US2701094A

US2701094A - A parker

Info

Publication number: US2701094A
Authority: US
Publication date: 1955-02-01
Anticipated expiration: 1972-02-01

Description

Feb. 1, 1955 c, PARKER 2,701,094

REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Filed Aug. 31, 1949 6 Sheets-Sheet l IN VEN TOR. Char [es /7. fal'terfl HTTORNE).

Feb. 1, 1955 c, PARKER 2,701,094

REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Filed Aug. 31, 194 9 6 Sheets-Sheet 2 IN VEN TOR. Char/e5 x7, Par/(er Feb. 1, 1955 g, PARKER 2,701,094

REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Filed Aug. 31, 1949 6 Sheets-Sheet 3 A67 ma INVENTOR. Charles J]. Par-fie) Feb. 1, 1955 c, A PARKER 2,701,094

REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Filed Aug. 51, 1949 6 Sheets-Sheet 4 v INVENTOR.

Cid/{es JZ Paw/Tel BY gghgw HTTOAIVEY.

Feb. 1, 1955 Q A. PARKER 2,701,094

REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Filed Aug. 31, 1949 6 Sheets-Sheet 5 128 130 175 0 9 INVENTOR.

Cfiarles .19. Parker" HTTORNEY.

Feb. 1, 1955 c, PARKER 2,701,094

REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Filed Aug. 51, 1949 6 Sheets-Sheet 6 IN VEN TOR. (flax-[es A Rwwfen 177' 7' ORA/E K United States Patent REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Charles A. Parker, Knoxville, Tenn., assignor, by mesne assignments, to Burroughs Corporation, a corporation of Michigan Appiication August 31, 1949, Serial No. 113,402

17 Claims. (Cl. 235-60) This invention relates to the art of calculating machines. It is concerned in particular with the register mechanism of such machines. Conventional calculating machine practice makes use of a register which incorporates some form of rack movable between two limit positions through a definite cycle to rotate register pinions in accordance with the directional movement of the rack. The pinions are variously shifted into and from mesh with their racks. Known machines employ relatively complicated mechanisms for effecting the shift of the register pinions at the appropriate time. Such mechanisms entail the use of a large number of separate parts and usually the various parts are located at spaced points about the machine assembly.

An object of this invention is to provide a timing mechanism for etfecting shift of the register pinions and which provides a compact unit that contains substantially all necessary elements to accomplish desired shifting of the register pinions. The unit is relatively small and occupies but little space and it condenses into one assembly the essential mechanism necessary for timing shifting of the register pinions.

Another object is to provide means for transmitting actuating energy from the main operating member of a calculating machine to the register pinion shifting means, in which a single compact element in fixed relation to the operating member furnishes the motive force for a plurality of shift elfecting mechanisms which operate separately and at different times at different locations.

A further object is to provide register pinion shifting mechanisms for calculating machines having means for freeing from idling movement all parts not necessary to the performance of work when other parts required to perform work are being moved to accomplish a shifting of the pinions.

Another object is to provide, in a calculating machine having an operating member movable through a cycle and a plurality of separately acting register pinion shifting mechanisms driven therefrom during its cycle, means for removing from driving actuation by the operating member all parts of those shifting mechanisms not called upon to perform work when any one of the shifting mechanisms is working.

Still another object is to provide timing means for register pinion shifting mechanism in a calculating machine, in which the various shifts of the pinions into and from mesh with their racks are all controlled from a single fixed element on a movable operating member of the machine, in cooperation with a plurality of devices operative selectively at predetermined points along the path of movement of the operating member to effect pinion shift in either of two opposite directions when the operating member element is at those points.

A further object is to provide a driving connection between the operating member and the register pinion shifting mechanism of a calculating machine, in which oppositely acting linkages form a coupling, with means operative selectively to disengage the coupling with respect to any linkage whereby to control the direction of pinion shift.

Other objects apparent to persons skilled in the art are incorporated in the following specification, which is illustrative and not restrictive.

in the accompanying drawings:

Fig. l is an elevation of a timing mechanism assembly constructed in accordance with this invention, the view being from the right hand side of the mechanism consid 2,701,094 Patented Feb. 1, 1955 ice ered on the longitudinal axis running from front to rear of the machine in which the mechanism is incorporated;

Fig. 2 is a similar elevation but taken from the left, or opposite, side with respect to Fig. 1;

Fig. 3 is an elevation of the structure of Fig. 1 with parts removed and broken away for clearness of illustration;

Pig. 4 is an elevation from the right hand side of the apparatus illustrating details of the register shift mechanism;

Fig. 5 is a rear view of the assembly of Fig. 1;

Fig. 6 is a front view of the assembly with parts broken away for clearness of detail;

Fig. 7 is a fragmentary elevation illustrating a detail of the mechanism;

Fig. 8 is a top plan view of the assembly;

Fig. 9 is a top plan view of a portion of the assembly shown in Fig. 8;

Fig. 10 is a fragmentary elevation illustrating certain details of the mechanism;

Fig. 11 is a longitudinal section taken substantially on the line 11-11 of Fig. 1 illustrating the position of parts when the apparatus is conditioned for addition or subtraction in the register;

Fig. 12 is a view similar to Fig. 11 but illustrating the position of the parts when the apparatus is conditioned for a subtotal operation;

Fig. 13 is also a view similar to Fig. 11 but illustrating the position or" the parts when the apparatus is conditioned for a total taking operation; and

Figs. 14 and 15 are illustrations of details of the mechanism.

In the present embodiment of the invention the timing mechanism is mounted on a vertically planar support S that is disposed longitudinally parallel to the longitudinal axis of the machine in which the mechanism is incorporated. By way of reference, the present mechanism is incorporated in the accounting machine illustrated in the copending application of Charles A. Parker and Clifton K. Rainey, Serial No. 99,081, filed June 14, 1949. it is to be understood, however, that the timing mechanism of this invention is readily adaptable to other types of calculating machines and the reference is by way of illustration and not by way of limitation. The support has front and

rear leg portions

18 and 19, respectively, that are rigidly attached to elements of the machine frame secured to the base B of the machine. The bottom portion of the support between the

legs

18 and 19, is cut away to accommodate movement of an operating member 20. The operating member 20 is driven by suitable means, not shown, to reciprocate through a full cycle at each actuation. Its path of reciprocation is be tween the

support legs

18 and 19 and it operates between forward and rearward limit positions. The rearward limit position of the operating member, as shown in Figs. 1 and 2, is its position of rest which it occupies prior to and at the conclusion of a cycling operation.

Energy of the operating member is utilized to shift register pinions in the register section of the machine in which the apparatus is incorporated. Fig. 4 indicates a portion of the register section of the mechanism, which incorporates a set of register pinions 21 adapted for shifting into and from engagement with

side bars

22 and 23 which are elements of the racks of the calculating mechanism. In the illustration of Fig. 4, the toothed bars 22 comprises the addition side of the racks while the bars 23 comprise the subtraction side. This arrangement may be varied as desired and is by way of illustration only. Through connecting links, later described in detail, movement of the operating member 20 is employed to actuate a rocker post 24 that is fulcrumed intermediate its ends on a pivot member 25 carried by the support S adjacent its forward end. Further as shown in Fig. 4, the rocker post 24 has a pivotal connection 26 with the forward end of a horizontally disposed lever 27 which extends rearwardly in parallel spaced relation with respect to the support plate S and which carries at its rear end a T-head 28 that cooperates with a coupling disc 29 to rotate the disc in accordance with directional move-- ment of the lever 27. The disc is provided with upper and lower diametrically opposed lateral studs and 31, respectively, which are adapted to be received in a keeper slot 32 in the adjacent flange of the T-head. As indicated in Fig. 4, the upper stud 30 of the disc 29 is engaged in the upper keeper slot on the T-head, so that when the rocker post 24 is actuated to shift the lever 27 rearwardly, to the right with respect to Fig. 4, a clock wise movement will be imparted to the disc 29. This clockwise movement of the disc is transmitted through a depending L-shaped link 33 to the set of register pinions 21 whereby the pinions are shifted from their neutral position intermediate the rack bars down into mesh with the lower rack bars 23. The link 33 has pivotal connec' tion at its upper end with the disc 29 and is slidable with shaft 34 which provides the mounting means for the freely rotatable pinions 21. It will be apparent that when the rocker post 24 is oppositely moved, the lever 27 will be pulled forwardly so that the disc 29 is rocked in a counterclockwise direction. This movement of the disc 20, acting through the link 33, will shift the register pinions upwardly into neutral position out of mesh with the lower rack bars. The lever 27 is held with its T-head elevated in driving connection with the upper disc studs 30 through the upward pull of a connector spring connected between a stud 36 on the shank of the lever and a stud 37 carried by the inner end of a control lever 38 that is itself pivoted intermediate its ends as at 39 to a support element 4% for oscillation in a vertical plane. The forward end of the control lever has a terminal portion 41 which, in the position of parts shown in Fig. 4, is held depressed by a subtract key element, not shown, of the machine in which the mechanism is incorporated. When the terminal 41 is freed, so that addition may be effected, the lever 27 and its T-head 28 are permitted to drop down so that the lower keeper slot 32 engages the lower disc stud 31, while the upper keeper slot 32 clears the stud 30. When thus positioned, it will be apparent that rearward movement of the rocker post 24, driven from its connecting linkage with the operating member 21), acts to rock the disc 29 in a counterclockwise direction so that the register pinions are shifted from neutral position upwardly into engagement with the top bars 22 of their racks. In like manner, but in reverse movement, when the post 24 is rocked forwardly the lever 27 is pulled forwardly to rock the disc 29 in a clockwise direction and thereby to lower the register pinions out of mesh with their upper rack bars 22 and back into neutral disengaged position.

It should here be pointed out that in the present disclosure the rack bars 22 and 23 comprise the upper and lower sides of separate racks arranged in denominational order for horizontal reciprocation forwardly and rearwardly in coincidence with reciprocation of the operating member 20. This arrangement is optional and is not by way of limitation. When the racks go forward in the normal operation of entering items into the machine, the register pinions are shifted out of engagement with their respective rack bars and they remain out of engagement until the operating member begins its rearward movement in the second half of its cycle. At this time the pinions are shifted into engagement with their rack bars so that the operation of addition or subtraction as the case may be is accomplished in the register. The pinions remain in mesh when the operating frame comes to its position of rest at its rear limit of travel and are disengaged when the operating member next is cycled to begin its forward movement. This is the normal operation of the mechanism.

The linkage which constitutes the driving connection between the operating member and the rocker post 24 is carried by the support plates S. As shown in Fig. 2. the operating member 20 has secured thereto a plate 42 to which is rigidly attached a double acting cam indicated generally at 43. The structure of this cam is best shown in Figs. ll, 12 and 13 in which it wil be seen that the body of the cam is substantially boatshaped and is positioned longitudinally of the path of re ciprocation of the operating member 20. The cam is formed from a block of material rectangular in crosssection that is relieved from its top face to provide downwardly inclined sloping faces that converge at the midpoint of the cam. The front end of the cam body has a nose portion 44 provided with fOIW 9 vergent side faces 45, and at its rear end the cam body has a similar nose portion 46 provided with rearwardly convergent side faces 47. As shown in Figs. 11, 12 and 13, the convergent side faces of

nose portions

44 and 46 intersect in the longtudinal axis of the cam body and this axis is in vertical registry with the longitudinal axis of the support plate S. Directly behind the forward nose portion 44, the downward sloping face of the cam body provides a riser 48 which intersects with the rear riser portion 49 formed by the sloping face extending up to the rear nose portion 46. This cam is adapted to cooperate with a pair of hell crank rockers 50 and 5'1, respectively, pivoted at the left hand side of the support plate S, and with a second pair of bell crank

rockers

52 and 53, respectively, pivoted at the right hand side of the support plate. The pivotal mounting for these rockers comprises in each instance a pin 54 passed transversely through the support plate S to project at opposite sides thereof. The fulcrum point of each bell crank rocker is apertured to play loosely over the pin, and an expansion spring 55 surrounding the shank of the pin between cotter-key anchored washer 56 and a bearing washer 57 normally urges the rocker laterally against the face of the support plate S. The fulcrum point aperture in each bell crank rocker is sufficiently large to permit lateral pivoting of the rocker on the pin and at the same time to permit free pivoting movement of the rocker for oscillation in a vertical plane. Each bell crank rocker comprises a thin plate vertically disposed for oscillation in a vertical plane parallel to the support plate S. The rocker 50 at the left hand side of the support plate is disposed over the forward travel limit point of the operating member 20. The bottom edge of this rocker has a downwardly directed cam portion formed with an upwardly and forwardly inclined cam edge 58, and the body of the rocker is further provided at its bottom portion with a rearwardly directed lug 59 that is flared laterally outward with respect to the vertical plane of the rocker to provide an inclined camming face adapted to cooperate with the inclined face 45 of the forward nose of the cam 43 when the operating member is moved to its forward limit position. The rocker 50 also is provided at its front edge with a similar laterally and outwardly inclined cam lug 60 that is directed forwardly for cooperation with a cam element of displacement means, later described. The rear bell crank rocker 51 is substantially similar to the rocker 50 and has a forwardly and downwardly inclined portion that provides a sloping cam edge 61 which, when the operating member 20 is in its position of rest at its rearward limit of travel, overrides the rear inclined riser 49 of the cam 43. The front edge of the rear rocker 51 is formed with a forwardly directed lug 62 that is flared forwardly and outwardly with respect to the plane of the rocker. This lug 62 is adapted for cooperation with the displacement means, later described. The vertical extent of the lug 62 equals the combined vertical extent of the

lugs

59 and 60 on the forward rocker 50, so that the lower end portion of the rear rocker lug 62 is adapted for cooperative camming engagement with the adjacent inclined side face 47 of the rear nose 46 on the cam when the operating member 20 is moving rearwardly through the second half of its cycle back into its limit position.

When the operating member 20, see Fig. 2, starts forward in the first half of its cycle, its riser 49 cams against the overriding edge 61 of the bell crank rocker 51 and rocks the bell crank in a counterclockwise direction. As the operating member continues forward, the bottom edge of the bell crank lever rides off the rear nose 46 of the cam 43. Rocking movement of the bell crank 51 is transmitted through a pull link 63 to the rocker post 24 to impart a forward rocking movement to the upper end portion of the rocker post. This link 63 parallels the support plate S and is inclined forwardly and downwardly relative to the assembly. At its rear end the link 63 has a pivotal connection 64 with a connector link 65 that is, in turn, pivoted at 66 to the upper portion of the bell crank rocker 51. The connector link 65 has a forwardly directed extension that lies alongside the shank of the link 63 and which is provided with a portion bent upon itself beneath the lower edge of the link 63 to provide a keeper 67 which lies alongside the opposite side of the link 63. A contractile spring 68 ponnected between a point of anchorage on the link 65 and a point of attachment on the link 63 normally biases the link 63 downwardly into seated engagement in its keeper 67. At its forward end the link 63 carries a hooked terminal 69 that is adapted to engage over a lateral stud 70 carried by the lower end of the rocker post 24. As the link 63 is pulled rearwardly by pivoting of the rocker 51, under the action of the cam on the operating member, the hook 69 engages the rocker post stud 70 to pull the lower end of the rocker post rearwardly and thus correspondingly rock the upper portion of the post forwardly to impart a forward shift to the lever 27 for correspondingly rocking the disc 29, as previously described, to elevate the register pinions 21 out of mesh with the rack bars 23 for a shift to neutral disengaged position, as shown in Fig. 4.

As the operating member goes forward, the inclined face 45 of its forward nose 44 engages behind the cam lug 59 of the forward rocker 50 and cams the rocker plate laterally outward to accommodate passage of the cam 43. When the operating member reaches its forward limit of travel the nose 44 of its cam will have passed beyond the lug 59 so that the rocker plate is permitted to shift back in the direction of the support plate to dispose its cam edge 58 in overriding relation to the forward riser 48 of the operating member cam. When the operating member starts rearwardly through the second half of its cycle it is necessary that the register pinions be in engagement with their rack bars. As the operating member starts back, its riser 48 earns the forward rocker 50 to rock in a counterclockwise direction with respect to Fig. 2. The upper end portion of the rocker 50 has a pivotal connection 71 with a connector link 72, similar to the previously described connector link 63, and which has pivotal connection 73 with the rear end of a pull link 74. The connector link 72 also is formed with a keeper 75 which guides the link 74. A contractile spring 76 between a point of attachment on the link 72 and a point of attachment on the link 74 biases the link 74 into engagement against the bottom of its keeper. The forward end of the pull link 74 has a hooked terminal 77 adapted to engage over a lateral stud 78 carried by the rocker post 24 at a point above its fulcrum. The pull of the linkage just described acts to rock the upper portion of the rocker post 24 rearwardly, so that the lever 27, see Fig. 4, is shifted rearwardly to effect a corresponding clockwise rotation of the disc 29, which acts to lower the register pinions 21 into engagement with their rack bars. At this point it should be made clear that if the control lever 38 had been released to lower the lever 27 for engaging the lower disc stud 31 in the lower keeper slot 32, the shifting of the lever 27 would have effected a counterclockwise rotation of the disc 29 which would have carried the pinions into mesh with the upper bars 22 of their racks.

The rocker post 24 carries at its upper end a laterally disposed roller 79 that is adapted to ride into either of two valleys 80 and 81 formed at the sides of a depending ridge member 82 in the bottom edge of a detent lever 83 that is pivoted at its rear end 84 to the support plate S. The forward end of the detent lever is biased downwardly by a contractile spring 85 connected between the end of the lever and a point of attachment on the support plate. The bias of the detent lever 83 serves to hold the rocker in either of the two positions to which it is shifted by the action of the linkage just described. As shown in Fig. 15, the upper end of the rocker post 24 is adapted to contact limiting stop flanges 86 and 87, respectively, which are integral with a horizontal plate 88. The plate 88 is secured to the support plate S so that the flanges 86 and 87 depend in parallel spaced relation to define the extent of rocking movement of the rocker post. The stop flanges hold the rocker post on the sloping side of the detent ridge 82 before it travels completely into the adjacent valley 80 or 81, so that it will not override the throw of the lever 27 and cause jamming of the disc lugs 30 and 31 relative to the head of the lever.

The linkage at the right hand side of the support plate S is illustrated in Fig. 1. This linkage is substantially similar to that at the left hand side of the plate and comprises a connector link 89 pivotally connected as at 90 to the upper portion of the rear bell crank rocker 53, with a pivotal connection 91 to the rear end of a horizontally disposed pull link 92 that has a hooked terminal 93 at its forward end for engagement over the upper stud 78 on the rocker post 24. The connector link 89 is provided with a keeper 94 and a spring 95 similar to the link 65, keeper 67, and spring 68 previously described. The spring 95 biases the link 92 against the bottom of its keeper 94 to retain the linkage in proper assembly. The rear bell crank rocker 53 is identical in structure to the rear rocker 51 at the left hand side of the assembly, except that its camming lug 96 is flared oppositely outward with respect to the plane of the rocker. In like manner the forward rocker 52 at the right hand side of the support plate is provided with

lugs

97 and 98 similar to the

lugs

60 and 59 of the forward rocker at the left hand side of the assembly. These lugs have the same function as those of the left hand forward rocker and are oppositely flared with respect to those at the left side. The upper portion of the rocker 53 has a pivotal connection 99 with the rear end of a pull link 100 which has attached to its forward end a hook terminal 101 that is adapted to engage over the bottom stud 70 of the rocker post 24. When the operating member 20 goes forward, and on its return movement, neither rocker 52 nor 53 is actuated during the normal addition or subtraction operation of the register. The

rockers

52 and 53 normally are held laterally out of the path of movement of the cam 43 on the operating member, as shown in Fig. 11. The rear rocker 53 is held in its outward position by the action of a displacement lever 102 that is pivoted intermediate its ends on a fulcrum 103 mounted in the support plate S. At its upper end the lever 102 has connection with a contractile spring 104 that is anchored to a point of attachment on the support plate S to bias the upper end of the lever forwardly in the position shown in Fig. 1. In this position a laterally and outwardly directed cam 105 on the lower end of the lever is engaged against the side of the rocker to hold the rocker angled outwardly in the position shown in Fig. 11. In this position the plate of the rocker is pivoted laterally on the mounting pin 54 against the bias of the spring 55, and the lug 96 on the rocker is held out of the path of travel of the cam on the operating member. Also, due to the angled position of the rocker, its inclined bottom edge will be held out of position with respect to the rear riser 49 on the cam of the operating member. Fig. 8 illustrates that the cam 105 is an outwardly directed portion that extends at a right angle from the plane of lever 102 and is provided with a rearwardly and inwardly inclined entrant edge 106, thus constituting the cam 105 substantially as a wedge member that is adapted to enter between the support plate and the flared lug 96 of the rocker when the displacement lever 102 pivots to bring the cam 105 into engagement with the rocker. When the displacement lever 102 is rocked to move the cam 105 forwardly, by means later described, the cam moves out from behind the rocker plate so that the rocker plate returns under the bias of the spring 55 against the support plate to the position as shown in Figs. 12 and 13. In this position its lug 96 and lower cam edge override the path of movement of the cam 43 on the operating member.

In like manner the forward rocker 52 is normally held out of the path of movement of the cam on the operating member by a second displacement lever 107 that is pivoted intermediate its ends to a fulcrum 108 mounted on the support plate S. The upper end of the lever 107 is biased forwardly by a contractile spring 109 connected between the end of the lever and a point of attachment on an element of the frame of the machine on which the apparatus is incorporated. The lever 107 also is provided at its lower end with a wedge cam 110 identical to the cam 105 on the lever 102. When the displacement lever 107 is rocked to the position shown in Fig. 1, its wedge cam 110 enters behind the rocker lug 97 and forces it laterally outward from the support plate into the position shown in Fig. 11, where both the rocker and its lug 98 are held out of the path of movement of the cam on the operating member. By reason of the holding action of the displacement levers 102 and 107, neither rocker 52 nor 53 can be actuated during the normal addition or subtraction operation of the register.

At the left hand side of the support plate a second pair of displacement levers functions similarly to the displacement levers on the right hand side for the purpose of moving the bell crank

rockers

50 and 51 out of the path of movement of the cam on the operating member. A displacement lever 111 is pivoted at the left hand side of the support plate on the fulcrum element 108. At its lower end the lever 111 is provided with a wedge cam 112 that is identical to the wedge cam 105 of its companion lever at the right hand side, except that it is angled oppositely to the cam 105. A second displacement lever 113 is pivoted on the fulcrum 103 and carries at its lower end a wedge cam 114 that is identical with the cam 112 on the forward displacement lever. in the normal operating position of the parts, as shown in Figs. 1 and 2, the

wedge cams

112 and 114 and their respective displacement levers are not engaged with the rockers and thus do not hold them out of the path of movement of the cam on the operating member. The lever 113 is biased into this non-engaged position by means of a contractile spring 115 connected between the upper end of the lever and a point of attachment on the support plate S. A link 116 has a pivotal connection 117 at its rear end with the upper end of the displacement lever 113, and has also a pivotal connection 118 with the upper end of the forward displacement lever 111. The bias of spring 115 thus serves to hold both displacement levers in forward position with their wedge cams out of engagement with the

rockers

50 and 51. The lever 116 extends forwardly and is provided at its end with a laterally directed stud 119 that is adapted to cooperate with means, later described, for imparting horizontal shifting movement to the lever for rocking the displacement levers 111 and 113. When the lever 116 is pulled forwardly, to the right with respect to Fig. 2, the displacement levers 111 and 113 are correspondingly rocked to move their lower ends rearwardly and thus to carry the

wedge cams

112 and 114 rearwardly to force the

rockers

50 and 51 outwardly out of the path of movement of the cam on the operating member in the position shown in Figs. 12 and 13. When thus conditioned, the cam 43 on the operating member 20 will have no effect on the linkage at the left hand side of the support plate when the operating member is cycled.

The forward end of the support plate S has secured thereto a vertically disposed stop plate 120 which extends transversely at opposite sides of the support plate, as shown in Fig. 6, for a sufficient vertical distance to provide a stop for the forward ends of the

links

92 and 100 at the right hand side of the support plate and for the links 63 and 74 at the left hand side. The stop plate 120 also provides a point of anchorage for a contractile spring 121 attached to the forward end portion of the link 92, and for a contractile spring 122 attached to the forward end portion of the link 100 at the right hand side of the support plate. In like manner, on the left hand side of the support plate, the stop 120 provides anchorage for a contractile spring 123 that is connected to the forward end portion of the link 63 and for a con tractile spring 124 that is connected to the forward end portion of the link 74-. These springs serve to bias the links forwardly into engagement against the stop plate 120 when they are not actively engaged with the studs of the rocker post 24. This bias of the springs serves to position the linkage so that the

rockers

50, 51, 52 and 53 are held in their proper positions for cooperation with the cam on the operating member. These springs serve also to pull their respective links and connected bell crank rockers back to normal position at all times except when being acted upon by the cam on the operating member. The connector links 65, 72 and 89 provide flexibility of coupling between the respective bell crank rockers and pull links, so that if the rocker 24 were held against rocking under the pull of the links for any reason, the bell crank rockers still would be permitted to rock under the influence of the cam on the operating member without damaging the links. In such case, the rearward throw of the pivots 90, 66 and 71 would merely pull the connector links rearwardly against the bias of their respective springs 95, 68 and 76 to pivot on the ends of their associated links without imparting any force greater than the tension of their respective springs.

When the mechanism is conditioned for the performance of a subtotal operation it is necessary that the register pinions remain in mesh with their racks as the rack'! go forward and that they be held in mesh during the return stroke of the racks so that the amount taken from the register in effecting the subtotal is restored to the register on return of the racks. This necessitates a disposition of bell crank rockers as shown in Fig. 12, in which the

rockers

50 and 51 at the left hand side of the support plate S are displaced out of the path of movement of the cam on the operating member, while at the same time the forward rocker 52 at the right hand side of the support plate is likewise displaced. The rocker 53 at the right hand side remains in position for actuation by the cam on the operating member. By virtue of this arrangement, when the operating member 20 goes forward it actuates only the rocker 53. This rocker, acting through the linkage previously described, throws the register pinions into mesh with their respective racks. The racks move in accordance with the movement of the operating member. When the operating member reaches its forward position the register pinions remain in engagement with their racks because the forward bell crank rockers are held out of the path of movement of the cam 43. When the racks return with the return movement of the operating member travelling back in the second half of its cycle, the register pinions remain in engagement with their racks.

The mechanism for effecting the subtotal operation 18 best shown in Figs. 8, 9, l0 and 3. The rod 125 from the subtotal key of the machine in which the mechanism is incorporated extends rearwardly into the zone of the timing mechanism, with its rear end supported for reciprocation in

elements

126 and 127 of the machine frame. The subtotal rod has a collar 128 secured thereon by a set screw 129. When the subtotal key is actuated the rod 125 is moved rearwardly to carry with it the abutting depending end portion 130 of a horizontal arm 131 that is coupled with a parallel horizontal lever 132 in the manner shown in Fig. 14. The spaced parallel ends of the

levers

131 and 132 are provided with pins 133 which are seated in sockets in the ends of a sleeve 134 that is freely rotatable on a depending stud shaft 135 that has threaded stem attachment 136 at its upper end with a support member 137 forming a part of the machine frame. A headed bolt 138 passed through the end of the lower lever 131 has threaded attachment in a receiving socket in the end of the shaft 135 to retain the lever against the end of the sleeve 134. A spacer sleeve 139 between the upper lever 132 and the support 137 disposes the connection at the proper point for cooperation with other elements of the mechanism. By reason of the coupling sleeve 134 it is evident that the

levers

131 and 132 are connected for movement in unison. Rearward travel of the subtotal rod acting through the collar 128 serves to rock the assembly of

levers

131 and 132 on the fulcrum provided by the shaft 135 so that the other end of the lever 132 is moved forwardly. The end of the lever 132 carries an upstanding stud 140 that engages behind the stud 119 on the link 116 which couples the upper ends of the two displacement levers at the left hand side of the support plate. As the end of the lever 132 is rocked forwardly the stud 119 is carried forward to impart a forward pull to the lever 116 and thereby to rock the displacement levers 111 and 113 to carry their

respective wedge cams

112 and 114 into position behind the bell crank rockers 5t) and 51, so that these rockers are held out of the path of movement of the cam on the operating member. At the same time, the rocking movement of the lever 132 is transmitted through a link 141 to free the cam wedge of the displacement lever 102 from the rear bell crank rocker 53 at the right hand side of the support plate so that the rocker moves into the path of travel of the cam on the operating member. The link 141 extends diagonally rearwardly and downwardly with respect to the assembly and at its upper forward end it is provided with a horizontally directed lug 142 that has a pivotal connection 143 with the end of the lever 132. Adjacent its lower end, the link 141 has a pivotal connection 144 with the lower end portion of the displacement lever 102, so that forward movement of the link 141 under actuation by the lever 132 serves to rock the lower end of the displacement lever 102 forwardly and release its wedge cam 195 from engagement with its associated bell crank rocker 53.

When the mechanism is to be conditioned for total taking operation, it is necessary that the same operations for subtotaling be carried out except that when the racks begin their return stroke the register pinions require to be disengaged from their racks. This requires that the parts be disposed as shown in Fig. 13, with the forward bell crank rocker S2 at the right hand side of the support plate disposed in the path of movement of the cam on the operating member. This disposition of parts is effected by a joint movement of the rod 145 from the total key of the machine and the subtotal rod 125. As shown in Fig. 10, the rod 145 from the total key has end contact with a set screw-anchored collar 146 on the subtotal rod 125, so that when the total rod 145 is moved rearwardly under actuation of its key, it carries with it the subtotal rod to accomplish the disposition of the linkage at the left hand side of the support plate in the manner previously described. Forwardly of its point of anchorage with the collar 146 the total rod 145 has anchored thereon a collar 147 that abuts the tip of a short lever 148 that is disposed alongside the forward end portion of a longitudinal shift bar 149. The short lever 148 has a pivotal connection 150 with the end of the bar 149 and is provided with a fixed stud 151 in engagement with an edge portion of the shift bar. A contractile spring 152 connected between the stud 151 and a stud 153 carried by the end of the bar 149 provides a connection between the bar and the short lever 148 so that when the tip of the lever 148 is moved rearwardly upon actuation of the total key in the machine, the pull of the spring 152 acts to shift the bar 149 rearwardly. The spring 152 has sufficient tension to accomplish this movement but is capable of yielding in the event of jamming or holding any of the parts so that damage or breakage is avoided.

A contractile spring 154 between a point of attachment on a support element of the machine frame and a point of attachment on the bar 149 serves to bias the bar to move forwardly so that its connected short lever 148 is held in contact with the collar 147 on the total rod. This spring serves also to return the bar to normal position, as shown in Fig. 10, when released. The bar 149 shifts horizontally on the frame element 126. At its forward end it is provided with a closed end slot 155 which plays over a guide stud 156 anchored to the frame, and at its rear end the bar has a longitudinal end opening slot 157 that is guided over a transverse shaft 158 that extends through the frame 126 to a bearing support in the support plate S. The slot 157 and the bearing in the support plate S journal the shaft 158 for oscillation. The end of the shaft 158 outwardly of the bar 149 has rigidly secured thereto a collar 159 to which is fixedly attached a finger 160 having a terminal portion disposed in the path of travel of a cam element 161 fixed to the bar 149. At its opposite end adjacent the support plate S as shown in Figure 7 the shaft 158 has fixedly secured thereto a cam element 162 normally engaged over the upper edge of a link 163 which is adapted to couple the displacement levers 102 and 107 for movement in unison. The rear end of the link 163 has a pivotal connection 164 with the upper end of the rear displacement lever 102 and adjacent its forward end the link is formed with a hook 165 adapted for engagement over a lateral stud 166 secured to the adjacent upper portion of the forward displacement lever 107. A biasing spring 167 between a point of attachment on the rear end portion of the link 163 and a point of attachment on the upper end of the rear displacement lever 102 normally biases the link 163 upwardly so that the hook 165 clears the displacement lever stud 166 when the rear displacement lever 102 is rocked to move its upper end rearwardly. In this normal position of the parts the upper edge of the link 163 is in engagement with the cam 162, as shown in Fig. 7. When the total rod 145 is moved rearwardly the bar 149 is correspondingly shifted to carry its cam 161 into engagement with the finger 160 and this action cams down the finger 160 to effect a corresponding rotation of the shaft 158 clockwise With respect to Figs. 10 and 7. As shown in Fig. 7, this clockwise rotation of the shaft 158 carries down its cam 162 to depress the link 163 and carry its hook 165 into a position where it will engage the stud 166 on the forward displacement lever 107 when the rear displacement lever 102 is rocked to exert a pull on the link. Consequently, when the link 141, Fig. 3, is pulled forwardly by the action of the lever 132, as previously described, the rocking movement imparted to the rear displacement lever 102 is similarly imparted to the forward displacement lever 107, so that both displacement levers move in unison to withdraw their respective wedge cams from the bell crank

rockers

52 and 53. This action permits these bell crank rockers at the right hand side of the support plate S to move under the bias of their springs 55 into the path of travel of the cam on the operating member.

Thus it will be seen that when the total rod 145 is actuated from its key, mechanism is brought into operation, as described, to eifect a coupling of the upper ends of the displacement levers at the right hand side of the support plate S, and this coupling is normally ineffective under all other conditions. It is within the purview of this invention that a similar coupling arrangement may be provided for the two displacement levers at the left hand side of the support plate S. Such an arrangement makes possible an independent operation of the left hand displacement levers so that the parts can be conditioned for a non-add operation of the racks and operating member. All that is necessary in such case is to remove all bell crank rockers except that at the rear left hand side from the path of travel of the cam on the operating member. It is the bell crank rocker at the rear on the left hand side of the support plate which controls the shifting of the register pinions to carry them out of engagement with their racks at the start of forward movement of the operating member and the racks.

The above description is directed to a specific embodiment of the principles of this invention. The principles may be incorporated in various other physical expressions and it is to be understood that the invention is not limited to the details of the present disclosure. Broad aspects of the invention include a combination in which the operating member is movable between two limit positions and has associated with it a plurality of devices, such as actuators or the like, that are adapted for driven movement by the operating member to accomplish shifting of the register pinions into and from mesh with their respective racks. The operating member cooperates with a device located adjacent one limit of its travel to shift the pinions in one direction, and it cooperates with another device located adjacent the same limit position of its travel for shifting the pinions in an opposite direction. At the other limit of travel, the operating member cooperates with a device for shifting the pinions in one direction, and with another device located at the same limit position for shifting the pinions in an opposite direction. All the devices are driven by a single fixed element of the operating member. Incorporated into this assembly is a selective control means by which the various devices are engaged with the driving element of the operating member or disengaged therefrom selectively either singly or in any desired combination. A control means, not shown, operated to move link 116 to the right with respect to Figure 2, would hold from engagement all the devices so that the operating member may move through a cycle without effecting any shift of the register pinions.

Another broad principle of the invention involves a plurality of linkages arranged so that one linkaged set operates in reverse to the other. These linkages are selectively controlled to establish a driving connection between the operating member and the pinion shifting mechanism. When one linkage provides the connection the pinions are shifted in one direction and when another linkage provides the connection they are shifted in an opposite direction. Modulating means such as earn 162 shown in Figure 7 is employed in connection with the linkages to alter their mode of operation under selective control to provide various combinations of register shifting.

The invention also contemplates in its broad aspects a plurality of selectively operative driving connections between the operating member and the register shift mechanism. These connections are normally conditioned to effect a shifting of the register pinions regardless of the position assumed by the pinions at any given instant in the cycle of the operating member. Means is provided for disabling any selected connection either wholly or in part so that the connection operates through those parts not disabled. Another broad principle incorporated in the invention deals with the moving parts of the mechanism. In this invention, when a register pinion shift is carried out, all those movable parts of the mechanism not ment of the cam. The actuators are adapted to be driven by the cam when the operating member is moving in a certain direction and when the cam clears any actuator the actuator returns to a position which normally would block return movement of the cam. The actuator is provided with cam means cooperative with the cam on its return movement to shift the actuator out of obstructing relation to the cam for that interval necessary to permi the cam to continue its movement to the point of reengagement with the actuator. When this point is reached the biasing means of the actuator returns it into operativ engagement with the cam.

I claim:

1. In a calculating machine, a frame, an operating member movable in a cycle between two limit positions, a cam on the operating member and movable therewith in a predetermined path, a set of register pinions adapted for shifting in opposite directions, two pairs of pinion shift actuators on opposite sides of said path and mounted on said frame for movement individually into and out of said path, the actuators in each pair being disposed adjacent opposite ends of said path, and means selectively operative to dispose individual actuators in the path of travel of the cam for actuation thereby and to remove the actuators from said path of travel.

2. The structure of claim 1, and the actuators in each plaitr being relatively reversed as to the direction of pinion s i t.

3. The structure of claim 1, and the two pairs of actuators being relatively reversed as to the direction of pinion shift.

4. In a mechanism for shifting the register pinions in a calculating machine into and from rack mesh, a planar support, a pinion shift actuator movable thereon, a reciprocable driving member, a cam on said member in the plane of the support, said actuator having a portion engageable with the cam from one side thereof when the cam is in a travel limit position to drive the actuator, means biasing the actuator into the path of travel of the cam, and a lateral deflector portion on the actuator engageable by the cam when nearing a limit of its travel to shift the actuator laterally out of the path of cam travel until the cam reaches that limit.

5. In a mechanism for shifting the register pinions in a calculating machine into and from rack mesh, a planar support, a pair of pinion shift actuators movable thereon in spaced relation at one side thereof, a pair of pinion shift actuators movable thereon in spaced relation at the other side thereof, a reciprocable driving member engageable with said actuators in the plane of said support,

an individual displacement lever pivoted on the support adjacent each actuator, and a cam on each lever engageable with its associated actuator to prevent engagement with said driving member.

6. In a calculating machine having a pinion shiftable selectively into meshing engagement with racks, an operating member movable between two positions of adjustment during a cycle of operation, an actuating cam movable with the operating member, a plurality of actuation means separately movable and said means independently shiftable relative each other into and out of the path of said actuating cam, an operative connection between each of said actuating means and said pinion for eifecting adjustment thereof responsive to operative engagement between said actuating means and said cam, means enabling movement of the pinion by any one of the actuating means independently of movement to any other of the plurality of said actuating means.

7. In a calculating machine having a pinion shiftable selectively into and out of meshing engagement with racks, a rocker arm pivoted intermediate its ends, an operative connection between said rocker arm and said pinion for causing shifting movement thereof responsive to rocking movement of the arm between two positions of adjustment, an operating member movable between two positions of adjustment during a cycle of operation, an operative cam movable with the operating member, a plurality of actuator means separately mounted for swinging movement in a place into and out of the path of the cam and for rocking movement in another plane responsive to operative engagement with said cam, an operative connection between said actuator means and said rocker arm for effecting rocking movement thereof in response to operative engagement between any one of the said actuator means and said cam, and means enabling rocking movement of the rocker arm independent of movement of any other said actuator means.

8. In a calculating machine as claimed in claim 7 in which the operative connection between said actuator means and the rocker arm comprises linkages pivoted at one end to the actuator means, and having a hooked portion at the other end, and posts extending from said rocker arm on opposite sides of the pivot and adapted to be operatively engaged by the hooked end portions of the linkages.

9. In a calculating machine as claimed in claim 8 in which the hooked end portion of each of the linkages comprises an elongate groove in which the posts may freely slide to permit lost motion whereby the rocker arm may be shifted between its two positions of adjustment independently of the linkages and the actuator means associated therewith.

10. In combination in a machine of the type described, a fixed frame member, a shiftable set of register pinions, a shifting member mounted for movement relatively to said frame member and connected with said pinions to shift them by such movement, an operating member shiftable linearly forward and back during a cycle of operation, a cam member thereon, a plurality of actuators mounted on said frame member independently of said pinion shifting member for movement between normal and operated positions of adjustment and for movement into and out of the path of said cam, means biasing said actuator into normal position in the path of said cam, means forming a part of said cam and said actuator for causing shifting movement of said actuator from normal position to operated position responsive to operative engagement with the cam upon movement in one direction and for deflecting said actuator in another direction out of the path of said cam upon operative engagement during movement of the cam in the opposite direction, and individual connecting means each connecting a respective one of said actuators with said pinion shifting member and each comprising elements coacting to move said shifting member to shift said pinions upon movement of the respective actuator from said normal position to said operated position by said cam, to permit movement of said shifting member by any other of said actuators without movement of said respective actuator, and to permit said respective actuator to be deflected out of the path of said cam without moving said pinion shifting member.

11. In a calculating machine, an operating member movable between two limit positions in a cycle of operation, a set of register pinions adapted for shifting movement in opposite directions, actuating means on said operating member and movable therewith in a predetermined path, two pairs of pinion shift actuators, said two pairs being on opposite sides of said path and the two actuators of each pair being adjacent opposite ends of said path, said pinion shift actuators being mounted for shifting movement in one direction into and out of the path of movement of said actuating means and for shifting movement in a different direction from the first responsive to actuation by said actuating means, means individually biasing all of said actuators into the path of travel of said actuating means for engagement thereby, and means operative selectively to remove individual actuators from the path of travel of said actuating means.

12. In a calculating machine, an operating member movable between two limit positions in a cycle of operation, a set of register pinions adapted for shifting movement in opposite directions, actuating means on said operating member and movable therewith in a predetermined path, two pairs of pinion shift actuators, said two pairs being on opposite sides of said path and the two actuators of each pair being adjacent opposite ends of said path, said pinion shift actuators being shiftable in one direction into and out of the path of movement of said actuating means and shiftable from normal to operated position in another direction responsive to actuation by said actuating means, means individually biasing each of said actuators into the path of travel of said actuating means for operative engagement thereby, means operative selectively to remove said actuators from the path of travel of said actuating means, and means individually biasing each of said actuators from operated to normal position upon disengagement by said actuating means.

l3. In a calculating machine of the type described, an operating member movable in a cycle between two limit positions, a set of register pinions adapted for shifting movement in opposite directions, actuating means on the operating member shiftable therewith in a path of movement, a pair of pinion shift actuators positioned on each side of the path of movement of the operating member adjacent each of the limit positions, said pinion shift actuators being shiftable in one direction into and out of the path of movement of said actuating means and shiftable in another direction from normal to operated position responsive to actuation by said actuating means, means individually biasing each of said actuators into the path of travel of said actuating means for engagement thereby, and means operative selectively to remove said actuators from the path of travel of said actuating means.

14. In a calculating machine of the type described, an operating member movable in a cycle between two limit positions, a set of register pinions adapted for shifting movement in opposite directions, actuating means on the operating member shiftable therewith in a path of movement, a pair of pinion shift actuators positioned on each side of the path of movement of the operating member adjacent each of the limit positions, said pinion shift actuators being shiftable in one direction into and out of the path of movement of said actuating means and shiftable in another direction from normal to operated position responsive to actuation by said actuating means, means individually biasing each of said actuators into the path of travel of said actuating means for engagement thereby, means operative selectively to remove said actuators from the path of travel of said actuating means, and means individually biasing each of said actuators to return from operated position to normal position upon its engagement by said actuating means.

15. In a calculating machine, an operating member movable in a cycle between two limit positions, a set of register pinions adapted for shifting movement in opposite directions, actuator means biased to position to engage the operating member adjacent one limit position for actuation thereby to shift the pinions in one direction, other actuator means biased to position to engage the operating member adjacent its other limit position for actuation thereby to shift the pinions in an opposite direction, said actuator means being movable from normal to actuated position upon engagement with said operating member for actuating shifting movement of the pinions, means coupled with said actuator means for returning the actuator means to normal position independent of shifting movement of the pinions, and means operative selectively to hold out of biased position any of said actuator means independently of each other.

16. In a calculating machine, an operating member movable in a cycle between two limit positions, a set of register pinions adapted for shifting movement in opposite directions, actuator means biased to engage the operating member adjacent one limit position for actuation thereby to shift the pinions in one direction, other actuator means biased to engage the operating member adjacent its other limit position for actuation thereby to shift the pinions in an opposite direction, and similar actuator means also adjacent the limit positions of the operating member for actuation thereby to shift the pinions in a reverse direction relative the limit position of first said actuator means, and means whereby the movement of any of said actuator means by said operating member is effected independently of movement to any other of said actuator means.

17. In a calculating machine, a supporting plate, an operating member movable linearly forward and back in a cycle of operation, a cam having two working sides operatively connected with said operating member for movement therewith, a set of register pinions adapted for shifting movement in opposite directions, pinion shift actuators on one side of the cam and other pinion shift actuators on the other side of the cam, means mounting said actuators on the supporting plate in a position normally to lie in the path of the cam, means operable by each actuator for shifting the pinions in one direction, means individually biasing each of said actuators into the path of travel of said cam for engagement thereby to drive the actuators, and means on the plate operative selectively to remove individual actuators from the path of travel of the cam.

References Cited in the file of this patent UNITED STATES PATENTS 1,118,682 Reed Nov. 24, 1914 1,934,747 Sundstrand Nov. 14, 1933 1,946,505 Sundstrand Feb. 13, 1934 1,957,501 Horton May 8, 1934 2,110,987 Kammel Mar. 15, 1938 2,194,270 Sundstrand Mar. 19, 1940 2,222,373 Rauh Nov. 19, 1940 2,226,960 Anderson Dec. 31, 1940 2,255,623 Landsiedel Sept. 9, 1941 2,285,311 Sundstrand June 2, 1947