US2274049A - Calculating machine - Google Patents

Description

Feb. 24, 1942.

E. H. DREHER CALCULATING momma Filed Feb. 12, 1937 5 Sheets-Sheet 1 INVENTOR E. H. DRE HER fid- HIS AT RN EY .Feb. 24, 1942. E. H. DREHER CALCULATING MACHINE 5 Sheets-Sheet 2 Filed Feb. 12, 1937.

lNVENTOR E LM ER H. DREHER 24, 1942- E. H. DREHER CALCULATING MACHINE Filed Feb. 12, 1937 5 Sheets-Sheet 3 INVENTOR ELMERHDREHER v HIS AT ORNEY Feb. 24, 1942. E. H.'DREHER 2,274,049

CALCULATING MACHINE Filed Feb. 12, 1937 5 Sheets-Sheet 4 FIG. 5.

INVENTOR ELM ER H.DREHER HIS TTORNEY Feb. 24, 1942. E. H. DREHER 2,274,049

CALCULATING MACHINE Filed Feb. 12, 1937 5 Sheets-Sheet 5 FIG.8

FIG. 7

ENTOR ELM H. DREHER ATTORNE Patented Feb. 24, 1942 2,214,049 cawum'rmo MACHINE Elmer ll. Dreher, Bockville Centre, N. Y., assignor to Remington Rand Inc., Bailalo, N. Y., a corporation of Delaware Application February 12, 1937, Serial No. 125,375

zclaims.

This invention relates generally to the tens transfer mechanism for adding and like machines, and particularly to mechanism of this type which is adapted for use in an adding machine capable of direct subtraction wherein a negative total is printed in a form complementary to the true negative balance.

The mechanism of this invention is herein embodied in the well known Dalton adding machine and is a modification of the machine disclosed in the United States patent to Dysart No. 2,014,560 issued September 17, 1935. The machine of the above patent performs problems of addition and subtraction and has its calculating or accumulating mechanism located at the rear of the machine and supported by frame plates which lie outside the regular framework of the machine. It is necessary, therefore, that additional linkage and actuating racks be provided to transmit the motion of the type sectors to the accumulating wheels. Also, in the machine of the above patent, tens transfer mechanism is provided which is adapted to be tripped and .to effect a carry as a part of one machine operation but which is not reset until the latter part of the following operation. It is necessary, therefore, to insert a blank stroke between the last accumulating operation and a total stroke, during which blank stroke the tens transfer mechanism is reset and the machine conditioned for totaling.

The mechanism of the present invention comprises a single set of accumulating wheels located near the front of the machine and adapted to mesh with actuating racks integral with the type sectors. are controlled by a variable operating means which enables them to engage their actuators at diilerent points in the machine operation and are thus capable of two directions of rotation. When moving in one direction the wheels accumulate positively and when moving in the opposite direction accumulate negatively. Individual tens transfer mechanism is provided for each accumulating wheel and is adapted to -be tripped as the wheels pass zero while moving in either direction. The actual carry operation occurs after the wheels are withdrawn from their actuators and before the end of the same machine operation the trip transfer pawls are reset and latched. Therefore, the necessity for a blank stroke is eliminated and the machine is conditioned at all times to effect a total taking operation. If the accumulating wheels are over.

The accumulating wheels translated by the operator into the true negative total.

One object of this invention is to record items of either addition or subtraction in an adding machine and, at the same time, to enter these items into a series of accumulating wheels by engaging the wheels with a set of actuating racks on the respective return or forward stroke of the actuators.

Another object of this invention is to effect carry operations from wheel to wheel in a single set of accumulating wheels through the provision of a novel transfer mechanism which is adapted to be tripped each time the wheels pass zero in either direction.

Another object of this invention is to eliminate the necessity for a blank stroke between the last accumulating operation and a total taking operation by providing means whereby the tens transfer mechanism is tripped and reset during a single machine operation.

Other objects and structural details of the invention will be apparent from the following specification when read in connection with the accompanying drawings wherein:

Fig. 1- is a sectional elevation taken from the right hand side of the machine showing the subtraction key and portions of the accumulating and recording mechanism;

Fig. 2 is a detailed sectional elevation taken through the accumulating unit showing the ham-; mer release mechanism and the tens transfer mechanism;

Fig. 2A is a detailed view of certain of the transfer mechanism shown in Fig. 2;

Fig. 3 is a sectional elevation taken from the left hand side of the machine showing the means for restraining the type sectors, the accumulator timing mechanism and part of the subtraction mechanism;

Fig. 4 is a fragmentary detail sectional elevation taken from the left hand side of the machine showing the accumulator timing mechanism and the means for initiating a total taking operation;

Fig. 5 is a view in side elevation of the left hand side of the accumulating unit;

Fig. 6 is a view similar to Fig. 5 showing the opposite side of theaccumulating unit Fig. 7 is an enlarged fragmentary detail elevational view of the cam plate and the cam slide with'said slide in the position assumed after operation of the total or subtract key; and

Fig. 8 is an enlarged fragmentary detail elevational view of the accumulator engaging and disengaging mechanism in the position assumed at the end of the forward stroke of the machine during total or subtract cycles.

The main features and general operating functions of the Dalton machine have been the subject of numerous patent grants and for this reason, and because of the wide commercial use of this type of machine, have become well known in the calculating machine art. The previously mentioned patent to Dysart No. 2,014,560, may be referred to as an example of standard Dalton construction combined with novel computing mechanism. Q

In the following description the terms front and rear or forward and rearward, as relating respectively to the front and rear portions of the machine, ar freely used to indicate the relative position or motion of the various parts.

According to the usual Dalton construction, and as disclosed herein, there is provided, at the front of the machine, ten numeral keys I (Fig. 1) each integral with an associated key lever 2. The key levers 2 are pivoted in any suitable manner near their mid points and extend toward the rear of the machine, each having a lug or upwardly extending projection 3 at its rear end. The projections 3 are positioned as to form a single horizontal line directly under a laterally movable stop carriage 4. The carriage 4 is guided upon rails 5 and moves in a series of step like motions cross ways through the machine. Supported in the carriage is a plurality of rows of vertically movable pins 6 which, in response to the movement of the carriage 4, are positioned one row at a time over the projections 3. De-v pression of any numeral key i, therefore, results in the elevation of the corresponding stop pin 6. The stop carriage 4 is spring tensioned to travel step by step toward the left of the machine and any suitable escapement mechanism may be provided to limit such movement and properly adjust the carriage with respect to the projections 3. One type of escapement mechanism which may be used in this machine is shown in the patent to Hopkins No. 1,039,130 issued September 24, 1912.

Pivotally supported on a shaft 1 (Figs. 1 and 3) in the upper section of themachine is a series of type sectors 8 of generally arc like construction and with a rearwardly extending portion 9. Springs ii, attached to the portion 9 tend to swing the sectors 8 upwardly and forwardly about their pivot I. Secured to each sector 8, in the manner shown in Fig. 3, is an accumulating sector [2 bearing the usual gear teeth along its lower edge and formedwith a downwardly extending arm i3 carrying a lug or heel l4 at its lower end (Figs. 1, 3 and 4). The heel l4 lies above the stop carriage 4 and is normally retained just behind the rear edge of a plate l5 pivoted to the frame of the carriage. The gear teeth on the accumulator sectors [2 mesh with the accumulating wheels or pinions i6 in a manner and at a time later to be described.

The type sectors 3 and their associated accumulator sectors l2 are normally prevented from forward movement by reason of a bail rod H which rests under the rear extensions 3 of the type sectors. The bail i1 is supported between a pair of arms l8 (see Fig. 1) fast to the shaft 1, and is adapted to be moved downward in response to movement of the main operating shaft is. With each cross step of the carriage 4 the plate I! is moved out of the path of a sector i2 (beginning with the extreme right hand sector), so that in those denominational columns in which stop pins 6 have been raised the sector i2 and its associated type sector 3 is free to move forward until stopped by contact of the accumulating sector heel l4 with the raised. pin 6. Part of the linkage necessary to rock the shaft 1 is shown in Fig. 1 and comprises a slotted cam member 2|, fast to the shaft 1, a roller 22, an arm 23 supporting the roller 22 and fast to a collar on the right hand side frame of the machine, and a link 24 pivotally' connected to the upper end of the arm 23. The link 24 is connected, at its other end, to the main shaft in a manner not herein shown. The shaft 13, as before mentioned, is the main operating shaft of the machine and is adapted to be moved in a reciprocal rocking motion either manually, by an operating handle secured to the shaft, or automatically by a motor. In order that superfluous wordage may be eliminated from this description we will assume that an operating handle is fixed to the shaft. The handle is normally in an approximate upright position and is capable of forward and return strokes imparting, of course, a like movement to the shaft l3. Forward motion of the shaft [9, will, therefore, cause a corresponding pulling movement of the link 24 to rock the arm 23 and by reason of the cooperation between roller 22 and cam plate 2| serve to rock said cam plate and the shaft 1 in a clockwise direction as shown in Fig. i. As the bail II is rocked with the shaft 1 all of the sectors 3 which have been released bythe cross movement of the carriage 4 will move forward to their respective printing positions under tension of springs H.

The printing mechanism of the present machine is also of the usual construction and is d sclosed in the patent to H. Landsiedel No. 1,395,121 issued October 25, 1921. A portion of the hammer release mechanism is shown herein in Fig. 2. Integral with each type sector 3 is a short arm 25 bearing a stud 28 at its forward end. When the sectors are in normal position and stud 28 contacts the rear extension of a latch 21 and holds it depressed against the tension of a spring 23. The latch 21 is pivoted at 29 and is formed with a nose 3! adapted to engage the printing hammer 32 and hold it in retracted position against the tension of a spring 33. The hammers 32 related to the raised type sectors 3 are released at the beginning of the return stroke of the main shaft 19 by means of a bail 34 which lies above all of the latches 21 and which receives its actuation at the proper time from a cam, not shown herein, on the main shaft.

The hammers 32 operate to drive the type lugs 32A carried by the sectors 3 to effect printing in the usual manner.

The mechanism, briefly described above, for setting up and recording numbers in accordance with the depression of certain numeral keys is believed to be well established both as to principle and practice so that further description herein is deemed unnecessary.

The accumulating mechanism of the invention comprises a single set of ten toothed gear wheels or pinions i6 individually mounted and spaced on a shaft 35 supported between a pair of arms 39 loosely pivoted to the shaft 31 (Fig. 2). The shaft 31 is supported between a pair of fixed frame members 49 connected by tie rods 99 and various cross shafts. The arms 39 extend forward a short distance beyond the shaft 31 and are rigidly connected by a rod 99 supported between their ends. A spring (not. shown) extendwith the extent of movement of their respec-" tive actuating sectors l2 and at the end of the return stroke are withdrawn from engagement and again assume their normal position. A total operation entails areversal of the above procedure, that is, the gear wheels l9 are moved into engagement with the accumulating sectors I2 at the beginning of the forward stroke and remain in mesh until they have cleared by reaching zero. The wheels are withdrawn at the beginning of the return stroke.

The accumulator shifting mechanism is shown herein in Figs. 3, 4, 5. 7 and 8. Secured to the main shaft l9 (Fig. 4) at the left hand side of the machine is a bail shaped bell crank lever formed with an operating arm 29, the free end of which arm is adapted to contact a roller 39 on one arm of a bell crank 39. The bell crank 39 is pivoted at 4| to the lower portion of a cam plate 42 fast to the shaft 43. Another arm on the bell crank 39 extends upward and bears against the shaft 43. A spring 44, connected at one end to the last mentioned arm of bell crank 39 and at its other end to a stud on the upper portion of the cam plate 42, tends to hold the member 39 in normal position, that is, with one arm bearing against the shaft 49 and with the other arm in a position where its roller 39 may be contacted by the arm 29 on the main shaft. As the arm 20 is rocked upwardly on the forward stroke of the operating handle it bears against the lower face of the roller 39 and by reason of the pivoted connection 4| cams the bell crank counter clockwise out of its path. As the arm 29 continues its upward movement the member 39 is released and immediately returned to normal by its spring 44. At the beginning of the return stroke the arm 29 engages the upper face of the roller 99 and as it continues its return movement forces the bell crank 39, the associated cam plate 42 and the shaft 49 in a clockwise direction, as shown in Fig. 4. As shown in Figs. 4 and 5, the cam plate 42 is formed at its upper end with a hook like portion 45 adapted to engage loosely a roller 49 on an arm 41. The roller 49 is situated approximately midway along the arm 41. The lower end of arm 41 is slotted and fits loosely about the shaft 43 (Fig. while the upper end of the same arm is secured to the shaft 35 which supports the accumulating wheels l9. As the plate 42 is turned clockwise at the start of the return stroke the roller 49 rides out of the recess in which it normally lies and up onto the inclined portion 49 of the cam plate. The upward motion thus imparted to the shaft 35 raises the wheels to into mesh with the actuators I2 as they start their return stroke, each wheel receiving a registration determined by the distance required for their respective actuators to return to normal. The wheels I. are shifted from engagement with their actuators at the end of the return stroke by the following means. Referring now to Fig. 4, an arm 49, also fast to the shaft l9. carriesastud 5| extending through an elongated slot 92 in one end of a link 59. The opposite end of the link 93 ispivoted-at 93A to the cam plate 42. As the arm 49 rotates with the shaft I 9 on the forward stroke of the shaft the stud 5| on the arm slides inei'l'ectively in the slot 92 and reaches its farthest forward position without effecting a change of position of the plate 42. At the start of the return stroke the cam plate 42 is shifted clockwise, as we have seen.

thus moving the link 53 far enough toward the It is evident that counter clockwise movement (Fig. 4) of the plate 42 will cause the hook 49 to again engage the roller 49 and that the roller will move off of the rise 49 and the wheels II will move out of engagement with the sectors l2 and return to rest position.

The accumulating mechanism will function in the above manner on each adding operation of the machine. The wheels I9 will be turned in a counter clockwise direction as shown in Fig. 4 a number of tooth spaces corresponding to the amount of movement permitted their respective sectors 9 and I2 so that a complete listing and accumulating operation will take place during one forward and return stroke of the main shaft I9.

Non add mechanism At some point in the operation of the machine it may be desired to list one or more numbers without entering the number or numbers into the accumulating wheels. Mechanism is provided for this purpose including a key 54 located at the front of the machine and bearing the inscription Non add (see Fig. 4)

Integral with the key 54 is a lever 55 extending upwardly and rearwardly in the machine and having a slot or cut out portion 59 in its rear edge. The slot 59 fits loosely about a shaft 51 supported between the side frames of the machine. Connected to the upper end of the key lever 55 is a link 59 extending toward the rear of the machine and connected at its other end to one arm 59 of a bail shaped bell crank loosely mounted on the frame supported shaft 9!. The other arm 62 of the bell crank is connected to the top of a T-shaped link 63 which is connected at its lower end to an arm 94 of another bail shaped bell crank loosely mounted on th shaft 95 likewise supported between the side frames of the machine. The other arm 99 of the last mentioned bell crank is adapted to cooperate with a tall or toe piece 91 integral with the member 39. In tracing the operation of the above linkage it will be seen that depression of the key 54 will rock the lever 55 clockwise about its pivot 51 and pull the link 59 forward to turn the bail shaped 7 member 39 in an opposite or counter clockwise direction about its pivot 4|. The resulting elevation of roller 39 carries it out of the path of arm 29 on both the forward and return strokes of the arm. The cam plate 88 is not rocked, the roller 88 remains in engagement with the hook 88 and the wheels i8 stay in their normal or rest position during the full operation. It is apparent that the non-add mechanism is eifective only so long as the key 88 remains depressed. Any suitable locking means may be employed to hold the key in operative position during several machine operations, or, if desired, it may simply be held down manually.

Subtraction mechanism In addition to performing the usual adding operations disclosed above, the machine shown in the present invention is also capable of exe-,

cuting direct subtraction operations from the same set of accumulating wheels. When it is desired to enter a number subtractively into the accumulating wheels IS. a subtraction key 88 (see Fig. 1) located at the front of the machine, is first depressed. The number is then set "up in the usual manner by depressing the numeral keys I and the main shaft I8 is rocked by its operating handle to complete a listing and accumulating operation.

As shown in Fig. ithe subtraction key 88 bears a latch 88 pivoted at H to the right hand side of the key. While the key 88 is held depressed, the latch 88 may be moved counter clockwise about its pivot Ii thus permitting the hook-like lower end of latch 88 to engage the fixed stud I8. A spring pressed detent i8 cooperates with the latch 88 in the manner shown to hold it in either of its two positions. The above latching means is adapted to use principally for the purpose of retaining the subtract key in operative position during a series of successive subtracting operations. A key control lock such as that disclosed in the patent to H. Landsiedel No. 1,537,314 issued May 12. 1925, may be provided herein to hold the subtract key depressed during one machine operation, after which it is automatically released.

A key lever 18 is integral with the subtraction key 88 and extends upwardly in the machine. A slot 18, formed in the rear edge of the lever 18 near its upper end, is passed about the shaft 81 which acts as a pivot for the key lever. A spring 18, tensioned between the upper end of the lever is and an arm 11 fast to a shaft 18, tends to hold the key 88 in its normal raised position. The lever 18 is formed at its upper end with a nose i8 bearing against the under side of a stud 8| on a lever 82 secured to one end of a shaft 88. It is evident that depression of the subtraction key 88 will rock the lever 18 counter-clockwise about its pivot 51 (Fig. 1) and that the resulting cooperation between the nose I8 and the stud 8| will cause the lever 88 and its shaft 88 to turn in a clockwise direction. A nose 18A of the lever 18A secured to the lever 18 engages the top of the stud 8| as shown in Fig. l. The stud 8|, therefore, rests in what is, in effect, a slot in the lever 18 so that when the key 88 is released the lever 88 will return to normal position. As shown in Figs. 3 and 4 a lever 88 is secured to the other end of the shaft 88 and is pivotally connected at its lower end to a link 88 extending toward the rear of the machine. A slot 88 is formed in the rear end of the link 88 and is adapted to engage a pin 81 on one arm 88 of a bail shaped bell crank pivoted at 88 to a stud on a fixed frame member. Another arm 8| of the bell crank extends rearwardly with its nose bearing upon the top of a roller 88 on the upper end of a slotted cam plate 88. The cam plate 88 is one member of a cooperating assembly comprising plate 88 and plates 88 and 88, the purpose of which is 'to 'rock the previously described cam plate 88 and bring about the engagement of the accumulating wheels II with the actuators l8 on their forward stroke. Both plates 88 and 88 are loosely mounted on the shaft 88. As shown in Figs. 4, 5, 7, and 8 the cam plate 88 lies flush against the plate 88 and has cut in its surface three slots 88, 8i, and 88. The slot 88 engages the shaft 88 and permits vertical sliding movement of the plate 88. The slot" engages a pin 88 on one end of the plate 88 while the slot 88 engages a similar pin III on one end of the plate 88. A spring I88 (Fig. 5) tensioned between the cam plate 88 and the lower end of plate 88 normally holds the latter in a raised position with the lower end of the slot 88 engaging a stud I88 on the bottom of the cam plate 88. Therefore, it will be seen, that counter clockwise movement of the shaft 88 (Fig. 4) will rotate the arm 8| counter clockwise through lever 88, link 88 and arm 88 to depress the plate 88 to the position shown in Fig. 7. Upon downward movement of the plate 88 it will be seen that the conformation of the slots 81 and 88 is such as to cause opposite motions of rotation of the plates 88 and 88. The arm 88 will move clockwise about its pivot 88 and the plate 88 will move in a counter clockwise direction. The plate 88 carries a pin I88 on its outer surface and a similar pin I88 is carried by the plate 88. The pins I88 and I88 are adapted to cooperate with a wipe pawl I88 which is raised and lowered on the respective forward and return strokes of'the main shaft i8. As shown in Fig. 4 the wipe pawl I88 is pivoted at I81 to an arm I88 secured to the main shaft. A spring I88 tends to rotate the pawl I88 counter clockw se about its pivot I81. An arm iii of the w.pe pawl normally rests on a stud H8 fixed to the bottom plate of the machine so that with the machine in rest position the pawl I88 is held in a generally erect position against the tension of the spring I88. In an ordinary adding cycle, the plates 88, 88 and 88 are retained in normal position. On the forward stroke of the machine the pawl I88 is moved upwardly carried by the arm I88 and under tension of the spring I88 is moved counter clockwise to pivot idly about the pins I88 and I88. As the arm I88 returns to normal the pawl I88 retraces its idle path about the pins I88 and I88 and is restored to the position shown in Fig. 4. During this operation, the wipe pawl does not alter the position of the plate assembly 88, 88 and 88. However, if the plate 88 is depressed as before described, through the operation of the subtraction key 88, or other means later to be described, the pin I88 on the plate 88 will be in a position where it may be engaged positively by a shoulder on the pawl I88 as the pawl rises on the forward stroke of the machine. mirther upward movement of the wipe pawl I88 will, therefore, cause the cam plate 88 and the plate assembly 88, 88 and 88 to turn as a unit in a clockwise direction to the positi n shown in Fig. 8 to place the rise 88 on the periphery of the cam 88 under the roller 88 and thus elevate the wheels i8 into engagement with the actuatin sectors l8 as the actuators and their type bars I begin their forward stroke. With the pin I88 thus displaced, continued upward movement of the pawl I 88 will cause it to pivot idly about the pins I88 and I88 to complete its forward movement. When the plate 88 has been thus moved from normal position, the pin I84 (Fig. 8) thereon is in a position wherein it may be positively engaged by the other shoulder on the pawl I84 at the beginning of the return stroke of the pawl to return the complete plate assembly to normal. As shown in Fig. 4, the spring pressed pivot member 38 carries a roller I13 which lies just under an inclined shoulder II3A an the slotted cam plate 83. The descending cam plate will, therefore, rock the member 38 counter-clockwise about its pivot H to raise the roller 38 and, as has been previously described, will render ineffective.

the arm 28.

Transfer mechanism It will be apparent from the description as thus far progressed that the accumulating pinions I8 will be turned in a clockwise direction,

as shown in Fig. 2 on adding strokes and in an opposite or counter clockwise direction on subtraction strokes. Certain novel transfer mechanism has been provided which is adapted to be tripped by the pinions I8 as they pass zero in either direction in order that a tens carry operation may be effected from one denominational order to the next higher order. The same mechanism is used in transferring additively or subtractively with the exception of certain additional linkage effective only on subtraction strokes and operated by the subtraction key in a manner later to be described. The transfer mechanism for each wheel I8 is identical, therefore a description of one will sufllce for all.

As shown in Figs. 2 and 2A, one tooth II4 on each of the accumulating wheels or pinions I8 is so formed as to beof approximately twice the width of the other teeth on the wheel. The portion of the tooth II4 which lies outside the plane tional order to the sector 'I 24 shown therein. The

accumulating wheel I8 and the transfer pawl II8 associated with the bell crank I34 have been omitted from the drawing for the sake of clearness. A spring II1 tensioned between a hook on the upper end of the bell crank I34 and an end plate of the frames I8 tends to hold the arm I38 in the position illustrated in Fig. 2. The cam slot I28 in the sector I24 is adapted to cooperate with a bail rod I38 in a manner and for a purpose soon to be described. The ball rod or shaft I38 common to all of-the gear sectors I24 is passed through the slot I28 and is supported at its ends by a pair of rock arms I38 pivoted to their respective frame plates 48. As shown in Fig. 5, the shaft I38 is connected at one end to the cam plate 42 by a link I and is connected at its other end through a link I48, to a lever I58 fixed to the shaft 43. At its lower end the lever I58 is formed with two notches I88 adapted to cooperate in the manner shown with a spring pressed arm I18 pivoted to the frame 48. The resilient detent thus provided by the cooperation between the members I58 and I18 acts to hold the shaft 43 and its operating cam plate 42 in either of their two positions.

The previously mentioned pawl H6 is formed with a depending arm I42 carrying a lug or projection I43 at its lower end. The projection I43 is adapted to engage a latch I44 pivoted at its upper end to a rod or shaft I45 fixedly mounted between the arms 38. A spring I46 tensioned between the arm I42 and the latch I44 tends to hold the two in contact but they normally c cupy the position in which they are shown in Fig. 2 since a shoulder on the pawl IIB abuts against the lower side of the shaft I45 and a tail I41 on the latch I44 is normally engaged by the shaft I38.

As shown in Fig. 4, a link I48 is pivotally connected at one end to the cam plate 42 and has a slot I49 cut in its surface near its other end. A pin II on the link I52 is passed through the slot I48 and acts as a guide for the link I48. The link I48 is formed with adownwardly extending arm I53 which has its lower end I54 bent in the between rear extensions of the arms 38 and, as

the accumulating wheels, is a spring' I23 adapted to retain the bail H8 in the position shown in Fig. 2.

A four toothed gear or carry sector I24 is normally in engagement with each wheel I6 and is pivotally mounted on a shaft I rigidly supported between the plates 48. As shown in Fig. 2, the sector I24 is of an odd shape and is formed with two arms I28 and I21 and has a cam slot I28 cut in its surface forward of the pivot I25. Connected to the arm I28 is a spring I28 fastened at its other end to a movable bail I3I pivoted to the frame plates 48 (Figs. 2. 5 and 6). The spring I28 tends to impart a counter clockwise movement to the sector I24 as shown in Fig. 2. The arm I21 of the sector I24 has a lug or projection I32 formed on its outer end adapted to cooperate with a notch I33 cut in one arm of a bell crank I34 associated with the next lower denominational order. The bell crank I34 is mounted loosely on a shaft I supported between the frames 48 and has another arm I38 the front end of which rests normally just under a flat undersurface I31 of the pawl H8. The bell crank I34 shown in Fig. 2 is of the preceding denominaform of a projection. As the cam plate 42 turns clockwise to elevate the wheels I8, the link I48 is drawn forward and near the end of the forward stroke the projection I54 contacts 9. lug I55 on an arm of the bell crank I22 to rock the shaft I2I and the bail II8 counter-clockwise (Fig. 4) to release the pawls H6.

The operation and timing of the transfer mechanism as thus far described is as follows:

In the light of previous description, it is evident that as the cam plate 42 is shifted in a clockwise direction, on adding strokes (Fig. 4) one immediate effect will be to elevate the arms 38 about their pivot 31, thus causing a similar elevation of the mechanism supported by the arms. Therefore, as the pinions I8 rise into engagement with their respective actuators I2, the relative positions of the pawls N8, the bail H8 and the pinions are retained. As another result of the movement of the cam plate 42, the shaft I38 is moved downward until it occupies a cutout portion I58 (Fig. 2) of the slot I28. The movement of the shaft I38 will also release the latch member I44 and allow it to swing forward a short distance under the tension of its spring I48 to contact the arm I42. The disabling of the bail II8 occurs in the manner previously described just before the plate 42 reaches the end of its forward movement. As shown in Fig,

tion on the return stroke of the actuators, the wide tooth 4' will contact the right hand face of the lug H8 and cam the pawl H8 and its arm I42 clockwise a short distance about the pivot 88 in which position it will be latched by the engagement of projection I48 and latching member I44. At the end of the return stroke the pinions I8 are withdrawn from the sectors I2 and return to engagement with the gear sectors I24. It is evident that as the wheel I8 engages the sector I24, the lower flat surface III of the pawl II8 will contact the arm I38 and, as the downward stroke continues, will rotate this arm and the bell crank I34, of which it is a part, counterclockwise about the shaft I88, and thus disengage the slot I38 from the projection I82 on the arm I21 of the sector I24 of the next the spring I28 the sector I24 will then pivot in a counterclockwise direction (Fig. 2) about the shaft I28 until the projection I82 contacts a shoulder I81 formed in the bell crank I84. The pinion I8 which is in mesh with the sector I24 will, therefore, be turned in a clockwise direction a distance of one tooth space which is in proportion to the movement permitted the sector I24. It will also be apparent that as the bail .rod I88 returns to normal, the latch I44 will be disengaged from the projection I48, permitting the pawl I I8 to move about its pivot 88 and again assume the normal position illustrated in Fig. 2.

However, if the above pinion I8 stood at 8" before being turned by its sector I24, the transfer pawl associated with the pinion of next higher order would be tripped against the tension of its spring I48 to effect a carrying into the next higher order. This would occur before the transfer pawl of lower order was fully restored to normal position. In this manner a chain of carry operations is effected during which time the bail H8 is prevented from returning to its normal position by the ends of the tripped transfer pawls II8. When all the pawls II8 are again raised to normal position, the bail II8 will be permitted to assume its usual retaining position under tension of the spring I28. The gear sector I24 is returned to normal on the following operation of the cam plate 42 when the descending rod I88 will engage the cam slot I28 and I88 of the displaced sector and return it to its correct alignment where it will be retained by the cooperation of lug I32 and slot I88 as before explained.

In a previous chapter it was pointed out that subtraction items are accumulated by rotating the wheels I8 in a direction opposite to that in which they are turned during adding strokes. Therefore, the transfer mechanism must be capable of carrying from order'to order in a subtraction direction as well as in the manner above described. In order to reverse the usual motion of the gear sector I24, the spring bail I8I pivotally connected to the frames 48 as previously described, is caused to move to the dot-dash posi tion of Fig. 2, so that the sector I24 may be tensioned to move in a clockwise direction. The transfer mechanism is conditioned to operate in the above manner as a consequence of depressing the subtraction key 88.

Referring now to Figs. 1 and 6, it will be seen that the lever 82 which, as has been previously described, is caused to rotate in a clockwise direction (Fig. 1) upon depression of the subtraction key extends t ward the rear of the machine and 2. if a pinion I8 is rotated past its zero poaiis connected at its far end to a downwardly extending link I88. The link I88 is forked at its lower end and loosely engages a pin I88 on the right hand side frame 48. Formed integrally with the link I88 is an arm "I connected by a pin and slot connection to a triangular shaped operating member I82. The lower end of the member I82 is loosely connected at I88 to a'nose on-the detent lever I88 (shown in Fig. 2) so that a downward pulling motion is imparted to the member I82 on each forward stroke of the operating handle in subtraction and each rearward stroke in addition. Formed in the upper end of the member I82 and placed at opposite ends are two hook like portions I88 and I84 each adapted to cooperate respectively with pins I88 and I88 on a lever I81 pivoted at I88 to the right hand 1 frame plate 48. The lever I81 is formed with a higher order. Due to the tension provided by r forwardly projecting extension I88 which is forked at its forward end and adapted to engage a pin III on one side of the spring bail I8l. It is apparent that if the triangular member I82 is operated while in the position shown in Fig. 8, the hook I88 thereon will engage the pin I88 without moving the lever I81 and act to retain the spring bail III in the position therein occupied which is the adding position previously described. The hook I84 will not engage the pin I88 during this operation. If, however, the link I88 is moved downwardly in response to the 'operation of the subtraction key, the arm "I of the link will act to rock the member I82 clockwise about its pivot I88 to place the-hook I84 just above the pin I88 and in position to engage said pin upon the operation of member I82. The hook I88 is thus rendered ineflective and on the above mentioned downward movement of the member I82 the lever I" will berocked in a clockwise direction about its pivot I88 and through the extension I88 will swing the spring bail III upward about its pivot until it occupies the position shown in dot-dash outline in Fig. 2. As shown in Fig. 6 the spring ball "I has an arm I88 pivoted to its left hand end. Tensioned between one end of the arm I88 and the left hand frame plate 48 is a spring 288 and the resulting cooperation between arm I88 and spring 288 tends to hold the bail I8I in either its add or subtract position. As shown in Fig. 2, with the spring bail III thus positioned, it is evident that when the bell crank I84 is operated in the previously described manner to release the gear sector I24, the spring I28 will rotate the sector one tooth space in a clockwise direction to turn its associated pinion I8 a similar distance in a subtract direction, or counter clockwise as shown in Fig. 2. A shoulder I" on the bell crank I84 limits the movement of the sector I24 in the same manner as the previously mentioned shoulder I81. In all other respects other than the exceptions noted above, the transfer mechanism functions in the same manner on both addition and subtraction operations. v V

In the above description of the transfer mechanism it was endeavored to limit the description in so far as possible to the operation of one gear wheel I8 and its associated carrysector I24. It should be borne in mind, however, that there is a gear sector I24 for each of the pinions I8 and duplicate mechanisms are provided for. effecting a carry from wheel to wheel with the exception that there is no provision for carrying into the wheel of lowest order. Taking the above mentioned wheel of lowest order as an example, it will be readily understood that the pawl II8 assostart of the retum stroke.

ciated with this wheel is adapted to be tripped as the wheel passes zero and'so disable the bell crank latching member I34 whichdies below the pawl H9 and approximately in the same plane. The bell crank I34 normally engages and holds ineffective the gear sector I24 which ls associated with the pinion II of the next higher order. On

adding strokes the release of this sector occurs at or subtract direction according to the position of the spring bail I3I which supports all of the.

springs I29. The means for restoring the sectors I24 to normal is believed to have been made willciently clear in the previous description.

Total taking mechanism Keeping in mind these several functions of the total link, it is evident that if the total key I18 is depressed and the operating handle then pulled forward, the pinions I9 will rise into mesh with their respective accumulator racks I2 and all of the sectors. and I2 are permitted to move forward to printing position. The printing position of each sector 8 is individually determined by the number of tooth spaces required for each pinion I9 to return to zero. On total strokes the lugs II present unyielding surfaces to their respective teeth H4 in order that all of the pinions I8 may be correctly aligned in their original position.

' Index sector As shown in Fig. 1, there is also provided in the machine of the present invention the usual index sector I8I adapted to be raised on total,

In order that the pinions I8 may be cleared and cause the simultaneous printing of their accumulated values, suitable total-taking mechanism, under control of a total key, is provided.

'Because of the novel transfer operation previ ously described, wherein the transfer pawls iii are tripped and reset all in one machine opera-,

front of the machine a key I13 fast to the shaft 51. Also fast to the shaft 51 is an upstanding arm I14 connected at its upper end to the front end of the previously mentioned link I52. The

link I52 or total link as it may be called extends rearwardly the entire length of the machine and is supported at its far end by a plate I15 fixed to the rear frame plate of the machine. Operation of the key I13 will, therefore, cause the link I52 to slide rearwardly through its support I15 and perform the several functions noted below. A pin I18 situated on the side of the link I52 is adapted to cooperate with a nose I11 of the arm 9I to rotate the arm 9I about its pivot 89 to depress the slotted cam plate 93 and so condition the accumulator timing mechanism to bring about the engagement of the wheels I9 with their actuators I2 at the beginning of the forward stroke as previously described. Another function of the total link I52 is to disable the link I48, the purpose of which, as we have seen, is to release the transfer pawls II 8 by rocking the bail II9 which normally holds them engaged. When the total link I52 is in operative position the pin I5I which engages the slot I49 lies a farther distance rearward than usualso that when the cam plate 42 1s rocked on a total stroke a cam surface I18 formed in the'rear of the slot I49 will engage the pin I5I, thus forcing the arm I53 downwardly subtract and non-add operations to print an identifying letter or insignia to the right of the printed item and on the same line. Mechanism of this same general type has been disclosed in numerous other patents, among them the one to Dysart 2,014,560. The sector I8I is similar in shape and operation to the sectors 8 and is provided with a stop arm I82 secured to the rear of the sector and adapted to cooperate through its lug I83'with a stepped bell crank I84. The bell crank I84 is pivoted to a short extension of the shaft 31, and has one arm I85 loosely connected to the rear end of a link I supported at its other end by the right hand frame plate 48 through a pin and slot connection I81 and I88. A spring I89, tensioned between a shoulder on the link I89 and the shaft 31 tends to hold the bell crank I84 elevated in the position shown in Fig. 1 so that the sector I8I is normally arrested from forward movement by contact of the lug I93 with the lowest step of the bell crank I84. On a total taking operation the sector I8I is adapted to rise one step to causethe imprint of a familiar insignia which will indicate that the amount just printed is a total and that the wheels are clear. Depression of 'the total key as previously described causes the rotation of the shaft 51 in a clockwise direction as viewed in Fig. 1. Secured to the shaft 51 is a dependent slotted lever I9I adapted to engage a pin I92 on the lower end of a link I93. At its upper end the link I92 is slidably connected through its arm I94 and I95 to the link I88. It is evident, therefore, that the operation of the total key I13 will cause the bell crank I84 to move in a clockwise direction to enable the lug I83 on the sector IN to engage the next'higher step on the bell crank I84, thus positioning the sector I8I in the printing position mentioned above.

In order that subtraction items and total may be easily recognized as such after they are printed, mechanism is provided for raising the printing ribbon (not shown) from its normal position and causing the aforementioned subtraction items and totals to be printed in red. As

. shown in Figs. 3 and 4, the lever 84, fast to the far enough to permit the projection I54 to pass gages the heels I4 of the sectors I2 and restrains them from forward movement.

shaft 83, has a pin I91 at its upper end adapted to engage a slot I98 formed in one end of a link I99. At its other end the link I99 is connected to another link 28I loosely connected at its upper end to an arm 282. The arm 282 is one of a pair which is fast to the shaft 283 in the frames 284 and which is adapted, when moved upward, to elevate the printing ribbon in a manner not herein shown. The lower end of the link 28I is formed with a notch 285 adapted on occasion to be engaged by a pm 288 on one arm of a bail shaped bell crank 291 loosely mounted on the shaft 31. The bell crank 191 is associated with the line space mechanism and is rocked in a clockwise direction about its pivot 81 on each forward stroke of the machine through the other 'arm 20. of the bell crank and link 299 connected to the arm I09 fast to the main shaft I9. During the regular adding strokes of the machine, the'notch 205 lies out of the path of the pin 2 and, therefore, the arms retain their normal position. However, when the lever 84 has been rocked counterclockwise, as viewed in Fig. 3, as a result of either the depression of the subtract key 98 or the total key I18, the link III will be moved rearwardly a sufficient distance to permit the pin 109 to engage the notch 29! and thus cause the elevation of the printing ribbon to a point where the hammers 32 will strike the red portion of the ribbon and cause the item to be printed in that color.

Example of negative transfer operation The mechanism of my invention may be more clearly understood from the following example in which the totalizer is caused to register a negative amount.

the usual manner to elevate corresponding stop pins 9. The subtraction key 88 is then depressed and the operating handle swung forward to release those sectors 8 and 12 associated with the V elevated stop pins 9. The operation of the subtraction key has positioned the spring bail III in subtract position and has disabled the regular accumulator timing mechanism so that as the main shaft I! starts its forward stroke the accumulating wheels IE will be raised into mesh with their respective actuating racks I 2. The racks I 2 and their associated sectors 8, under tension of their springs ll follow the forward movement of the printing handle until limited by their stops 9. Referring now to Fig. 2 it will be seen that the wheel ll of lowest order will be turned in a counter-clockwise direction a distance of four tooth spaces. The wheel of. next higher order will turn two spaces in the same direction and the next wheel 9 spaces. During the operation each of these wheels I will pass its zero position to trip its associated pawl Ill and condition the transfer mechanism for operation. At the completion of the forward stroke, the operating handle will be permitted to start on its return stroke back to normal. At the beginning of the return stroke the printing hammers 82 will be released to print and the accumulating wheels will be withdrawn from engagement with their actuators I 2 and returned to engagement with their gear sectors I. the reengagement of the pinions l9 and sectors I the latter are released from their latches Ill and a transfer operation occurs which is effective in all of the pinions it except, of course, the wheel of lowest order. At the conclusion of the return stroke, therefore, the wheels will contain Immediately after a negative amount of 999999888 which is the complement of the true negative amount 000000112.

Assuming now that a tota i' desired to be taken immediately after the above operation, the total key I194. first depressed. The operating handle is then 1: .led fcrwr and all of the sectors I and I2 swing forward, engaging as they do so their respective pinions ll returning them to zero and causing the amount represented therein, or 999999888 to be printed in the usual manner. As mentioned above, this amount is the complement of the true negative total and must be translated into the correct negative balance by the operator.

Anegative total may be easily recognized by the series of nines which are caused 10 be printed to the left of the first significant digit.

While I have described what I consider to be 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 a hereinafter claimed.

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

1. In an adding or like machine, the combination of a plurality of register wheels, actuators therefor, a main operating mechanism, means including an oscillating member operable by said main operating mechanism for moving said rogister wheels into and out of cooperative relation with said actuators, a plurality of transfer pawls associated with said register wheels, locking means normally holding said pawls in positive engagement with said wheels, and an operating element connected to said oscillating member and operable thereby to disable said locking means after said wheels are moved into cooperative relation with said actuators.

2. In an adding or like machine, the combination of a plurality of register wheels, actuators therefor, a main operating mechanism, means including an oscillating member operable by said main operating mechanism for moving said register wheels into and out of cooperative relation with'said actuators, a plurality of transfer pawls associated with said register wheels, locking means normally holding said pawls in positive engagement with said wheels, an operating element connected at one end to said oscillating member and operable thereby, said operating element being guided at the other end by a cam slot formed therein and a pin normally engaging a portion of said slot whereby movement of said operating element is guided in a, manner to disable said locklng means after said wheels are moved into cooperative relation with said actuators, a key, and means operable upon the depression of said key to shift said pin into another portlon of said slot whereby movement of said operating element is guided in a manner to pergilt said locking mean to remain in locking posi- ELMER H. DREHER.

Images