US3035763A - Code punching machine - Google Patents

Description

H. E. MORRIS CODE PUNCHING MACHINE May 22, -1962 3 Sheets-Sheet 1 Filed Jan. 25, 1961 May 22, 1962 H. E. MORRIS 3,035,763

CODE PUNCHING MACHINE Filed Jan. 25, 1961 3 Sheets-Sheet 2 IN VEN TOR.

May 22, 1962 H. E. MoRRxs 3,035,763

CODE PUNCHING MACHINE Filed Jan. 25, 1961 3 Sheets-Sheet 3 jig. 14

IN V EN TOR.

United States Patent O 3,035,763 CODE PUNCHING MACHINE Howard E. Morris, Arlington Heights, lll., assignor, by

mesne assignments, to Victor Comptometer Corporation, Chicago, Ill., a corporation of Illinois Filed Jan. 25, 1961, Ser. No. 84,875 7 Claims. (Cl. 234-128) The present invention relates to code punching or perforating machines and is concerned particularly with problems which arise in the perforation of a very wide recording body of indefinite length which is indexed or stepped through a code punching station.

One object of the inventio-n is to provide an improved code punching machine which will operate eiciently and dependably at high speed to punch data in code in a very wide recording body of indefinite length.

Another object is to provide a code punching machine adapted to punch code in a wide recording body and having a new and improved construction which brings the recording body to a Vcomplete stop in each of a succession of recording positions with reference to a punching station while at the same time providing for very fast advancement lof the recording body to successive recording positions ina manner which effects a smooth acceleration `and a smooth deceleration of the body as it advances from one recording position to another.

Another object is to provide an improved code punching machine in which high speed intermittent advancement of a recording bodyto a succession of punching positions is provided by improved means which maintains a positive control of the position of the recording body at all times no hold the body completely still in each successive punching position of the body and to effect quick advancement of the recording body between successive punching positions in a manner that avoids the application of impact loads to recording body indexing structure in the machine by providing for mutual engagement of coacting parts of the indexing structure before the parts are subjected to recording body advancing forces.

A further object is to provide an improved code punching machine of the character recited in which operating forces transmitted between coacting parts of the recording body indexing structure in the machine are spread over extensive mutually engaged surface areas of the coacting parts to avoid stress concentrations and effectively minimize wear even though the machine is operated at high speed.

Other `objects and advantages Will become apparent from the following description of the exemplary embodiment of the invention illustrated in the drawings, in which:

FIGURE 1 is a fragmentary plan view illustrating the organization of major components of the code punching machine forming the illustrated embodiment of the invention;

FlG. 2 is a fragmentary vertical sectional view taken generally along the line 2 2 of FIG. l;

FlG. 3 is a fragmentary vertical sectional with reference to the line 3 3 of FIG. 1;

FIG. 4 is a simplified sectional view similar to FIG. 3 but illustrating a different operating phase of the recording body indexing mechanism shown;

FIG. 5 is a fragmentary sectional view similar to FIG. 4 but illustrating a still different phase in the operation of the mechanisms;

FiG. 6 is an exploded perspective view of indexing elements incorporated into the machine; and

FIG. 7 is an end view of the assembly of operating cams used in indexing the recording body in the machine.

Referring to the drawings in greater detail, the code punching machine 1G forming the exemplary embodiment View taken lCC Y.

of the invention illustrated is adapted to punch data in y code in a very wide recording body 12 of indenite length. In this instance, the recording body 12 is formed by a strip of recording paper which is approximately sixteen inches wide. The width of the recording body 12 is determined by considerations which relate largely to the various functions the recording body is designed to serve and cannot be substantially controlled by the design of the code punching machine.

ln the present instance, the recording body 12 consists of a connected series of utility bills which extend longitudinally across the width of the recording body. Each bill must have sufficient length to accommodate information adequate for billing a customer by mail and to provide space for recording data in punched code.

ln the code punching machine 16, the wide recording body 12 is moved along a path which carries a portion of the body through a punching station 14 defined by the punching machine. In passing through the code punching or perforating station 14, the recording body 12 is stepped or indexed across a deck or table 16 of a punching head 18 which is controlled by electrical code signals supplied to a bank of punch control solenoids 20.

The punching or perforating head 18 is designed to record data in a telegraphic code, such for example as the Teletype code. The head 1S, as such, is formed of a, conventional construction requiring no specific description here. A bank `of perforating punches 22 is selectively operated in response to coded electrical signals to punch a transverse line of apertures in the portion of the recording body 12 located in the punching station 14.

The recording body 12 is held stationary in the recording station 14 while coding punches 22 are moved through the recording body to punch a coded line of apertures 24 in the body. After the punches 22 are withdrawn, the recording body 12 is indexed or stepped to its next recording position which brings an imperforate portion of the body into alignment with the punches 22. This intermittent indexing of the recording body 12 to a succession of recording positions in which the body is stopped and punched in code is characteristic of the mode of operation Aof code punching machines which record data in punched code in this manner.

However, special problems arise in the punching of wide recording bodies, such for example, as the sixteen inch wide recording body 12 which is coded in the machine 10.

In the interest of production eiciency, it is important that the recording body 12 be intermittently indexed and punched in code at a rapid operating speed. However, the matter of effecting a rapid intermittent indexing of a very Wide recording body 12 presents a source of problems which are not encountered in the indexing of narrow recording bodies, such as the narrow recording tapes in which data is commonly punched in code.

In order to rapidly index and properly position the wide recording body 12 with reference to the punching station :14 it is necessary to provide relatively massive Isupport structure `for the recording body, which support structure must be indexed with the body. As illustrated, in the drawings, the two marginal side edges of the wide recording body 12 are trained over two widely spaced sprocket wheels 2S, 3i) rotatably fixed to a common indexing shaft 32. Sprockets on the wheels 23, 30 fit into sprocket openings 34 in the marginal side edges of the recording body 12 to effect a positive positioning of the recording body with reference to the sprocket wheels.

Because of the great width of the recording body 12, it is necessary to provide support to the recording body between the sprocket wheels 28, 30. This is effected by means of a plurality of support wheels or rollers 35, 36, 3S, 44) nonrotatably iixed to intermediate portions of the shaft 32 as shown in FIGS. 1 and 2, to fnctionally engage the recording body y12, which is trained over the intermediate support rollers in the same manner that it is trained over the sprocket wheels, as shown in FIG. 3.

The recording body 12 is intermittently advanced with reference to the punching station 14 by intermittent rotary indexing movement of the indexing shaft 32. This shaft together with the sprocket wheels 28 and 3G, the intervening support , wheels 35, 36, 38 and 4i), and the means connected with the shaft 32 to effect rotary indexing lmovement of the shaft have in the aggregate a relatively large rotary inertia. This rotary inertia, which tends to resist rotary acceleration and deceleration of the shaft 32, is cumulative with the rather substantial inertia of the wide indexing body 12.

During the actual punching of the recording body, all the structure which moves with the recording body is held stationary. To advance the recording body 12 from one indexed position to another, it is necessary to accelerate the body and the structure rotatable with the shaft 32 from a standing st-art to a maximum indexing speed and then decelerate all this mass to a complete stop.

In order to achieve an eicient operating speed of the code punching machine it is necessary that the total elapsed period for each successive punching cycle be reduced to only a small fraction of a second. Moreover, the total time consumed in indexing the recording body from one punching positioning to the next should be the lowest possible fraction of the total operating period for each punching cycle in order to maximize the operating efficiency of the machine. The effect of these considerations is to place a great premium on reducing the time required to advance the recording body to its successive recording positions.

In the machine 10, the shaft 32, which controls the position of the recording body 12, is operated by a gear 42 drivingly connected to one end of the shaft as shown in FIGS. 1 to 3 and having a diameter approximately equal to that of the sprocketV wheels 28, 30. Controlled indexing movement of the gearV 42 is powered by a rotary cam shaft 44 parallel to the shaft `=32. The cam shaft 44 is energized by an electric motor 46 connected through a speed reducing transmission 48 and a clutch 49 Vwith the cam shaft as shown in FIG. 1. The clutch 49 is controlled by a solenoid 51 to effect starting and stopping of the shaft 44 independently of acceleration and decelera- 'tion of the driving motor 46.

One end of the shaft 44 projects through a support bracket 48 which provides support to both the shaft 44 and the shaft 32.

The end of the shaft 44 which projects beyond the bracket 48 supports three coaxial operating cams 50, 52, 54 disposed in fixed predetermined rotary positions relative to each other and nonrotatably fixed -to the shaft 44. The three cams 50, 52, and 54 are axially spaced somewhat from each other as shown in FIG. 2. The middle one 52 of the three cams 50, 52 and 54 serves as a power driving or actuating cam for physically advancing the gear 42 intermittently to index the recording body 12 to successive recording positions.

As will presently appear, the three cams 56, V52, 54 cooperate with coacting parts to effect two complete indexing cycles of the recording body positioning structure for each complete revolution of the cam shaft 44.

As best shown in FIG. 7, the power driving or actuating cam 52 has a double Iobed form designed to produce two advancing movements of the gear 42 for each revolu.- tion of the shaft 44. The cam surface on the periphery of the cam 52 engages a following roller 56 on one end of a swingable feed actuator 58, which is pivotally supported at its opposite end for swinging movement vabout the rotary axis of the shaft 32. As shown, the swingable actuator 58 has a generally U-shape and comprises two parallel legs 60, 62, FIG. 6, which embrace the gear 42, FIG. 1, and have apertured support ends which are pivoted on the shaft 32.

The cam follower 56 is held in engagement with the cam 52 by the action of a tension spring 64 as will presently appear. The feed actuator 58 follows the cam 52 to oscillate between a retracted position shown in FIG. 5 and an advanced position shown in FIG. 3 through an angle equal to the angle through which the gear 42 is to be advanced to index the recording body 12. The cam 52, moreover is shaped to effect dwelling of the feed actuator 58 in each of its two extreme positions and to effect a quick swinging movement of the actuator between its extreme position with smooth acceleration and deceleration of the actuator movement.

The portion of the peripheral cam surface on each of the cams 50, S2, 54 which is activated in a single complete indexing cycle extends only 180 degrees around the cam and merges with an identical por-tion of the cam surface which extends around the second half of the cam.

The periphery of the cam 52 denes a pair of inner dwelling surface segments 70, 72 spaced 180 degrees from each other around the cam. Each of these surfaces has a center of curvature coinciding with the yaxis of the shaft 44 and extends around the cam through a radial angle of approximately twenty degrees.

Each of the cam surface segments 70, 72 coacts with the cam follower S6 to provide yfor dwelling of the feed actuator 58 in its retracted position illustrated in FIG. 5. Dwelling of the feed actuator 58 in its Vadvanced position illustrated in FIG. 3 is provided for by a pair of outer, dwelling surface segment 74, 76 of the cam 52 located on diametrically opposite sides of the cam between the dwelling surfaces 70, 72, as shown lin FIG. 7. Each outer dwelling surface segment 74, 76 has a `center of curvature coinciding with the yaxis of the shaft 44 and extend circumferentially through a radial angle of approximately twenty degrees.

The cams 50, 52, and 54 are rotated in the counter- Iclockwise direction with reference to FIGS. 3, 4, 5 and 7. Two diametrically opposed actuator retracting cam surface segments 78, 80 on the cam 52 extend from the outer dwelling ysurfaces 74, 76 respectively to the respective inner dwelling surfaces 72, 70 as shown in FIG. 7. These surfaces are shaped to effect a smooth acceleration and deceleration of the actuator 58 to quickly return the actuator from its advanced position to its retracted position.

Two actuator `advancing cam surface portions 82, 84 are formed on the cam 52 in diametrically spaced relation to each other and extend from the inner dwelling surfaces 7 0, 72 respectively to the respective outer dwelling surfaces 74, 76 and serve individually to smoothly accelerate and decelerate the feed actuator 58 to swing from its retracted position to its advanced position.

To review the operation of the cam 52, we may start with the assumption that the feed actuator 58 is dwelling in its extended position with the follower 56 moving along the outer dwelling surface 74. As the follower roller 56 moves olf the surface 74 onto the surface 78, the actuator 58 is quickly but smoothly accelerated and then smoothly decelerated to locate the actuator 58 in its retracted position as the roller moves off the surface 78 onto the surface 72. The actuator 58 dwells in its retracted position until the roller moves from the surface 72 onto the surface 84, which effects a smooth acceleration of the actuator in -a feeding or advancing direction. The actuator 58 is smoothly Adecelerated las the roller 56 moves Ialong the trailing end of the surface 84 to the surface 76 which causes the actuator to again dwell in its advanced position. This cyclic action of the actuator 58 is repeated as the roller 56 moves on -along the surfaces 80, 70 and 82 back to the surface 74. Y

The swinging movements of the :actuator 58 in a recording body indexing direction are transmitted to the gear 42 through a feed pawl 90 pivotally supported on the actuator 58 between the roller 56 and the pivotally supported end of the actuator.

The feed pawl 90 defines -a plurality of locking elements or teeth 92, three in this instance, disposed in opposing relation to the gear 42 and adapted to interfit with opposing teeth on the gear upon swinging of the pawl into engagement with the gear.

The previously mentioned biasing spring 64 connects with a laterally extending -anchoring element 94 on the pawl 90 to apply a rotary biasing force to the pawl tending to cause it to swing about its support pivot 96 on the actuator 58 to engage the teeth `elements 92 on the pawl with the gear 42, FIG. 3. The reaction of the spring 64 on the pawl 90 is transmitted through the pivot 96 to continuously hold the actuator 58 in engagement with the cam 52 as previously described.

Movement of the feed pawl 90 into and out of engagement with the gear 42 is controlled by a cam follower 98 rigidly connected to the pawl 90 to swing with the pawl about the pivot 96 on the actuator 58. A roller 100 on the follower 98 bears directly on the periphery of the cam 50, which is shaped in relation to the position of the follower 98 and in relation to the cam 52 to engage the pawl 90 with the gear 42 while the actuator 58 is dwelling in its retracted position and to disengage the pawl 90 from the ygear 42 while the actuator 5S is dwelling in its advanced position.

Having reference to FIG. 7, when the feed -actuator roller 56 is in engagement with the outer dwelling surface 74, for example, the feed pawl cam following roller 100 moves over a rising cam surface 102 on the cam 50, which l disengages the feed pawl 90 from the gear 42, FIG. 4. By the time the -actuator roller 56 reaches the end of the dwelling surface 74 to move onto the retracting surface 78, the feeding pawl control roller 100 'has moved onto a raised cam surface 104 on the cam 50. The cam surface 104 is conformed to the cam surface 7S to hold the feed pawl 90 in its released position throughout the return movement of the actuator 58 to its retracted position.

After the actuator roller 56 has reached the inner dwelling surface 72, the feed pawl control roller 100 travels down a declining cam surface 106 on the cam 50 to allow the spring 64 to reengage the feed pawl 90 with the gear 42 before the roller 56 reaches the end of the dwelling surface 72, FIG. 5. Hence, the pawl 90 is fully engaged with the gear 42 before the actuator 58 starts to advance.

As the roller 56 moves along the surface 84 to advance the actuator 58, the feed pawl control roller 100 moves along a surface 108 of lthe cam 50 which conforms to the surface 84 of the cam 52 to maintain full engagement of the pawl 90 with the gear 42 until the actuator 58 reaches its fully advanced position.

As the roller 56 continues along the outer dwelling surface 76, the feed pawl control roller 100 continues along a second pawl disengaging surface 110 on the cam S which is identical to the previously mentioned disengaging surface 102 on the cam 50. From the surface 110, the roller 100 continues along Vsurface portions 112, 114 and 116 of the cam 50 which form identical counterparts of the previously mentioned cam surface portions 104, 106, and 108.

A positive control of the rotary position of the indexing gear 42 is maintained at all times by positively locking the gear in a stationary position after it has been advanced to a new position and before the feed pawl 90 is released from the gear. Moreover, the gear 42 is held stationary by the positive locking means until the feed pawl 90 is again fully engaged with the gear to effect the next successive rotary advancement of the gear, whereupon the locking of the gear 42 is repeated cyclically in timed relation to operation of the feed pawl. g

. The gear 42 is positively locked in each indexed position to which it is moved by means of a locking pawl 120 swingably supported on a pivot 122. The locking pawl ,120 denes a plurality of locking teeth elements 124, three in this instance, adapted to mesh in locking engagement with opposing teeth on the gear 42 upon engagement of the pawl with the gear. The pawl is urged toward engagement with the gear by means of the previously mentioned spring 64 which is connected between a spring anchor 126 on the pawl 120 and the previously mentioned anchor 94 on the pawl 90.

Movement of the pawl 120 into and out of engagement with the gear 42 is controlled by the coaction of a cam following roller 123 on the pawl 120 with the previously mentioned cam 54.

As shown in FiG. 7, the cam 54 defines two locking cam engaging surfaces 130, 132 located on diametrically opposite sides of the cam and spaced apart by two intervening locking cam release surfaces 134, 136. The surfaces 130, 132 and 134, 136 on the cam 54 have positions which are correlea'ted to the position of the coacting roller 128 and to the positions of the previously described cam surfaces on the cams 50 and S2 to produce the desired synchronization `of the locking pawl 120 with the feed pawl 90.

The locking pawl release surface 136 is designed to hold the pawl 120 in its gear releasing position as the actuating roller 56 moves over the indexing surface S2 of the cam S2, FiG. 3. When the roller 56 reaches the outer dwelling surface 74, the locking pawl control roller 123 moves from the surface 136 down a declining surface 13S on the cam 54 to reach the lock engaging surface 132 and effect engagement of the locking pawl 1.20 before the feed pawl control roller 100 moves up the surface 192 on the cam 50 to release the feed pawl 9o.

The locking pawl control roller 128 remains in engagement with the cam surface 132 until the feed pawl control roller 100 has passed over the declining cam surface 106 to reengage the feed pawl 90 with the gear 32. After the pawl 90 is fully engaged with the gear 32 and before the advancing roller 56 starts up the advancing surface S4, the locking pawl roller 128 moves up a raising cam surface 140 onto the lock releasing cam surface 134, which holds the locking pawl in released position only until the advancing roller 56 reaches the next dwelling surface 76, whereupon the roller 12S moves down a declining cam surface 142 to again reengage the locking pawl.

The locking pawl control surface is identical to the surface 132 and connects with the cam surface 136 through a rising cam surface portion 144 identical with the rising cam surface portion whereby the cyclic action of the locking pawl 120 is performed twice during each revolution of the shaft 44.

The indexing structure thus described is capable of applying powerful rotary indexing torque to the indexing shaft 32 to eect a high speed intermittent indexing of the recording body 12 without imposing excessive stress on the indexing structure. The feed pawl 90 is fully engaged with the gear 42 and occupies a stationary position with reference to the gear and with reference to the feeding actuator 5S before indexing force is applied through these fully engaged parts to advance the gear 42.

This full engagement of the coacting parts with each other before indexing force is applied to any of the parts avoids impact loading of the structure which would tend to overstress the parts and tend to cause excessive Wear on the indexing structure. Moreover, the gear actuating forces transmitted between the feed pawl 90 and the gear 42 are distributed over rather extensive mutually engaged -surfaces of the feed pawl teeth elements 92 and the opdata in punched code in a recording -body 12 which can have an extensive width.

It will be understood that the invention is not necessarily limited to use of the particular construction illustrated but includes the use of variants and alternatives within the scope of the invention as defined in the claims.

The invention is claimed as follows:

l. A code punching machine adapted to punch coded data into a Wide sheet of recording paper and comprising, in combination, means delining a punching station, code punching means for punching coded information into a recording sheet in said punching station, two widely spaced sprocket wheels yadapted to simultaneously engage a wide recording sheet to determine the position of the recording sheet with reference to said punching station, a drive shaft connecting said sprocket wheels, a plurality of recording paper support rollers mounted on said shaft, a rotary driving and locating gear connected in driving relation, to said shaft to continuously conform the rotary position of the latter with the rotary position of the gear, a rotary cam shaft, a feed cam on said cam shaft, a feed actuator mounted for swinging movement about the axis of said gear and including a cam follower engaging said feed cam, means continuously biasing said actuator follower into engagement with the feed cam, said feed cam being shaped to effect swinging movement of said actuator between forward and retracted positions with motionless dwelling of the actuator in each of said positions and with smooth acceleration and deceleration of the actuator between said positions, a feed pawl cam on said cam shaft, a feed pawl pivotally mounted on said actuator and including gear teeth adapted to mesh with teeth of said gear, a cam follower on said feed pawl 'biased into engagement with said feed pawl cam, said feed pawl cam being shaped to effect engagement of the feed pawl with said gear during stationary dwelling of said actuator in its retracted position, and to eifect disengagement of the feed pawl from said gear during stationary dwelling of the actuator in its advanced position, a holding pawl cam on said cam shaft, a pivoted holding pawl defining a plurality of teeth thereon adapted to simultaneously engage a plurality of teeth on said gear and including a cam `follower biased into engagement with said holding pawl cam, said holding pawl cam being shaped to effect disengagement of the holding pawl from said gear during stationary dwelling of said actuator in the retracted position thereof and subsequent to engagement of said feed pawl with the gear and to effect engagement of the holding pawl with the gear while said actuator is stationary in its advanced dwelling position and prior to release of the feed pawl from the gear, and each of said cams having a .double lobed construction vwhich eects two complete advancing cycles of said gear for each revolution of said cam shaft.

2. A code punching machine adapted to punch data in code in a recording body and comprising, in combination, means defining a punching station, code punching means for punching information in code ito a recording body in said punching station, recording body driving means adapted to engage a recording body and determine the position of the recording body with reference to said punching station, a rotary driving wheel connected in driving relation to said recording body driving means to vcontinuously determine the position of the latter, a rotary feed cam, a feed actuator including a cam follower continuously engaging said feed cam and being mounted for movement by said feed cam between forward and retracted positions, a rotary feed pawl cam rotated in synchronism with said feed cam, a feed pawl mounted on Vsaid actuator for intermittent engagement with said wheel and including a cam follower continuously engaging said feed pawl cam, said feed pawl cam being shaped to eect driving engagement of the feed pawl with said wheel when said actuator is in its retracted position and to eifect disengagement of the feed pawl from said wheel when said actuator is in its advanced position, a rotary holding pawl cam rotated in synchronism with feed cam and said feed pawl cam, a holding pawl supported for intermittent holding engagement with said wheel and including a cam follower continuously engaging said holding pawl cam, and said holding pawl cam being shaped to effect disengagement of the holding pawl from said wheel when said actuator is in the retracted position thereof and to effect holding engagement of said wheel by said holding pawl when said actuator is in its adv-anced position.

3. In a code perforating machine, the combination of means defining a perforating station, code perforating means for perforating a recording body located in said station, rotary sprocket means adapted to coact with a recording body to determine the position of the body with reference to said perforating station, a rotary driving gear connected in driving relation to said sprocket to determine the rotary position of the latter, a pivoted holding pawl defining a plurality of gear teeth elements thereon adapted to mesh with opposing teeth on said gear, spring means urging said pawl in a direction Vfor engaging said teeth elements thereon with said gear, a rotary cam shaft, a cam on said shaft coacting with a cam follower on said pawl to control engagement and disengagement of the latter with said gear in timed relation to rotation of said shaft, an oscillatory driving element mounted for swinging movement about the axis of said gear, spring means coacting with said driving element to bias the latter rotatably in one direction, a second cam on said cam shaft coacting with a follower on said driving element to effect controlled oscillation of said driving element through an `angle corresponding to desired rotary angles of indexing movement of said gear, a feed pawl pivotally mounted on said driving element and defining a plurality of gear teeth elements adapted to engage opposing teeth on said gear, said feed pawl being biased to urge said gear teeth elements thereon toward engagement with said gear, a third cam on said shaft coacting with a follower on said Ifeed pawl to effect movement of the latter into and out of engagement with said gear in synchronism with rotation of said shaft, said third cam being shaped in relation to said second cam to effect full engagement of said feed pawl with said gear prior to swinging of said driving element in a gear advancing direction and to effect disengagement of said feed pawl from said gear at the completion of gear advancing movement of said driving element and before the driving element is retracted in the opposite direction, and said iirst cam lbeing shaped in relation to said second and third cams to effect engagement of said holding pawl with said gear subsequent to completion of the advancing movement of said driving element and prior to the release of said feed pawl from said gear and to effect disengagement of said holding pawl from said gear subsequent to re-engagement of said feed pawl with said gear and prior to subsequent advancement of said power driving element.

4. A code punching machine adapted to punch coded data into a wide recording body and comprising, in combination, means defining a punching station, code punching means for punching information in code into a recording body in said punchig station, rotary recording body driving means adapted to engage a -wide recording body to determine the position of the recording -body with reference to said punching station, a rotary driving gear connected in driving relation to said driving means to continuously determine the rotary position of the latter, a rotary feed cam, a feed actuator mounted for swinging movement about the axis of said gear and including a cam follower biased -into engagement with said feed cam, said feed cam being shaped to elect swinging movement of said actuator between forward and retracted positions with dwelling of the actuator in each of said positions, a rotary feed pawl cam operated in synchronism with said feed cam, a feed pawl mounted on said actuator for Iintermittent engagement with said gear and including a cam follower biased into engagement with said feed pawl cam, said feed pawl cam being shaped to effect engagement of the feed pawl with said gear during dwelling of the actuator in its retracted position and to eect disengagement of the feed pawl from said gear during dwelling of the actuator in its advanced position, a rotary holding pawl cam operated in synchronism =with said feed cam and said feed pawl cam, a holding pawl supported for intermittent engagement with said gear and including a cam follower biased into engagement with said holding pawl cam, and said holding pawl cam being shaped to effect disengagement of the holding pawl from said gear during dwelling of the actuator in the retracted position thereof and to eect engagement of the holding pawl with the gear while said actuator is dwelling in its advanced position.

5. In a code perforating machine, the combination of means dening a perforating station, code perforating means lfor perforating a recording body located in said station, rotary means adapted to coact with a recording body to determine the position of the body with reference to said perforating station, a rotary driving gear connected in driving relation to said rotary means to determine the rotary position of the latter, a holding pawl movably supported for intermittent engagement with said gear, a rotary power shaft, a rst cam driven by said shaft and coacting with said pawl to effect engagement and disengagement of the latter with said gear, an oscillatory driving element, means including a second cam driven by said shaft and coacting with said driving element to effect controlled oscillation of said driving element, a feed pawl mounted on said driving element for intermittent engagement with said gear, a third cam driven by said shaft and coacting with said feed pawl to effect movement of the latter into and out of driving engagement with said gear in synchronism with rotation of said shaft, said third cam being shaped in relation to said second cam to effect engagement of said feed pawl with said gear prior to advancement of said driving element in a gear advancing direction and to effect disengagement of said feed pawl from the gear at the completion of -gear advancing movement of said driving element, and said first cam being shaped in relation to said second and third cams to effect engagement of said holding pawl with said `gear subsequent to completion of the advancing movement of said driving element and prior to retraction of the driving element and to effect disengagement of said holding pawl from said gear prior to subsequent advancement of said power driving element.

6. In a code perforating machine, the combination of means defining a perforating station, code perforating means for perforating a recording body located in said station, rotary means adapted to coact with a recording body to determine the position of the body with reference to said perforating station, a rotary driving wheel connected in driving relation to said rotary means to determine the rotary position of the latter, a holding pawl movably supported for intermittent engagement with said wheel, a

rotary shaft, a first cam driven by said shaft and coacting with said pawl to effect engagement and disengagement of the' latter ywith respect to said wheel, an oscillatory driving element, means including a second cam driven by said shaft and coacting with said driving element to effect controlled oscillation of the latter, a feed pawl mounted on said driving element for intermittent engagement with said wheel, a third cam driven by said shaft and coacting with said feed pawl to effect movement of the latter intoand out of engagement with said wheel in synchronism with rotation of said shaft, said third cam being shaped in relation to said second cam to effect full engagement of said feed pawl with said wheel prior to advancement of said driving element in a wheel advancing direction and to effect disengagement of said feed pawl from said wheel at the completion of wheel advancing movement of said driving element and before the driving element is retracted in the opposite direction, and said first cam being shaped in relation to said second and third cams to effect engagement of said holding pawl with said wheel subsequent to compietion of the advancing movement of said driving element and prior to the release of said feed pawl from said gear and to effect `disengagement of said holding pawl from said wheel subsequent to re-engagement of said feed pawl with said wheel and prior to subsequent advancement of said power driving element.

7. In a code punching machine adapted to punch data in code in a wide recording body, the combination of means defining a punching station, code punching means for punching information in code into a recordig body in said punchig station, two widely spaced indexing wheels adapted to simultaneously engage a wide recording body to determine the position of the recording body with reference to said punching station, a rotary driving gear connected in driving relation to said indexing wheels, an actuator swingably mounted for oscillation about the axis of said driving gear, a rotary cam shaft, a feed cam on said cam shaft coacting with said actuator and being shaped to effect oscillation of the actuator between advanced and retracted positions and to effect dwelling of the actuator in each of said positions as an incident to rotation of said cam shaft, a feed pawl mounted on said actuator in coacting relation to said gear to transmit to said gear successive advancing movements of said actuator from said retracted position to said advanced position thereof, a holding pawl vmovably supported to intermittently engage said gear in locking relation thereto, and a holding pawl cam on said cam shaft coacting with said holding pawl and being shaped to disengage the holding pawl from said gear during stationary dwelling of said actuator in the retracted position thereof and to re-engage the holding pawl with said gear while said actuator is dwelling in its advanced position.

References Cited in the le of this patent UNITED STATES PATENTS 2,293,077 Potts Aug. 18, 1942

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