US3646268A - Carriage-shifting arrangement for teleprinters and terminal apparatus in general - Google Patents

Carriage-shifting arrangement for teleprinters and terminal apparatus in general Download PDF

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Publication number
US3646268A
US3646268A US803754A US3646268DA US3646268A US 3646268 A US3646268 A US 3646268A US 803754 A US803754 A US 803754A US 3646268D A US3646268D A US 3646268DA US 3646268 A US3646268 A US 3646268A
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Prior art keywords
lever
carriage
shaft
operative
stops
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US803754A
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English (en)
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Giuseppe Ricciardi
Bruno Sandrone
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Olivetti SpA
TIM SpA
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Olivetti SpA
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    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04L—TRANSMISSION OF DIGITAL INFORMATION, e.g. TELEGRAPHIC COMMUNICATION
    • H04L13/00—Details of the apparatus or circuits covered by groups H04L15/00 or H04L17/00
    • H04L13/18—Details of the apparatus or circuits covered by groups H04L15/00 or H04L17/00 of receivers
    • H04L13/186—Page printing; tabulating

Definitions

  • the shifting arrangement includes an actuating means controlled by a code combination for rendering a normally operative carriage shift mechanism inoperative and a normally inoperative carriagetabulating mechanism including a series of tabulating stops operative, and for rendering at least one counter-stop operative to selectively individually contact the tabulating stops for selectively arresting the carriage.
  • the present invention relates to a carriage-shifting arrangement for teleprinters and other terminal apparatus, of the type comprising a support for paper and a support for type characters to be written, one of said supports being mounted on the carriage of the apparatus, a step-by-step shift mechanism controlled by a code combination fornormally shifting said carriage one step upon the writing of each character, and a normally inoperative tabulating mechanism comprising a series of tabulating stops which are movable together with said carriage and are adapted to individually contact at least one counterstop.
  • the tabulating stops are normally set from time to time by the operator according to the format of the form on which it is desired to write.
  • one or more tabulation programs are generally preset on a tabulating bar. The program can be changed only by the intervention of the operator. These arrangements are therefore not adapted to be remotely controlled by telegraphic means or by means of a computer.
  • the object of the invention is to obviate the foregoing drawbacks
  • the technical problem solved by the invention is that of remote selection of the stops at which a carriage is to be arrested from time to time.
  • the shifting arrangement of the invention which is characterized by actuating means adapted on reception of at least one given code combination to render a shift mechanism temporarily inoperative and to render a tabulating mechanism comprising a series of tabulating stops operative, remotely controlled means being provided for rendering operative those tabulating stops at which a carriage is to be arrested from time to time.
  • the carriage is fixed to a rack, and the shift and tabulating mechanisms act on said rack through a single shaft, said shaft being adapted to be actuated under the control of the shift mechanism through the medium of a first coupling which is normally operative and under the control of the tabulating mechanism through the medium of a second coupling which is normally inoperative, the actuating means being adapted to deactivate said first coupling to render the shift mechanism inoperative and to activate said second coupling to actuate the tabulating mechanism.
  • FIG. 1 is a partial plan view of a teleprinter incorporating the carriage-shifting arrangement of the invention
  • FIG. 2 is a rear view of the shifting arrangement;
  • FIG. 3 is a partial section taken on the line III-III of FIG. 2;
  • FIG. 4 is a partial section taken on the line IV-IV of FIG. 2;-
  • FIG. Sis a'partial section taken on the line V-V of FIG. 2;
  • FIG. 6 is a partial section taken on the line VIVI of FIG. 2;
  • FIG. 7 is a partial plan view of the tabulating mechanism
  • FIG. 8 is a partial rear view ofthe mechanism of FIG. 7;
  • FIG. 9 is an exploded partial rear perspective view from the left of the shift mechanism.
  • FIG. 10 is another plan view of the mechanism of FIG. 7;
  • FIG. 11 is a partial section taken on the line XI XI of FIG.
  • FIG. 12 is a partial plan view of another detail of FIG. 2;
  • FIG. 13 is a partial section taken on the line XIIIXIII of FIG. 2;
  • FIG. 14 is a partial lateral section from the right showing another detail of FIG. 2;
  • FIG. 15 is a partial section taken on the line XV-XV of FIG. 2;
  • FIG. 16 is a partial lateral section from the right showing another detail of FIG. 2;
  • FIG. 17 is a partial lateral section from the right showing another detail of FIG. 2.
  • the carriage-shifting arrangement of the invention is adapted to be incorporated in a teleprinter.
  • the usual teleprinter paper support is shown in FIG. 1, comprising a platen 6 fixed on a shaft 7 rotatable in the fixed frame 5 of the machine.
  • the teleprinter is also equipped with a support for the type characters to be written, comprising a carriage 8 carrying a series of type wheels 9 and slidable by means of the rollers II along a guide 12 parallel to the platen 6.
  • the shaft 16 can be rotated step-by-step by a shift mechanism controlled by a code combination.
  • the shift mechanism thus shifts the carriage 8 one step upon the writing of each character.
  • the shaft 16 is connected via a coupling, indicated generally by the reference numeral 17, to a shaft 18.
  • a coupling indicated generally by the reference numeral 17
  • the shaft 18 in turn can be actuated in both directions by a driving shaft 21 which is rotated continuously by the action of the electric motor of the machine.
  • the coupling I7 has a driven part constituted by a sleeve 22 provided with front teeth 23 and fixed to the shaft 16, and a driving part comprising a first sleeve 24 provided with front teeth 26 for engagement with the teeth 23 and a second sleeve 27 which is rotatable but fixed axially on the shaft 16.
  • a worm wheel 28 constantly in mesh with a worm 29 fixed to the shaft 18.
  • Shaft 18 is normally held at rest by a spring-biased positioning member 31 which, by means ofa roller 32 (FIG. 3), constantly engages a recess 33 of a disc 34 fixed to the shaft 18.
  • the transmission ratio between the worm 29 (FIG. 2) and the worm wheel 28 and between the pinion l4 and the rack 13 is such that upon each revolution of the shaft 18 the rack 13 is shifted by one step.
  • the sleeve 24 is rotatable and slidable on the sleeve 27 and is adapted to be carried along in rotation by two crosspieces 36 fixed to the sleeve 27 in diametrically opposite positions and on which the sleeve 24 is slidable by means of two slots 37.
  • the sleeve 24 is normally in engagement with the sleeve 22, since it is biased axially by a compression spring 38 bearing at the other end on one side of the worm wheel 28.
  • the two-direction clutch 19 includes two driven parts each for one direction of rotation of the shaft 18 and constituted by two like discs 39 (FIG. 3) and 41 (FIG. 4), respectively, fixed to the shaft I8.
  • Each of the discs 39 and 41 has a cam profile and is provided with a shoulder 42, 43, respectively, the shoulders being angularly directed in opposite senses and offset from each other.
  • Each of the discs 39 and 41 has a corresponding driving part constituted by a sleeve 44 (FIG. 5) and a sleeve 46 (FIG. 6), respectively, both rotatable but fixed axially on the shaft 18 and to which there are fixed two gears 47 and 48 (FIG. 2).
  • the gear 47 (FIG. 5) is always in mesh with another gear 49 of equal diameter fixed to the shaft 21, while the gear 48 (FIG. 6) is always in engagement via an idler gear 51 with another gear 52 of equal diameter fixed to the shaft 21.
  • the sleeves 44 and 46 (FIGS. 5 and 6) are therefore rotated continuously in opposite directions by the shaft 21 and at the same angular velocity.
  • Each of the sleeves 44 and 46 is fixed to a disc53, 54, respectively, provided with a cam profile similarly to the discs 39 and 41 (FIGS. 3 and 4) and having a shoulder 56, 57 respectively (FIGS. 5 and 6).
  • the shoulder 56 of the disc 53 (FIG. 5) is angularly opposite to the shoulder 42 of the disc 39 (FIG. 3), while similarly the shoulder 57 of the disc 54 (FIG. 6) is angularly opposite to the shoulder 43 of the disc 41 (FIG. 4).
  • the two sleeves 44 (FIG. 5) and 46 (FIG. 6) are set on the shaft 18 in such manner that the plane of symmetry of the two shoulders 56, 57 (FIGS. 5 and 6) always coincides with the plane of symmetry of the two shoulders 42 and 43 (FIGS. 3 and 4) for each angular position assumed by the sleeves 44 and 46 (FIGS. 5 and 6) during their rotation.
  • the sleeves 44 and 46 can come into engagement individually and selectively with the corresponding driven discs 39 and 41, respectively, via relative connecting members constituted by a disc 58 (FIG. 5) and a disc 59 (FIG. 4), respectively, rotatable on the shaft 18 and normally held in a rest position by means of spring-biased positioning members 61 and 62, respectively.
  • a pin 63 projecting from both sides and on which a latch 66 and a push member 67 pivot, respectively.
  • the latch 66 and the push member 67 also are fixed together by means of a crosspiece 68 extending through an aperture 69 in the disc 58.
  • the latch 66 is adapted to be carried along in rotation by the shoulder 56 of the driving disc 53 by means of a shoulder 71, while the push member 67 is adapted to push the shoulder 42 of the driven disc 39 by means of a shoulder 72.
  • the latch 66 and the push member 67 are normally held with their shoulders 71 and 72 out of the path of the shoulders 56 and 42, in opposition to the elastic force of a spring 73, by a release lever 74 which normally cooperates with a stop tooth 76 of the latch 66.
  • the lever 74 is adapted to release the clutch 19 to cause the carriage 8 (FIG. 1) to advance by one step when said lever is rotated clockwise in any known manner on the reception of each writing or spacing code combination.
  • a latch 77 and a push member 78 similar to the latch 66 and the push member 67, and fast with one another through the medium of a crosspiece 80.
  • the latch 77 is adapted to be carried along in rotation by the shoulder 57 of the driving disc 54 by means of a shoulder 79, while the push member 78 is adapted to push the shoulder 43 of the driven disc 41 by means of a shoulder 81.
  • the latch 77 and the push member 78 are normally held with their shoulders 79 and 81 out of the path of the shoulders 57 and 43, in opposition to the elastic force of a spring 82, by a release lever 83 which normally cooperates with a stop tooth 84 of the latch 77.
  • the lever 83 is adapted to release the clutch 19 to cause the carriage 8 (FIG. 1) to move back by one step when said lever is rotated clockwise in any known manner on the reception of each return by one step code combination.
  • the tabulating mechanism Connected to the carriage 8 is a tabulating mechanism which essentially comprises a series of tabulating stops movable together with the carriage 8 to permit the arrest of the carriage 8 at predetermined columns of the paper. More particularly, the tabulating mechanism comprises a drum indicated generally by the reference numeral 86 (FIG. 2) and formed by two discs 87 and 88 interconnected by a series of peripherally disposed pins 89.
  • the drum 86 is releasably fixed on a shaft 91 rotatable in the frame of the machine. To the shaft 91 there is moreover fixed a gear 92 which is always in mesh with a corresponding gear 93 fixed to the shaft 16.
  • the discs 87 and 88 are each provided with a series of slots 94, 96, respectively, which are angularly inclined with respect to the radii of the corresponding discs 87 and 88.
  • the slots 94 and 96 are aligned with each other and are adapted to house the usual tabulating stops or plates 97 in correspondence with the various transverse positions of arrest of the carriage.
  • a disc 98 (FIG. 2) is fixed to the disc 88 of the drum 86 by means of the screws 101 and rests on shoulders 99 of the stops 97, which are thus normally locked in the slots 94 and 96 (FIG. 7).
  • Each stop 97 is provided with an individual profile 102 facing towards the periphery of the drum 86 and by means of which it is adapted to control the arrest of the drum 86 in accordance with three tabulation programs, two programs or a single program.
  • each stop 97 has a succession of teeth 103 and spaces 104 suitably disposed along three different tracks according to the positions of arrest that are desired for each tabulation program.
  • the teeth 103 of each track are adapted to cooperate individually with a projection 106, 107 and 108 (FIG. 8) of a corresponding counterstop 109, 111 and 112, respectively.
  • the three counter-stops 109, 111 and 112 are alike and are each constituted by a lever pivoting at one end on a pin 113 (FIG. 7) fixed to a carrying frame 1 14 and normally bearing at the other end by the action of a corresponding spring 116 (only one of these springs is shown in FIG.
  • the frame 114 comprises a lefthand crosspiece and a right-hand crosspiece 120.
  • the frame 114 can pivot in turn in two arms 118 and 119 of a bail or bridge element 121 fulcrumed on a shaft 122 fixed to the frame of the machine.
  • the frame 1 14 is caused to bear by means of the pin 113 against a shoulder 123 of a lever 124 and, on the other hand, is retained by means of a pin 126 by a shoulder 127 of a release lever 128 (FIG. 9) in such manner as to hold the projections 106, I07 and 108 (FIG. 8) of the counter-stops 109, 111 and 112 out of the path of the profiles 102 (FIG. 2) of the stops 97.
  • the lever 124 (FIG. 7) is fulcrumed at one end on a shaft 129 fixed to the frame of the machine and engages at the other end a guide slot 131 in the crosspiece of the frame 114 and, by the action of a spring 132, normally bears against the pin 113 of the frame 114. Moreover, the lever 124 is adapted to cooperate with the pin 113 by means of an inclined surface 133.
  • the release lever 138 (FIG. 9) is fulcrumed on a fixed shaft 134 and normally bears by the action of a spring 136 against a stop pin 137.
  • the lever 128 is adapted to be turned clockwise to release the frame 114 in the manner described hereinafter.
  • a latch 138 adapted to cooperate with the fixed shaft 129 and normally bearing thereon as in the drawing due to the action of a spring 139.
  • the latch 138 is engaged in a guide slot in the crosspiece 120 of the frame 114 and by means of a shoulder is able to cooperate with a shoulder of the crosspiece 115 of the frame 114.
  • a lever 141 (FIG. 10) which is slidable on the fixed shaft 129 by means of a slot 140.
  • One edge 145 of the slot is adapted to cooperate with the fixed shaft 129 to define the maximum stroke of the lever I41 and, therefore, of the frame 114.
  • the lever 14] is disposed by means of a shoulder 142 in the path of a pin 143 fixed to the gear 92.
  • the pin 143 is located in the position shown in the drawing to the left of the shoulder 142 at a distance from the latter greater than the distance of the shoulder 145 from the fixed shaft 129.
  • a circular slot 144 is formed in the lever 141 to pennit the passage of the pin 126 of the frame 114.
  • the slot 144 is concentric with the pin 113 to permit the frame 114 to turn about said pin 113.
  • each of the counter-stops 109, 111 and 112 is provided with a projection 146, 147 and 148, respectively, adapted to cooperate with a baffle 149 slidable vertically on a fixed pin 151.
  • the baffle 149 is provided with a recess 152 which can be aligned selectively in correspondence with any one of the three projections 146, 147 and 148, the three positions of the baffle 149 being defined by a springbiased positioning member 153.
  • the baffle 149 is connected by means of a connecting rod 154 to an arm 156 of a lever 157 which can turn on a fixed shaft 158 and is provided with another two like arms 159, 161 disposed perpendicularly to the arm 156.
  • Two pins 162 and 163, respectively, are fixed to the two arms 159 and 161 at an equal distance from the shaft 158.
  • the pin 162 is engaged in a slot 164 in a slider 166 and in a notch 167 in a slider 168, while the pin 163 is engaged in a slot 169 similar to the slot 164 in a slider 171 and in a second notch 172 in the slider 168.
  • the notches 167 and 172 are alike and have a length equal to 1% times that of the slots 164 and 169.
  • the three sliders 166, 168 and 171 are normally urged by respective springs 173, 174 and 176 against a fixed stop shaft 177.
  • the lever 157 is shown with the arms 159 and 161 in the vertical position, to which there corresponds a position of the baffle 149 in which the recess 152 is aligned with the projection 147 of the intermediate counter-stop 111.
  • the pins 162 and 163 are situated in the center of the slots 164 and 169 of the sliders 166 and 171 and at a distance from the right-hand end, in the drawing, of the notches 167 and 172 in the slider 168 which is equal to the length of the slots 164 and 169.
  • Each of the sliders 166, 168 and 171 is connected by a pin and slot to a bail 178, 179 and 181, respectively, turning on a fixed shaft 182 and normally urged against the corresponding slider by a spring 183, 184 and 186, respectively, having a force smaller than that of the corresponding springs 173, 174 and 176.
  • the three bails 178, 179 and 181 can be turned anticlockwise individually upon the reception of a corresponding code combination transmitted by a distant telegraph station, or set on the spot by the operator on the keyboard of the machine, to select a corresponding tabulation program.
  • Each bail 178, 179 and 181 is moreover adapted to cooperate with a lever 187 turning on the shaft 182 and normally urged by a spring 188 against the end of a slot 189 in a slider 191.
  • the latter is slidable on a fixed shaft 190 and, due to the action of a spring 193 stronger than the spring 188, is normally urged against the stop shaft 177.
  • the slider 191 is provided with a lug 194 adapted to cooperate with a pin 196 fixed to the release lever 128.
  • the shaft 16 (FIG. 2) can be actuated in both directions by a driving shaft 197 via a two-direction coupling indicated generally by the reference 198.
  • the driving shaft 197 can be rotated by the shaft 21 through a cyclic clutch indicated generally by the reference 201 in FIG. 2.
  • the clutch 201 comprises a driven part constituted by a disc 202 (FIG. 11) fixed to the shaft 197. This is normally locked in a rest position by means of a spring biased positioning member 203. To the disc 202 there is fixed a pin 206 on which there is fulcrumed a latch 207 connected to the disc 202 by means of a spring 208.
  • the latch 207 is adapted to engage by means of a shoulder 211 a corresponding shoulder 212 of a sleeve 213 fixed to a driving gear 214 (FIG. 2) rotatable on the shaft 197.
  • the gear 214 is rotated continuously by a gear 216 fixed to the main shaft 21.
  • the latch 207 (FIG. 11)
  • the two-direction coupling 198 (FIG. 2) comprises a driven part constituted by a sleeve 221 rotatable but fixed axially on the shaft 16.
  • the sleeve 221 is integral with a bevel pinion 222 for the advance of the carriage 8 and with a bevel pinion 223 having a diameter half that of the pinion 222 and concentric with the latter for the return of said carriage.
  • the sleeve 221 is connected to the shaft 16 via a friction coupling 199 comprising a sleeve 224 rotatable on the sleeve 221 and slidable by means of two slots 226 on two crosspieces 227 fixed to the shaft 16 in diametrically opposite positions.
  • the sleeve 224 is provided with a disc 228 adapted to be carried along in rotation on both sides through the medium of two rings 229 and 231 made of material having a high coefficient of friction.
  • the ring 229 can be carried along in rotation directly by the two pinions 222 and 223, while the ring 231 can be carried along in rotation in the same direction by a disc 232 rotatable on the sleeve 224 and engaging a series of pins 233 fixed to the pinions 222 and 223.
  • the disc 232 is normally biased axially by a series of compression springs 234 in such manner as to press the two rings 229 and 231 against the corresponding driving surfaces, the compression springs 234 bearing at the other end against another disc 236 rotatable on the sleeve 224 and engaging the pins 233.
  • a series of stop rings 237 fixed to the pins 233 prevent the disc 236 slipping off 'said pins 233.
  • the pinion 222 is always in mesh with a bevel pinion 238 rotatable on the shaft 197, while the pinion 223 is always in mesh with another pinion 239 rotatable on the shaft 197 and similar to the pinion 238, the two pinions 238 and 239 being locked axially on the shaft 197 on opposite sides with respect to the shaft 16.
  • Each of the pinions 238 and 239 is provided with a pin 241, 242, respectively, projecting in the axial direction and adapted to engage in a corresponding recess of a series of recesses 243, 244 formed in flanges 246 and 247, respectively, of a sleeve 248 forming the driving part of the coupling 198.
  • the sleeve 248 is slidable, but locked angularly, on the shaft 197 through the medium of a slot 249 engaging a pin 251 fast with the shaft 197.
  • the sleeve 248 is normally held in an inoperative axial position, with the flanges 246 and 247 at an equal distance from the pins 241 and 242, by means of a crossshaped lever 252 (FIG. 12) having a roller engaged between the two flanges 246 and 247.
  • the lever 252 is fulcrumed on a fixed shaft 253 and is normally positioned as shown in FIG. 12 by means of a spring-biased positioning member 254.
  • the lever 252 is moreover adapted to assume selectively two turned positions defined by the positioning member 254 and symmetrical with respect to the position shown in the drawing, for engaging the sleeve 248 with the pinion 238 or the pinion 239.
  • the lever 252 is provided with two pins 256 and 257, respectively, disposed symmetrically with respect to the shaft 253 and which are each able to engage selectively corresponding slots 258 and 259, respectively, formed in a twoposition slider 261.
  • the slots 258 and 259 each comprises a widened portion 262, 263, respectively.
  • said slider is moreover adapted to engage one or the other of two fixed pins 267 and 268, respectively, in line with the pins 256 and 257.
  • the slider 261 is moreover provided with a slot 269 by means of which it is engaged with a pin 271 of an operating lever 272 fulcrumed on the pin 268.
  • the operating lever 272 is adapted to be turned about the pin 268 to operate the slider 261 in the manner described hereinafter.
  • the slider 261 is moreover provided with two projections 273 and 274.
  • the projection 273 is adapted to cooperate with a pin 276 of a lever 277 pivoted at 278 and connected in turn to a slider 279.
  • the slider is connected to the slider 191 (FIG. 9) through the medium of a lever 281 fulcrumed on a fixed spindle 282.
  • the projection 274 (FIG. 12), on the other hand is adapted to cooperate with a pin 283 of a slider 284 connected in turn to a lever 280 (FIG. 9) fulcrumed on the spindle 282.
  • the lever 280 is connected to a slider 286 slidable on the shaft and normally urged against the stop shaft 177 by a spring 287.
  • the slider 286 is moreover connected by a pin and slot to a lever 288 fulcrumed on the shaft 182 and nonnally urged against the slider 286 by a spring 289 having a force less than that of the spring 287.
  • the lever 288 is adapted to be turned anticlockwise in any known manner to shift the slider 286 on reception of a carriage return" code combination transmitted by a distant telegraph station or set on'the spot by the operator on thekeyboard of the machine.
  • the cam 291 (FIG. 16) cooperates with a lever 296 rotatable on the shaft 219 and connected in turn by a pin and slot to a lever 298 fulcrumed on a pin 299.
  • the lever 298 is adapted to cooperate with the pin 126 of the frame 114 by means of a lug 301 and is normally held by the cam 291 with the lug 301 slightly spaced from the pin 126.
  • the cam 292 (FIG.
  • the cam 293 (FIG. 13) cooperates with another lever 307 rotatable on the shaft 219 (FIG. 11).
  • the lever 307 is connected on the one hand via a link 308 to the release lever 218 of the clutch 201 and on the other hand via a connecting rod 309 (FIG. 13) to a forked lever 311 (FIG. 2) adapted to open or disengage the coupling 17.
  • the lever 311 is constantly in engagement with a flange 313 of the sleeve 24.
  • the sleeve 294 (FIGS. 2 and 14) is fast with a disc 314 forming the driven part of a clutch having a cycle of 360 in two stages of 120 and 240, respectively, and indicated generally by the reference 316.
  • the disc 314 is normally locked in the position shown in the drawing by a spring-biased positioning member 317 adapted to engage a corresponding recess 318 in the disc 314.
  • This disc is moreover provided with a recess 312 disposed at 120 anticlockwise from the recess 318, and with two cam surfaces 319 and 321, respectively.
  • a pin 323 (FIG. 15) on which there can pivot a latch 324 connected by means of a spring 326 to a pin-327 fixed to the disc 314 (FIG. 14).
  • the latch 324 (FIG. 15) is adapted to engage by means of a shoulder 328 a corresponding shoulder 329 of a sleeve 331 fixed to the driving gear 214 (FIG. 2) and is connected by means of a pin 332 (FIG. 15) to a crank 333 (FIG. 14) turning on the extension of the pin 323 on the opposite side to the disc 314.
  • the shoulder 329 is offset angularly with a delay with respect to the shoulder 212 (FIG. 11) of the sleeve 213.
  • the crank 333 (FIG. 14) is connected to a link 336 connected in turn to a lever 337 pivoting on a pin 338 fixed to the disc 314.
  • Thelatch 324 (FIG. 15) is nonnally held by means of a projection 339 in the position shown in the drawing, with the shoulder 328 out of the path of the shoulder 329, by-a release lever 341 for the first stage of the cycle.
  • This lever is fulcrumed on the shaft 219 and, due to the action of a spring 34, is normally caused to bear by means of a roller 343 against cam profiles 344 and 346 (FIG. 12), respectively, of the sliders 279 and 284.
  • the lever 337 (FIG. 14), on the other hand, is adapted to cooperate by means of a projection 347 with a shoulder 348 of a release lever 349 for the second stage of the cycle.
  • This lever is fulcrumed on the shaft 219 and is provided with a notch 351 in which there is normally engaged a pin 352 of a link 353 connected in turn to a lever 354 also fulcrumed on the shaft 219.
  • a spring 356 stretched between the link 353 and the lever 354 normally urges the pin 352 against the base of the notch 351.
  • the link 353 is moreover adapted to cooperate with a projection 357 of the lever 281 (FIG. 9).
  • the lever 354 (FIG. 14) is connected via a tie rod 358 to a bail 359 which can turn on a fixed spindle 361 and is adapted to cooperate with a lever 363 fulcrumed on a fixed pin 364 (FIG. 10.
  • the lever 363 is adapted to cooperate by means of a pin 366 with a control lever 367 which can turn on the shaft 129 and is engaged by means of a pin 368 in a slot 369 in the frame 114.
  • the arrangement operates in the following manner.
  • the bail I78 turning anticlockwise, causes the lever 187 to turn in the same direction and then shift the slider 191.
  • the latter causes the lever 281 to turn anticlockwise and, on the other hand, by means of the lug 194, causes the lever 128 to turn clockwise in opposition to the force of the spring 136, thus releasing the pin 126 of the frame 114.
  • the frame Due to the action of the three springs 1 16 (FIG. 7), the frame then turns clockwise until it bears by means of the pin 126 against the lug 301 (FIG. 16) of the lever 298.
  • the lever 281 (FIG. 9), on turning anticlockwise, causes the link 353 (FIG.
  • the lever 281 causes the slider 279 to shift to the right. Said slider then causes the lever 277 (FIG. 12) to turn anticlockwise and shift the slider 261 to the left by means of the pin 276 so as to engage the pins 267 and 257 in the open-ended slot 264 and the slot 259 and disengage the pins 256 and 268 from the slot 258 and the open-ended slot 266. Moreover, the slider 279 pushes the roller 343 (FIG. 15) by means of the cam surface 344 and causes the lever 341 to turn clockwise until it releases the latch 324 of the clutch 316. Due to the action of the spring 326, the latch 324 then pivots clockwise until it brings the shoulder 328 into the path of the shoulder 329, thus closing or engaging the clutch 316.
  • the bail 178 (FIG. 9) returns clockwise and thus brings the slider 166, the lever 187, the slider 191, the slider 279 and the release lever 341 (FIG. 15) back into their initial position.
  • the lever 341 thus presets the arrest of the sleeve 294 after rotation through 360.
  • the lever 128 (FIG. 9), no longer affected by the lug 194 of the slider 191, then turns anticlockwise due to the action of the spring 136 until it bears against the pin 126 of the frame 114 in the new position reached.
  • the link 353 (FIG. 14), no longer affected by the projection 357 of the lever 281 (FIG. 9), turns clockwise due to the action of the spring 356 (FIG.
  • this last-mentioned lever pushes the slider 261 upwardly by means of the pin 271 and the slider now turns anticlockwise about the fixed pin 267 and, by means of the slot 259 engaged with the pin 257, also causes the lever 252 to turn anticlockwise, the pin 256 being able to tune: as.
  • the cam 291 causes the lever 296 to turn clockwise and said lever in turn causes the lever 298 to turn anticlockwise.
  • the last-mentioned lever allows the frame 114 (FIG. 7) to turn clockwise about the pin 113, urged by the springs 116.
  • the projections 147 and 148 (FIGS. 8 and 9) of the counter-stops 111 and 112 are then arrested by the baffle 149, while the frame 114 bears against the fixed shaft 129 (FIG. 7), bringing the projection 106 of the selected counter-stop 109 into the path of the profiles 102 (FIG. 2) of the stops 97 ofthe drum 86.
  • the cam 293 causes the lever 307 to turn clockwise and said lever then causes the fork 311 (FIG. 2) to turn anticlockwise by means of the connecting rod 309, thus causing the sleeve 24 to slide downwardly and opening the coupling 17.
  • the lever 307 causes the lever 218 to turn clockwise and disengage the latch 207 of the clutch 201. Due to the action of the spring 208, the latch 207 then turns clockwise until the shoulder 211 is brought into the path of the shoulder 212 of the sleeve 213, thereby presetting the closing of the clutch 201.
  • the frame 114, the counter-stop 109 and the lever 141 are guided by the shaft 129, while the pin 113 turns clockwise about the shaft 122.
  • the pin 113 encountering the surface 133, causes the lever 124 to turn slightly clockwise, the energy ofimpact of the drum 86 against the counter-stop 109 is dissipated elastically by the spring 132.
  • the arrest of the drum 86 moreover determines the stopping of the shaft 16 which, however, because of the friction coupling 199, permits the rotation of the pinion 222.
  • the frame 114 causes the lever 367 (FIG. 10) to turn clockwise. Said lever engages the pin 366 of the lever 363, bringing it back anticlockwise into the inoperative position. Via the bail 359 (FIG. 14), the tie rod 358, the lever 354 and the link 353, the lever 363 causes the lever 349 to turn clockwise until the shoulder 347 of the lever 337 is disengaged. Due to the action of the spring 326 (FIG. 15), the lever 337 then turns clockwise together with the latch 324 until the latter brings the shoulder 328 into the path of the shoulder 329 of the sleeve 331, thus presetting the second stage of the cycle of the clutch 316.
  • the lever 307 causes the lever 218 to turn anticlockwise until it is brought back again into the path of the projection 217 of the lever 207. Then, as soon as the projection 217 encounters the lever 218, the lever 207 is turned anticlockwise and thus opens or disengages the clutch 201, as a result of which the shaft 197 is stopped in its rest position, held by the positioning member 203.
  • the cam 292 causes the lever 302 to turn clockwise and, via the block 304 (FIG. 12), said lever causes the lever 272 to turn anticlockwise, bringing the slider 261, the lever 252 and the sleeve 248 back to the inoperative state.
  • the cam 291 causes the lever 296 to turn anticlockwise and thus turns the lever 298 in the opposite direction.
  • the last-mentioned lever now pushes the pin 126, causing the frame 114 (FIG. 10) to turn anticlockwise about the pin 113 together with the latch 138, which is urged by the shoulder of the frame 114.
  • the frame 114 jumps to the right owing to the action of the springs 116 and the spring 139, turning the pin 113 anticlockwise about the shaft 122 until the pin 113 (FIG. 7) is arrested against the shoulder 123 of the lever 124. Moreover, by means of the slot 369 (FIG. 10) and the pin 368, the frame 114 brings the lever 367 back to the inoperative state, releasing the lever 363 and, therefore, also the bail 359 and the levers 354 and 349 (FIG. 14). The lever 349 released in this way then turns anticlockwise due to the action of the spring 372 until it is brought back into the position shown in dashes in the drawing.
  • the usual writing operations can be effected in any position reached by the carriage 8 (FIG. 1).
  • the lever 74 FIG. is turned clockwise until it releases the latch 66 of the twodirection clutch 19. Due to the action of the spring 73, the latch 66 then turns clockwise until it bears on the cam surface of the disc 53, while by means of the pin 68 it causes the push member 67 (FIG. 3) to turn in the same direction until the shoulder 72 is brought in front of the shoulder 42 of the driven disc 39.
  • the lever 74 (FIG. 5) is released and returns anticlockwise to its rest position in the path of the projection 76 of the latch 66.
  • the projection 76 of the latch 66 encounters the lever 74, as a result of which the latch 66 turns anticlockwise together with the push member 67 (FIG. 3), disengaging the corresponding shoulders 56 and 42.
  • the disc 58 is immediately arrested together with the shaft 18 by the positioning member 31, which reengages the recess 33 of the disc 34 by means of the roller 32, while the disc 53 (FIG. 5) continues its clockwise rotation, carried along by the shaft 21.
  • the lever 83 (FIG. 6) is turned clockwise until it releases the latch 77 of the two-direction clutch 19. Due to the action of the spring 82 (FIG. 4), the latch 77 then turns anticlockwise until it bears on the cam surface of the disc 54 (FIG. 6) together with the push member 78 (FIG. 4), which brings it shoulder 81 in front of the shoulder 43 of the driven disc 59.
  • the lever 83 (FIG. 6) is released and returns anticlockwise to its rest position.
  • the projection 84 of the latch 77 encounters the lever 83, as a result of which the latch 77 is turned clockwise together with the push member 78 (FIG. 4), disengaging the corresponding shoulders 57 and 53.
  • the disc 34 (FIG. 3) is immediately arrested together with the shaft 18 by the positioning member 31, which reengages the recess 33, while the disc 54 (FIG. 6) continues its anticlockwise rotation, carried along by the shaft 21.
  • the slider 284 engages the roller 343 by means of the cam surface 346, thus causing the lever 341 (FIG. 15) to turn clockwise and then initiate the first stage of the cycle of the clutch 316.
  • the lever 288 (FIG. 9) is turned clockwise, bringing the sliders 286 and 284 (FIG. 12) and the release lever 341 (FIG. 15) back to the rest position.
  • the cam 292 causes the lever 302 to turn anticlockwise and, through the medium of the block 304 (FIG. 12), the lever causes the lever 272 to turn clockwise and lift the slider 261. Pivoting on the pin 268, said slider then turns clockwise and, by means of the slot 258, causes the pin 256 and the lever 252 to swing in the same direction, whereby the sleeve 248 is shifted to the right in FIG. 12 until one of the recesses 244 thereof engages with the pin 242 of the pinion 239.
  • the cam 291 (FIG. 16), on the other hand, causes the lever 298 to be disengaged from the pin 126 of the frame 114.
  • the clutch 201 driving the shaft 197 and acting through the sleeve 248, the piniona 239 and 223, the gears 14 and 93, the rack 13 and the gear 92, causes the carriage 8 to perform a continuous return travel and the drum 86 to execute an anticlockwise rotation (FIGS. 7 and 10) at a speed twice the tabulation speed, since the diameter of the pinion 223 (FIG. 2) is one half of that of the pinion 222.
  • the clutch 316 (FIG. 14) is temporarily opened or disengaged by the lever 349, which is now located with the shoulder 348 in the path of the shoulder 347 of the lever 337.
  • the pin 143 serves as an end-of-tabulation-program stop.
  • the carriage 8 (FIG. 1) is shifted to the right.
  • the pin 143(FIG. 10) strikes against the shoulder 142 of the lever 141.
  • the lever is then shifted to the left together with the frame 114, as in the case of the stop 97 against a counter-stop 109, 111, 112, as a result of which the tabulation cycle is completed.
  • a carriage shifting arrangement comprising:
  • an actuating means controlled by a plurality of code comoinations for individually selectively rendering said counter-stops operative, and for temporarily rendering said shift mechanism inoperative and said tabulating mechanism operative.
  • said actuating means comprises a plurality of code responsive members, each of said members being operable upon the reception of one of said code combinations, a selecting member differentially movable to a plurality of positions under the control of said code responsive members, each of said selecting member positions corresponding to one of said tracks, said selecting member being operable for individually selectively rendering said counter-stops operative, and a common member operable by each of said code responsive members for rendering said shift mechanism inoperative and said tabulating mechanism operative.
  • each of said code responsive members comprises a slide movable through a constant stroke; and wherein said actuating means further comprises a three-armed lever, said selecting member being linked to one arm of said lever, and said slides being engageable with the other two arms of said lever for differentially moving the lever to different positions corresponding to and upon the operation of each of said slides.
  • a teleprinter as recited in claim 1; wherein said shifting arrangement further includes a rack affixed to said carriage and a shaft drivingly engaging said rack for shifting the carriage; and wherein said shift mechanism is drivingly connectable to said shaft by a normally engaged first coupling and said tabulating mechanism is drivingly connectable to said shaft by a normally disengaged second coupling; and wherein said actuating means is operable to disengage said first coupling to render the shift mechanism inoperative and to engage said second coupling to render the tabulating mechanism operative upon reception of any of said code combinations; and wherein said shift mechanism comprises a two-direction clutch drivingly connected to said first coupling for cyclically shifting the carriage step-by-step, said clutch comprising a driven part having a pair of shoulders affixed thereto, said driven-part shoulders being angularly opposed and angularly offset from each other, a pair of driving parts continuously rotated in opposite directions at the same angular velocity and each having a shoulder affixed thereto, the plane of
  • a teleprinter as recited in claim 4; wherein said actuating means is operative to initiate a first actuating cycle upon reception of one of said code combinations and, during a first stage of said first cycle, to render one of said counter-stops operative and, during a second stage of said first cycle initiated when one of said tabulating stops contacts said one counter-stop to render said one counter-stop inoperative; and wherein said second coupling is engageable in a first direction for rotating said shaft in one direction to produce carriagetabulating movement and is engageable in a second direction for rotating said shaft in the other direction to produce carriage-return movement; and wherein said actuating means is operative to initiate a second actuating cycle upon reception of another of said code combinations and, during a first stage of said second cycle, to engage said second coupling in said second direction; and wherein said actuating means further includes release means for rendering said counter-stops inoperative upon reception of said other code combination, said release means being operative to initiate a second stage of said second cycle upon completion of said carriage

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  • Engineering & Computer Science (AREA)
  • Computer Networks & Wireless Communication (AREA)
  • Signal Processing (AREA)
  • Mechanical Operated Clutches (AREA)
  • Transmission Devices (AREA)
US803754A 1968-03-02 1969-03-03 Carriage-shifting arrangement for teleprinters and terminal apparatus in general Expired - Lifetime US3646268A (en)

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Application Number Priority Date Filing Date Title
IT5074268 1968-03-02

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US3646268A true US3646268A (en) 1972-02-29

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CH (1) CH483929A (enExample)
DE (1) DE1911693B2 (enExample)
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3777870A (en) * 1970-09-16 1973-12-11 Olympia Werke Ag Escapement controlling tabulating apparatus
US3927274A (en) * 1973-07-12 1975-12-16 Olivetti & Co Spa Control for printing and service functions of an accounting machine
US3938644A (en) * 1973-06-12 1976-02-17 Ing. C. Olivetti & C., S.P.A. Horizontal tabulation apparatus for accounting machines or the like
US3985220A (en) * 1970-10-23 1976-10-12 Olympia Werke Kg Tabulator apparatus for a typewriter carriage moving in steps of different length
US4149619A (en) * 1971-09-14 1979-04-17 Casio Computer Co., Ltd. Tabulation control systems for printing apparatus

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2111387A (en) * 1935-11-27 1938-03-15 Teletype Corp Printing telegraph apparatus
US2529238A (en) * 1946-07-27 1950-11-07 Western Union Telegraph Co Printing telegraph apparatus
US2701045A (en) * 1951-11-08 1955-02-01 Teletype Corp Backspacing mechanism
US2956120A (en) * 1956-08-22 1960-10-11 Int Standard Electric Corp Tabulator mechanism for teleprinters
US3045798A (en) * 1960-07-15 1962-07-24 Royal Mcbee Corp Banking and escapement apparatus for electric typewriters or the like
US3121487A (en) * 1960-04-11 1964-02-18 Olivetti & Co Spa Paper carriage control mechanism for accounting machines
US3225886A (en) * 1963-01-17 1965-12-28 Royal Typewriter Co Inc Multi-uniform and variable pitch escapement mechanism
US3283872A (en) * 1964-06-03 1966-11-08 Royal Typewriter Co Inc Tabular stop assembly
US3389774A (en) * 1965-10-05 1968-06-25 Scm Corp Typewriter carriage control

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2111387A (en) * 1935-11-27 1938-03-15 Teletype Corp Printing telegraph apparatus
US2529238A (en) * 1946-07-27 1950-11-07 Western Union Telegraph Co Printing telegraph apparatus
US2701045A (en) * 1951-11-08 1955-02-01 Teletype Corp Backspacing mechanism
US2956120A (en) * 1956-08-22 1960-10-11 Int Standard Electric Corp Tabulator mechanism for teleprinters
US3121487A (en) * 1960-04-11 1964-02-18 Olivetti & Co Spa Paper carriage control mechanism for accounting machines
US3045798A (en) * 1960-07-15 1962-07-24 Royal Mcbee Corp Banking and escapement apparatus for electric typewriters or the like
US3225886A (en) * 1963-01-17 1965-12-28 Royal Typewriter Co Inc Multi-uniform and variable pitch escapement mechanism
US3283872A (en) * 1964-06-03 1966-11-08 Royal Typewriter Co Inc Tabular stop assembly
US3389774A (en) * 1965-10-05 1968-06-25 Scm Corp Typewriter carriage control

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3777870A (en) * 1970-09-16 1973-12-11 Olympia Werke Ag Escapement controlling tabulating apparatus
US3985220A (en) * 1970-10-23 1976-10-12 Olympia Werke Kg Tabulator apparatus for a typewriter carriage moving in steps of different length
US4149619A (en) * 1971-09-14 1979-04-17 Casio Computer Co., Ltd. Tabulation control systems for printing apparatus
US3938644A (en) * 1973-06-12 1976-02-17 Ing. C. Olivetti & C., S.P.A. Horizontal tabulation apparatus for accounting machines or the like
US3927274A (en) * 1973-07-12 1975-12-16 Olivetti & Co Spa Control for printing and service functions of an accounting machine

Also Published As

Publication number Publication date
FR1600685A (enExample) 1970-07-27
DE1911693B2 (de) 1976-09-02
CH483929A (it) 1970-01-15
DE1911693A1 (de) 1969-11-27

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