US3545672A - Rotary transfer means for receiving and distributing amounts in a printing calculator - Google Patents

Description

United States Patent [72] Inventors Bernard Deleuze Paris; Rene Francois Lucas, Noisy-Le-sec, France [21 1 Appl. No. 773,435 [22] Filed Nov. 5, 1968 [45] Patented Dec. 8, 1970 [54] ROTARY TRANSFER MEANS FOR RECEIVING AND DISTRIBUTING AMOUNTS IN A PRINTING 62(X)4, 60(Gen.)

[56] References Cited UNITED STATES PATENTS 3,093,305 6/l963 Englund 235/60 3,315,884 4/1967 Bennett 235/60 Primary Examiner-Stephen J. Tomsky Attorneys- Kenneth L. Miller and Frank H. Cullen ABSTRACT: A plurality of ordinally arranged wheels are provided with a sufficient number of teeth to engageably accommodate a plurality of exterior processing and storage means which may be disposed along the perimeters thereof. A shaft supporting the wheels is rotatable one complete revolution during each cycle of operation to thereby advance and return the wheels a nine tooth or lesser distance, depending upon whether the zeroizing of pinions associated with the exterior means serves to restrict their advancement. By activating selected ones of the exterior means into timely engagement and disengagement with and from corresponding teeth of the wheels, digital information is transferred between such exterior means for processing or storage purposes.

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SHEET 2 OF 5 NUI minnow BIHZU 3.545572 SHEET 5 0F 5 FIG. 5.

ROTARY TRANSFER MEANS FOR RECEIVING AND DISTRIBUTING AMOUNTS IN A :I i if G CALCULATOR BACKGROUND OF THE INVENTION Inherent in high speed, multiple-function printing calculators is the need for rapidly and conveniently transferring digital information as between the various operating sections. When such a calculator also provides storage means for the retention of raw or processed data, the need for fast and reliable distribution of the stored data is equally critical. As an example, it is an important requirement of a high speed printing calculator that adds, subtracts, multiplies and divides either input or stored data, that fast and reliable means be provided for handling the input and output data and for bidirectionally transferring diverse data as between the various storage and processing means, such latter means including accumulators wherein amounts are added and subtracted and computing sections wherein amounts are multiplied and divided.

In recognition of these requirements, considerable effort was directed in the development of a high speed, four-function printing calculator having mechanical memory means, to the development of a highly efficient data transfer device that is eminently qualified for receiving and emitting input and output data and for distributing numerical data as between the various operating and storage sections of the machine. The preferred embodiment of the present invention is the direct result of this effort, such result effectively serving the bidirectional data transfer needs of such a calculator.

CROSS-REFERENCES TO RELATED APPLICATIONS This application is related to an application by Bernard Deleuze et al. titled Accumulator with Tens Transfer Means Disposed Internally of Its Pinion-Bearing Shaft, such application having been filed in the US. Patent Office on Sept. 16, 1968 and assigned Ser. No. 762,165. A plurality of accumulators of the type disclosed in this referenced application may be arranged along the perimeter of the transfer device of the present invention.

The present application discloses the character and mode of operation of a plurality of transfer wheels which were described as rotary actuators in the above-identified application and shown at 113 in the drawings thereof, such transfer wheels having been utilized as a representative means for actuating the pinions of such accumulator in both an additive and subtractive rotational direction.

SUMMARY OF THE INVENTION It is accordingly an object of the present invention to provide a fast and reliable means for receiving and emitting input and output data and for bidirectionally transferring digital information as between the various storage and operating sections of a high speed, multiple-function printing calculator.

It is a further object of the present invention to provide data transfer means that is simple in construction and highly flexible in its mode of operation.

A still further object of the invention is to provide a data transfer device that is economical to manufacture and to maintain, such advantages arising from the simplicity of the parts employed and the limited degree of mechanical motion involved in their operation.

An important aspect of the invention is the arrangement of a plurality of large toothed-wheels on a rotatable shaft, such wheels being rotatable on the shaft and couplable therewith so that the shaft may impart a controlled rotational advancing and return motion to the wheels during each of its revolutions.

Another aspect of the invention is the use of a sleeve and a plurality of locking spacers for rotatably mounting the wheels on the shaft, the sleeve being rotatable on the shaft, the spacers being lockingly fixed to the sleeve, and the wheels being mounted on the locking spacers and qualified for a limited rotational movement thereon.

Another aspect of the invention is the use of a 45-point wheel in each order of such transfer means, each of such wheels engageably accommodating a plurality of exterior pinions associated with corresponding orders of the plurality of storage and processing means herein before indicated.

Still another aspect of the invention is the use of yieldable means for rotationally coupling each toothed-wheel with its associated locking spacer, such coupling serving to advance the wheel a nine tooth distance in unison with the spacer when the former is unrestricted by the zeroizing of a corresponding exterior pinion, and to permit the full nine tooth advancement of the spacer when the advancement of the wheel is differentially restricted by the zeroizing of such exterior pinion.

An additional aspect of the invention is the use of a plurality of ratchet pawls to effectively secure the toothed wheels in their differentially advanced positions as the zeroized exterior pinions are disengaged therefrom, such ratchet pawls being activated into coupled relationship with the wheels at a predetermined point in the revolution of the shaft, and retained in such coupled relationship during the return rotation of the wheels to their zero positions.

BRIEF DESCRIPTION OF THE DRAWINGS These and other objects, aspects and advantages of the invention will be more clearly understood from the following description when read in conjunction with the accompanying drawings, in which:

FIG. 1 is a sectional elevation of a calculating machine schematically showing the rotary transfer means in relation to a plurality of storage and operating means which are disposed along the perimeter thereof;

FIG. 2 is a perspective view of the preferred embodiment of the invention taken from the left front corner and showing a plurality of transfer wheels in mounted relationship with their supporting shaft and showing also means for rotationally activating such shaft and such wheels;

FIG. 3 is a perspective cutaway view of a keyboard showing a single operation control key and linkage means responsive to the depression of such key for coupling the wheel supporting shaft of FIG. 2 to a constantly rotating shaft also shown in FIG.

FIG. 4 is a perspective view showing a single transfer wheel in mounted relationship with the supporting shaft as in FIG. 2 but with various parts omitted to more clearly illustrate the details of such mounting and the details also of the means employed for rotationally coupling the shaft to the wheel; and

FIG. 5 is a right side view of a transfer wheel mounted on a locking spacer and a right side view also of a transfer wheel and a locking spacer in their disassembled states.

DETAILED DESCRIPTION OF THE INVENTION The preferred embodiment of the invention is schematically illustrated in FIG. 1 by the transfer wheel 113. A plurality of gears and pinions are also shown in FIG. 1 in contiguous relationship with this transfer wheel, such gears and pinions representing a plurality of storage and operating sections of the printing calculator in which the invention is incorporated. In considering the general purpose and function of the present invention, it is deemed advantageous to first briefly describe the types of storage and operating sections represented by these gears and pinions. The two ten-point pinions 21 may be representative of accumulators of the type disclosed in the above-identified application by Bernard Deleuze et al. The l2- point pinion may be representative of mechanical memory wheels which are continuously engaged with the transfer wheels 113, such memory wheels having been described as intermediate actuators" in this related application inasmuch as they were alternately employed therein as a means of subtractively entering amounts into the accumulating pinions 21.

The ten-point pinion 128 may be representative of one of several sets of pinions of a printing mechanism which is effective for imprinting digital information on a platen 134. The 12- point pinion 129 may be representative of a plurality of printing memory wheels effective for storing the amount that was last printed by the printing mechanism, and effective also for use as input wheels when entering amounts indexed in the keyboard and registered in a selector carriage. The wheels 130, 131 may be representative of a selector carriage into which the digit values of a numerical amount may be entered one digit at a time beginning with the most significant and end ing with the least significant digits thereof, such selector carriage escaping one unit of travel to the left upon the entry of each digit. When all of the digits of a number have been so entered, the selector carriage 130, 131 may then be rotated in a clockwise direction to couplingly engage the pinions 131 and 129 and to thereby condition the transfer wheels 1113 for receiving the indexed amount. The ten-point pinion 132 may be representative of a single entry wheel which is successively engaged with the adjoining lower order pinions 131 as the selector carriage is successively escaped to the left during the digit-by-digit entry of an indexed amount.

The pinions 133, 135 and 137 may be representative of the operating gears of a computing section wherein both multiplying and dividing calculations may be performed, the pinions 133 serving as second factor wheels when multiplying and as quotient wheels when dividing, the pinions 1337 serving as product wheels when multiplying and as first factor wheels when dividing, and the pinions 135 serving as first factor wheels when multiplying and as second factor wheels when dividing. The block 139 shown in FIG. 1 may be representative of suitable motive means for providing activational power forth e various operating sections of the printing calculator.

With reference to FIGS. 2 and 4, the preferred embodiment of the invention comprises a plurality of 45-point transfer wheels 113 which are rotatably supported by means of a sleeve 141 on a driven shaft 143. Each of the wheels 113 is rotatably mounted on an associated mounting spacer 145 which is lockably fixed to the sleeve 141 and rotatable therewith on the shaft 143. The shaft 143 is journaled within machine frame members 147 and 149, and is couplable with a rotating shaft 151 and a large rotating gear 153 which are connected to a constant running motor 139 (FIG. 1) by means of a motor shaft 167, a pulley 169 and a belt 171. The shaft 143 is accordingly effective for transmitting rotational power to the transfer wheels 113, and for transmitting motive power also to other operating sections of the machine by means of a pulley 155 fixed to the rightmost extremity of the shaft 143.

As shown in FIG. 5, each of the mounting or locking spacers 145 comprises a plurality of offset arcuate flanges 157 which confinably cooperate with a corresponding plurality of inwardly directed arcuate abutments 161 of its associated transfer wheel 113, and also a plurality of inwardly directed arcuate abutments 159 which are fitted between a corresponding number of adjoining pairs of circumferential ridges 163 formed on the outer circumference of the sleeve 141 and locked into position therebetween by means of a plurality of locking strips 165 shown in FIGS. 2 and 4.

The motor shaft 167 and the rotating shaft 151 are journaled in the frame member 173, and the shafts 175, 177 and 179 are supported by the frame members 147 and 149 and by the frame members 183 and 185 shown in FIG. 4. A shaft 187 shown in FIGS. 2 and 4 is supported by the frame members 183 and 185 and passes through an arcuate slot 189 formed in each of the transfer wheels 113. A spring 191 is connected to a lug 193 attached to the left side surface of each of the transfer wheels 113, and to the shaft 187. Each of the springs 191 serves to urge its associated transfer wheel 113 in a clockwise direction (as viewed in FIG. 2) on its associated locking spacer 145, to etfectively hold a stud 195 fixed to the left side surface of the transfer wheel into contacting relationship with a step 197 formed in its associated locking spacer 145, the latter spacer, as previously stated, being fixed to the sleeve 141 and rotatable therewith on the shaft 143.

Two pairs of cams each consisting of a cam 199 and a companion cam 201 are fixed in spaced-apart relationship to the shaft 143, each of the cams 199 being cooperably associated with a roller 203 carried by a corresponding cam-follower assembly 207 and each of the cams 201 being cooperably associated with a roller 205 also carried by its respective camfollower assembly. Each of these cam-follower assemblies 207 is pivotally supported by the shaft 175 and each comprises a roller supporting member 2073 and a toothed member 207A, the latter members having a plurality of teeth disposed along the frontmost edge of an arcuate slot formed therein. Fixed to the outermost extremities of the sleeve 141 are a pair of gears 209 disposed in cooperating relationship with the teeth of the members 207A of the cam-follower assemblies 207.

An elongated gear 211 is fixed to the rotating shaft 151 and keyed to the large gear 153. The motor shaft 167, the pulley 169, the large gear 153, the elongated gear 211, and the shaft 151 are rotated in a continuous counterclockwise direction whenever the motor 139 is maintained in an operating state. Contiguous to the rightmost extremity of the elongated gear 211 is a cam disc 213 fixed to the leftmost extremity of the shaft 143. A clutch-dog 215 is pivotally carried by the cam disc 213 by means of a stud 217. A spring 219 is connected at one end to a stud 221 fixed to the cam disc 213, and at the other end to a stud 223 carried by the clutch-dog 215, such spring thereby serving to bias the clutch-dog in a counterclockwise direction on the stud 217 and to thereby bias a detent dog 225 formed thereon in the direction of its engaged relationship with the elongated gear 211. A bifurcated drive trip lever 227 is pivotally connected to the frame member 173 by means of a shoulder stud 229. An offset projection 227A formed on the upper branch of this bifurcated drive trip lever is maintained in contacting relationship with the free-end extremity of the clutch-dog 215 whenever the drive trip lever is situated in its inactive, counterclockwise-rocked position, thereby holding the clutch-dog 215 in disengaged relationship with the elongated gear 21 1 against the bias of the spring 219. As will be explained in greater detail in subsequent paragraphs with reference to FiG. 3, the depression of an operation control key of the keyboard causes the drive trip lever 227 to be rotated in a clockwise direction on the shoulder stud 229, thereby raising the offset projection 227A out of contacting relationship with the clutch-dog 215 and permitting the spring 219 to rotate the clutch-dog in a counterclockwise direction to engage the elongated gear 211. The shaft 143 is accordingly coupled to the rotating shaft 151 for a one revolution counterclockwise rotation. As the bifurcated drive trip lever 227 is rotated in a clockwise direction on the shoulder stud 229, a roller carried by its lower branch (not shown) is raised into contacting relationship with the camming surface of the cam disc 213. During the revolution of the cam disc 213 and shaft 143, a raised portion of the cam disc activates the trip lever 227 in a counterclockwise direction by means of this roller, to thereby reposition the offset projection 227 A into blocking relationship with the free-end extremity of the rotating clutchdog 215 and to disengage the clutch-dog from the elongated gear 211 when the offset projection is contacted by such extremity. The raised portion of the cam disc is so oriented relative to the shaft 143 that it will clear the roller of such lower branch of the drive trip lever at the time a full revolution of the shaft is completed, so that such raised portion in combination with the roller will not interfere with the clockwise tripping of the lever during the inception of a succeeding operation of the transfer mechanism.

At the approximate point in the counterclockwise rotation of the shaft 143, the cams 201 activate the rollers 205 of their respective cam follower assemblies 207 in a downward direction to thereby rotate the cam follower assemblies in a clockwise direction on the shaft 175. This rotation of the cam follower assemblies 207 is effective to rotate the gears 209 of the sleeve 141 in a clockwise direction on the counterclockwise rotating shaft 143, by means of the engagement of the teeth of the members 207A with the gears 209. This clockwise rotation of the assemblies 207 is sufficient to rotate the sleeve 141 and the locking spacers 145 the equivalent of a nine tooth clockwise distance relative to the circumference of the transfer wheels 113. During this clockwise rotation of the locking spacers 145, the transfer wheels 113 are rotated a differential clockwise distance as motivated by the springs 191 which, as previously stated, are anchored to the lugs 193 of the wheels and to the shaft 187. At such time as the clockwise rotation of an individual wheel 113 is arrested by the zeroizing of a corresponding exterior pinion (as illustrated in FIG. ll), the corresponding locking spacer 145 will 1 continue to travel the remainder of its nine tooth distance independently of the arrested wheel 113, such continued travel of the locking spacer resulting in a separation between the stud 195 of the wheel and the step 197 of the locking spacer.

At the approximate 225 point in the counterclockwise rotation of the shaft 143, the cams 199 activate the rollers 203 of their respective cam follower assemblies 207 in an upward direction to thereby rotate the cam follower assemblies in a counterclockwise direction on the shaft 175. The gears 209 and the sleeve 141 are accordingly rotated an equivalent nine tooth distance in a counterclockwise return direction by means of the teeth of the members 207A. During this return rotation of the gears 209 and sleeve 141, the locking spacers 145 rotate their associated transfer wheels in a counter clockwise direction through contact of the steps 197 with the studs 195, the wheels being returned from their differentially set positions to their zero home positions.

The keyboard of the printing calculator into which the preferred embodiment of the invention is incorporated is provided with means for activating the bifurcated drive trip lever 227 in such manner as to effectuate the coupling of the driven shaft 143 and the rotating shaft 151, as previously described. This keyboard means is illustrated in FIG. 3 wherein the keyboard is shown in cooperating relationship with the drive trip lever 227. The various operation control keys of the printing calculator are disposed on the right side of the keyboard block 231. A single one of these keys, namely the plus motor bar, is shown at 233. As in the case of all of these operation control keys, the plus motor bar is attached at its foremost and rearrnost ends to a pair of upright projections 235A of a pair of keyboard indexing levers 235, such levers being pivotally connected to a shaft 236 disposed on the left side of the keyboard and being also biased in a counterclockwise direction thereon by springs 234 connecting the rightmost extremities of the levers to a shaft 238 disposed on the right side of the keyboard. Each of the keyboard levers 235 is pivotally disposed in a corresponding vertical transverse groove formed in the keyboard block 231, and each lever is provided with a depending projection 235B arranged on its lowermost edge in cooperating relationship with a pivot bail 237 which is pivotally and longitudinally disposed in a cutout formed in the underside of the keyboard. The pivot bail 237 is provided with a pair of pivot studs 239 fixed to the frontmost and rearrnost surfaces thereof, such pivot studs being disposed for rotational movement in a pair of apertures formed in the keyboard block, the frontmost of the pivot studs 239 being also journaled in a cylindrical housing on the front side of the keyboard as shown in FIG. 3. The pivot a bail 237 is also provided at its rearrnost end with a depending projection 237A and a depending lip portion 237B. The lip portion 2378 is provided on its rearrnost surface with a biased pin 241 which is engageable with an aperture 243 formed in the rearrnost vertical surface of the keyboard block, when the pivot bail is disposed in its clockwise-rocked position on the pivot studs 239. The depending projection 237A is cooperably aligned with a slide rod 245 which is translatably disposed in a cylindrical chamber formed in the left rear portion of the keyboard.

Upon depression of the plus motor bar 233, the corresponding pair of keyboard indexing levers 235 are rotated in a clockwise direction on the shaft 236, against the bias of the springs 234. The pivot bail 237 is rotated in a clockwise direction on the studs 239 by means of the depending projections 235B, such rotation resulting in the engagement of the biased pin 2411 with the aperture 243 where it remains throughout one complete cycle of the printing calculator. The rotation of the pivot bail 237 is also effective to translate the slide rod 245 a predetermined distance in a leftward direction, through the camming action of the depending projection 237A. This leftward translation of the slide rod 245 is effective, through contact of its leftmost extremity with a nut 247 fixed to the rightmost extremity of a plunger shaft 259, to activate the latter shaft assembly to the left into its retracted position relative to an abutment sleeve 260 fixed to the frame member 173. This plunger shaft assembly 259 is comprised of an axially slidable disc 249, a collared sleeve 250 having its collar positioned on the leftmost extremity thereof, a collared sleeve 251 having its collar positioned on its rightmost extremity, and a pair of helical springs 255 and 257. The spring 255 is resiliently disposed between the frame member 173 and the collar of the sleeve 251, and the spring 257 is resiliently disposed between the collar of the sleeve 250 and the slidable disc 2 59. The collar of the sleeve 251, which is of lesser diameter than the collar of the sleeve 250, provides a limit for the bifurcated drive trip lever 227 when the latter is thereby held in its counterclockwise-rocked position on the shoulder stud 229 against the bias of a spring 263, such spring being anchored to a stud 265 fixed to the lever 227 and to a shaft 267 supported by the frame members 1.73 and 1 17. In such counterclockwise-rocked position, the drive trip lever 227, as previously explained, serves to hold the clutch-dog 215 (FIG. 2) in disengaged relationship relative to the elongated gear 211, by means of the offset projection 227A.

As the slide rod 245 (11G. 3) is translated to the left by the rotation of the pivot bail 237, the nut 247 of the plunger shaft assembly 259 contacts the slidable disc 249, the disc in turn compresses the spring 257 and contacts the rightmost extremity of the sleeve 250, the collar of such sleeve contacting the collar of the sleeve 251 to axially translate the latter sleeve to the left to thereby further compress the spring 255, the plunger shaft 259 during this translation assuming its retracted position relative to the abutment sleeve 260. The leftward translation of the sleeve 251 effectively displaces the collar thereof from its blocking position relative to the drive trip lever 227, such lever thereby being relatively positioned at a point of separation 253 between the two abutting collars whereupon the spring 263 effectively rotates the lever in a clockwise direction to release the clutch-dog 215 to the control of the spring 219 (FIG. 2), the foremost extremity of the lever 227 being insertably positioned between the two collars at said point of separation. A grooved limit stud 261 fixed to the frame member 173 serves to limit the depth of insertion of the drive trip lever between the abutting collars and to define the clockwise-rocked position of the drive trip lever wherein the projection 227A (FIG. 2) is held clear of its blocking position relative to the clutch-dog 215.

As previously explained with reference to FIG. 2, the drive trip lever 227 is rotated in a counterclockwise direction by the cam disc 213 during the rotation of the shaft 143, to thereby reposition the projection 227A in blocking relationship with the clutch-dog 215. This rotation of the lever 227 is effective to displace its foremost extremity from said inserted position between the two collars 250 and 251, such displacement resulting in a minimal rightward translation of the sleeves 251 and 250, as motivated by the spring 255, to thereby reposition the collar of sleeve 251 in blocking relationship with the frontmost extremity of the drive trip lever. The spring 257 is effective to axially translate the disc 249 and the plunger shaft 259 to their rightward home positions at such time as the biased pin 2 11 (FIG. 3) is disengaged from the aperture 243 of the keyboard by suitable means associated with the printing calculator (not herein shown or described). The rightward axial translation of the plunger shaft 259 is effective to restore the slide rod 2 15 and the pivot bail 237 to their respective home positions.

Means are also provided in the preferred embodiment of the invention for preventing the advancement of the transfer wheels 113 beyond their differentially set positions, as selected ones of the exterior storage and operating means (shown in FIG. 1) are disengaged therefrom during the transfer of digital information therebetween. A plurality of ratchet pawls 271 (shown in FIG. 2) are pivotally supported on the shaft 177 in cooperating relationship with ratchet strips 269 fixed to the leftside surfaces of the transfer wheels in contiguous relationship with their arcuate slots 1851. Each of these ratchet pawls is biased in a counterclockwise direction on the shaft 177 by a spring 273 connected to an upright projection thereof and to the shaft 179, and each is provided with a rearwardly extending tail 271A. A pair of spaced-apart oscillating arms 275 are disposed in contiguous relationship with the innermost surfaces of the frame members 147 and 1419. These arms are provided with a slot 275A formed in the uppermost extremities thereof, a slot 275B formed in their lowermost extremities, and a spring stud 275C fixed to the outermost side surfaces thereof. The slots 275A are slidably engaged with the shaft 177, and the slots 275B with a pair of collared sleeves 279 within which the shaft 143 freely rotates. A shaft 1151 connecting the arms 275 is supported by an aperture formed in the uppermost portion of each arm, such shaft being disposed in cooperating relationship with the rearwardly extending tails 271A of the ratchet pawls 271. A spring 277 anchored to the spring stud 275C of each arm and to the associated collared sleeve 279 effectively biases each of the arms 275 in a downward direction wherein the respective slots 27513 are fully engaged with the associated collared sleeves 279. A pair of cams 281 fixed to the shaft 143 adjacent the arms 275 cooperate with a pair of rollers 283 fixed to the innermost side surfaces of the arms 275, as the shaft 143 is rotated in a manner previously described. When the shaft 143 is located in its home position, raised portions of the cams 281 in cooperation with the rollers 283 serve to hold the arms 275 in their uppermost translated positions against the bias of the springs 277. The shaft 181 is accordingly also held in its uppermost position wherein the ratchet pawls 271 are held in a clockwise-rocked position on the shaft 177 against the bias of the springs 273. When the pawls 271 are so held, their lowermost extremities are positioned clear of the ratchet strips 269 of the wheels 113, where they are retained throughout the differential advancement of the transfer wheels. At a predetermined point in the rotation of the shaft 143, such point coinciding with the full clockwise advancement of the sleeve 141 and locking spacers 1 15, these raised portions of the cams 281 are displaced from the rollers 283 to thereby permit the springs 277 to lower the arms 275 into full engagement with the sleeves 279. The shaft 181 is accordingly lowered from its blocking position relative to the tails of the pawls 271, and the springs 273 are thereupon effective to rock the pawls into engaged blocking relationship with the ratchet strips 269. With the pawls 271 blockingly activated in this manner, the transfer wheels 113 are blocked against further clockwise rotation. During the return rotation of the transfer wheels, as motivated by the cams 199 and rollers 203, the ratchet strips 269 are freely ratcheted past their associated ratchet pawls 271, until at the culmination of such return rotation the transfer wheels are located in their zero positions and the raised portions of the cams 281 are again located in contacting relationship with the rollers 283 of the arms 275, the shaft 181 thereupon being relocated in its blocking position relative to the tails 271A wherein the ratchet pawls 271 are held in their clockwiserocked and cleared positions relative to the ratchet strips 269.

GENERAL OPERATION To further contribute to a full and complete understanding of the present invention, an explanation of its mode of operation is set forth in the following paragraphs with reference to FIGS. 2 and 3, a the operation selected for such purpose being an entry operation involving the single digit wheel 132, the

selector carriage wheels 1311, 131, the intermediate wheels 129, and a selected set of accumulator wheels 21, each of which is illustrated in FIG. 1. Assuming that the amount to be entered has been indexed in the keyboard and accordingly registered in appropriate orders of the selector carriage, the plus motor bar 233 (P16. 3) is then depressed to effectively engage the wheels 131 with the intermediate wheels 129 and to advance the transfer wheels 1113 a differential clockwise distance as the wheels 131 are zeroized, such latter wheels being thereafter disengaged from the wheels 129 as the accumulator wheels 21 are engaged with the transfer wheels 113.

Upon depression of the plus motor bar 233, an associated pair of indexing levers 235 are rotated in a clockwise direction on the shaft 236, and the pivot bail 237 is rotated in a clockwise direction on the pivot studs 239. At the point of maximum clockwise rotation of the pivot bail 237, the biased pin 241 engages the aperture 243 of the keyboard. During this clockwise rotation of the pivot hail, the slide rod 245 is axially shifted to the left by the projection 237A to thereby translate the plunger shaft 259 to its retracted position relative to the abutment sleeve 2611. As the plunger shaft 259 is translated to the left, the disc 2 39 effectively translates the sleeves 250 and 251 to the left as the springs 255 and 257 are further compressed between their respective boundaries. During the leftward translation of the sleeve 251, the collar of such sleeve is displaced from its blocking position relative to the drive trip lever 227 thereby releasing such lever to the control of the spring 263. The lever 227 is accordingly rotated in a clockwise direction on the shoulder stud 229 so that its frontmost extremity is inserted between the abutting collars of the two sleeves at a point of separation designated 253 in FIG. 3. The clockwise rotation of the drive trip lever 227 is effective to release the clutch-dog 215 to the control of the spring 219, the clutch-dog thereby being rotated into engagement with the rotating elongated gear 211. The shaft 14-3 and the several cams fixed thereto are thereupon rotated one complete revolution in a counterclockwise direction. Early in this rotation of the shaft 143, the cams 201 impinge against the rollers 2115 of their respective cam follower assemblies 207 to thereby rotate these assemblies in a clockwise direction on the shaft 175, such clockwise rotation resulting in a nine tooth clockwise advancement of the gears 209, the sleeve 141, and the locking spacers 145. The transfer wheels 113 tend to follow the nine tooth advancement of the locking spacers 145, as motivated by their respective springs 191, until such time as they are individually limited by the zeroizing of the corresponding intermediate wheels 131. When, during the rotation of the shaft 143, the sleeve 141 and locking spacers 145 have been rotated a full nine tooth distance, the raised portions of the cams 281 recede from the rollers 283 of the arms 275, the springs 277 thereupon activating the arms 275 and the shaft 181 downwardly to release the tails 271A of the ratchet pawls 271. The latter pawls are accordingly rotated into blocking relationship with the ratchet strips 269 by the springs 273. The transfer wheels 113 are correspondingly blocked against additional clockwise rotation during the time the intermediate wheels 131 are disengaged therefrom and the accumulator wheels 21 are engaged therewith.

At a predetermined later point in the counterclockwise rotation of the shaft 143, a raised portion of the cam disc 213 effectively rotates the drive trip lever 227 in a counterclockwise direction on the shoulder stud 229, to thereby reposition the projection 227A of such lever into the path of travel of the clutch-dog 215, the latter being thereafter intercepted by such projection as the cam disc 213 completes its counterclockwise revolution. As the drive trip lever 227 is rotated in a counterclockwise direction, the frontmost extremity thereof is withdrawn from its inserted position between the collars of the sleeves 250 and 251, against the bias of the spring 263. The sleeve 251 is accordingly translated rightwardly by the spring 255 into limiting contact with the collar of the sleeve 250, the collar of such translated sleeve thereupon assuming a blocking position relative to the frontmost extremity of the drive trip lever.

At a predetermined point in the counterclockwise rotation of the shaft 143, the cams 199 impinge against the rollers 2&13 of their respective cam follower assemblies 207 to thereby rotate these assemblies in a counterclockwise direction on the shaft 175, such counterclockwise rotation resulting in a nine tooth counterclockwise return of the gears 209, the sleeve 141, and the locking spacers 145. This return rotation of the locking spacers is effective to return the transfer wheels 113 from their differentially set positions to their zero home positions, by means of the steps 197 and the studs 195. The return of the transfer wheels from their differentially set positions to their zero home positions is effective to transfer the indexed amount into the accumulator wheels 21 (FIG. 1), such wheels, as previously indicated, having been engaged with the transfer wheels prior to such return rotation thereof.

At still a later point in the counterclockwise rotation of the shaft 143, the raised portions of the cams 281 cooperate with the rollers 283 of the arms 275 to elevate the latter arms and the shaft 181 supported therebetween, the shaft thereby serving to rotate the ratchet pawls 271 in a clockwise direction on the shaft 17 7 so that their lowermost extremities are located in a cleared relationship with the ratchet strips 269.

Upon completion of the described data entry operation, means associated with the selector carriage 130, 131 of the printing calculator is effective to release the biased pin 241 from the aperture 243 of the keyboard 231, whereupon the plunger shaft 259 and the slide rod 245 are translated rightwardly to their home positions by means of the spring 257, the rightward translation of the slide rod 245 being effec tive to rotate the pivot bail 237 in a counterclockwise direction to its home position, by means of the projection 237A. It can thus be seen that the preferred embodiment of the invention is effective to receive digital information from selected exterior means representatively illustrated in FIG. 1, and to thereafter distribute such information to selected storage or operating sections of the printing calculator.

While the invention has been shown and described in considerable detail, it will be understood that other variations thereof may be had without departing from the spirit and scope of the invention.

We claim:

1. Transfer means for receiving and distributing data in a calculator having motive means, a keyboard, and a plurality of data processing means, said transfer means comprising:

a. a rotatably supported first shaft disposed in contiguous relationship with said data processing means;

b. coupling means associated with said motive means and responsive to said keyboard, said coupling means being effective to rotate said first shaft one complete revolution during each cycle of operation of said calculator;

c. a plurality of toothed wheels rotatably supported by said first shaft in engageable relationship with said plurality of processing means;

d. means for mounting said toothed wheels on said first shaft for reciprocal rotation thereon as said shaft is rotated 'said complete revolution;

e. yieldable means associated with and providing said toothed wheels with a differential rotational movement on said mounting means; and

f. means for reciprocally and differentially rotating said toothed wheels during said revolution of said first shaft, said rotation of said toothed wheels in combination with the controlled engagement of selected pairs of said processing means therewith being effective to selectively transfer data as between a yielding one and a receiving one of said means.

2. The transfer means defined in claim 1 wherein said means for mounting said toothed wheels on said first shaft for reciprocal rotation thereon additionally comprises:

a. a sleeve rotatably supported by said first shaft;

b. a plurality of mounting collars fixed to said sleeve, each of said collars comprising a plurality of arcuate flanges disposed along the inner diameter thereof in contiguous relationship to said sleeve; and

c. a plurality of arcuate projections disposed along the inner diameter of each of said toothed wheels.

3. The transfer means defined in claim 2 wherein each of said arcuate flanges disposed along said inner diameter of each of said mounting collars additionally comprises:

a. a web portion disposed at right angles to the plane of said mounting collar; and

b. an upturned portion extending in the direction of the periphery of said collar, said web portion and said upturned portion forming a channel within which the corresponding arcuate projection of the associated toothed wheel is retainably and rotatably nested.

4. The transfer means defined in claim 2 wherein said yieldable means associated with and providing said toothed wheels with a differential rotational movement on said mounting means additionally comprises:

a. a stud fixed to each of said toothed wheels;

b. a radially disposed abutting surface angularly formed in the circumference of each of said mounting collars in cooper-able relationship with said stud fixed to said toothed wheel;

c. a spring anchor fixed to each of said toothed wheels at a point contiguous to the circumference thereof;

d. an arcuate slot formed in each of said toothed wheels in contiguous relationship to its circumference and in a hemicycle thereof opposite the hemicycle comprising said spring anchor;

e. a rod supported by suitable means disposed in said calculator and extending through said arcuate slots formed in said toothed wheels; and

f. a semicircularly arranged spring connecting said spring anchor of each of said toothed wheels and said rod, each of said springs serving to bias its associated toothed wheel in an advancing rotational direction relative to its associated mounting collar such that said stud fixed to said toothed wheel is urged into contacting relationship with said abutting surface formed in said mounting collar.

5. The transfer means defined in claim 1 wherein each of said plurality of toothed wheels comprises a predetermined equal number of teeth disposed along the circumference thereof, said predetermined number being sufficient to accommodate the coincidental nine tooth advancement of the pinions of said plurality of processing means with which it is engageably related.

6. The transfer means defined in claim 4 wherein said means for reciprocally and differentially rotating said toothed wheels during said revolution of said first shaft additionally comprises:

a. a pair of gears fixed to said sleeve in spaced-apart relationship;

b. first cam means fixed to said first shaft in contiguous relationship to said pair of gears; and

e. a pair of rotatably supported cam followers disposed in cooperating relationship with said first cam means and with said pair of gears, each of said cam followers comprising a plurality of teeth engageably associated with a corresponding one of said gears, said first cam means in cooperation with said pair of cam followers and with said pair of gears being effective to advance and return said sleeve and said plurality of mounting collars a predetermined rotational distance during each revolution of said first shaft, said predetermined advancing rotation of said mounting collars in cooperation with said springs biasing said toothed wheels in an advancing direction relative thereto being effective to yieldably advance said toothed wheels a differential rotational distance as influenced by said yielding one of said plurality of processing means, said predetermined return rotation of said mounting collars being effective to differentially return said toothed wheels by means of the driving action of said abutting surfaces of said mounting collars against said studs fixed to said toothed wheels.

7. The transfer means defined in claim l1 wherein said coupling means effective for rotating said first shaft said one complete revolution during each cycle of operation of said calculator additionally comprises:

a. rotatable driving means associated with said motive means and responsively conditionable by said keyboard for continuous rotation in a predetermined direction;

b. clutch means associated with said first shaft and with said driving means, said clutch means being effective for coupling said first shaft to said rotating driving means; and

c. clutch control means responsive to said keyboard for activating said clutch means, and responsive also to said revolution of said first shaft for deactivating said clutch means.

8. The transfer means defined in claim 7 wherein said rotatable driving means additionally comprises:

a. a second shaft rotationally connected to said motive means, said second shaft being axially disposed of said first shaft and conditionable by said keyboard for continuous rotation in a predetermined direction; and

b. an elongated gear fixed to said second shaft, said elongated gear being continuously rotated by said motive means as conditioned by said keyboard.

9. The transfer means defined in claim 8 wherein said clutch means effective for coupling said first shaft to said rotatable driving means additionally comprises:

a. a cam disc fixed to one extremity of said first shaft in contiguous relationship to an adjoining extremity of said elongated gear, said cam disc comprising a raised portion disposed along the circumference thereof and a pivot stud disposed on its outermost side surface at a point angularly adjacent said raised portion;

b. a clutch-dog pivotally carried by said pivot stud of said cam disc said clutch-dog comprising a freeend abutting surface and at least one detent dog disposed intermediate said pivot stud and said free-end abutting surface in engageable relationship with the teeth of said elongated gear; and

c. spring means effectively biasing said clutch-dog in such direction on said pivot stud as to engage said detent dog with said teeth of said elongated gear, said engagement being effective to couple said rotating second shaft of said driving means with said first shaft.

10. The transfer means defined in claim 9 wherein said clutch control means effective for activating and deactivating said clutch means additionally comprises:

a. a bifurcated drive trip lever pivotally supported in cooperating relationship with said clutch-dog and with said cam disc said drive trip lever having an offset projection disposed in cooperable relationship with said freeend abutting surface of said clutch-dog and a roller disposed in cooperable relationship with said cam disc;

b. lever biasing means effectively biasing said drive trip lever in the direction of its clockwise-rocked position wherein its said offset projection is positioned in cleared relationship with said free-end abutting surface of said clutch-dog and wherein its said roller is positioned in contacting relationship with said cam disc;

c. lever blocking and release means effective for holding said drive trip lever in its counterclockwise-rocked position wherein its said offset projection is positioned in contacting relationship with said free-end abutting surface of said clutch-dog and its said roller is positioned in cleared relationship with said cam disc said lever blocking and release means being biased in the direction of its lever blocking position and being also translatable to a lever releasing position wherein said drive trip lever is released to the control of said lever biasing means;

d. at least one depressibly activated operation control key associated with said keyboard; and

e. linkage means responsive to the depression of said operation control key and effective for translating said lever blocking and release means to its said lever releasing position wherein said lever is released to the control of said lever biasing means and said clutch-dog is released to the control of its said spring means to thereby engage said detent dog with said elongated gear and to couple said rotating second shaft with said first shaft.

ll. The transfer means defined in claim 10 wherein said clutch control means is effective to deactivate said clutch means upon completion of a single revolution of said first shaft, said deactivation being effectuated by the action of said raised portion of said cam disc on said roller of said drive trip lever, said action serving to rock said lever to its said counterclockwise-rocked position wherein its said offset projection is positioned in the path of travel of said free-end abutting surface of said rotating clutch-dog and wherein its foremost extremity is elevated to a position permitting said lever blocking and release means to be resiliently translated to its said blocking position relative to said drive trip lever, said clutchdog carried by said first shaft being disengaged from said elongated gear fixed to said rotating second shaft when said freeend abutting surface of said clutch-dog contacts said offset projection of said drive trip lever.

12. The transfer means defined in claim 10 wherein said lever blocking and release means of said clutch control means additionally comprises:

a. a plunger shaft translatably supported by an abutment sleeve, said plunger shaft having a disc fixed to the extending end thereof;

b. a first collared sleeve translatably carried by said plunger shaft, the collar of said sleeve serving to blockingly hold said drive trip lever in its said counterclockwise-rocked position;

0. a second collared sleeve axially disposed of said first collared sleeve on said plunger shaft, said second sleeve having a collar of greater diameter than the collar of said first sleeve, said collars of said sleeves being disposed in adjacent abutting relationship;

d. a first spring carried by said first collared sleeve, said spring effectively biasing said first sleeve into blocking relationship with said drive trip lever; and

e. a second spring carried by said second collared sleeve, said spring effectively biasing said second sleeve into cleared relationship with said disc and biasing also said plunger shaft into an extended relationship relative to said abutment sleeve.

13. The transfer means defined in claim 12 wherein said linkage means effective for translating said lever blocking and release means to its said lever releasing position additionally comprises:

a. at least one pivotally supported and upwardly biased keyboard indexing lever transversely disposed in said keyboard, said indexing lever having a depending projection disposed along the lower edge thereof;

b. a pivot bail longitudinally disposed in a cutout formed in the underside of said keyboard, said pivot bail having a depending projection disposed at the rearmost extremity thereof and a web portion disposed in contactable relationship with said depending projection of said indexing lever; and

c. a slide rod disposed in a cylindrical chamber of said keyboard in axially alined relationship with said depending projection of said pivot bail and with said plunger shaft of said lever blocking and release means, said depression of said operation control key being effective to translate said slide rod into contacting relationship with said plunger shaft by means of said indexing lever and said pivot bail, said translation of said slide rod effectively translating said plunger shaft into its retracted position in said abutment sleeve, said retraction effectively translating said first collared sleeve to its releasing position relative to said drive trip lever, said latter translation being effectuated against the bias of said second and said first springs and by means of said disc of said plunger shaft acting on said second collared sleeve, said arrival of said first collared sleeve in its said lever releasing position being effective to release said drive trip lever to the control of its said lever biasing means whereupon the foremost extremity thereof is insertably positioned between said adjacent collars of said first and said second collared sleeves.

14. The transfer means defined in claim 13 wherein said counterclockwise rocking of said drive trip lever by said cam disc of said clutch means during said single revolution of said first shaft is effective to displace said foremost extremity of said lever from its said inserted position between said adjacent collars of said first and said second collared sleeves, said displacement being effective to translate said first collared sleeve to its blocking position relative to said drive trip lever as motivated by said first spring, said second collared sleeve and said plunger shaft of said lever blocking and release means and said slide rod of said linkage means being returnably translated thereafter by said second spring as said pivot bail, said indexing lever and said operation control key of said keyboard are returned to their respective home positions by means disposed within said keyboard.

15. The transfer means defined in claim 6 and additionally comprising: means for limiting said differential advancement of said toothed wheels as said receiving one of said plurality of processing means is engaged therewith and as said yielding one of said processing means is disengaged therefrom.

16. The transfer means defined in claim 15 wherein said means for limiting said differential advancement of said toothed wheels additionally comprises:

a. a ratchet strip disposed on the side surface of each of said toothed wheels adjacent said arcuate slot formed therein;

b. a stationary third shaft disposed in transverse contiguous relationship to said plurality of toothed wheels;

c. a plurality of ratchet pawls pivotally carried by said third shaft in cooperable relationship with said ratchet strips of said toothed wheels; and

d. means for activating and deactivating said ratchet pawls at predetermined points in said revolution of said first shaft, said point of activation corresponding to the time during said reciprocal rotation of said mounting collars when said toothed wheels have been advanced their full differential distance, and said point of deactivation corresponding to the time when said toothed wheels have been returned their full differential distance to their home positions, said activation of said pawls consisting of their pivotal movement into contacting relationship with their corresponding ratchet strips, and said deactivation of said pawls consisting of their pivotal movement away from said contacting relationship.

17. The transfer means defined in claim 16 wherein said means for activating and deactivating said ratchet pawls addi tionally comprises:

a. a third and fourth collared sleeve outwardly disposed of said pair of gears fixed to said sleeve supported by said first shaft, said first shaft being freely rotatable within said third and fourth collared sleeves;

b. a pair of end-slotted oscillating arms disposed in upright adjacent relationship to said third and fourth collared sleeves, said slots formed in the lowermost extremities thereof being disposed in straddling relationship with corresponding grooves formed by said collars thereof, each of said arms being biased downwardly by means of a spring connected at one end to said arm and at the other end to an aperture formed in a corresponding one of said collared sleeves, each of said arms having a roller disposed on the innermost surface thereof;

c. second cam means fixed to said first shaft in cooperating relationship with said rollers of said pair of oscillating arms, said cams of said cam means having both raised and depressed portions;

d. an oscillating fourth shaft carried by apertures formed in said pair of oscillating arms adjacent said slots in said uppermost extremities thereof; e. a stationary fifth shaft disposed in parallel relationship to said third and fourth shafts;

f. a plurality of springs connected to said ratchet pawls and to said fifth shaft, said springs pivotally biasing said ratchet pawls into contacting relationship with said ratchet strips; and

g. a plurality of rearwardly extending tails disposed on said ratchet pawls in cooperating relationship with said fourth shaft, said raised portions of said cam means in cooperation with said rollers of said oscillating arms being effective to hold said arms and said fourth shaft in their respective elevated positions when said mounting collars and toothed wheels are located in their home and advancing positions, and said depressed portions of said cam means in cooperation with said rollers permitting said springs connected to said oscillating arms to activate and to hold said arms and said fourth shaft to and in their respective lowered positions during said return rotation of said mounting collars and toothed wheels, said elevated positioning of said fourth shaft being effective to maintain said ratchet pawls in disengaged relationship with their associated ratchet strips against the bias of their respective springs attached to said fifth shaft, and said lowered positioning of said fourth shaft permitting said springs to maintain said ratchet pawls in engaged relationship with said strips, said engaged relationship of said pawls and said strips being effective to block said toothed wheels against further advancing movement.

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