US2351785A - Printing telegraph apparatus - Google Patents

Description

June 20, 1944. A. H. REIBER I 2,351,785

PRINTING TELEGRAPH APPARATUS Original Filed May 4, 1936 6 Sheets-Sheet l INVENTOR ALBERT H. REIBER Eur/Z 3 ATTOPN A. H. REIBER PRINTING TELEGRAPH APPARATUS- June 20, 1944.

Original Filed May 4, 1936 6 Sheets-Sheet I5 34 R 2 4 7 023%? E M m wuawg a I R 4 w y a n m- T 7 0 am a 4 w w MH. m w M m u 7% w w m NT m Mm m IR A h B w I a n a 1 I FIG. 3

June 20, 1944. A. H. REIBER v PRINTING TELEGRAPH APPARATUS Original Filed May 4, 1936 6 Sheets-Sheet 4 lmmir INVENTOR} I j ALBERT H. REIBER BY;

'ATTOR Y June 20, 1944. A. H. REIBER PRINTING TELEGRAPH APPARATUS Original Filed May 4. 1956 v e Sheets-Sheet 5 INVENi'OR H. REIBER ALBERT BY 3; 3

M c F ATTORNE June 20, 1944. A. H. REIBER PRINTING TELEGRAPH APPARATUS 6 Sheets-Sheet 6 Original Filed May 4. 1936 lllmuumnlllllllmllllfl INVENTOR ALBERT H. REIBER Patented June 20, 1944 STATES PATENroFFIcE "Albert H. Reiber, Evanston, Ill., assignor. to Toletype Corporation, Chicago, Ill acorporation l of Delaware .Original application May 4, 1936, Serial No. 17,796. Divided and this application OGtObB! 27, 1941, Serial N0. 416,722

2 Claims.

This present invention relates to printing telegraph apparatus and particularly to a type wheel printer forrecording printed characters in page form. i

This application is a division ,of application Serial No. 77,796 filed May.4,fl9.36, which has her 29, 1942', a

A primary object of the present invention is to matured lntoliatent No. 2,296,874,"issued Septemembody in a printing apparatus, features which are conduciveto reliable and efficient operation. H Thepre sentinvention features a novel type Wheel structure ,and other constructional arrangements which impart to a type wheel printer .many of the advantageous features of a type bar printer while retaining the simplicity of constmction characteristic of type wheel printers.

Briefly, the;,principal elements of the receiving printer-according tosthe present invention are a selecting mechanism including a single magnet selector and acode disc selector, power driven operating cams controlled from the selecting mechanism, a type, wheel and means for stopping it in accordance with the operation, of the code disc selector, cam operated means for effecting printing from the type wheel, cam con- .trolled and operated mechanisms for performing the necessary'stunts ,or functions of the printer, mechanism for feeding an inked ribbon between thetype wheel and a printing platen including means for controlling the direction of feeding of the ribbon, and a movable Carriage whichcarries the paper upon which printing is The single magnetselector operates in accordance with signalqimpulses received sequentially to position settable elements in accordance with a received signal combination. Power operated transfer mechanism then operates through the elements thus set totransfer simultaneously all of the conditions established by the received signalimpulses to a code disc selector which has a a plurality of stop elements, any one of which, upon selection, is projected into the path of an arm on a type wheel shaft, to which a constant torqueis applied, to stop the type wheel in a position corresponding to the received signal combination. The single magnet selector mechanism controls the operation of a set of operating cams, one of which operates the transfer mechanism to effect the setting of the code discs,

another of which operates a printing bail and in addition, under certain selective conditions, performs certain non-printing functions and conditions other non-pronting functions for printing. of letter combinations.

performance, and the third and final cam of which operates the spacing mechanism and performs those functions that are conditioned but not performed by the printing bail.

Spacing from one character to another and between words is accomplished through a pawl and ratchet, thelatterof which is connected to a pinion meshing with arack included in the platen carriage The spacing operation tends to be performed w'ith invariable regularity but is,

under certain circumstances, suppressed, as for example, during the performance of functions which, if accompanied by spacing, might result in the introduction of undesirable spaces in the Those functions whichare performed by operation of the spacingcam "are the functions which it is desirable to per form slowly, in order to obviate attempted violent movement of relatively massive elements: Those functions that are performed by the print bail operating cam are functions involving the movement of relatively light elements, theinertia of which is relatively light so that they may be operated with relatively great rapidity,; as the printing bail operating cam is arranged'toperform an operation in a very brief interval. In the case of certain functions, a

yielding connection is provided between a function conditioning leverand an associated lever, andthelatterlever may be blocked by any desired means and in particular by the case shift mechanism of the printer, so that the function ing and printing mechanism;

I Fig. 2 is 'a side elevation of th transmittingand receiving mechanism;

Fig. 3 is a vertical sectional view through the receiving and printinng mechanism;

Fig. 4 is an elevational viewof a modified print hammer operating mechanism;

Fig. 5 is a top plan View of the transmitting and receiving mechanism;

Figifiisa-horizontal sectional view showing the spacing and function performing mechanisms;

Fig. '7 is a horizontal sectional view showing details of the spacing mechanism;

Fig. 8 is a perspective view of the platen carriage showing particularly paper holding and guiding means;

Fig. 9 is a perspective view of a removable paper roll holder shown in broken lines in Fig. 8;

Fig. 10 is a perspective view of a paper guiding plate;

Fig. 11 is a vertical sectional view through the platen carriage showing the manner of mounting the plate shown in Fig. 10 upon the carriage;

Fig, 12 is a vertical sectional view showing the line feeding mechanism;

Fig. 13 is a perspective view of the space suppression function selective and performing mecham'sm;

Fig. 14 is a detail view of the space suppression mechanism; and

Fig. 15 is a perspective view of the line feed function selective and performing mechanism.

Keyboard transmitter Referring now to the drawings and particularly to Figs. 2 and 5 the reference numeral I5 indicates generally a keyboard transmitter mechanism which may be of any desired form such as the one disclosed in U. S. Patent 1,595,472, granted August 10, 1926 to Howard LzKrum. The keyboard transmitter I5 includes a base casting I6 which carries a plurality of character selecting key levers I8. The key levers operate upon a set of permutation bars (not shown) to control transmitting apparatus indicated generally by the reference numeral I6. The transmitting apparatus includes a camshaft 2| which carries aplurality of transmitting cams 22. A contact controlling bell crank lever 23 is associated with each of the transmitting cams 22. One end of each'of the bell crank levers 23 is disposed in engagement with one spring of a pair of transmitting contact springs 24 and the other end is aligned with a lever 26 which .is controlled by the permutation lever I8, the permutation bars and therefore the levers 26 which they control are set permutatively,

whereby certain of the bell crank levers '23 are blocked so that they cannot rotate and others are freed so that they may rotate to allow closing of the associated transmitting contacts 24 when .per-

mitted to do so by its associated transmitting cam 22. The transmitting cams are so arranged upon the shaft 2| that they release the several transmitting contact bell crank levers 23 successively for rotation and thus the transmitting contacts corresponding to the particular permutation code established by the operated key leverare. closed successively. A locking ball 28 has a cam follower 29 which rides on a cam 3| carried by cam shaft 2!. Ball 28 drops into blocking relation to 1 the levers 26 after they are set by the permutation bars and prevents disturbance of an established code combination during, the transmission of the corresponding code impulses. Power for driving the transmitting cam shaft 2| is communicated through a spring loaded clutch 32 from a gear 33 which is driven through suitable intermediate gearing 35 from a gear 4] (Figs. 1 and 2).

The base casting I6 removably supports the foundation for a receiving printer comprisin a vertically extending frame casting 36 and a frame casting 37 secured to the casting 36. The frame casting 36 extends from front to rear of the base casting I6 and the casting 31 extends transversely thereof. The frame casting 36 has secured thereto bearing blocks 38 which rotatably support a shaft 39. Shaft 39 has secured thereto a gear 4| (Figs. 1 and 2) which is driven by a spiral gear 42 (Fig. 3) which is mounted on the rotor shaft of motor 34 and. constitutes the main driving gear of the receiving printer as well as of the transmitting mechanism. The shaft 39 actuates the selector mechanism of the receiving printer and also the operation performing cams.

The driving gear 42 (Fig. 3) also meshes with a gear 43 which is mounted on a shaft 44 and is voperatively connected thereto through a friction clutch 46. Shaft 44 is journalled in a code disc selector mechanism indicated generally by the reference numeral 41 (Fig. 2) which is removably supported on the frame member 36.

, Type wheel The type wheel shaft 44 has a reduced portion I2I at the upper end thereof which provides a shoulder I22 (Fig, 3). A hub I23 is journalled on the reduced portion I2I of shaft 44 and is slidable thereon. At its upper end th hub I23 carries a disc I24 to which is secured an annular type wheel frame I26. The frame I26 has slots in radial arrangement equally spaced therearound, and in each of the slots upper and lower type pallets I21 are slidably disposed. The type pallets I2! are arranged in upper and lower annular rows, one row of which may carry any desired group of characters such as letters and the other of which may carry other characters such as figures and punctuation marks. The type pallets comprise type faces I28 to which are secured thin shanks I29 which extend inwardly and radially of the type wheel structure within the radial slots thereof. The shanks of each annular row of type pallets are notched to receive a garter spring I3I which biases all of th type pallets of an annular row to their innermost positions with the type faces I28 disposed about the periphery of the slotted frame I26. An annular ring I32 is fioating'ly disposed in the notches in both annular rows of type pallets and prevents the type pallets from accidental displacement from the type wheel structure due to centrifugal force in the event that one of the garter springs I3I should break. At one portion of its periphery, the type wheel structure has no type pallets and at that point the disc I24 and frame I26 are provided with recesses in which is disposed a perpendicular portion I 33 of a type wheel driving arm I34 which is adjustably secured by screws I36 to an arm I35 which is carried by the type wheel shaft 44 at the top thereof in fixed relation to the shaft to be driven thereby. The adjustability between the arms I 34 and I35 is angular.

The type wheel structure is slidable longitudinally of the type wheel shaft to bring either of the two rows of type pallets into printing alignment with the printing platen, the shifting of the structure being accomplished by a sliding movement of the hub I 23 with respect to the type wheel shaft 44 produced by mechanism to be described hereinafter. As the type wheel is shifted, the recesses in which the perpendicular portion I33 of driving arm I 34 is disposed slides upon the portion I33 and driving relation between the type wheel shaft and the type wheel is maintained. A printing hammer I36 is pivotally mounted on screws I31 threaded into the stationary bracket I25 (Fig.2). and has its head in alignment with the printing position so that it is disposed behind .the'shank of the type palletof either of the annular rows of type pallets, depending upon whethertthe type wheel is in its upper or lower position. The printing hammer I36 has integral therewith a bail portion I I6 at the opposite end of which is integrally formed a lever arm T (Fig. 2) which carries an impact receiving member I38. A limit screw II8 limits the operative move Carriage mechanism The printing platen I39 is rotatably mounted in end plates I40 of a reciprocating carriage I4I' (Fig. 1). The carriage MI is supported in adjustable rails I42 at the top of the main frame member 31. Anti-friction balls I43 (Fig. 3) are disposed between the carriage MI and the rails I42 and provide free movement of the carriage with respect to its supporting rails. The rotatable platen is provided with a feed ratchet I46 (Fig. l) with which there cooperates a feed pawl I41 (Fig. 12). I l

The platen feeding pawl is articulated to lever I'49.(Fig. 12) that is fixed to a rock shaft I50. The rock shaft I50 is rotatably journalled in the carriage I4! and has fixed thereto at a point substantially midway between the ends of the carriage I4I an operating lever I50. The lever I49, rock shaft I50, and opera-ting lever I60 are biased counterclockwise by a spring I65. Feeding of the ratchet I46'in the direction indicated by the arrow is effected by clockwise rotation of operating lever I60, by a power actuated bailto be described later, against the tension of spring I65, which subsequently acts to reciprocate the pawl I4! to pickup the next tooth or teeth for the next line feeding operation. A lever I10, pivoted on the carriage end plate I40, provides two abutments for deflecting the pawl at different points in its travel to idle or unoperated position to establish single or double line spacing. When the lever is in the position shown in full line, it permits the pawl to travel sufficiently far in engagement with the ratchet I46 to pick up two teeth, whereas if the lever is in the dotted line position the pawl is deflected from the ratchet and is permitted. when it operates, to pickup only. onetooth. An adjustable.

eccentric I75 (Fig. 12), is mounted on the carriage end plate I40 and is disposed in the path of a camming lug I85 on the pawl I41 for wedging the pawlagainst the ratchet to prevent overtravel of the ratchet and platen. A spring biased jockey roll I90 bears against the ratchet I46 and controls the positioning of the platen I39.

The carriage MI is moved to its right-hand position by a belt II' (Fig. 1) ,.which has one end connected to a drum I52 which contains a spiral spring by which the drum is urged to rotate in a clockwise direction and which has its other end connected to a pin I53 (Fig. 2) carried by the carriage MI.

The carriage I4! is moved left- .Wardly by spacing'mechanism to be described hereinafter against the action. of the spiral spring. A lever I56 pivoted at I5! (Fig. 2) has one end articulated to the plunger rod I58 of a dash pot I59 and has its other end positioned to be engaged by the carriage I4I as it travels into its extreme right-hand position by the action of the spiral spring. With this arrangement, the return of the carriage to its extreme right-hand position is cushioned by the dash pot I50. Stop screws I54 threadedly engage the carriage supporting portion I4? of the frame casting 3'1 at opposite ends of said portion, and the inner ends of the stop screws are disposed in the path of a bracket I45 mounted on carriage MI. The screws I54 limit the movement of the carriage in both directions of travel.

Operating came The operation of the ribbon feed bail 206, the print hammer lever I I I, and the transfer bail I02 is effected by operating cams mounted on the shaft 39 above the gear 4| (Fig. 3). The operating cams are assembled in fixed relation with respect to each other on a sleeve which is mounted on shaft 39 and which has associated therewith the driven portion of a spring loaded tooth clutch 2H,. the driving portion of which is keyed or staked to shaft 39. A clutch throw-out lever 2I2 pivotally mounted on shaft M3 is spring biased into engagement with the driven portion of the clutch 2H and has an arm 2M (Fig. 1) disposed in the path of a cam projection 250 (Fig. 3) included on the selector cam barrel 62. With this arrangement, at a given point in the cycle of operation of the cam barrel 52, cam projection 2H1 rocks the arm 2H!- which withdraws the clutoh throw-out lever 21?. from restraining engagement with the driven portion of the clutch 2 II and permits driving engagement to be established between the shaft 39 and the cams mounted thereon.

The uppermost of the cams is a channel or box cam designated by thereference numeral 2 I0, the camgroove 2I'I' (Fig. 6) of which receives the follower roller 2I8 rotatably mounted on a bell crank lever 2I9 rockably mounted on the pivot shaft 22 I. The bell crank lever 2E0 is articulated at 222 to a bar 223 to which it is arranged to impart a reciprocatory motion due to the fact that the cam groove 2 I! has one offset 224 which, when encountered'by the follower roll 2i 3, causes the lever 2I9 to rock counterclockwise uponits mounting shaft. 22! and in this way the bar 2233 is reciprocated rearwardly of the typing unit. A lever 226 is also rockably mounted upon the shaft MI and is secured at its forward end to the cam operated bell crank 2!!) by a clamping bolt 227 which passes through a slot 228 in the bell crank 2I9. The slot 220 provides adjustability in the clamping vof the levers 2l9 and226 together. The lever 226 is effective in the conditioning of functions when they are selected, and its operation will be described later; I

The bar 223 carries intermediateits ends an eccentrically mounted abutment against which abuts the operating arm 229 of a striker member or hammer 23I pivotally mounted at 232 (Fig. 1). The bar 223 has a depending lug 220, and a tension spring 225 has one end connected to the lug 220 and the other .end connected to the operating arm 225 of striker The striker member 23I is provided at its upper end with a .massive head 233 which describes an arc as the hammer 23I isrocked and which delivers a'sharp ;'blow to an impact receiving abutment I38 ofrepin IBM.

silient materiaLsuch as rubber or leather, car.- ried by the print hammer operating lever arm l1. As indicatedin Fig. 6, the offset 224 in the groove 2| 1 of cam 256 is very abrupt and very short, so that the reciprocation of bar 223 to its rearmost position is very rapid and thus the blow imparted by the striker member 23! to the print hammer operating lever arm I i7 is very sharp. The bar 223' has a further function which it performs only under certain circumstances which will be described later.

The lowest cam in the group is designated by the reference numeral 24!. This cam, as shown in Fig. 7, is'contoured to impart gradual rotation to'a lever 2 32 pivoted onthe stud 22L The lever 242 has a follower roll 243 which rides against the cam 24!. As shown in Fig. '7, the radius of the cam 2M increases steadily from minimum to maximum with an abrupt drop between the portions ofrninimum and maximum radius, and this causes the lever 242 which is pivoted on the shaft 2M, tofrotate counterclockwise steadily until it reaches its extreme counterclockwise position, whereupon it is restored rapidly to its extreme clockwise position. A bell crank lever which comprises a single arm 24% and two arms 249 disposed in spaced horizontal planes and in substantially the same'vertical plane is adjustably connected to lever 242 by a clamping engagement afforded by screw 24'! extending through slot 246 in arm 248. Near their outer ends the arms 2&9 support the pivot The pivot pin 25;! serves as means for articulating to the bell crank, lever arms 2% a spacing pawl and a plurality of function performing bars. Cain 2M and levers 242 and M3 serve, through the elements articulated to the lattenas the means for effecting character spacing and function performance through the cooperation of elements provided therefor.

Spacing mechanism The spacing pawl designated by the reference numeral 256 is articulated to the pin 25! through a spring yield connection comprising slot 251, spring 258, and guide pin 259' (Fig. 6). The pivot .pin 25! enters the. slot 257 and is urged to the forward end of the slot by the compression spring 258. The pin 259 is retained within the slot inside the convolutions of the spring 2E8 and prevents the spring from escaping from the slot.

The normal movement of the pawl 256 is recip rocatory, due to the rocking of the bell crank lever arm 249 by the cam 2M, but if the movement of the pawl 255 is blocked as it may be under certain circumstances, the pin.25l may move within the slot and the spring 258 will take up the movement imparted by'the cam and will restore the pivot pin 2-5l to the forward end of the slot 25'! when the cam follower M3 has escaped from the highest portion of cam 24!. The

pawl 256 has at its opposite end a ratchet engaging prong '26! which engages a ratchet 262 to impart counterclockwise rotation thereto as the pawl is reciprocated. The pawl is spring biased into contact with theratchet by a spring 283. The ratchet 262 is fixed to a rotatable carriage spacing shaft 264 which carries at its upper end a pinion 263 (Fig. 3) meshing with a rack 267 connected to the platen carriage Mi.

A step-by-step movement of the carriage for letter spacing is effected by counterclockwise rota tion'of the spacing ratchet 262 responding to the reciprocation of the spacing pawl 256. As the carriage is stepped, it rotates the return spring ill drum I52 counterclockwise by drawing the belt l5! leftwardly, thus tensioning the spring and storing energy for a carriage return operation. A retaining pawl 265 (Fig. 6) pivotally mounted at 268 and urged in a counterclockwise direction by a spring 259 engages one after another of the teeth of the ratchet 262 and retains the ratchet and thus the platen carriage in the successive positions to which they are advanced by the pawl 2565.

Function mechanism The functions of the hereindescribed printing apparatus, suchas Line feed, Shift, Unshift, etc., are selected in accordance with stop positions of the type wheel, as determined by certain of the stop pins 96 which may be selected by the code discs 9|, are conditioned for operation by the lever 226 actuated by the print hammer operating cam 2IB, and are performed by the lever arms249 actuated by the spacing cam 24!. Any other desired functions may be selected, conditioned, and operated in the same manner, and in the present embodiment of the invention, certain other ones are so controlled, these functions providing for the operation of electrical contacts for circuit control, such as rendering the transmitting mechanism inoperative, remotely controlling apparatus for stopping the operating motor, and operating an audible signal, such as a bell.

Other functions, particularly those which may conveniently be performed with great rapidity, may be actuated directly from the print hammer operating cam 2| 6, rather than from the less violent spacing cam 24L In the present embodiment of the invention Carriage return and Space suppression are so controlled.

Since, as hereinbefore outlined, the selection of functions is controlled in accordance with certain stop positions of the type wheel, means must be provided for efiecting response of the function conditioning or performing mechanisms. Such means has been provided on the type wheel shaft 44 just above the gear 43 and comprises a plu rality of index pins or abutment pins 2H (Fig. 6) disposed in various horizontal planes and in various radial positions with respect to the type wheel. In certain horizontal planes, only one index pin is found, whereas others contain several pins. The number of pins in a horizontal plane indicates the number of type wheel stop positions in which a particular function is selected. Index pins in different horizontal planes may be disposed in the same vertical plane; indicating that a plurality of functions may be selected simultaneously.

For cooperation with the index pins Zlfth'ere are provided a plurality of superposed levers, the uppermost of which is designated 215 in Fig. 6, pivotally mounted at their forward ends on a pivot pin 210 carried at the rearmost end of lever 226 and extending through and supported in horizontal slots in a plate 273. The levers are aligned with the index pins 27! in the several horizontal planes, and each carries an abutment arm 212 extending leftwardly therefromat a point on the lever toward which the associated type wheel shaft index pin 27! points when the shaft is stopped in the position to select the function represented by that pin. At their rearmost ends the lever 215 and corresponding levers are provided with disc-like portions 2% disposed in notches in the forward ends of associated function levers which are pivotally mounted on the. pivot shaft 216 and which will be identified by individual reference numerals in the description of .the several function operations.

Since the lever 215 and corresponding levers are articulated to the lever 226 (Fig. 6), they undergo movement when the print cam 2I6 operates lever 226, and a leversuch as 215 associated with selected index pins 21I moves differently than. do those associated with unselected index pins. The function levers to which the lever 215 and corresponding levers ,are articulated by their disc-like portions are biased to their unoperated positions by. springs211, and they rotate in opposition to the tension of such springs only when forced to do so. When the lever 226 is-actuated by camv 2| 6, it carries the pivot pin 210 leftwardly as viewed in Fig. 6, and with it the iorwardends of lever 215 and those disposed below it. If no index pins'21I are aligned with the abutment arms 212, the lever 215 and corresponding levers pivot about 1 their disc-like portions 214 and rock idly. If, on the contrary, an index pin is aligned with an abutment arm 212, it blocks the leftward movement or that arm, and becomes a fulcrum for thehparticular lever, thus causing the lever to operate as a first class lever to actuate its associated function lever and rotate the latter counterclockwise.

Certain of the function levers operated by the lever 215 and corresponding levers are adapted to perform the associated function and others are adapted to condition a function. The conditioning is effected through superposed function performing bars, the uppermost of which is designated 280, pivotally mounted on the pivot pin 25I carried by the spacing cam operated bell crank lever arms 249. The function bar 288 and corresponding bars are supported intermediate their ends in spaced horizontal slots 219 in the vertical plate 213 (Fig, 2). They are reciprocated rearwardly when the bell crank lever arms 249 are rotated counterclockwise by cam 24I and they may rotate about the pivot pin 25I within the confines of their supporting slots 219. They are biasedcounterclockwise by springs 218.

Carriage return The uppermost index pin 2H and lever 215 are associated with the restoration of the platen carriage I-II to line beginning position, which is' accomplished by withdrawing the spacing pawl 256 and retaining pawl 261 (Fig. 6) from engagement with the feed ratchet 262, whereupon the spring loaded drum I52 acts through the belt II to restore the carriage to its extreme right-hand position. The function lever to which the lever 215 is articulated is designated 28I, andthis lever is rotated counterclockwise when the uppermost index pin21Iis eifective upon its associated lever 215. The lever 28I carries upstanding pins 282 and 283 located at the left and right of the spacing pawl 258 and theretaining pawl 261, respectively, and in close proximity thereto. When the lever 28I is rotated counterclockwise, it moves the pins 282 and 283 to right and left, respectively, and the pins rotate the spacing pawl 256 and retaining pawl 261 clockwise about their pivotal mountings 25I and 268, respectively, to withdraw the pawls from engagement with the ratchet 262. The carriage, being under no other restraint, responds to the force exerted by the spring in the drum I52 and moves to its extreme right-hand position, rotating the spacing ratchet 262 clockwise as it does so. 7 1

.Itcwillbe notedthatthe lever 28I is provided, near itsrearmost end, with anotch in which are formed shoulders286 and. 281 (Fig. 6). A latching lever "288 is pivotally mounted at .289 andis' biased for clockwise rotation by spring 29I which hasone jend connected to thelever 288 and the other end connected tothe function lever 28I.- When thelifunctionlever 28I is in its .un-

operatedor extreme, clockwise. position as viewed in Fig. 6, the-lever 2881s held ,in engagement with the shoulder 286 by spring 29L The rock- All ingrof thefunction lever 28I counterclockwise to .effect- ,a' carriage return operation permits the lever 28,8.toescape fromthe shoulder 286 and to come to rest against theshoulder 281 whereby the function lever 128I is. latched. in its operated position to maintain thepawls 256 and 261 out of engagement with the ratchet 262. The purpose of latching the function lever 28] in the operated position is to permit the carriage I4I; which may bounce slightly asit comes into engagement withthe dash pot controlled lever I56 or the stop screw I54, to settle into its extreme right-hand position before the pawls are permitted to reengage thespacing ratchet 262. Manifestly, the function lever 28I must be unlatched before any carriage spacingfoperation I can occur and an arrangement has been provided whereby the lever 28I"is unlat' hed upon the next'operation of the t an,

'The ar'rang'ement includes a lever292 (Fig. 6) whichhas' a slot 293 which is entered by a screw 294 carried by lever 288. The slotted engagemerit between lever 288 and lever 292 provides a yielding connection, and a spring 296, which has'one end connected to-the lever 292 and the other. end connected to an extensienor the lever 28,8, 'tendsto I rotate the lever 292 in a counterclockwise direction which is. prevented by a lug 291 carried by a fixed plate 295 against which the lever -292 rests. Since the spring 296 is disposed between the lug 291 and the screw 294,'the extreme left endfof the slot 293 abuts against screw 294. A r'od'298 is slidably supported in thelug 1291 and in a portion 299 of the frame of the mechanism and occupies the same horizontal plane as the lever 292. The plunger298 slides freely within frame member 299 and the lug 291 and isurged to its rightward position by the lever 292. The lever I56 which is articulated to the dash pot plunger rod "I51'carries an eccentrically mountedadjustable abutment 3IlI in alignment with the right-hand end of the rod 298. The 'abutmentfMI 'is' similar .to the previously described abutment 239 and is below the pivotal mounting I51'of the lever I56 so that itismoved toward therod'298' as the carriage I II rotates the lever I56 clockwise at the completion of a carriagereturri operation; When the lever I 56 comes, to rest in its extreme'clockwise position at the conclusion of the carriage return operation, its abutment 30I m'ovesthe rod 298 leftwardly 'a distance sufficient to" cause it to rotatelfthe lever 292 clockwise and position the fOTWLldjGlld; of that lever inalignment with the rod 223 articulated to the-bell crank lever 2I9. Llever 2 92 will occupy this position as long as the carriage MI is in its extreme right-hand position and upon the next counterclockwise rocking of the bell crank lever 2I9 bythe box cam 2I6, rod 223 will be reciprocated rearwardly-and will communicate its reciprocating motion to lever 292, which will cause the latching lever 288 to be rotated counterclockwiseout of engagement with the shoulder 28! and into engagement with the shoulder 28E. Thefunctionlever 28! will thus be restored to itsunoperated position and the pawls 256 and 56l-wil1 reengage the spacing ratchet 262 inprepa'ration for normal spacing operations. The slotted mounting. of lever 232 provides a yield connection which may, under certain circumstances,'operate yieldin'gly on account of a blocking condition. The carriage I4! may, particularly if it travels through only a short distancein returning to its extreme right-hand position, reach that 'positiorn while the bar 223 (Fig. 6) is being operated by the cam 2i! and before the bar has been withdrawn to its foremostposition. Under this condition the rod 298 mightjam theforward end of lever 292 against the right-hand face of operating bar 223, whereby the rod 298 .might be prevented from traveling its normal distance and the carriage i l! be prevented from-assuming its extreme right-hand position. The slotted connection permits the. lever 292 to be fully moved by the rod 7 298, even should the forward endof lever. 292

be blocked by bar 223. I Shift and unshift mechanism 215, but which is associated with the index pin in the fourth level from the top. This function lever is associated with the shift operation by means of which thetype wheel is shifted to re move one of the annular sets of type pallets from alignment with the print hammer I36 and to bring the other set of typ'epallets into alignment therewith, This lever doesnot' perform the shift function butmerely establishes a condition as a result of which the function maybe performed, and'to this end' it isfproyidecl witha projection 303 which occupies thej'sianie horizontal plane as the bar 280' (Fig. 6). This bar has its rearmost end disposed slightly to the left of a latching projection 304' of a latching lever 306' which is pivotally mounted'on' shaft 268 and is'biased in a clockwise'directionbyspring 3|!I. All levers corresponding tolever 30.6 are biased clockwise by springs 3 I 0 and'areli'mite'd by abutment against stud3ll0 (Fig. 6). Upon the selection of the index pin associated-with said lever which is comparable to lever 215 and upon the operation of that lever, the'lever whichis comparable to lever 28! is 'rotated counterclockwise similarly to the previously described function lever 28!,and through its projection it imparts a' clockwise rotation tothe bar 'ZBUi The-latter bar, in rotating, moves to therig'ht'of latching projection 3M; and'at the same time it moves rearwardly due-to operation of bell crank lever arms 249' by-cam 2 It, and becomes latched in its clockwise position.

The bar 280 carries on the right side thereof a projection 33'! which is disposed in alignment with the lower end of a shifter lever arm 308 (Fig. 2) to which it imparts a counterclockwise motion as viewed in Fig. 2' as the bar 280 isreclockwise rocking of thebell -crank lever arms 249 by the cam. 2.4!..(Fig. '7). The shifter lever arm 398 is one arm'of. a bell crank-lever pivotally mounted upon the previously described pivot shaft 232 and having itsaotherarm 3!! extending rearwardly of the printeru The lever. arm 3!! is bifurcated at its outer end 'and..has-disposed in the bifurcation. apin: 3.12. carried byiarni 3!3 of shifter frame 3% (Fig. .2). The frame 3M is mounted on shaftv 232 by means of a slot'so that it may be raised and loweredvertically to lift and lower the type wheel through its horizontal arm 35? (Fig. 3),;which is-guide'don guide screw 3l5 (Fig. 2) and which-'engageszthetype wheel hub !23 (Fig. 3). The operation of the lever arm 3% upon the shifter frame 3M isto lift the latter through the articulation of the lever arm 3! to the frame 3M by virtue of. the pin 3l2. The frame 3% carriesga' pivoted spring loaded detent 3H3 which has notches; at the lower end thereof, either of which may engage a bushing on the shaft 232 to maintain the shifter frame 3 in aposition to which it is moved. A spring (not herein shown, but clearly illustrate'din the parent application) counterbalances the shifter frame 3M and type wheel 0!, and thus equalizes the forces required tojelfectshift and unshift operations.

An operating bar 32!) is articulated to the pivot pin 25! directly below the operating bar 280 and is provided at the side thereof with a projection which, when the bar is latched in its extreme clockwise position by a projection (comparable to 304) of a lever comparable to lever 306, is disposed in operating alignmentwith a lever arm 32'! (Fig. 2) similar to the lever arm 308 but necessarily slightly longer than that lever arm. The lever arm 32-! constitutes, together with a forwardly extending arm 328, a bell crank lever pivotally mounted upon the pivot shaft 232. The outer end of the lever arm 328 is bifurcated similarly to the lever arm 3! and-engages a pin 329 carriedby a forwardly extending arm 33! of the shifter frame are: When the leverarm 32! is rocked in counterclockwise direction due to movement of the projection 323 of the operating bar 32!], the lever arm 328 will also be rocked counterclockwise and will move pin 329 downwardly, whereby shifter frame3l4 ismoved downwardly to elfect an unshiftoperation. It is apparent that the lever -arms 30 8 and 32'! operate oppositely and simultaneously so that as one effects movement of the shifter frame, the other isoppositely rotated and presented in position to be next effective in the'shifting of theshifter frame 316.

. ,The unshifting operation conditioned by the unshift function leverandperformed by the bar 320 'may be selected for' either of two stop'positions of the type wheel shaft, asindicated by the presence of two index pins 27-! in the same horizontal planev (Fig. 6) either of which may be effective. One of the pins is associated with the unshift signal and is presented in operating position when the signal combination assigned to un-' shifting is received. The other pin is presented in operative position'when'that code combination is received which is assigned to spacing, for the reason that it has been found that in many instances printing following a-blank spacing operation is to be effected'with an unshift condition of the printing mechanism, and it is therefore convenient to effect the unshifting automatically simultaneously with'the spacing, thu obviating the transmission of a separate unshift code combination.

'spect to the lever.

' printingposition. The selection of the line feed index pinand the rocking of a lever 335, Fig. 15,

against the pin causes the operation of a function lever 332 which has a projection for operating the associated function performing bar 340. A function operating lever'334 is pivotally mounted (below said latch lever) on the pivot shaft 260 and has operative connection with the line feeding mechanism, as will be described, and is therefore a true function performing lever, but it has no latching projection. A separate latching lever 336 is provided which is also pivotally mounted on the pivot shaft 268 and which has at its right-hand end a forwardly projecting arm 33'! which terminates in an upwardly turned projection' 336 which occupies a position such that the rearmost end of lever 3401s disposed slightly to the'left of the latching projection 338.

When the function bar thus latched is reciprocat'ed rearwardly in the manner common to ;all of the function performing bars, the lever 334 is'rotated counterclockwise about the pivot 268. The lever 334 has secured thereto at its righthand end by screw 34I a link 342 which is provided with a slot in which is disposed the operating arm 343 of a line feed bail 344. The ball 344 (Figs. 3 and 12) is pivotally mounted in suitable brackets 346 on the rear of the machine and extends slightly above the lower end of the previously described line feeding lever I60. The lever I66 travels with the carriage IM and the extent of thebail 344 transversely of the machine is sli'ghly greater than the travel of the lever I60,so that the lever may be engaged by the bail at anyfposition in the travel of the carriage.

The line feed lever I60 is provided with an antifriction roll I48 which constitutes means for engagement of the bail 344 with the lever I60. A certain amount of freedom is provided in the interconnection between the link 342 (Fig. 15) and thelever 334 to permit the link to rock with re- '343 of'the bail 344 enters also provides limited freedom necessitated by the rocking movement of the arm 343 within the reciprocated link 342. A tension spring 341 keeps the arm 343 from chattering within the slot in the link 342.

The provision of a separate latching lever 336 for latching the operating bar 340 in position to operate the function performing lever 334 instead "of'providing the lever 334 with a latching prolevers-306 and 323 being light, return substantially instantaneously to their extreme clockwise positions after being thus bounced, and latch the bars 280 and 320 in function performing position.

ShouIdthe lever 334 be provided with a latching projection and be depended upon to latch its asiated bar'340'in conditioned position, it might The slot into which the arm Cit insome instances bounce away from the bar 340 or be slow in returning for a repetition of the function, and fail to return to its extreme clockwise position-quicklyenough, due to the mass articulated to it, to latch its associated function bar 340. In order that such possibility may be avoided, the, light and readily responsive latching lever 336 is provided and the function performing lever 334is not depended upon to accomplish thelatchingoperation.

- Space suppression Two other functions that are I subjected to suppression are those represented by the clusters of index pins in the second and third horizontal levels of index pins from the top. These functions were not discussed in the foregoing descriptions of the several functions, and they will now be described. The functions now under consideration are identical in character but are effected under varying conditions and are designatedffSpace suppressionj, It will be understood, from description hereinbeiore presented, that'for eachcycle. of operation of the cam barrel 62 the clutch throw-out lever 2I2 will be operated and the clutch 2| I'Will drive the spacing cam 24I which will, in turn, cause the spaci ng pawl 256 to drive the spacing ratchet 262, unless aspace suppressingor preventing mechanism intervenes. Spacing is thus seen to occur cyclically unless prevented. 'Spacing is usually desired after the printing of each character, in order to present an unprinted portion of the page to receive the next character. However, with certain functions, such as shift, unshift, and possibly others, a spacing. operation may cause a space to be inserted inthe printed matter at a point where none is desired. This can be overcome by suppressing the spacingoperationwhen afunction is performed.

As shown in Fig. 13, there is associated with the uppermost cluster of index pins 2', through the lever 305 a combination of levers comprising levers 394 and 396 interconnected by a tension spring 301. Also there is associated with the next cluster of index pins 2', through the lever 405, a combination of levers 398 and 390 similar to levers 394 and 396 and similarly interconnected by afs'pring 40L As shown in Fig. 6, the spacing pawl 256 is" provided with a downwardly extending pinf402l which is in close proximity to the levers 306 and 399 and which is of sufficient length to be engaged by either of said levers upon counterclockwise rotation thereof. Engagement between the mum and the rotating lever 395 or 390 causes the pawl 256 to be moved clear of the spacing ratchet 262. Accompanying rearward reciprocation of the pawl 256 by the action of spacing cam 24I causes the extended arm 403 (Fig. 6) of the pawl to engage pawl withholding arm 404 of a lever 406 which is pivotally mounted at 216 and is biased clockwise by a spring 408 into engagement with a depending portion of an adjustably fixed stop 409. 1 The arm 404 of lever 466 thus holds spacing pawl 256 out of engagement with spacing ratchet 262 during one cycle of operation of cam 24I. When the pawl 256 performs a normal spacing operation, arm 403 thereof engages arm 404 of lever 40 6 and rotates the lever idly in counterclockwise direction.

It will be observed in Fig. 1 3.that levers 396 and 309 are provided with arms 4H and M2, respectively. These lever arms terminate in close proximity to downward projection 4I3 of arm 3I3 of type wheelsl ifter frame 3| 4 (Figs. 2 and 14).

Projection 413 is provided with "shoulder m which bloc-ks arm 4H of space suppression lever 396 when the shifter frame 3'4 is in its lower or unshift position and is also provided with shoulder 4!? which blocks arm N2 of space suppression lever 399 when the sh-ifterfra-rne is in its upper or shift position. Blocking of the lever arms 4! l or 4l2 results in prevention of operation of levers 396 or 399, respectively, and thus one set of space suppression index pins'is-e'ffective only in upper case selections and the other set is effective only in lower case selections. The yieldable interconnection of levers 394 and 396, and of levers 328 and 399 permits the blocking of levers 396 and 399.

It will be noted that the upper cluster-of space suppression index pins contains more pins than the lower cluster, which indicates that space suppression occurs in connection with a greater number of upper than lower case select-ions. will also be noted by reference to relative positions of pins in the two clusters, that space suppre'ssion occurs in association with certain selections irrespective 'of the shift or unshift condition of the printer. 7

Operating cam sequence From the foregoing description of the various functions it will be observed that the cams 2H5 and 2M, besides performing the printing and spacing operations, respectively, also figure prominently in theperformance of the-functions. It i therefore deemed advisable to discuss the sequence of operations performed by [these cams. The description will refer particularly to Figs. 6 and '7, from which comparisons may be drawn.

The cams 2 l6 and 24 l, have been shown in Figs. 6 and '7, respectively, in their stop positions and since, as previously stated, the cams are fixed to a sleeve carried by the shaft 39, the sequence of operation when driven by the tooth clutch 2| I, is as indicated in the two figures. It will be observed that the centers of cam followers 218 and 243 are disposed at the right of the cams 2I6 and 241 on'a line parallel to the path of travel of the carriage Ml. In the stop positions the cam follower 2I8 isabout to enter the'offset in cam 2l6, the cam follower 243 engages the lowest point of cam 24 I. When the cams begin to rotate due to operation of the clutch throw-out lever 2 l 2, the bell crank lever 2 l9 which controls printing is rocked almost immediately, due to'th'e presentation of the offset 224 to cam follower 218. Simultaneously with this operation, the lever arms 249 are rotating relatively slowly counter clockwise due to the steady rise of the surface of cam 244. As the bell crank lever 2l9i's being restored to its normal position after being operated, the transfer cam follower beginsits out- I ward motion due to the 'fact'that it encounters the sharp rise and thus it effects thetransfer operation after the bell crank lever 219 has been returned to its unoper'ated position as fully disclosed in the parent application. After the operations performed by the transfer cam and cam 2E6 have been completed, the cam 24! continues to operate upon its follower 243 and the highest point on the cam is reached just before the cams return to their stop position.

As previously stated, the operation of the cams 2! 6 and 24!, and the transfer cam is related in time to the operation of the-cam barrel '62, due to the fact that the clutch throwout leve'r2l2 is tripped by a cain projection 210011 the cam barrel 62. In-the preferred embodiment of the It a invention, the clutch throw-out lever 2l2 is tripped at an instant. in the cycle of operation of cam barrelv 62which will permit printing and transfer operations to be consummated before the next group of signal impulses begins to be received. Thus the interval which begins with the beginning of rotation of the cam barrel 62 in response to a start signal and which ends with the conclusion of one revolution of the cams 2H5 a1'1d24l, and the transfer cam is occupied first in the setting of the selector fingers in accordance with a signal combination, next with the operation of levers 2H] and 226 by cam 216 to effect printing of a character or conditioning or operation of a function in accordance with the setting of the code discs 9|, next the operation of the transfer bail by the transfer cam to transfer the'set'ting of the fingers to the discs 9i, and lastly the completion of the operation of cam 24! to effect spacing or' function operation. A printing operation occurs between the setting of the selector fingers and the setting of the code discs 9| and therefore it will be obvious that the printing cannot relate to the character selected but must relate to the character previously selected because the latest selection has not yet been transferred to the code discs 9|. Such a condition results in storage of a signal combination in the code discs, if the cam barrel 62 is brought to its stop position and held there, which will result in stopping of the cams 2H5 and 2M, and the transfer cam after the completion of their cycle of operation. The stored signal combination can be rendered effective .by applying another signal combination to the selector magnet -61 which will result in another cycle of operation of the cam barrel 62 and earns 2 l6 and 241, and the transfer cam. The printing of characters and the performance of functions always lags one signal combination behind the operation of a key lever, or the reception of a signal combination by the magnet 81. The final character in a message may be cleared out by an idle operation of a key lever, preferably to store a signal combina- 'tion representing some function such as unshift rather than acharacter selection.

Paper guiding mechanism As been previously stated, the printing platen I39 is rotatably supported in the end plates MB of a movable carriage M! (Fig. 8). Carriage I4l supports an arcuate paper guiding plate 42| which extends around the lower portion of the platen and is conformed to the contour thereof. The arcuate plate 42i is provided with bearing members 422 in which are supported shafts 423 (Figs. 3 and 8) The shafts 423 have mounted thereon pressure rolls 424 and the plate MI is provided with apertures in registry with the pressure rolls '42! to permit "the rolls to frictionally engage the platen when no paper is inserted in the carriage and to frictionally'engage. paper upon which characters are to'be printed.

The end plates I40 are provided with inwardly turned ears 426 whichv support in abutment with the forward faces thereof a paper tear-off blade be guided paper passing upwardly from the platen after having beenfe'd "between the platen 1 19 and arcuate guide plate 42L The lower edge of the guide p1ate428 *is disposed in close proximity to-the platen 139 and the plate functions after the manner of a stripper to guide the paper away from the platen. Guide fingers 43l are ad'- 5 -justably mou'nte'd by screws 432 upon the tearoif blade 42! and the fingers extend downwardly and overlap the arcuate plate 42l so that paper emerging from between the platen I39 and armbe inthe form of single sheets or acontinuous web. An arrangement for supporting a roll of paper is shown in' Figs. 3, 8, and 9 and comprises a bar 433 having at the ends thereof rearwardly extending concave roll-supporting arms 434 and intermediate the arms 434 a rearwardly extending oppositely curved roll retaining arm 436.; The roll"supporting arms 434 are provided with upwardly turned ears 431 which prevent axial displacement of a supply of paper in the form of a r'oll, The roll supporting member just described is removably supported on the carriage I41 by "means of downwardly extending projections 438 carried by the bar 433 to be received in retain in'g means now to-be described. i It will be observed byreference to Fig. 8 that theguide plate'428 is provided at the top thereof with a horizontal flange 439 in which are formed slots 44! spaced apart a distance equal to the spacing of the projections 438 of the roll supporting bar 433. At the lower edge of the guide plate 428 and below each slot 44!, two slits or cuts are'madewhereby tongues 442 are formed and these tongues are bent backwardly and upwardly to form pockets toreceive and retain projections 438 on the bar 433. The paper roll holder may be' easily removed from the carriage by lifting it vertically to withdraw the projections 438 from the pockets formed by the tongues 442 and from the slots 4. I

.Under some circumstancesit may be desired to supply paper in the form of a web which'is not supported on the carriage but which isstationarily mounted: upon anysuitable support behind the carriage. There is shown in Figs. 10 and 11 a .guide member supportable in either of two posi- .tions and means on the carriage for supporting the guide member. As shown in Fig. 11, the carriage, l4! has secured thereto and extending across the rear thereof a convexly formed plate g443jin which are formed spaced slots near the, l; forward edge thereof and other similar slots near the rearmost edge'thereof. A'guideplate 444 which is adapted to be received by the convex plate 443 (Figs. 10 and 11) is provided at its opposite ends with flanges 446 between which there extends a paper retaining rod 441 in spaced relation to the plate 444. The plate 444 is provided at the foremost edge thereof withtongues 448' spaced apart a distance equal to the spacing of the slots in the convex plate 443, each tongue 448 having an offset 449. The plate 444 may be supported in an upwardly inclined position on the convex plate 443 by inserting the tongues 448 in the forward set of slots so that the foremost portions of the tongues abut the inner surface of the plate 443 with the offsets 449 disposed within the slots. This manner of mounting the guide plate 444 is disclosed in broken lines in the upper portion of Fig. 11. The plate 444 may also be supported in a downwardly inclined position similarly-irlserting-the tongues 448 in the rearmost slots in the convex plate 443. This mounting is shown in broken lines in the lower part of Fig. 11.

Modified printing mechanism In Fig. 4 there is showna modified arrange- :ment for operating the printing striker member 23!. In this arrangement the arm 229 of the striker member 23! instead of being disposed behind the eccentric abutment 228 as in the previously described arrangement, is disposed ahead of it so that upon the operating stroke of the bar 223 the abutment 228 tends to move away from operating engagement with the striker member 23I and upon the return stroke, the

abutment 228 operates against arm 229 to restore the striker member 23! to its unoperated position.

.The bar 228 is provided with lug 46l upon which is pivoted lever 462. The upper arm 453 of lever 462 abuts the foremost surface of striker lever 229 and the lower arm 464 of the lever 462 has connected to it the rearmost end of tension spring 225 which, in the previously described arrangement, was connected to the striker arm 229. The arm 2230f striker'23l is thus between the .eccentric abutment228 and the arm 463 of lever .462. The operation of thisarrangement differs from thatofthe previously described .arrange ment in that the striker member 25H is operated thecombined action of the operating bar 223 and'spring 225 and is restored by action of the abutment 228, whereas in the previously described arrangement the striker 23l is operated bythei bar 223, through abutment 228 and is restored to unoperated position by the tension [spring 225. The specific details of the operation ofth arrangement shown; in Fig. 4 are as follows: When the operating bar 223 is reciprocated to theright, the abutment 228 tends to move away unmoved. When the inertia of that member is overcome, the striker 23lis operated very sharply, due to the energy stored in the spring 225.

}The striker 23! ji'sfljpositively brought to its idle ,brgfres't position upon the bar 223;

the return movement of General operation A complete description of the cycle of operations involved in the printing of a character and e in the operation of afunction will be described. Let'itbe assumed that a character is "to be printed, following which a function, such as s hift, is to be performed.

lY Astlie signal impulses representing the characten-areapplied to the selector magnet 61, the selector 'cam' barrel 62 is released for'operation'in themanner described in the hereinbefore men tioned Walter J. Zen'ner-"p'atent, and the selector .fingers are successively positioned in accordance with. thereceivedimpulses. Ab'out the time that by theeam 2|0.of cam barrel 62 and the clutch 32H becomes'iengaged, whereby rotation is imipartedto thecam's 216 and 24!, and the transfer cam. Almost immediately after the cams begin to:rotateLtlIetcami follower 2 [8 (Fig, 6) is operated by the cam 2l6 to effect an operation in ac 'be assumed to, be a shift function.

selector 47 (in the manner disclosed in the parent application) the particular stop pin 96which had been selected The setting of these discs causes previously to be cammed out of engagement with the type wheel stop arm .38 and as the code discs SI assume their new positions, a new alignment of notches is established which permits a stop pin 95 corresponding to the new character'code selection to move into the path of the type wheel stop arm 33. The withdrawal'of the previously selected stop pin 96 from engagement with the type Wheel stop arm 98 eliminates the restraint upon the stop arm, and type wheel shaft 44, which is under constant torque due to the friction clutch 46, is rotated until the arm 98 is stopped by the newly selected pin 96.

About the time that the transfer of the signal combination to the code discs 9| is effected, the next set of impulses is received by the selector magnet 61, which permits the cam barrel 62 to rotate and cooperate in the resetting of the selector fingers. These may now be reset because the combination representing the character which is to be printed has been transferred to the code discs. During the time that the cam barrel 62 is rotating to condition the selector mechanism in accordance with the second set of impulses and the type wheel is being rotated to its new position, the cam 2 is actuating its follower 243 (Fig. '7) to operate the spacing pawl 256,

which rotates the spacing ratchet 262 to space the carriage for printing of the next character. When the clutch 2 I I has completed a single revolution, it is disengaged by its throw-out lever 2I2 but is almost immediately permitted to be reengaged due to operation of the lever 2M as the cam barrel B2 approaches the end of a revolution after receiving the impulses for the next selection which, as previously mentioned, will The cams 2I6 and 24!, and the transfer cam thus begin a second revolution, and almost immediately the cam 2 I6 operates its follower 2 I8 (Fig. 6), whereby the bell crank lever 2I9 is rotated counterclockwise and the operating bar 223 is reciprocated rearwardly. The striker member 231 (Figs.

1 and 2) is operated by the bar 223 and strikes the impact member- I38 of the print hammer lever II! a sharp blow. The print hammer operating lever I I1 will be rocked counterclockwise (Fig. 2) and the print hammer I36 (Fig. (i) will strike the shank of the type pallet which has become aligned with it due to the stopping of the type wheel in a position corresponding to the character selection and the character will be printed on a page carried by the platen I39. Immediately after the character has been printed, the transfer cam will operate to transfer the shiftfunction selection to the code discs, and the type wheelIIlI will be rotate'dto a position corresponding to the shift function which is to be selected. It should be noted at this point that there is a stop position of the type wheel for every character to be printed or every function to be selected and that the printing of the character or the performance of the function can be 1 effected only after the type wheel has come t rest in the particular position.

v In order that the mechanism shall not come to rest with the shift function stored in the code discs, let it be assumed that another signal combination which may relate to any character or function is ap lied tov the selector magnet 61, which will result in setting of the selector fingers. During the reception of this third signal combination, the spacing cam-2M will be operating to advance the carriage one character space. After the third signal combination has been received and the operating cams ZIB and 24I, and the transfer cam have completed a cycle of rotation, the clutch throw-out lever 2 I2 will be tripped and the cams will begin to rotate. The cam 2I6 will operate the striker member 23 I, as previously described, but since the code combination relates to a function, no character is to be printed, and

therefore the print hammer I36 will be operated idly behind a dummy type pallet which has a short shank and which carries no character on the face thereof. Simultaneously with the operation of the operating bar 223, the lever arms 226 (Fig. 6) will be operated and the function selecting lever will be rocked and will engage an index pin 2II which has been positioned as a result of the stopping of the type wheel in shift selection position to form a fulcrum for the function selecting lever. The latching of function performing bar 280 behind latching projection '304 is due not only to shifting of the bar by the -most position.

Since, as previously stated, it is desirable that the platen carriage I 'll shall not be spaced when a function is performed, the space suppression function lever 394 will be operated, due to engage- .ment of lever 395 with an index pin 2', simultaneously with the shift function lever to withdraw the spacing pawl 255 from engagement with the spacing ratchet 262, andthe pawl will reciprocate idly against the arm GM of hell crank lever 406. At the conclusion of the shifting and space suppression operations, the cams 2I6 and I, and the transfer cam will come to" rest due to disengagement of the clutch 2| I by clutch throwout lever 2I2 and if no further signal combinations are applied to the selector magnet 61, the selector cam barrel 62 will come to rest with the last received code combination stored in the code disc selector 4?.

The universal adaptability-of the herein described receiving and printing mechanism to particular operating requirements and conditions is an outstanding characteristic of this invention. Characters to be printed may be identified with any code combinations as desired. merely by arranging the type pallets accordingly within the type wheel. Functions may be identified with any code combinations desired. and a plurality of functions may be identified with a single code combination, or a single function may be identified with a plurality of code combinations, merely by providing index in particular horizontal and vertical planes. From this it is apparent .that 'receiving and printing units iniaccordance with a single standard of manufacture may be suited to different individual requirements by providing different arrangements of pallets within the type wheel and different arrangements of function index pins. It will also be apparent that a unit already conforming to a particular requirement may be readily converted to conform to a different re quirement by changing the arrangement of type pallets within the type wheel, and the arrangement of function index pins. Such conversion of a typing unit is facilitated by having the type wheel at the top of the type wheel shaft, and readily removable therefrom, the set of index pins at the bottom of the type wheel shaft and also readily removable therefrom, and by having the sole rotational mounting of the type Wheel shaft between the type Wheel and the index pins, so that both ends of the shaft and the elements mounted thereat are readily accessible.

Although a particular embodiment of the invention has been described herein, it will be understood that the apparatus is capable of many modifications and substitutions in the various elements and combinations thereof within the scope of the appended claims.

What is 'claimedis:

1. In a printing apparatus having a stationary frame, a type wheel, a rotatable shaft mounting said type wheel, permutation mechanism for controlling the rotation of said shaft, means carried by said shaft for selecting functional operations to be performed, function performing means, a line feed operating lever to be actuated by said function performing means, a platen carrier, means for moving said carrier relative to said type wheel to form character spaces, line feeding means movable with said carrier, a plate" pivoted on said stationary frame for engaging said line feeding means in any position of said carriage, said plate provided with a depending in its effective position to thus render said function performing means effective irrespective of the inertia effect incident to the rocking of said plate to assur the complete operation of said line feeding means, and anti-chatter means comprising a reciprocable spring and link articulation between said extension and said line feed operating lever conformed to compensate for the oscillatory and reciprocatory movements of said extension and said link, respectively.

2. In a printing apparatus having a stationary frame, a type wheel, a rotatable shaft mounting said type Wheel, a permutation mechanism for controlling the rotation of said shaft, a function selecting abutment pin carried by said shaft, a sensing lever movable for selective engagement with said function selecting pin to have its function controlling movement thereby modified, a platen carrier, means for moving said carrier relative to said type Wheel to form character spaces, means movable with said carrier for rotating said platen, a plate pivoted on said stationary frame and exceeding in length the maximum travel of said carrier for engaging said platen rotating means in any position of said carriage, saidplate provided With a depending extension, said, extension having oscillatory movement imparted thereto incident to the pivotal operation of said plate, an operating lever for rocking said plate, means for actuating said operating lever, means articulated to said sensing lever to control the effectiveness of said actuating means, spring actuated means associated with and operable independently of said operating lever to latch said actuating means in its effective position to thus render said function performing means effective irrespective of the inertia effect incident to the rocking of said plate to assure the complete operation of said ALBERT H. REIBER.

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