US2628029A - Broido - Google Patents

Description

Feb. 10, 1953 D. BROIDO 2,628,029

TRANSFER MECHANISM FOR CALCULATING MACHINES Filed Dec. 26, 1951 5 Sheets-Sheet l min Inventor Attorney 5 Sheets-Sheet 2 I03 pl 2 Inventor .Feb. 10, 1953 D. BROIDO TRANSFER MECHANISM FOR CALCULATING MACHINES 5 Sheets-Sheet 5 Filed Dec. 26, 1951 Inventor B j M Attorney Feb. 10, 1953 D. BROIDO 2,628,029

TRANSFER MECHANISM FOR CALCULATING MACHINES Filed Dec. 26, 1951 5 Sheets-Sheet 4 Fig 5.

Inventor y W M Attorney I30 I27 I27 Inventor B j M Altorney 5 Sheets-Sheet 5 Feb. 10, 1953 D BROIDO TRANSFER MECHANISM FOR CALCULATING MACHINES Filed Dec. 26, 1951 *i /57 /5s a] Patented Feb. 10,1953

TRANSFER MECHANISM FOR CALCULATING MACHINES Daniel Broido, Barnet, England Application December 26, 1951, Serial No. 263,177 In Great Britain January 2, 1951 6 Claims.

This invention relates to adding, accounting, 5

calculating and like machines, and more specifically to tens transfer or carry devices of the totalizers employed in such machines.

In order to speed up the operation of such devices it has been previously suggested to use a method known as Plus One Minus One. In a mechanism based on this method, unity is added in all orders or the totalizer simultaneously after an additive value-entering operation; then unity is subtracted simultaneously in all orders which do not require a carry. After a subtractive valueentry, unity is subtracted in all orders, and then added in those orders which do not require a carry. In a mechanism of this type the carry can be eiiected faster than in the conventionalstaggered type carry devices, which require a timed sequence of carries from the lower orders to the higher orders of the totalizer.

This invention contemplates a method of simultaneous carry in all totalizer orders in a manner which is faster and more convenient than that of the Plus One Minus One method. This novel method provides means for checking the totalizer orders which require a conditional carry after a value-entering operation; thus, it may be conveniently termed the Check method of carry.

In particular, this invention contemplates a method of simultaneous carry suitable with but few minor alterations both for machines of the type referred to wherein digital values 0 to 9 are entered into various totalizer orders during the value-entering operation in a conventional manner, and also for machines of the type referred to wherein the digital values to be entered into various totalizer orders are each increased by unity, for instance as described in the specificat cn to my co-pen-ding application No. 263,176.

The main object of this invention is to provide a carry device which is relatively simple in construction and speedy in operation.

Another object is to provide a method and means for effecting the carry by one single operation simultaneously in all totalizer orders.

More specifically, an obiect of the invention is to provide means for checking the totalizer orders which stand either at 9 or at 0 after a value-entering operation, according to whether this operation was additive or subtractive, and thus require a conditional carry.

Another specific object is to provide storage means for definite carry impulses, and means for interlocking the storage means of adjacent totalizer orders.

An object of the present invention is to provide a carry device suitable, with but minor adjustments, both for totalizers which receive true values and for totalizers which receive values increased by unity.

Other objects will become apparent as the description proceeds.

With these objects in view, a method of carry according to the present invention comprises a storage of definite carry impulses produced during a value-entering operation, a check of totalizer orders which have to transmit these definite carry impulses, and a simultaneous application of a one-step movement to all totalizer orders which require a carry, in a direction depending on whether the value-entry was additive or subtractive.

Means for carrying this method into efiect comprise, in operative association with each totalizer order, carry storage means operable when the associated order moves from 9 to 0 in addition and from 0 to 9 in subtraction, check means operable after a value-entering operation for indicating whether the associated order stands at 9 or 0, depending on the direction of the valueentry, interlock means controlled by said check means for interlocking the said carry storage means of adjacent orders, and driving means controlled by the said carry storage means for driving the individual totalizer orders simultaneously one step in the direction depending on that of the value-entry.

Considering first an additive value-entering operation:

it is evident that the units order has produced a definite carry impulse; it may be termed a Sending order. The tens order may be termed a Transmitting order; it has produced a carry impulse merely due to the fact that it is next-higher to a Sending order. Similarly, the hundreds order is a Transmitting order; it has produced a carry impulse because it is chain-higher to a Sending order (units). It may be stated that if an order stands at 9 after an additive value-entry, it is a Transmitting order; it produces a carry impulse conditional on this order being chainhigher or next higher to a Sending order.

Similarly, when an order moves from 0 to 9 during subtraction, it produces a definite carry impulse and may be termed a Sending order. An order which stands at 0 after a subtractive value-entry may be termed 9. Transmission order; it produces a carry impulse conditional on this order being chain-higher or next-higher to a Sending order.

The present check method of carry contemplates an arrangement whereby the definite carry impulses produced during a value-entering operation are stored; after the value-entering operation all totalizer orders are checked to determine which are Transmitting orders and which Transmitting orders are next-higheror chain-higher to Sending orders; the carry is eiiected simultaneously in all orders which receive a definite carry impulse (from a Sending order) or a conditional carry impulse (from a Transmitting order chain-higher to a Sending order), by moving these orders one step in, the required direction.

Thus, the above example may be treated as follows:

9 0 9 9 9 Totalizer stand before value-entry. 2 Value-entering operation.

9 0 9 9 1 Totalizer stand after value-entry. t t t s Check (t=lransmitting order, s= Sending order). l 1 1 Carry operation.

9 l 0 0 l Totalizer stand after carry.

In subtraction the operation may be as follows:

Totalizer stand before value-entry. Value-entering operation.

Total zer stand after value-entry. heck. Carry operation.

hdo 1 0 8 9 8 Totalirer stand after carry.

Considering now the arrangement whereby the di tal values to be entered into various totalizer orders are each increased by unity, it will be se n that the carry must take place in reverse; that is, after a value-entering operation those orders which do .not require a carry must be moved one step in the direction opposite to that of the value-entry.

Considering the above additive example, the procedure is as follows:

Considering the above subtractive example, the procedure in the case of totalizers which receive values increased by unity is as follows:

- 1 0 9 0'0 Totalizer stand before value-entry. l 1 l 1 3 Value-entering operation (actual value: 2).

0 9 8 9 7 Totalizer stand after value-entry.

t t s Check. l l O O 1 Carry operation.

1 0 8 9 8 Totalizer stand after carry.

It will be seen that in the case of totalizers which receive values increased by unity a Sending order is one which has moved, in addition, from 9 to 0 and beyond, while a Transmitting order is one that has moved from 9 to 0 and has remained at 0. Similarly, in subtraction a'Sendracks 20 with the gears H.

4 ing order has moved from 0 to 9 and beyond, while a Transmitting order has moved from 0 to 9 but not beyond.

The present invention will now be described, firstly as applied to totalizers which receive values increased by unity, and secondly as modified to suit totalizers which receive true values.

In the accompanying drawings illustrating a preferred embodiment of the present invention: 7 Figure 1 is a vertical section, taken substantially on line I-I of Figure 2, showing the carry device in an inoperative or non-carrying position,

Figure 2 is a vertical section substantially on line IIII of Figures 1 and 6,

Figure 3 is a view in the direction of arrow III in Figure 1, the machine cover being removed,

Figure 4 is a section similar to Figure 1 but showing the carry device in the carrying position,

Figure 5 is a vertical section substantially on line V V of Figure 2, showing part of the operating mechanism,

Figure 6 is a vertical section substantially on line VI-VI of Figure 2, showing another part of the operating mechanism, and

Figure 7 is a section similar to that of Figure 1 but showing a modified carry device.

Referring to Fig. 1, the totalizer Wheels ill are rotatably mounted on a shaft H suitably supported in the machine structure 12, I3, Fig. 2; they are visible through suitable apertures in the machine cover 14, Figs. 1 and 4. Fixed to each totalizer Wheel 10 is a pinion I5 and a carry lug [5. Each pinion i5 meshes with a gear ll rotatable on a shaft I8 fixedly supported in the machine structure. Gears II are operatively associated with difierentially displaceable racks 20 more fully described in the specification to my co-pending patent application No. 263,176. It is sufiicient to state here that racks 20 are movable by springs I9 in guides 2|, 22, 23, 24 under the control of a drive bar 25 which normally holds the racks in a retracted position shown in Fig. 1. When the drive bar 25 moves to the left as viewed in Fig. 1, each spring 19 pulls its associated rack 20 to the left until its tip 28 abuts against one of the stops of a set generally indicated at 0-9. Each of the stops 0-9 is individually and selec tively settable or movable into the path of the associated rack 20, and each stop is so positioned and dimensioned that the distance between the stop and the tip 26 of rack 20 is equal to the digit associated with the stop plus unity. Thus, there is a gap equal to one rack step (which is proportionate to the spacing of the totalizer wheels I0) between the 0 stop and the tip 26 of rack 20 when the latter is in the retracted position; the distance between the I stop and the rack is equal to two rack steps, and so on, the distance between the 9 stop and the end of rack being equal to ten rack steps. Thus, when a rack 20 moves from its retracted position onto one of stops 0-9, the rack movement is representative of the value associated with the respective stop plus unity.

Means for selectively setting stops representative of various digital values are well known in the art; for instance, reference may be had to my British patent specification No. 577,330.

Idler gears 21 rotatably mounted on a shaft 28 secured in a support 29 serve to interconnect the As shown in Fig. 2, the width of an idler 21 is substantially equal to the combined width of a rack 29 and gear 17. Prior to an additive value-entering operation the idler shaft 28 is raised so as to mesh the idlers 21 with the associated gears I1 and racks when the drive bar 25 moves to the left as viewed in Fig. 1, racks 26 rotate their idlers 21, and each idler drives the associated gear I! and totalizer wheel l6 through a distance representative of the respective stops 6-9 plus unity, whereby the totalizer wheels I3 are rotated additively in the anti-clockwise direction. At the end of forward stroke of bar 25 the idler shaft 28 is lowered, so that idlers 21 are demeshed from racks 20 and gears H; as now the drive bar 25 is moved to the right as viewed in Fig. 1, it restores the racks 23 to their retracted position while the totalizer wheels Ill remain stationary.

During a subtractive value-entering operation the idler shaft 28 is not raised until the drive bar 25 reaches the end of its forward stroke; only then are the idlers 2T meshed with gears I! and racks 23, so that the totalizer wheels ||l are rotated subtractively in the clockwise direction during the return stroke of racks 20.

A carry pawl 33 rockable on shaft I8 is associated with each carry lug It, on to which it is biased by a spring 3|. An arm 32 on each carry pawls co-acts with a storage plate 33 rockable on shaft 34 fixedly supported in the machine structure. Each storage plate 33 has a lug 35 supporting the end of a striker 36 rockable on shaft 37! secured in a support 36. Each striker 36 is biased by a spring 36 and presses the associated storage plate 33 towards a restoring bar 40; however, storage plates 33 are normally latched by arms 32 of carry pawls 30. If a totalizer wheel l8 moves from 9 to 0 during addition, or if it moves from 0 to 9 during subtraction, its carrying lug I6 causes the associated carry pawl 36 to rock anti-clockwise, and the arm 32 delatches the associated storage plate 33 which rocks slightly clockwise on to restoring bar 40 due to spring 39. In this manner, carry impulses received from Sending and Transmittin orders are stored.

As previously explained, it is necessary to differentiate between Sending orders (that is, totalizer wheels l0 which have moved from 9 to 0 and beyond in addition or from 0 to 9 and beyond in subtraction) and Transmitting orders (that is, totalizer wheels which have moved from 9 to 0 and have remained at 0 during addition, or from 0 to 9 and have remained at 9 during subtraction). To this end, each totalizer Wheel l6, except that of the lowest order, is associated with a check rocker 4| mounted on a shaft 42 slidably and rockably supported in the machine structure. Each rocker 4| is biased by a torsion spring 43 towards the respective totalizer wheel l0; one end of the spring passes through a hole in the hub 44 of the rocker and is secured in a hole of shaft 42, thus normally preventing the rocker from touching the totalizer wheel. A recess 45, Fig. 3, is provided on the right-hand side of the rim of each totalizer wheel ID in such an angular position that it is located opposite the end of check rocker 4| when the wheel is at 0. A similar recess 46 is provided on the lefthand side of each totalizer wheel in angular alignment with the check rocker whenthe wheel is at 9. After an additive value-entry the check shaft 42- is axially located, in a manner to be described in due course, so that the check rockers 4| are aligned with the 0 recesses45, as shown in dotted lines in Fig. 3, whereupon the shaft is rocked anti-clockwise as viewed in Fig. 1; if a rocker finds a recess, it rocks into it, otherwise the rocker does not rock appreciably, being arrested by the circumference of the totalizer wheel I 0. Similarly, after a subtractive valueentry the check shaft 42 is shifted so that the check rockers 4| are transversely aligned with the 9 recesses 46, as shown in full lines in Fig. 3; when the shaft is rocked anti clockwise those rockers which are angularly aligned with recesses 46 rock out appreciably while the other rockers remain substantially stationary. In this manner, rockers 4| check the positions of the associated totalizer wheels l0 and ascertain which wheels stand at 0 after an additive value-entry or at 9 after a subtractive value-entry, that is, which wheels belong to Transmitting orders.

Each check rocker 4| has a pin 41 co-acting with a latch 48 rockable on a shaft 49 fixedly supported in the machine structure. Each latch 48 is biased by a spring 50 into engagement with a trigger 5| rockable and slidable on a shaft 52 fixed in the machine structure. Normally each latch 48 latches its associated trigger 5| in the position shown in Fig. 1. However, if the respective check rocker 4| has rocked out during the checking operation just described, pin 41 has caused its latch 48 to delatch its trigger 5|, which now swings anti-clockwise due to its spring 53 into position indicated in Fig. 4. Immediately after the checking operation the check shaft 42 is restored clockwise, thus restoring the check rockers 4|, whereby pins 41 allow the latches 48 to return to their normal position; however, previously delatched triggers 5| remain in the delatched position for the purpose presently to be described.

As previously stated, it is necessary to differentiate between those Transmitting orders which are chain-higher to a Sending order and those which are not; this differentiation is effected by triggers 5|, each of which has a nose 54 co-acting with a lug 55 on the associated storage plate 33 and with a lug 56 on the storage plate 33 of the next-lower order. Lugs 55, 56 are arranged axially adjacent each other on storage plates 33 of adjacent orders, a trigger 5| being of a width substantially equal to the combined width of two adjacent lugs 55, 56, as clearly shown in Fig. 2. There is an angular gap between the associated lugs 55, 56, as clearly shown in Fig. l, the nose 54 of each trigger 5| being normally positioned just above this gap. On being delatched by its latch 48, a trigger 5| rocks as described, so that its nose 54 enters the gap between lugs 55, 56 on associated storage plates 33 of adjacent orders, as shown in Fig. 4. Thus, triggers 5| establish a chain or cross-connection between adjacent totalizer orders.

After the checking operation of rockers 4| the storage restore bar 40 is caused to move clockwise, by means to be described in due course, and in consequence some of storage plates 33 also rock clockwise due to springs 39, namely those 'storage plates which (a) have been previously delatched by their carry pawls 30 and (b) are not prevented from doing so by their triggers 5|. Indeed, if a trigger 5| has interposed its nose 54 between lugs 55, 56 of two adjacent storage plates 33, the storage plate of the higher order can rock into position indicated in Fig. 4 only if the storage plate of the next-lower order rocks, too. However, if the storage plate of the nextlower order does not rock, because it does not belong to a Sending order and has not been delatched during the value-entering operation, then the trigger 5| prevents the storage plate 33 of the next-higher order from rocking and this 'plate, although delatched, remains substantially stationary in the position of Fig. 1. If a number of adjacent storage plates 33 belong to Transmitting orders, they will all be interconnected by their triggers as described. It will be noted that the storage plates 33 and the strikers 36 of all totalizer orders which require a carry rock out when the restore bar 40 is rocked clockwise, while the storage plates and strikers of all orders which do not require a carry remain substantially stationary.

Each gear :1, except that of the units order, coacts with a gear segment 5'! rockable on a shaft 53 secured in a support 59; each segment 51 is located by a ball 66 biased by a spring 6 I. Prior to the carry operation the gear segment support 59 and the idler gear support 29 are so moved, by means to be described in due course, that the gear segments 5'? are meshed with, and the idler gears 21 are demeshed from, the gears I1 driving the totalizer wheels l0.

Each gear segment 51 has a stud 62 normally located in a grooved pawl 63 rockable on shaft 31 in association with a striker 36. If a striker 36 has not rocked out as described and has remained in the position shown in Fig. 1, stud 62 remains in engagement with the pawl 63 even after the respective gear segment 51 has moved into mesh with its gear ll. However, if the striker is associated with a totalizer order requiring a carry and has rocked as described into position shown in Fig. 4, then the pawl 63 clears the stud 62 when the associatedgear segment 51 ismeshed with gear ll. Thus, after the gear segments 51 have been meshed with gears H, the segments remain in operative connection with pawls 63 only in those totalizer orders which do not require a carry.

At the end of an additive operating cycle the striker support 38 is moved, by means to be described in due course, substantially downwards. Thereby those striker pawls 63 which have remained in engagement with their gear segments 51 cause the latter to rock clockwise and to advance the respective totalizer wheels In one step clockwise, that is subtractively. In this manner the unity entered into all totalizer orders during the value-entering operation in excess of the actual amount to be added is now subtracted, as a carry is not required in these orders. Those pawls 63 which have been previously disengaged from their gear segments 51 move down idly; unity is not subtracted in these totalizer orders, that is, the carry is eifected.

.Similarly at the end of a subtractive cycle the striker support 33 is moved upwards, and those striker pawls 63 which have remained in engagement with studs 62 on gear segments 51 rock the latter one step anti-clockwise and thus advance the respective totalizer wheels [6 anti-clockwise, that is additively, in order to cancel the unity previously entered into these orders in excess of the actual amount to be subtracted, as a carry is not required in these orders. Those striker pawls which have been disengaged from their gear segments move up idly and the excess unity remains in these orders, thus effecting the carry.

Prior to the next value-entering stroke of racks 29 the storage restore bar 46 moves anti-clockwise and restores the storage plates 33, the strikers 36, and the pawls 63, whereupon the gear segments 51 are demeshed from gears l1; studs 62 on previously rocked gear segments re-engage their associated pawls 63. Prior to the next carry operation'the striker support '38 is restored to its normal position, thus restoring the strikers 36, the striker pawls 63, and the previously rocked gear segments 51. Each striker pawl 63 is connected to its associated striker 36 by a spring 64. If a gear segment 51 has remained stationary during the carry stroke of strikers 36, the respective pawl 63 during return stroke rocks out slightly, whereupon the spring 64 causes the pawl to re-engage the stud 62 of the gear segment.

It may happen that a totalizer wheel l0 actuates its carry pawl 30 during the carry stroke of strikers 36; this would delatch the associated storage plate 33 and the striker pawl 63 would drop out of engagement with stud 62 before the completion of the one-step movement of gear segment 51. In order to prevent this occurrence. each striker 36 is provided with a slot 65 engaged by a lug 66 of a rocker 61 mounted at 68 and normally maintained in the position shown in Figs. 1 and 4 by a spring 69 anchored in a block 10. Slots 65 are so shaped that before the carry stroke starts the strikers 36 can rock freely into carry position shown in Fig. 4; springs 69 permit their rockers 6! to follow the subsequent movement of strikers 36. However, if a striker 36 has remained in the no-carry position of Fig. 1, its rocker 61 will prevent a rocking movement of the striker during the carry stroke of striker support 38.

The storage restore bar 40 restores the storage plates 33 sufiiciently for carry pawl arms 32 to latch thev storage plates, whereupon it moves slightly back into position shown in Fig. 1. As the storage plates 33 are being restored, they shift across the trigger shaft 52 those triggers 5| which have previously been in action, whereupon a trigger restore bar H restores these triggers slightly beyond their normal position and then moves slightly back, so that the triggers are latched by the check latches 43.

The clearing device for the totalizer does not form a part of the present invention. Briefly, it may comprise a number of studs 12 fixed to gears I! in evenly spaced positions, the distance between two adjacent studs 12 corresponding to a full turn of totalizer wheel 10. A clearing bar 13 rotatable and radially shiftable on shaft 18 has grippers 74 adapted to cooperate with studs 12. When the clearing bar 13 is rotated anti-clockwise (by means not shown), it is first caused to move slightly towards the shaft l8, so that each gripper I4 is interposed in the path of studs 12 on the associated gear l1. On continued rotation of bar 13 the grippers i4 engage the nearest studs 12 and rotate the gears I! and the totalizer Wheels I0 into the zero position; whereupon the clearing bar 73 is restored, preferably by a spring. Prior to rotation of bar 13 the storage restore bar 40 is caused to restore the storage plates 33, and the gear segment support 59 is moved to demesh the gear segments 5'! from gears l1, whereupon a crossbar 15 is lowered to lock the carry pawl arms 32, so that any overthrow of totalizer wheels 16 may be prevented by carry pawls 30 engaging the carry lugs I 6. After clearing the cross bar 15, the storage restore bar 40, and the gear segments 57 are restored to their normal positions.

Operating means The machine is operated by a main driving shaft 76, Fig. 2, suitably journalled in machine frame l1, l2 and rotated once during each opcrating cycle by a suitable handle or motor (not shown).

Referring to Figs. 2 and 5, the mesh-demesh operation of idler gears 21 and gear segments 51 is controlled by a grooved cam 18 fixedly mounted on main shaft 16. Cam 10 coacts with a roller 19 journalled in a follower 80 fixedly mounted on a shaft 9! journalled in machine frame 11, 82. An arm 33 is fixedly mounted at each end of shaft I; each arm 89 has a pin-and-slot connection 84 to a lever 85 rockable on a trunnion 86 fixedly supported in machine frames 11, 82, respectively. The idler shaft support 29 is fixed at each end to one of levers 85. Rockable on each trunnion 89 is an arm 81 connected by a spring 88 to the respective lever 85; the gear segment support 59 is fixed at each end to one of arms 81. During addition the main driving shaft 16 is rotated clockwise as viewed in Fig. 5, and early in the cycle the cam 18 causes its follower 80 to rock anti-clockwise, which causes levers 85, arms 81, and supports 29, 59 to rock clockwise around trunnions 86, and thus to mesh the idler gears 21 with, and to demesh the gear segments 51 from, the driving gears I1, as described hereinbefore. The parts remain in this position until shortly before the racks 20 start on their return stroke; now cam 18 restores the follower 80 and supports 29, 59, so that the idler gears 21 are demeshed from, and the gear segments 51 are meshed with. the gears I1. During subtraction the main shaft 16 is rotated anti-clockwise; at about the middle of the cycle cam 18 rocks its follower 80 anti-clockwise, thus meshing the idler gears 21 with, and demeshing the gear segments 51 from, the gears I1. Near the end of cycle cam 18 restores the follower 80 and the supports 29, 59.

Trigger restore bar 1| is operated by a grooved cam 89, Fig. 5, fixed to shaft 19 and co-acting with a roller 99 journalled in a follower 9| rotatable on a sleeve 92 on follower shaft 8|. Linked at 93 to the follower 9| is a connecting rod 94 linked at 95 to an arm 96 secured. to a sleeve 91 rockable on a shaft 98 journalled in the supporting structure. An arm 99 is fixed at each end of sleeve 91. Linked at I00 to each arm 99 is a connecting rod I9I linked at I02 to a bracket I03 rockable on trigger shaft 52; the trigger restore bar H is fixed at each end to one of brackets I93. Rotation of cam 89 in either direction causes its follower 9I to rock anti-clockwise early in the cycle and to swing the trigger restore bar 1I clockwise around the trigger shaft 52, thus restoring the triggers I near the end f cycle the cam follower 9i is restored clockwise, thus rocking the trigger restore bar 1| anti-clockwise and releasing the triggers 5i as described.

Storage restore bar 49 is operated by a cam I 04, Fig. 2, fixed to the main shaft 16. Cam I04 is somewhat similar in shape to the trigger restore cam 89; it co-acts with a roller I05 journalled in a follower I06 identical in shape with follower 9!, Fig. 5. Cam follower I06 is rockable on sleeve 92 on follower shaft 8I and has a pin-and-slot connection I01 to a rod I08 linked to a plate I09 secured to shaft 98 through a suitable hole in sleeve 91. Fixed at each end of shaft 98 is an arm H0 to which is linked at III a connecting rod II2 linked at I53 to a bracket H4 rotatable on the storage shaft 34. The storage restore bar 40 is fixed at each end to one of brackets II4. Rotation of cam I94 in either direction causes the storage restore bar 40 to rock anti-clockwise just before the restoring operation of the trigger restore bar TI, and to restore the storage plates 33 10 and the strikers 38 as described; near the end of cycle, just after the release of triggers 51, the storage restore bar 40 rocks clockwise and releases the storage plates 33 and the strikers 36 to effect the carry operation as described.

A spring II5 exerts a bias on the connecting rod I08 towards the cam follower I05. As described above, the storage restore bar 49 is operated to restore the storage plates 33 and the support 59 is operated to demesh the gear segments 51 from gears I1 during the clearing operation, whereupon the storage restore bar 40 and the support 59 are restored. by springs H5, 88, re spectively.

Striker support 38 is operated during addition by a cam H5 and during subtraction by a cam II1, Figs. 6 and 2, both these cams being rotatably mounted on the main shaft 16. A driver I I8 is adapted during additive (clockwise as seen in Fig. 6) rotation of shaft 16 to engage a pawl II9 pivoted at I20 in the additive cam H6 and biased by a torsion spring I2I into engagement with driver H8. Cam follower I22 is rockably mounted on sleeve 92 on follower shaft 8I; journalled in cam follower I22 is a roller I23 coacting with cam IIB. Linked at I24 to the follower I22 is aslide I25 mounted on a guide pin I23. Prongs I21, I28 on slide I25 co-act with pins I29 in a plate I30 secured to a shaft I 3I suitably journalled in the supporting structure. Two brackets I32 are secured to shaft I3 I; the striker support 38 is fixed at each end to one of brackets I32. Spring I33 anchored in the supporting structure maintains the roller I23 in contact with the cam IE6.

Between 45 and of an additive cycle cam H6 rocks its follower I22 clockwise, thus causing the slide I25 to move downwards; thereby, one of prongs I21 moves the upper pin I29 downwards until both pins I 29 are level, any overthrow being prevented by the other prong I21. This brings the striker support 38 into a neutral position shown in Fig. 1 and in dotted lines in Fig. 6. Assuming the previous cycle was an additive one, pins I29 would have remained in positions shown in Fig. 6, and the downwards movement of slide I25 would rock thebrackets I32 clockwise to bring the striker support 33 into the neutral position. If the previous cycle was subtractive, the left-hand pin I29 would remain higher than the right-hand pin I29, and the downwards movement of slide I 25 would rotate plate I30 and brackets I32 anti-clockwise. In either case the slide I25 while moving downwards restores the striker support 38 to its neutral position.

Guide pin I20 is fixed in a rocker I34 rotatable at I35 in the supporting structure; rocker I34 has an upper arm I36 with a nose I31 and a lower arm I38 with a nose I39. As will be presently explained, rocker I34 remains after an additive cycle in the position shown in Fig. 6. It is maintained in this position by a detent I40 pivoted at I M and biased by a spring I42 into engagement with the lower one of two recesses I43 formed in the lower arm I38 of rocker I34. Upper nose I31 co-acts with a pin I44 fixed in the additive cam II6, while the lower nose I39 coacts with a pin I45 in the subtractive cam I I1. At about 90 in an additive cycle the pin I44 approaches the upper nose I31. If the previous cycle was a subtractive one, rocker I34 would be in such a position that the upper recess I43 would be engaged by detent I40; in this case,

pin 144 would now engage the upper nose I31- and rotate the rocker I34 into position shown in Fig. 6. Assuming the previous cycle was additive, pin I44 will just touch the nose I31 without affecting the position of rocker I34 and slide |25.

Near the end of an additive cycle cam H6 allows the cam follower I22 to rock anti-clockwise, thus raising the slide I25; the right-hand prong I28 in slide I25 being aligned with the right-hand pin I29 in plate I30, this prong causes the plate I30 to rotate anti-clockwise, so that brackets I32 lower the striker support into position shown in full lines in Fig. 6. This results in a 1 carry stroke of strikers 35 as described above.

Considering now a subtractive cycle, during which the main shaft I6 is rotated anti-clockwise, a driver I46 fast on the main shaft drives the subtractive cam III by means of a pawl I4! mounted in this cam in a manner similar to the mounting of pawl H9 in the additive cam ||6. Shortly after one-half of the cycle cam III operates roller I23 in cam follower I22 and causes slide I25 to move downwards and to restore the striker support into the neutral position as described. At about 232 pin I45 approaches the lower nose I39 and, if the previous cycle was additive and the part have remained in the position of Fig. 6, engages the nose I39 and rotates the rocker I34 anti-clockwise, so that detent I40 engages the upper recess I43; thereby the guide pin I26 causes the slide I25 to rock anti-clockwise around its pivot I24, so that now the left-hand prong I28 is aligned with the left-hand pin I29 in plate I30. Near the. end of cycle the subtractive cam III causes the slide I25 to move upwards, whereby the left-hand prong I28 engages the left-hand pin I29 and rotates the plate I30, shaft I3I, brackets I32, and striker support 38 clockwise. In this manner the strikers 36 and pawls 63 effectthe +1 carry stroke, as described.

It will be noted that the additive cam I I6 is driven only during additive cycles, while the subtractive cam I I1 is driven only during subtractive cycles. Suitable means such as springloaded detents, not shown, may be provided to prevent inadvertent rotation of cams H6 and II! during subtractive and additive cycles, respectively. Operating means for the check rocker shaft 42 will now be described. A double pawl I48 is fixedly mounted on shaft |4| suit-ably journalled in the supporting structure, a spring I 42 tend ing to rock the pawl I48 towards the main shaft 16. Laterally the pawl is disposed between the striker cams ||6, II'I, its two prongs being 're-' spectively in lateral alignment with a pin I49 fixed in the additive cam 6 (see also Fig. 2) and wih a pin I50 fixed in the subtractive cam 1. When either of the cams is rotated, one or the other of pins I49, I50 contacts the associated prong of pawl I48 near the end of cycle, and rocks the pawl and the shaft |4| clockwise, whereupon the pawl and the shaft are restored by the spring I42. This reciprocation of shaft |4| is communicated to an arm Fig. 5, secured to shaft |4| andlinked at I52 to a connecting rod I53 linked at I54 to an arm I55 slidably but not rotatably mounted on the check rocker shaft 42. Thus, as the shaft MI is 'rotated clockwise and then restored, the rocker shaft 42 is rotated first anti-clockwise and then clockwise, and the checking operation is effected as described above. y

As shown in Fig. 6, the upper prong I36 of rocker I34 has a pin-and-slot connection I56 to an arm I51 secured to a sleeve I58 rotatable on shaft I4I. Secured to sleeve I58 is a bracket I59, Fig. 5, on which is fixedly mounted a groove cam piece I69 engaged by the lower end |6| of a clutch fork I62 pivotally mounted at I63 in the supporting structure. Forked upper end I64 of clutch fork I62 engages a groove in a clutch disc I65 fixedly mounted on the check rocker shaft 42. Cam piece I60 is so shaped that, as long as the main shaft I6 is rotated additively and the rocker I34 remains in the position of Fig. 6, clutch fork I62 keeps the check rocker shaft 42 shifted axially to the right as viewed in Fig. 3, and check rockers 4| remain laterally aligned with 0 recesses 45 in the totalizer wheels ID, as described. When the main shaft 16 is rotated subtractively, rocker I34 rotates slightly anti-clockwise as viewed in Fig. 6 as previously described, and the resulting clockwise rotation of shaft MI and cam piece I50 causes the clutch fork I62 to shift the check rocker shaft 42 axially to the left in the sense of Fig. 3, so as to align the check rockers 4| with 9 recesses 46 in the totalizer wheels I8.

The invention will now be described as applied to totalizers which receive true values, and not values increased by unity as described above with reference to the preferred embodiment.

It will be apparent from a perusal of calculation examples given above that, while in the preferred embodiment the function of check rockers 4| after an additive value-entry is to check which totalizer orders stand at 0, in the present modification their function is to check which orders stand at 9. Similarly, after subtraction the check rockers 4| in the preferred embodiment have to check which totalizer orders stand at 9, Whereas in this modification the rockers have to check which totalizer orders stand at 0. Thus, the function of check rockers 4| is reversed in this modification as compared to the preferred embodiment. This reversal of function can be achieved simply by replacing the cam piece I60, Fig. 5, by another cam piece adapted to keep the check rocker shaft 42 during additive revolutions of the main shaft 16 in the left-hand axial position of Fig. 3, so that check rockers 4| are,

aligned with 9 recesses 46 in the totalizer wheels I0, and during subtractive revolutions of shaft I6 to align the check rockers with the righthand 0 recesses 45. Alternatively, in this modification the O recesses 45 may be arranged on the left-hand side of wheels I8 as viewed in Fig. 3," and the 9 recesses 46 may be arranged on the right-hand side; that is, the axial position of recesses 45, 46 may be reversed as compared with the preferred embodiment.

The modified carry device is shown in Fig. 7, the modified parts similar to those of the preferred embodiment being identified by the same reference numerals with suffix A, Strikers 35A are adapted to co-act with studs 62 on gear segments 5'1 directly, without the intermediary of pawls 63. There is normally a somewhat larger clearance between the storage plates 33 and the storage restore bar 40. Each striker 36A has a slot I66 which normally engages the stud 62 on the associated gear segment 51. However, when gear segments 51 are meshed with gears IT as described above, stud 62 moves out of slot I66 if the striker 36A remains in the no-carry position shown in Fig. 7. If the striker 36A is allowed by its storage plate 33 to rock anti-clockwise around its shaft 37, then the slot I66 remains in engagement with stud 62 even after gear segments 5'! have been meshed with gears ii. The carry is effected as in the preferred embodiment by a movement of the striker support 38. In this modification, striker support 38 moves substantially upwards after an additive value-entry and downwards after a subtractive value-entry, so that those strikers 36A which have remained in engagement with their gear segments 5'! advance the associated totalizer wheels Ill one step additively or subtractively, respectively.

If a, totalizer wheel Ill moves from 9 to I) in addition, or from to 9 in subtraction, it produces a definite carry impulse which is stored by the action of lug I6 rocking the carry pawl 30, so that its arm 32 unlatches the storage plate 33 which drops on to the restore bar 46; thus, the striker 35A controlled by this Sending order remains in engagement with gear segment of the next-higher order after the meshing of segments 5? with gears I'I. Consequently, carry will be effected to the next-higher order by advancing it one step during the carry stroke of strikers 35A, additively after an additive valueentry or subtractively after a subtractive valueentry.

Transmitting orders are checked by rockers MA which, as already explained, sense the 9 recesses 45 after addition and 0 recesses 45 after subtraction. Each check rocker BIA has an extension It? which, when the rocker enters a recess 46 or G6, causes the carry arm 32 to delatch its storage plate 33 just after the respective latch 48 has delatched its trigger 5|. Thus, when the trigger restore bar II releases the triggers 5| as described, the storage plates 33 of those Transmittin orders which are next-higher or chain-higher to a Sending order will rock clockwise and permit their strikers 36A to reengage their gear segments 5'! and to effect the carry. On the other hand th storage plates 33 of those Transmitting orders which are not nexthigher or chain-higher to a Sending order will not rock out, being locked by their triggers 5|; their associated strikers 36A will not re-engage their gear segments '51 and will not efiect a carry in the respective totalizer orders.

It will be noted that in the present modification the direction of the carry stroke of strikers 36A is opposite to that of strikers 36 of the firstdescribed arrangement. This change of direction of striker support 38 can be achieved very easily by arranging the upper prong I36 of rocker I34, Fig. 6, to cooperate with the subtractive cam H1, and reversely to arrange the lower prong I33 to co-act with the additive cam H6, by securing pins I46, I45 in cams H1, H6, respectively.

It will be seen that the modification just described diiiers very little from the first-described embodiment, the difierent action being achieved mainly by a reversed operation of the check rockers SI, MA and of the striker support 38.

It may be noted that the operation of check rockers 4i, SIA, the movement of storage plates 33 and of strikers 36, 36A into the carry position, and the engagement of gear segments 51 with gears H can take place immediately on completion of the value-entering o eration and while the sensing racks 2c are being demeshed from gears IT. The actual carry operation, namely 14 the movement of the striker support 38, can be eilected very quickly and positively, inasmuch as there is no possibility of a rebound or overthrow.

It will be obvious to those skilled in the art that the carry devices described above may be modified in many respects without departing from the spirit of the present invention.

Th invention may be readily applied to directmultiplying machines of the type requiring two carries during each operating cycle; if required, one carry may be effected additively, and the other carry may be effected subtra'ctively, as described.

What I claim is:

1. In a machine of the type referred to having a totalizer with a plurality of denominational orders, carry storage means operatively associated with each totalizer order and operable when the associated order moves from 9 to 0 during addition and from 0 to 9 during subtraction, check means operable after a value-entering operation for indicating whether the associated order stands at 9 or 0, depending on the direction of value-entry, interlock means controlled by said check means for interlocking the said carry storage means of adjacent orders, and driving means controlled by said carry storage means for driving the individual totalizer orders simultaneously one step in the direction depending on that of the value-entry.

2. In a machine of the type referred to having a totalizer with a plurality of denominational orders adapted to receive additive and subtractive digital values each increased by unity, carry storage elements each associated with a totalizer order and operable when the associated order moves from 9 to 0 during addition and from 0 to 9 during subtraction, check elements each associated with a totalizer order and movable into an operative position when the associated order stands at 0 after an additive value-entry and at 9 after a subtractive value-entry, interlock members each movable by an operative check element to lock the said storage element of the associated order to that of the next-lower order, and means for driving all totalizer orders associated with storage elements which were operated during the value-entry and are associated with inoperative check members, and also all totalizer orders associated with storage members, locked to these operated storage elements associated with inoperative check members, substantially simultaneously one step in the direction opposite to that of the value-entry.

3. In a machine of the type referred to having a totalizer with a plurality of denominational orders, carry storage elements each associated with a totalizer order and operative when the associated order moves from 9 to 0 in addition and from 0 to 9 in subtraction, check elements each associated with a totalizer order and operable when the associated order stands at 9 after an additive value-entry and at 0 after a subtractive value-entry, interlock members each movable by an operative check element to lock the said storage element of the associated order to that of the next-lower order, and means for driving all totalizer orders associated either with operative storage elements or with storage elements locked by the said interlock members to operate storage elements one step substantially simultaneously in the direction of the value-entry.

4. Carry device according to claim 1, comprising carry storage rockers each associated with a totalizer order and rockable, when the associated order moves from 9 to during addition and from 0 to 9 during subtraction, into an operative position in which it remains until after completion of the value-entering operation.

5. Carry device according to claim 1, comprising suitable representations of the 9 and 0 positions of individual totalizer orders, check rockers each associated with a totalizer order and rockable into an operative position when brought into operative association with one of said representations, and means for operatively associating the said check rockers after the value-entering operation with representations of either the 9 positions or the 0 positions of the totalizer orders.

6. In a totalizer of a machine of the type referred to, a carry device comprising carry storage means each associated with a totalizer order and movable, when the associated order moves from 9 to 0 during addition and from 0 to 9 during subtraction, into an operative position in which it remains until after completion of the value-entering operation, representations of the 9 and 0 positions of individual totalizer orders and check means operative when associated with these representations, actuating means for operatively associating the said check means with representations of either the 9 or the 0 positions of the re- I6 spective totaliz'er orders, interlock means for looking a carry storage means to that of the nextlower totalizer order when the associated check means is operative, driving members each movable under the control of one of said carry storage means into operative association with the respective totalizer Wheel, and a driving actuator adapted to displace all driving members simultaneously a predetermined amount in either of two opposite directions, depending on the direction of the preceding value-entering operation, whereby the driving members if in operative association with the respective totalizer wheels advance the latter additively or subtractively.

DANIEL BROIDO.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,471,770 Bernau Oct. 23, 1923 1,767,674 Horton June 24, 1930 1,957,960 Hosack May 8, 1934 2,302,422 Crouse Nov. 17, 1942

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