US2367386A - Calculating machine - Google Patents

Description

Jan. 16, 1945. L p CROSMAN CALCULATING MACHINE Filed Aug. 21, 1943 5 Sheets-Sheet l -aub mi w INVENTOR A TTORNE Y Jan. 16, 1945. R CROSMAN 2,367,386

CALCULATING MACHINE Filed Aug. 21, 1945 3 Sheets-Sheet 2 gZh \f p ATTORINEY Jan. 16, 1945. P. CROSMAN 2,367,386

CALGULAT ING MACHINE Filed Aug. 21, 1945 3 Sheets-Sheet 3 W 33 29 P Q 55 Patented Jan. 16, 1945 UNITED STATES PATENT OFFICE CALCULATING MACHINE Lorlng Pickering Crosman, South Orange, N. 1., assignor to Monroe Calculating Machine Company, Orange, N. 1., a corporation of Delaware Application August 21, 1943, Serial No. 499,742

9 Claims. (Cl. 102-145) The invention has relation to calculating machines, and more particularly to means for completing an operation and for bringing the machine to rest with the parts in normal-position.

In rotary type calculating machines the operations of multiplication and division commonly involve repeated cycling of the differential actuators, followed by a cycle terminating action responsive to a signal which may be transmitted at any stage of the operation, up to the fullcycle position of the actuators. U. S.Pate nt No. 1,566,650, issued to George C.- Chase on December 22, 1925, shows means for bringing the machine to rest without shock by permitting a retarded overrun of the differential actuators beyond their full-cycle position in response to a stopping signal, followed by the location of the parts in their normal, full-cycle positions.

. The completion of a machine operation, however, and the normalizing of the various control devices, may involve considerable drag upon the overrun means, as for instance in completing the tens transfer action in the register, as shown in U. S. Patent No. 1,845,863, issued to George C. Chase on February 16, 1932. It is an object of the present invention to insure completion of the machine operation in a uniform manner under all conditions, by providing a positive drive of the differential actuators beyond and reversely back to their full-cycle position.

The invention consists in the novel construction and combination of parts, as set forth in the appended claims.

In the accompanying drawings, illustrating the invention:

Fig. 1 is a left side elevation of the clutch control mechanism of a calculating machine embodying the invention.

2 is a similar view of the main clutch and controlling elements.

Fig. 3 is a left side elevation of the rear portion of the calculating machine with the casingremoved, showing portions of the novel mechanism.

Fig. 4 is a front elevation of the clutches and driving connections.

Figs. 5, 6 and '7 are detail views of the locating cams, the harmonic stopping cams, and the auxiliary clutch respectively, shown in their normal positions of rest.

Figs. 8, 9 and 10 are corresponding views with the parts shown in positions taken" during the cycling of the machine.

Figs. 11, 12 and 13 are corresponding views showing the parts in the positions taken at the extreme limit of the overrun of the differential actuators.

Transmission control means I05 (Figs. 2 and 4) through which power is taken from the electric motor I00 to operate the differential actuators of the calculating machine is herein termed the main clutch since it includes two members engageable to effect the transmission. The transmission means is of the differential gear type disclosed in Patent No. 1,566,650, hereinbefore referred to, this patent showing details of such mechanism not herein specifically shown. With the motor running idle two legs of the differential are driven in opposite directions. Upon interruption of rotation of one leg of the differential, by engagement of one arm of a clutch lever III with a lug I0I fixed upon the rotating part, the third leg of the differential (having driving connection with the differential actuators of the calculator) will be driven in a given (additive) direction, whereas interruption of rotation of the other leg of the differential, by engagement of the other end of clutch lever III with a lug H0, fast to the rotating part, will effect reverse or subtractive rotation of the actuator.

The driven element of clutch I05 has gearing connection It with a shaft I0 having one-to-one driving connection with the differential actuators (not shown), shaft I9 also being provided with a crank arm 20, through which the actuators are located in full cycle position at termination of a calculating operation.

The selection of the arm of clutch lever III which is to be engaged with the differential gear clutch I00 is effected by movement of a rock shaft I25 (Fig. 1), which may be rocked in one direction or the other by means of add and subtract keys (as in Patent No. 1,566,650) or by means of other operation control mechanisms. Shaft I25 is provided with an arm having link connection H2 with a bell crank lever H3, said bell crank having ,pin and slot connection with a plate Ill (Fig. 2) slidably supported upon a shaft H5, and having shoulder portions H6, H1 lying above and adjacent to pins fixed in the opposite arms of clutch lever III, and upon rotation of shaft I25 in a counter clockwise direction as viewed in Fig. 1, plate III will be moved to the right as seen in Fig. 2, and shoulder H6 will be brought into position over the left hand pin of clutch lever III. In this position of the parts depression of plate I It will move clutch lever I I I into position to be engaged by one of the lugs I0'I of the clutch, and additive rotation of the diflerential actuators will be eflected. Clockwise rotation of shaft I25, on the other hand, will move plate H4 to the left, and lug HI will lie above the opposite pin of clutch lever l l i, so that depression of plate H4 will effect engagement of the clutch lever with a lug H of the clutch to effect subtraction.

According to the present invention the main clutch is engaged by means of an auxiliary clutch, this auxiliary clutch being also given a second operation to effect the stopping and rotation of the differential actuators. The auxiliary clutch is tripped upon rocking movement of shaft I25 in either direction, this engagement being effected by means of a link 2i (Fig. 1) connecting bell crank lever I I3 with an arm 22, fast upon a shaft 23, shaft 23 being also provided with an arm 24 (Fig. 3) having a roller normally lying between two lpawls 25, 25, mounted upon an intermediately fulcrumed lever 26. The lower arm of lever 26 has a, lug 21 normally resting against a shaft 26 anad underlying a cam portion of one element 29 of a toggle link. Element 29 is pivoted upon the framing of the machine at 36, the associated element 32 of the toggle having pivotal connection with a bail 33 (Figs. 1, 3 and 7) mounted upon shaft 28. Toggle 29, 32 normally locks ball 33 against clockwise rotation under the influence of a spring 43, secured to an arm 42 to be described. The detent 35 of the auxiliary clutch is also mounted upon shaft 26 and has an arm lying in front of the ball 33, as seen in Fig. 7.

Upon rocking movement of the shafts I25 and 23 in either direction the roller of arm 24 will be brought against one of the pawls 25 and lever 25 will be rocked counterclockwise as seen in Fig. 3, breaking toggle 29, 32, and allowing the bail 33 to move the detent 35 out of restraining engagement with a pawl 36, pivoted upon the driven member of the clutch.

As shown, there are two clutch pawls 35, 31

' biased by a spring 39 for engagement with internal ratchet teeth of the driving element 39 of the clutch, these pawls engaging in opposite directions, so that the driven element may not outrun the driver. The pawls are provided with engaging extensions, pawl 36, when held out of engaging position by detent 35, holding pawl 31 out of engagement. The driving member 39 of the clutch is fixed upon a shaft 40 (Fig. 4) having gearing connection 4! with the shaft iii of motor Hill, which extends through clutch Hi5.

In order to hold the sign determining slide H4 as set until the main clutch may be operated, no matter how quickly the finger of the operator may be removed from the operating key, a quick stroke latch is provided, comprising an arm 42 (Fig. 1) held by the spring 43 in contact with the ball 33. Upon clockwise movement of ball 33 arm 42, which is pivoted upon the shaft 29, will follow in a clockwise direction, the free end of this arm engaging either above or below a lug 44, formed upon an extension of the arm 22 of shaft 23, according to the direction in which said shaft has been rocked. l'hus arm 42 prevents the return of membms 22, 2|, H3 and H4 to their normal unset position.

The auxiliary clutch having been engaged, the first action will be the unlocking of the difler- .rtial actuators from tne restraint of the devices which normally h; '1 them in full cycle position. This locating means comprises a pair of cams 45 (Figs. 3 and fixed for rotation with the driven element of the auxiliary clutch. Normally cams 45 stand in the position illustrated in Fig. 5, in which position both cams engage the roller mounted in a rocker frame 43, having link connection with the crank arm 23 of shaft I 3. Game being rotated in clockwise direction by the auxiliary clutch, will move into the position illustrated in Figure 8, wher n h y will lie out of the path of movement of the rollers of rocker frame 46, leaving the differential actuators free to rotate.

Operation of the auxiliary clutch will effect engagement of the main clutch as follows: Fast with the driven element of the auxiliary clutch is a notched disk 41 (Figure 1) having its periphery engaged by a roller mounted upon the end of an arm 45 fixed upon the shaft H5. An arm 49 (Fig. 2) is also fixed upon shaft H5, this arm having pin and slot engagement with the free end of plate H4. Rotation of disk 41 by the auxiliary clutch will bring the notched portion thereof opposite the roller of arm 46, whereupon a spring 50 will rock the arms 49 and 49 counterclockwise, bringing the lug H6 or the lug H! of plate H4 into contact with the related pin of clutch lever iii, and rocking said lever to engage the main clutch.

Operation of the auxiliary clutch is now interrupted by engagement of clutch pawl 38 with the inclined wall of a plate 5| (Figure 10) fixed upon the machine frame. Plate 5| is provided with an extended or dwell portion to prevent reengagement of the auxiliary clutch by the momentum of the disengaged driven elements.

During the calculating operation of the machine the auxiliary clutch detent 35 will be re leased from restraint by bail 33, and the quick stroke latch 42 will be disengaged, as follows: Toggle element 29 is provided with a cam extension 52 (Figure 3 which, in the broken or operated position of the toggle will lie in the path of movement of a roller 53 mounted on a rocker frame 54 (Figure 6) having link connection with crank arm '20 of shaft i9, and in the rotation of said shaft roller 53 will be rocked into en gagement with the cam portion 52 of toggle element 29, moving bail 33 and arm 26 back to their normal positions, and reinstating toggle lock 29, 32.

At the end of a calculating operation the auxiliary clutch is reengaged by means of a lever 54 (Figs. 1, 10 and 13) fulcrumed upon the framing of the machine and normally latched in inoperative position by means of an escapement device comprising primary and secondary latches 55, 56. Primary latch 55 normally engages a lug 51 of lever 54, said latch being pivoted upon the framing at 58, and held in latching position by a spring 59. The ball 33 engages latch 55, and upon clockwise movement of said bail, the latch will be disengaged from ing 57, whereupon lever 54 will be moved slightly clockwise, by the action of a spring 66, into engagement with the secondary latch 56, in which position lug 51 will lie above latch 55 and prevent the reengagement thereof. The signal for disengaging the main clutch and bringing the actuators to rest may come through the manual release of the operation key, or through movement of the numeral wheels of thu. register, as set forth in Patent No. 1,566,650. Ir case of manual release of the key a centralizing or normalizing device 6| for the shafts I25 and 23 will operate to bring the cam tooth 62 (Figure 1' into contact with a pin fixed in the secondary latch 56, moving said latch out of engagement with lug 51 and allowing lever 54 to be fully retracted by spring 60. This movement will bring assm'se move only a short distance into contact with roller 53, and will move into fully retracted position when roller 53 has been moved below cam portion 65, approximately at the end of the actuator cycle. As the actuators pass through the full cycle position, roller 53 will rise and lever 54 will be rocked counterclockwise, bringing pawl 83 against roller 64, and rotating the driven member of the clutch sufficiently to allow the clutch pawl 36 to drop from engagement with plate 5| into engagement with the ratchet teeth of the drive member 38 of the clutch.

The same operations will follow a stopping signal from the numerals wheels, transmitted through the known lever 3| operated by said wheels and engaging an arm of the secondary latch 56.

The lever 54 will be reengaged with the'primary latch 55 during the final action of'the" auxiliary clutch by engagement of the roller 64 with an arm 86 of said'lever (Fig. 13). The auxiliary clutch being reengaged, will drive notched disk 41, forcing the roller of arm 48 out of the notch and thereby releasing the main clutch by the contact of arm 49 with the pins of clutch lever'l I I.

The overrun of the differential actuators and the return thereof to full cycle position is governed by means of a pair of cams 61, 88 (Figures 6, 9 and 12), fast with the driven element of the auxiliary clutch and engaging rollers of the rocker frame 54. Actually, as shown, the cam 81 forms such driven member, the pawls 36, 3! and the roller 64 being mounted upon said cam. Preferably, the initial movement imparted to the calculator drive by cam 68 is faster than the running speed of the machine, so that there will be no frictional resistance to the disengagement of the main clutch. The cams are so designed that movement of the differential actuators from full cycle to full overrun position will be harmonieally retarded, and thereafter the actuators will be returned to their full cycle position by a harmonically accelerated and retarded movement. Toward the end of this operation the cams l5 effect the final restoration and locking of the actuators in their full cycle position.

As the cams come back into the positions illustrated in Figs. 5 and 6, the pawl 36 of the auxiliary clutch will contact the detent 35 and the pawls will be lifted out of engagement with the teeth of driving member 39. At the same time a lug 69 of cam 61 will engage the end of detent 35 as seen in Figure '7, arresting the movement of the driven members of the auxiliary clutch mechanism. I

I claim:

1. In a motor driven calculating machine having power transmission control me 5 including two members engageable to effect t e transmission, an operating shaft cyclically driven under control of said means, and engaging means alternately adjustable to engage and to disengage said transmission control elements; an auxiliary clutch, power operated means acting to engage the auxiliary clutch, and means operable by the auxiliary clutch and cooperating with the engaging mean to disengage the transmission control elements and acting to drive the operating shaft first through a given number of degrees of rotation beyond and thereafter reversely back to full-cycle position.

.2. In a motor driven calculating machine having power transmission control means includins two members engageable to eilect the transmission, an operating shaft cyclically driven under control of said means, and engaging means alternately adjustable to engage and to disengage said transmission control elements; an auxiliary clutch, power operated means acting to engage the auxiliary clutch, and means operable by the auxiliary clutch and including elements acting to adjust the engaging means to disengage the tron control elements and cams rotatable to drive the operating shaft first through a given number of degrees of rotation beyond its full-cycle position at a harmonically diminishing speed and thereafter reversely back to said full-cycle position.

3. In a motor driven calculating machine having power transmission control means including two members engageable to effect the transmission. an operating shaft cyclically driven alternatively in one or in the other direction under control of said means, and provided with a crank arm, and engaging means alternately adjustable to engage and to disengage said transmission control-elements; an oscillatory arm, a link connecting said arm with the crank arm of the operating shaft and maintaining the parts out of dead center position, an auxiliary clutch, and means operable by the auxiliary clutch and including elements acting to adjust the engaging means to disengage the transmission control elements and cams rotatable to drive the oscillating arm. to eflect movement of the operating shaft through a given number of degrees of rotation beyond its full-cycle position.

4. In a motor driven calculating machine having power transmission control means including two members engageable to effect the transmission, an operating shaft cyclically driven under control of said means, and engaging means alternately adjustable to engage and to disengage said transmission control elements; an auxiliary one cycle clutch cooperating with the engaging means to engage the transmission control elements, means for disengaging the auxiliary clutch in mid cycle position, power operated means acting to reengage the auxiliary clutch, and cam means driven by the auxiliary clutch to operate and locate the operating shaft, including elements normally holding said shaft in full-cycle position, elements cooperating with the engaging means upon initial action of the auxiliary clutch to disengage the transmission control elements, and elements operable upon reengagement of the auxiliary clutch to drive the operating shaft first beyond and thereafter reversely back to its full-cycle position, said cam means being designed in the position assumed thereby in the mid-cycle disengaged position of the auxiliary clutch, to release the operating shaft for rotation through the transmission control means.

5. In a motor driven'calculating machinehaving a power transmission control means includ- 1113 two members engageable to effect the transmission, machine operating means cyclically driven under control of said means, and engaging means alternately adjustable to engage and to disengage said transmission control elements; an auxiliary one cycle clutch cooperating with the engaging means to engage the transmission control elements, means for disengaging the auxiliary clutch in mid-cycle position, power operated means acting to reengage the auxiliary clutch, cam means driven by the auxiliary clutch during the initial action thereof to condition the operating means for operation by said transmission control means, and cam means driven by the auxiliary clutch during the final operation thereof to restore the operating means to normal position of rest.

6. In a motor driven calculating machine having power transmission control means including two members engageable to effect the transmission, machine operating means cyclically driven under control of said means, engaging means alternately adjustable to engage and to disengage said transmission control elements, and means operable to signal the completion of a machine operation; an auxiliary one cycle clutch cooperating with the engaging means to engage the transmission control elements, means for disengaging the auxiliary clutch in mid-cycle position, means operating in time with the machine operating means and controlled by the signal means to reengage the auxiliary clutch, cam means driven by the auxiliary clutch during the initial action thereof to condition the operating means for operation by said transmission control means, and cam means driven by the auxiliary clutch during the final operation thereof to restore the operating means to normal position of rest.

7. In a motor driven calculating machine having an operating train; a clutch in said train comprising a toothed rotary driving member, a rotary driven member, and a spring urged pawl mounted on said driven member, a stationary plate projecting into the path of movement of said pawl and designed to disengage the pawl from the teeth of the driving member, and means for inparting sumcient rotary movement to the driven member to move the pawl out of contact with the plate and thereby allow engagement of the pawl with said teeth.

8. In a motor driven calculating machine having an operating train; control means interposed in said train and comprising a driven transmission member, rotary cam means for driving said member and designed in a given angular position to free said member for independent relative movement, and a clutch comprising a toothed rotary driving member, a rotary driven member having driving connection with said cam means, and a spring urged pawl mounted on said driven clutch member, a stationary plate projecting into the path of movement of said pawl and designed to disengage the pawl from the teeth of the driving member as the cam means move into position of independent movement relative to the driven transmission member, and means for imparting sufficient rotary movement to the driven clutch member to move the pawl out of contact with the plate and thereby allow engagement of the pawl with said teeth.

9. In a motor driven calculating machine having an operating shaft, and power transmission control-means including two members engageable to effect the transmission selectively engageable to effect forward or alternatively reverse rotation of said shaft; engaging means including a member adjustable to determine engagement of the transmission control elements for forward or alternatively for reverse rotation of the shaft, an auxiliary clutch, means operable by the auxiliary clutch to operate the engaging means, an operation key, and means operable by said key to adjust the direction determining member of the engaging means and to engage the auxiliary clutch.

LORIN G PICKERING CROSMAN.

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