 110 attaches plate 113 to top plate 124.

The row of apertures in top plate 124 and guide plate 197 serve to align and guide punches 76 and 9096 for engagement with dis block 98. The punches are carried upward through the paper tape which is positioned in tape passage and into the die block 98 by interposers 19, 29, etc. These interposers are carried on shaft 18 which in turn is driven by bellcrank 16. One end of shaft 18 is carried on bellcrank 16 which pivots on shaft 17 which in turn moves in bearing 14%. The bellcranl: is powered from eccentric 15 as explained in connection with FIGURE 1. The alternate end of shaft 18 is carried in collar which is fixedly attached to arm 138. Arm 138 has its alternate end attached to shaft 147 which moves in bearing 13?. This arrangement permits shaft 18 to be carried upward along a substantially rectilinear path, with the interposers carried thereon, being guided by bottom plate 1%. Belle-rank 15 is fixedly attached to the opposite end of shaft 18 as described earlier. The shaft 17 on which bellcrank 16 is pivotally mounted is supported by bushing 140 in side plate 1. The oscillatory motion imparted to bellcrank 16 will move shaft 18 upward and downward to impart a simple harmonic motion to the interposers carried thereon.

Punch Reset Assembly The positive return of the punches is accomplished by a reset bail driven by a linkage from the main drive shaft. This reset bail ultimately restores all of the powered punch elements to their initial condition near the end of the perforating cycle. The cycle function is accomplished as follows:

As shown in FIGURES 1 and 3, each punch has a notch (cg. punch 7:5 has notch 143) located between the bottom end which engages its associated interposer and the top end which engages the die block 98. The reset bail 142 transversely engages the notch in each of the punches. The reset bail 142 is mounted on reset bail pivot shaft 144 by rivet 146 or other suitable fastening means, and is driven by drive link 141. Drive link 141 is carried on shaft 18 for reciprocating drive with the interposers. The end of the interposer support shaft carries an eccentric extension 11?, which extends through the central support aperture of drive link 141. This eccentricity of the pivotal axis of the drive link 141 for the reset bail 142, as compared with the pivotal axis of the interposers 19-20, is indicated by the step in the dashed centerline 148 corresponding to shaft 18 in FIGURE 3. This will permit any necessary adjustment to be made in the operation of the reset bail.

The downward movement of the punch elements is checked by the upper end of their notches engaging stop bar at the downward limit of the reciprocating motion.

Tape Feed Mechanism The tape feed mechanism is shown in FIGURES l0 and 11; with reference to FIGURE 10, the rotation of first cam 47 causes reciprocating displacement of cam follower 149 which is carried on shaft 150. Cam 47 is cyclically driven by main drive shaft 1!). Cam follower arm 151 is pivotally mounted on shaft 152 and also by nut 156 and lock washer 157 and carries spacer 155.

Looking now at FIGURE 11, bolt 153 passes through an elongated opening in jamb rack 154, spacer 15S, and is fastened thereto by nut 159. Spring 16% has one terminus restrained by shaft 152, encircles shaft 153 and has its alternate terminus restrained by stud 162. Spring 160 serves to bias jamb rack 154 to engagement with cam follower arm 152 in order to eliminate play. Jamb rack 154 is further urged into orthogonal relationshhip with cam follower arm 151 by spring 161. The cam follower 149 is urged against cam 47 by the biasing action of spring 163 attached to the upper end of cam follower arm 151 through hole 164 and being referenced to the side plate 1 by having its alternate end attached to stud 165.

The oscillating movement of cam follower arm 151 about pivot shaft 152 causes the jamb rack 154 to reciprocate once for each revolution of the main drive shaft 10. The reciprocating path of jamb rack 154 is guided by roller 166 attached to side plate 1 by stud 167 and is fastened thereto by retaining ring 168. Reciprocation of jamb rack 154 causes detent 121 to intermittently engage the teeth of ratchet wheel 176i and rotate the sprocket assembly carried therewith on shaft 171. The detent end portion of jamb rack 154 is guided in slot 172 of block 175. Block 173 is attached to side plate 1 by means of screw 174 or other convenient means.- Spring 122 in cylindrical opening 123' urges jamb rack 154 upward to aid detent 121 in its engagement with the sprocket teeth 170. Spring 122 is retained by any suitable means held in opening 125.

Spring 163 urges the jarnb rack 154 to return to the starting position. Pawl spring 169 urges the jamb rack 154 upward about pivot 153 to maintain engagement of the jamb rack with detent wheel 170.

Tape Check System The condition of the paper tape 63 and its proper operation through the device is checked by means of a system of linked electrical contacts. The first of these comprises a tape tension assembly for detecting the presence or absence of the proper degree of tension of the paper tape coming from the supply reel. The second determines whether the paper tape has been broken; and the last determines if the tape hold-down assembly is properly closed.

The tape tension assembly comprises guide roller 64 over which the paper tape 63 passes. The tape moves over tape guide roller 64 rotatably supported by shaft 65 which is in turn carried on tape tension arm 67. The tape tension arm 67 rotates about shaft 77. Stud 84 engages contact spring 85 which provides an electrical indication of the position of the tape tension arm 67. In the event that there is excessive tape tension, the arm 67 will be carried in a clockwise direction about shaft 77 by the tape 63 moving over roller 64. This will result in contact 85 being closed to provide the above stated electrical indication. Under conditions of proper tape tension, the position of the tape tension arm 67 will allow contact 85 to remain open. This normal position of the tape tension arm is biased in a counter-clockwise direction by tension arm spring 86 attached to stud 87 on arm 67 and stud 88 on plate 1.

Tape channel arm 39 is normally carried in a raised position on the upper surface of the paper tape 63. Tape channel arm 89 is pivoted on shaft 104 and is normally urged upward (counter-clockwise) by the tension of the tape 63. An alternate end of this arm carries a stud which is linked to a switch link which actuates tape sensing switch 111. In the event the tape becomes torn or is not properly placed in the tape channel 115, the tape channel arm 89 will move downward (clockwise) and actuate the tape sensing switch 111.

Tape hold-down175 is pivotally mounted on shaft 176. The alternate and of tape hold-down 175 carries a spring mounting stud 177 which is attached to spring 178 for holding the tape hold-down in either an open or closed detented position. Spring 178 has its alternate end fixedly attached to fastener pin 179 carried by the main supporting side plate 1. Also located on the tape hold down is pin 18% connected to linkage 181. The alternate end of linkage 1S1 engages tape hold-down switch 182 which will be caused to close whenever the tape holddown is open, i.e., rotated clockwise.

Electrical Interlock System In addition to the electrical contacts discussed above, there are additional switch contacts actuated by the clutch, the punch magnet mechanisms, and the cam assemblies. These provide electrical interlocks for indieating and controlling the proper operation of the cyclical punching. Interlocking cam switch 59 is actuated via link 68 which is in turn moved by cam follower 53 rotated by interlocking cam 5t Once during each revolution of the main drive shaft 10 switch 59 will be closed.

Clutch and punch magnetic switch 57 is actuated by link 58 carried by cam follower 52 associated with clutch and punch magnet cam 49.

Clutch and punch magnetic switch 55 is similar to that previously described except that it is actuated by clutch and punch magnetic cam 48 via link 56.

Typical Punching Operation A typical punching operation begins with the selective energization of themagnet coils 68, 72, etc. This unlatches the related interposers causing them to moveinto engagement with their associated punches and will thereby control the appropriate punching pattern. Thereafter, the single revolution clutch 45 is actuated to couple drive power to drive shaft 10. Drive shaft 10 will power the cam ring 13 driving link 12 and shaft 18 via bellcrank 16. This will in turn urge the selected interposer-s upward to drive the selected punches through the paper tape. At the proper time during the revolution of the drive shaft, the tape advance mechanism will be actuated via cam 47, link 151, and jamb rack 154 causing the sprocket roller 17% to advance the tape one step. Subsequent to this action, the main drive shaft will actuate the reset bail 142 via linkage 141 to restore the actuated punches. The magnets will be de-energized and the return motion of the eccentric drive will restore the interposers to a latched condition. A new drive cycle may now be initiated.

While particular embodiments of the present invention have been shown and described, it will be obvious to those skilled in the art that changes and modifications may be made without departing from this invention in its broader aspects, and, therefore, the aim in the appended claims is to cover all such changes and modifications as fall within the true spirit and scope of this invention.

I claim:

1. Apparatus for perforating a tape in accordance with coded signals representing information characters to produce a coded perforation pattern in said tape comprising a plurality of perforating elements including punches and a die having die openings for receiving said punchm, means for feeding tape between said punch elements and said die, a plurality of interposer means, movable for selective engagement with said punches from a latched to an unlatched state, a plurality of pivots each mounting a corresponding one of said interposer means, means for imparting a driving motion to each of said pivots during said unlatched state, a plurality of signal responsive selector means each corresponding to a different interposer means for unlatching said interposer means prior to the application of said driving motion to said pivots and thereby permitting said interposer means to drive said engaged punches through said tape into said die openings upon application of said driving motion.

2. In a record punching device, a punch element mounted for rectilinear reciprocation, a die having a die opening for receiving said punch element, a reciprocating driving means, a unitary interposer connected with said driving means for movement thereby, and selectively movable into position to engage and move said punch element in one direction, a reciprocating restoring reset bail movable into driving engagement directly with said punch element to return said punch element to its origdnal position, said driving means sequentially driving said interposer and said restoring reset bail.

3. Perforating apparatus comprising a plurality of punch elements adapted to be rectilinearly driven and retracted, a plurality of unitary interposer members each having a first end portion for engaging a corresponding one of said punch elements in driving relationship, each interposer being pivotally rotatable to permit said interposer to be moved into and out of engagement with a related one of said punch elements, a latch integral with each of said interposers, reciprocating means co-acting with each of said interposer pivots for driving said interposers, a plurality of positionable stop members, one for each interposer, for normally engaging said latches to retain said interposers out of engagement with said punch elements, and means for selectively operating the said stop members to release said latches and thereby move the related interposers into engagement with said punch elements, thereby causing the released interposers to drive the related punch elements.

4. Perforating apparatus comprising a plurality of punch elements, a plurality of interposers one for each punch element, each interposer being pivotally mounted for angular rotation into or out of driving engagement with a related punch element, driving means co-acting with the pivot points of said in-terpo-sers for rectilinearly reciprocating the latter, start-stop control means for rendering the said driving means operative for a cycle of reciprocation, a plurality of positionable latch members, one for each interposer, means for selectively operating the said latching members and releasing the related interposers so that the latter engage the related punch elements prior to the start of said cycle of rotation whereby said driving means will drive said punch elements through said related interposers during said cycle of operation, and reset means adapted for co-action with said driving means near the end of the cycle of reciprocation for restoring said driven punch elements to their initial position.

5. Perforating apparatus comprising, a plurality of punch elements adapted to be rectilinearly driven and retracted, a plurality of unitary interposers each having a first end portion for engaging one of said punch elements in driving relationship, a plurality of pivots each rotatably mounting one of said interposers, reciprocating drive means for bodily moving all of said pivots, a latch integral with each of said interposers and displaced from said pivot for each interposer, stop means normally located for engagement with said latch, means for continually biasing said latch into engagement with said stop means, said one end of each interposer being out of alignment with its corresponding punch element during movement of said pivots while said latch engages said stop means, and means selectively operable for moving said stop means away from said latch to cause said biasing means to move said on end into engagement with its corresponding punch element to cause punching movement during movement of said pivots.

6. Perforating apparatus as defined in claim 5 wherein said one end of each interposer contains a notch, one side of said notch engaging a side of its corresponding interposer upon movement of said latch away from said stop means and the other side of said notch engaging the bottom of its corresponding punch element to move said punch element in a punching direction upon movement of said pivots.

7. Perforating apparatus as defined in claim 6 having reset means positively driven by said drive means in unison with said plurality of punch elements, said reset means comprising means engageable with each of said selectively operated punch elements at the end of its punching stroke for positively returning said operated element to its starting position upon further rotation of said drive means, said return movement causing each interposer to move about its pivot and against said biasing means and into position for engagement of its latch with said stop means.

8. Perforating apparatus as defined in claim 7 wherein said stop means is movable and spring biased toward each latch to permit each latch to move past said stop means during return of said operated punch elements and permit said stop means to engage each latch after complete return thereof.

9. Perforating apparatus as defined in claim 8 wherein said step means is mounted at the end of a movable arm, a cam surface on said latch for moving said stop means away from said latch to permit said stop means to move underneath said latch into locking position.

10. Perforating apparatus as defined in claim 9 a second end on each interposer in alignment with said first end anti-bounce spring means normally located below said second end, said second end being movable to engage the end of said anti-bounce spring means upon movement of said stop means to release said interposer, said spring means thereafter holding said one side of said notch in engagement with its corresponding interposer to assure positive drive of the corresponding punch element.

References Cited in the file of this patent UNITED STATES PATENTS 775,237 Collins Nov. 15, 1904 2,346,267 Mills et al. Apr. 11, 1944 2,675,078 Zenner Apr. 13, 1954 2,761,508 Gofi Sept. 4, 1956 2,859,816 MacNeill Nov. 11, 1958

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