US3652826A - Binary entry apparatus for a calculating machine - Google Patents

Binary entry apparatus for a calculating machine Download PDF

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Publication number
US3652826A
US3652826A US1627A US3652826DA US3652826A US 3652826 A US3652826 A US 3652826A US 1627 A US1627 A US 1627A US 3652826D A US3652826D A US 3652826DA US 3652826 A US3652826 A US 3652826A
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Prior art keywords
shaft
gear wheel
relationship
clutch
effective
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US1627A
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English (en)
Inventor
Rene Chekroun
Jean-Claude Ragot
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Unisys Corp
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Burroughs Corp
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Assigned to BURROUGHS CORPORATION reassignment BURROUGHS CORPORATION MERGER (SEE DOCUMENT FOR DETAILS). DELAWARE EFFECTIVE MAY 30, 1982. Assignors: BURROUGHS CORPORATION A CORP OF MI (MERGED INTO), BURROUGHS DELAWARE INCORPORATED A DE CORP. (CHANGED TO)
Assigned to UNISYS CORPORATION reassignment UNISYS CORPORATION MERGER (SEE DOCUMENT FOR DETAILS). Assignors: BURROUGHS CORPORATION
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    • G—PHYSICS
    • G06—COMPUTING OR CALCULATING; COUNTING
    • G06C—DIGITAL COMPUTERS IN WHICH ALL THE COMPUTATION IS EFFECTED MECHANICALLY
    • G06C7/00—Input mechanisms
    • G06C7/02—Keyboards
    • G06C7/08—Keyboards with one set of keys for all denominations, e.g. ten-key board

Definitions

  • Control of the driven shaft and its associated gear wheel is provided by means of a plurality of slides responsive to key depression, four of said slides being separately activatable in the entry of decimal values 1, 2, 4 and 8 and activatable in selected combinations in the entry of values 3, S, 7 and 9.
  • a fifth slide provides for the controlled activation of a gear wheel associated with the driving shaft each time a key is depressed, to thereby effectuate a one unit translation of the selector carriage preparatory to the entry of the next lower order digit of the amount being entered.
  • An important aspect of the invention is the use of a rotating shaft and means associated therewith for entering digit values ranging from one through nine in the ordinally arranged toothed members of a selector carriage, such associated means comprising a driven cam shaft, a pair of friction clutches, and a gear wheel associated with the cam shaft.
  • Selected cams of the cam shaft are separately operable for activating the gear wheel for varying intervals of time sufficient to advance the individual toothed members of the selector carriage a l, 2, 4 and 8 tooth distance, and operable in combination for activating the gear wheel for varying intervals of time sufficient to advance the members a 3, 5, 7 and 9 tooth distance.
  • Another aspect of the invention is the use of means associated with a different selected cam of the cam shaft for translating the selector carriage to the left each time a listing key of the keyboard is depressed, such means comprising a third friction clutch, a gear wheel associated with the rotating shaft, and a gear train and grooved shaft cooperating translatably with the frame of the selector carriage.
  • Still another aspect of the invention is the use of a plurality of keyboard slides and a plurality of transverse levers which are responsive to the depression of the listing keys of the keyboard, for activating the cam shaft, the friction clutches, and the gear wheels associated with the cam shaft and with the rotating shaft for differentially advancing each toothed member of the selector carriage and for translating the carriage to the left preparatory to the entry of a digit value in the next lower order toothed member.
  • a further aspect of the invention is the use of pivotal lever means associated with the various cams of the cam shaft and with the keyboard slides to controllably activate the friction clutches, such lever means comprising a plurality of cam follower levers operably responsive to the cams of the cam shaft and a plurality of pivotally connected sensing arms blockably associated with the keyboard slides, the blocking of the sensing arms by the keyboard slides being effective to activate the friction clutches to effectuate the rotation of the cam shaft and the gear wheels associated with the cam shaft and with the rotating shaft.
  • FIG. I is a schematic sectional elevation of a calculating machine in which the preferred embodiment of the invention is incorporated and in which representative components thereof are shown in relationship with the various operating sections of such calculator;
  • FIG. 2 is a top plan view of the keyboard of the embodiment showing the listing keys in relationship with their associated transverse levers;
  • FIG. 3 is a bottom plan view of the keyboard showing the transverse levers in relationship with the longitudinal slides, such slides being disposed in a cutout formed in the underside of the keyboard;
  • FIG. 4 is a front sectional elevation of the keyboard showing the longitudinal slides and the transverse lever associated with the 1 key, said lever appearing in non-activated relationship with its associated slide;
  • FIG. 5 is a front sectional elevation of the keyboard showing the transverse lever of FIG. 4 in activated relationship with its associated slide;
  • FIG. 6 is a sectional view of the keyboard taken along the line 66 of FIG. 4 showing one of the keyboard slides in its home position relative to the transverse levers;
  • FIG. 7 is a sectional view of the keyboard showing the slide of FIG. 6 in its translatably activated position relative to the transverse levers;
  • FIG. 8 is a sectional view of the keyboard taken along the line 8-8 of FIG. 4 showing one of the slides in its home position and in inactivated relationship with the transverse levers and its associated sensing arm;
  • FIG. 9 is a sectional view of the keyboard showing the slide of FIG. 8 in activated relationship with the transverse levers and in a translatably activated position relative to its associated sensing arm;
  • FIGS. 10A and 10B present a left and right portion, respectively, of a perspective view of the entry apparatus taken from the left front corner, the two portions when mutually orientated by means of a coordinating line appearing in each portion showing the selector carriage of the embodiment and means responsive to the keyboard effective for entering digit values therein, and showing also means for translating the selector carriage preparatory to the entry of the next lower order digit;
  • FIG. ll is a sectional view taken along the line ll-ll of FIG. 10A showing various details of the entry apparatus;
  • FIG. 12 is a perspective view of the cams and cam shaft of the invention in relationship with an associated friction clutch and driving shaft;
  • FIG. 13 is an exploded view of the friction clutch by means of which the toothed members of the selector carriage are advanced;
  • FIG. 14 is an exploded view of the friction clutch by means of which the selector carriage is translatably activated preparatory to the entry of the next lower order digit;
  • FIG. 15 is a sectional view taken along the line [5-15 of FIG. 10B showing the friction clutch controllably associated with the differential advancement of the toothed members of the selector carriage and showing also release means associated with such clutch;
  • FIG. 16 is a sectional view taken along the line l6-l6 of FIG. IDA showing the friction clutch controllably associated with the translation of the selector carriage and showing also release means associated therewith;
  • FIG. 17 is a perspective view of the selector carriage of the embodiment taken from the right front corner and showing various support and control details thereof.
  • the preferred embodiment of the invention comprises a "IO-key keyboard 51 as shown in FIG. 2, and a translatable selector carriage 21 as shown in FIGS. 10B and 17. Means are provided for differentially advancing the toothed members and for translating the selector carriage in opposing directions.
  • the selector carriage is comprised of a plurality of toothed members 23 and a plurality of intermediate gear wheels 25 (FIG. 17).
  • the toothed members 23 are each comprised of an arcuate webbed portion bearing the numbers through 9, and of teeth disposed along the periphery thereof opposite the webbed number-bearing portion.
  • the invention is adapted for use in a printing calculator of the type schematically illustrated in FIG.
  • a single pinion 35 shown in FIGS. 1 and 10B is maintained in cooperating relationship with a gear wheel 37, and is individually cooperably with the intermediate gear wheels 25 as the carriage is translated to the left in step-by-step fashion during the entry of the individual digit values constituting an amount to be processed.
  • the carriage is rotated in a clockwise direction (as viewed in FIG. 1) to thereby engage the intermediate gear wheels 25 with the receiving pinions 27.
  • the rotary transfer wheels 29 are advanced a nine tooth distance in a clockwise direction to thereby zeroize the toothed members 23.
  • Means for rockably engaging the selector carriage 21 with the receiving pinions 27, and for advancing the rotary transfer wheels 29 in a clockwise direction, are not germane to the present invention and are accordingly omitted from this disclosure.
  • the pinion 39 is representative of a plurality of printing wheels effective for printing amounts on a paper-bearing platen 40.
  • the lO-pitch pinions 41 are representative of a pair of accumulators which receive additive amounts directly from the rotary transfer wheels 29, and subtractive amounts from a plurality of intermediate wheels designated 43.
  • the pinions 45 and 49 and the pin wheels 47 are representative of a calculating section capable of performing shortcut multiplication and division.
  • the keyboard of the embodiment comprises a block 51 having a plurality of transverse grooves 53 (FIGS. 8 and 9) formed in its upper portion, and a pair of cutouts 55 and 57 formed in its lower portion.
  • a plurality of transverse levers 59 are rockably disposed in the transverse grooves 53 and are rotatably supported by a shaft 61 attached to a pair of rightwardly extending arms of the keyboard block, said levers being also biased in an upward clockwise direction on the shaft 61 by a plurality of springs 63 connected to the leftmost extremities of the levers and to a shaft 65 supported by a pair of leftwardly extending arms of the keyboard block.
  • Each of the transverse levers 59 is pro vided with an upright extension (as best shown in FIGS. 4 and 5) that is fitted snugly into a slot formed in the underside of a corresponding key 67, each key being so attached to at least one of the transverse levers.
  • the keys I through 9, 00, and 000 are each connected to a separate single transverse lever 59, and the decimal point and 0 keys are each connected to a separate pair of transverse levers.
  • the motor bar also shown in FIG. 2, along with other operation control keys and motor bars, are connected to a plurality of separate transverse levers 59' which are pivotally disposed on a shaft 69 also supported by the leftwardly extending arms of the keyboard block.
  • These levers 59' are biased in a counterclockwise direction on the shaft 69 by springs 63' (FIG. 3) connected to a shaft 65' which is also supported by the rightwardly extending arms of the block.
  • the shaft 69 in
  • Mechanism associated with the motor bar and with other operation control keys of the printing calculator may be disposed within the cutout 57 (FIG. 3) of the keyboard block, for cycling the calculating machine.
  • a plurality of longitudinal slides 71A through 710 are slideably supported within the cutout 55 of the keyboard block by means of a pair of shafts 73 fixed to the side walls of such cutout. the shafts 73 cooperating with a pair of elongated slots formed in each of the slides as shown in FIGS. 6 through 9.
  • These slides 71A through 710 are provided with a series of vertical slots of predetermined size and shape formed in their uppermost portions, the pattern of slot formation and the predetermined angle of the slopes of the slots for each slide determining whether the rockable lowering of a given transverse lever will cammingly contact one of its slopes and thereby translate the slide rearwardly.
  • Each of the slides 71A through 716 is biased forwardly on the shafts 73 (to the right as viewed in FIG. 8) by means not shown in the drawings, and each is translatable rearwardly (to the position shown in FIG. 9) by the camming action of at least one transverse lever against at least one of the slopes formed by the slots of the slide.
  • the transverse levers 59 have been separately identified in FIGS. 2, 6 and 8, in order to facilitate an identification and explanation of the slides that are translatably activated by the various transverse levers and their associated keys of the keyboard. It can be seen from FIG. 2 that the 0 key is connected to the levers 59 and 59, the 00 key is connected to the lever 59 the 000 key is connected to the lever 59", the 1 key is connected to the lever 59", the 2 key to the lever 59', the 3 key to the lever 59", the 4 key to the lever 59", the 5 key to the lever 59", the 6 key to the lever 59 the 7 key to the lever 59", the 8 key to the lever 59", and the 9 key to the lever 59.
  • the decimal key is connected to the transverse levers S9 and 59". Like the 30 motor bar, the decimal point key, although shown in FIG. 2, is neither included nor described in the present disclosure, it not being an essential part of the invention.
  • the pattern of slot for mation of the slide 71A is shown in FIGS. 8 and 9. It can be seen that this slide, which corresponds to a digit value of l, is translatable to the position shown in FIG. 9 by the rockable lowering of the levers 59 S9 59, 59", and 59". The slide 71A is accordingly translatable through the depression of the 3, I, S, 9, and 7 keys of the keyboard respectively.
  • the slide 71B which corresponds to a digit value of 2 is translatable to a position corresponding to that shown in FIG. 9 by the rockable lowering of the levers 59", 59, 59', and 59".
  • the slide 718 is accordingly translatable through the depression of the 3, 2, 6 and 7 keys of the keyboard respectively.
  • Slide 71C which corresponds to a digit value of 4, is translatable rearwardly by the rockable lowering of the levers 59", 59", 59" and 59, or by the depression of the 6, 5, 4 and 7 keys respectively.
  • the slide 71D which corresponds to a digit value of 8, is translatable rearwardly by the depression of the 9 and 8 keys and through the consequent lowering of the levers S9 and 59
  • Slide 71E is provided with a pattern of slot formation such that the rockable lowering of the levers 59 and 59, which is to say the depression of the 000 and 00 keys, will translatably activate the slide to a position corresponding to that shown in FIG. 9.
  • Slide 71F is provided with a pattern of slot formation such that the rockable lowering of each of the levers 59 through 59" with the exception of the levers 59 and 59' will cammingly translate the slide to the position of FIG. 9.
  • Slide 71F is accordingly translatably activated by the depression of the 0 and 000 keys, and by the depression of each of the listing keys I through 9.
  • the longitudinal slides 71A through 71E are each provided with a depending projection 72 as shown in FIGS. 8 and 9, such projection assuming a cleared relationship with its associated sensing arm 74 when the slide is located in its forward home position, and assuming a blocking relationship with said sensing arm (as shown in FIG. 9) when the slide is translated rearwardly by a transverse lever 59.
  • the slide 71G shown in FIGS. 6 and 7 may be identified as a power slide effective for initiating each entry operation. The pattern of slot formation provided this power slide is such that the slide is translated from the position shown in FIG. 6 to the position shown in FIG. 7 each time a transverse lever 59 is rockably lowered by the depression of any one of the listing keys (excluding the decimal point key).
  • Slide 71G is provided with a depending projection 75 and a pivotal arm 77 rotatably connected thereto by means of a stud 81.
  • a hair spring 79 effectively biases the pivotal arm 77 in a clockwise direction on this stud to thereby provide a blocking limit for an upwardly biased sensing member 83 when the slide is located in its forward home position, said pivotal arm 77 and projection 75 permitting entry of the sensing member 83 therebetween when the slide is translated rearwardly to the position shown in FIG, 7.
  • a driving shaft 85 rotatably supported by an exterior frame member of the calculating machine and by a frame member 143 is connected to a motor 87 (illustrated in FIG. 1) by means of a continuous drive belt 89 disposed between a pulley 91 fixed to the shaft 85 and a pulley-carrying shaft of the motor (not shown).
  • the shaft 85 is continuously rotated in a counterclockwise direction (as viewed in FIG. 10A) whenever the motor 87 is maintained in an operating state.
  • Fixed to the driving shaft 85 are a pair of spaced-apart disks 93 (FIG.
  • the friction clutch 97 is operably effective to couple a cam shaft 101 to the rightmost disk 93 of the rotating driving shaft 85, as will be explained in detail in a subsequent section.
  • the cam shaft assembly 101 is rotatably supported by frame member 145 and 147, and, as shown in FIGS. 10A and 12, comprises a cylindrical housing portion 103 within which the friction clutch 97 is disposed, a plurality of cams 105A through 1051 and a fixed disk 107 (FIG. 13) disposed within and forming a part of a third friction clutch 99.
  • the cams 105A through 105D are provided with raised portions which are cooperably effective for advancing the individual toothed members 23 of the selector carriage 21 from one to nine units of rotational travel, and the cams 105E and 105F are provided with raised portions which are individually effective for translating the selector carriage two and one units of lateral movement, respectively, and cooperably effective for translating the selector carriage three units of lateral movement.
  • cams 105A and IOSF are each provided with raised portions which extend one tenth of their circumference (36), the cams 105B and 105E are each provided with raised portions extending one fifth of their respective circumferences (72), cam 105C has a raised portion extending two fifths of its circumference H44), and cam 105D is provided with a raised portion extending four-fifths of its circumference (288).
  • the raised portions of various of these cams are staggered relative to one another in such manner that the trailing end of the cam 105F coincides with the leading end of the cam 105A, the leading end of the cams 10513 and 105D coincide with one another and also with the trailing end of the cam 105A, the leading end of the cam 105C coincides with the trailing end of the cam 1058, and the trailing end of the cam 105D coincides with the leading end of the cam 105F.
  • the raised portions of the cams 105E and 105F are also staggered relative to one another in such manner that the trailing end of the cam 105E coincides with the leading end of the cam 1051 As shown in FIGS.
  • each of the friction clutches 95, 97, and 99 is comprised of a disk member 93 or 107 fixed to a rotatable shaft, and a spring member 109 having a pair of outwardly and oppositely directed projections 11] anchorably fixed to a hub member 113, 115 or 117, and to a housing member 103, 119 or 121.
  • the hub member 113 ofthe clutch 97 is provided with a single stop 123, and the hub members 115 and 117 are provided with a plurality of stops 125 and 127, respectively.
  • the cylindrical housing portion 103 of the cam shaft assembly 101 is provided with a single backup stop 129, and the housing members 119 and 121 are provided with a plurality of backup stops 131 and 133, and are fixed to the gear wheels 37 and 135, respectively.
  • the single stop 123 of the hub member 113 and one of the stops 127 of the hub member 117 are blocked by means hereinafter described, the spring members 109 forming a part of the clutches 97 and are held in expanded disengaged relationship with their respective disks 93, to thereby maintain the cam shaft 101 and the gear wheel 135 in an inactivated state.
  • Each of the cams 105A through 105F of the cam shaft assembly 101 is cooperably associated with a separate cam follower lever 151 pivotally supported by a shaft 153 which is journaled within a pair of frame members 143 and 145.
  • Each of the cam follower levers 151 is provided with a lower arcu ate prong 157 that cooperates with the raised portion of its respective cam 105, and with an upper arcuate prong 159 that cooperates with a recess formed in a companion follower portion of each cam disposed at a point I80 removed from such raised portion, as shown in FIGS. 8 and 9.
  • Each of the cam follower levers 151 is also pivotally connected by means of a pin 161 to a sensing arm 74 corresponding thereto, such connection occurring at the extremity thereof opposite the extremity comprising said arcuate prongs.
  • Each of the sensing arms 74 is biased in a clockwise direction on its connecting pin 161 by means of a spring 163 which is anchored at one end to an aperture formed in the sensing arm and at the other end to a shaft 165 also supported by the frame members 143 and 145.
  • a slot 167 formed in the rearmost extremity of each of the sensing arms 74 is cooperably engaged with a short shaft 169 or 171, the particular functions of which are hereinafter described.
  • Each of the sensing arms 74 is also provided with an upwardly projecting abutment 173 formed on the frontmost extremity thereof, said abutment being cooperably associated with the depending projection 72 of its associated longitudinal slide 71 of the keyboard.
  • This counterclockwise rotation of the cam follower levers 151 is effective to rotate the sensing arms 74 a minimal counterclockwise distance on their respective pins 161, whenever the abutments 173 thereof are unrestricted by the depending projections 72 of their forwardly positioned keyboard slides 71, such minimal counterclockwise rotation being realized under such circumstances without displacing the short shafts 169 and 171 from their normal home positions.
  • a latch arm 181 is connected to the cylindrical housing 179 and is rotatable with the hub member 175 on the shaft 155.
  • the rearmost extremity of the latch arm 181 is disposed in cooperating relationship with the stops 125 of the friction clutch 99, assuming a blocking relationship therewith when the short shaft 169 is situated in its normal home position and a cleared relationship therewith when the short shaft is located in an elevated positionv It can thus be seen that the stops 125 of the clutch 99 are released by the latch arm 181 whenever, during the rotation of the cam shaft 101, one or more of the longitudinal slides 71A through 71D is located in its rearwardly translated position, such released condition being maintained for a differential period of time corresponding to the time at least one of the cams 105A through 105D remains in camming contact with its associated cam follower lever 151.
  • the hub member 175 and short shaft 169 supported thereby are biased in a clockwise direction on the shaft 155 by spring means which is not shown in the drawings.
  • the latch arm 181 is rotatably returned to a blocking position relative to the stops 125 when the short shaft is released from its elevated position by the cams 105A through 105 D.
  • release of the stops 125 is effective to couple the gear wheel 37 with the rotating disk 107 of the cam shaft assembly 101, and blockable contact of the latch arm 18] with one of the rotating stops 125 is effective to disengage the spring member 109 of the clutch 99 from the disk 107 and to thereby inactivate the gear wheel 37.
  • a hub member 183 (FIG. 10A), which is also rotatably disposed on the shaft 155, in the proximity of the shafts leftmost extremity, is provided with a pair of arms 185 connecting a cylindrical housing 187 thereto, said cylindrical housing serving to rigidly support the short shaft 171 which extends rightwardly therefrom into engaged relationship with the slots 167 of the sensing arms 74 associated with the cams 105E and 105F.
  • a latch arm 189 is connected to the cylindrical housing 187 and is rotatable with the hub member 183 on the shaft 155.
  • the rearmost extremity of the latch arm 189 is disposed in cooperating relationship with the stops 127 of the friction clutch 95, assuming a blocking relationship therewith when the short shaft 171 is located in its normal home position and a cleared relationship therewith when the short shaft is located in an elevated position.
  • the stops 127 of the clutch 95 are ac cordingly released by the latch arm 189 whenever, during the rotation of the cam shaft 101, either of the keyboard slides 71E or 71F is located in its rearwardly translated position, such released condition being maintained for a differential period corresponding to the time one of the cams 105E or 105F remains in camming contact with its associated cam follower lever 151.
  • the hub member 183 and short shaft 171 are also biased in a clockwise direction by spring means not shown, and, as a consequence of this bias, the latch arm 189 is returned to a blocking position relative to one of the stops 127 when the short shaft is released from its elevated position by the cams 105E and 105F. Release of the stops 127 is effective to couple the gear wheel 135 with a rotating disk 93 of the driving shaft 85, and blockable contact of the latch arm 189 with one of the rotating stops 127 is effective to disengage the disk 93 and to thereby inactivate the gear wheel 135.
  • the slide 71F is activated rearwardly each time a listing key of the keyboard is depressed.
  • the gear wheel is accordingly activated for a predetermined interval upon the depression of each of the listing keys of the keyboard, such activation resulting from the elevation of the short shaft 171 by the sensing arm 74 associated with the cam 105F.
  • the sensing member 83 to which reference was made in connection with the keyboard slide 710, is rotatably supported by the shaft and is biased in a counterclockwise direction thereon by a spring 191 connected thereto and to a stud fixed to the frame member 143.
  • a slot 193 formed in this sensing member accommodates the rotation of the short shaft 171 relative to the shaft 155, and the rearmost extremity of this sensing member is disposed in cooperating relationship with the single stop 123 of the friction clutch 97,
  • the sensing member 83 is normally held in a clockwise rocked position on the shaft 155, against the bias of the spring 191, by the depending projection 75 and the biased pivotal arm 77 of the forwardly positioned power slide 71G, as shown in FIG. 6.
  • depression of any one of the listing keys of the keyboard results in the rearward activation of the slide 710, such activation being effective to release the sensing member 83 to the bias of the spring 191, the upright extension of the sensing member moving into interposed relationship with the projection 75 and the pivotal arm 77 of the slide 71G, and the sensing member itself experiencing a counterclockwise rotation on the shaft 155 to release the stop 123 of the hub member 113.
  • the cam shaft 101 is coupled to the rotating driving shaft 85 by means of the clutch 97, and the cam shaft 101 is rotated one complete revolution in a counterclockwise direction.
  • the sensing member 83 is rotated in a clockwise direction through the camming action of a raised portion of the housing 103 on an upright arm of the sensing member.
  • the rearmost extremity of the sensing member 83 is accordingly repositioned in blocking relationship with the stop 123, and the upright extension of the sensing member is again blockingly contacted by the depending projection 75 and the pivotal arm 77 of the forwardly restored power slide 710.
  • the backup stop 129 formed in the housing portion 103 provides clearance as between the hous ing 103 and the upright arm 195 when the cam shaft assembly 101 is located in its normal home position, such clearance being essential to the counterclockwise release rotation of the sensing member in relation to the stop 123.
  • the selector carriage 21 shown in FIGS. 10B and 17 is comprised of a plurality of ordinally arranged toothed members 23 disposed between the rightmost of the frame members 31 and the frame member 33.
  • Each of these toothed members as was previously indicated, is provided with an arcuate webbed portion extending for approximately one half of its circumference, and a toothed portion consisting of 10 teeth extending over the remaining half of its circumference.
  • the arcuate webbed portion of each member is provided with readable numeric values ranging from 0 through 9, such values being readable through a rectangular aperture formed in the case of the calculating machine.
  • the toothed members 23 are rotatably supported by a grooved shaft 199 journaled within the frame member 143 (FIG.
  • a shaft 201 to the opposite ends of which a pair of cams 203 (FIG. 17) are keyed, is also journaled within the frame members 143 and 149, such shaft passing through a slot 205 formed in each of the carriage frame members and through elongated arcuate slots formed in the toothed members 23.
  • the frame members 31 and 33 (FIG. 10B) are connected to form a unitary carriage by means of a plate 209 and a shaft 207.
  • a shaft 211 (FIG.
  • This shaft 211 also serves to rotatably support a plurality of ordinally arranged intermediate gear wheels 25 disposed between the innermost frame member 31 and the frame member 33. These intermediate gear wheels are maintained in cooperating relationship with the teeth of the toothed members 23, and are selectively engageable with the receiving pinions 27 of the calculating machine according to the number of units of leftward translation that are experienced by the selector carriage during the entry of digit values.
  • the grooved shaft 199 is provided with a spiral groove extending over its full length.
  • a sleeve 215 (FIG. B) loosely fitted on the shaft 199 and snugly fitted between the frame members 31 of the selector carriage is provided with an internally disposed spiral groove corresponding to the groove of the shaft 199.
  • the groove of the sleeve 215 in cooperation with that portion of the groove of the shaft transitionally located between the frame members 31 serves to house a plurality of ball bearings sufficient in number to occupy the linear distance between said carriage frame members.
  • the sleeve 215 is also provided with a depending forked member 217 which straddles the shaft 201 as the selector carriage is translated in either direction.
  • the spiral groove of the shaft 199 in cooperation with the sleeve 215 and jointly housed ball bearings, is effective to translate the selector carriage in a leftward direction when the shaft 199 is rotated in a counterclockwise direction (as viewed in FIG. 10A), and to translate the carriage in a rightward direction when the shaft is rotated in a clockwise direction.
  • a slideable shaft 219 (FIG. 10A) supported by the frame members 143 and 145 and an auxiliary frame member 237 provides rotational support for three associated gear wheels 221, 223, and 225, said gear wheels being maintained in laterally fixed position by the frame members 143 and 237.
  • the gear wheel 223 is maintained in cooperating relationship with the gear wheel 135 of the friction clutch 95, and is selectively coupleable with either the gear wheel 225 or 221 by means of a minimal translation of the shaft 219 in a rightward or leftward direction, respectively.
  • the shaft 219 is provided with a fixed key which is engageable with companion internal keyways in the gear wheels 221 and 223, when the shaft is located in its leftmost position, and engageable with companion internal keyways in the gear wheels 223 and 225 when the shaft is located in its rightmost position.
  • a sleeve 227 comprising a pair of spaced-apart gear wheels 229 and 231 is fixed to the leftmost extremity of the grooved shaft 199, lehwardly adjacent the frame member 143.
  • the gear wheel 229 is maintained in cooperating relationship with the gear wheel 225 of the slideable shaft 219, and the gear wheel 231 is disposed in cooperating relationship with an intermediate gear 233 rotatably supported by a short shaft 235 fixed to the frame member 143.
  • the intermediate gear 233 is maintained in cooperating relationship with the gear wheel 221 of the slidesble shaft 219.
  • the latter shaft is also provided with a pair of fixed spaced-apart actuators 239 and 241, the rightmost actuator 239 having a pair of slotted arms disposed in straddling relationship with a guide shaft 243, and the leftmost actuator 241 having a slotted arm cooperably engaged with a groove formed in a roller 247 carried thereupon.
  • a profiled cam 245 (FIG.
  • Means not directly related to the present invention are provided for rotating the shaft 201 of the selector carriage in a clockwise direction (as viewed in FIG. 10A) when all of the digits of an amount to be entered have been registered in the toothed members 23, such clockwise rotation of the shaft being efiective to engage the intermediate gear wheels 25 (FIGS. 1 and 17) with the receiving pinions 27 (FIG. 17).
  • a profiled cam 249 fixed to the leftmost extremity of the shaft contacts a curved surface of the grooved roller 247 and thereby translates the shaft 219 to the left to effectively engage the key thereof with the companion keyways of the gear wheels 22] and 223.
  • the gear wheels 221 and 223 coupled in this fashion, the counterclockwise rotation of the gear wheel 135 will effectuate a rightward return translation of the selector carriage by means of the gear train consisting of gear wheels 221, 233, and 231.
  • cams 105A through 105F effectively activate their respective cam follower levers 151 in a counterclockwise direction on the shaft 153, their associated sensing arms 74 (FIG. 108) being elevated to either idle in a counterclockwise direction when unrestricted by slides 71A through 711-" (FIG. 3), or to activatably elevate the short shaft 169 (FIG. 108) or 171 (FIG. 10A) with which they are engaged when blockingly restricted by their associated and rearwardly positioned slides 71.
  • Elevation of the short shaft 169 is effective to couple the gear wheel 37 with the rotating cam shaft 101 by means of clutch 99, such coupling continuing for an interval of time corresponding to the time a sensing arm 74 is held in an elevated state by cams 105A through 105D.
  • Elevation of the short shaft 171 (FIG. 10A) is effective to couple the gear wheel with the rotating driving shaft 85 by means of the clutch 95, such coupling continuing for an interval of time corresponding to the time a sensing arm 74 is held in an elevated state by the cams 1055 and 1051-.
  • the cam 105A elevates the short shaft 169 for an interval of time sufiicient to advance a toothed member 23 of the selector carriage a onetooth distance, by means of the gear wheel 37, the single pinion 35 and the intermediate gear wheel 25 associated with the toothed member.
  • the cam 105B elevates the short shaft 169 for an interval of time sulficient to advance a toothed member 23 a two-tooth distance.
  • the cam 105C or 1050 elevates the shaft 169 for an interval of time sufficient to advance a toothed member a four-tooth or eighttooth distance, respectively.
  • Depression of the 3 key is effective to rearwardly activate the slides 71A and 71B, the cams 105A and 1058 being thereby rendered effective to hold the short shaft 169 in an elevated state for an interval of time sufficient to advance a toothed member 23 a three-tooth distance, the cam 105A producing a one-tooth advancement and the cam 1058 producing a two-tooth advancement.
  • Depression of the 5 key is effective to activate the slides 71A and 71C into blocking relationship with their respective sensing arms 74, the cams 105A and 105C being thereby rendered effective to hold the shaft 169 in an elevated state for an interval sufiicient to ad vance a toothed member 23 a five-tooth distance, the cam 105A producing a one-tooth advancement and the cam 105C producing a four-tooth advancement.
  • Depression of the 7 key is effective to activate the slides 71A, 71B and 71C into blocking relationship with their respective sensing arms 74, the cams 105A, 105B and 105C being thereby rendered effective to hold the shaft 169 in an elevated position for an interval sufficient to advance a toothed member 23 a seven-tooth distance, the cam 105A producing a one-tooth advancement, and the cams 105B and 105C producing a two-tooth and fourtooth advancement, respectively.
  • Depression of the 9 key is effective to activate the slide 71A and 71D into blocking relationship with their respective sensing arms 74, the cams 105A and 105D being rendered effective to hold the shaft 169 in an elevated position for an interval sufficient to advance a toothed member 23 a nine-tooth distance, the cam 105A producing a one-tooth advancement and the cam 105D producing an eight-tooth advancement.
  • each of the listing keys 1 through 9 in addition to activating selected ones of the slides 71A through 71D, is also effective to activate the slide 71F into blocking relationship with its associated sensing arm 74, the rotation of the cam 1051- being thereby rendered effective to elevate the short shaft 171 for an interval of time sufficient to translate the selector carriage 21 a one-unit distance in a leftward direction, such elevation of the shaft and leftward translation of the carriage occurring during the last 36 degrees of rotation of the cam shaft 101 when the raised portion of the cam lF is in contact with the lower arcuate prong of its associated cam follower lever 151.
  • the profiled cam 245 (FIG.
  • Depression of one of the three 0 keys is effective to initiate a one revolution rotation of the cam shaft 101 during which the cams [05A through 105D are ineffective for coupling the gear wheel 37 for the advancement of a toothed member 23, but wherein the cams 105E and/or 105F are rendered effective for producing a one, two or three unit leftward translation of the selector carriage by means of the gear wheels 135, 223, 225, and 229.
  • the cam 105F is rendered effective to elevate the short shaft 171 for an interval of time sufficient to produce a one-unit leftward translation of the carriage, in similar fashion to that resulting from the depression of the keys 1 through 9.
  • the cam 105E When the 00 key is depressed, the cam 105E is rendered effective to hold the shaft l7l in an elevated state for an interval sufficient to produce a two-unit leftward translation of the carriage, such cam, as previously indicated, having a raised portion extending over one fifth (or 72") of its circumference.
  • the cams 1055 and 105F When the 000 key is depressed, the cams 1055 and 105F will combine to hold the short shaft 171 in an elevated state for an interval of time sufficient to produce a three-unit leftward translation, the cam 105E producing a two-unit translation and the cam l05F producing a one-unit translation.
  • depression of the decimal point key (shown in FIG. 2) is ineffective to produce either an advancement of a toothed member 23 or a leftward translation of the carriage, such decimal point key relating more specifically to a separate aspect of the calculating machine into which the preferred embodiment of the present invention is incorporated.
  • this calculating machine provides for a differential leftward translation of the selector carriage, through means not herein disclosed, said differential translation being effective to cooperably align the toothed member 23 containing the least significant whole digit (non-decimal) of the entered amount with a predetermined order of the receiving pinions 27.
  • Such difi'erential translating means provide but still another mode of elevating the short shaft 171 and of coupling the gear wheel 135 with the rotating driving shaft for a differential leftward and full return rightward translation of the selector carriage.
  • the preferred embodiment of the invention is effective for entering decimal amounts in a calculating machine by means of improved mechanism which is also readily adaptable for receiving and converting binary information such as would be transmitted from data processing equipment.
  • improved entry mechanism well known circuitry in association with solenoid means could be employed as substitute means for blockably activating the sensing arms 74 associated with the cams A through l05D, said cams and said sensing arrns having binary significance in that they are separately qualified for entering decimal values of l, 2, 4 and 8 and collectively qualified for entering decimal values of 3, S, 7 and 9.
  • a translatable selector carriage having a frame and a plurality of rotatable toothed members representing decimal orders
  • advancing means comprising a predetermined number of sets of associated elements that are separately operable in the entry of decimal values 1, 2, 4 and 8 in said individual toothed members, and operable in combination in the entry of decimal values 3, S, 7 and 9, and
  • first coupling means responsive to said keyboard for connecting said first gear wheel to said continuous motive means, said connection resulting in the rotational advancement of an individual toothed member of said selector carriage through the unidirectional rotation of said first gear wheel
  • first controlling means responsive to said keyboard and to said first coupling means for regulating the interval of rotation of said first gear wheel, said interval of rotation being effective to advance an individual toothed member a differential rotational distance representing a selected decimal value.
  • second coupling means for differentially connecting said second gear wheel to said first shaft for a bidirectional translation of said selector carriage, said difi'erential connection being effective for rotating said first shaft in a first and a second direction as motivated by said second gear wheel, and
  • second controlling means responsive to said keyboard coupling means comprises:
  • a driven third shaft having a plurality of cams and a disk fixed thereto, said cams forming a part of said first and said second controlling means
  • first clutch means effective for resiliently connecting said third shaft to said second shaft for one complete revolution therewith, said first clutch being disposed in cooperating relationship with a first of said pair of disks of said driving second shaft,
  • second clutch means responsive to said revolution of said third shaft and to said first and second controlling means for resiliently connecting said first gear wheel to said third shaft, said second clutch being disposed in cooperating relationship with said disk of said driven third shaft.
  • said second coupling means for differentially connecting said second gear wheel to said first shaft comprises:
  • third clutch means responsive to said revolution of said driven third shaft and to said second controlling means for resiliently connecting said second gear wheel to said driving second shaft, said third clutch means being disposed in cooperating relationship with the second of said pair of disks fixed to said driving second shaft,
  • a slideable fourth shaft providing rotatable support for a a sixth gear wheel fixed to said first shaft and disposed in cooperating relationship with said fifth gear wheel
  • a seventh gear wheel fixed to said first shaft and disposed in coplanar and nonengaging relationship with said third gear wheel
  • an eighth gear wheel rotatably supported by an abbreviated fifth shaft and disposed in cooperating relationship with said third and said seventh gear wheels, said unidirectional rotation of said second gear wheel being effective, when said slideable fourth shaft is located in its rightmost position, to rotate said first shaft in said first direction by means of said fourth, fifth and sixth gear wheels, and effective, when said fourth shaft is located in its leftmost position, to rotate said first shaft in said second direction by means of said fourth, third, eighth and seventh gear wheels.
  • first, said second and said third clutch means are each comprised a. a first, second, or third hub member, respectively, having at least one stop formed on the periphery thereof, said hub member being rotatably supported by said second or said third shaft,
  • said housing member being provided with at least one backup stop and either connected to or provided with actuating means consisting of said third shaft, said first gear wheel, or said second gear wheel, respectively, and
  • a spring member disposed in coplanar and encompassing relationship with one of said disks of said second or said third shafts, said spring member having a plurality of coils terminating in a pair of offset extensions protruding outwardly in opposite directions therefrom, one of said extensions being snugly fitted in a slot formed in said hub member and the other of said extensions being snugly fitted in a slot formed in said cylindrical housing member, the arrangement being such that said spring member is held in expanded and disengaged relationship with the peripheral surface of its associated rotating disk when a stop of its associated hub member is blockably limited, said spring member being released into a contracted and gripping relationship with said peripheral surface when said stop is released from said blockably limited condition.
  • a sensing member rotatably supported by a sixth shaft and biased in a counterclockwise direction thereon by spring means, said member being provided with an upright extension formed on its frontmost extremity, said upright extension being disposed in blockable relationship with said keyboard, the rearmost extremity of said sensing member being disposed in blocking relationship with said stop of said first hub member of said first clutch means when said upright extension is blockably limited by said keyboard, and being also rockably displaced from said stop when said sensing member is released by said keyboard to the control of said spring means, said rockable displacement of said sensing member from said stop being effective to release said spring member of said first clutch means into gripping relationship with said first disk of said driving second shaft and to thereby couple said driven third shaft connected to said first cylindrical housing member of said first clutch means with said driving second shaft, and

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US1627A 1969-05-30 1970-01-09 Binary entry apparatus for a calculating machine Expired - Lifetime US3652826A (en)

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FR6917808A FR2061838A5 (enrdf_load_stackoverflow) 1969-05-30 1969-05-30

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3858035A (en) * 1971-10-08 1974-12-31 Hugin Kassaregister Ab Position selecting device
US3993892A (en) * 1974-12-10 1976-11-23 Werner Haug Device for transmitting information in the form of electrical signals to at least one mechanism for displaying or printing this information

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2837274A (en) * 1955-05-09 1958-06-03 Olivetti Corp Of America Printing mechanism
US3009633A (en) * 1961-11-21 Slide d
US3050246A (en) * 1962-08-21 corner etal
US3255960A (en) * 1963-07-24 1966-06-14 Victor Comptometer Corp Device for converting binary or decimal code into printed decimal data

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3009633A (en) * 1961-11-21 Slide d
US3050246A (en) * 1962-08-21 corner etal
US2837274A (en) * 1955-05-09 1958-06-03 Olivetti Corp Of America Printing mechanism
US3255960A (en) * 1963-07-24 1966-06-14 Victor Comptometer Corp Device for converting binary or decimal code into printed decimal data

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3858035A (en) * 1971-10-08 1974-12-31 Hugin Kassaregister Ab Position selecting device
US3993892A (en) * 1974-12-10 1976-11-23 Werner Haug Device for transmitting information in the form of electrical signals to at least one mechanism for displaying or printing this information

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FR2061838A5 (enrdf_load_stackoverflow) 1971-06-25
GB1273102A (en) 1972-05-03

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