Patent GB-624371-A (GB)
Abstract: 624,371. Calculating-apparatus. REMINGTON RAND, Inc. Sept. 9, 1946, No. 27059. Convention date, Feb. 12. [Class 106 (i)] In a recording and computing machine a control unit is connected with an epicyclic gear train which is in continuous driving engagement with a totalizer actuating master-wheel and depression of a key couples the control unit with a rotating power shaft to rotate the masterwheel, which is then stopped in its corrected position by a stop element which is operated by the corresponding key and limits the rotation of the gears. The invention is described as embodied in the Remington machine described in Specification 374,109. Key operation of power shaft. Each numeral key lever 20, Fig. 1, has a depending lever 21 with a pin 51 which engages a shoulder 50 on a latch lever 48 and with a bent-over portion 26 which is adapted to engage a shoulder 27 on a lever 28 so that depression of a numeral key 20 turns its lever 48 clockwise and its lever 28 anticlockwise. A shoulder 30 on the displaced lever 28 is thus moved away from a pin 31 on a corresponding slide 32 which is then moved forward by a spring 44 and is moved back after one cycle. A pin 47 on the slide rotates the lever 21 clockwise out of the path of shoulder 27 so that, when the slide 32 is returned after one cycle, the lever 28 is in its latching position. As the slide moves forward a cam surface 57 on its front engages a pin 58 on an arm 60 and rotates the arm anticlockwise, thus rotating an arm 62 and via a spring 64, an arm 63, the upper portion of which is thus interposed between two balls 65 of the usual ball lock mechanism and prevents operation of another key. The engagement of a latch lever 48 with its lever 21 prevents the slide from moving forward again if a key 20 is accidentally pressed before the slide has fully returned. The rear of each slide 32, Figs. 1, 14, has a stud 70 which engages an arm 71 and turns it clockwise, rocking a lever 77 via a link 76 and moving a hook 80 so that a snatch pawl 15 engages a snatch roll 16 in known manner. An arm 82 engages a bail rod 83 and via arms 85 and 87 moves a link 90 rearward to disengage a latch member 94 from a dog 100, which is pivoted on a cam unit 104 and moves, resiliently, into engagement with a cam clutch member 101. The cam unit comprises four cams 195-198 and is loosely pivoted on the shaft 102 of the clutch member so that it will now turn with that shaft until the link 90 moves forward near the end of a cycle. Differential actuator mechanism. A totalizer 120 has its master-wheel 123, Figs. 1 and 3, rotated by an epicyclic gear-train which is continuously in mesh with one of two gears 125 for addition, or a pinion 127 for subtraction. A link 152 is reciprocated down and up, once per cycle, by the cam 197, Fig. 7, its downward movement being limited according to the value of the key depressed. This occurs because ten differential arms 161, Figs. 1, 6 and 7, are rotated by a shaft 158 connected via links 157, 154 with the link 152, and a stop element or block 162 on a pair of arms 163 is moved beneath one of the arms 161 by the action of the corresponding slide 32. This downward movement of the link 152 will rotate an arm 144 which, via planetary gears 142 will rotate a gear 145 clockwise, a sun-gear 141 being locked against rotation, and thus operate the master-wheel 123 via a gear 125 or 127. Subsequently, during the upward movement of link 152, the arm 144 is rocked counter-clockwise, but the sun-gear is free to rotate and the master-wheel 123 is locked. Thus the planetary gears 142 and sungear 141 will return to normal position. The means for locking the master-wheel include a pawl 168, Figs. 3 and 8, which is operated by rotation of a shaft 179, while the sun-gear is locked by means of a gear 178 on the same shaft 140 which is engaged by a pawl 180, Figs. 3 and 10, when a shaft 185 is rotated. The shafts 179 and 185 are rotated at the appropriate time by means of the cam 196, Fig. 8, when the cam unit is clutched to the power shaft 102, the cam operating via a roller 220 and linkages to reciprocate a link 237 and rotate the shaft 179. This, via linkages 191, 190, 188 rotates the shaft 185. Escapement mechanism. When the cam unit is clutched to the power shaft 102, as described above, the cam 195, Fig. 12, rotates counter-clockwise, a link 214 is moved horizontally against the action of a spring 208 and an element 217 is rocked to operate a known escapement mechanism. Restoring mechanism. The cam 198, Fig. 13, rotating counter-clockwise, will pivot a lever 266 about a pivot 95, thus moving a bail 274 rearward to engage projections 277 on the slides 32 and restore them to their normal position, the bail being subsequently moved forward by a spring 275 to allow slides 32 to move when the next key is depressed.