US2371914A - Accounting machine - Google Patents

Description

March 20, 1945. H. RAUH fXCCOUNTING MACHINE Filed Dec. 8, 1939 4 Sheets-Sheet l /n ventor: 7'. fed @4? 2 91am March 20, 1945.

H. RAUH ACCOUNTING MACHINE 4 SheetSheet 2 Filed Dec. 8, 1939 March 20, 1945. RAUH 2,371,914

I ACCOUNTING MACHINE Filed Dec. 8, 1939 4 SheetsSheet 3 //7 vemor:

March 20, 1945.

H. RAUH 2,371,914

ACCOUNTING MACHINE Filed Dec; 8, 1939 4 Sheets-Sheet 4 Patented Mar. 20, 1945 ACCOUNTING MACHINE Hermann Rauh, Berlin-Zehlendori', Germany; vested in the Alien Property Custodian Application December 8, 1939, Serial No. 308,2 60 In Germany January 1'7, 1939 13 Claims.

The machine according to the invention belong to the class of accounting machines with a balance mechanism for positive and negative totals and with accumulating mechanisms whose adjustment takes place on tabulation.

It has already been proposed, to coordinate to the individual columns two accumulating mechanisms for plusand minus amounts respectively, especially to the balance column. In this known construction the accumulating mechanism for plusor the accumulating mechanism for minus line totals is actuated under control of the subtraction control of the balance mechanism. This requires especial attention or the arrangement of a separate control of the balance mechanism in such a manner that upon the operation of the fugitive one transfer mechanism to insert a "fugitive one upon a change of sign from positive to negative, the total key is locked, so that the subtraction control element (minus balance lever) has first to be actuated in order to register a minus-total.

According to the present invention a new arrangement is proposed for the selection of the two co-ordinated accumulating mechanisms for positive and negative line-totals, which makes this selection absolutely independent of the manipulation and the attention of the operator and effects the selection positively in a correct manner.

This is attained according to the invention by placing the selection of either of the two accumulating mechanisms for positive and negative linetotals exclusively under the control of the fugitive one transfer mechanism of the balance mechanism. In the accounting machine according to the invention there are consequently provided:

a. A selecting device for the accumulating mechanisms so that to every column an accumulating mechanism is coordinated; to the linetotal column (balance column), however, two accumulating mechanisms are coordinated, one for positive and one for negative balances,

b. The subtraction control for the balance mechanism is adapted to be adjusted by the paper carriage or by hand,

0. An additional negative control is provided for the totalizer in the balance mechanism, this operation of the fugitive one transfer mechanism of the balance mechanism, in such a manner that each time the zero in negative direction has been passed, the second single counting mechanism coordinated to the balance column is automatically selected.

In order to carry out automatically these different operations under'the control of the fugitive one transfer mechanism, such mechanism is not, as usual, constructed so that the tens transfer is effected directly from the highest order of the balance mechanism to the unit order, but in a special manner so that the balance totalizer wheel of the highest order in passing through zero in either direction, merely conditions the transfer to the unit order, and the actual entry is carried out by releasing a pawl, which in turn liberates a separate spring operated mechanism. Thisspring operated mechanism, during the calculating operation trips a tens-transfer in the lowest order and controls the reversing of the balancesmechanism to subtraction and the selection of the accumulating mechanisms in the balance column. My arrangement relieves the fugitive one transfer mechanism of practically all of the work with which it was heretofore overloaded and provides 'sufilcient power for the rapid reversing of the balance mechanism and for the selection of the accumulating mechanisms.

In the accompanying drawings embodiments of the invention are illustrated by way of example.

Figs. 1 to 'I show the special means cooperating with the fugitive one transfer mechanism,

Figs. 8 to 10 show the reversing device for the balance mechanism and for selecting the accumulating mechanisms.

I. The means cooperating with the fugitive one transfer mechanism ential segments,

Fig. 3 shows a top plan view of Fig. 1, Fig. 4 shows in elevation the position of certain elements of Fig. 1 upon a negative entry by the fugitive one transfer mechanism,

Fig. shows in elevation certain of the same elements upon a positive entry,

Fig. 6 shows a locking arrangement for the fugitive one transfer mechanism in the actual transfer position,

Fig. '7 shows the arrangement for returning the elements to normal position.

In Fig. 1 the toothed totalizer wheels of the balance mechanism are designated by i and these wheels are driven in additive direction by a gear 2, and in subtractive direction by gears 3 and i. The balancing mechanism is mounted in the balancing mechanism frame 5 and during the calculating operation it is brought into engagement with the differential segments 6 of the numeral key controlled mechanismby being shifted in downward direction. For subtraction purposes the calculating mechanism must also be axially displaced. On every toothed wheel I of the calculating mechanism a tens transfer disc 1 with a tens transfer projection 8 and a total stop 9 is mounted. Assume that the calculating mechanism is driven subtractively and that a tens transfer in the highest order is proceeding. The

tens transfer projection 8 will be turned clockwise in the direction of the arrow A from the zero position to strike in known manner against a projection I l of a tappet oscillatably mounted on a stationary pin it], near the free end of an upwardly projecting transfer lever the arms 1 2, i3 of this tappet bearing against offset ears (4 and i5, respectively, of the oscillatable tens-transfer lever I! mounted on a pivot l6 adjacent the wheel of highest order. The tens transfer lever i l is therefore rocked towards the left (compare for instance the position in Fig. 2) when the projection 8 wipes past the projection ii of the tappet in either direction. The tens transfer lever ii of the highest order of the balance mechanism carries a rearwardly projecting tripping arm I8 hingedly connected with it. As the balance mechanism, during the calculating operation, had been lowered from the position shown in Fi 1 into the position, Fig. 2, in which it engages with the segments 6 of the selecting mechanism, the rearwardly projecting tripping arm i 8, during the rocking movement of the lever 11 towards the left, enters the recess 19 of a locking pawl 22 controlled by a spring 21 and oscillatable about a pin 29. The tens transfer lever I 1 is further rigidly connected with a catch 23 having an offset lug 2 3 which, during the rearward rocking of the transfer lever ll, positions its offset lug 24 behind the shoulder 25 ofa keeper 21 oscillatably mounted on pin 26, so that this keeper 2! under the action of its spring 28 brings its shoulder 25 in front of the offset lug 24 of catch 23 and securely holds this catch together with the tens transfer lever I! in the position to which it has been moved towards the left (Fi 2).

The catch 27 retains the tens transfer lever I! in effective position, as the projection 8 on the wheel of highest order wipes past the projection H of the so-called star stop in rocking the tens transfer lever counter-clockwise.

However. as the totalizer carriage Z rises to disengagethe transmission gears 2 or 3 of the totalizers from their actuators 6, but after the locking pawl 22 .or 220. has been tripped, it I latched arm 23, whereupon the spring 29 withdraws the transfer lever and its tripping arm I8 to clear the upper end 30 of the locking pawl.

When the balance mechanism, after completion of the calculating operation, is again shifted away from the segments 6, the inclined face 29 of rearwardly projecting tripping arm l8, contacts an inclined face 39 of pawl 22, and pushes this pawl to the left. The pawl 22, the lower end of which is provided with a laterally extending toe 3| normally entered in a notch 32 formed in the forwardly extending arm of a driving lever 34 oscillatable about an axle 33, now liberates this lever 34. This driving lever is oscillated from the position shown in Fig. 1 into the position shown in Fig. 4 by the action of a preliminarily tensioned spring 35. A projection 36 of the driving lever 34 presses against the adjacent edge 31 of an intermediate lever 39 fast on a horizontal shaft 38 journaled in the side plates (Fig. 3), to rock the intermediate lever from the position shown in Fig. 1 into that shown in Fig. 4, the oscillating movements of the driving and intermediate levers being limited by a jaw 40 formed on the rear end of the intermediate lever 39 co-acting with a bolt M embraced by this jaw (Figs. 1 and 4).

A crank e2 is fast on the pivot shaft 38 with the intermediate lever 39, and carries a pin 43 connected by a link 56 (Fig. 8) to a similar pin on a crank 58 fast on the fugitive one control shaft 51, which shaft effects 3 1.. The tens transfer in the balance mechanism from the highest order to the lowest order and 2. The alternation of the positive and negative total accumulating mechanisms in the totals column.

In order to yieldingly retain the parts in the positions illustrated in Fig. 4 corresponding to a negative entry, a latch G4 fast on the shaft 38 and having a wedge shaped end 45 is provided which, in the position shown in Fig. 6 and corresponding to the negative entry, bears with its face 45' against a laterally projecting stud 46 of a detent 49 oscillatable about the- axle 33 and 7 held by a spring 48 in the locking position.

When the balance mechanism effects a positive entry of the fugitive one transfer mechanism, a corresponding reverse rotation of the fugitive one control shaft 51 occurs. To produce this, a second set of elements 22a and 34a is provided alongside the elements 22 and 36, the locking pawl 22a being spaced apart relative to the locking pawl 22 by a distance equal to the axial movement of the balance mechanism from additive to subtractive adjustment, that is, when it is desired to shift the positive gears 2 of the totalizer out of alinement with the actuating racks 6 and bring the negative gear trains 3, 4 in line there-' 36a upon the operation of the fugitive one transfer mechanism when the sign of the accumulated total shifts from negative to positive, is illustrated in Fig. 5. The driving lever 34a is shown in its operated position. A link 5| is pivoted at 53 to the driving lever 34a and a pin 53 projecting from the intermediate lever 33 engages in a slot 52 of said link. In the normal position (Fig. 1) the pin 53 is at the right hand end of slot 52. If the fugitive one entry is negative, the intermediate lever 33 as it is rocked by the negative driving lever 34 shifts pin 53 to the left end of slot 52 where it remains until the signpf the total accumulated again changes. If then a positive entry takes place, the positive driving lever 34ain rocking counter-clockwise. draws the bar to the right, causing the left hand end wallof the slot 52 in contact with the pin 53 on the intermediate lever 33 to rock the intermediate lever counter-clockwise (instead of clockwise, as when actuated by the negative driving lever 34) from the position shown in Fig. .4 into the position shown in Fig. 5. Thereupon a locking of the parts takes place again, the latch 44 bearing with its wedge-shaped end from the other side against the stud 46 of detent 43 (Fig. 6).

The tripped driving lever 34 or 34a, as the case may be, is restored to normal position at the beginning of an incident to, the next following operation of the machine as follows:

A restoring shaft 54b (Figs. 1, 3 and '7) journaled in and extending between the frame side plates is oscillated at each machine operation by a bar 54 connected to a crank 54a fast on the restoring shaft, and driven in any suitable manner from the main shaft of the machine.

A pair of parallel restoring arms and 55a are fast on the restoring shaft 54 and extend upwardly beneath laterally projecting pins on the respective driving levers 34, 34a, to rock counterclockwise from their positions shown in Fig. l with the restoring shaft 54b and return the tripped driving lever 34 or 34:: clockwise a little past its normal position until the locking pawl 22 or 22a can clear the point of the driving lever, whereupon the pawl spring 2l or 2|a rocks the pawl into locking relation with its driving lever 34 or 34a, to hold its driving lever in cocked position when the restoring arm 55 or 55a returns to its idle position.

The driving lever springs 35 or 35a are tensioned by the driving levers on -their return to with the change of sign in a positive or negative direction. However, there are also cases of tens transfer in the highest order when the positive or negative calculating capacity of the totalizer constituting the balance mechanism is exceeded. In this case the fugitive one transfer mechanism should not function. This result is attained according to the invention by providing for positive calculations a pair of members 22 and 34 and for negative calculations a further pair of members 22a and 34a, which determine the .positive or negative direction of rotation of the shaft 33. Thus, if a plurality of additions take place in the negative direction, that is, if the calculating capacity in the negative direction is exceeded several times, members 22 and 34 are always actuated a plurality of times, so that the pin 35 always'tends to turn the intermediate lever 33 in the clockwise direction. However, the lever 33 has already been turned once to the right upon the negative passage of the zero (that is, as the tens transfer projection 3 wipes past the projection ii of the tappet during its first rotation in a negative direction), and another rotation to the right is not possible because the shaft 33 is held in the negative position by the wedge-shaped latch 45, stud 43 and spring-pressed detent 48. The same operations also occur in the reverse direction during ositiveactuation, by the members 22a and 34a. In this operation, the intermediate lever 43 and the shaft 38 are turned to the left through link 5| and are held by the springpressed detent 43 in the positively adjusted position until an opposite actuation is effected through the members 22 and 34, i. e. when zero is exceeded in' the positive direction.

Otherwise stated, let it be assumed that, at the beginning of anoperation, both triangular driving levers 34 and 34a are in their cocked or potentially operable positions, held in such positions by their respective latches 22, 22a and that the forked intermediate lever 33 acted upon by the respective driving levers 34, 34a, is at the limit of its counter-clockwise travel, as shown in Fig. 1. Furthermore, the balance or grand totalizer Z, is in its additive position, that is, its adding gear wheels 3 are in line with the differential adding racks 3, in which adjustment the trip finger 23 of the balance or grand totalizer is in line with the locking member 2211, and the slotted link 5| connecting the associated driving lever 34a with the intermediate lever 33 common to both driving levers 34, 34a, is in its advanced position, shown in Fig. l.

With the foregoing elements in their normal positions as set forth, let it be assumed that the addition of an amount to such amount as may have been previously added and standing on the totalizer wheels I is sufficient to exceed the capacity of the totalizer.

In such event, the tens-transfer projection 8 on the totalizer wheel I of highest order will rotate, in an additive direction (counter-clockwise in Fig. 1) past projecting arm H of the tappet, and

rock counter-clockwise the tens-transfer lever l1 to the left of the highest order wheel with its trip finger l8, whereupon the tens-transfer lever is locked in its tripped position by the catch 21.

Upon the disengagement of the totalizer driving gears 3 from the differential racks 6, the beveled free end 23 of the trip finger l3 displaces the latch 22a to release the driving lever 34a for operation by its spring 35a, which rocks its driving lever counter-clockwise. The driving lever 34:: as it rocks, draws with it the link 5|, but such motion is idle as the link advances relatively to the stud 53 of the intermediate lever 33, and as such intermediate lever is already at the limit of its counter-clockwise travel no motion is transmitted to the intermediate lever and its fugitive one control mechanism, and restoring arm 55a returns the driving lever 34a to its cocked position on the ensuing operation of the machine.

The tripped tens-transfer lever i1 is restored as the totalizer is raised to its fully disengaged position.

Similarly, in the event, that a number of items amounting to a sum exceeding the capacity of the totalizer are to be successively subtracted from the totalizer, the machine is conditioned for such subtractions by shifting the grand or balance totalizer axially to position the reversing train of gears 3, 4 in line with the differential adding racks 6, which positions the trip finger l8 opposite the locking pawl 22 for the driving lever 34, as shown in Fig. 1.

Upon the first subtracting operation, which exceeds the capacity of the machine in negative direction, the trip finger l8 displaces the locking pawl 22, and the driving lever 34 rocks counterclockwise under the tension of its spring 35. The stud 36 of the driving lever, in turn rocks the intermediate lever 39 to the position shown in Fig. 4, thereby efiectingthe operation of the fugitive mechanism, and the latch member 43 (Fig.

- 6) frictionally retains the intermediate lever 39 in its rocked position, even after the restoring arm 55 has returned the driving lever 34 to its normal cocked position.

Immediately succeeding subtractive operations will effect operations of the tens transfer lever l1 and trip finger l8 controlled by the ttalizer wheel of highest order, and the trip finger will release the restored driving lever .34 for operation, but such operation will be idle as the intermediate lever 39 is already at the limit of its clockwise travel.

Hence, in either event, no excess of fugitive ones are ever entered on the totalizer.

Assuming the totalizer to have a negative amount registered thereon, in which event, the intermediate lever 39 will be at its extreme clockwise limit of travel, shown in Fig. 4, and that an amount greater than the negative amount registered, is to be entered additively on the totalwar.

The totalizer is first positioned with the direct adding gears 2 in line with the differential racks 6.

Upon the entry of the amount additively, the totalizer wheel of highest order will be rotated counter-clockwise, to zero during which rotation the tens-transfer lever l1 and its tripping finger l8 are rocked rearwardly (counter-clockwise, Fig. 1) displacing the locking pawl 22a and releasing the driving lever 34a to the action of its spring 35a.

The driving lever 34a in rocking counter-clockwise draws the link to the right (Fig. 4), and since the pin 53 of the intermediate lever 39 is at the rear end of the slot 52 of the link, the intermediate lever is rocked counter-clockwise back to its normal position, actuating the fugitive one mechanism on such return.

II. The carrying out of the tens transfer from the highest order to the unit order As can be seen from Figs. 1 and 8, an arm 58 fixed on shaft 51 is oscillated by the crank 42 through the intermediary of the link 56, and thereby the shaft 51 is rotated. This shaft extends through the machine from the highest order to the lowest order and effects, by an element (not shown) arranged onits opposite end, the transfer of the fugitive one" into the unit order.

III. The change of the accumulating mechanism in the balance column In Fig. 8, the mechanism for conditioning the machine for taking a positive or a negative total under control of the fugitive one mechanism and upon depression of a total key is shown in its initial position, i

Fig. 9 shows the mechanism in the position after the negative operation of-the fugitive one transfer mechanism and after actuation of the total key, and

Fig. 10 shows the position assumed by certain of the elements during the operation of the main termediate lever 39 of the "fugitive one control mechanism, the fugitive one control shaft 5'! will be rocked in one directiornorthe other.

The parts are shown in Fig. 8 in their normal positions during the accumulation of a positive total.

Upon a change of sign indicating a negative total, the "fugitive one" control shaft is rocked counter-clockwise and through the crank 59, shifts the bar 60 in the direction of the arrow in Fig. 8. An abutment face 63 of bar 66 in its initial position bears against a pin 64 of a shouldered pawl 65 pivoted connected at T0 to an arm 66 of a bell crank lever 68, 68a oscillatable about a pin 61. The pawl 65 which, under the action of a spring 69, tends to swing counter-clockwise, is restrained from so doing as the pin 64 bears against the abutment face 63. This pawl is further restrained by a pin H carried by the pawl, which bears against the rear edge of an arm 13 fast on a suitably journaled shaft 12. If the jawbar 60 is shifted towards the right, its abutment face 63 liberates the pin 64, so that pawl 65 could rock counter-clockwise were it not for the contact of its pin ll against-the arm 73. At each operation of the fugitive one transfer mechanism this release of pawl 65 by the abutment face 63 takes place. However, the pawl is still locked by the pin II which bears against the arm 13.

If then a bar 14 is shifted by the total key T or by the subtotal key St, it actuates a bar 15 rearwardly to rock a lever 11 oscillatable about apin 16, one arm of which lever H by means of a rod 18, rocks a crank l9 on the shaft 12 and thereby rocks the arresting arm 13 to the right in the direction of the arrow. At this moment, after the fugitive one entry has been completed and the total or subtotal key actuated, the pawl 65 is liberated and rocks towards the right under the action of spring 63, so that its shouldered face en a es over an extension 8| of a connecting rod 83 oscillatable about pin 82. The pawl 65, is thus coupled with the connecting rod 83. This rod or its roller 85 is lifted, during the calculating operation by a cam 84 oscillated at each machine operation, and thereby lifts the pawl 65 and with it the arm 66 of the bell crank lever 68, 66a.

The arm 68 of the bell crank lever 68, 68a shifts the bar 88 towards the right and through lever 89 and 89a, raises a bar 90, by which the change element 9| is actuated for the changing over from the accumulating mechanism for the positive amounts to the accumulating mechanism for the negative amounts.

The upper arm of element 9| shifts the pusher to the left and the,lower arm allows the pusher shown in dotted lines to be moved to the right by its spring (not shown). During this procedure, the drum moves one step So that the accumulator mechanism (not shown) for the negative balance is in engaged position. Normally, however, the positive accumulator mechanism (not shown) is always in engaged position.

IV. The reversing of the balance mechanism from addition to subtraction under control .0] the fugitive one transfer mechanism The axial shift of the balance mechanism from addition to subtraction or inversely is effected by the same angle lever 68, 68a (Fig. 8) under the control of the fugitive one transfer mechanism. When the angle lever 68, 68a (compare Section III) the wedge face 86 of arm 68a is rocked by the cam 84 subsequently to the depression of a total key, of the angle lever 68 crowds the reversing lever 81 of the balancing mechanism counter-clockwise (Fig. 8a) to shift the balancing mechanism Z from the positive into the negative position (compare also Figs. 8a and 10).

I claim:

1. In a calculating machine, the combination wth a set of denominational actuators; a set of totalizer wheels shiftable in a direction transverse to the axis of rotation of the wheels, to

engage with and disengage from the actuators; and means to effect rotation of the totalizer wheels in either direction; of a fugitive one control mechanism including a control shaft; spring-driven means to actuate the shaft in one direction; means to lock the spring-driven means in cocked position; normally idle trip means mounted to partake of the motion of the totalizer wheels into and out of engagement with the actuators, and shiftable by the totalizer wheel of highest order to effective position only during engagement of the totalizer wheels and actua-' tors; and means to retain the trip means, when conditioned for operation, in its effective position, to displace said locking means and release the spring-driven means for operation incident to and as a result of the disengagement of the totalizer wheels from their actuators.

2. In a calculating machine, the combination with a set of denominational actuators; a set of totalizer wheels shiftable in a direction transverse to the axis of rotation of the wheels, to engage with and disengage from the actuators; and separate transmission means to effect rotation of the totalizer wheels by the actuators, in either direction; of a fugitive one control mechanism, including a control shaft; a plurality of relatively independent spring-driven means to actuate said shaft in one direction or the other, respectively; a motion-transmitting member connected with the fugitive one control shaft and operable in opposite directions by either springdriven means, to rotate the control shaft in either direction accordingly; means independent of each other to lock the respective spring-driven actuating means in their cocked positions; a single normally idle trip means mounted to shift with the totalizer wheels as they engage with and disengage from their actuators; said set of totalizer wheels being axially shiftable to position one or the other of said separate transmission means in line with the actuators and to position the normally idle trip means in effective position relatively to the corresponding locking means; and means operable by the totalizer wheel of highest order to shift said trip means from its idle position to a position wherein it will displace the selected locking means during the return of the totalizer wheels to their disengaged position, to

free the associated spring-driven means for operation.

3. In a calculating machine, the combination with a set of denominational actuators; a totalizer frame shlftable towards and from the actuators;

shaft;

a set of totalizer wheels mounted in the frame to shift therewith into and out of engagement with their actuators; and means to rotate the totalizer wheels in either direction, for addition or direct subtraction; of a fugitive one control mechanism, including a control shaft; spring-driven means to actuate the shaft in one direction; means to lock the spring-driven means in cocked position; normally idle trip means under control of the totalizer wheel of highest order, and mounted to shift with the totalizer frame to trip the locking means during the movement of the totalizer frame away from the actuators; latch means to retain the trip means in its effective position after said trip means has been set by the wheel of highest denomination; and means engaged by the latch means during such return of the totalizer frame to normal position, to cause the latch to release the trip means for return to ineffective position.

4. In a calculating machine, the combination with a set of denominational actuators; a totalizer frame shiftable towards and from the actuators; a set of totalizer wheels mounted in the frame to shift therewith into and out of engagement with their actuators; and means to rotate the totalizer. wheels in either direction for addition and direct subtraction, respectively; of a fugitive one control mechanism, including a control shaft; relatively independent spring-driven means to actuate said shaft in one direction or the other; relatively independent means to lock the respective spring-driven means in their cocked positions; at single normally ineffective trip means mounted to shift with the totalizer frame relatively to the locking means; and means controlled by the totalizer wheel of highest order to set the trip means to effective position relatively to either locking means, to trip the selected locking means under control of the totalizer frame as it dlsengages the totalizer wheels from their actuators.

5. In a calculating machine, the combination with a set of denominational actuators; a totalizer frame shiftable towards and from the actuators; a set of totalizer wheels mounted in the frame to shift therewith into and out of engagement with their actuators; and means to rotate the totalizer wheels in either direction for addition and direct subtraction, respectively; of a fugitive one control mechanism, including a. control relatively independent spring-driven means to actuate said shaft in one direction or the other; relatively independent means to lock the respective spring-driven means in their cocked positions; a single normally ineffective trip means mounted to shift with the totalizer frame relatively to the locking means; and means,

controlled by the totalizer wheel of highest order to set the trip means to effective position relatively to either locking means, to trip the selected locking means under control of the totalizer frame as it disengages the totalizer wheels from their actuators; means mounted to travel with the totalizer frame to retain the pawl-tripping means effective during the first stage of movement of the totalizer frame away from the actuators; and means contacted by the retaining means subsequently to the tripping of the locking pawl, to cause the retaining means to release the trip fileans for return to its normal ineffective posi- 6. In a calculating machine, the combination with a single set of denominational actuators; a totalizer frame shiftable towards and from the actuators; a set of totalizer wheels mounted in the frame to shift therewith into and out of engagement with their actuators; and means to rotate the totalizer wheels in either direction to eifect addition and subtraction, respectively; of a fugitive one control mechanism, including a control shaft; a single transmitting member in train with said shaft to rock the shaft; independently operable spring-driven means to actuate the single transmitting member and said shaft in one direction or the other; independently releasable means to lock the spring-driven shaft-actuating means in cocked position; and a single trip means adjustable to one or another position to release the selected locking means.

, 7. In a calculating machine, the combination with denominational actuators; a totalizer frame shiftable toward and from the actuators; denominational totalizer wheels mounted in the frame to shift therewith, into and out of engagement with the actuators; and means to effect addition and subtraction on the totalizer wheels; of a fugitive one control mechanism, including a control shaft; a sin le transmitting member in train with said shaft; a pair of independently operable spring driven means arranged to impart motion to the single transmitting member in opposite directions to turn said transmitting member and said shaft in one direction or the other; independently releasable means to lock the spring-driven shaft actuating means in cocked position; and normally ineffective trip means set to effective position by the totalizer wheel of highest denomination and operating to release the locking means incident to the disengagement of the totalizer wheels from their actuators.

8. In a calculating machine, the combination with denominational actuators; a totalizer frame 7 a connection between the remaining springdriven actuator and the transmitting member to enable said remaining spring-driven actuator to rock the transmitting member in the opposite direction; separate locking means for the respective spring-driven actuators to retain the actuators cocked; and a trip means shiftable axially with the totalizer and controlled by the totalizer wheel of highest denomination to release one or the other of the locking means depending upon its axial adjustment.

9. In a calculating machine, the combination with denominational actuators; of a totalizer frame shiftable towards and from the actuators in a direction transverse to its longitudinal axis, and also adjustable axially relatively to said actuators; denominational totalizer wheels mounted in the frame; adding and subtracting gears associated with each totalizer wheel and shiftable with the carriage towards and from the actuators into and out of engagement with the actuators, and axially with the carriage to select which of the gears shall co-act with the actuators; a fugitive one control mechanism, including a control shaft; independently operable spring-driven means to turn the control shaft in one direction or the other, respectivelyyindependently releasable means to lock the respective spring-driven means in cocked position; and normally inefiective trip means under the conjoint control of the totalizer wheel of highest order and of the totalizer frame in its transverse and axial movements, to select and release the locking means according to the sign of the accumulated total.

10. In a calculating machine, the combination with denominational actuators; and totalizer wheels engageable with and disengageable from the actuators; of a fugitive one control mechanism, including a control shaft; spring-driven means to rock said shaft; means to lock the spring-driven means in cocked position; normally ineffective means to trip the locking means; and

means under the control of the totalizer wheels of highest order to shift the tripvmeans to effective position, said trip means, when in effective position, being operable to trip the locking means incident to the disengagement of the totalizer wheels from their actuators.

11. In a calculating machine, the combination with denominational actuators; of totalizer wheels having adding and subtracting transmission gears engageable with and disengageable from the actuators; a totalizer frame in which the totalizer wheels are mounted, said frame being axially adjustable to select which set of gears shall engage with the actuators; a fugitive one ,control mechanism, including a control shaft; means under the conjoint control of the totalizer wheel of highest value, and of the totalizer frame to impart motion to the control shaft; a power-driven member; means to positively shift the totalizer frame in one direction; connections, including a shiftable coupling between the power driven member and the totalizer frame shifting means; a plurality of independently operable means to restrain the shiftable coupling in itsineffective position, one of which meansis controlled from the control shaft; and a manually operable key to control the other of said restraining means, displacement of both of which restraining means is a prerequisite to the automatic operation of the totalizer frame shifting means by the power-driven member.

12. In a calculating machine, the combination with denominational actuators; of totalizer wheels having adding and subtracting transmitting gears engageable with and disengageable from the actuators; a totalizer frame in which the totalizer Wheels are mounted, said frame being adjustable axially to select which set of gears shall engage with and disengage from the actuators; a fugitive one control mechanism, including a control shaft; spring-driven means to rock the control shaft; means to lock the springdriven means in cocked position; normally idle tripping means under the conjoint control of the totalizer wheel of highest order and of the totalizer carriage, to release said locking means; means to positively shift the totalizer frame axially in one direction, a power-driven member; a normally interrupted coupling between the power-driven member and the totalizer frame shifting means; a manually operable key; and separately operable means controlled by said key and said control shaft to enable the coupling to effectively connect the power-driven member and the totalizer frame shifting means upon the taking of a negative total.

13. In a calculating machine, the combination with denominational actuators; of totalizer wheels having adding and subtracting transmitting gears engageable with and disengageable from the actuators; a totalizer frame in which the totalizer wheels are mounted, said frame being adjustable axially to select which set of gears shall engage with and disengage from the actuators; a fugitive one control mechanism, including a control shaft; spring-driven means to rock the control shaft; means to lock the springdriven means in cocked position; normally idle tripping means under the conjoint control of the totalizer wheel of highest order and of the total-= izer carriage, to release said locking means; means operable to positively shift the totalizer frame axially in one direction; a power-driven member to render the last named means effective to shift said totalizer frame and to retain it in shifted position during a cycle of the machine; connecting means between the powerdriven member and the means for positively shifting the totalizer frame, including a shiftable coupling; means normally restraining the shiftable coupling in its inefiective position, and controlled by the control shaft to release the shiftable coupling at each change of total on the totalizer to the negative sign; additional means to retain the shiitable coupling ineffective; and manually operable means to release such additional restraining means.

HERMANN RAUH.

Certificate of Correction Patent No. 2,371,914. March 20, 1945.

HERMANN RAUH It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows:

Page 3, second column, line 13, for lever 49 read lever 39;

and that the said Letters Patent should be read with this correction therein that the same may conform to the record of the case in the Patent Oifice.

Signed and sealed this 15th day of February, A. D. 1949.

THOMAS F. MURPHY,

Assistant Commissioner of Patents.

Certificate of Correction Patent No. 2,371,914. March 20, 1945.

HERMANN RAUH It is hereby certified that error appears in the printed specification of the above numbered patent requiring correctlon as follows:

Page 3, second column, line 13, for lever 49 read lever 39;

and that the said Letters Patent should be read with this correction therein that the same, may conform to the record of the case in the Patent Office.

Signed and sealed this 15th day of February, A. D. 1949.

THOMAS F. MURPHY,

Assistant G'ommz'ssioner of Patents.

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