US3076602A - dombrowski - Google Patents

Description

Feb. 5, 1963 E. J. DOMBROWSKI 3, ,6

TRANSFER MECHANISM FOR CALCULATING MACHINES I Filed Feb. 21, 1962 4 Sheets-Sheet 1 ATTOK/Vf) Feb. 5, 1963 E. J. DOMBROWSKI 3,

TRANSFER MECHANISM FOR CALCULATING MACHINES Filed Feb. 21, 1962 4 Sheets-Sheet 2 INVENTOR. EDWARD J fidMbWOM JK/ Feb. 5, 1963 E. .1. DOMBROWSKI 3,

TRANSFER MECHANISM FOR CALCULATING MACHINES Filed Feb. 21, 1962 4 Sheets-Sheet 3 INVEN TOR. [0/4 1450 J'- DflA/BAUWIK/ Feb. 5, 1963 J, DQMBROWSKI 3,076,602

TRANSFER MECHANISM FOR CALCULATING MACHINES Filed Feb. 21, 1962 4 Sheets-Sheet 4 --\\m. V H4 10. H6? 72. Y I 37 im 35 I. :5 33= 190 1 3:

ATTORNEY United States Patent Ofiice 3,076,602 TRANSFER MECHANISM FOR CALQULATING MACHXNES Edward J. Dombrowsld, Derby, Conn, assignor to Sperry Rand Corporation, New York, N.Y., a corporation of Delaware Filed Feb. 21, 1962, Ser. No. 174,854

18 Claims. (Cl. 235-137) This invention relates to transfer mechanisms for calculating machines and the like, and more particularly to such mechanisms for effecting primary and secondary transfer operations simultaneously with each other. Transfer mechanisms of the present invention may be usefully employed in various types of machines operable for accumulating items, such as, machines for adding and/or subtracting, calculating, item registering, accounting, and bookkeeping, provided that such machines utilize a mechanically operating memory device for each denominational order for storing the items accumulated by the machine. Transfer mechanisms are provided in such machines for transferring one unit to a memory device of a higher order either additively or subtractively when the memory device of the next lower order accumulates its capacity and must therefore transfer its accumulation, as a unit, to the next higher order.

For example, in machines arranged for accumulating items in decimal notation form by means of an accumulator or storage device for each order, Whenever the accumulator device of an order accumulates through 9 to 0, or vice versa, as the case may be, its accumulation must be transferred, as a unit, to the accumulator device of the next higher order, either additively or subtractively. Under conditions where such a transfer to a higher order accumulator device is directly initiated by the entering of an item input into the accumulator device of its next lower order, rather than by a transfer of a unit input into such next lower order, it is termed a primary transfer operation.

- It maylhappen that the accumulator device into which the transfer unit is entered during the primary transfer operation is itself accumulated to capacity, and is, thus, in turn, moved from 9 to 0, or vice versa, which movement may be termed through its transfer position, thus causing, in turn, a unit transfer of its accumulation into the accumulator device of the next, next higher order. This second transfer operation, which is directly initiated by a primary transfer and only indirectly by an item entering operation, may betermed a secondary transfer. Such a secondary transfer may, in turn, initiate other secondary transfers in successive next higher orders. Normally, such additional secondary transfers follow each other in aripple-like sequence, such that the cycling time of the machine must be lengthened appreciably in order to allow for the total time required to perform the possible maximum number of secondary transfers, which lengthening is undesirable. Since the amount of maximum secondary transfer time which must be allowed for increases in proportion to the number of orders for which the machine is equipped, such lengthening may become prohibitive, or, in any case economically unfeasible.

In attempts to minimize the cycling time of such calculating machines, transfer mechanisms for effecting primary and secondary transfer operations concurrently with each other have been devised. However, such transfer mechanisms, which may be termed simultaneous, usually required an additional time consuming conditioning or presensing operation of the transfer actuator means before their operat'on, and are of intricate design, thereby tending to be uneconomical and unreliable.

Other transfer mechanisms of the simultaneous type undesirably are not sufiiciently positive acting, and, while 3,076,602 Patented Feb. 5, 1963 tending to initiate primary and secondary transfer operations simultaneously, do not effect their completion simultaneously; the latter deficiency usually being due to operating tolerances necessarily provided between coacting parts of their respective mechanisms. Such necessary operating tolerances introduce a lag in the sequence of secondary transfer, which lag increase in magnitude in proport'on to the number of orders involved in the secondary transfer sequence and, in certain cases, is appreciable. This lag, in addition, may often be of unpredictable varying magnitude and, if not, compensated for, results in misalignment of the accumulator devices, particularly the ones towards the end of the transfer sequence. This, in turn, results in inaccurate storage of input items by the calculator. Such transfer mechanisms, therefore, tend to be unreliable. In addition, wear and tear of the coacting parts, of the calculator tend to increase the dimensions of the aforementioned operating tolerances, thereby causing the calculators, as wear continues, to become progressively less reliable.

Attempts have been made to improve the reliability of such calculators by devising and incorporating therein independently acting final alignment devices which are effective after the operation of the transfer mechanism to bring the accumulator devices into proper final alignment. Such alignment devices, in effect, complete the transfer operations; However, they require additional control mechanism for their operation, undesirably in crease the cycling time of the machine, add to its manu facturfng cost, and make for a more intricate design which may malfunction.

It is, therefore, an object of the invention to provide for calculating machines transfer mechanism whichis of simple construction, reliable, and effective to minimize the t'me consumed by transfer operations.

Another object is to provide in such machines transfer.

mechanism which effects all the primary and secondary transfers simultaneously and positively under the sole control of the accumulator devices and without any 'addi-' tional presensing or final alignment operations.

It is still another object to provide in such machines: transfer mechanism which effects all the primary .and secondary transfers simultaneously with each other, and proper final alignment of the accumulator devices con currently with the simultaneous transfer operations. A further object is to provide in such machines transfer mechanism which, in initiating primary transfers and in eifecting all primary and secondary transfers simultaneously, is sufficiently positive acting to be reliable in its operation.

A still further object is to provide in such machines transfer mechanism which effects all primary and secondary transfers simultaneously and accurately, and yet is constructed simply and economically of components which need not be engineered and manufactured to or maintained at extreme exact tolerances.

The invention involves providing in each denomina tional order of a transfer mechanism an accumulator device movable into a plurality of item storage positions, a transfer element movable therewith througha predeter mined transfer distance and a transfer actuator. The transfer element of a first order in passing through such transfer distance is engageable with the transfer actuator of the next higher order. Under conditions where, during an item entering operation, the accumulator device moves through its transfer distance, its transfer element drives the actuator of the next higher order into what may be termed a transfer accept position, conditioning it for a primary transfer. Means are provided for locking actuators thus moved into transfer accept position to a transfer driving device which, when the accumulator devices are in driveable engagement with their respective 3 actuators, is effective to drive the actuators thus locked to a third position, effecting the primary transfers. Under conditions where an accumulator device of a next higher order is itself, in turn, driven through its transfer distance by a primary transfer, its transfer element, in turn, engages the actuator of the next, next higher order, driving it towards transfer accept position to effect a secondary transfer simultaneously with the primary transfers. Means individual to each actuator and operatively responsive to driven movement of its associated actuator towards transfer accept position are also provided and are efiective for applying to their respective actuators forces of sufiicient magnitude and in a direction to move such actuators to transfer accept position to complete the secondary transfers and, simultaneously therewith, proper alignment of the secondary transfer accumulators.

Features and advantages of the invention will be seen from the above, from the following descriptions of the preferred embodiments when considered in conjunction with the drawings in which like numerals refer to like parts in different figures, and from the appended claims.

In the drawings:

FIGURE 1 is a simplified diagrammatic cross-sectional view in side elevation of a portion of a calculating machine embodying the invention showing one denominational order thereof with the parts in non-operated condition;

FIGURE 2 is an enlarged fragmentary end view of the transfer mechanism of FIGURE 1 looking from the right of FIGURE 1 showing various parts in operated condition, and with the elements for the lowest to highest denominational orders positioned consecutively from left to right;

FIGURE 3 is an enlarged fragmentary view of a portion of FIGURE 1 showing the parts in condition for accumulating;

FIGURE 4 is a view similar to FIGURE 3 showing portions of the transfer mechanism for two adjacent denominational orders with portions broken away and the transfer mechanism for one denominational order in transfer accept position; like parts of diiferent denominational orders being diflerentiated by the lower case suffix letters a and b appended to their common numeral designations;

FIGURE 5 is a view similar to FIGURE 3 showing one denominational order of the transfer mechanism with portions broken away, with transfer actuator 41 in its fully operated position, and also fragmentary illustrations of the actuator in its respective unoperated and transfer accept positions;

'FlGURE 6 is a view similar to FIGURE 3 of another embodiment of the subject transfer mechanism, which embodiment is particularly suited for calculating machines which add algebraically, showing in solid line outline the parts i in condition for accumulating, and in broken line outline a transfer actuator 41 in its transfer accept add position;

FIGURE 7 is a simplified schematic view of a portion of the mechanism of FIGURE 6 showing a tarnsfer actuator 41 in its transfer accept subtract position;

FIGURE 8 is a simplified schematic representation of a portion of the drive mechanism for the add and subtract transfer bails 61a, 61s of the mechanism of FIGURE 6, showing both bails in condition for accumulating;

FIGURE 9 is a view similar to FIGURE 3 of still another embodiment of the subject transfer mechanism showing in solid line outline the parts in condition for accumulating, and in broken line outline transfer actuator 41 in both its transfer accept and fully operated positions; and k FIGURE 10 is a fragmentary rear end view of the transfer mechanism of FIGURE 9, looking from the right of FIGURE 9.

For the sake of simplicity and clarity, the invention is shown and will be described as applied to calculating machines arranged for accumulating items in decimal notation form, i.e. in powers of the numeral 10, entered. by means of a 10 key keyboard and utilizing racks and pinion gears for listing the items and storing the accumulations; it being understood, nevertheless, that the invention is also applicable to machines arranged for calculating items in denominational orders other than powers of 10, and utilizing other types of entering, listing and storing mechanisms. Also for simplicity, zero, "0, will be termed a digit herein.

FiGURES 1 through 5 of the drawings illustrate a preferred embodiment particularly suitable for calculating machines arranged for accumulating items unidirectionally only, such as, for example, machines which add but do not subtract.

The adding machine illustrated is of the well known type consisting of a pin box 11 (FIGURE 1), a set of horizontally arranged, longitudinally movable racks 12 and coacting register pinion gears or accumulator wheels 14; the mechanism for one denominational order only being shown in FlGURE 1.

The main drive shaft of the machine is designated 15. As is well known in the art, this drive shaft makes one revolution at constant speed for each machine cycle and, by known means, not here shown or described, imparts predetermined movements to various operating mechanism, such as universal bar 16 positioned in the forked end of actuating lever 17. Universal bar 16, during a first portion of the machine cycle, is caused to move to the right, travelling in longitudinally extending guide, slots 19 defined in the racks 12. Such movement releases the racks which may then also move linearly towards the right under the influence of their respective biasing springs 21. Racks 12 are guided in their linear movements by means of rods 22, 23 fixedly positioned in guide slots 19, 24, respectively.

As is usual in this type of machine, pin box 11 is mounted on a pin carriage (not shown) movable transversely of racks 12 step-by-step in response to each actuation of any of the input keys (not shown) of the machine. Pin box 11 is provided with a longitudinally extending row of ten pins 26 for each denominational order; the pins in each row corresponding to the digits 0 through 9 and being so designated. When a first digit, for example 7, of an amount to be entered is set up in the keyboard (not shown) the pin box is caused to move transversely one step into alignment with the rack 12 of the first denominational order, in the present example, the rack for the units order. At the same time the pin 26, corresponding to digit 7 in the first pin row is moved downward to act as a stop upon projection 23 of the rack 12 with which it is then aligned. The pins 26 correspond ing to digit 9 are fixed in their downward positions and act as final limits to movement of the racks toward the right. With the setting up on the keyboard of each subsequent digit of the amount to be entered; a corresponding digit pin 26 is depressed in a successive pin row in accordance with such amount; pin box 11 continuing its step-by-step transverse movement at each input, thereby placing, as the last digit is entered, each depressed pin into proper alignment with the rack 12 associated with its denominational order in accordance with the most significant number of the amount to be entered. A suppressor member 3! movable with pin box 11 projects in the direction of pin box movement, and, in a well known manner, coacts with projection 28 of the racks 12 associated with denominational orders greater than the most significant number of the amount to be entered, preventing the release of such racks.

When universal bar 16, in moving to the right, releases racks 12, they move under the influence of their respective biasing springs 21 to the right. The movement of the racks for which an input has not been set up is arrested, as has been explained previously, by rack suppressor 3d engaging their respective projections 23. Each of the racks into which a digit is to be entered continues moving or escapes to the right until arrested by the pin 26 set into the path of its projection 28.

Thus, it may be seen that the arrested position of each rack 12 which escapes is determined by the relative position of its arresting pin 26 with respect to the other pins in the same pin row, and indicates the digit corresponding to such arresting pin. The amount to be stored and accumulated by the machine has now been, What may be termed, entered into the racks.

The mechanism for storing and accumulating the entered amount comprises for each denominational order a pinion gear 14, having as many peripheral teeth 33 as there are possible inputs into its order. For the present example of accumulations in decimal notational form, each pinion gear 14 is provided with ten teeth 33 spaced 36 apart and corresponding to the digits 0 through 9. Pinion gears 14 are rotatably mounted on shaft 35, and are normally held out of engagement with coasting teeth 37 formed on their respective associated racks 12. Each pinion gear 14 is provided with an axially projecting side or transfer tooth 39 (FIGURES l and 2), for purposes to be explained hereafter.

A set of transfer actuators 41, one for each denominational order, are pivotally mounted on a fixed shaft 43. However, the actuator 41 for the lowest order is prevented from pivoting by rod 42 (FIGURE 2) rigidly securing such actuator to a fixed side wall 44 of the machine. Each transfer actuator 41 consists of a segmental gear portion 45, having three teeth 47 spaced 36 apart and facing the pinion gear 14 associated with its denominational order (with whose peripheral teeth 33 they are aligned for meshing cooperation) and a transfer pawl portion 49 offset from the segmental gear portion 45 and extending towards the pinion gears 14 for cooperating with the transfer tooth 39 of the pinion gear 14 of the next lower order. An additional transfer actuator 41 without a segmental gear portion 45 is also provided, and is positioned on the right end of fixed shaft 43 (FIGURE 2) so that its transfer pawl portion 49 may cooperate with the side tooth 39 of the pinion gear 14 of the highest order, for purposes to be explained hereinafter. Spacers 38 and 41) (FIGURE 2) rotatably mounted on shafts 35 and 43, respectively, maintain pinion gears 14 and transfer actuators 41 in proper alignment with each other.

A set of toggle springs 51, one for each transfer actuator 41, are provided. Each toggle spring 51 has two attaching ends, one of which is attached to a fixed shaft 53, common to all the springs, and the other of which is attached to projecting arm 55 of its associated transfer actuator 41. Under conditions where the transfer actuators 41 are in their respective non-operated or rest positions I (FIGURE 1), they are individually urged by their respective toggle springs 51 against a stop 57 in the form of a fixed rod common to all the transfer actuators.

Mechanism for driving the transfer actuators, in a manner to be described hereinafter, is provided and includes a transfer bail 61 of U-shaped configuration (FIG- URE 2) rotatably mounted at its bent over end portions 59, 60 on fixed shaft 43. Transfer ball 61 is actuated within a limited arcuate path in a predetermined manner during the machine cycle by means of a cam follower arm as, cooperating with a cam 67 mounted on an auxiliary drive shaft 69 driven from main drive shaft 15. Bail 61 is pivotally connected at its bent over end portion 60 to one end of cam follower arm 63 by means of a short shaft 64 (FIGURE 2), the other end 65 (FIGURES l, 2) of which cam follower arm is pivotally secured to stationary side wall 44 of the transfer mechanism. A cam follower 72 is rotatably mounted on cam follower arm 63 and is biased by spring '74 (FIGURE 1) into rolling engagement with the cam surface of cam 67 for actuation of the cam follower arm and, in turn, bail 61.

An axially extending transfer bar 78 is carried by bail 61. Formed in each bent over end portion 59, 60 of bail 61 is a radially extending guide slot 76 (FIGURE 1) into which transfer bar 78 is disposed for limited radial movement. Transfer bar 78 also extends through arcuate cam slots 81 formed in the oppositely disposed stationary side walls 44, 83 (FIGURE 2) of the machine. Bail 61, in its movements, carries transfer bar 78 along arcuate cam slots 81 which act to limit arcuate movement of the bail. A radially disposed coil spring 86 (FIGURE 5), under tension, biases transfer bar 78 inward toward shaft 43 of the transfer actuators 41, causing the transfer bar, as it travels in cam slots 81, to ride along the inward edge cammin-g surfaces 90 of such cam slots thereby moving radially within radial guide slots 76 as it travels.

It may be noted that each transfer actuator 41 has formed on its side edge surface adjacent transfer bar 73 a camming projection 93 and a transfer bar receiving cut-out portion 95 (FIGURE 3); they being provided for cooperation with the transfer bar, in a manner and for purposes to be explained hereinafter. In addition, the midsection of arcuate cam slot 81 is slightly enlarged to allow limited radial movement of transfer bar 78 within such slot section, for purposes also to be explained hereinafter. As will be apparent from the drawings, transfer bar 78 may be carried clockwise by bail 61 from its rest position, designated I (FIGURE 1) along arcuate cam slot 81 to amid position II (FIGURE 3) and then to a third position III (FIGURES). Bail 61, during its return stroke, carries transfer bar 78 counterclockwise back to its rest positionI.

During the escape of racks 12 to the right, previously described, and which occurs during the amount entering portion of the machine cycle, pinion gears 14 are held in engagement with their'corresponding transfer actuators 41 (FIGURE 1) and out of engagement with racks 12. Next in the cycle, bail 61 is driven to position II (FIGURE 3), carrying transfer bar 78 along with it into the slightly enlarged midsection of arcuate'cam slot 81. Pinion gears 14 are then moved out of engagement with their respective transfer actuators 41 and into engagement with their corresponding racks 12 (FIGURE 3) 'in preparation for transferring the amount (presently entered into the racks) into pinion gears 14 for storage. The mecha nism for moving pinion gears 14 between their respective transfer actuator engaging positions and rack engaging positions is well known in the art, and, therefore has not been shown and will not be described herein.

It may be noted that racks 12, pinion gears 14.and transfer actuators 41 are positioned with respect to each other such that pinion gears 14 engage rack teeth37 of their respective corresponding racks before they become entirely disengaged from the segmental gear portions 45 of their respective associated transfer actuators 41. Such relative positioning obviates unintended slip rotation of pinion gears 14, while they are being disengaged from transfer actuators 41 and engaged with racks 12, or vice versa, which slip rotation may result in the incorrect storage of accumulations.

The racks 12, which have escaped to the right to predetermined respective positions corresponding to the amount entered therein, are next driven by universal bar 16 leftward back to their respective normally non-operated positions. These racks, in moving leftward, rotate their corresponding pinion gears 14 with which they are presently meshed, counter-clockwise predetermined amounts in accordance with their own respective linear movements. Such translation of the linear rack movement to rotational gear movement transfers the amount previously entered into the racks into their corresponding pinion gears for storage.

It may be noted that the transfer pawl portion 49 of each transfer actuator 41 is positioned with respect to the side tooth 39 carried by the pinion gear 14 of the next lower order so as to be engaged thereby whenever such pinion gear has accumulated to the digit 9 in its denominational order.

Next assume that a pinion gear 14 of a certain denomination is rotated counter-clockwise by its corresponding rack 12 one unit past its storage capacity, in the present example 9, necessitating that its accumulated total be transferred, as a unit, to the pinion gear of the next higher order. In such a case, as such certain pinion gear 14 is thus rotated through what may be termed its transfer position or arc its side tooth 39, presently in engagement with the transfer pawl portion 4% of the transfer actuator 41 of the next higher order, drives such transfer actuator clockwise one step to position If (FIGURE 4), which position may be termed the transfer accept position, in preparation for effecting a primary transfer to the pinion gear 14 of the next higher order.

As transfer actuator 41 is thus rotated from its rest position I (FIGURE 3) to position II, its toggle spring 51 (FIGURE one end of which is attached to the actuator, is moved off center sufiiciently so as to apply its biasing force to actuator il in a direction to aid the clockwise movement of the actuator. In addition, as transfer actuator 41 rotates clockwise toward position II, its camming edge surface 93 engages transfer bar 73, pushing it outward, against the force of biasing coil spring 856 out of engagement with the inner cam surface 90 of arcuate cam slot 81, thereby causing bar 78 to ride along camming edge surface 93. Upon movement of actuator 41 to position II, coil spring 86 urges transfer bar 78 into cut-out portion 95- of the actuator, thereby effectively locking the transfer actuator to the transfer bar in the transfer accept position. it may thus be seen that any transfer actuator 41 which is rotated to transfer accept position II in preparation for effecting a primary transfer becomes, in such position, locked to transfer bar '78.

Pinion gears 14 (FIGURE 5) are next moved out of engagement with their respective racks 12 and back into engagement with the segmental gear portions 45 of their corresponding transfer actuators 41. Transfer bail 61 is then driven clockwise by its operating mechanism from position II to position III, driving the prepared transfer actuators 4]. (locked to transfer bar 78 in position II) clockwise from transfer accept position II to position III, thereby rotating the pinion gears M, presently meshed with such prepared actuators, counter-clockwise one step to effect the primary transfers.

Next assume that a transfer actuator 41, in rotating from position II to III to effect a primary transfer t the pinion gear 14 of a next higher order, drives such higher order pinion gear, in turn, through its transfer position. This necessitates a secondary transfer of the accumulation of such higher order pinion gear to the pinion gear 14 of the next, next higher order. In such a case, as the pinion gear 14 of such next higher order is rotated counter-clockwise through its transfer position, its side tooth 39, presently in engagement with the transfer pawl portion of the transfer actuator 41 of the next, next higher order, drives such actuator clockwise one step from its rest position I to position II. Actuator 41 of such next, next higher order in rotating clockwise one step, in turn, drives its corresponding intermeshed pinion gear 14, one step counter-clockwise, thereby effecting a secondary transfer thereto simultaneously with the aforementioned primary transfer. As was previously described, transfer actuator 41 in rotating from position I to II moves its toggle spring 51 off center sufiiciently to cause such spring to exert in a snap action manner its biasing force in a direction to aid the secondary transfor for purposes to be explained hereinafter.

Next assume that the pinion gear 14 of such next, next higher order is also thus rotated through its transfer position, causing its side tooth 39, in turn, to drive the transfer actuator 41 of the next successive higher order to position II, thereby effecting another secondary transfer simultaneously. It may therefore be seen that, under certain conditions, a series of secondary transfers may occur simultaneously. For example, in the case of the digit 1 being added to the numeral 99999, it is seen that a primary transfer occurs from the first to the second orders, and concurrently therewith secondary transfers occur to the third, fourth and fifth orders. Since it is seen that all the transfers are effected by hail of being driven from position II to position III, it is apparent that they are all (both primary and secondary and in all orders) effected simultaneously with each other.

It may be noted that the pinion gears 14 instrumental in the above example to effect a series of concurrent secondary transfers may, due to operating tolerances necessarily provided between transfer actuators 4i and pinion gears 14, be moved less than one full step during the transfer operation, and, therefore, not be properly aligned at the completion of the transfers. In order to remove such a possibility, toggle springs 51 individual to the transfer actuators 41, are effective, during movement of the transfer actuators from position I to II, to exert individually on their respective transfer actuators snap action forces sufficient in magnitude and in a direction to drive such actuators to position II. The application of these individual snap action spring forces to actuators 41 causes rotation of the pinion gears 14 with which the actuators are then meshed a full step into proper alignment. In efiect, such individual toggle springs 51 act as a snap action" despiraling device in cases of successive secondary transfers to obtain, simultaneously with the transfer operations, accurate final alignment of pinion gears 14- and, consequently, correct storage of the amount entered. The springs 51 are especially useful whenever a series of concurrent secondary transfers occurs.

In order to return the transfer mechanism to its normally unoperatcd condition in preparation for the next operation without affecting the present data storage positions of pinion gears 14, the pinion gears are again moved out of engagement with their corresponding tran fer actuators 41 and back into engagement with racks 12. Bail 61 is then driven through a counter-clockwise return stroke from position III to position, I, driving any previously actuated transfer actuators 41 back to their rest positions against stop 57. As transfer actuators 41 are thus returned to rest position, transfer bar 78, carried by bail 61, rides along the inner camming edge surface 9% of cam slot 81, moving as it travels past the midsection of slot 81, out of locking engagement with transfer actuators 4i. Pinion gears 14 are then returned into engagement with their corresponding transfer actuators .41 in preparation for the next operation of the machine.

During total taking, the respective pawl portions 49 of transfer actuators 41 in cooperation with their corresponding side teeth 39 of the pinion gears 14 act as Zero stops for the pinion gears, as is well known in the art; the transfer pawl 49 (FIGURE 2) for the highest denominational order (which pawl, as was previously stated, is not part of a transfer actuator) acting as a zero stop for the pinion gear 14 of such highest order.

In order to illustrate the operation of the present transfer mechanism assume that the amount of 61,579 has been entered into racks 12, in a manner similar to that previously described, and is to be added to the amount 563,439 already accumulated in pinion gears 14. Under such conditions, pinion gear 14 for the first order has already accumulated its storage capacity, i.e. to 9 and its side tooth 39 is presently in engagement with the transfer pawl portion as of the transfer actuator 41 for the second denominational order. Next assume that the amount 61,579 is transferred from racks 12 to pinion gears 14 for storage by driven return movement of the previously escaped racks to the left, as was previously described. Such rack movement drives the pinion gears 14 for the first, second and fifth orders counterclockwise beyond their respective 9 positions, causing their respective side teeth 39 to engage the drive the transfer pawl portions 49 of their respective next higher order transfer actuators 41 clockwise from rest position I to transfer accept position II in preparation for effecting primary transfers to the second, third and sixth order pinion gears 14. Thus, after the amount has been entered into the pinion gears 14 for storage but before the tens transfers have occurred, the transfer actuators 41 associated with the second, third and sixth denominational orders are in transfer accept position If and locked to transfer bar 78.

Next, pinion gears 14 are moved into meshing engagement with the segmental gear portions 45 of their corresponding transfer actuators 41, and transfer bail 61 is driven clockwise from position If to III, driving (by means of transfer bar 78) the prepared transfer actuators 41 to position III, thereby effecting primary transfers to the second, third and sixth orders by driving the pinion gears 14, corresponding to such prepared transfer actuators, counter-clockwise one step. Moreover, since the pinion gear 14 for the third order, in receiving the unit of primary transfer from the second order, in turn, moves from its 9 to positions, its side tooth 39 engages the transfer pawl portion 4) of the transfer actuator 41 associated with the fourth order, driving it clockwise to position II. Rotation of the transfer actuator 41 for the fourth order to position II drives its intermeshed corresponding pinion gear 14 one step counterclockwise, efiecting a secondary transfer to the fourth order pinion gear. In addition, as the transfer actuator 41 of the fourth order moves from position I to 11, its toggle spring 51 is moved off center sufiiciently to exert a snap action spring force in a direction to aid clockwise movement of such transfer actuator to position II and of sufficient magnitude to effect proper alignment of pinion gear 14 for the fourth order, thereby correctly storing the accumulated total amount 625,018 in the pinion gears.

In FIGURES 6 through 8 is illustrated a slightly modified embodiment of the add only transfer mechanism of FIGURES 1 through 5, which modified embodiment is particularly suitable for calculating machines arranged for accumulating items algebraically, i.e., machines which not only add but also subtract. The algebraic embodiment of FIGURES 6 through 8 is similar in construction and operation to that of the add only embodiment, previously described. For the sake of brevity and clarity, similar elements of both embodiments bear the same numeral designations; the sufiix letters a and s being added to the numeral designations in FIGURES 6 through 8 of elements which are utilized for adding and subtracting, respectively, to differentiate therebetween. For example, the rack in FIGURE 6 is designated 12, as it is in FIGURES 1 through 5, and, in FIGURE 6, 61a designates an add transfer bail while 61s designates a second bail, termed a subtract transfer bail; both bails being similar in construction and operation to transfer bail 61 of the add only embodiment of FIGURES 1 through 5.

Transfer bail 61a for adding and transfer bail 61s for subtracting are arranged to be simultaneously driven during predetermined portions of the machine cycle from their respective rest positions I, to transfer accept positions II and then to transfer complete positions III. The mechanism for driving transfer bails 61a, 61s simultaneously is represented schematically in FIGURE 8 wherein 63 designates a cam follower arm cooperating with a cam 67 mounted on auxiliary drive shaft 69 which, in turn, is driven from main drive shaft (not shown). Cam follower arm 63 is mounted on the calculating machine frame (not shown) to pivot at 101, and has formed on one of its ends a segmental gear portion 193 which is intermeshed with a segmental gear portion 195 formed on an auxiliary cam follower arm 1G7. Arm 107 is also mounted on the machine frame to pivot at 169. Add bail 61a has a driven portion 62a connected to the driving end of cam follower arm 63 by means of a short stub shaft 111a positioned in an elongated slot 113a defined in the cam follower arm. Subtract bail 61s has a driven end 62s similarly attached to auxiliary cam follower arm 107 by means of short stub shaft 111s positioned in elongated slot 113s formed in the driving end of auxiliary cam follower arm 167.

Clockwise rotation of cam follower arm 63 by cam 67 causes simultaneous counter-clockwise rotation of auxiliary cam follower arm 107 with which it is intermeshed. Such follower arm movement drives transfer bails 61a, 61s simultaneously, during predetermined portions of the machine cycle, from their respective rest positions designated I to positions II and, finally, to positions III. Counter-clockwise movement of cam follower arm 63, during the machine cycle, and corresponding clockwise movement of auxiliary cam follower arm 167 returns bails 61a, 61s to their respective rest positions I in preparation for subsequent reoperation.

A dog eared member 115 is provided for each transfer actuator 41; the dog eared members 115 being rigidly attached to a common manually rotatable shaft 117 supported on the calculating machine frame (not shown). Shaft 117 may be manually rotated into either of two positions, depending upon whether an add or subtract operation is desired. With members 115 in what may be termed their respective add positions, as shown in FIG- URE 6, the members 115 limit counter-clockwise movement of their respective associated transfer actuators 41 by means of a lateral stop projection 57a formed on the right ear of each member. When the dog eared members 115 are rotated clockwise into subtract position (FIGURE 7), a similar stop projection 57s formed on the left ear of each member limits clockwise movement of their associated transfer actuators 41.

Toggle springs 51, one for each transfer actuator 41, are pivotably attached at one end to a common spring shaft 53 which is, in turn, rigidly attached to the respective mid portions of dog eared members 115 for movement therewith. With dog eared members 115 in position for adding (FIGURE 6), toggle springs 51 urge their respective transfer actuators 41 against their corresponding stops 57a, while with dog eared members 115 in position for subtracting (FIGURE 7) springs 51 urge their respective transfer actuators 41 against their c0rresponding stops 57s.

As may be seen from FIGURE 6 (wherein the parts are shown in condition for accumulating, additively), the racks 12, pinion gears 14 and transfer actuators 41 for each denominational order may each be driven in either of two opposite directions, depending upon whether an amount is to be accumulated additively or subtractively; the proper directions being indicated by appropriately designated directional arrows. Upon a rack 12 being driven to the left (in any well known manner) a predetermined linear distance in accordance with the amount to be accumulated additively in its order, its corresponding pinion gear 14 is rotated counter-clockwise a corresponding distance, thereby entering the amount additively into the pinion gear for storage. Each pinion gear 14 is provided with a side tooth 39 in position for engaging and driving transfer pawl portion 49 of the transfer actuator for the next higher order as the pinion gear passes through its transfer position either additively or subtractively; each portion 49 being dimensioned in Width as to be engaged by its associated side tooth 39 as such side tooth arrives at transfer position either additively or subtractively. R0- tation of pinion gear 14 counterclockwise through its transfer position causes the right or add side edge of its side tooth 39 to engage the left side edge of transfer awl portion 49 of the transfer actuator 41 of the next high order, driving such transfer actuator clockwise from its rest position I to its transfer accept position II in preparation for effecting a primary transfer to the pinion gear of such next higher order. Each actuator 41 has formed on its lower left side edge surface a camming projection 93a and a transfer bar receiving cut-out portion 95a for cooperation with add transfer bar 1 8a to lock transfer actuator 41 to the transfer bar when the actuator is rotated clockwise to transfer accept position If for additive accumulations, in a manner similar to that previously described for the add only machine.

Racks 12 may similarly be driven to the right predetermined linear distances in accordance with the amount to be accumulated subtractively in their respective orders. Such driven movement of racks 12 to the right drives their associated pinion gears 14 clockwise corresponding respective distances, thereby accumulating the amount therein for storage. Under conditions where such a pinion gear 14 passes through its transfer position subtractively, the left or subtract side edge of its side tooth 39 engages the right side edge of transfer pawl portion 49 of the transfer actuator 41 for the next higher order, driving such next higher transfer actuator counterclockwise from its rest position I to transfer accept position II (FIGURE 7) where it becomes locked to subtract transfer bar 78s, in a manner similar to that previously described for additive accumulations, in preparation for effecting a primary transfer subtractively to the pinion gear 14 of such next higher order.

In operation, assume that it is desired to accumulate a certain amount additively. Dog ear-ed member 115 is manually moved to its acid position (FIGURE 6) and pinion gears 14 are disengaged from racks l2 and moved into engagement with their respective segmental gear portions 45 of their corresponding transfer actuators 41. Next in the machine cycle, the add and subtract bails 61a, 61s, respectively, with their respective corresponding transfer bars 78a, 78s are driven simultaneously from their rest positions I to their respective positions II, and certain racks 12 allowed to escape to the right predetermined respective distances in accordance with the amount to be entered therein.

Next, the pinion gears 14 are moved out of engagement with their associated transfer actuators 41 and into engagement with their corresponding racks 12. The escaped racks 12. are next driven to the left to their original respective unoperated positions, rotating their respective intermeshed pinion gears 14 additively (counter-clockwise) corresponding distances, thereby placing the amount to be accumulated additively into the pinion gears 14 for storage.

In order to demonstrate the operation of the transfer mechanism for additive accumulations, next assume that, as a pinion gear 14 is rotated additively (counter-clockwise by movement of its associated rack I2 to the left), it passes through its transfer position. Under such conditoins, as it passes additively through its transfer position,

the add side edge of its side tooth 39 engages and drives the trans'er pawl 49 of the transfer actuator 41 of the next higher order one position clockwise, rotating such next higher order transfer actuator 41 from its rest position I to transfer accept position II, where it becomes locked to add transfer bar 78a in preparation for effecting a primary transfer additively; toggle spring 51 aiding such movement of the transfer actuator.

Next in the machine cycle, pinion gears 14 are moved out of engagement with racks 12 and into engagement with their corresponding transfer actuators 41. Transfer bails 61a, 61s are then simultaneously moved from their respective positions II to III; add transfer bar 78a (carried by bail 61a), driving the next higher order transfer actuator 41 (which is locked to it) from position II to III to effect additively a primary transfer to the next higher order, as has been previously described (such movement of transfer actuator 41 from position II to III, causing it to drive its corresponding pinion gear 14, with which it is presently intermeshed, one position counteri2 clockwise to transfer the accumulation, as a unit, additively to the next higher order pinion gear). It may be noted that, during such transfer operation, the movements of subtract bail 61s and its associated transfer bar 78s are without effect.

As was previously described for the add only machine, should the pinion gear i i of such next higher order, in turn, be rotated by the primary transfer counterclockwise past its transfer position, the add side edge of its side tooth 39, in turn, engages the transfer pawl portion 49 of the transfer actuator 41 for the next, next higher order, driving such next, next higher actuator 41 from its rest position I to position II. Such movement of the next, next actuator 4-1, in turn, drives its corresponding pinion gear I4 (with which it is presently intermeshed) one position counter-clockwise, effecting an additive secondary transfer to the pinion gear 14 of such next, next high order simultaneously with the primary transfer.

As has been previously described, upon movement of of such next, next transfer actuator 41 from its position I to II to effect a secondary transfer, its associated toggle spring 51 is moved off center sufficiently to exert a snap action spring force on such transfer actuator in a direction and of sufficient magnitude to propel its corresponding pinion gear 14 into proper final alignment simultaneously with the effecting of the primary and secondary transfers.

During subtractive accumulations, subtractive primary and secondary transfers are effected in a similar manner. To effect subtractive accumulations and transfers, dog eared member is manually rotated clockwise to its subtract position (FIGURE 7), moving toggle springs 51 into a position where they bias their associated transfer actuators 41 against their corresponding stops 57s. Certain of the racks 12 are driven to the right predetermined respective linear distances, corresponding to the amount to be accumulated su'otractively, driving their corresponding pinion gears 14 clockwise corresponding distances, thereby accumulating the amount subtractively therein for storage.

Next assume that a pinion gear 14 is rotated subtractively (clockwise) through its transfer position. Under such circumstances, the subtract side edge of its side tooth 39 engages the right side of the transfer pawl portion 49 of the transfer actuator ill of the next higher order, driving it counter-clockwise from its rest position I to transfer accept position II (FIGURE 7), where it becomes latched to subtract transfer bar 7hr in preparation for effecting a primary transfer. It may be seen that upon pinion gears 14 being moved out of engagement with their corresponding racks I2 and into engagement with their corresponding transfer actuators 41, and upon simultaneous driven movement of the transfer bails 61a, his and their associated transfer bars 78a, '78s from position II to HI, all transfer actuators 41 which are presently locked to subtract transfer bar 78s are moved to position III, reflecting the necessary primary and secondary transfers, in a manner similar to that previously described for additive accumulations; toggle springs 51, during secondary transfers, now acting to urge transfer actuators ll involved in secondary transfers counterclockwise from position I to position II, exerting a snap action, spring force of suflicient magnitude to properly finally align pinion gears 14 simultaneously with the effecting of the primary and secondary transfers.

If it is desired, stop projections 57a, 57s of dog eared member 115 may be omitted, and, during additive accumulations and transfers, subtract bail 61s and its transfer bar '78s disengaged from the bail driving mechanism and held immobile in their rest positions I to act as a stop, limiting counter-clockwise movement of transfer actuators 41; and vice versa, during subtractive accumulations and transfers.

FIGURES 9 and 10 show the subject transfer mechanism slightly modified for use in calculating machines equipped with accumulators of the well known two pinion gear type for algebraic addition. Accumulator 172 is an algebraic type, comprising a pair of constantly intermeshed accumulating pinion gears 14, 15 for each denominational order. The pinion gears are rotatably mounted on fixed pinion shafts 35 on a carriage 1'75. Carriage 175 may be rotated through 180 to pre;ent either of pinion gears 14, 15 to their corresponding racks (not shown) for receiving from the racks the amount to be stored and accumulated. Normally, accumulator 172 is held out of engagement with the racks while the amount to be accumulated and stored by the pinion gears is entered into the racks during e:cape movement of the racks, in a manner similar to that previously described for the add only machine; it being understood however, that for the subject embodiment escape movement of the racks is to the left. Accumulator 172 is then moved into engagement with the racks, and the racks driven to the right to transfer the amount from the racks to their corresponding pinion gears 14, 15 for storage.

With pinion gears 14, 15 in rack engaging position, as shown in FIGURE 9, the amount to be accumulated is added into the pinion gears by the racks driving the top pinion gears 14 clockwise. Upon reversal of carriage 175 through 180", the bottom pinion gears 15 are placed into engagement with the racks and are rotated clockwise thereby to subtract the amount, thus transferred, from the amount previously stored and accumulated in pinion gears 14, 15; the direction of rotation of the respective pinion gears 14, 15 for adding and subtracting being indicated by appropriately dsignated directional arrows. The mechanism for rotating carriage 175 through 180 to present either the add or subtract pinion gears 14, 15, respectively, to the racks, and the mechanism for shifting accumulator 172 into and out of rack engaging position are both well knownin the art and therefore will not be described herein.

Each pinion gear 14, 15 is provided with a side tooth 39. A set of arcuate shaped transfer index levers 177, one for each pair of pinion gears 14, 15 are pivotally mounted intermediate their respective ends on a common fixed shaft 179. The upper arm of each index lever 177 has formed at its end a pawl portion 181 for engaging the side tooth 39 of its corresponding pinion gear (14, 15, as the case may be) when such pinion gear is in rack engaging position. The other arm of each index lever 177 has also formed at its end a pawl portion 183, and is slightly bent in a lateral direction to position pawl portion 183 into engagement with a gear tooth 4'7 of the segmental gear portion 45 of a transfer actuator 41 provided for the next higher order. A set of leaf springs 185 is provided, one for each index lever 177 and fixedly mounted in position to bias its corresponding lever counter-clockwise into side tooth engaging position (shown in FIGURE 9 in solid outline). Transfer actuators 41 are rotatably mounted on a common fixed shaft 43. Spacers 190 (FIGURE 10) are provided on actuator shaft 43, pinion shafts 35 and lever shaft 1'79 to properly align the pinion gears 14, 15, levers 177 and actuators 41 with each other.

The segmental gear portion 45 of each transfer actuator 41 is provided with a side tooth 193, projecting laterally in a direction for engagement with side tooth 39 of the pinion gear (14, 15, as the case may be) provided for v the next lower order, under conditions where accumulator 172 is moved downward into engagement with segmental gear portions 45 of transfer actuators 41.

It may be seen that the remainder of the transfer mechanism of FIGURES 9, 10 is similar in structure and operation to that provided for the previously described add only embodiment shown in FIGURES 1-5, i.e., bail 61 may be driven from position I to 11, carrying transfer bar 78 with it along arcuate guide slots 81. Transfer bar 78 when in position II is efiective by means of its biasing spring 86 and the radial guide slot 76, re cessed portion 95 and camming surface 93 formed in each transfer actuator 41 to lock the transfer actuators 41 which are rotated into transfer accept position, as will be described hereinafter, to bail 61. Bail 61 may then be driven from position 11 to III to effect the primary and secondary transfers simultaneously, as will be described hereinafter. Toggle springs 51, one for each transfer actuator 41 are effected; as was previously described, in response to clockwise movement of their associated trans fer actuators 41 from position I to II to exert individual snap action spring forces on their respective transfer actuators 41 to aid their movement to position II.

Assume that an amount is to be transferred additively from the racks (into which it has been previously entered) into accumulator 172 for storage. Under such conditions, accumulator 172 is in its add position (i.e. with pinion gears 14 in their upper positions) and is moved into engagement with the racks (not shown) while bail 61 is driven clockwise to position 11, carrying transfer bar 78 with it. Next, the racks are driven to the right back to their normally non-operated positions, rotating their corresponding top pinion gears 14 clockwise in accordance with the amount previously entered to transfer such amount to pinion gears 14, in turn, driving their respective inter-meshed bottom pinion gears 15 counter-clockwise like amounts.

Next assume that one of the top pinion gears 14 is rotated by its corresponding rack through its transfer position or are. As such pinion gear 14 moves through its transfer are of 36, its side tooth 39 constantly engages top pawl portion 181 of its associated index lever 177 causing such lever to pivot clockwise (as shown in FIG- URE 9 in broken line outline) about its pivot point against the biasing force of leaf spring 185-. This pivotal movement of index lever 177 positively drives, by means of lower pawl portion 183 of the lever, the transfer actuator 41 for the next higher order clockwise one step into transfer accept position 11, in preparation for a primary transfer. As such transfer actuator arrives at position II, it becomes locked to transfer bar 7 8, as was previously described. In addition, movement of such actuator 41 from position I to position If at the same time causes its toggle spring 51 to be moved off center sufiiciently to exert its spring force in a snap action fashion in a direction to aid clockwise rotation of the transfer actuator.

Next, accumulator 172 is moved into engagement with transfer actuators 41; its bottom pinion gears 15 meshing with the segmental gear portions 45 of their respective corresponding actuators 41. Bail 61 is then driven clockwise from position If to ill to effect the primary transfers by rotating the aforementioned next higher order transfer actuator 41 (presently locked to transfer bar 78) to position HI. Such transfer actuator in rotating clockwise from position II to H1 drives the bottom pinion gear 15 with which it is presently engaged counter-clockwise one step to transfer one unit additively thereto, thereby effecting a primary transfer to the aforementioned next higher order pinion gears.

Next assume that the bottom pinion gear 15 of such next higher order is, in turn, moved through its transfer are by the primary transfer. In such a case, its side tooth 39 engages the side tooth 193 of the transfer actuator 41 for the next, next higher order, driving it clockwise one step from position I to II. Such transfer actuator 41, in turn, rotates the pinion gear 15 of such next, next higher order, with which pinion gear it is presently intermeshed, one step, counter-clockwise effecting a secondary transfer to the next, next higher order pinion gears 14, 15 simultaneously with the previously described primary transfer to the next higher order pinion gears 14, 15. At the same time, toggle spring 51 of such next, next higher order transfer actuator 41, as has been previously described, is moved sufficiently ofi center by rotation of its transfer actuator 41 clockwise frorn'position I to H 15 to apply a snap action spring force to such transfer actuator in a clockwise direction. Toggle springs 51 are selected so as to exert snap action forces of sufficient magnitude to drive the pinion gears l4, 15, with which their respective transfer actuators 41 are intermeshed, into final proper alignment for correct storage of the amount accumulated thereby To prepare the calculating machine for its next operation, accumulator 172 is again disengaged from transfer actuators d1, and hail 61 is driven counter-clockwise through its return stroke back to rest position 1, thereby also returning the previously actuated transfer actuators 41 to rest position I.

It may be seen from FIGURES 9 and 10 of the drawingsthat, upon rotation of accumulator carriage 172 through 180 to present pinion gears to the racks and upon operation of the subject transfer mechanism in a manner similar to that previously described for adding an amount entered to the amount previously stored and accumulated by pinion gears 14, i5, an amount entered into the racks will be subtractively transferred from the racks to pinion gears 14, 15 and any required primary and secondary transfers effected simultaneously with each other and with final properalignment of the pinion gears.

As many changes could be made in the above construction and many apparently widely different embodiments ofthis invention could be made without departing from the scope thereof, it is intended that all matter contained in the above description or shown on the accompanying drawings shall be interpreted as illustrative and not in a limiting sense.

What'is claimed is:

I. In a simultaneously operable transfer mechanism for calculating machine registers having in each denomirrational order a register wheel and a transfer element rotatable therewith through a transfer position; a transfer actuator arranged for driving engagement with-the wheel "of the next higher order and having an integral portion extending into position for rotation of said actuator by said transfer element in a direction opposite to the direction of rotation of said register wheel under conditions where said transfer element is rotated through said transfer position, said transfer element rotating said actuator in said opposite direction from a normal position to a second position; said actuator being furthermore movable in said opposite direction from said second position to third position; a driving bar common to said actuators and operable, during driving engagement of said actuators with their respective higher order wheels, for rotating the actuators positioned in said second position to said third position effecting primary and secondary transfers simultaneously; and a plurality of gear despiraling means individual to said actuators and responsive to movement of their respective actuators from said normal position to said second position, each of said despiraling means effecting proper alignment of the register wheel with which its associated actuator is engaged during a secondary transfer operation.

2 A- transfer mechanism as set forth in claim 1 wherein latching means are provided for establishing individual latching connections between said actuators and said driving bar, said latching means being operatively responsive to rotative movement of their associated actuators from said normal to said second positions under conditions where said actuators are out of driving engagement with their respective higher order wheels.

3. A transfer mechanism as set forth in claim" 1 wherein said plurality of gear despiraling means individual to said actuators each includes a toggle spring operably connected to its associated actuator and maintained in compression, said toggle spring being effective, upon movement of its associated actuator from said normal position towards said second position, to apply a snap action spring force to said associated actuator aiding such movement.

4, In a simultaneously operable transfer mechanism for calculating machine registers having in each denomirrational order a register wheel and a transfer element rotatable therewith through a transfer position; a transfer actuator arranged for driving engagement with the wheel of the next higher order and having an integral portion extending into position for rotation by said transfer element in a direction opposite to the direction of rotation of said register Wheel; said transfer actuator, under conditions where said transfer element rotates through said transfer position and said actuator is disengaged from its associated wheel, being rotated in said opposite direction from a normal position to a set position for conditioning a primary transfer operation; said actuator being furthermore movable from said set position to third position in said opposite direction; said actuator when in normal position and during engagement with said higher order wheel and, under conditions where said element of the next lowerregister wheel is rotated through said transfer position, being moved by said next lower element into said set position simultaneously with said rotation to effect a. secondary transfer operation; a driving bar common to said actuators and operable during driving engagement of the actuators with their respective higher order wheels, for rotating in said opposite direction the actuators so set for a primary transfer; and a plurality of gear despiraling means individual to said actuators and responsive to movement of their respective actuators from said normal position to said set position, each one of which despiraling means effects proper alignment of the register wheel with which its associated actuator is engaged during a secondary transfer operation.

5. A simultaneously operable transfer mechanism for calculating machine registers comprising; in each denominational order, a register pinion gear and a transfer element rotatable therewith through a transfer position; a plurality of transfer actuators, one for each of said pinion gears, said actuators each having a segment gear portion intermeshable with the pinion gear of the next higher order and a pawl portion engageable with said transfer element of the pinion gear for which it is provided as such transfer element rotates through transfer position; said actuators, during disengagement with their respective said higher order pinion gears, being settable in a direction opposite to the direction of rotation of said pinion gear by such engagement from a normal position to a set position for conditioning primary transfer operations; said actuators when in normal position and during engagement with their respective said higher order pinion gears also being settable by such engagement from said normal to said set position simultaneously with said rotation of their associated said elements through transfer position to effect secondary transfer operations; said actuators being furthermore movable from said set position to a third position in said opposite direction; and a driving bar com mon to said actuators and operable, under conditions where said actuators are in engagement with their respective higher order pinion gears, for driving in said opposite direction to said third position the actuators so set; and a plurality of gear despiraling means, one for each of said actuators and responsive to movement of its associated actuator from said normal position to said set position for effecting proper alignment of the higher order pinion gears with which such associated actuator is engaged during a secondary transfer operation.

6. In a simultaneously operable transfer mechanism for calculating machine registers having, in each denominational order, an accumulator mechanism including at least one pinion gear adapted for rotative movement for storing the input in its order and a transfer element rotatable with said pinion gear through a predetermined transfer are; a transfer lever engageable throughout said are by said transfer element and driven thereby; a transfer actuator engageable with the pinion gear of the next higher order, said actuator, during disengagement with said higher order pinion gear, being settable by driven movement of said transfer lever from a normal position to a set position in a certain direction for conditioning a primary transfer operation; said actuator being furthermore movable from said set position to a third position in said certain direction; said actuator also having a portion which, when the actuator is in normal position and in engagement with said higher order pinion gear, is engageable by said transfer element and, under conditions where said transfer element is rotated through said predetermined transfer arc, said portion drives the actuator into said set position simultaneously with said rotation to effect a secondary transfer operation; and a driving bar common to said actuators for driving the actuators so conditioned for a primary transfer to their respective third positions during engagement with their respective higher order pinion gears and, in turn, simultaneously effecting secondary transfers.

7. A transfer mechanism as set forth in claim 6 wherein latching means individual to said actuators are pro vided, said latching means being responsive to rotative movement of their respective associated actuators to said set position for establishing latching connections between said driving bar and the actuators conditioned for primary transfer erations as the latter arrive at said set position.

8. In a simultaneously operable transfer mechanism for calculating machine registers having in each denominational order a register wheel and a transfer element rotatable therewith through a certain arcuate distance in a first certain direction; a transfer actuator arranged for driving engagement and disengagement with the wheel of the next higher order; a transfer lever engageable by said element throughout said arcuate distance, under conditions where said actuator is disengaged from its asso ciated wheel; said transfer lever being operable when so engaged to rotate said actuator through said certain arcuate distance in a direction opposite to said first certain direction from a normal position to a set position for conditioning a primary transfer operation; said actuator being furthermore movable from said set position to a third position in said opposite direction; said actuator also having a portion which, when the actuator is in normal position and in driving engagement with said higher order Wheel is engageable by said transfer element, said portion, under conditions where said transfer element is rotated through said certain arcuate distance, drives said actuator into said set position simultaneously with said rotation to effect a secondary transfer operation; and a transfer bar common to said actuators, said transfer bar being operable, under conditions where said actuators are in driving engagement with their respective higher order wheels, for rotating in said opposite direction the actuators so set; and a plurality of gear despiraling means individual to said actuators and responsive to movement of their respect actuators from their respective said normal to said set positions for effecting proper alignment of the register wheels with which their respective associated actuators are in driving engagement during a secondary transfer operation.

9. In a simultaneously operable transfer mechanism for calculating machine registers having in each denominational order a register pinion gear and a transfer element rotatable therewith through a transfer position in a first certain direction; a transfer lever rotatable by said element in a direction opposite to said first certain direction; a transfer actuator intermeshable with the pinion gear of the next higher order, said actuator, during disengagement with said higher order pinion gear, being settable in said opposite direction by said lever from a normal position to a set position for conditioning a primary transfer operation; said actuator being furthermore movable from said normal position to a second position in said opposite direction; said vactuator, when in normal position and during engagement with said higher order pinion gear, having a portion engageable by said element 18 upon rotation through transfer position for moving the actuator into said second position simultaneously with said rotation to effect a secondary transfer operation; and a driving bar common to said actuators, said driving bar being operable, under conditions Where said actuators are in engagement with their respective higher order pinion gears, for rotating in said opposite direction the actuators so set; and a plurality of gear despiraling means individual to said actuators and responsive to movement of their respective actuators from said normal position to said set position, each of said despiraling means effecting proper alignment of the register wheel with which its associated actuator is engaged during a secondary transfer operation.

1-0. A transfer mechanism for a plurality of denominational orders for calculating machine registers for simultaneously transmitting calculated amounts between such orders for storage in accordance with predetermined transfer points between successive orders; said transfer mechanism in each denominational order comprising; an accumulator mechanism including at least one pinion gear rotatable predetermined amounts in proportion to the parts of its denominator to be registered for storing such parts input; a transfer element rotatable with said pinion gear through a certain associated transfer position; a transfer actuator engageable in driving relation with the pinion gear provided for the next higher order for driving such next higher pinion; a transfer lever actuatable by said transfer element under conditions where said transfer element is rotated through said certain transfer position during disengagement of said actuator with said next higher order pinion gear; said transfer lever, when so actuated, actuating said actuator from a normal position to a set position in a certain direction for conditioning a primary transfer operation; said actuator being furthermore movable from said set position to a third position in said certain direction; said actuator having a portion which, when said actuator is in normal position and in driving engagement With said higher order pinion gear, is engageable by said transfer element; said actuator upon rotation of said transfer element through transfe' position being driven thereby to said set position simultaneously with said rotation and driving its associated next higher order pinion gear to effect a secondary transfer operation; a driving bar common to said actuators, said driving bar being operable during engagement of said actuators with their respective higher order pinion gears, for driving the actuators so conditioned for primary transfers from their respective set positions to their respective third positions, and, in turn, simultaneously effecting said secondary transfers; and gear despiraling means, one for each of said actuators and operatively responsive to movement of its associated actuator from said normal toward said set position for applying forces thereto aiding such movement.

11. In a simultaneously operable transfer mechanism for calculating machine registers having in each denominational order; a storage mechanism including at least one register pinion gear arranged for rotative movement predetermined discrete amounts in proportion to certain corresponding inputs received by said machine; said register pinion gear having a laterally extending member rotatable therewith through a predetermined transfer position for effecting a transfer of the accumulated input stored on the register gear to the storage mechanism provided for the next higher order; a longitudinal member mounted in position for actuation through a certain arcuate distance by said laterally extending member, under conditions where the latter is rotated through said transfer position; a segmental gear adapted for rotative engagement with the register gear of the next higher order and being conditioned from a first to a second position by actuation of said longitudinal member in preparation for a primary transfer operation, said segmental gear having a laterally extending lug engageable by said laterally extending member, upon rotation of said extending member through said transfer position, for effecting a secondary transfer operation simultaneously with said rotation; a transfer bar common to said segmental gears and effective, under conditions where said register gears are in engagement with their respective segmental gears, for rotating the register gears so conditioned for a primary transfer a certain amount to effect said primary transfer and simultaneousiy therewith secondary transfers to the next, next higher order; and a plurality of spring means, one for each of said segmental gears and operably connected thereto, said spring means being effective, uponrotation of the segmental gear for which it is provided from said first toward said second position, for applying despiraling forces through said segmental gears to their associated engaged register gears to correctly align the register gears registering the secondary transfers.

1 2. A transfer mechanism as set forth inrclaim 11 wherein said segmental gears are each provided with a transfer bar engaging side edge surface including a transfer bar receiving cut-out portion defined therein, and said transfer bar is yieldably mounted for limited radial movement with respect to said segmental gears and spring biused against said side edge surface for radial movement into said cut-out portions establishing individual latch ing connections between said transfer bar and the saidv in each denominational order are formed integral one with the other.

14. In a simultaneously operable transfer mechanism for calculating machine registers having, in each denomi-v national order; a storage mechanism including at least one register gear for accumulating certain inputs associated with its order, such register gear being arranged for rotative movement into a plurality of predetermined input storage, positions in accordance with the said associated inputs received by the machine, said register gear having a laterally extending member rotatable therewith through a predetermined transfer arc for effecting transfer of the accumulated input stored on the register gear to the storage mechanism provided for the next higher order; a segmental gear adapted for inter meshing engage" ment with the register gear of the next higher order; a longitudinal member pivotably mounted in position for constant driven engagement with said extending member under conditions where the latter is rotated through said transfer are and said segmental gear is disengaged from its associated register gear; said segmental gear being driven by said longitudinal member from a first to a second position in preparation for a primary transfer operation, vsaid segmental gear having a laterally extending lug engageable by said extending member upon rotation through said transfer are, under conditions where said segmental gear is intermeshed with its associated register gear, for effecting a secondary transfer operation simultaneously with said rotation; a driving bar common to said segmental gears and effective, under conditions where said register gears are in engagement with their respective segmental gears, for rotating the prepared'register gears. insaid second position a certain amount to effect said primary transfers and simultaneously therewith secondary transfers to the next, next higher order, and a plurality of spring means, one for each of said segmental gears and operably connected thereto, said spring means being effective upon rotation of the segmental gear for which it is provided from said first to said second position, for applying despiraling forces through said segmental gears to their assoicated inter-meshed register gears to correctly align the register gears registering secondary transfers.

' 15. A transfer mechanism as set forth in claim 14 wherein said segmental gears are each provided with a driving bar engaging side edge surface including a drivingbar receiving cut-out portion defined therein, said driving bar is spring biased in a radial direction towardsthe axis of rotation of said segmental gears for movement into said cut-out portions for locking thesaid segmental gears conditioned for aprimary transfer operation to said driving bar asisuch conditioned gears arrive at said second position, and wherein said transfer mechanism is provided effective after completion of said simultaneous transfers for driving said segmental gears-back to said first position, said cam slot being configurated to cause actuation of said driving bar out of said locking engagement with said segmental gears'as said driving bar moves past said second position during segmental gear restoring operation.

16. A transfer mechanism for a plurality of denominational orders for calculating machine registers for simultaneously transmitting calculated amounts between such orders for storage in accordance with predetermined transfer points between successive orders; said transfer mechanism comprising; in each denominational order an accumulator mechanism including a pair of constantly inter-meshed pinion gears rotatable predetermined amounts in proportion to the parts of the denominator of their order to be registered for storing such parts input; two transfer elements, one for each pinion gear, rotatable with said pinion gears through a certain associated trans for position; a transfer actuator engageable in driving re-' lation with one pinion gear of the pair provided for the next higher order for driving such next higher pair of pinion gears; a transfer lever actuatable by the transfer? element of theopopsed gear of the pair associated with its order-under conditions where such transfer element is rotated through said certain transfer position during disengagement of said actuator with said one next higher order pinion gear; saidtransfer lever,- when so actuated, actuating said actuator from a normal position to a set position in a certain direction for conditioning a primary transfer operation; said actuator being furthermore movable from said set position to a third position in said certain direction; said actuator having a portion which, when said actuator is in normal position and in driving engagement with said one higher order pinion gear, is engageable by the transfer element opopsed to the transfer ele-. m-ent operating said lever; said actuator upon rotation of said opopsed transfer element through transfer position being driven thereby to said set position simultaneously with said rotation and driving its associated said one next higher order pinion gear to effect a secondary transfer operation; a driving bar common to said actuators, said driving bar being operable during engagement of said actuators with their respective said one next higher order pinion gears, for driving the actuators so conditioned for primary transfers fro-m their respective set positions 4 to'their respective third positions, and, in turn,v simultaneously effecting said secondary transfers; and gear despiraling means, one for each of said actuators and operatively responsive to movement of its associated actuator from said normal toward said set position for applying forces thereto aiding such movement.

17. A simultaneously operable transfer mechanism for calculating machine registers comprising; in each denominational order, a register pinion gear and an associated transfer element rotatable therewith through a transfer position, saidregister pinion gear and associated transfer element being rotatable in unison in a first direction for additive register operations and in a second direction opposite thereto for subtractive register operations; a transfer actuator having a segment gear portion inter-V Imeshable with the pinion gear of the next higher orderv and a pawl portion engageable with said associated trans:

fer element under conditions Where such transfer element rotates through transfer position; said actuator, during disengagement with'its respective said higher order pinion gear being settable by such transfer element engagement from a normal position to a set position in a direction opposite to the direction of rotation of such associated transfer element to condition additive and subtractive primary transfer operations; said conditioned actuator being further movable from said set position to a third position in said direction opposite to the direction of rotation of such associated transfer element; said actuator when in normal position and during engagement with said higher order pinion gear also being settable by such transfer element engagement from said normal to said set position in a direction opposite to the direction of rotation of such associated transfer element to effect additive and subtractive secondary transfer operations; a pair of driving bars common to said actuators and operable in opposite rotative directions one to the other, said oars, under conditions where said actuators are in engagement with their respective higher order pinion gears, being effective for driving said conditioned actuators from said set position to said third position efiecting additive and subtractive primary and secondary transfers.

18. A simultaneously operable transfer mechanism for calculating machine registers comprising; in each denominational order, a register pinion gear and an associated transfer element rotatable therewith through a transfer position, said register pinion gear and associated transfer element being rotatable in unison in a first direction for additive register operations and in a second direction opposite thereto for subtractive register operations; a transfer actuator having a segment gear portion intermeshable with the pinion gear of the next higher order and a pawl portion engagea-ble with said associated transfer element under conditions where such transfer element rotates through transfer position; said actuator, during disengagement with its respective said higher order pinion gear being settable by such transfer element engagement from a normal position to a set position in a direction opposite to the direction of rotation of such associated transfer element to condition additive and subtractive primary transfer operations; said conditioned actuator being further movable from said set position to a third position in said direction opposite to the direction of rotation of such associated transfer element; said actuator when in normal position and during engagement with said higher order pinion gear also being settable by such transfer element engagement from said normal to said set position in a direction opposite to the direction of rotation of such associated transfer element to effect additive and subtractive secondary transfer operations; a pair of driving bars common to said actuators, one of said bars for additive transfers and the other for subtractive transfers, said bars being operable, under conditions where said actuators are in engagement with their respective higher order pinion gears, said one bar for driving actuators conditioned for additive transfer from said set position to said third position, in a direction opposite to said first direction, and said other bar for driving actuators conditioned for subtractive transfer from said set position to said third position in a direction opposite to said second direction, and gear despiraling means, one for each of said actuators and responsive to movement of its associated actuator from said normal to said set position during additive and subtractive secondary transfer operations for effecting proper alignment of the higher order pinion gear then engaged with said associated actuator, said gear despiraling means being selectively conditionble for effecting such proper alignment during additive and subtractive transfers.

Horton Nov. 11, 1930 Reynolds Nov. 16, 1954

Claims (1)

1. IN A SIMULTANEOUSLY OPERABLE TRANSFER MECHANISM FOR CALCULATING MACHINE REGISTERS HAVING IN EACH DENOMINATIONAL ORDER A REGISTER WHEEL AND A TRANSFER ELEMENT ROTATABLE THEREWITH THROUGH A TRANSFER POSITION; A TRANSFER ACTUATOR ARRANGED FOR DRIVING ENGAGEMENT WITH THE WHEEL OF THE NEXT HIGHER ORDER AND HAVING AN INTEGRAL PORTION EXTENDING INTO POSITION FOR ROTATION OF SAID ACTUATOR BY SAID TRANSFER ELEMENT IN A DIRECTION OPPOSITE TO THE DIRECTION OF ROTATION OF SAID REGISTER WHEEL UNDER CONDITIONS WHERE SAID TRANSFER ELEMENT IS ROTATED THROUGH SAID TRANSFER POSITION, SAID TRANSFER ELEMENT ROTATING SAID ACTUATOR IN SAID OPPOSITE DIRECTION FROM A NORMAL POSITION TO A SECOND POSITION; SAID ACTUATOR BEING FURTHERMORE MOVABLE IN SAID OPPOSITE DIRECTION FROM SAID SECOND POSITION TO THIRD POSITION; A DRIVING BAR COMMON TO SAID ACTUATORS AND OPERABLE, DURING DRIVING ENGAGEMENT OF SAID ACTUATORS WITH THEIR RESPECTIVE HIGHER ORDER WHEELS, FOR ROTATING THE

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