US3136482A

US3136482A - oldenburg etal

Info

Publication number: US3136482A
Authority: US
Publication date: 1964-06-09
Anticipated expiration: 1981-06-09

Description

June 9, 1964 K. F. OLDENBURG ETAL ACCUMULATOR CONTROLS FOR CALCULATING MACHINE 9 Sheets-Sheet 1 Filed Sept. 25, 1961 June 9, 1964 K. F. OLDENBURG ETAL ACCUMULATOR CONTROLS FOR CALCULATING MACHINE Filed Sept. 25, 1961 9 Sheets-Sheet 2 M E U MM 0 ya 7 VD A 417 NM ma w Mam/ June 9, 1964 K. F. OLDENBURG ETAL 3,

ACCUMULATOR CONTROLS FOR CALCULATING MACHINE Filed Sept. 25, 1961 9 Sheets-Sheet 3 244 z z5a INVENTORS KENNETH [moan/wee MILTON v 56022454144 BY f/Cl/ARD J: MARK az AM i mum/5 June 9. 1964 K. F. OLDENBURG ETAL 3,136,482

ACCUMULATOR CONTROLS FOR CALCULATING MACHINE 9 Sheets-Sheet 5 F'iled Sept. 25, 1961 FFIHFIFIHFF :EIE l@ June 9, 1964 K. F. OLDENBURG ETAL 3, 3 ,48

ACCUMULATOR CONTROLS FOR CALCULATING MACHINE Filed Sept. 25, 1961 9 Sheets-Sheet 6 55 wrz/vraes a xsA/A/ir/mowwaz es M/uav u 8602245044 4 5y HCMED-SZMAEK seam/rm ATTOENEY June 9, 1964 K. F. OLDENBURG ETAL 3,135,482

ACCUMULAT R CONTROLS FOR CALCULATING MACHINE 9 Sheets-Sheet 7 Filed Sept. 25, 1961 FIE- l5 MILTON vsmzggrmf are/rmgma-mez BEKM/[KU June 9, 1964 K. F. OLDENBURG ETAL 3,136,482

ACCUMULATOR CONTROLS FOR CALCULATING MACHINE;

Filed Sept. 25, 1961 9 Sheets-Sheet 8 zse Q37 .lfILfil L INVENTORS 6 2W 7 m M Emu E w; m MM .fi m oi ENR ZM m me/ Mea n 1964 K. F. OLDENBURG ETAL ACCUMULATOR CONTROLS FOR CALCULATING MACHINE 9 Sheets-Sheet 9 Filed Sept. 25, 1961 I I J FIE- Q EJ! 263 M JT'ILTIL :1:

INVENTORS (EA/NE 7/! F 0L DEA/8026 1 4/170 L JZUZZAFA V4 BY BMW/1E0 J". MAEK a mu 7N6 ATTOE/Vf) rIm- :1:

Patented June .9, 1964 3,136,482 ACCUMULATOR CGNTROLS FOR CALCULATING MACHINE Kenneth F. Oldenburg, Monterey Park, Milton V. Scozzafava and Richard S. Mark, Arcadia, and Bryan F.

Kuhne, Monrovia, Calif., assignors, by mesne assign- I ments, to Addmaster Corporation, San Gabriel, Calif., a corporation of California Filed Sept. 25, 1961, Ser. No. 140,547

8 Claims. (Cl. 235-60) of functions whereby to reduce the total number of parts and cost of the machine.

Another object is to provide a simple and effective mechanism for causing subtract and add control elements to performing totaling and subtotaling functions, respectively, under certain conditions.

A still further object is to provide a simple and effective means to print symbols representing the types of factors and results printed by a listing machine of' the above type.

The manner in which the above and other objects are accomplished will be readily understood on reference to the following specification when read in conjunction with the accompanying drawings, wherein:

FIG. I is a longitudinal sectional view of an addinglisting machine embodying a preferred form of the present invention.

FIG. 2 is asectional plan view illustrating part of the pin carriage'and is taken along the line 2-2 of FIG. 1.

FIG. 3 is a perspective view of the pin carriage.

FIG. 4 is an enlarged sectional view through a portion of the pin carriage.

FIG. 5 is a sectional plan view illustrating the printing sectors and part of the main drive mechanism and is taken substantially along the line 5-5 of FIG. 1.

FIG. 6 is a sectional view taken along the line 6-6 of FIG. 5 illustrating mainly the accumulator control cam and associated follower.

,7 FIG. 7 is another sectional view through the accumulator control cam and is taken along the line 7-7 of FIG. 5.

FIG. 8 is another sectional view through the accumulator control cam and is taken along the line 8-8of FIG. 5.

FIG. 9 is a sectional view illustrating the sector, ribsubstantially along the line 99 of FIG. 5.

FIG. 10 is a sectional view illustrating the aligner control cam operating mechanism.

FIG. 11 is a plan view taken along the line 1111 of FIG. 9 illustrating the mechanism for operating the printing ribbon and zero elimination control slides.

FIG. 12 illustrates a timing chart of the machine.

FIG. 13 is a sectional view illustrating the clutch control and is taken along the line 13-43 of FIG. 5.

FIG. 14 is a sectional view taken substantially along the line 14-14 of FIG. 1 illustrating the printing ribbon and zero elimination control slides in normal retracted condition. V

FIG. 15 is a sectional view similar to FIG. 14 but is taken substantially along the line 15-15 of FIG. 1 illustrating the printing ribbon and zero elimination control slides in extended conditions. i

FIG. 16 is a transverse sectional view through the combined ribbon magazine and inker and is taken along the line 16--16 of FIG. 15.

FIG. 17 is a sectional view through the combined ribbon magazine and inker and is taken along the line 1717 of FIG. 16.

FIG. 18 is a sectional plan view through the printer and is taken substantially along the line 18-18 of FIG. 1.

FIG. 19 is a sectional view illustrating the interlock slide for the machine control bars.

FIG. 20 is a sectional view illustrating the paper advance mechanism and is taken along the line 20-20 of FIG. 5. 7

FIG. 21 is a transverse sectional view through the key board and is taken along the line 21-21 of FIG. 1.

FIG. 22 is a sectional view through the pin' carriage illustrating partof the controls for the symbol print sector.

FIG. 23 is a sectional plan view taken along the line 2323 of FIG. 22.

FIG. 24 is a sectional plan view taken substantially along the line 2424 of FIG. 1 illustrating part of the accumulator controls and pin carriage return mechanism.

FIG. 25 is a sectional side view of the pin carriage return cam and follower and is taken along the line 25-25 of FIG. 24.

FIG. 26 is a fragmentary view taken in the direction of the arrow 26 in FIG. 24.

General Design The present invention is disclosed as associated with a ten-key adding-listing machine. However, it should be understood that the same, at least in its broader aspects, could be equally well associated with other types of printing machines of this general class.

Digits of a value are entered into the machine through ten amount keys, four of which are shown at 11, which keys range in value from 0 to 9. Operation of the machine to perform digit entry and total or subtotal functions is controlled by depressible add-subtotal control bar 12 and a subtract-total bar 13 (FIGS. 13 and 19).

Depression of an amount key sets an appropriate stop pin 14 (FIG. 1) in a pin carriage, generally indicated at 15, which shifts laterally of the machine into cooperative relation with combined differential actuators and printing sectors 16. Each of the latter carries a series of type characters 17 on its periphery, ranging from 0 to 9, the character 0 being located at the clockwisemost location relative to the rest of the series.

The sectors 16 cooperate with a printing mechanism, generally indicated at 18, to print amounts registered by the sectors 16 onto a paper strip 20. The sectors also cooperate with an accumulator, generally indicated at 21, to enter amounts therein or to remove accumulated amounts during totaling and subtotaling operations.

The machine is driven by an electric motor (not shown) through a cyclically operable clutch, generally indicated at 22 (FIGS. 5 and 13), the clutch being effective to drive a main shaft 23 (FIGS. 1, 6, 9, 1O, 13 and 25) one complete revolution during each cycle of operation. The shaft 23 carries various cams, to be described hereinafter, for driving dilferent operating units of the machine in proper timed relation and for advancing the paper strip one increment as an incident to each cycle.

Keyboard The amount keys 11 are mounted on key stems 24 (FIGS. 1 and 21) which are slideable vertically in slots provided in upper and lower

key frame plates

25 and 26, respectively, forming part of the framework of the machine. Tension springs 27 attached at their ends to the lower frame plate 26 extend under the key stems to normally hold the amount keys in raised positions. Such springs extend across openings 28 in the plate 26 to permit depression of the keys.

Each key stem has an extension 29 which is attached to the upper end of a respective flexible cable 36. The various cables are vertically aligned with each other and are slideably mounted for endwise movement in grooves 31 formed in a guide block 32 suitably attached to the lower frame plate 26. The various cables 39 terminate in an arcuate pattern concentric with a shaft 33 which rotatably supports the sectors 16. The shaft is rotatably mounted in bearings formed in side frame plates 34 and 35 (FIG. forming part of the machine framework.

Pin Carriage The pin carriage (FIGS. 1, 2, 3, 4, 22 and 23) is formed of an arcuate body 36 of plastic or the like mounted within an enclosing frame 37. The latter is provided with bearing

tabs

38 and 39 at its lower end which are slideably mounted on a stationary rod 40 extending across the machine and suitably supported in frame plates 41 and 42 forming part of the machine framework.

The pin carriage has an extension 43 which projects through a slot 44 in a channel member 45 secured at its ends to the frame plates 41 and 42. A slide 46 attached to the extension 43 is guided by the channel member to likewise guide the upper end of the pin carriage across the machine. The extension 43 also extends through a slot 47 in a machine cover 48 and terminates in a knob 50, permitting the pin carriage to be returned manually to its home position shown in FIG. 2, if so desired.

The stop pins 14 are slideably mounted for endwise movement in a field of openings in the pin carriage body 36. Each pin has a head 51 and a body which is bifurcated to form two spring legs 52 which yieldably press outwardly against the adjacent edges of a respective opening in the pin carriage body, thereby frictionally maintaining the pin in either of two positions to which it may be set.

It will be noted that the stop pins 14 are arranged in a plurality of vertical columns and are located in horizontal rows aligned with the lower ends of the flexible cables 30. Thus, upon depression of a selected amount key 11, the respective cable 30 will be moved endwise to likewise move an aligned stop pin from its normal ineffective position shown in FIGS. 1, 3 and 4 to a position wherein it forms an abutment in the path of a shoulder 53 formed on an aligned sector 16.

An additional row of escapement pins 54, similar to pins 14, are located above the latter pins. Such pins cooperate with a stop shoulder 55 (FIGS. 1 and 2) extending downwardly from the channel member 45 to normally maintain the pin carriage in its home or any other denominational position. The pins 54- are aligned with the various vertical columns of pins 14 and are engage able by a finger 56 of a bail 57 which is pivotally supported at 58 in frame plates 60 and 61 forming part of the machine framework for movement about a horizontal axis. The bail 57 is pivotally connected at 62 to a second bail 63 (see also FIG. 21) which is pivotally supported at 64 from movement about an axis extending longitudinally of the machine. The bail 63 underlies the extensions 29 of the amount keys so that upon depression of any thereof the bail will rock bail 57 to depress Whichever escapement pin is aligned with the finger 56.

The pin carriage 15 is urged to the left in FIGS. 2 and 5 by a tension spring 64 (FIG. 24) connected between a part of a bottom frame plate 65 and a lever 66 fulcrumed at 67 on the plate 65 and provided with a slot 68 which embraces a pin 70 depending from the pin carriage. Thus, upon depression of any amount key to set an appropriate stop pin 14, the

bails

63 and 57 will depress an aligned escapement pin 54, permitting the pin carriage to escape one column to the next wherein the next escapement pin 54 will arrest against the stop shoulder 55.

A zero stop blade 71 is pivotally supported at 72 in the pin carriage frame 37 for movement about a horizontal axis and is urged upwardly by a spring (not shown) toward a position in blocking relation with the shoulders 53 of those sectors 16 with which it is aligned.

The blade 71 has its forward edge 73 aligned with the lower or zero row of stop pins 14 so as to block the aligned sectors 16 at zero registration.

A cam formation 74 is formed on the blade 71 and when the pin carriage is in its home position, as depicted in FIG. 3, the cam formation will cam against a ledge 75 on the frame plate 60, moving the blade downwardly out of blocking relation with the sectors. Therefore, during totaling and subtotaling operations wherein the pin carriage is located in its home position, as depicted in FIG. 3, the blade 71 will permit all sectors 16 to be differentially advanced under control of the accumulator.

Pin Carriage Return Mechanism During the latter stages of a machine cycle, the pin carriage is returned to its home position shown in FIGS. 2 and 3 by a cam 76 (FIG. 25) carried by the drive shaft 23. The cam 76 engages a roller 77 on a cam follower lever 78 which is pivotally supported at 80 and is pivotally connected at 81 to a link 82 (see also FIG. 24). The latter is coupled through a pin and open slot connection 83 to a bell crank 84 fulcrumed at 67 independently of the lever 66. A bypass pawl 85 is pivoted at 86 on the bell crank and is urged counterclockwise relative thereto by a tension spring 87 extending between an ear 88 on the bypass pawl and a part of the bell crank.

The cam 76. is effective to cause link 82 to first swing the bell crank 84 counterclockwise of its position illustrated in FIG. 24 against the action of a relatively strong tension spring 90. During this movement, the car 88 on pawl 85 will recede from a stationary projection 91, allowing the spring 87 to rock the pawl counterclockwise and into the path of movement of an ear 92 on the lever 66. Accordingly, during clockwise return movement of the bell crank 84 under the action of spring 90, the pawl 85 will engage the ear 92, causing the lever 66 to drive the pin carriage to the right toward its home position against the action of the relatively weaker spring 64. During this movement of the pin carriage, depressed ones of the stop pins will engage a stationary arcuate cam 89 (FIG. 22) extending between the channel member 45 and the plate 65, camming those stop pins outwardly to their normal positions.

As the pin carriage moves into its home position, the ear 88 will strike the projection 91, rocking the pawl 85 clockwise so that it will pass below the car 92. The pin carriage is thus freed of the bypass pawl so that it may again be indexed to the left by depression of the amount keys.

Means are provided to perform repeat operations. For this purpose, a repeat key 99 (FIG. 21) is provided, the stern of the latter being slideable vertically in a slot 290 formed in a frame plate 291. A tension spring 292 urges the key into its upper illustrated position. Upon depression of the repeat key, an inclined camming surface 293 on its stem will cam the link 82 to the left in FIG. 24 sufliciently to uncouple the link from the bell crank 84 so that the link will be ineffective to return the pin carriage. The spring 292 is also effective to hold the depressed repeat key in a position slightly cocked to the left wherein a latching shoulder 293 on the key stem is effective to latch under a ledge 294.

Main Drive and Controls Therefor The machine is driven by a suitable motor (not shown) through the cyclic clutch 22 (FIGS. 5 and 13). The latter comprises a pawl 94 pivotally supported at 95 on a disc 96 attached to the drive shaft 23. The pawl is urged toward driving engagement with a drive ratchet 97 by a yieldable tail 98 on the pawl, which tail engages a pin 100 on the disc. However, normally, the pawl is held out of driving engagement with the ratchet by a clutch dog 101. The latter is provided with slots 102 which slideably embrace frame studs 103 whereby to guide the clutch dog in and out of blocking engagement with the clutch pawl 94.

The clutch dog is coupled at 104 to a control slide 105 having slots 106 which are guided over stationary projections 107 extending from the machine framework, the slide being urged to the right in FIG. 13 by a tension spring 108 to normally maintain the clutch in its illustrated disengaged condition.

The control slide 105 has inclined camming surfaces 110 engageable by projections 111 extending laterally from stems 112 and 113 on which the control bars 12 and 13, respectively, are mounted. Thus, when one or the other of such control bars is depressed, the clutch dog 101 will be withdrawn to cause a cycle of operation. An car 109 on the clutch dog is effective, when the latter is actuated, to close contacts 119 located in the power circuit of the drive motor for the machine.

In order to prevent simultaneous depression of the control bars 12 and 13, an interlock slide 114 (FIG. 19) is provided, the latter having slots 115 thereon guided over the stationary projections 107. An inclined guideway 116 in the interlock slide 114 embraces a projection 117 on the stem. 113 while a vertical slot 118 in the slide underlies a projection 120 on the stem 112.. Thus, depression of the bar 13 will cause the slide 114 to move to the left to position a shoulder 121 directly below the projection 120 to prevent concurrent depression of the bar 12. On the other hand, depression of the bar 12 will lower the projection 120 into slot 118 to prevent shifting of the slide 114 by depression of the bar 13.

Sector Drive The various printing sectors 16 are yieldably driven clockwise from their home positions illustrated in FIG. 1 during digitizing and totaling operations by a bail rod 122. The latter is mounted at its opposite ends on gear sectors 123 and 124 (FIGS. 5 and 9). The sector 124 meshes with a second sector 125 pivoted on a shaft 126 and carrying a roller 127 which engages a cam groove 128 formed in a cam 130 suitably attached to the drive shaft 23.

The bail rod 122 extends through openings 131 in the various sectors 16 and is normally engaged by a detent shoulder 132 formed on a yieldable tail 133 extending integrally with each sector. As the bail rod is rocked clockwise from its home position, it will correspondingly rock the sectors 14 through engagement with the detent shoulders 132 until they strike depressed stop pins 14 in the pin carriage during digit entry operations or until they are arrested by the accumulator during totaling and subtotaling operations, whereupon the detenting shoulders 132 on the tails 133 will yield, permitting the bail rod to proceed to the limit of its excursion.

It should be noted at this time that each sector 16 has a pin 129 thereon which arrests against a stationary comb plate 134 after the sector has advanced 9 incremerits.

After the printing phase of a machine cycle, the bail rod 122 will be returned by the cam 130 and, in doing so, the frictional engagement between the bail rod and the tails 133 will drive the sectors slightly beyond, i.e., approximately 2, counterclockwise of their zero positions where they are arrested by the comb plate 134, the latter being engaged by pins 135 extending from the sectors. The bail rod will continue to slide along the tails 133, coming to rest adjacent edges 136 of the respective shoulders.

Printer and Paper Feed As noted heretofore, the sectors 16 cooperate with the printing mechanism 18 to print amounts registered by the sectors onto the paper strip 20.

The strip 20 is fed from a supply roll 137, between feed rolls 138 and 139, through a guideway 140 and past a printing station located between the sectors 16 and respective printing hammers 141. From such station, the strip is guided upwardly at substantially 90 over a stationary guide plate 142 and behind a transparent tearoff bar 143. It will be noted that the strip is deflected upwardly in a relatively sharp bend by the tearolf bar.

The hammers 141 are guided for endwise movement at their upper ends in guide slots formed by a cross brace 144 extending between the frame plates 60 and 61. The lower ends of the hammers have slots 145 which are guided over a guide bar 146 also extending between the frame plates 60 and 61.

A leaf spring 147 (see also FIG. 18) is secured by rivets 148 to the underside of the bar 144 and is formed into a plurality of spring fingers 150 at its forward end, each engaging in a notch 151 in a respective hammer whereby to urge the hammers downwardly toward printing contact with the paper strip. However, the spring fingers are normally prevented from actuating the hammers by a bail 152 pivotally supported on a cross rod 153. The bail'152 overlies a cam 154 carried by a rotatable shaft 155. The latter carries a gear 156 (FIG. 10) which is entrained with a gear 157 fixed on the drive shaft 23 through an idler gear 158.

During the printing phase of the machine cycle (see FIG. 12, item 2), a shoulder 160 on the cam 154 passes one edge of an opening 161 in the bail 152, permitting the spring fingers 150 to impel those hammers 141, which are otherwise allowed to do so, downwardly to effect an imprint of aligned type characters. Immediately thereafter, the cam 154 is effective to retract the hammers to their normal upper positions.

Means are provided for incrementally advancing the paper strip 20 after a printing operation to render the last printed line visible through the transparent tearotf bar 143. For this purpose, the feed roller 138 is fastened to a rotatable shaft 163 to which is also fastened a ratchet wheel 164 (FIG. 20). The latter is engageable by an ear 1651 of a pawl 1661 which is pivotally mounted at 1671 on the aforementioned gear sector 125. A tension spring 168 extending between the pawl and the gear sector 125 urges the pawl toward engagement with the teeth of the ratchet wheel so that during the latter half of a cycle, the pawl will be effective to advance the ratchet wheel. A detent lever 1701 is pivotally supported at 1711 and urged clockwise by a tension spring 1721 to detent the ratchet Wheel 164 and, consequently, the feed roll 138 in their different positions. A

The tearoif bar 143 is prismatic in cross section, as seen in FIG. 1, to render the last printed line located therebehind visible from above the machine. The tearoff bar is provided with comb teeth 165 which, when the bar is in its normal lower position, extend between adjacent sectors 16 to laterally guide the sectors. Also, the tearoff bar is provided with spaced arms 166 which are pivotally mounted at 167 on the machine framework. When it is desired to thread a new strip 20 through the printer, the machine cover 48 is suitably removed from the machine and the tearoff bar is swung into its dotted line position 143a shown in FIG. 1, permitting the leading edge of the strip to be readily located over the guide bar 142. When the tearoff bar is returned to its lowered position, its rear surface extends parallel with the surface of the guide plate 142 to form a strip guiding channel.

An inked printing ribbon 170 (FIGS. 14 to 17, inclusive) is provided for transferring impressions from the sectors 16 to the strip 20. The ribbon is relatively short and has the effective inking portion thereof normally housed within a cylindrical magazine 171. The latter comprises a side Wall 172 to which is secured a cupshaped shell 173. The flange has a tubular sleeve 174 integral therewith which, when the magazine is in place, fits over a stud 175 extending from a bracket 176 which is attached to the frame plate 61). The magazine is prevented from rotating by means of a stud 177 thereon which fits into a mating hole in the bracket.

A spool 178 is rotatably mounted on the sleeve 174 and is formed of two flanges 189 and 181 held in spaced relation to each other by four studs 182. A core 183 of felt or similar material impregnated with a suitable ink is attached between the flanges of the spool. One end of the printing ribbon 171i is attached to one of the studs 182 and is normally wrapped around the core 183 to transfer ink thereto.

A tension spring 184 is fitted over a partial annular flange 185 integral with the magazine side wall 172 and is attached at one end to a stud 186 integral with the side wall 172. The opposite end of the spring is attached to a stud 187 extending from the spool, thus tending to main tain a projection 179 on the ribbon spool against a stud 189 on the side wall 172 to likewise maintain the ribbon wrapped around the spool.

The free end of the ribbon is passed out through a slot 183 in the side of the magazine and over a roller 191i rotatably supported by the bracket 176. Thence, the ribbon is guided between the various sectors 16 and their respective hammers 141 directly below the path of the paper strip 20. The ribbon is guided around a second roller 191 carried by a slide 192 and is anchored at 193 to the frame plate 61.

The slide 192 is mounted for endwise movement in guides formed in the plates 61) and 61 and is normally urged to the left into its positions shown in FIG. 14 by a tension spring 194 extending between a suitable point on the framework and the right-hand end of the slide.

A cable 195 (FIGS. 9 and 11) is attached at one end 1% to the slide 192 and is guided over a stationary guide 197 extending from the side plate 61 and onto the periphery of a grooved pulley 198, being attached thereto at 200. The pulley is attached to a gear 2111 which meshes with the aforementioned gear sector 125.

Normally, when the machine is in its full cycle or rest position, the spring 194 will hold the slide in its lefthand position shown in FIG. 14 and the magazine spring 184 will be elfective to maintain the left-hand or inked portion of the printing ribbon within the magazine and wrapped in contact with the spool core 183.

Shortly after a machine cycle is initiated, the sector 125 will cause a pulley 198 and cable 195 to drawthe slide 192 to the right into its position shown in FIG. wherein the inked portion of the ribbon will be withdrawn from the magazine and will extend between the sectors 16 and the printing hammers 141. Subsequent to the printing operation, the sector 125 is retracted, allowing the slide 192 to be returned to its normal position.

Zero Elimination Device Means are provided to prevent printing of zeros to the left of the highermost significant digit in an amount being printed. For this purpose, a sensing slide 210 (FIGS. 1, l4 and 15) is provided, the slide being mounted for endwise movement in guide slots formed in the frame plates 60 and 61.

It will be noted that the slide 210 lies parallel to and closely adjacent the ribbon actuating slide 192 and is provided with a projection 211 which, when the parts are in their normal position shown in FIG. 14, is held in engagement with an ear 212 on the slide 192 by a spring 213 tensioned between the two slides.

The slide 2113 is substantially U-shaped, having a lower leg 21 1 which is guided in a guide slot 215 in the frame plate db. The leg 21- is aligned with rectangular slots 216 in the sectors 16 only when the latter are in their zero positions shown in FIG. 1, but such leg is normally out of the path of the sectors as shown in FIG. 14.

The slide 2111 is also formed with a ledge 216 which includes an extended hammer blocking section 217 normally lying to the left of the hammers 14-1 and terminating substantially in line with the right-hand end of the lower leg 21d thereof. However, when the slide 211) is moved to the right, the blocking section 217 moves into blocking relation with one or more shoulders 213 formed on the hammers 141. 7

It will be noted that the slides 192 and 211) are so related to the bail rod 122 that they will commence movement to the right as a unit concurrently with rocking of the bail rod to advance the sectors. However, the leg 214 is normally spaced a sulficient distance from the leftmost sector 16 (as seen in FIG. 14) so that it will not reach the same until the latter sector has advanced its slot 216 out of the path of the leg, if it is allowed to so advance.

Thus, for example, if the four leftmost sectors 16 are retained at 0 by the zero stop blade 71 (FIG. 3) as depicted in FIG. 15, the slide 210 will be advanced to the right along with slide 192 through the spring 213 until the leg 214 strikes the side of the sector which registers the highermost significant digit. Accordingly, the blocking ledge section 217 will block the four highermost hammers from printing. During return of the slide 192 in the latter half of the cycle, it will pick up the slide 2111 to return the same to its normal left-hand position.

Symbol Printing Controls A symbol indicating the type of factor or result printed is produced by a special symbol sector 22%) (FIGS. 5 and 22). The latter is rotatably mounted on the shaft 33 and is located to the right of the digit printing sectors 16. The symbol sector 221) is aligned with the left-hand row of stop pins 14- in the pin carriage when the latter is in home position, but is not controlled by these pins since, when such a pin is depressed, the pin carriage is concurrently advanced one step to the left to locate that pin in cooperative relation with the right-hand digit printing sector 16.

The symbol sector has a total symbol type character 221, a subtotal type character 222 and a minus type character 223 thereon, each cooperable with a special printing hammer 224. which is similar in construction to the printhig hammers 141 except that it is provided with a special ledge 225 (FIG. 6), the function of which will be described later.

The symbol sector 220 has two abutment shoulders 226 and 227 thereon spaced both angularly and radially relative to eachother.

The shoulder 226 is adapted to arrest against a stop projection 228 on a bail slide 231 (see also FIG. 23) when the pin carriage is in its home position and when the bail slide is in its illustrated position relative to the pin carriage. The bail slide is slideable on the rod 411 and is normally held in its position shown in F16. 23 by a compression spring 231 extending between the slide and the bearing tab 38 of the pin carriage.

When a total operation is initiated, as will be described later, the pin carriage and slide 230 will be in their normal illustrated positions wherein the stop projection 228 is aligned with the symbol sector and accordingly will block the symbol sector in a position to effect an imprint of the total type character 221.

However, when a subtotal operation is initiated, the pin carriage will likewise be in its home position but depression of. the add-subtotal bar 12 will have caused its stem 112 (FIGS. 24 and 26) to cam against an inclined edge 232 of a lever 233 fulcrummed at 234, causing its opposite end to engage a foot 235 onthe slide 231), causing the latter to move to the left in FIG. 23 relative to the pin carriage so that the symbol sector 220 may advance to a position where the shoulder 227 thereof engages a second stop projection 236 on the pin carriage frame 37 (see also FIG. 3). In this position, the subtotal type symbol 222 will be in position to effect a printing impression.

When an add or minus operation is initiated, the pin carriage will obviously be out of its home position wherein both stop

projections

228 and 236 will be out of alignment with the symbol sector 220 whereupon the latter will be advanced until the shoulder 226 limits against the edge 237 of the pin carriage frame 37 in which case the minus type character 223 will be located in printing position.

As will be described later, the symbol type hammer 223 is prevented from operating during add operations.

Accumulator The accumulator 21 and total stop mechanism is disclosed in detail and claimed in the copending application of R. E. Busch, Serial No. 130,078, filed August 8, 1961, for Calculating Machine. Therefore, for the sake of brevity, such details are not disclosed herein and reference may be had to said application for a complete understanding of the accumulator and its operations.

However, it will be noted that the accumulator is of the crawl carry type comprising denominationally arranged gears 240 and other elements rotatably mounted on an accumulator shaft 241. Normally, the accumulator is held in a lower position as shown in FIG. 1 wherein the accumulator gears are located out of mesh with gear sections 242 formed on respective ones of the sectors 16.

During a digitizing phase of a machine cycle, the accumulator is raised to mesh the gears 240 with the sectors 16 so as'to transfer digital amounts from the sectors into the accumulator. Likewise, during totaling and subtotaling operations, the accumulator is raised to mesh with the sectors for the purpose of transferring amounts from the accumulator to the sectors so that such amounts may be printed. During such totaling and subtotaling operations,

total stop levers 243 pivoted on the shaft 126 are swung counterclockwise to positions wherein shoulders 244 thereon are engaged by zero stops in the form of zero stop shoulders 245 formed on accumulator elements 246, when the latter reach their zero positions.

Accumulator Controls The accumulator is meshed and demeshed with the sectors 16 at different times in a machine cycle as set forth in

items

5, 6 and 7 in the timing diagram of FIG. 12, depending on whether additive or subtractive entries are being made or whether totaling or subtotaling operations are being performed.

For this purpose, an accumulator control cam 247 (FIGS. 5, 6, 7 and 8) is attached to the main drive shaft 23. Such cam is provided with three axially spaced camways 248, 250 and 251,the camways being separated by broken flanges 252.

A cam follower bail 253 is mounted on the shaft 126 for both pivotal and longitudinal movement thereon. A follower nose 254 is formed on the bail to follow a selected camway. The bail is connected through a pin and slot connection 255 with a camming bail 256 also pivoted on the shaft 126. Bail 256 is provided with spaced arms having camming grooves 257 therein which embrace rollers 258 on opposite ends of the accumulator shaft 241. Accordingly, when the bails 253 and 256 are rocked counterclockwise by a selected camway against the action of a tension spring 260, they will cam the accumulator along suitable guides (not shown) into mesh with the sectors 16.

It will be noted that the flanges 252 are broken at 261 to permit lateral shifting of the follower bail 253 when the machine is in full cycle position.

Means are provided to shift the follower bail 253 into cooperative relation with anyof the camways on the cam 247. For this purpose, the bail 253 has a depending leg which is engaged by a bifurcated lever 262 (FIG. 24) pivotally supported at 263 and urged counterclockwise by a tensioned spring 264 tending to locate the nose 254 of the bail 253 in engagement with the camway 248 of the control earn 247. In such case, the accumulator would be meshed with the sectors 16 during the return or counterclockwise rocking movements thereof as oc curs during additive entry operations (see also item 7 of the timing diagram).

Now, the aforementioned stud 70 of the pin carriage is embraced within a slot 265 formed in a blocking plate 266. The latter is slideably mounted for fore and aft movement of the machine on the bottom frame plate through pin and slot connections 267. When the pin carriage is moved into its right-hand or home position, the stud cams the blocking plate forwardly into its position shown in FIG. 24, causing an ear 268 thereof to cam against an inclined edge 270 onthe lever 262, thus moving the latter into its neutral illustrated position wherein the cam follower bail 253 is positioned in cooperative relation with a central camway 250. It will be noted on reference to FIGS. 6 and 12 (item 6) that the camway 250 has a high portion extending around the major part of its periphery whereby to maintain the accumulator in mesh with the sectors 16 during both the advance and retraction of the latter. This occurs during subtotaling operations of the accumulator.

Thus, when no amount has been entered into the pin carriage, i.e., when the pin carriage is in its home position, and the add-subtotal bar 12 (FIG. 13) is depressed to cause engagement of the clutch 22, a subtotal operation will ensue. However, when an amount has been entered into the pin carriage, i.e., when the latter is moved out of its home position, the blocking plate 266 will be cammed rearwardly of its position shown in FIG. 24 permitting the lever 262 to rock counterclockwise, thus moving the follower bail 253 into cooperative relation with the camway 248. Upon rearward movement of the blocking plate 266, a blocking ledge 271 thereon (see also FIG. 1) is moved into blocking relation with lugs 272 formed on the zero stop levers 243, thus preventing the latter from movinginto zero blocking relation with the accumulator elements.

The stem 113 (FIGS. 21 and 24) of the subtract-total bar 13 has a camming edge 273 engageable with the forward end of the lever 262 so that upon depression of the bar 13 the lever 262 will be cammed clockwise to position the cam follower bail 253 in cooperative relation with the camway 251 of the cam 247. As shown in FIG. 8 and item 5 of the timing chart, the camway 251 has a high portion so located as to mesh the accumulator with the sectors 16 during the early portion of a machine cycle or during advance of the sectors so as to effect a subtractive entry or totaling operation.

Means are provided for preventing printing of a symbol during additive entry operations and for this purpose, a

lever 275 (FIG. 6) is provided having a slot 276 pivotally embracing a frame stud 277. A stud 278 on the lever rides on a camming surface formed on the camming bail 256. Normally, the stud 278 engages a low portion of the camming surface on the bail 256 whereby to locate an ear 279 under the ledge 225 of the symbol printing hammer 224, thus blocking the same from printing.

During an add operation, as noted heretofore, the bail 256 will not be rocked counterclockwise from its position shown in FIG. 6 until after the printing operation so that the lever 275 will be effective to block the symbol print- Sector Aligner In order to ensure proper alignment of the sectors 16 during a printing operation and to ensure proper meshing of the accumulator gears therewith, an aligner 280 (FIGS. 1 and is provided which extends across the "arious sectors and is pivotally mounted at 281 on the arms of a bail 282 pivotally supported at 283 on the machine framework. A spring 284 is tensioned between the aligner and bail 282 to normally maintain the aligner in a counterclockwise rocked position relative to the bail and wherein a projection on the aligner engages a projection 289 on the bail.

The bail 282 is coupled through a pin and slot connection 285 to a cam follower bail 286 which is pivotally supported on the shaft 126 and carries a stud 2%? held in engagement with the periphery of a cam 28% fastened to the shaft 23 by a tension spring 290.

Just prior to the end of a machine cycle and just prior to a printing operation as depicted in the timing chart of FIG. 12 (item 4), the cam 288 causes bail 286 to rock the bail 2S2 counterclockwise, first moving the aligner 28f? into engagement with the teeth of the sectors. As the bail 282 continues its movement, a toggle action results, causing the aligner 280 to retract the sectors counterclockwise slightly, i.e., approximately 2. When such retraction occurs near the end of a cycle, the shoulders 53 are spaced sufficiently from alignment with the zero stop pins 14 that the pin carriage may be readily moved to successively higher denominational positions even though one or more zero pins 14 have been set without such zero pins engaging the shoulders.

Although the invention has been described in detail and certain specific terms and languages have been used, it is to be understood that the present disclosure is illustrative rather than restrictive and that changes and modifications may be made without deparing from the spirit or scope of the invention as set forth in the claims appended hereto.

Having thus described the invention, what is desired to be secured by United States Letters Patent is:

1. In a calculating machine having an accumulator including accumulator elements carrying zero stops; differential actuators for said accumulator, a pin carriage having settable pins for controlling said actuators, means for advancing said pin carriage out of home position as an incident to setting a said pin, and total stops adapted to arrest said zero stops; of add, subtract and total control cams, and cam follower means selectively cooperable with any of said cams for effecting cooperative relation between said actuators and said accumulator, spring means tending to effect cooperative relation between said cam follower means and said add cam, a control member settable into a first position by said pin carriage upon movement out of home position and settable into a second position by said pin carriage upon movement into home position, said control member being effective in said first position to prevent said total stops from arresting said zero stops and to permit said spring means to effect cooperative relation between said cam follower means and said add control cam, said control member being effective in said second position to enable said total stops to arrest said zero stops and to effect cooperative relation between said cam follower means and said subtotal control cam, and subtract-total control means operable to effect cooperative relation between said cam follower means and said subtract control cam regardless of the position of said pin carriage.

2. In a calculating machine having differential actuators, a pin carriage having settable pins for controlling said actuators, means for setting said pins, means for advancing said pin carriage out of home position upon setting a said pin, an accumulator including accumulator elements carrying zero stops; and total stops adapted to arrest said zero stops; of add, subtract and subtotal control cams, a cam follower movable into cooperative relation with any of said cams, means controlled by said cam follower for effecting cooperative relation between said achiators and said accumulator, spring means tending to move said cam follower into cooperative relation with said add cam, a control member settable into a first position by said pin carriage upon movement out of home position and settable into a second position by said pin carriage upon movement into home position, said control member being effective when moved into said first position to prevent said total stops from arresting said zero stops and to permit said spring means to move said cam follower into cooperative relation with said add cam, said control member being effective when moved into said second position to enable said total stops to arrest said zero stops and to move said cam follower into cooperative relation with said subtotal cam, and means operable to move said cam follower into cooperative relation with said subtract cam regardless of the position of said pin carriage.

3. in a calculating machine having an accumulator including accumulator elements carrying zero stops; differ ential actuators for said accumulator, a pin carriage having settable pins for controlling said actuators, means for advancing said pin carriage out of home position as an incident to setting a said pin, and total stops adapted to arrest said zero stops; of add, subtract and subtotal control cams, cam follower means selectively cooperable with any of said cams for effecting cooperative relation between said actuators and said accumulator, spring means tending to effect cooperative relation between said cam follower means and said add control cam, a control member controlled by said pin carriage and movable into a first position upon movement of said pin carriage out of home position, said control member being movable into a second position upon movement of said pin carriage into home position, said control member being effective in said first position to prevent said total stops from arresting said zero stops and to permit said spring mean to effect cooperative relation between said cam follower means and said add control cam, said control member being effective in said second position to permit said total stops to arrest said zero stops and to effect cooperative relation between said cam follower means and said subtotal control cam, and subtract-total control means operable to effect cooperative relation between said cam follower means and said subtract control cam regardless of the position of said pin carriage.

4. In a calculating machine having an accumulator including accumulator elements carrying zero stops; differential actuators for said accumulator, a pin carriage having settable pins for controlling said actuators, means for advancing said pin carriage out of home position as an incident to setting a said pin, and total stops adapted to arrest said zero stops; of add, subtract and subtotal control cams, a cam follower movable into cooperative relation with any of said cams, means controlled by said cam follower for effecting cooperative relation between said actuators and said accumulator, spring means tending to move said cam follower into cooperative relation with said add control cam, a control member controlled by said pin carriage and movable into a first position upon movement of said pin carriage out of home position, said control member being movable into a second position upon movement of said pin carriage into home position, said control member being effective in said first position to prevent said total stops from arresting said zero stops and to permit said spring means to move said cam follower means into cooperative relation with said add control cam, said control member being effective in said second position to enable said total stops to arrest said zero stops and to move said cam follower into cooperative relation with said subtotal control cam, and subtracttotal control means operable to move said cam follower into cooperative relation with said subtract control cam regardless of the position of said pin carriage.

-5. In a calculating machine having an accumulator including accumulator elements carrying zero stops; differential actuators for said accumulator, a pin carriage an incident to setting a said pin, and total stops adapted to arrest said zero stops; of add and subtotal control cams, cam follower means selectively cooperable with either of said cams for effecting cooperative relation between said actuators and said accumulator, spring means tending to effect cooperative relation between said cam follower means and said add control cam, and a control member controlled by said pin carriage and movable into a first position upon movement of said pin carriage out of home position, said control member being movable into a second position upon movement of said pin carriage into home position, said control member being effective in said first position to block said total stops from arresting said zero stops and to permit said spring means to effect co operative relation between said cam follower means and said add control cam, and said control member being effective in said second position to permit said total stops to arrest said zero stops and to effect cooperative relation between said cam follower means and said subtotal control cam.

6. In a calculating machine having an accumulator including accumulator elements carrying zero stops; differential actuators for said accumulator, a pin carriage having settable pins for controlling said actuators, means for advancing said pin carriage out of home position as an incident to setting a said pin, and total stops adapted to arrest said zero stops; of add and subtotal control cams, a cam follower movable into cooperative relation with either of said cams, means controlled by said cam follower for effecting cooperative relation between said actuators and said accumulator, spring means tending to move said cam follower into cooperative relation with said add control cam, a control member controlled by said pin carriage and movable into a first position upon movement of said pin carriage out of home position, said control memher being movable into a second position upon movement of said pin carriage into home position, said control member being effective in said first position to prevent said total stops from arresting said zero stops and to permit said spring means to move said cam follower into cooperative relation with said add control cam, and said control member being effective in said second position to permit said total stops to arrest said zero stops and to move said cam follower into cooperative relation with said subtotal control cam.

7. In a calculating machine having an accumulator including accumulator elements carrying zero stops; differential actuators for said accumulator, a pin carriage having settable pins for controlling said actuators, means for advancing said pin carriage out of home position as an incident to setting a said pin, and total stops adapted to arrest said zero stops; of add, subtract and subtotal control cams, cam follower means selectively cooperable with any of said cams for effecting cooperative relation between said actuators and said accumulator, a control member controlled by said pin carriage and movable into a first position upon movement of said pin carriage out of home position, said control member being movable into a second position upon movement of said pin carriage into home position, means controlled by said control member including a spring for positioning said cam follower means in cooperative relation with said add control cam upon movement of said control member into said first position; said last mentioned means being effective to position said cam follower means in cooperative relationwith said subtotal control cam upon movement of said control member to said second position, said control member being effective in said first position to prevent said total stops from arresting said zero stops, said control member being effective in said, second position to permit said total stops to arrest said zero stops, and subtract-total control means selecively operable to overcome said spring to position said cam follower means in cooperative relation with said subtract control cam regardless of the position of said control member.

8. In a calculating machine having an accumulator including accumulator elements carrying zero stops; differential actuators for saidaccumulator, a pin carriage having settable pins for controlling said actuators, means for advancing said pin carriage out of home position as an incident to setting a said pin, and total stops adapted to arrest said zero stops; of add, subtract and subtotal control cams, a cam follower selectively cooperable with any of said cams, means controlled by said cam follower for effecting cooperative relation between said actuators and said accumulator, a control member controlled by said pin carriage and movable into a first position upon movement of said pin carriage out of home position, said control member being movable into a second position upon movement of said pin carriage into home position, means controlled by said control member including a spring for positioning said cam follower incooperative relation with said add control cam upon movement of said control member into said first position; said last mentioned means being effective to position said cam follower in cooperativerelation with said subtotal control cam upon movement of said control member to said second position, said control member being effective in said first position to prevent said total stops from arresting said zero stops, said control member being effective in said second position to permit said total stops to arrest said zero stops, and subtract-total control means selectively operable to overcome said spring to position said cam follower in cooperative relation with said subtract control cam regardless of the position of said control member.

References Cited in the file of this patent UNITED STATES PATENTS 2,424,359 Liljestrom et al. July 22, 1947 2,740,582 Parker Apr. 3, 1956 2,954,922 Chall Oct. 4, 1960 2,969,176 Anderson Jan. 24, 1961 2,989,231 Mark et al. June 20, 1961 3,069,077 Rosati Dec. 18, 1962 FOREIGN PATENTS 809,523 Great Britain Feb. 25, 1959

Claims

5. IN A CALCULATING MACHINE HAVING AN ACCUMULATOR INCLUDING ACCUMULATOR ELEMENTS CARRYING ZERO STOPS; DIFFERENTIAL ACTUATORS FOR SAID ACCUMULATOR, A PIN CARRIAGE HAVING SETTABLE PINS FOR CONTROLLING SAID ACTUATORS, MEANS FOR ADVANCING SAID PIN CARRIAGE OUT OF HOME POSITION AS AN INCIDENT TO SETTING A SAID PIN, AND TOTAL STOPS ADAPTED TO ARREST SAID ZERO STOPS; OF ADD AND SUBTOTAL CONTROL CAMS, CAM FOLLOWER MEANS SELECTIVELY COOPERABLE WITH EITHER OF SAID CAMS FOR EFFECTING COOPERATIVE RELATION BETWEEN SAID ACTUATORS AND SAID ACCUMULATOR, SPRING MEANS TENDING TO EFFECT COOPERATIVE RELATION BETWEEN SAID CAM FOLLOWER MEANS AND SAID ADD CONTROL CAM, AND A CONTROL MEMBER CONTROLLED BY SAID PIN CARRIAGE AND MOVABLE INTO A FIRST POSITION UPON MOVEMENT OF SAID PIN CARRIAGE OUT OF HOME POSITION, SAID CONTROL MEMBER BEING MOVABLE INTO A SECOND POSITION UPON MOVEMENT OF SAID PIN CARRIAGE INTO HOME POSITION, SAID CONTROL MEMBER BEING EFFECTIVE IN SAID FIRST POSITION TO BLOCK SAID TOTAL STOPS FROM ARRESTING SAID ZERO STOPS AND TO PERMIT SAID SPRING MEANS TO EFFECT COOPERATIVE RELATION BETWEEN SAID CAM FOLLOWER MEANS AND SAID ADD CONTROL CAM, AND SAID CONTROL MEMBER BEING EFFECTIVE IN SAID SECOND POSITION TO PERMIT SAID TOTAL STOPS TO ARREST SAID ZERO STOPS AND TO EFFECT COOPERATIVE RELATION BETWEEN SAID CAM FOLLOWER MEANS AND SAID SUBTOTAL CONTROL CAM.