US1884743A

US1884743A - Single magnet reperforator

Info

Publication number: US1884743A
Application number: US411122A
Authority: US
Inventors: Edward E Kleinschmidt
Original assignee: Teletype Corp
Current assignee: AT&T Teletype Corp
Priority date: 1929-12-02
Filing date: 1929-12-02
Publication date: 1932-10-25
Anticipated expiration: 1949-10-25

Description

Oct. 25, 1932. E. E. KLEINSCHMIDT,

\ SINGLE MAGNET REPERFORATOR Original Filed Dec. 2,1929 4 Sheets-Sheet 2 'Oct. 25, 1932'.

E. E. KLEINSCHMIDT SINGLE MAGNET REPERFORATOR Original Filed Dec. 2, 1929 4 Sheets-Sheet 5 Oct. 25, 1932. Q E. E. KLKEINSCHMIDT SINGLE MAGNET REPERFORATOR 'Original Filed Dec. 2. 1929 Shh A. Nuhnm l ATTORNEYJ' Nvw Patented Oct. 25, 1932 I UNITED STATES PATENT (OFFICE EDWARD KLEINSCI-IMIDT, OF HIGHLAND PAR-K, ILLINOIS, ASSIGNOR TO TELETYPE CORPORATION, OF CHICAGO, ILLINOIS, A CORPORATION OF DELAWARE SINGLE MAGNET REPERFORATOB Application filed December 2, 1929, Serial No. 411,122. Renewed February 18, 1932.

This invention relates to signalling apparatus and systems in which telegraphic and brings the mechanism to rest ready for a succeedingsignal. .In accordance with my present invention only the selecting signals are perforated, the start and stop pulses being invariably controlled by means independent of the perforations, thereby providing imill).

proved and simplified perforating mecha nism and apparatus.

In recent years, highly eflicient printing" telegraph systems using a single magnet operating 1n response to electrical signals to mechanically and selectively control the recordance with my present invention similar efficient-mechanisms are applied to the receiving perforating devices in a novel manner.

In addition to its utility in printing telegraph systems, my present invention is especially adapted'to the transmission of signals to operate a stock quotation board for example in such a system as shown in my copending application, Serial Number 393,7 61 filed September-19,1929. My invention is also adapted to receive signals from start stop circuits for retransmission on a channel of multiplex signalling circuits, and furthermore forms an important improvement in the art of setting type by telegraph such as shown in my co-pend1ng applications, Serial Numbers 270,848 and 368,641 filed April 18,-1928 and June 5, 1929, respectively.

A primary object of the present invention accordingly is to provide novel tape p'er forating mechanism that may be controlled by electrical signals received over telegraph circuits.

Another object of my invention is to pro-' vide novel tape perforating mechanisms in which one group of holes are being perforated in the tape While the selecting elements are being set in accordance with a succeeding group of signals being received, whereby an overlap is provided.

Still another object of this invention is to provide novel tape perforating mechanisms controlled by a neutral magnet with a spring return armature.

A further object of my invention is to provide novel tape perforating mechanisms controlled by a. olarized magnet.

Two specific preferred embodiments of the invention are herein disclosed, one using a neutralmagnet with spring return armature and the other using a polarized magnet. Further novel objects of the invention, and novel features in the receiving, recording, storing of the signals, and the arrangement of parts, will be pointed out in the following specifieation and claims.

My invention is illustrated in the accompanying drawings in which ceiving device have been developed. In ac- Figure 1 is a plan view of one embodiment of my invention.

Figure 2 is a front elevation of the apparatus shown in Figure 1.

Figure 3 is a vertical section on an enlarged scale with some parts in elevation showuig the selecting mechanism, punch operating mechanism and tape feeding mechanism.

Figure 4 is a view, partly in section and partly in elevation,'of the main drive shaft and the clutch mechanism thereon.

Figure 5 is a detailed sectional view 0 the starting elements.

Figure 6 is a broken fragmental view showing the cam which controls the perforating operation and the cam roller which co-opcrates therewith.

Figure 7 is a fragmentary sectional View showing the feed hole perforating punch and its associated parts.

Figure 8 is a broken detail View of the erating shaft and control magnets of the modified embodiments of my invention.

Figure 11 is a detailed elevational and sectional view of the clutch mechanism of the embodiments shown in Figure 10.

Figure 12 is a similar view of the transfer 3am employed in the embodiment shown in Figure 10.

Figure 13 is a developed view of the pin barrel.

Figure 14 is a vertical sectional view showing the selecting mechanism of the modified form.

Figure 15 is a view partly in plan and partly in section showing the main driving shaft and clutch mechanism and selector mechanism, in the modified embodiment.

Figure 16 is a detailed view of the polarizedmagnet employed in the modified arrangement, as seen from the right end in F igure 10.

Figure 17'is a view showing a transmitter which may be employed in connection with the present invention.

In the form of the invention disclosed in Figures 1, 2 and 3, the mechanism is controlled by a single magnet which may be of any well known construction. As shown more clearly in Figure 3, is the magnet secured to a bracket 11, which in turn is secured to a plate 12. The magnet 10 has an armature 13 which is fixed to a lever 14. The latter is U-shaped in form at its end adjacent the magnet 10 and is connected at this end by a pivot pin to a bracket 16. The

latter is fixed to the plate 12. A spring 17 has one of its ends secured to the armature 13 and its other end secured to an adjusting screw 18 and tends to move the armature 13 into engagement with an adjustable stop screw 19. When the magnet 10 is energized, the armature 13 is held against the head of an adjustable stop screw 20. The stop screws 19 and 20 are mounted, as shown, upon the bracket 16.

The free end of the lever 14 is T-shaped and is provided with a pair of laterally extending arms or abutments 21 and 22, which co-operate with laterally projecting arms 23 and 24 on the rearends of swords 25 to position the latter either in their right or left hand positions as will be described hereinafter. j

The swords 25, of which there are six, are thin flat members separated by thin flat guide plates 26, see Figure 8, which serve to keep the swords 25 in alignment. The guide plates 26 are mounted on studs 27 and are spaced by washers 28 and the studs are fixed to the plate 12. The swords 25 are adapted to go through two different movements, first a reciprocating movement and then a rocking movement, the manner in which these movements are produced and the result thereof will be described hereinafter. Each sword 25 has a knife edge 26' which engages a rockable T- lever 29. The T-levers 29 are pivoted on a shaft 30 and each comprises three

arms

32, 33 and 34. The arm 34 of each T-lever is rounded, as shown,'and engages a notch 35 in a lever 36 which is pivoted at 37 Each lever 36 has at its lower end a knife edge 38 for co-operation with a knife edge 39 on the universal bar 40 which is pivoted at 41. The levers 36 are adapted to be locked in their clockwise position between the knife edge 39 and a stop 42 and in their counterclockwise posit-ion between the knife edge 39 and a stop 43. Pivotally connected to each lever 36 at 44 is an arm 45 which has at its outer end an enlargement 46. The enlargements 46 of arms 45 rest on a lever 47 and, as the levers 36 are rocked about their pivots 37, the enlargements 46 of arms 45 slide back and forth upon the upper surface of the lever 47. When a lever 36 has been rotated to its clockwise position, the enlargement 46 on the associated arm 45 will be positioned directly beneath a punch 48.

The punches 48 are carried in guide plates 49 and 50 and each punch has a shoulder 51 for limiting its downward movement. To maintain the upper faces of the punches 48 normally below the upper surface of guide plate 50 and clear of the material to be perforated, a lever 52 having projections 53, is provided. The lever 52 is pivoted on shaft 54 and has secured thereto at a point 55 intermediate its ends, one end of a spring 56, the other end of which is secured to a fixed point 57. The spring 56 normally pulls the lever 52 downwardly so that the projections 53 on the end of the lever 52 normally maintain the punches 48 in the position shown in Figure 3 with their upper faces below the upper surface of guideplate 50. Disposed above the guide plate 50 and spaced slightly therefrom is a punch plate 58, having a hole corresponding to. each of the punches 48. The tape 59 which is to be perforated is passed between the guide plate 50 and the punch plate 58.

The means for reciprocating the punches comprises an adjustable hammer 60 which is carried by the end of a lever 61. This lever is pivoted at 62 (see Fig. 2) and carries at the end opposite the hammer head 60, a roller 63 (see Fig. 6) which engages the outer surface of a cam 64 mounted on a clutch sleeve which is driven by a suitable source of power as will be described hereinafter.

In addition to the code punches 48 there is provided a feed hole punch (see Fig. 7) which is smaller in diameter than the code punches 48.

Mountedon the outer end of the lever 47 is a roller 72 which engages a cam surface 73 on bell crank 74 which is pivoted at 75. A spring 76 has one of its ends secured to a fixed point 77 and its other end secured at 78 to the bell crank 74, and tends to rock the bell crank 74 in a clockwise direction about its pivot 75 whereby the cam surface 73 is normally held in engagement with the roller 2 7'2. Pivoted to the bell crank 74 at 79 is a spacing'pawl 80. A spring 81 has one of its ends connected to the bell crank 74 at 82 and its other end connected to the spacing pawl at 83. The spring 81 normally tends to rock the spacing vpawl 80 in a counterclockwise direction about its pivot 79 and thereby maintains the spacing pawl in engagement with a tooth on the ratchet wheel 84. Batchet wheel 84 forms part of a revoluble cylinder 85. Cylinder 85 carries a series of pins 86 equally spaced around the circumference of the cylinder and equal in number to the number of teeth on the ratchet wheel 84. Pins 86 are adapted to engage the feed holes in the'tape 59.

Vhen lever 61 moves upward, lever 47 also moves upward and cam roller 72 cooperating with the cam surface 78 rocks the bell crank 74 in a counterclockwise direction, thereby moving the spacing pawl 80 into engagement with the next tooth on the ratchet wheel 84. When the lever 6l moves downward, bell crank 74 under tension of spring 76 rotates clockwise and advances ratchet wheel 84 through an angle corresponding to one tooth and at the same time pins 86 advance the tape 59 through the distance between two successive pins. A ockey roller 87 is held in engagement with the teeth of ratchet wheel 84 by a spring (not shown).

' plied by a motor 101 mounted on the main 7 tion.

frame of the machine. Carried on the shaft 102 of the motor 101 is a speed governor 103 which may be of any well known construe Secured to the other end of the shaft is a worm 104 which engages -a worm gear 105, the latter being rigidly secured to the main driving shaft 106. The shaft 106 is journaled in anti-friction bearings 106v supported in bearing brackets 106" which are secured to the frame of the machine. Mounted upon the shaft 106 are a pin barrel 107 and a clutch member 108, shown in detail in Figures 4and 9 and described hereinafter.

Pin barrel 107 carries a series of projections 110 arranged in a spiral manner, as shown in Figure 9. A plurality of bell cranks 111 is provided, there being one bell crank for each of the projections 110 for co operation therewith. The bell cranks 111 are pivoted on a shaft 112, as shown in Figure 3, and each bell crank has a spring 113 for normally urging it in a clockwise direction; Each spring 113 has one of its ends connected to a bell crank 111 at point 113 and its other end secured to a fixed point 114. Each bell crank has a circular cut out portion or seat 115 for receiving the correspondingly shaped portion 116 of one of the swords 25.

To provide a wide margin of operation, the setting of the swords 25 should take place at definite points of time uniformly spaced throughout the selecting cycle, so that such points may register with the mid portions of the intervals of the received signals or code combinations. It is difiicult, however, to so construct the parts of a mechanical selector as to effect such an operation-and particularly, as is highly desirable in order to permit rapid operation, where the parts are of light weight and the vibratory movement of the armature lever slight. To provide for a wide margin, means is employed for intermittently locking the vibrating armature lever 14 in one or the other of its selectin positions, such locking occurring at delinitely spaced points in the selected cycle and which points are slightly in advance of the time intervals or portions of the cycle during which the setting of the swords 25 is effected.

In the form shown in Figure 3, the locking device comprises a lever pivoted on .the stud 112 and provided with a nose 126 which is continuously pressed into engagement with a cam member 127 that forms part of and rotates with the pin barrel 107. This cam member 127 is provided with a circular series of notches 128, six in number, which successively vibrate the lever 125 during each operating cycle. One end of the lever 125 is provided with a knife edge 129 which co-operates with a knife edge 130, fixed to the underside of the armature lever 14 adjacent its outer end. When the nose 126 of the locking lever 125 is on the high portions of the cam member 127, the knife edge 129 is slightly out of the path of movement of the co-operating knife edge 130 on the vibrating armature lever 14. But when the nose 126 passes over the radial shoulders of the teeth 128, knife edge 129 will engage knife edge 130 and hold the armature lever 14 either in its right hand or left hand position.

The number of teeth 128, in cam member 127, corresponds to the number of selecting intervals of .each signal and they are so spaced that the locking device is quickly shifted into engagement with the armature lever 14 by'the spring 13'1 at definite points in each revolution or setting cycle of the cam member 127 and which points are so arranged that the armature lever 14 is locked in one or the other of its positions just before any engagement of the arms 28 and 24 with the abutments 21 and 22 occurs so that the setting of the respective selectors is definitely determined at such points for briefintervals. Furthermore, the teeth 128 are so arranged that the armature lever 14 .is held against vibration while the arms 23 and 24 of the swords 25 are in engagement with the abutments 21 and 22 and in this way the armature lever 14 is securely held against vibration during any of the changes in the setting of the selectors.

Referring now to Figures 4 and 9 which show the pin barrel and the clutch mechanism, pin barrel 107 is loosely mounted on shaft 106 and at one end has aflange 140. Secured to the end of the shaft 106 is a flange 141 and between the flanges and 141 is a friction washer 142. On the other end of pin barrel 107 is another flange 143 and adjacent thereto is a friction disk 144 and a flange 145 loosely mounted on shaft 106. The flange 145 has a cylindrical extension 147 in which isa slot 148, which'is engaged by a projection 149 fixed to the shaft 106. A spring 150 exerts pressure against all of the parts described above so that when shaft 106 rotates pin barrel 107 also'tends to rotate.

Clutch member 108 is loosely mounted on the shaft 106 and the clutch elements and 161 thereof have slots 162 and 163 respectively. A sleeve 164 is mounted loosely on a sleeve 165 forming a part of the clutch member 108. The sleeve 164 has a projection 166 which engages in the slot 162. At the end opposite projection 166, the sleeve 164 is provided with teeth 167 which are adapted to 'mesh with similar teeth 168 in member 169, the latter member being fixed to the shaft 106. A spring 170 tends to force the teeth 167 into mesh with the teeth 168 and such intermesh will take place except when prevented by the engagement of latching member 171 withlug 172 as will be described hereinafter. Slot 163 is engaged by a projection 175 on the hub of disk 176. Adjacent to the disk 176 is a friction washer 177 and on the other side of the friction disk 177 is a disk 178 fixed to the shaft 106. A spring 180 exerts pressure against disk 17 6, 177 and 178 so that the clutch member 108 tends to rotate wit-h the shaft 106.

The lug 172 is fixed to the sleeve 164 and when it is in engagement with latch 171 as shown in Figure 9, teeth 167 are held out of engagement with the teeth 168. Clutch mem her 108 and clutch member 164 are thus prevented from rotating by the engagement of lug 172 with latch 171. However, as will be described hereinafter, when pin barrel 107 rotates and after all projections 110' have passed their associated bell cranks 111, projection engages member 186 and lever 187 rocks counterclockwise thereby removing latch 171 from engagement with lug 172.

Forming part of the clutch member 108 is a cam member 200, see Figures 1 and 9. Cam member 200 co-operates with a roller 201 carried by an arm 202 which is fixed to the end of a shaft 41. Shaft 41 carries the universal bar 40, see F iguresl and 2. Cam

member 200 rotates with the clutch member 108 and is so timed that knife edge 39 is removed from engagement with knife edges 38 immediately after all of the swords 25 have been set and just before lever 61 begins to rotate clockwise to performthe perforating operation and to prepare the spacing pawl 80 for advancing the tape.

Pin barrel 107 tends to rotate through the friction drive as explained above, but is prevented from rotation when arm 210, which is fixed to the pin barrel, engages the ate.

arm 211. The gate arm 211 is part of a ell crank lever 212'which is pivoted on a pin 213 extending laterally from a fixed support 214. Lever 212 has a tip or projection 215 which is adapted to be engaged by the end 216 of a lever 217 which is provided with a pivot pin 218. The other end of lever 217 is adapted to be engaged by one end of a. bell crank lever 219 having a pivot pin 220. The other end of the bell crank lever 219 engages a pin 221 whichin turn engages an eccentric screw 222 fixed to the armature lever 14 of magnet 10. Normally magnet 10 is energized so that the parts occupy positions as shown-in Figure 9, but when the magnet 10 is deenergized armature 13 rotates under tension of spring 17 in a clockwise direction and through screwhead 222, pin 221, and bell crank lever 219, the lever 217 is rocked in a counterclockwise direction. End 216 of the lever 217 moves out of engagement with end 215 of lever 212 and the pressure of arm 210 against arm 211 (Figure 9) rocks lever 212 counterclockwise storing up energy in spring 223 and permits arm 210 to pass. After arm 210 passes arm 211 spring 223 returns lever 212 in a clockwise direction so that lever 217 under tension of a spring 209, can return to engage projection 215 when magnet 10 is again energized. Bell crank 212 and lever 217 are mounted on a plate 224, see Figure 2, attached to an adjustment arm 225 which can be rotated about the axis of shaft 106. A scale 227 is provided to indicate the position as this adjustment changes the stop position of shaft 106, the function of which will be explained later.

Operation It will be assumed that the motor is running and that the various parts of the machine are stopped in their normal position and that magnet 10 has just been deenergized by a no-current or spacing signal. Armature 13, under tension of spring 17, rotates clockwise and through eccentric screw 222, pin 221 and bell crank 219 the lever 217 moves the tip 216 of lever 217 from engagement with tip 215 of lever 212 and the pressure of arm 210 against arm 211 of bell crank lever 212, due to the friction drive of pin barrel 107, rotates the bell crank lever 212 counterclockwise against the tension of ISO spring 223 and permits the tip of arm 210 to pass the tip of'arm 211 and thereby frees the pin barrel 107 for rotation.

As the pin barrel 107 rotates, the cam member 127 which is fixedto the pin barrel also rotates.

The magnet 10 now responds to the first of the impulse conditions in the code combina tion and its armature lever 14 will assume a position in accordance with the character of this impulse. Immediately after the ar1nature lever 14 has assumed this position, the nose 126 of the locking lever 125 will drop into the first notch in the cam member 127 thereby rocking the lever 125 counterclock- Wise and the knife edge 129 thereon engages the knife edge 130 of armature lever 14 on one side or the other of the knife edge 130, depending upon the position Which has been assumed by the armature lever 14. The engagement between these knife edges effects a locking of the armature lever 14 until the setting of the sword 25 has been completed. Immediately after the locking action, just described, has taken place the first projection 110 on the pin barrel 107 engages its associated bell crank 111 and rocks this-bell crank in a counterclockwise direction thereby reciprocating its associated sword 25 in a manner hereinbefore described, until the arm 23 engages the abutment 21 or the arm 24 engages the abutment 22 as the case may be. The sword 25 is thereby rocked until it engages the pin 117 or pin 118. After the proection 110 has passed the bell crank lever 111, spring 113 will rotate the bell crank lever clockwise and the sword 25 will be reciprocated in the opposite-direction forcing the knife edge 26 thereof against the associated T-lever 29. But T-lever 29 will not rotate at this time due to the fact that the knife edge 39 engages knife edges 38.

It will be noted from the above description that there must be a definite time relationship between the operation of the pin barrel 107 and the incoming signal impulses. This relation is such that the nose 126 of the locking lever 125 is engaged with a notch in the cam member 127 immediately after a signal has been received andis engaged with a portion 128 of the cam member 127 during the interval when a signal is coming in. Since the cam member 127 is fixed to the pin barrel 107, it willjbe evident that there is a definite time relationship between the operation of the levers 125 by the teeth 128 of cam member 127 and the operation of the bell crank 111 by the projections 110 on the pin barrel 107. This relation is such that first a locking of the armature lever 14 by the locking lever 125'takes place and then a reciprocation of a sword member 25 by a bell crank 11 in the direction of the armature lever 14 takes place so that when the arm of the sword 25 engages the lug on the armaturelever 14,

the armature lever 14 is held locked againstmovement.

' As each impulse is received by the magnet the above described operation takes place and the sword member is positioned with its knife edge 26' in engagement with arm 32 or arm 33 of the T-lever 29. After all o f the swords have been so positioned, a pro]ect1on 185 on the pin barrel 107 comes into engagement with the arm 186 of lever 187 and rocks this.

106, the clutch member 108 will rotate with.

the shaft. Spring 170 will move the member 164 towards the member 169 until the teeth 167 engage the teeth 168 but do not intermesh. As clutch member 108 rotates, the

load thereon increases as will appear hereinafter and it will slip with respect to the shaft 106 until the teeth in member 164 are opposite the opening or spacing between the teeth in member 169 and at that moment the member 164 will slide to the left and the teeth of the two members will intermesh so that positive connection will be established between the clutch member 108 and the shaft 106.

As clutch member 108 rotates, the high part of cam 200 engages roller 201 on arm 202 and rotates the knife edge 39 counterclockwise I thereby removing the knife edge 39 from engagement with knife edges 38. Under tension of their individual springs 113, swords 25 rock the T levers 29 which in turn rock.

the levers 36 so that they receive a setting corresponding to the settlng of the swords 25 and corresponding also to the signals just received. At this time the high part of cam 200 has passed the roller 201 so that knife edge 39 returns into engagement with knife edges38. 7

Arms 45 have now been moved so that the enlargements 46 thereon are either directly underneath their associated punches 48 or out of alignment therewith. As clutch member 108 continues to rotate, cam 64 thereon rocks lever 61 clockwise andthrough hammerhead 60 and lever 47, the punches 48 are pushed upward and make the perforations in tape 59. At the same time, lever 47 moves perforating pin 7 0 upward and makes a feed hole perforation in the tape, and roller 72 engages cam surface 73, rocking bell crank74 counterclockwise and causin stepping pawl 80' to engage the next tooth o? ratchet 84. As cam 64 continues to rotate, lever 61 is rocked counterclockwise permitting bell crank lever 74 to rock under tension of spring 76 in a clockwise direction and through pawl 80 advance ratchet wheel 84 and the tape 59 one step, where it is held by the jockey roller 87.

Just prior to any movement of the tape 59 and under tension of spring 56, lever 52 moves counterclockwise and pro ections 53 engage the shoulders 51 on the perforating punches removing the punches from engagement with the tape.

this time a stop "signal is received, ener gi'zing magnet 10 and rocking armature 13 counterclockwise and lever 217 is permitted to move clockwise and when arm 210 engages arm 211, lever 212 is rotated counterclockwise until the end 215 of the lever 212 rests against device will now have been brought to normal position and are ready to receive the next signal. P

It will, of course, be understood that barrel member 107 may be in to rotate to receive the next code combination of impulse conditions as soon as knife edge 39 has moved out of engagement with the knife edges 38 so that the operation of perforating the tape in accordance with one code combination of impulse conditions takes place while the next code combination of impulse conditions is being received.

In the modified form of my invention, shown in Figures 10 to 16, the selector magnet 300 is of a polarized type such as used in stock ticker operations and comprises a permanent U-shaped magnet 301 surrounding the pole pieces 302. Disposed between the pole pieces 302 are the

magnet windings

303 and 304 which are energized in'accordance with impulses received over the signalling line to operate the armature 305. Armature 305 is pivotally supported on the armature bearing 306 in any conventional manner and has a protruding extension 307 formed on one end thereof. The motion of the armature 305 is limited by the adjustable screws 308 carried by the member 309 on the magnet 301 and adapted to separately engagethe opposite sides of the inner end of the armature.

Referring to Figure 10, as the magnet 300 is energized and de-energized' in accordance with marking and spacing impulses received over the signalling line, the extension 307 of armature 305 is moved into and out of the pathof a flutter lever 312. The flutter lever 312 comprises two arms 313 and 314 arranged substantially at right angles to' each other, the outer end of the arm 313 having a stop 315 formed thereon and adapted when the armature 305 is moved to a position as shown in Figure 10, to engage the extension 307 thereof. The flutter lever 312 is pivotally mounted on a pivot pin 316. The other arm 314 of the flutter lever 312 terminates in a bifurcated jaw 317 having extensions or cam followers 318 and 319 thereon, the purpose of which is to be described hereinafter.

In operative relation with the bifurcated jaw 317 is the flutter cam 320 having a plurality of rigidly arranged right and left corrugations having apices such as 321, 322 and 323 formed thereon and disposed at equal distances from the median plane thereof. The apex of ear-h corrugation alternately engages either of the extensions or followers 318 or 319 of the bifurcated jaw 317, and the flutter cam 320 is moved by reason of this engagement as will be described in detail hereinafter.

A second lever 325 is pivotally mounted on the pin 316 and is normally biased in a clockwise direction by a spring 326, one end of which is secured to the lever 325 and the other end to the frame work in any well known manner. Lever 325 is provided with a follower 327 which rides upon a smooth annulus of the flutter cam 320.

The flutter cam 320 is secured to and rotatable with a longitudinally slidable sleeve member or pin barrel 330 which is mounted on the shaft 331 driven by a motor such as motor 101 (Fig. 1) through suitable gear connections. The pin barrel 330 is adapted to be rotated with the shaft 331 in a manner to be described hereinafter.

Normally the spring 326 will urge the lever 325 in a clockwise direction about the pivot pin 316 so that theprojection 327 on the lever 325 engages the surface of the flutter cam 320 as it rotates and forces the pin barrel 330 to its right hand position. As the flutter cam 320 continues to rotate, the followers 319 and 318 are successively engaged by the flutter cam 320. the flutter lever 312 is rocked first clockwise and then counterclockwise about the pivot pin 316. This will be the condition of operation during the spacing impulse intervals when the armature 305 is in its left hand position with its extension 307 out of the path of the stop 315.

pin barrel 330 are forced to the left as the flutter cam rotates. As the flutter cam 320 moves to the left, it rocks the lever 325 countBI'C'lOCkWlSG about its pivot 316 tensioning the spring 326. If during the next impulse interval, a spacing impulse is received, the armature 305 is moved to the left releasing the stop 315 and the spring 326 will thereupon rock the lever 325 clockwise about its pivot 316 and through the follower 327 will move the flutter cam 320 to the right as deandaccordingly uniform tension is applied to the pin barrel 330.

As will be clear to those skilled in the art, all of the movements of the pin barrel 330 are accomplished substantially entirely by power supplied by the motor driving the pin arrel; that is, not only is the power for rotating the pin barrel supplied from this original source, but due.to the shaping of the flutter cam 320, the rotary movement is translated' into a reciprocatory movement for shifting the pin barrel to the right or left, although this movement is controlled by the line magnet. Except, therefore, for releas ing the clutch in response to a start impulse there is a minimum requirement of power from the line magnet, the sole requirement of the line magnet during the signalling period being to move the armature 305 which is free from any incumbrance as in the case of a relay. The receiving line magnet may therefore be of a very delicate structure responsive to very small currents and having a minimum of inertia, and may operate at very high speed. Inasmuch as the local source of power supply may be of any value, within practical limits, the pin barrel 330 may rotate and move longitudinally at a very high speed.

It will, of course, be understood that the pin barrel is rotated at a speed which is in synchronism with the speed of code impulsmg, each impulse being received while the right hand corrugatlon 321 is engaglng the follower 319 and tending to rock the flutter lever 312 in a clockwise direction.

In order to insure synchronous operation, the pin barrel 330 is rotated on the start-stop I principle, the start and stop impulses condescri ed hereinafter. f -The engagement of the stop arm 331' with the stop lug 332 occurs only when the pin barrel 330 is in its left hand position. This condition is obtained when the pin barrel, having rotated to a position at which; stop arm 331 engages lug 332, the

marking impulse is being received. In re-' sponse to a marking impulse at this time,

armature 305 has been moved to its right hand. position and as the flutter lever 312 is rocked clockwise by the right hand apex 321 engaging the follower 319, the armature 305 and flutter lever 312 engage, as described above, and the flutter cam 320 is moved to its left, shifting the pin barrel 330 in a similar direction and then the stop arm 331' engages the stop lug 332. Engagement of these two prevents rotation of the pin barrel farther, as will be described. This is the normal stop condition. A received spacing impulse will rock the armature 305 to the left releasing thereby the flutter lever 312. Spring 326 now moves the lever 325 and through flutter cam 320 shifts pin barrel 330 to the right withdrawing stop arm 331' from engage ment with the stop lug 332' The pin barrel 330 is now rotated by moto 101 as will now be described. As shown in Figure 15, the pin barrel 330 is loosely mounted on the main shaft 331 which is rotatably mounted in anti-friction bearings 335, only one of which is shown in Figure 15. These bearings are supported on the frame of the machine in any well known manner.

.Mounted on the shaft 331 between the antifriction bearing 335 and the pin barrel 330 is a friction clutch 336 comprisinga flanged sleeve member 337 keyed to the shaft 331 in any well known manner, the flanged portion of the sleeve member'337 being adjacent the pin barrel 330. Rotatably mounted on the sleeve member 337 is a drive disk 338 and a plate 339 between which a friction member 340 as for example, a felt disk is placed. A similar friction member 340 is positioned between the drive disk'338 and the flanged portion of the sleeve member 337. The plate 339 is engaged by the slit annularv spring 341 which presses against another disk 342 in threaded engagement with the end of the sleeve member 337 and held in position by means of the lock nut 343, the tension of the spring 341 being adjustable by the threaded disk 342. I

As will now be clear the friction mechanism may be removed as a unit without altering the adjustment. The drive disk 338 which is driven by the motor through the shaft 331 and flanged sleeve 337, at all times is in operative relation with the pin barrel 330 through the medium of the stop arm 331. lVhen the, pin barrel 330 is in its left hand position, as described above, the stop arm 331 comes into engagement with the sto lug332 and as a result the drive disk 338 will siip with respect to the rotating sleeve member 337 and the pin barrel is stationary. Stop arm 331' has a horizontal portion which passes through a slot 338 in drive disk 338 so that when this disk rotates. the pin barrel 330 rotates with it. p i

In response to a start impulse, pin barrel 330 is moved to the right, as described above,

and the stop arm 331' is moved out of engagement with the stoplug 332. Pin barrel 330 is thereupon rotatively driven through clutch 336. In this manner the transmission of a starting or spacing impulse starts the pin barrel revolving.

The speed of rotation of the pin barrel 330 is such that when the transmitting distributor has revolved a suflicient distance to transmit the first impulse, the pin barrel revolves to a proper position to receive it. When the transmitter has revolved to a position to send out the pin barrel has made a complete revolution and stop arm 331' is in operative relation with stop lug 332, and when the drum is moved to the left, the two engage bringing the drum to a stop.

In the present case, the pin barrel 330 is geared to rotate one-twelfth faster than the transmitter, but it is so constructed that the distance from the position where it can receive one impulse and where it can receive the next impulse is one-twelfth greater than the distance where the transmitting distributor can send one itself and the next. This difierence in speed between the pin barrel 330 and the transmitting distributor is provided in order to insure that the pin barrel will return to its normal stop position before the transmitting distributor. As will be noted from the above description, the transmitting distributor transmits the start impulse to control the starting of the pin barrel. Accordingly if the pin barrel should reach its normal position after the transmission of the start impulse and after the transmitting distributor has started rotating the pin barrel would come to a stop as it would not at that instant receive the start impulse. Thus, it is essential that the pin barrel reach its normal position before the transmitting distributor in order that it may be in condition to receive an impulse.

One alternative would be to maintain the two units at exactly the same speed which in practice has been found to be undesirable as in a short time even a slight difference would cause the transmitting distributor and receiving mechanism to fall out of step so that when the transmitting distributor was sending out the first impulse of a code combination, the

. p n barrel might be in a position to receive the second impulse. By rotating the pin barrel slightly faster than the transmitting distributor, the former completes its revolution somewhat sooner than the transmitting distributor. Inorder to correct for this difference in speed, the selecting positions of the pin barrel are spread further apart than are the transmitting positions of the distributor; thus, if the transmitting, distributor travels 45 degrees from the first'to the second transmitting position, the pin barrel is arranged to travel 48 degrees in travelling from the first to the second position. Inasmuch, however, as the pin barrel travels one-twelfth faster, it will reach its second selecting position at the same time that the transmitting distributor reaches its second position.

When the pin barrel has completed a revolution, it comes to a stop until the transmitting distributor again sends out a start impulse. Should the speed of the pin barrel be slightly faster than the proper speed, the a only effect will be that it will remain at rest slightly longer. Although there will be a slight error in each selecting position, the mechanism is so constructed as to provide for this and due to the fact that the pin barrel starts each revolution in unison with the transmitting distributor this error never becomes very large.

It will be clear that the relative position of the pin barrel 330 with respect to the received signals is very important inasmuch as the pin barrel must be at a position such that the stop arm 331' engages stop lug 332 before the start signal is received and must be in proper position to receive the code impulses. This is, in part, taken care of by adjusting the speed of rotation. It is, however, also important to start the rotation at a predetermined position of the pin barrel 330.

To this end, an orientation plate 345 having a scale is mounted on brackets, not shown. and carries the stop lug 332 directl behind the friction clutch 336. The plate 3 5 is provided with a slot and screw adjusting means 346 whereby the plate 345 may be adjusted to move the stop lug 332 into different positions. To take an orientation range, a test sentence such as The quick brown fox, etc., is transmitted to the perforator continually while the range is being taken. While this sentence is being received by the perforator, the orientation scale plate 345 is shifted by the adjusting means 346 toward zero until errors begin to appear in the test sentence.

.Then it is moved back slowly until these errors disappear. This position indicates one limit of the orientation range. The same performance is repeated toward the opposite end of the scale and the other limit is found. After the two limits or extreme positions of perfect perforating have been found, the orientation scale is set midway between these two points.

The pin barrel 330 comprises a hollow cyl- III inder with twelve selector cams 350 projecting from its outer surface. Six of these cams are marking cams and six are spacing cams. Associated with each pair of selector cams 350, that is, a pair comprising a spacing and a marking selector cam, is one of six selector levers 351, Figure 15, pivotally mounted on a shaft 352, Figure 14, suitably carried by the frame of the machine. Each of said levers 351 comprises arms 353 and 354 located respectively on diametrically opposite sides of pin barrel 330. The ends of the arms 353 and 354 are ofiset with respect to each other, the marking arm 354 being offset in one direction and the spacing arm 353 being offset in the other direction. This is done so that when the marking cam associated with a particular selector lever lines up with the marking arm, the spacing arm will pass to the rear of the spacing cam individual thereto and when a spacing cam is in line with the spacing arm, a marking cam will pass to the front of the marking arm.

Accordingly, in response to a marking impulse, the pin barrel 330 is moved to the left as described above, the marking arm 354 of the selector lever 351 will be engaged by the associated marking cam 350 and the spacing cam will pass by the spacing arm 353. As a result of the engagement of the cam 350 with arm 354, the selector 351 rocks about its pivot in a counterclockwise direction.

On the other hand, in response to a spacing impulse, pin barrel 330 will be moved to the righthand position, as described above, and the cam associated with the selector lever 351 will engage the arm 353 rocking the lever 351 in a clockwise direction about the. pivot 352. In this manner the selector levers 351 are set in one or the other position in accordance with the received code. As will be described more fully hereinafter, the first five selectors are operated in accordance with code combinations of impulses to make a selection. A sixth selector may also be provided operating in response to a sixth or shift pulse to select a case shift character.

The selector levers 351 are carried in a selector lever unit or guide 355 located to one side of the pin barrel 330 which functions to hold the selector levers in position so that they can be moved to either their spacing or marking position by the selector cams 350 as described above. The selector levers are mounted in slots 356 in the guide 355, Figure 14.

The selector levers 351, it will be noted, have no normal position but remain set in either operated position until the impulse in a succeeding code is such as to shift them to the opposite position. Inasmuch as they have no normal position, very little power is necessary to operate them and the number of oper- In order to insure against accidental movement of the selector levers to their alternate position, a latching means is provided as shown in Figure 14. This latching means comprises jockeys 357 pivotally mounted on a pin 358 and each normally urged about the pivot 358 by a compression spring 359. A projection 360 on the jockey 357 engages the edge of the associated selector lever in one position and the top of the lever in the opposite position. A jockey such as shown in Figure 14 is provided for each of the selector levers and is individual thereto. With the selector lever 351 in the position shown in Figure 14, the extension 360 on the jockey 357 engages the edge of the selector lever 351 and maintains the selector lever in the position shown. In the event, however, that the selector lever is operated to its alternate position, the selector lever as it moves will rock the jockey 357 about its pivot 358 in a counterclockwise direction compressing the spring 359 until projection 360 moves over the edge of the selector lever 351, whereupon jockey 357 will be rocked clockwise by action of its 1 spring 359'to press against. the top of the selector lever 351 and maintain it in its new position. Similarly when the selector lever 351 is rocked to the position shown in figure 14 it will raise the jockey 357 compressing the spring 359 until its edge passes over the left edge of the projection 360 to the side, as shown, and whereupon the compression spring 359 again rocks the jockey 357 in a clockwise direction and the projection 360 engages the edge of the projection of the selector lever 351. v In this manner, the selector levers are each held in their operated position immediately after their operation.

Each of the selector levers 351 is provided with apair of diverging arms 361 and 362 adapted to operably engage the

projections

363 and 364, respectively, of a transfer T-lever 365 associated with each selector lever 351. Each transfer T-lever 365 is in alignment with its associated selector lever and is pivotally mounted on a pivot shaft 366 carried by a pair of transfer arms'367 rigidly mounted on the shaft 368, pivotally attached to the machine. Transfer power arm 367' also is fixed rigidly upon the rocking shaft 368 and is provided with a roller or cam follower 369 (Fig. 12) which is in operative relation with a cam groove 370 in a main or operating cam 371.

The main or operating cam 371 is mounted on the main shaft 331 for rotatable movement with respect thereto and between the bearing brackets of the shaft 331. The cam 371 IS driven by a friction clutch 3T5 positioned on the main shaft 331 and to the right of the cam 371, the friction clutch being substantially identical with the friction clutch 336,

described in detail above, and comprising the sleeve and flange 376, the friction plate 377, a drive disk 378, a pair of friction disks 37 9, an annular spring 380, an adjustable plate 381 and a lock nut 382, the whole being assembled in the same manner as described above for the friction clutch'336, the flange and sleeve 376 being pinned or keyed to the main shaft 331 in any desired manner.

I The operating cam 371 is driven by the friction clutch 375 through a suitable pin connection 383 positioned between the operating cam 371 and drive disk 378. During predetermined periods in the operation, the drive disk 37 8 is held against rotation and cam 371 is therefore stationary. To this. end, the drive disk 378 has formed on its periphery, adjacent the pin connection, a stop lug 384 adapted to be engaged by a bail 385 at a certain interval in the cycle of operation of the perforator. The shift bail 385 is pivotally mounted loosely on transfer bail shaft 368 and is provided with a'roller or cam follower 386 adapted to engage the periphery of the drive disk 338 fOI'IIIIII part of ,clutch 336. A' spring 387 constantly urges the follower 386 against disk 338. Whenthe clutch 336 has been released and rotated over a predetermined distance, the follower 386 riding on drive disk 338, rocks the bail 385, moving the bail out of engagement with the stop lug 384.

With the trip bail 385 engaging the stop lug 384, the drive disk378 will be prevented from turning and will slip with respect to the shaft 331 which is constantly rotating and accordingly the operating cam 371 will not be rotating. When the trip bail 385 disengages the stop lug 384, the clutch will be released to rotate the operating cam 371.

Slidably mounted on the main shaft 331 and to the left'of the operating cam 371 is a sleeve member 390 operablyconnected to the hub of the operating cam 371 by means of interengaging tooth members 391 shown in Figure 15. The sleeve member 390 comprises the sliding element of a tooth or grab clutch 392, the fixed portion 393 of which is secured to the main shaft 331.

Formed on the sleeve member 390 is a flange 394 having an inner cam surface 394 .adapted to engage a fixed cam follower 395. The sleeve member 390 being normally held to the right out of engagement with the fixed member 393 against the tension of a coil spring 396 positioned between the sleeve member 390 and the operating cam 371. The initial movement of the operating cam 371 and A sleeve member 390, as described above, rotates flange 394 until the cam follower 395 rides over the shoulder of the cam and the sleeve member 390 is moved to the left by action of spring 396 engaging fixed member 393 on the main shaft 331. In this manner, the main or operating cam 371 is started slowly at first from power through the friction clutch 37 5 engages.

and after a short initial movement is directly and positively coupled to the drive shaft through the grab clutch. In this manner, the advantages of a positive grab clutch connection for transferring power are obtained while at the same time, the shock or jar due to sudden starting'by engagement of the teeth of such a clutch is obviated through the use of the friction clutch 375. In operation, the friction clutch 375 when released, as described above, starts the rotation of

cams

371 and 394. After cam 394 has rotated a few degrees, the grab clutch 392 engages and carries the

cams

370 and 394 nearly to the end of the revolutionwhen follower 395 rides over the shoulder of cam 394 forcing the sleeve member 390 to the right against the action of spring 396 and the sleeve member 390 dis- The friction clutch 375 continues to drive the main or operating cam 371 for the small remainder of the revolution until it is stopped by the stop lug .384 on the drive I disk 378 of the clutch 37 5 striking against the cam release trip bail 385.

As the main earn 371 rotates, the transfer arm roller 369 rides in the cam groove 370 and moves the power arm 367, the rock shaft 368, the arms 367 and transfer levers 365 carried thereon forward toward theselector levers 351 and as the roller reaches the peak of the cam groove, the transfer levers 365 are forced against their individual selector levers 351. As the transfer levers 365 engage selector levers 351 the former will be rocked about their pivot 366 in either a clockwise or counterclockwise direction, depending on the set ting of the selector levers 351. If a selector lever 351, for example, has been rocked clockwise in response to a marking setting of selector cam 350 the arm 363 will engage the extension 361, rocking the transfer lever 365 counterclockwise as the transfer lever is moved toward the selector lever 351.

Each of the transfer levers 365 is provided with a head 400 projecting into a slot 401 of an individual punch selector lever 402.

As each of the transfer levers 365 is rocked about its pivot 366, as described above, it will in turn move the head 400 moving the associated lever 402 to either of its two operative positions. If the transfer lever 365 is rocked clockwise, it will rotate its associated lever 402 counterclockwise; if lever 365 is rocked counterclockwise it will rotate lever 402 clockwise.

It will be noted from the description thus far given that although the selector pin barrel 330 is operated successively, the code impulses are'received and in turn successively position the selectors 351, the transfer operation for setting the levers 402 takes place in a single operation as a result of the movement of the transfer levers 365 by the transfer arms 367 operated by the main cam 371.

As soon as this transfer has taken place, the a selector levers'351 are free for reoperation in accordance with a new permutation while the levers 402 selectively control the operation of the perforating mechanism as will now be described.

It will also be noted that the selector le vers 351 and 402 have no normal position but are rocked to their marking or spacing position in accordance with each received code so that in the event the selector lovers are already in the position in which the code impulse is to operate them, no operation is necessary, thereby reducing the number of selector operations. Due to the pivotal arrangement of these members and the absence of means tending to return them to a normal position it will also be clear that little power is necessary for performing the operations thereof to either marking or spacing position.

The levers 402 are similar in shape to the levers 36 of the form of the invention shown in Figures 1, 2 and 3. Each lever 402 is pivoted at 403 and has at its lower end a knife edge 404 in cooperation with a knife edge 405 on a locking bar 406 which is pivoted at 407; A spring 408 normally tends to maintain the knife edge 405 of the locking bar 406 in engagement with the knife edge 404 of the associated lever 402 so as to lock the lever 402 in the position to which it has been moved by its transfer lever 365. Pivotally connected to the lever 402 at 409 is an arm 410 which has an enlargement 411. The arms 410 are similar to the arms 45 in the form of the invention previously described and the enlargements 411 thereof are adapted to co-operate with punches 412 in the same manner as described in connection with the other form of the invention.

Operation The operation of the modified form of the invention shown in Figures 10 to 16 will now be described. Assuming that a code is received comprising a start impulse which is always spacing and a code comprising marking, spacing, marking, spacing and spacing impulses for the first five impulses and a spacing for the sixth impulse.

As already explained, the stop condition is a marking impulse. The armature 305 is to the right, 307 stops the flutter lever 312, the jaw 317 spans a right apex of the flutter cam 320, and the pin barrel 330 is to the left. Stop arm 331 and lug 332 are in engagement and the clutch 336 is therefore sl pping as the motor rotates the sleeve 337. In response to a spacing or start impulse, the armature 305 is moved to its left hand posi tion and out of the path of the flutter lever 312, thus unlocking the flutter lever'3l2, the flutter cam 320.and the spring arm 325, and permiting the sprin 326 to move the pin barrel 330 toward the right. As a result of this longitudinal movement of the pin barrel, the stop arm 331' disengages itself from the stop lug 332 and initiates the rotation of the pin barrel 330. At this instant the e tension 318 is opposite the right apex 321. During the next movement the extension 318 is engaged by left apex 322 and lever 312 rocks counterclockwise until the stop 315 is out of the path of the armature 305.

The first code impulse, being a marking impulse, the armature 305 is moved to the marking or right hand position which it is now free to do as the stop 315 is out of its path. As the flutter cam 320 continues to rotate, extension 319 is engaged by a right apex 323 and tends to rockthe flutter lever 312 clockwise. The flutter lever 312 is, however, blocked by the stop 307 on the armature 305 and accordingly the flutter cam 320 is operated to the left as it rotates. As a result, the marking cam 350 on the drum will be moved into line with the marking arm of the first selector lever 351 andwill move this lever to marking position as the pin bar rel 330 rotates.

The succeeding left apex passes into the jaw 317, the in barrel 330 moves to the right and the. utter lever 312 rocks counterclockwise until the fiutter stop 315 disengages from the armature stop 307. The second pulse of the currently received code being a spacing pulse, the armature 305 is moved to the spacing or left position and the path of the flutter stop 315 thus is cleared. The succeeding right apex passes into the jaw 317, the flutter lever moves and the pin barrel does not slide. The second spacing cam 350 thus remains in line with the second selector lever 351 and as the pin barrel rotates the second selector lever 351 will be moved to the spacing position. This operation is repeated during the third, fourth, and fifth impulses of this code in the same manner.

The sixth impulse is a spacing impulse, consequently the sixth selector lever 351 is moved to its spacing position as described. After the reception of the sixth selecting impulse, the stop impulse is'received. As this impulse is always marking, the armature 305 is moved into the path of the flutter lever 312 and pin barrel 330 is moved to the left. At this point in the rotation, the stop arm 331 strikes against the stop lug 332 and the pin barrel 330 is held at rest until the reception of the next start impulse.

During the rotation of the pin barrel 330 and after the reception of the fourth impulse, the roller 386 of the cam release or trip bail 385 rides in a depression in the edge of the friction disk 338. Through the act on of spring 387 this roller follows the depression in the cam 338 and the bail 385 is rocked until it disengages the stop 384 and the operating cam 371 is released. The operating cam 371 starts to rotate shortly after the reception of the fifth impulse and through mechanism not shown, operates the perforating punches.

However, the character perforated will not be the one just selected, but one selected by l a previous rotation of the pin barrel as explained above. Following the sixth impulse, the operating cam 371 has moved into a position at which it operates transfer bail 367 and the combination set up in the selector levers 351 will be transferred to the levers 402. The selector pin barrel 330 may at this time be at rest as described above or started into rotation again by a start impulse of the succeeding code. The operating cam, however, continues to rotate operating the tape feeding mechanism for advancing the tape to present a new space for perforation. Thereafter the cam is stopped as stop 384 engages the stop arm of the bail 385.

Perforation of the character for the code, the selection of which has just been described, does not take place until the next selection is received and the pin barrel has revolved far enough to release the operating cam 371.

It will be seen from the above description that a character code which is selected during one revolution of the cam drum or pin barrel is not punched until another revolution of the pin barrel. In other words, while one character is being selected, the preceding character code is being perforated. A complete overlap ofthe apparatus is thus provided and the perforator'is operating at all times by utilizing the full line time available while the code is being received.

One form of the transmitter for transmit ting the code combinations of impulse conditions under the control of a perforated tape to a receiving station having a reper-'- forating device, such as of either of the forms above described, is illustrated in Figure 17 v and will now be described.

Transmitter A motor 425 drives a shaft 426 having thereon a speed governor 427 and a friction mechanism comprising disks 428 and 429 having adjacent thereto friction disks 430 and 431, respectively. Loosely mounted on the shaft 426 between the friction disks is a gear wheel 432 and an arm 433, the purpose of which will be described hereinafter. The shaft 426'has a shoulder 434', and a spring 435, positioned between the shoulder 434 and the friction mechanism, continually exerts a pressure against the friction mechanism whereby gear wheel 432 and arm 433 normally tend to rotate with the shaft 426. Such rotation ll take place except when 60 the arm 433 is prevented from rotating by a means to be described.

i The gear 432 is in mesh with a gear 436 fixed to a shaft 437 which carries a cam 438, the purpose of which will be described hereinafter. The arm 433 carries two brushes 440 and 441 which are electrically connected to each other. The brush 440 wipes over a distributor ring 443 comprising eight segments and the brush 441 wipes over a slip ring 444.

For controlling the rotation of the arm 433, a stop arm 445 is provided, the stop arm 445 forming the armature of a magnet 446 and being pivoted at 447 to the supporting member 448 of the magnet. A spring449 normally tends to movethe stop arm 445 into" the path of movement of the arm 433. Energization of the magnet 446 over a circuit from positive battery, through resistance 450, windingof magnet 446, switch 451 in its closed position, to negative battery, moves the armature 445 out of the path of the arm 433 against the tension of the spring 449. This releases the arm 443 for rotation and the arm will be rotated by the shaft 35 426 through the frictional drite above described.

As shown in Figure 17, the positive source 455 is connected to a plurality of contacts 455 and the negative source 456 is connected to a plurality of contacts 456, the latter contacts being associated with the contacts 455. As shown, these contacts are arranged in pairs, each pair comprising a lower contact 455 and an upper contact 456 and between each pair of contacts is a switch arm 457 which is secured to a feeler lever 458 pivoted at 459 and having a feeler pin 460. Positioned above all of these feeler levers 458 is a depresser rod 461 which is operable by a lever 462 pivoted at 463. The lever 462 is operable by the cam 438 which, as described above, is connected to the shaft 437. A spring 464 normally maintains the lever 462 in engagement with the cam 438. The feeler pins 460 are adapted to co-operate with the perforations in the tape 456 which is fed by, the pins 466 on the feed wheel 467. The feed wheel 467 is mounted on a shaft 468 which has mounted thereon a ratchet wheel 469 adapted to be operated by a pawl 470 pivoted at 471 on the end of a lever 472. The lever 472 is pivoted at 473 and has connected thereto the rod 461, as shown.

The conductor which leads from the first segment of the segmented ring 443 is con nected to the positive source 455'. The conductor which leads from the second segment is connectedto negative source 456. The sources 455 and 456' are grounded as shown. The remaining six segments are connected respectively to the feeler levers 458. Connected to the slip ring 444 is the line-475 which leads to the receiving station. The perforated tape 465 is placed in the transmitter with the row of guide holes en aging the pins 466 on the feed wheel 467. gwitch 451 is then closed energizing magnet 446 and attracting armature 445. Armature 445 rotates about its pivot 447 and moves out of 130 into the perforation.

the path of the brush arm 433 releasing the brush arm for rotation. Brush arm 433 begins to rotate through the friction mechanism driven by the motor 425 and simultaneously cam 438 begins to rotate through the gear connections 432 and 436. When the brush 440 reaches the second segment of the distributor ring 443, the negative polarit from the source 456 is connected throng brushes 440 and 441, slip ring 444 and over a the line 475 to the receiving station.

When brush 440 reaches the third segment of the distributor ring 443, the high part of cam 438 will have moved away from the lever 462, permitting the spring 464 to rotate the lever 462 in a counterclockwise direction thereby raising the rod 461 so as to permit the feeler levers 458 to rotate in a counterclockwise direction under the influence of individual springs associated therewith. When the feeler pin 460 of the first feeler lever 458 comes into engagement with the tape, if there is a perforation in the tape at the first position of the code combination of perforations, the feeler lever 458 will be rocked counterclockwise and the feeler pin 460 will move As the feeler lever 458 rocks counterclockwise, its switch arm 457 comes into engagement with its associated upper contact 456 and a negative impulse will be transmitted over the line 475 from source 456 through contact 456, switch arm 457, first feeler lever 458, third segment of the ring 443, brush 440, brush 441, slip ring 444, and over the line 475 to the-receiving station. If, however, there is no perforation in the tape at the first position of the code combination of perforations, the first feeler lever 458' will be prevented from rotating counterclockwise and its switch arm 457 will remain in engagement with its associated lower contact 455. In this event, a positive impulse will be transmitted from source 455 through lower contact 455, switch arm 457, first feeler lever 458, third segment of the ring 443, brush 440, brush 441, slip ring 444 and over the line 475 to the receiving station.

\Vhen the brush 440 reaches the fourth segment on the ring 443, a negative or positive impulse will be transmitted over the line 475 depending upon whether the tape was perforated at the secondposition, or not. As above described, if the tape is perforated at the second position, the secondfeeler lever 458. will i be rocked counterclockwise and a negative impulse will be transmitted, and, if the tape is not perforated, the second feeler lever 458 will not be rocked and switch a'rm 457 will remain in engagement with its lower contact 455 and a positive impulse will be transmitted. The operation for the remaining segments is the same as that just described.

When the lever 462, rotates in a counterclockwise direction, the lever 472 also rotates in a counterclockwise direction and the pawl 470 moves into engagement with the next tooth on the ratchet wheel 469. When brush 440 again reaches the first segment of the distributor ring 443, the high part of cam 438 engages the lever 462 and rocks the same in a clockwise direction, thereby forcing the rod 461 against all of the feeler levers 458 which have been rotated to their counterclockwise position and returns them to their clockwise position. At the same time the pawl 470 moves downward and advances the tape one step.

I claim:

1. In a perforating device, a series of punches, a series of selectors, one directly associated with each punch and means comprising a single magnet responsive to electrical impulse conditions for controlling the setting of said selectors.

2. In combination, a plurality of punches, a plurality of punch control members, a plurality of selector members, means comprising a single magnet for setting the selector members in accordance with a code combination of electrical impulse conditions, means for transferring the setting of the selectors to the punchcontrol members and means for operating said punch control members while said sel tor setting means is operating in respouse to a new code combination of impulse conditions.

,3. In combination, a plurality of selector elements having no normal position, said elements being subject to a reciprocating motion and a rocking motion, means responsive to electrical impulse conditions for determining the direction of rocking movements of said selector members and perforating mechanism operated in accordance with the setting of said selectors.

' 4. In combination, a plurality of punches,

a punch control element associated with each tions.

5. In a perforating mechanism, a plurality of punches, a punch bar associated with each punch, a selector element for each punch bar, means responsive to electrical impulses for controlling the setting of the selector elements in accordance with a received code combination of electrical impulses and means for temporarily locking said last mentioned means.

i to said punch control elements and subsequently locking said punch control elements.

7. In combination, a constantly rotating member, a member to be driven by said constantly rotating member, a frictional connection between the two members and means for locking the second mentioned member against rotation, said last mentioned means compris- Iiang a plurality of pivotally mounted memers.

8. In combination, a rotatable member, a locking lever adapted to engage the rotatable member for preventing rotation thereof, a second lever adapted to engage the first lever for locking the same and means for controlling the second lever.

9. A locking means comprising a pivotally mounted lever, one end of which is adapted to engage the member to be locked, a second lever, one end of the second lever being adapted to engage the other end of the first lever and means for controlling the second lever.

10. A locking means comprising a bell crank lever, one end'of which is adapted to engage the member to be locked and means cooperating with the other end of said bell crank lever for preventing rotation thereof.

11. In combination with a member to be locked, a locking lever having one end adapted to engage said member, said member tending to rock said locking'lever, and a second lever for locking the first lever against rocking movement.

12. In a perforating mechanism, a plurality of punches, each punch having associat ed therewith a punch bar, means for setting said punch bars in predetermined positions in accordance with a code combination of electrical impulse conditions, means for lock-.

ing said punch bars in the position to which they have been set, means for operating said punch bars into engagement with said punches and cam controlled means for controlling said last mentioned means.

13. In a perforating mechanism, a plurality of punches, a punch operating bar for each punch, a selector lever for each of said bars, means for intermittently reciprocating said selector levers, an abutment in the path of said selector levers, said abutment being adapted to occupy one of two positions, an electro-magnet for controlling the position of said abutment, said selector members being adapted to come into contact with said abutment member and rocked in one direction or another, depending upon the position of the abutment member and means for transferring the setting of the selector levers to the punch operating bars.

14. In a perforating mechanism, a pin barrel selector, marking and spacing cams on said pin barrel selector, selector levers, one for each pair of marking and spacing cams, said selector levers being arranged to be operated by their associated pairs of cams in accordance with the operation of the pin barrel selector as said members come into opposed relation with said selectors, punch bars and means for transferring the setting of said selector lovers to said punch bars. I

15. In combination, a plurality of punches, each punch having associated therewith a punch bar, a punch bar operating lever, a transfer lever and a selector lever, means for setting the selector bars in predetermined position in accordance with a code combination of electrical impulse conditions, means for transferring the setting of the selector levers to the punch bars, the transfer operations taking place through the transfer levers and the punch bar operating lever, means for locking the punch bars in the position to which they have been moved and means for pressing the punch bars into engagement with the punches for perforating a tape.

16. In combination, a rotatable member having a plurality of marking and spacing cams thereon, a selector lever associated with each pair of marking and spacing cams, each of said selector levers being provided with projections offset from each other whereby with said rotatable member in one position, one projection will be in engagement with the marking cam while the other is out of engagement with the spacing cam, and with the rotatable member in the other of its positions, the other projection is in engagement with the spacing cam and the first is in engagement with the marking cam, means whereby said levers are operated in accordance with. the longitudinal position of said rotatable member, a second marking and second spacing projection on each of said selector levers, a set of transfer levers, one for each of said selector levers operated by either said marking or said spacing projections depending on the operated position of said selected levers," an operating cam, a second set of selector levers in operative relation with said transfer levers, means controlled by said operating cam for variably operating said transfer levers in accordance with the operation ofsaid first mentioned selector levers whereby said second set of selector levers are operated in accordance with the operation of said first mentioned selector levers, a plurality of punches, each punch having associated therewith a punch bar and each punch bar being connected with one of the selector levers of the second set, 'a hammer for forcing the punch bars into engagement with thepunches and means for operating said hammeratpredetermined time intervals.

17 In combination, a rotatable member having a plurality of marking and spacing cams thereon, a selector lever associated with each pair of marking and spacing cams, each of said selector levers being provided with projections offset from each other whereby when said rotatable member is in one position, one projection will be in engagement with marking cam while the other is out of engagement with the spacing cam and when the rotatable member is in the other of its positions the other projection is in engagement with the spacing cam and the first projection is out of engagement with the marking cam whereby said levers are operated in accordance with the longitudinal position of said rotatable member, a second marking and second spacing projection on each of said selector levers, a set of transfer levers, one for each of said selector levers operated by either said marking or said spacing projection, depending upon the operated position of the selector levers, an operating cam, a second set of selector levers in operative relation with said transfer levers, a plurality of punch bars, one for each of the selector levers of the second set, a plurality of punches, one for each punch bar, means controlled by said operating cam for variably operating said transfer levers in accordance with the operation of said first mentioned selector levers whereby said second set of selector levers are operated in accordance with the operation of the first mentioned selector levers, and a hammer cooperatively associated with said punch bars, said hammer being controlled by said operating cam.

18. Incombination, a rotating selector, a first set of selector levers, variably operated in accordance with code signals by said rotating selector, a second set of selector levers, means for transferring the setting of said first set of selector levers to said second set of selector levers, a plurality of punch bars, one for each lever in the second set of selector levers, a hammer for operating the punch bars to perforate a tape, a cam for operating the hammer and means whereby said cam is controlled by said rotating selector.

19. In combination, a rotating sleeve comprising a plurality of marking and spacing cams, selector levers, one for each pair of marking and spacing cams, a motor, means for transmitting power from said motor to said rotating sleeve, means responsive to code combinations of impulse conditions for operating said rotating sleeve whereby said selector lovers are variably operated, a plurality of punches, each punch having associated therewith a punch bar, a hammer adapted to co-operate with said punch bars, an oper ating cam, a cam mechanism controlled by said rotating sleeve for starting said operating cam into operation, means controlled by said operating cam for transferring the setting of said selector levers to said punch bars and means controlled by said operating cam for operating said hammer against the selected punch bars.

20. In combination, selector mechanism responsive to received code combinations of impulse conditions, a plurality of punches, a punch bar for each punch, a hammer for operating said punch bars, a tape, a feed mechanism for said tape, cam controlled means for transferring the setting of the selector mechanism to the punch bars, means for locking the punch bars in the position to which they have been set and means for operating the hammer against the punch bars to punch the tape.

21. In combination, a plurality of punch bars, each punch bar having an operating lever, a plurality of floating levers, one for each punch bar operating lever, a plurality of selector levers for each floating lever, means for setting said selector levers in accordance with a code combination of impulse conditions, means for bodily moving said floating levers into engagement with said selector levers whereby the setting of said selector levers is transferred to the punch bar operating levers, means for locking the punch bar operating levers in the positions to which they have been moved and means for operating the punch bars into engagement with the punches.

22. In a perforating mechanism, a plurality of punches, each punch having associated therewith a punch bar, each punch bar having associated therewith a punch bar operating lever, a floating lever and a selector lever, a pin barrel having thereon a plurality of cams, a polar relay for controlling the position of said barrel, said polar relaybeing responsive to code combinations of electrical impulse conditions, means for rotating said pin barrel as impulse conditions are being received whereby said selector levers are given a setting in accordance with the code combination received, cam operated means for moving the floating levers into engagement with the selector levers for transferring the setting of the selector levers to the punch bars and cam operated means for moving the punch bars into engagement with the punches for performing the perforating operation.

23.,In combination, a pin barrel, a flutter cam carried by said pin barrel, a flutter lever co-operating with said flutter cam for moving said cam to predetermined positions, means for rotating said pin barrel, electromagnetic means responsive to code combinations of impulse conditions for.controlling the operation of said flutter lever for variably operating said pin barrel longitudinally, a pluralityof punches, a plurality of punch operating bars associated with said punches, said punch operating bars being positioned in accordance with the positions of the pin barrel.

24. In combination, a rotatable pin barrel, means for moving said pin barrel longitudinally, means responsive to code combinations of impulses for permitting or preventing said movement and tape perforating mechanism controlled by the position of said pin barrel.

25. In combination, a pin barrel, a motor for rotating said pin barrel and for moving said pin barrel longitudinally, electro-magnetic means responsive to code combinations of impulse conditions for preventing or permitting such longitudinal movement of said pin barrel in accordance with the code combinations of impulse conditions; selector.

mechanism to be operated in accordance with the operation of the pin barrel and tape perforating mechanism adapted to be variably operated in accordance with the operation of the selector mechanism.

26. In combination, a plurality of selector levers, said selector levers having a plurality of operating positions, means responsive to code combinations of impulse conditions for variably operating said selector levers to either of their positions, means for holding said selector levers in either of their operating positions and punch operating bars variably operated in accordance with the operation of the selector levers.

27 In a perforating mechanism, a plurality of punches; a punch bar associated with each punch; selecting mechanism for controlling the operation of said punch bars; an electromagnet for controlling the setting of the selecting mechanism in accordance with code combinations of electrical impulse conditions; and camoperated means for operating the punches in accordance with the operation of the punch bars.

28. In a perforating mechanism, a plurality of punches, a punch bar associated with each punch; a plurality of punch control elements associated with said punch bars; means .for controlling the setting of said punch control elements in accordance with code combinations of electrical signalling conditions; and means started into operation at the beginning of each code combination and automatically stopped at the end of each code combination for controlling the setting of said punch control elements.

29. In a perforating device, a series of punches; a punch bar associated with each punch; a series of selectors; one associated with each punch bar; and means comprising ity of punches, a punch bar associated with each punch; a punch operating lever asso-' said punch bars being variably positioned in accordance with the positions of the cam shaft.

31. In combination, a tape perforating mechanism; a rotatable pin barrel controlling the operation of said perforating mechanism and means responsive to code combinations for intermittently reciprocating said pin barrel simultaneously with its rotary movement to variably control the operation of said perforating mechanism.

32. In a perforating mechanism, a constantly rotating shaft; a, normally arrested selector member mounted on said shaft and operatively connected thereto; a plurality of punches; and a plurality of selector elements, one associated with each punch, the setting of which are controlled by said member; said member being variably operated in accordance with code combinations of electrical signalling conditions and started into operation at the beginning of each code comblnation and automatically stopped at the end of each code combination.

33. In combination, a tape perforating mechanism; a constantly rotating shaft; a

1 mechanism.

In testimony whereof I affix my signature.

EDWARD E. KLEINSCHMIDT.