US2214015A - Tabulator - Google Patents

Description

Sept. 10, 19 E. H. DREHER TABULATOR Filed June 24. 1937' 8 Sheets-Sheet 1 INVENTOR ELMER H. DREHER A TORNEY P 10, 1940- E. H. DREHER 2,214,015

'TABULATOR I Filed June 24, 1937 8 Sheets-Sheet 2 (v: I 9 LL.

lNVENTOR ELMER H. DREHER -AT ORNEY p 1940' E. H. DREHER 2,214,015

' ELMER H. DREHER AT RNEY Sept. 10, 1940. a. H. DREHER TABULATOR Filed June 24; 1,8,3

8 Sheets-Sheet 4 v a w w W INVENTOR ELMER H. DREHER mww mam 5m TTORNEY Sepia 1Q, 1946. g D R 2 21 5 3315 TABULATOR Filed June 24, 1937 3 Sheets-Sham 6 INVENTOR ELMER H. DREH ER Sept 10, 19 E. H. DREHER TABULA'I'OR Filed June 24, 193? 8 Sheets-Sheet "i NVENTOR ELMER H. DREHER I y A BY A ORNEY w, mm.

FIG. IO.

E. H. DREHER F'IG.9.

w) on INVENTOR ELMER H. DREHER ATTGRNEI Patented Sept. 10, 1940 PATENT OFFICE TABULATOR Elmer H. Dreher, Rockville Centre, N. Y., assignor to Remington Band 1110., Buffalo, N. Y., a corporation of Delaware Application June 24, 1937, Serial No. 150,073

14 Claims.

This invention relates generally to mechanism, in accounting and like machines, for printing true negative balances, and more particularly to mechanismoi this type employing a single ac- 5 cumulator and novel transposition means for eiiecting correct printing of a negative balance from a complementary amount stored in the accumulator.

The mechanism of the present invention is directed primarily towards an improvement or" the machine disclosed in the U. S. application of Dreher S. N. 125,375, filed February 12, 1937. A portion or" the above application discloses an accumulator capable of performing problems of adlr'i dition and subtraction, and has special reference to transfer mechanism therein for effecting tens carry operations of either a positive or negative character. Mechanism is also provided for extracting totals from the accumulator and causgo ing them to be printed on a tally roll or record sheet. A positive total is printed in its correct whereas a negative total is printed corry orm and must be translated by the the true negative total.

of the previous application, unable to print a true negative total the means for overcoming this dislity the c sent application is concerned. no conjunction with 'he accumulating unit noted above, the machine of the present invention pro= vides printing mechanism adapted to be con trolled by the accumulator on total cycles. Ineluded the printing mechanism are printing or type carryin sectors each of which bears the usual series of type elements zero to nine on its upper portion, and in addition to these bears, beneath the first set, a second series of elements of opposite numerical progression, that is, from nine sero. The two sets of elements are in vertical 4o alignment and an extra zero element is interposed between them. Normally effective latching means causes the upper set of type elements to be effective on all listing operations and positive totals. The lower set of elements is used only on a 45 negative total taking operation. Machanism is provided for disabling the above mentioned latching means, the disabling mechanism being automatically conditioned for operation when the accumulator contains a negative amount. If 2. 51 total cycle is initiated while the accumulator is in a negative condition, the disabling mechanism will be rendered eifective and a total will be printed through the second set of type elements. Additional mechanism, also effective only on neg- 55 ative total taking operations, is provided for causing all of the printing sectors to the left of the lowest significant denominational order to move one additional space in order that a true negative total may be printed. It should be understood, however, that this extra or fugitive one 5 is not entered into the accumulator and is associated solely with the printing mechanism.

The invention is shown in the present disclosure as embodied in a Powers tabulator. As is well known in the art, the Powers machine op- 1o crates on perforated record cards and is adapted for use in a great variety of accounting problems. The accumulating and printing mechanisms are card controlled on both listing and total taking operations and are divided into a plurality of in i5 dividually operable units. In the particular embodiment shown herein an accumulator of the type disclosed in the application S. N. 125,375 is provided for each unit in the tabulator and negative total printing mechanism is associated with 539 each accumulator. The normal function of the 8.001 tor is to ace ulate all items positive so tha; it: is necessai hole all fields of negat item.

relate to mocha. entered into later in spec s to insure the linother object of my printing of a true neg tal roni a compl rnentary negative amount stored in a single ac= cum'olator.

Another object Of my invention with a single acc "or, capable m traction, novel pi i. g mechanism inclndif printing sectors having two sets of type elements, one set of which is efifective on all listing and positive total taking operations, and the other set of which is effective only on negative total taking 45 operations.

Other objects and structural details of my invention will be apparent from the following descriptionwhen read in connection with the accompanying drawings, wherein: 50

Figs. 1, 2, and 3, when read together, comprise a composite view in right-hand cross section of the entire machine. The three sheets are drawn to a scale of approximately one half size and should be arranged vertically with Fig. 1 at the 55 bottom, Fig. 2 directly above it and Fig. 3 at the top.

Figs. 4 and comprise a composite view of the head section of the tabulator as viewed in righthand cross section, and disclose the detailed construction of the true negative total printing mechanism. The composite view Figs. 4 and 5 is an enlarged view of Fig. 3.

Fig. 6 is a view in elevation of the right-hand side of the tabulator head. A portion of the outside casing is broken away to disclose some of the drive mechanism and the means for initiating a subtraction operation in the machine.

Fig. '7 is a view in side elevation of the lefthand side of the tabulator head with the outside casing removed. Shown in the view is a portion of the accumulator, some of the total taking mechanism and the operating means for releasing the printing hammers. I

Fig. 8 is a detail view of the carry sector of highest denominational order in subtract position with its associated blocking latch raised out of efiective position.

' total control mechanism.

The mechanism with which this invention is chiefly concerned, namely, the printing and computing mechanism, is located in the head section of the tubulator and, therefore, a major portion of the following description will be directed towards a disclosure of that portion of the machine. The main operating features of the tabulator itself are old, well known in the art, and

have been disclosed in numerous patents and previous applications.

In the present instance reference is made to the patent to William W. Lasker, No. 2,044,119, issued June 16, 1936 for all controlling mechanisms not herein specifically indicated.

MACHINE OPERATION Situated at the front of the machine in its base section is a card hopper I (see Figs. 1 and 2) adapted to receive a stack of sequentially arranged perforated record cards. The cards are ejected from the hopper I seriatim by a picker knife and block 2 connected to a rock shaft 3 through a link 4 and an arm 5 fast to the shaft 3. The shaft 3 is given a reciprocable rocking motion once for each machine cycle by a cam (not shown) on the main cam shaft 6, so that, unless otherwise interrupted, the picker knife 2 will feed the bottom card of the stack out of the hopper l and into position for sensing each revolution of the shaft 6. The main cam shaft 6 is a constantly driven rotating shaft geared to an electric motor in a manner not herein shown. For the operation of shaft 6 and all other base mechanisms reference should be made to the previously mentioned Patent 2,044,119. The main operating mechanism of the base in the present machine is identical with that shown in the above patent. After the ejection of the card from the hopper I it is picked up by a pair of constantly driven feed rolls I and 8 and thereby fed into a sensing chamber comprised of a pair of perforated plates 9 and H. A card stop l2, driven from a cam (not shown) on the main cam shaft 6, operates at this time to block the exit of the sensing chamber and retain the card in sensing position. Immediately beneath the sensing chamber is a pin box I3 in which is supported a plurality of sensing pins It. The pins it are arranged in forty-five columns of twelve pins to a column so that the entire card maybe sensed with one operation. The pin box 13 is given a vertical reciprocable motion once for every cycle of the cam shaft 6 by an eccentric disc l5 secured to the shaft 6. The pins M are urged upwards by springs 16 and are, adapted, as the pin box l3 rises on a sensing operation, to pass through the perforations in the plate II of the sensing chamber, and also through whatever perforations may be present in the card held in the chamber. Those pins 14 which find no perforation in the card merely press against its lower surface and are ineffective. Cooperating with each column of pins I4 is a locking slide H, the purpose of which is to impart a positive upward movement to those pins M which have passed through a perforation in the card. The locking slide l1 reciprocates horizontally through the pin box [3 and cooperates with the extrusions i8 on the pins M in a manner more completely disclosed in the Lasker Patent 2,044,119. After the card has been sensed, the card stop 12 is withdrawn and a pair of spring-pressed rollers (not shown herein) causes the ejection of the card from the sensing chamber into a receiving pocket 59 by way of feed rollers 2| and 22.. At the time one card is leaving the sensing chamber another card is being fed in to take its place so that card analyzing may proceed without interruption.-

Positioned directly above the sensing chamber is another pin box 23 (Fig. 2) in which is supported a plurality of intermediate pins 24 equal in number and arrangement to the pins 14 of the lower pin box l3. The lower ends of the pins 24 lie just above the sensing chamber and are in alignment with the upper ends of the sensing pins 14. Any pin M, therefore, which passes through a perforation in the card, will also pass through the perforated plate 9 to contact and elevate its corresponding intermediate pin 24. Associated with each column of pins 26 is a pair of locking slides 25 and 26 adapted to cooperate with extrusions 21 on the pins 24. The locking slides 25 and 26 shown herein are of the type adapted for use with 90-column cards and their construction and operation is briefly as follows: As viewed in Fig. 2 the outer slide 25 is formed with six cam slots 28 on its left-hand side and six open slots 29 on its right-hand side. The inner slide 26 is immediately adjacent the slide 25 and is formed with similar slots 28 and 29, arranged in reverse position to the slots in the outer slide 25. Each column of pins 24 has six hensive disclosure of the locking slides 25 and 26 reference is made to the U. S. Patent to Lasker No. 2,151,406 issued March 21, 1939. The retract mechanism comprises in part, a bail 32, a pair of arms 33 (one shown) supporting the bail 32 and a rock shaft 34 to which the arms 33 are secured. The shaft 34 is rocked once for each machine cycle by a cam on the main cam shaft 6 in a manner not herein shown. As viewed in Fig. 2 if the shaft 34 is rocked in a clockwise direction, the ball 32 will force the slides 25 and 26 leftward against the tension of their retaining springs and cause the release of the elevated pins 24. Also associated with each column of pins 24 is a pair of so-called change-of-designation slides indicated in Fig. 2 by the single reference numeral 35. The slides 35 are similar in construction to the slides 25 and 26 with the exception that the cam slots cut therein are not of the looking type, that is, their function is not to lock the pins 24 but to coact with extrusions 36 on the pins 24 to cause the displacement of the slides in a leftward direction (as viewed in Fig. 2). The function of these slides 35 is disclosed in the previously mentioned Patent No. 2,151,406 and will be entered into in somewhat greater detail further on in the present description.

Positioned in the mid section of the tabulator is the usual translator 31 in which is supported a plurality of rigid wires for the purpose of transmitting the sensing represented by the elevated pins 2 2 to the head section of the machine where it is accumulated and printed. The lower ends of the wires 88 lie directly above their respective pins so that the elevation of any pin 24 will cause a corresponding elevation of the associated wire The six wires illustrated in Fig. 2 represent one column of a card. The first five wires from the left represent the numerals 1 to 9 while the extreme ri ht-hand wire, designated by the numeral is a control wire the purpose of which is later to be explained. For the sake of clearness only one column of translator wires is shown in Fig. 2, but it should be understood that the translator is capable of supporting individual columns of wires and that, therefore, the six left-hand pins are adapted to operate a separate column of wires 3839 (not shown) positioned to the left of the set illustrated and in the same row. Referring now to Figs. 2, 3, and 5 it may be seen that the upper ends of the wires 38 lie just beneath the bars ii of a stop basket 2. The stop basket may be of. the same construction as that disclosed in the patent to Lasker No. 1,780,621, issued November 4, 1930, but the one illustrated herein differs slightly from the basket of the patent although both use the same principle of operation. A stop basket 22 is provided for each computing unit of the tabulator and a stop tray 40, secured between the side frames provides a common support for all of the baskets. In the present instance each basket supports ten denominational columns of stop bars 4i. There are five stops 4! to each column plus a normally effective zero stop 43. The essential points of difference between the present basket and that of the Patent.No. 1,780,621 lies in the control of the zero stop and the nine stop of each denomination. The nine stop is the extreme lefthand bar 41 (as viewed in Fig. 3) and corresponds generally, in function, to the bar shown in Fig. 2 of the cited patent and indicated therein by the reference numeral I08. As described in the above patent the five digit stops 4] represent, in order from left to right, the odd numerals 9, 7, 5, 3, and 1. To obtain an even number the odd numbered stop of next lower value is raised in combination with the nine stop of the same denomination. As a result of this operation the digit stops in this denomination are permitted to move a step forwardly to set the differentially settable racks, which they control, to the representation of an even number. As shown in Fig. 3 the nine stop of each denomination is formed with a pin 4IA which is normally seated in a notch cut in an arm 4IB rigidly supported between the side walls of the basket 42. While the nine stop is thus held all of the stops in that denomination are prevented from shifting forwardly. Elevation of the nine stop will move the pin NA out of the notch in arm MB and the stops are free to shift a measured distance in a forward direction. A spring-pressed arm 41C bears upon a second pin formed on each nine stop 4i and serves to restore the stops to normal position. The operation of the zero stops will be considered in a later paragraph. Associated with each column of stops l! is a type carrying sector 44 pivoted loosely to the shaft :35. Also mounted loosely on the shaft 45, and associated with each type sector, is an actuating sector db formed with a slot 6? in its lower horizontal surface. -A stud $8 on the sector 0.4 is passed through the slot 4? and is normally engaged by a latch 59 pivoted at 51 to the actuating sector 56. During normal machine operation, therefore, the sectors and retain the relation shown in Fig. 3 and operate as a unit. Latch t9 and stud 38 may, however, be disengaged during certain conditions of machine operation later to be described. Each sector id is urged to move in a clockwise direction (Fig. 3) about its shaft by means of a spring 52 tensioned between a rear extension of the sector and a spring anchor The sectors M are, however, normally retained in retracted position against the tension of their springs 52 by a bail rod 55 individual to each unit in the machine. As shown in the drawings, in the extreme retracted position of the sectors the studs 48 thereon are positioned slightly to the rear of the engaging shoulders of the latches 69 in order that the latches may be easily rocked into disengaged position. The bail is supported between a pair of arms 56 (one shown) secured to the shaft #5. The arms 5% and the shaft 4'5 are rocked in a clockwise direction, and returned, once for each machine cycle, to permit the sectors 4 to move forward to their respective printing position. The amount of movement permitted each type sector 44 on listing operations is individually determined by its associated column of stop bars M, as previously noted. As shown in Fig. 3 a spring 57 is tensioned between the rear extension 53 of each type sector 44 and one end of a pawl 58 pivoted at 59 to the actuating sector 46. The other end of the pawl 58 engages a notch formed in the previously mentioned latching member 49 so that the tension exerted by the spring 57 provides a resilient force for keeping the latch 49 and the stud 48 engaged, and in addition to that causes the sector 45 to assume a normal position slightly to the rear of the type sector 44. The actuating sector 46 is formed with a downward extension 6| to which is secured a heel 62 which, in the normal position of the sector, lies slightly behind the upraised zero stop 43 and abuts against a tie rod 62A. It is evident, therefore, that while a zero stop 43 is up the pair of sectors 44 and 46 associated with that particular column of stop bars cannot move from normal position. In each separate unit of the machine mechanism is provided for lowering the zero stops 43 either individually, during listing operations, or as a group during total taking operations. As shown in Fig. 3 the zero stop 43 is connected, at its lower end, to one arm of 'a bell-crack 63 loosely mounted on a shaft 84. A spring 65 tensioned between another arm of. the bell-crank 63 and the base plate of the stop basket 42 tends to rotate the bell-crank in a clockwise direction about the shaft 64 and retain the zero stop 43 in its raised position. A third arm of the bell-crank 63 bears against one end of a slide 66 which extends horizontally through the stop basket 42. Each slide 66 is formed with a plurality of cam shoulders 67 (one for each bar 4|) which cooperate with pins 68 on the lower portion of each bar 4 l The elevation of any bar 4i, therefore, will cam the slide 66 to the right (as viewed in Fig. 3) to rotate the bell-crank 63 counter-clockwise (Fig. 3) and cause the withdrawal of the zero stop 43 from its upraised position thus freeing the heel 62 of the sector 46. A rock shaft 89 is rotatably mounted in the side frames of the machine and occupies a position immediately behind the bellcranks 63. The shaft 69 is known as the rear total shaft and is adapted to be rocked, in a manner later to be described, only during a total taking operation. For each unit of the machine there is provided a pair of arms H (one shown) secured to the shaft 69 and supporting between them a bail 1 IA which normally contacts the rear edge of all the bell cranks 63 in the unit. During a total taking operation the shaft 69 will rock in a counter-clockwise direction (Fig. 3) and the motion thus imparted to the arms H and their supported bail 1 IA will rotate the bell cranks 63 also counter-clockwise to free all of the sectors 44 and 46, as above.

Referring now to Figs, 3 and 6 there is shown therein a portion of the hammer release mechanism and certain drive mechanisms of the head, including the means for reciprocating the bail rod 55. The shaft 12, 'positioned between the side frames near the rear of the machine, is the main drive shaft of the head and is continuously driven in a clockwise direction (Fig. 3) by a chain of gearing, not shown herein, which has its origin in the base of the machine. As shown in Fig. 6. a cam 13 is secured to the shaft 12 at its extreme right-hand end, and pivotally connected to the outside surface of the cam near its lower edge is a pitman i4 connected at its upper end to an arm 15 secured to a shaft 16. Rotation of the shaft 12, therefore, causes a reciprocatory rocking motion of the shaft 18. Referring now to Fig. 3, a lever 11 is also secured to the shaft 16 and bears on its outer end a stud 18 adapted to cooperate with the rear edge of an arm 19 loosely mounted on the shaft 18. The lower end of the arm 19 is connected to a longitudinal link 8|, the front end of whichis fastened to one of the arms 56 supporting the bail rod 55. It is apparent from the linkage just described that the shaft I6 will rock in a clockwise direction (Fig. 3) during the first 180 of rotation of the shaft 12 and that during that period the stud 18 will pick up the arm 19 and through the connecting link 8| will cause the bail arms 56 to move forward about their pivot 45 to release the sectors 44 and 46. During the second 180 of rotation of the shaft 72, the shaft 16 returns to normal position thus permitting the ball 55 to restore the type seetors under tension of spring 82 connected at one end to the link 8| and anchored at its other end to the rear frame of the machine. As shown in Fig. 3 the link 8| extends rearwardly of the arm 19 and limits against a set screw 83 in order to prevent an overthrow of the restoring bail 55. In order to insure an even positive driving action of the bail rod 55 there is provided a pair of levers 17, a pair of arms 19 and a pair of links 8| for each unit of the machine, each link 8| being connected to a separate bail arm 56.

The hammer release mechanism operates as follows: Each of the type sectors 44 is formed with a cam shoulder 84 (Fig. 3) cut in its lower edge and adapted to cooperate with one end of a lever 85 pivoted at 85 to a fixed frame plate. The other end of the lever 85 rests in a comb plate or bracket 81 and lies just under an arm 88 also guided in the comb plate 81. The front end of the arm 88 is pivotally connected to a latch member 89 pivoted at its lower end to a rod 91.

1 The upper end of the latch 89 normally engages a lip on a printing hammer 92 and holds the hammer in ineffective position against the tension of a spring 93. The hammer 92 is further prevented from moving from normal position by a bail 94 supported between a pair of arms 95 (one shown) secured to ashaft 99. The hammer 92 pivots on this shaft 96 and a short extension of the hammer engages the bail 94. The shaft 95 receives a reciprocable rocking motion once for each cycle of the main shaft 12 and thus causes the bail 94 to swing away from the hammer 92, which continues to be held ineffective by the latch 89. It is evident that with the parts positioned as shown in Fig. 3 bail 94 will pass idly over the arm 88. However, if a type sector 44 is permitted to move forward at about the same time the bail 94 begins its forward motion the cam shoulder 84 will rotate the lever 85 a short distance clockwise (Fig. 3) about its pivot 86 and cause a corresponding elevation of the arm 88 and so position the said arm as to enable the bail 96 to strike its rear edge and force the latching member 89 out of engagement with its hammer 92. The spring 93 is then free to exert its tension to swing the hammer 92 about its pivot 96 and causes the hammer to strikewhichever type element 9'! has been moved to printing position. The type elements 91 recordtheir impression upon a record sheet surrounding a platen 98 in the usual manner. The mechanism for rocking the shaft 95 is shown in Figs. 3 and 7. A longitudinal link 99 is pivotally connected at one end to the arm 19, loosely mounted on the shaft 16, and is resiliently connected at its forward end to another link in! (Fig. 7) which is in turn connected to an arm I02 fast on the shaft 99, Rotation of the arm 19, therefore, results in movement of the restoring bail 55, as previously mentioned, and also causes the rocking of the bail 94 to release the hammers 92. The bail 94 is common to all of the hammers 92 in one unit and there is also provided a second arm I92, on the opposite end of the shaft 96, and a second set of links 99 and HH motivated in 'the previously described manner by the second arm 19.

As shown in Fig. 6 mechanism is also provided for rocking a third operating shaft I03, which is situated near the front of the machine and controls the accumulator timing mechanism. The cam 13, secured to the shaft I2 as previously described, is adapted to cooperate with a roller! on one arm of a bell crank I05. The

bell crank I05is pivoted at I06 to an upstanding bracket I'I secured to the base plate of the head. Pivotally connected to the other arm of the bell crank I is alink I08, which extends towards the front of the machine and is connected at its other end to an arm I09 fast on the shaft I03. With the above linkage positioned as shown in Fig. 6, which is its normal position, the roller I04 is resting on the low dwell of the cam I3 and hence is inactive. During the course of rotation of the shaft I2 the rise on the cam 83 will move under the roller I04 to rock the bell crank I05 counter-clockwise (Fig. 6) and so cause a corresponding rocking motion of the shaft I03. A spring III tensioned between a stud II2 on the bell crank I05 and the frame work of the machine serves to maintain the roller I04 in constant contact with its cam I3.

ACCUMULATING MECHANISM The description of the machine as thus far progressed has been confined to the means for sensing and recording items from a perforated record card. Mechanism is also provided for storing these items in a set of accumulator wheels I I 3 (Figs. 3 and 4) and for releasing their accumulation during total taking operations. The accumulator employed in the present machine is identical in construction and mode of operation to the accumulator disclosed in the previously mentioned application S. N. 125,375 and is capable of accumulating items of either a positive or negative character. The several units of the machine each contain their own accumulator which is individually operable from a respective field in the card, so that, while a positive item is being accumulated in one unit, a negative item may be accumulated at the same time in another unit.

During a total taking operation all of the units clear simultaneously and effect printing of their respective balance, which may be either postive or negative. As shown in Fig. 4, the actuating racks 46 are formed with gear teeth I I4 adapted to mesh with and rotate the gear wheels I I3. The wheels II3 are normally disengaged from the racks 46 and occupy the position shown in Fig. 4 enmeshed with carry sectors II5. During adding cycles of I the machine, the wheels II 3 are permitted to remain out of mesh with the teeth II 4 during the forward stroke of the sector racks 46 and are caused to engage the teeth at the beginning of the return stroke. At the end of the return stroke they are again disengaged and resume their normal position. During subtracting and total taking cycles the procedure is just the opposite, that is, the accumulating wheels I I3 are moved into engagement with the racks at the beginning of their forward stroke and out of engagement at the beginning of the return stroke. The normal function of the accumulator is to operate additively and it will alter its operation only whe a special control hole is sensed in a card. A total takingoperation is initiated automatically upon a change in the designatory matter of a card.

The shaft I03, which, as previously mentioned, is given a reciprocable rocking motion for every cycle of the main shaft 12 is the equivalent of a similar shaft disclosed in Figs. 1, 3 and 4 of the previous application S. N. 125,375 and indicated therein by the reference numeral 19. Each unit of the present machine is separately controlled by operating mechanism, mounted on the shaft I03, which is identical to that shown in the above application as mounted on the shaft 19. The construction and operation of the accumulator unit is, briefly, as follows: A pair of frame plates II6 of the accumulator and these plates are themselves supported by cross shafts I I1, I "A, and I I8 mounted between the side frames of the machine. The accumulator wheels II3 are loosely mounted on a shaft H9 supported between a pair of arms I2I (one shown), one of which is pivotally mounted on the inner surface of each side frame II6. A downwardly extending arm (not shown) is connected to the left-hand side of the pivoted frame comprising the arms I2I and shaft I I9 and bears a roller I22 (Fig. '7) midway along its surface. The roller I22 rests on the upper edge of a cam plate I 23. The cam plate I 23 is secured at its middle to a shaft I24 and is adapted to be rocked in a manner not completely shown herein by an arm I25 secured to the shaft I03. The motion of the cam plate I23 as it is rocked from normal is clockwise, as viewed in Fig. '7, the arm I25 being ineffective on the forward stroke of the shaft I03. Clockwise motion of the cam plate I23 causes a rise formed thereon to move under the roller I22, thus forcing upward the roller, the arm supporting the roller and the arms I 2I which support the shaft H9. The above operation causes the engagement of the wheels II3 with the racks 46 at the beginning of the return stroke of the racks which, as explained above, is its adding operation. The wheels I I3 are withdrawn from engagement with their racks at the end of the return stroke by a link I26 connected at one end to the cam plate I23 and connected at its other end, by means of a pin and slot connection, to an arm I21 secured to the shaft I03. As explained more fully in the above mentioned previous application, the arm I2! engages the link I26 positively at the end of the return stroke of the racks 46 and causes the cam plate I23 to rock in a counter-clockwise direction (Fig. '7) to permit the roller I22 to descend from its raised position and so disengage the wheels II3 from the teeth II4. During subtraction operations the mechanism described above is disabled and a separate chain of actuating mechanism is rendered effective to engage the wheels II 3 and the racks 46 at the beginning of the forward stroke and to cause their disengagement at the beginning of the return stroke. The arm I 25 comprises one arm of a bail-shaped rock lever, the other arm of which is indicated at I28 in Fig. 7. A wipe pawl I29 is pivotally connected to the rear end of the arm I28 and is adapted to cooperate with an assembly of plates comprising two pin carrying plates I 3! and I32 loosely mounted on the shaft I 24 and a third plate I33 which is slotted to engage pins on the plates I3I and I32 and a stud I34 on the cam plate I 23. A spring I35 tensioned between the upper portion of the cam plate I23 and an arm (not shown) of the slotted plate I33 tends to retain the plate assembly I 3I I32, and I33 in the position shown in Fig. 7. With the plates thus positioned, the wipe pawl I29 will pivot idly about the pins on the plates I3I and I32 and will move from and return to its normal position without altering the position of the cam plate I23. If, however, the slotted plate I 33 is moved downwardly by means of a lever I36, against the tension of the spring I 35, the pin plates I3I and I32 will pivot from their normal position and enable the pins carried thereon to be positively engaged by shoulders on the wipe pawl I 29, on both the forward and return stroke of the shaft I03. Downward motion of the plate I33 serves to disable the first mentioned actuating shown herein, but which isfully disclosed in the application S. N. 125,375. Operation of the lever I36, therefore, will render ineffective one train of accumulator timing mechanism and render effective another train of mechanism. The lever I36 is adapted for operation only during subtract and total taking cycles.

As mentioned earlier in the specification each subtract item which is punched in a card, must also have punched in the same field a special control hole, the ultimate function of which is to cause the operationof the lever I36 and so permit the accumulator timing mechanism to function subtractively.

As shown in Figs. 2 and 6, the special control wire 39 is located at the extreme ri ht hand side of the translator 31 and is provided with a block I31 secured to the wire 39 near its upper end. A lever I38 (Fig. '6) pivoted at I39 to the inner frame of the translator 31, is provided with a stud Itl at one end which overlies the block I31. Theforward end of the lever I38 extends through the frame of the translator and overlies a stud I42 on an arm I63 loosely mounted on a shaft I48 supported by brackets I fastened tothe underside of the base plate of the head. A spring I30 tensioned between the arm IE3 and a fixed plate I40 tends to retain the arm I63 in normal elevated position. Pivotally connected to the right hand end (Fig. 6) of the arm I03 is a link I66 extending upwardly through an opening in the base plate of the head and connected at its upper end to an arm I41 secured to the right hand end of a shaft I48 loosely supported between the frame plates I I6. An individual shaft I48 is provided for each accumulator in the machine. In tracing the above linkage through an operation it is apparent that, when a special control hole is sensed in a card, the wire 39 and the block I31, integral therewith, will be moved upward to rotate the lever I38 about its pivot I39 a short distance in a counter-clockwise direction, (Fig. 6) thereby depressing the arm I43 against the tension of spring I30, and, through the connecting link I66, rock the shaft I48 in a clockwise direction (as viewed in Fig. 6). Individual subtract mechanism, including a wire 39 and associated linkage, is provided for each computing unit of the machine. As shown in Fig. 7 an arm I49 is secured to the left hand end of the shaft I48 and one end of a link I5I is connected to the lower end of the arm. The link I5I extends rearwardly and is operatively associated, through a pin and slot connection, with one arm I52 of a bail shaped member I53. The member I53 is pivoted at I56 to a stud in the frame member H6 and is formed with another arm I36, which, as previously described, is the operating medium for depression of the plate I33. As viewed in Fig. 7, the direction of rotation of the shaft I48, as it moves from normal position, is counter-clockwise so that actuation of lever I38, as previously described, will operate lever I36 in the desired manner.

In the accumulator of the previous and present application there is provided a single wheeldelayed carry transfer mechanism adapted to function during both adding and subtracting operations of the machine. The construction and operation of the tens carry mechanism employed herein is fully disclosed in my previous application S. N. 125,375 so only a brief description of the mechanism will be included in this specification. As previously mentioned, the accumulating wheels H3 are normally in mesh with a set of four toothed carry sectors H5 (see Figs. 3 and 4). The carry sectors H5 are loosely mounted on a shaft I55 rigidly supported between the frame members H6. Fastened to the forward end of each of the carry sectors H5 is a spring I56 connected at its other end to a movable spring tensioning bail I51. The spring bail I51 is supported by arms I58 pivotally connected to the side frames H6 (see Figs. 4, 6, and 7), and normally occupies the position shown in Fig. 4 wherein it tends to impart a counter-clockwise motion of rotation to the carry sectors H5, In order to retain the sectors H5 in normal position, against the tension of springs I56, an arm I59 of each sector H5 is normally engaged by a latch I6I associated with the accumulating wheel H3 of the next lower denominational order, and pivoted on a rod I62 supported between the frames H6. Also associated with each wheel H3 is a trip pawl I63 pivoted to a rod I66 and formed with an upstanding cam tooth I65 which normally engages a wide tooth (not shown) on the wheel H3. The tooth I65 and the wide tooth on the wheel H3 are normally held in positive engagement by a bail I66 which extends under the rear edge of all the trip pawls I63. The ball I66 is supported between rear extensions of the pair of arms I2I, which support the shaft H9. so that the trip pawls I63, the bail I66 and the wheels H3 all retain the same relative position as the wheels are moved into engagement with the racks 46. As shown in Figs. 4 and 7, the bail I66 is moved out of its retaining position, at about the same time the wheels H3 reach engaging position with the teeth I I6, by a slide I61 pivotally mounted on the cam plate I23, and a bell crank I68 operable by slide I61. The bell crank I68 is secured to the same shaft to which the bail I66 is fastened. The shaft is indicated in the drawings at I69. The motion of cam plate I23 as it moves from normal, therefore, will disable the retaining bail I66 and free the trip pawls I63, although the pawls I63 and the wheels H3 will retain their same relative position for the moment. When, however, one of the wheels H3 is caused to rotate beyond its zero position, in either direction, the wide tooth on the wheel H3 will strike the cam tooth I65 and force thetooth out of the path of the wheel thereby rotating the entire pawl I63 a short distance in a clockwise direction (Fig. 4), about its pivot I64 in which position it will be retained by a latch member I1I. Now, as the wheels are returned to normal, out of engagement with the rack 66, the lower edge of the displaced trip pawl I63 will strike a forwardly extending arm I12 of the latch I6I of next higher denominational order to cause the disengagement of the latch I6I and the arm I59 thus freeing the sector H5 and allowing it to rotate under the tension of the spring I56 a distance limited to one tooth-space by shoulders cut in the latch I6I. The wheels I I3 are fully restored to normal just prior to the release of the sectors H5 so that the carry motion of any sector H5 is transmitted directly to its associated accumulator wheel H3. A cam slot I13 is cut in each of the carry sectors H5 and a shaft I14, supported between arms I10 (one shown) pivotally mounted on the side frames I I6, cooperates with the slots I13 to return the sectors H5 to normal and to release the trip pawls I63. The shaft I14 is connected by a link (not shown) to the cam plate I23 and is moved thereby into the lowermost portion of the slot I13. and returned, once for each '15 cycle of the main shaft I03. The trip pawls I 63 are reset during the same machine cycle in which they are tripped while the carry sectors H are not reset until the accumulating wheels H3 move from normal position on the following cycle. The spring tensioning bail I51 is, as before stated, pivotally mounted on the side frames H6 and is adapted, during subtracting cycles, to be shifted to the position shown in Fig. 8. When the bail I51 is in subtract position, the tension imparted to the carry sectors H5 is clockwise (as viewed in Fig. 4). Referring now to Fig. 6, mechanism is provided for shifting the spring bail I51 from add to subtract position automatically when a negative control hole is sensed in a card. As previously described the elevation of special control wire 39 causes the arm I41 and the shaft 148 to which the arm I41 is secured to rock in a clockwise direction and alter the timing of the accumulator actuating mechanism. Pivotally connected to the rear end of the arm I41 at the same point where the link I46 is connected is a downwardly extending slide I slotted at its lower end to engage a stud I16 fixed on the outside of the right hand frame member H6. A rearwardly extending arm I11 of the slide I15 engages, through a pin and slot connection, a triangular shaped operating member I18. The upper end of the member I18 is formed with a hook I 19 on its left-hand end and a. similar hook I 8I on its right-hand end adapted to cooperate with pins I82 and I83 respectively, on a swinging lever I84 pivoted at I85 to the frame member II 6. The lever I84 is formed with a forwardly extending arm I86 which is slotted at its forward end to engage a pin I81 on one arm I58 supporting the spring bail I51. The operating member I18 is connected at I88 in a manner not herein shown, to the shaft I14, and through it receives a downward pulling motion once for every com plete operation of the shaft I03. When the above linkage occupies its normal adding position (Fig. 6) the hook I19 on the member I18 and the pin I82 on the lever I84 are in efi'ective cooperative position while the hook I8I and the pin I83 are in ineffective position. When the operating member I18 is actuated while in its adding position, therefore, the hook I19 will engage the pin I 82 at about the end of its (the hooks) stroke and serves no purpose other than to retain the bail I 51 in the position it now occupies. If, however, a subtract item is to be entered into the accumulator, the arm I41 of that unit will be rocked, as previously described, the slide I15 will be depressed and through its arm I11 shift the member I 18 rearwardly about its pivot I88 to a point where the hook I8I lies just above the pin I83 and at the same time render the hook I19 and the pin I82 ineffective. Now, if the actuating member I18 is pulled, the lever I84 is given a positive actuating movement about its pivot I85 and the arm I88 rises upward carrying with it the spring bail I51 to shift it to subtract position. The spring bail shift mechanism just described is returned to normal after each subtract operation by the previously mentioned spring I38.

With the exception of the controlling means for instituting a'subtract operation, the accumulating mechanism of the present machine is the same as that disclosed in the previously mentioned application S. N. 125,375.

TOTAL TAKING MECHANISM The machine of the present invention is adaptslide 35. When the operator of ed to take totals automatically from a change in the designatory matter on a card. The mechanism for performing this function is old and well known in the Powers machine and is fully disclosed in the patent to Lasker 2,044,119. The total taking mechanism comprises, briefly, a normally inactive cam and ratchet unit under the control of a cam on the main cam shaft 6 (Fig. 1) and adapted to be tripped and thus made active through movement of the change of designation slides 35. When it is desired to take totals by this method all of the cards to be fed through the machine are punched with a designating number. Any column or columns on the card may be used for this purpose, but the same columns must be used throughout one set of cards. In the usual accounting problem, the items to be listed and accumulated will fall into a plurality of separate groups or divisions and ordinarily it is desirable to clear the accumulators after each group has been tabulated and to print that total on the record sheet. Each group may be designated by a different serial number and each card of a group will bear the number assigned to that group. Before tabulation the cards must first be sorted according to serial numbers in order that all the cards belonging to one group will be arranged together. As previously stated each time a pin 24, of the upper pin box 23, (Fig. 2) is raised the change of designation slide 35 associated with the same column as the raised pin will be cammed leftward or toward the front of the machine. Positioned above and to the front of the pin box 23 is a plurality of hand settable slides I89 each of which pivotally supports a dependent interponent I9I. A slide I89 and an interponent I9I are provided for each column of the card. The normal position of each slide I89 is the position shown in Fig. 2 with the lower end of the interponent I9I just above and in front ofthe nose of its respective the machine has determined in which columns of the card the group serial numbers appear, he selects and depresses the corresponding slides I89. The interponent ISI for each of the depressed slides is thus lowered from its normal in the path of its slide 35. A spring detent I92 serves to retain the slide I89 in either of its set positions. Also in the path of the slides 35, but beyond their scope of movement, is a bail I93 supported between a pair of arms I98 (one shown) secured to the shaft I94. The interponent I9! is lowered between the slide 35 and the bail I93 so that motion of the slide 35 will be imparted directly to the bail I93 and through its supporting arms to the shaft I94. The slides I89 are set to lowered position before the machine is started so that as the sensing pins rise on the first card, the slide 35 is cammed out of its normal position to trip a total and, when the pins 24 reach their extreme elevated position, returns to normal. As fully explained in the Patent 2,844,119 the retraction of the locking slides 25 and 26 occurs at position and lies directly a time when the sensing pins I4 are in approxi- I original pins 24 will not be permitted to descend L and the extrusions, 36 on each elevated pin 24 will remain in the upper portion of its associated cam slot in the slide 35. As soon as all the cards of one group have been listed the first card of a new group, bearing a new serial number, will appear. A new set of pins I4 will pass through the card, a

i new set of pins 29 will be elevated and the old clockwise direction (Fig. 4).

pins 24 will descend to normal. Either the ascent of the new pins or the descent of the old pins may cam the slide 39 leftward and in either case the result is the tripping of a total, as described above.

A complete view of the mechanism of the total unit is not included in this application, only one cam of the complete assembly being shown here. The cam I shown in Fig. 2 is the total pull cam of the total unit and it is adapted to cooperate with an arm I96 pivoted at I97 and bearing, at one end, a roller I98 which is spring urged to follow the contour of the cam. A link I99 is connected to the other end of the arm I96 and extends upwardly and forwardly in the machine (see Figs. 2, 3, and 4) where it is connected to an arm 29I secured to a rockshaft 202 pivotally supported between the side frames of the head. It is apparent that when a high point of the cam I95 passes under the roller I98 on the arm I96 the arm I96 will pivot in a counter-clockwise direction (Fig. 2) to pull the link I99 downward and so rock the shaft 202 a short distance in a One arm 29I is secured to the shaft 202 for each unit of the machine, for a purpose later to be described. There is, however, but one link I99 for the purpose of rocking the shaft 202. The shaft 202 may be called the total shaft of the machine since the rocking motion thus imparted to it is employed to clear the accumulators and condition the machine for a new series of listing operations. As shown in Fig. '7, the motion of the shaft 202 is also used to rock the previously mentioned rear total shaft 69 to depress the zero stops 43 during total strokes. An upstanding arm 59 is secured to the shaft 292 near its left-hand end and the upper end of the arm is pivotally connected to a long rearwardly extending link 69,

the rear end of which is connected to a downwardly extending arm 10 fast on the shaft 69. Counter-clockwise rocking motion (Fig. 7) of the shaft 292, therefore, will be transmitted through arm 5!), link 69 and arm 10 to the shaft 69 to rock thelatter shaft a short distance in a clockwise direction. As shown in Figs. 4 and 7 a short rearwardly extending arm 203 is also secured to the shaft 292, near its left-hand end, and is connected at its free end to an upwardly extending link 299. The link 299 is connected, at its upper end to an arm 205 fast on another rock shaft 206. The shaft 206 is loosely supported between the main side frames of the machine. Also secured to the shaft 206 is an upstanding arm 201 pivotally connected at its upper end to a long rearwardly extending link 208 supported at its rear end by a fixed bracket (not shown) in such a. manner as to permit horizontal sliding movement of the link. As viewed in Fig. '7 a counterclockwise motion of the shaft 202 will rock the shaft 296 in the same direction (through link 294) to force the slide or link 298 rearwardly. Positioned on the side of the slide 208 is a stud 209 which is adapted, when the slide 208 is actuated, to contact an arm 2| I formed on the lever I36 and to rotate the said lever I36 counterclockwise about its pivot I54 to depress the plate I33 and render the wipe pawl I29 effective, as previously described. The above operation results in the engagement of the wheels II3 with their actuating racks 66 at the beginning of the forward stroke of the racks. An additional function of the slide 298 is to prevent the disabling of the locking bail I66 in order that the wheels II3 may be returned to a positive zero position and thus accurately position their associated type sectors M. This is done-through a pin 2I2 positioned on the side of the slide 298 and a cooperating cam slot 2I9 cut in the previously mentioned slide I61.

When the slide 209 is shifted rear-.

wardly the pin 2I2 is moved into position where it may be engaged by a raised portion of the slot 2 I 3 and so force downward the slide I61 to a point where its operating arm is unable to contact the bell crank I68, and, therefore, cannot rock the shaft I69. The shaft 209, as previously noted, extends between the side frames of the machine and for each computing unit there is provided an arm 20'! and slide 299. Each unit is identical in its operation to the one described above.

TRUE NEGATIVE TOTAL Pnm'rmc MECHANISM The accumulating mechanism thus far described is the same as that disclosed in the previously mentioned application S. N. 125,375 with the exception that subtract and total taking operations are initiated automatically from perforated record cards instead of manually through the depression of a key. However, the machine of the earlier application was not particularly well adapted for the printing of negative totals. In the above application, if a total was caused to be taken while a negative balance was in the accumulator, the amount printed would not be the true algebraic total but the complement of the true amount. Mechanism was provided whereby a negative total could easily be recognized as'such, and then it had to be visually translated by the operator into the true algebraic representation. In the present machine novel printing mechanism has been evolved which operates without a change in the old accumulator and which operates eifectively to print a true algebraic total upon every total taking operation of the machine, regardless of whether the balance contained in the accumulator is of a positive or negative character.

As shown in Figs. 4 and 9, herein, each of the type sectors 99 carries two separate sets of type elements 97 and 2| 9. The upper set of elements 91 is arranged in the usual order from zero to nine, while the lower set of elements 2M is arranged in opposite numerical progression, that is, from nine to zero. A blank space 2l5 separates the two sets of elements and an additional zero element precedes the nine element of the second set. The type sectors shown in Fig. 9 illustrates the exact arrangement of all of the above mentioned elements 91 and 2M. In all listing and positive total taking operations printing is effected through the upper set of type elements 91 while the lower set 2H3 is latched in inefiective position. However, if a total is taken while the accumulator contains a negative balance, printing will be effected through the lower set of type elements ZI I while the upper set 91 will be raised beyond the range of the printing hammers 92 and hence rendered ineffective.

Referring now to Figs. 4 and 8, the carry sectors H5 are, as previously described, under the control of the shiftable spring tensioning bail I51 and the latches IBI. The carry sectors, therefore, have three different positions. They have, first, a normal position at which time the latches IBI are effective and the springs I56 ineffective, second, with the latches I6I inefiective and the spring bail I51 in add position, and third, with the latches I 6| ineffective and the spring bail I51 in subtract position. It should be understood that the latches IIiI operate independently of one another, as do the carry sectors 5. It should also be understood that when the accumulator wheels H3 are overrun in a negative direction all of the carry sectors to the left of the highest significant order will move in a subtract direction and assume the third position noted above. In Fig. 8 hereof the carry sector I I5 of highest denominational order is shown in the position it assumes immediately following an operation which causes the wheels H3 to overrun in a negative direction. The dotted circles N and A in the same figure represent respectively the normal and add positions of the same carry sector H5. The carry sector H5 of highest denominational order bears a stud 22| (Figs. 4, 8, and 14) on its lower front surface which is adapted to cooperate with a pair of fingers 222 and 223 formed in a latch 224. The latch 224 is pivoted near its mid-point at 225 to a small frame member 226 fixed to the base plate of the head. The front edge of the latch.224 is formed with a pair of detent notches adapted to cooperate with a roller 22? on the upper end of an arm 228 pivoted to the frame 226. A spring 229 tensioned between the arm 228 and the frame 226 serves to retain the roller 22! in constant contact with the front edge of the latch 224. As viewed in Fig. 4 the carry sector I i5 is in its normal position with the finger 222 resting directly on the stud 225. If, however, the spring bail i5? is shifted into subtract position and the accumulator goes negative then the latch lti associated with the sector of highest order will be dis abled and permit its sector I I5 to move in a clockwise direction about its pivot I55 until it reaches its full carry position (Fig. 8). The latch 224 is thus caused to rotate, with the sector l 55, in a counter-clockwise direction (Fig. 4) about its pivot 225 until the roller 22'! on the arm 228 engages the upper detent in the front edge of the latch (Fig. 8). The latch 224 will remain in its raised position until the accumulator changes its registration from negative to positive, at which time the stud 22! on the last sector will lie in the position marked A in Fig. 8. In moving from N to A the stud 2211 will pick up the arm 223, rocking it downward and thus restore the latch 224 to normal. Positioned on the lower rear surface of the latch 222 is a stud 23% which normally lies in the path of a bent-over lug 232 formed at the front end of a horizontally movable slide (see also Fig. 14) Also normally in the path of the lug 232 is an arm 234 pivoted at to the frame plate 226, and urged to retain its normal position by a spring 234A. A lever 23313 is also pivoted at 235 and is formed with a rearwardly extending bent over portion 2340 which lies under the arm 234. The forward end of the lever 23418 is pivotally connected to an upstanding arm 236 connected to the rear end of one of the previously mentioned arms 28! secured to the total shaft 282. It is apparent that the rocking of the total shaft 2G2 (clockwise as viewed in Fig. 4) will rotate the lever 234B in a counterclockwise direction, about its pivot 235, thus elevating the arm 234 in the same direction out of the path of the slide 233. As shown in Figs. 4 and 5 the slide 233 extends rearwardly through the machine and is loosely supported by rods 237 and 238 which form a part of the stop basket 42, and by cross bars of .the stop tray (not shown in full) which supports all of the stop baskets 42. Resiliently connected to the rear end of the slide 233 is aqlink 239 formed with two slots 24i each of which is adapted to cooperate with studs 242 formed on the side of the slide 233. A spring 243, tensioned between dependent arms of the slide 233 and the link 239 normally serves to maintain the studs 242 in the forward end of the slots 24!. The rear end of the link 239 is connected to a short forwardly extending arm 244 the front end of which is, in turn, connected to an upstanding lever 245 (see Figs. 5 and 10). The lever 245 is pivotally connected at its upper end to a stud 246 (Fig. 10) secured to an auxiliary frame member 241 fastened to a pair of cross bars 248 and 249. As shown in Fig. 10 there are two auxiliary frame members 241 for each computing unit of the machine. Both are fastened to the cross bars 248 and 249.. Referring again to Fig. 5 the lever 245 bears a roller 25l which rides in a grooved box cam 252 secured to the main head shaft 12. The normal position of the cam 252 is shown in Fig. 5 with the highest portion 253 bearing directly on the roller 25!. When the shaft 12 begins to rotate, however, the roller 25E rides off of the rise 253, causing the lever 245 to move in a clockwise direction about its pivot 246 to draw the link 2319 forward. The spring 243, connecting the link 239 and the slide 233, will tend to carry the slide 233 forward also, but, if either the arm 234 or the latch 224 are in their normal blocking positions, the slide 233 will be held in its original position, against the tension of the spring 243. This attempted reciprocation of the slide 233 occurs once for every cycle of the shaft l2. It is apparent, however, that the only time at which the slide 233 will be permitted to complete a full forward stroke is when the latch 22:?! has been raised to subtract position (at which time the stud 223i will be out of the path of the lug 232) and the total shaft 2632 rocked while the latch 224 is held out of blocking position.

Also secured to the shaft '52 is another cam adapted to cooperate with a roller bearing arm loosely mounted on a rock shaft 256 supported between a pair of brackets (one shown) dependent from the cross bar A spring 257. tensioned between the arm 255 and a stud on the cross bar 2&8 serves to maintain the roller on the arm in constant contact with the cam 25%. The arm 255' is reciprocated about its pivot 255 by the cam once for each cycle of the shaft l2. Rigidly secured to the shaft 256 is a short, downwardly extending finger 253 lying in approximately the same plane as the arm 255 but with a distance separating the two members that about equals the distance moved by the arm when the high point of the cam 25 i engages its roller. The purpose of the arm 255 is to rock the finger 252 and hence the shaft 256, on negative total taking operations. During all listing and positive total taking operations the arm reciprocates ineffectively and the shaft remains motionless. As shown in Fig. 5 a slide 2% is mounted on a bracket 26f), (shown in Figs. 12 and 13), fixed to the rear of the stop tray fill, in such a manner as to permit the slide 25%} to move vertically with respect to the bracket 2%. Pivoted to the upper end of the slide 259 is an in terponent 263! which has its upper end bent over in the form or" a lug 262. A spring 269A, tensioned between the lower end of the interponent 259 and a stud on the slide 259 tends to maintain the interponent in vertical alignment with the slide. Positioned on the lower end of the slide 259 is a roller 263 which is urged into contact with the lower edge of the slide 233 by a spring 264 tensioned between a stud on the rear of the slide 259 and the shaft 256. The lower edge of the slide 233 is formed with a cam surface 265 along which the roller 263 is permitted to ascend only during a negative total taking operation. When the slide 233 moves, forward and the roller 263 ascends the. cam surface, 265, the interponent 261 will rise and position its turned over lug 262between. the arm :25 and the finger 258.so that clockwise motion (Fig. 5) of the arm 255 will be transmitted through the in+ terponent 26l to the finger 258 and result ina similar (clockwise) 'motion of the shaft 256.

Also secured to the shaft 256 a pair of arms,

266 (one shown) which support between their forward ends a bail 261 positioned directly under a plurality of slides 268. There is one slide 268 for each denominational order of a computing unit, that is, one forevery type sector 44. The slides 268 are formed with downward extensions 268A guided in the stop basket 42, each extension being connected to an arm on the bell crank 63 by a spring 240. Each slide 268 is resiliently associated with an elevating member 269 through pin and slot connections and a spring 211. Clockwise rocking motion of the shaft-256, therefore, willelevate all ofthe slides 268, and also the elevating members 269, through springs 21L The upper edge of each member 269 is normally positioned just under a stud 212 on the previously mentioned latch 49. Elevation of each membr 269 will, therefore, cause its associated latch 49 to rock counter-clockwise about its pivot 51 and move out of engagement with the stud 46 on-the type sector 44. The type sectors 44 are thus free to move forward, without the actuating racks 46, under tension of their springs 52. Each type sector 44 is formed with a rearwardly extending portion 213, the rear end of which is formed as a cam-like book. The computing unit in which the above operation has taken place is now conditioned to print a true negative total, and it will be seen that as the restoring bail 55 swings upward, as previously mentioned, all of the sectors .44 will follow in the usual manner and the studs 48 of the released type sectors 44 will move forward in the slots 41 of the stationary actuating sectors 46 until they reach a point just short of the forward end of the slots. At this point the hook-like ends of the extensions 213 will engage the studs 212 of the latches 49 and each pair of sectors 44 and 46 will move forward together a distance determined by the number of tooth spaces required for their associated wheel I 13 to return to normal. The zero stops 43 have, in the meantime, been withdrawn in the'previously described manner. As shown in Fig. 5 each of the members 269 is formed with aforwardly extending arm 210 along'whichthe stud 212 rides and which acts to retain the stud 212 and the hook on 213 in positive engagement. At the time the extensions 213 engage the studs 212 the type sectors 44 have progressed upward to such'an extent that the lower sets of type elements 214 are in printing position and the upper setsof elements 91 arein effective. held immovable at this time, the first type element (zero) of the lower set would be aligned in printing position. One step of movement would bring the nine element into printing position, two steps, the eight element, and so on.

In considering the above linkage it is evident that if this were-the only mechanism provided for printing a true negative total, the printed balance would still be inaccurate in nearly every case, since each sector 44 would print-the tens If an actuating sector 46 were to' be.

complement of the amount in the accumulator, whereas the true negative total must be represented by a" nines complement in all denominational orders to the left of the lowest significant order. It is evident that in a negative total operation which involved theiprinting of just one significant numeral, and that one numeral appeared in the highest denominational order, then the balance would be represented as a full tens complement and the above mechanism would. be ,adequate for the operation. The number 1,000,000,000, for example, would be printed as a full tens, complement- However, in order to insure the printing of a true balance upon every Y negative total taking operation of the machine, mechanism is provided for permitting all of the type sectors 44 to theleft of the lowest significant order to move one additional space whenprinting a negative total. Positioned just above each of the studs 212 is the forward end of a lever 214 (Figs. 5 and 10) pivoted'to a shaft 215secured between the auxiliary frames 241. 4 The lever 214 extends rearwardly' of the pivot-215 and hasconnected at its rear end a vertical arm 216 guided in a bracket 211. 'Resting on the upper end of each of the arms 216 is a carry. link 218 also guided in slots in the bracket 211. The forward end of each link 218 is-connected to one arm 219 of a bell crank pivoted on the shaft 215. The other arm 281 of the bell crank overlies a rear extensionof the elevating member 269 associated with the next higher denominational order and is adapted to depress, it through the following means. Secured to'a shaft 282, loosely supported between the side frames of the machine, is an arm 283 bearinga roller 284 on its lower end which is constrained through a spring 285 to contact the outer surface of the box cam 252. The outer surface of the cam 252 is formed with a .rise 266 adapted to pass under the roller 284, and, in so doing, rock the shaft .282 in a counterclockwise direction (Fig. 5). Also secured to opposite ends of the shaft 282 is a pair of arms 281 (one shown) which support betweentheir upper ends an actuating bail 288. Under normal conditions of operation, the actuating bail 288 is positioned directly behind the rear edges of the carry links 218 and is adapted when reciprocated by the shaft 282 to propel the links 218 forward and rotate the bell cranks 219 and 28l counterclockwise'about their pivots 215 to depress the members 269. This motion .occurs with every cycle of the main shaft 12 but if no members 269 are raised the motion is, of course, ineffective.

A spring 289 tensioned between the lever 214 and the link 218, acts to maintain the. link and the arm 216 in contact. Another spring 291, tensioned between the arm 219 and the lever 214 maintains the bell crank 219 and 281 and the carry link 218 in normal position, and also serves to keep elevated the rear end of lever 214. A comb platef280, supported between the frames 6 241, guides and limits both the lever 214 and the bell crank 219'- 28l.

Returning now to the previously described operation involving the elevation of the members 269 and the consequent disabling of the latches 49, it is apparent that as the studs 212 are raised the levers 214 will pivot in a clockwise direction (Fig. 5) about the shaft 215 and thus lower the arms 216 and the carry links 218 which the arms support. The links 210 are thus placed below the range of the actuating bail 268 and as long as the studs 212 remain below the forward end of their respective levers 214, and in elevated position,

the links will remain in this ineffective position, Now, as the sectors 44 swing forward with the bail 55, the extensions 213, thereof, will engage the studs 212 and, in all those denominational orders which are not forced to remain at zero, the sectors 44 and the racks 46 will move forward together. Considering now the lowest significant order,.it will be seen that, as the stud 212 leaves its normal position, under the lever 214, the lever will rock back to normal under the tension of spring 29! and thus elevate its associated link 218 again into the path of the bail 288. Immediately following this movement the bail 288 is actuated to propel the link 218 forward and rock the bell crank 219 and 281 counter-clockwise (Fig. 51 about its pivot 215 to depress the next higher order elevating member 269. Depression of this elevating member 269 will cause its associated latch 49 to rock in a clockwise direction about its pivot (through spring 51 and pawl 58) to release the hooklike extension 213 and permit the stud 48 on the type sector 44 to move to the full extent of the slot 41, thus providing the extra necessary step of movement to the sector 44 which will enable it to print a nines complement of the amount contained in the accumulator. It is evident that the sector of lowest significant order will not be released in the above manner and it will print a tens complement in the manner previously described. The actuation of the bail 288 is in such timed relation to the actuation of the bail 55 that the link 218 is propelled forwardly immediately after its elevation to effective position. Therefore, by the time the stud 212, of the next higher order, has moved one tooth space, its supporting member 269 will be forced clown and the sector 44 released. Fig. 11 hereof shows the true negative total printing mechanism in operative position just prior to the actuation of the bail 288. As shown in Figs. 5 and each of the carry links 218 is formed with a bent over ear 292, the forward end of which lies directly behind an open shoulder of the link 218 of next higher order. Forward motion of any link 218, therefore, will be imparted through the ear 292 to all of the links 218, to the left of the first operated link. The ear 292 and the shoulder of each link 218 are so arranged that even if a link is out of effective relation with the bail 288, the link may still receive and transmit the above described carry motion. All of the sectors 44 to the left of the lowest significant sector, therefore, will print a true nines complement, even though the normal function of some of those sectors would be to remain at zero. At the end of each negative total taking operation the enabling mechanism therefor is restored and completely reset through the operation of cams 252, 254 and the restoring bail 55. The bail 55 picks up all of the sectors 44 and 45 and returns them to normal, permitting the latches 49 to reengage their studs 48 and causing the sector heels 62 to again assume their normal position just to the rear of the upraised zero stops 43 (Fig. 5). The elevating members 259 are returned to normal through springs 24! just prior to the complete restoration of the sectors 44 and 45, when the roller on arm 255 rides off of the rise on its cam 254. A short time after the release of members 266 the high point 253 of the box cam 252 engages the rolier25l, causing the slide 233 to be retracted and forcing down the interponent slide 259. The blocking arm 234 will, of course, re turn to its original position immediately upon the restoration of slide 233 through the action of its spring 234A.

True negative total printing mechanism, identical to that just described, is provided for each computing unit of the machine. Each unit is individual with respect to both its controls and its operation and all units are adapted to clear simultaneously during a total taking operation. The balance printed in each unit may be either negative or positive and in either case the operation of one unit will not affect the operation of another,

Example of true negative total printing operation In order that the essential purpose and function of my invention may be easily understood the following specific example of a negative total taking operation is included in the specification.

Assume that a series of algebraic items have been entered into an accumulator and that the amount now contained therein is a positive five hundred and seventy-nine (579). Now assume that another card is fed into the sensing chamber and a negative amount of six hundred and twenty-five (625) is entered into the same accumulator as above. Since the amount -subtracted from the wheels is greater than the amount already contained therein it is evident that the accumulator will register a negative balance and if a total taking operation is initiated at this point the above described true negative total printing mechanism will automatically be rendered effective. The problem to be performed may be represented as follows:

579 Positive amount 625 Negative amount 999999954 Complementary balance set up in accumulator 000000046 True negative total During the carry operations incident to the entry of the above negative amount, the carry sector H5 of highest denominational order will rotate to subtract position and thereby elevate its associated blocking latch 224 out of the path of the slide 233, in which position it will be retained by the detent 228. Now, when the total shaft 202 is rocked and the blocking arm 234 moves out of normal position, the slide 233 is free to complete a full horizontal stroke and so permit the roller 263 on the vertically movable lever 259 to ascend along the cam surface 265 and position the interponent 261 between the arm 255 and the finger 258. Actuation of the arm 255, by the cam 254, follows immediately and causes the shaft 256 to rock and elevate all of the members 269 associated with that particular computing unit. All of the latches 49 will consequently be rendered ineffective and when the bail rod 55 swings upward. the type sectors 44 will follow under tension of their springs 52. Extensions 213 will finally engage the studs 212, on the latches 49, thereby picking up the actuating sectors 46, so that all of the sectors 44 and 46 will move forward together to position the proper type elements 214. The actuating sector 46 of lowest denominational order will be permitted to move four tooth spaces before the carry lug on its associated accumulating wheel H3 reaches zero. By referring to Fig. 9 and counting down four spaces from the top zero position of the lower group of elements it will be seen that the above four spaces of movement will position the type element six (6) at the printing line. Forward motion of the lowest order sector 46 will re-establish lever 218 in efl'ective position and permit its actuation by the operating bail 288. In the present example all of the sectors 44 will have moved forward so that all of the levers 218 will be in effective position, and an operation of the carry lugs 292 is unnecessary. All of the bell cranks 219-28! will be rotated counter-clockwise (Fig. 5) about their pivot 215, against the tension of springs 29L and all of the elevating members 269 to the left of the lowest order member will consequently be depressed against the tension of springs 21L The studs 212 associated with the depressed members 269 .are thus moved out of engagement with the hook-like extensions 213 and the studs 48 on the sectors 44 will move to the extreme forward end of the slots 41 before picking up their sectors 46. Thus an extra step of movement is provided for all sectors to the left of the lowest order sector. In the present example we have seen that the units order sector will print a six. The tens order sector will move five tooth spaces under the control of its wheel H3 and this plus the extra step of movement Just described brings the four (4) element to printing position (Fig. 9). The hundreds order sector and all of the sectors to ,the left of this order will move nine spaces under the control of their respective accumulating wheels H3 and the extra step of movement imparted to them results in a series of zeros being aligned in printing position. The printed balance, therefore, is 0000000 16 which is the true negative total.

Unless the negative total itself occupies all ten denominational orders, a string of zeros will a highly desirable embodiment of my invention,

it is obvious that many changes in form could be made without departing from the spirit of my invention, and I, therefore, do not limit myself to the exact form herein shown and described, nor to anything less than the whole of my invention as hereinbefore set forth, and as hereinafter claimed.

What I claim as new, and desire to secure by Letters Patent, is:

1. In a machine of the class described, the combination of an accumulator including accumulator wheels adapted to register a positive balance in its true form and a negative balance in its complementary form, actuating racks reciprocable from and to a normal position to enter items into said accumulator wheels, mechanism for causing a total taking operation during which operation said actuating racks reset said wheels to zero, type carriers operatively connected to said actuating racks and spring-urged to advance independently of said racks, a set of type elements mounted on each of said type carriers and arranged to print the number representative of the numerical position of a respective rack, a second set of type elements mounted on each of said type carriers and arranged in reverse order to the first said set for printing the complement of the numerical position of a respective rack, latching devices between each of said type carriers and its respective actuating rack whereby each type carrier is caused normally to move in unison with its rack and whereby the second said set of type elements is normally held out of printing position, normally ineffective means for disabling said latching devices, means acting in the operation of taking a negative total for conditioning said disabling means for operation to permit said type carriers to advance a determined distance relatively to said racks to bring the second said set of type elements into printing position, a set of feelers operating during a negative total taking operation and controlled by said actuating racks, each of said feelers being set in one position under control of its respective rack when the latter has not advanced from normal position and in another position when its rack has so advanced, and means controlled by each feeler whose rack has so advanced to permit all of the type carriers of hig er denomination to advance one additional type space.

2. In a machine of the class described, the combination of an accumulator including accumulator wheels adapted to register a positive balance in its true form, and a negative balance in its complementary form; actuating racks for said accumulator wheels; type carriers operatively connected to said actuating racks and springurged to advance independently'of said racks; two separate sets of type elements of opposite numerical progression mounted on each of said type carriers; three means for arresting the independent advance of said type carriers, one of said means acting to hold said type carriers in such position relative to said racks as to place in printing position the sets of type elements representing the numerical positions of the racks, the second of said means acting to arrest said type carriers in such positions relative to said racks as to place in printing position the set of type elements representing the ten complements of the numerical positions of the racksyand the third said means acting to arrest said type carriers in positions to print the nine complements of the numerical positions of the racks; means for disabling said first arresting means; mechanism for causing a total-taking operation during which operation said actuating racks reset said accumulator wheels to zero; means controlled jointly by said accumulator and said mechanism and efiective when a total is taken with a negative balance in said accumulator for conditioning said disabling means for operation; a separate disabling means for said second arresting means; and means controlled by the lowest order rack which advances to reset its associated accumulator wheel during a negative total-taking operation for conditioning said separate disablingmeans for eperation.

3. In a machine of the class described, the combination of an accumulator, actuating racks therefor advanceable dilferentially to numerical positions, type carriers operatively connected to said actuating racks and spring-urged to advance independently of said racks, two separate sets of.

latching devices whereby said type carriers are permitted to advance independently of said racks and move said normally effective set of elements

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