Patent GB-450599-A (GB)
Abstract: 450,599. Calculating apparatus. MARCHANT CALCULATING MACHINE CO., 1475, Powell Street, Oakland, California, U.S.A. Dec. 18, 1934, No. 36324. Convention date, Dec. 18, 1933. [Class 106 (i)] In a machine for the four rules means are provided for effecting the process of division automatically such means including a mechanism for comparing the amount set up on the differential selecting mechanism (divisor) with an amount registered in aligned denominations of the totalizing-counter (dividend) and utilizing said comparing mechanism to control the sequential operation of the machine. By the provision of this comparing means the usual corrective addition cycle of operation prior to the lateral shaft of the totalizer carriage is in the case of certain problems eliminated. Keyboard. The numeral keys 100 Figs. 2, 3, and 5 are arranged in sections constituted by channel bars 101 supported on end members 108, 109 and adjustable by screws 133. The keys are held in raised position by springs 102 and are maintained in the bars 101 by means of strips 105 secured to the bars, each strip having a strip 107 of resilient material to diminish noise. Between the key sections is arranged decimal markers 113 any one of which can be rotated to display position by manipulating its finger lever 114. Differential mechanism. Associated with each key section is a notched bar 120 pivotally suspended by links 128, 129 and connected by pins and slot means to a pivoted member 132 provided with toothed sectors 138, 139. Each bar 120 is moved differentially in accordance with the key depressed and rocks the corresponding member 132 accordingly to transmit the movement through the sectors 138, 139 to a value indicating drum 140 and a gear 151 respectively. Each gear 151 forms a unitary structure, Figs. 6, 7, and 8 comprising a set of cams 152 ... 156, and spacers 157 secured to a sleeve 158 rotatable on a shaft common to all the denominations. Each cam has two high and two low points in staggered relation and is adapted to be felt by a pair of feelers 211, 219 on corresponding arms 210, 217, there being a pair of arms for each cam. The arms 210 are pivoted on a common shaft 213 supported by links 214 and each is connected by a link 216 to its arm 217 which is pivotally mounted on the shaft 218. These arms 210 are also connected to corresponding selection plates 172, 178, 184, 190 and 196, Fig. 15 pivotally mounted on a shaft 170. The plate 172 as shown in Fig. 2, carries gear wheels 173, 174, the latter being in mesh with a gear 171 keyed to a sleeve 169 ; the other plates are similar and have gears 177, 183 and 189 secured to the sleeve 169. When a clutch shaft 431 is operated cams 526, 527 are effective to withdraw a locking bar 236 from the central notch 238 on the selection plates to free them, and cams 220, 221, operate a plate 224 and a linkage 226 to rock the arms 210, 217 to permit one of the feelers to enter the notch of the aligned cam presented thereto and thereby effect a rocking of the corresponding arm 210 to displace the appropriate selection plate to one side or the other of its neutral position. The locking plate 236 is then restored to effective position to hold the setting and the arms 210, 217 are withdrawn to enable a second item to be entered while the machine is performing a calculating operation. By this means one of the idler gears 173 can be moved into mesh with gear wheels on one or other of the driving shafts 166, 167, 168 operatively connected through a reversing gearing to the main clutch shaft 429, Fig. 53. The gears on the shafts 166, 167, 168 have different numbers of teeth so that the movement transmitted to the sleeve 169 depends upon the value of the key depressed. A zero selection is effected by holding gear 189 against rotation by means of a pawl 201 which is retained in position when the selection plate 196 is swung to the left. Totalizer engaging mechanism. The totalizer numeral drums and pinions 273, Figs. 2, 16, 25 and 26 are mounted on a shaft 270 carried in a series of frames 266, connected by a bail 269 and pivotally mounted on a shaft 262 supported by cross frames of the laterally movable carriage 250 that is slidable on shafts 259, 260, Figs. 20, 21, 22 and 24. The pinions 273 gear with intermediate pinions 271 and when the bail 269 is lowered these intermediate pinions are adapted to be entrained by the gears 189 and to be actuated thereby during a calculating operation to transmit the item value set to the totalizer pinions. The pinions 271 are held aligned by pawls 319 which are freed when the bail is lowered. The lowering of the bail is effected by a cam 574, Fig. 48 on the shaft 431 rocking a lever 570 to which is connected a link 566 carrying rollers 568 engaging the bail. A latch lever 575 is provided to hold the bail in either its upper or lower position and is mechanically released and re-engaged at the proper time in the cycle. The lever 570 is also effective to rock the pawls 201 by connection with depending levers 586 excepting in those orders in which a zero has been set up. Each totalizer unit comprises a spider 274 secured to a sleeve 275 on the shaft 270 and carrying a ring of internal teeth 276 and a numeral bearing drum 279. Integral with the sleeve 275 is a sun gear 280 and snail cam 281. Meshing with the internal gear 276 is a pair of planet wheels 298 interconnected by another sun wheel 299 secured to one end of a sleeve 293 on which is loosely mounted a plate 292 fixed to the totalizer pinion 273 and carrying a plate 296 on which the planet gears are mounted. To the other end of the sleeve 293 is secured a spider 300 carrying an internal gear 301. Transfer mechanism. For the purpose of carrying tens a sleeve 294 on which the sleeve 293 is mounted supports a double armed member 304 on one arm of which a stub shaft 307 carrying planet gears 308, 309 is mounted. The gear 308 meshes with the internal gear 301 while the gear 309 engages the sun gear 280 of the adjacent lower order. The member 304 is provided with a toothed segment portion 311 meshing with teeth 312, Fig. 24 on a lever 313 pivoted on the shaft 272 of the intermediate gear wheels 271. Lever 313 is formed with an extension 314 engaging a lever 315, Fig. 22, mounted on the shaft 272 and carrying a roller 316 in the plane of the snail cam 281. In the units denomination the sleeve 293 is fixed. This arrangement enables actuation and transfer to take place simultaneously. By virtue of this continuous gearing the numerals will not be properly aligned when the gears 271 are in engagement with the actuating gears 189 and in order to bring them into alignment at the sight openings 318. When the gears are disengaged by raising the bail 269 the snail cam 281 and co-operating lever 315 are provided to back out the amount by which the numeral drums stood ahead of an even position. The downward movement of the lever 313 on the lowering of the bail is rotated anticlockwise by a projection thereon engaging a fixed shaft 339 Fig. 24, thereby lowering the lever 315. As the lever 313 does not permit the lever 315 to fall as fast as the steep face of the cam tried to move the lever 315 the cam as shown in Fig. 27, is mounted for limited movement on a sleeve on the sun gear 280 by a projection 287 on the spider extending into an elongation slot in the cam, a spring 289 being provided to hold the projection normally against one side of the slot. The cam may be provided with a stepped contour to ensure accurate line up. Zeroizing mechanism. To reset the numeral drums a shaft 320, Figs. 20, 21, and 24 is rocked clockwise and an arm 350 thereon disengages the holding pawls 319 by co-operation with a projection 351 thereon. At the same time levers 353 are rocked to place stops 354 into the path of projections 278, 302 on the numeral drums and toothed rings 301. During the movement of the pawls 319 projections 357 thereon engage projections 356 on the levers 313 to rock them counter-clockwise and through planetary pinions 308, 309, rotate the numeral drums to zero. Rebound is prevented by resilient members 355 mounted on the levers 353. The shaft 320 is operated on the depression of a clear key 373, Fig. 30, which couples a one revolution clutch 360 to an operating cam 363 and follower arm 364 operatively connected to the shaft 259 which is thereby rocked. An arm 370, Fig. 17 on the shaft 259 has a roller engaging an arm 372 on the shaft 320 whereby the latter is rocked. Operating by motor. A motor 640, Fig. 53 drives, through a flexible coupling 642, a shaft 643 with a slip clutch 644 and gear 645 to transmit the drive to a main clutch 428, a setting clutch 430, a clear clutch 360, a restore clutch 700 and carriage shift clutch. The main clutch 428, Figs. 34 and 35 comprises an annular gear 415 mounted on a flange 416 of a disc 417 with three apertures having rollers 420 co-operating with the inner periphery of the gear 415 and with flats on a disc 418 keyed to a sleeve 419 rotatably mounted on a fixed shaft 429. The gear 415 is constantly rotating but the discs 417, 418 are held against rotation by a clutch dog 395. To ensure immediate transmission of power the flange 416 has three recesses 425 for the reception of springs and metal cups 426 that are pressed by the springs against the inner periphery of gear 415. This clutch is utilized to drive through a reversing mechanism the shafts 166, 167, 168 of the totalizer actuating mechanism ; the clutch has a normal cycle of one-half a revolution and during each cycle drives the shafts 166, 167, 168 through 180‹, 90‹ and 30‹, respectively. The construction of the setting clutch 430 is similar but its driven side is keyed directed to its shaft 431. These clutches and the shafts 166, 167 are provided with a centralizing cam and lever to locate them in proper positions. The setting clutch 430 is under the control of any one of the control keys of the machine and depre