US1867603A - Calculating machine - Google Patents

Calculating machine Download PDF

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Publication number
US1867603A
US1867603A US488362A US48836230A US1867603A US 1867603 A US1867603 A US 1867603A US 488362 A US488362 A US 488362A US 48836230 A US48836230 A US 48836230A US 1867603 A US1867603 A US 1867603A
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Prior art keywords
carry
gear
drum
cam
machine
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US488362A
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Talamini Louis
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MARCHANT CALCULATING MACHINE
MARCHANT CALCULATING MACHINE Co
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MARCHANT CALCULATING MACHINE
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    • GPHYSICS
    • G06COMPUTING; CALCULATING; COUNTING
    • G06CDIGITAL COMPUTERS IN WHICH ALL THE COMPUTATION IS EFFECTED MECHANICALLY
    • G06C15/00Computing mechanisms; Actuating devices therefor
    • G06C15/26Devices for transfer between orders, e.g. tens transfer device
    • G06C15/38Devices for transfer between orders, e.g. tens transfer device for pin-wheel computing mechanisms

Description

July 19, 1932. l.. TALAMlNl 1,867,603
A CALCULATING' MACHINE l Filed Oct. 13. 1930 l| HIIII NIW FILLE E Bip/MI /W ATTORNEY Patented July 19. y waaA UNITED. STATES PATENT OFFICE.I
Y LOUIS TALAMINI, OF OAKLAND, CALIFORNIA, ASSIGNOR T MARCHAJ'T CALCULATING MACHINE COMPANY, A CORPORATION OF CAI.IFO1`\|1\TIII.A.r
CAI;C'U'LA'JJING' MACHINE Application med october 1s, 1930. serm No. 488,362.
The present invention relates to calculating. machines and particularly to machines having rotary tens-carrying actuators, an example of which is disclosed in the patent to 5 Odhner, No. 514,725, datedv February 13th,
Machines of the Odhner type are provided with a laterally shiftable numeral wheel carriage, the numeral wheels 4being adapted to be differentially advanced by a reversible rotary actuator commonly called the drum, and which consists of a luralityof actuating sections, each rovide with differential actuating means or advancing the numeral wheel 7.5 from one to nine steps, and a pair of tens-carrying teeth disposed adjacent each end of the differential actuating means.-` Only one of these tens-carrying teeth, however, may beactive in a given cycle of the machine operation; one being operable for an additive tens-- carry and the other for a subtractive tenscarry, depending upon the direction of rotation of the drum. These tens-carrying teeth are normally inactive and are rendered active by the transit of the next lower numeral wheel between ninev and zero '1n either direction which interposes a cam in the path of the' carry tooth, moving it at the proper time to active position. l .f In view of the fact that the action of the carry tooth in a given order may move the numeralwheel between nine and zero, causing interposition of a cam in the path of the carry tooth of the next higher order, the carry teeth of Iall orders cannot be voperated simul-` taneously, but* must be staggered so that the carry tooth of each superior order comes to active position enough later in the cycle to permit the inter osition of the cam by the action ofthe tootli of the next lower order to be completed. The result of this requirement is that the carry teeth of the drum as a whole form a spiral around the periphery of the drum, as shown in Figure 4 of the Odhner patent aboye referred to, andthe additive and subtractive spirals of carry teeth apfproach a point of convergence toward the le end of the drum. This approach to the point of convergence 5 of the tens-carrying spiral limits the capacity `spect thereto.
of the machine. Suliicient space must be left between .the left end teeth of the two spirals to permit passage of the transfer levers laterally in shifting the carriage, and, therefore the spirals can not completely converge. The capacity of the machine, that is, the number of actuating sections contained in'the drum, is, therefore, determined by the) number of carry teeth which can be placedin proper displacement betweenthe end of the actuating section of the periphery of Athe drum and the carry levers of the carriage.
Two ways appear by which it is possible to l increase the number of carry teeth which can be placed in this space. The first is to. increase the diameter .of the drum section.
This, however, is impractical because the increased peripheral speed of the drum, caused by an increase in diameter, imparts a Agreater momentum to the' numeral Wheels and causes overthrow thereof at lower speed of rotation than for a drum of smaller diameter. The only other way involves decreasing the peripheral displacement of the carrying pins of successive orders, and it is toward this meansv that the present invention is'directed.
An object of the invention is the provision of a high capacity tens carrying mechanism for a calculating machine.
Another object of the invention is the provision of an actuating drum for a machine of tlf class described, in which accurate centraliz .tion of the drum is not necessary in order to permit lateral shift of the carriage with re- Other objects will appear as the specication progresses.
The invention is disclosed as applied to a machine having a selector of the type disclosed in the patent] to Friden, Number 1,524,924, dated February 3d 1925, to which, together with the Odhner patent above referred to, reference is made for a `full disclosure of details herein omitted, it ylosing noted that the invention is particularly advantageous when appliedto `machines of this type adapted for automatic operations involving alternate operations ofthe actuator. and automatic shifting of the carriage, such as disvclosed in the application 0f Friden, Serial 100 Number 252,175 filed Februalg 6th 1928, and the application of Friden, erial Number 303,387 iled September 1st 1928.
, carry lever and numeral wheel cam.
Figures 3 and 4 are details of the improved .tens carrying pins. l
Figure 5 isa diagrammatic development of the improved actuator. l,
Figures 6 and 7 are details comparing the old and new structures, respectively.
Numeral wheels 1 (Figure 1) are loosely mounted on a shaft 2 carried in the laterally shftable'carriage 3, and each is provided with a gear 4, adapted to mesh with an intermediate gear 5 loosely mounted on shaft 6, also carried in the carriage 3. Gears 5 areadapted vto mesh with diferential actuator 4segments 7 and to be advanced thereby from one to nine steps, depending upon the setting of the selection controlling device. During each rotation of the shaft 8 carryingthe segments numeral wheels 1 are thus selectively advanced from one to nine steps during each cycle of the opposite side of the numeral wheel from vthe gear 4 is a cam 9 so placed that when the reading at the sight opening of each numeral wheel passes from nine to zero,'or vice versa, the said cam will rock a lever 10 to the rear where it will be latched by well-known means,
placing a cam surface 11 thereon in the path of tooth 12 carried by the actuating section associated with the numeral wheel of the next higher order.
As shown in Figures 6 and 7, the tooth 12 normally traverses a pathto one side of the teeth of intermediate gear 5, .but when the lever 10 is rocked to the rear its cam face 11 is placed in the path of tooth 12. As the tooth progresses it is r'st cammed into position to drive gear' 5, and, after such positioning, is
'moved to drive ear 5 through one step.
Since a secon carry lever 10 may be moved to the reai` bythe action of a carry tooth 12 upon any numeral wheel standing at nine or zero, the pin 12 of the next higher vorder must be suiiciently displaced around the periphery of the drum from the active pin to permit the lever 10 to be moved sufliciently to the rear before the higher pin is in position to impinge it. The amount ofthe peripheral displacement between. successively acting pins, therefore,.cannot be less than the distance that the periphery of the drum moves while a pin 12 is 'cammed from its normal vposition into position to drive gear 5, plusthe distance thatl the periphery of the drum operation of the machine. Fixed to.
moves while the lever 10 `is cammed, by numeral Wheel cam 9, sufficiently to the rear to first phasel (camming the pin into position to drivey the' gear) is dependent on the amount of displacement of the pin necessary, Width of the pin, andthe camming angle chosen. The amount of drummovement-necessary to complete the second phase (driving lthe` gear) is dependent on the pitch of the gear.
avoid striking the end of the next approach- Changing any of these factors may result. l
in less drum movement being required to complete the operation and hence permit the pins to be spaced closer together, but each is rather closely limited by requirements of strength, ease of operation, etc.
The present invention contemplates `reducing the peripheral spacing of pins 12 without -fao disturbing the balance y of the above-me-- tioned factors by overlapping the abovementioned phases of operation of the said pins. In the present embodiment of the invention this is effected by beveling the portion of pin 12 which impinges cam face 11 to conform substantially to the cam face 11 as v shown at 15 in Figure 3, and in Figure 7. Thus, as shown in Figure 7, the gear operating phase begins `somewhat before the completion of the positioning phase and the amount of drum movement required for the completion of both phases is substantially reduced permitting closer peripheral spacing of the pins.
A round pin 12, while apparently possessing the advantages of the invention here disclosed, presents objections which render it useless for the present purpose. In addition to the undesirable point contact with gear 5 and sliding line contact with cam face 11 which it gives as compared with the line contact withgear 5 and sliding vsurface con' tact with cam face 11 ofthe` present structure, it is apparent that fora given overlap of the phases, the, round pin will have a 4.
in the present structure, by varying `the amount of cham'fer of the beveled surface of the pm, the tendency to overthrow past the gear 5 canbe readily avoided. vIn the practical manufacture of calculating machines, these considerations are 'of great importance,=
and the present invention has been found by actual .experiment to permit the safe peripheral displacement of the pins 12 to be decreased about twenty-two per cent without any increased care in the manufacture and assembly of parts.
It will be noted in Figure 1 that the pins l2 of the second and third sections from the right, are placed relatively close to the end of actuator segment 7. When one of the said actuator segments has advanced its associated gear 5 through nine steps, and the said segment passes beyond the gear, there is a slight overthrow of the intermediate gear 5 which is taken up in a well-known manner by the centralizing pawls; however, since a very slight displacement of gear 5 is likely to cause a pin l2 coming into engagement with it, to jam on the end of a gear tooth, it has been found .desirable to chamfer the end of the pin as shown at 16 in Figure 4, the said chamfer conforming with the outline of the associated gear tooth and permitting accurate engagement of the pin between ear teeth, even when the gear is slightly out o normal position.
As heretofore noted, it is necessary to leave suflicient space between the leftmost pins 12 and 13 of both the addition and subtraction spirals, to permitxlateral passage of transfer levers 10 in the operation of shifting the carriage. lWhile it is clear from the foregoing that about twenty per cent more actuating segments may be included in the same machine while maintaining the same spacing between these leftmost pins, the advantages of the invention are even more marked in machines of present standard capacity. In such machines, the close spacing of the leftmost pins has made very accurate centralization of the actuator before a carriage shifting operation necessary. Since accurate centralization of such a balanced and freely rotating actuator,'especially in motor driven machines, requires the absorption of considerable momentum, very complex, accurately adjusted -mechanism has been required to attain the desired results, and the attainable speed of the machine has been considerably limited by the necessity for so accurately centralizing the actuator. Since it is obvious, however, thatl when the invention is utilized in machines of less than the maximum capacity available therewith, a considerably wider space will be left between the leftmost pins of the two spirals, extremely accurate centralization of the actuator will not be necessary in order to permit shifting of the carriage. Therefore, extremely accurate centralizing mechanisms may be dispensed with and the speed of operation substantially increased.
While the invention has been disclosed as embodied in a particular type of machine, it
will be obvious to those skilled in the art thatV it is ca able of beneficial use in many other types, or instance, those which carry the l.members 12 on a shaft separate from that carrying the differential actuators 7, or which have only a single spiral. Other applications within the scope of the appended claims will occur to those skilled in the art to which the invention appertains.
I claim:
1. In a calculating machine, accumulator wheels, a pluralit of successively acting carry actuating mem rs therefor, carry controlling elements associated with said members, and means for concurrently conditioning said members and operating said wheels thereby comprising complementary cam faces on said members and said elements.
2. In a calculating machine, the combination of a plurality of carry controlling elements having cam faces thereon, and successively acting carry actuating members havi-ng portions adapted to impinge said cam faces, the impinging portions of said members being beveled to conform substantially to said cam faces.
3. In a calculating machine, the combination of a plurality of successively acting carry actuating members, and carry controlling elements adapted to be impinged by said members, said members being chamfered to conklorm to the impinged portion of said memers.
4. In a calculating machine, registering elements, a plurality of successively acting carry actuating members adapted to actuate said registering elements, a plurality of carry controlling elements adapted to be displaced by a registering element to condition the carry actuating members of next higher order to actuate its associated registering element, and means comprising a registering element and controlled during the conditioning movement of a carry actuating member for effecting displacement of the carry controlling element of next higher order.
5. In a calculating machine, register driving gears, a pluralit of successively acting carry actuating mem ers therefor, and carry controlling elements adapted to be impinged by said members, said members being chamfered to conform to the impinged portions of said gears and said members.
In witness whereof, I have hereunto set my hand. A
LOUIS TALAMINI.
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2641410A (en) * 1948-12-09 1953-06-09 Ochsner Cyrill Calculating machine with rack drive
US3243111A (en) * 1964-05-29 1966-03-29 English Numbering Machines Two input counter unit

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2641410A (en) * 1948-12-09 1953-06-09 Ochsner Cyrill Calculating machine with rack drive
US3243111A (en) * 1964-05-29 1966-03-29 English Numbering Machines Two input counter unit

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