US2777386A - Multiple item receipt printing - Google Patents

Description

Jan. 15, 1957 ll She'ets-Sheet 1 Filed Feb. 27, 1953 [NVENTOR GEORGE H. SEENEY BY 14,, M '43 ,W

IS ATTORNEYS Jan. 15, 1957 e. H. SEENEY 2,777,386

MULTIPLE ITEM RECEIPT PRINTING MECHANISMS Filed Feb. 27. 1953 11 Sheets-Sheet 2 INVENTOR GEORGE H. SEENEY I zwW HIS ATTORNEYS Jan. 15, 1957 G. H. SEENEY MULTIPLE ITEM RECEIPT PRINTING MECHANISMS Filed Feb. 27, 1953 ll Sheets-Sheet 5 IN VE NTO R GEORGE H. SEENEY m s jATToRNEYs Jan. 15, 1957 G. H. SEENEY 2,777,383

MULTIPLE ITEM RECEIPT PRINTING MECHANISMS Filed Feb. 27, 1953 ll Sheets-Sheet 4 FIG. 5 6

MM 2w" w INVENTOR GEOIRGE H. SEENEY BY 4 W HIS ATTORNEYS Jan. 15, 1957 G. H. SEENEY 2,777,386

MULTIPLE ITEM RECEIPT PRIN'IING MECHANISMS Filed Feb. 2'7. 1953 ll Sheets-Sheet 5 INVENTOR v GEORGE H. SEENEY m v BY IS ATTORNEYS Jan. 15, 1957 s. H. SEENEY MULT J IPLE ITEM RECEIPT PRINTLENG MECHANISMS 11 Shets-Sheet 6 Filed Feb. 27. 1953 INVENTOR GEORGE H. SEENEY BY I W H |S ATTORNEYS Jan. 15, 1957 G. H. SEENEY 2,777, 6

MULTIPLE ITEM RECEIPT PRINTING MECHANISMS Filed Feb. 27, 1955 ll Sheets-Sheet 7 mverrron GEORGE H. SEENEY HIS\ATTORNEYS' Jan. 15, 1957 G. H. SEENEY, 2,777,386

MULTIPLE ITEM RECEIPT PRINTING MECHANISMS Filed Feb. 27, 1953 11 Sheets-Sheet a I INVENTOR GEORGE H. SEENEY HIS ATTORNEYS Jan. 15, 1957 G. H. SEENEY MULTIPLE ITEM RECEIPT PRINTING MECHANISMS Filed Feb. 27, 1953 ll Sheets-Sheet 9 INVENTOR" GEORGE H. SEENEY IS ATTORNEYS FIG. I3

FIG. l4

Jan. 15, 1957 G. H. SEENEY 2,777,385

MULTIPLE ITEM RECEIPT PRINTING MECHANISMS Filed Feb. 27, 1953 11 Sheets-Sheet 1o INVENTOR GEORGE H. SEENEY M Xx HIS ATTORNEYS Jan. 15, 1957 ca. SEENEY 2,777,386 MULTIPLE ITEM RECEIPT PRINTING MECHANISMS Filed Feb. 27, 1953 11 Sheets-Sheet 11 +-*--2.4 s56 Hmcm, 541 l*- -5.a 4 :4

(N 555 m I m*--|.2 4:4

' mae- I. 4 2 w. BROWN 0. SON B I 0 l5 ST. '5 (T)* 4 I ANYTOWN M I v Q w. BROWN 3. SON

r*- 0.0 549 I5 HIGH ST. Tom. AT THE TOP ANY TOWN I M I-*5.l4.ll 543 I5 Ah TOTAL AT THE TOP TOTA W. BROWN 8 SON l5 HIGH ST. ANYTQWN INVEN TOR TOTAL AT THE TOP GEORGE H. SEENEY Bygwm HIS ATTORNEYS nited States Patent MULTIPLE ITEM RECEIPT PRINTING MECHANISMS George H. Seeney, Chingford, London, England, assignor to The National Cash Register Company, Dayton, Chic, a corporation of Maryland Application February 27, 1953, Serial No. 339,264

Claims priority, application Great Britain March 13, 1952 6 Claims. (Cl. 10166) This invention relates to cash registers and similar accounting machines and is more particularly concerned with the control of the ticket printing and feeding mechanisms.

The invention is illustrated as applied to machines of the type disclosed in the United States patents to Ernst Breitling, No. 2,209,763, issued on July 30, 1940, Warren P. London, No. 2,628,774, issued on February 17, 1953, Frank R. Werner, No. 2,661,061, issued December 1, 1953, and Karl H. Tenoort, No. 2,666,573, issued Ianuary 19, 1954.

In certain systems for which these machines are used, it is often desirable to feed the ticket strip variable extents depending upon the type of machine operation which is being performed; that is to say, in accordance with which function control member,.such as a depressible key or a movable lever, is operated.

For example, such machines may be adapted to issue two different kinds of receipt tickets, one bearing a single printed item and the other bearing a series of multiple items, either with or Without the total thereof. Where the total is printed, it is desirable that it be readily distinguishable from the individual items, as by being spaced well apart therefrom.

It is the object of the present invention to provide a simple and inexpensive mechanism by means of which, under the control of the function control members, the spacing of the items on the ticket can be varied, and which is easily incorporated into an existing machine without substantial modifications thereto, or which can be built into a new machine during assembly.

Accordingly, the invention comprises a cash register or similar accounting machine, including function control members, amount setting members, printing mechanism for printing on a record material, a record material feeding roller, a pressure roller cooperable with the feeding roller, a first engaging mechanism operable a-t machine operations, controlled by certain of the function control members, to bring the rollers into engagement with one another during part only of the rotation of the feeding roller so as to feed the record material a certain extent, a second engaging mechanism effective to engage the rollers during a longer period of rotation of the feeding roller so as to feed the record material a greater extent, a clutch for moving the pressure roller to engaged position, and a control device actuated upon operation of a certain other one of the function control members to actuate the clutch to cause the record material to be fed under control of the said second engaging mechanism to said greater extent.

The above and other, subsidiary, features of the present invention, as applied, by way of example only, to one manner of c" rying it into eifect, will now be described and are illustrated in the accompanying drawings.

In the drawings:

Fig. l is a perspective view of the machine.

Fig. 2 is a section taken alongside one of the amount key banks.

Fig. 3 is a view similar to Fig. 2 but shows the differential mechanism set under control of a depressed 7 amount key.

Fig. 4 is a front view of the ticket strip printing and feeding mechanisms.

Fig. 5 is a plan View of the ticket strip printing and feeding mechanisms.

Fig. 6 is a rear view of the ticket printing and feeding mechanisms.

Fig. 7 is a side view of the ticket strip printing and feeding mechanisms.

Fig. 8 is a perspective view of the ticket strip feeding mechanism and the mechanism controlled by the total key for causing a multiple line space feed.

Fig. 9 is a right side view of the machine driving gears.

Fig. 10 is a section taken alongside the clerks key and total key bank showing the connections to the totalizer shifting cam.

Fig. 11 is a plan view showing one denomination of the total-izer assembly and the clutch control mechanism for the resetting shaft, showing the No. 1 clerks totalizer selected for operation.

Fig. 12 is a detail View of the totalizer shifting cam and the slide for shifting the totalizer frame.

Fig. 13 is a side view showing the mechanism by which the clerks keys and the total key control the release of the machine.

Fig. 14 is a side view of the drive from the motor.

Fig. 15 is a detail view of the clutch for coupling the machine main shaft to the motor.

Fig. 16 is a detail view of the motor switch control mechanism.

Fig. 17 is a detail view of the mechanism for engaging the amount setting segments with the totalizcr wheels.

Fig. 18 is a right side view showing part of the machine release control mechanism, the resetting clutch control cam, and the slide for obscuring the totalizer wheels under control of the control lock.

Fig. 19 is a detail side view of one totalizer reset gear and associated totalizer wheel.

Fig. 20 is a side View of the totalizer reset clutch control mechanism in ineffective or normal position, with the main shaft partially rotated.

Fig. 21 is a side view of the totalizer reset clutch mechanism in effective position, with the main shaft partially rotated.

Fig. 22 is a detail view of part of the mechanism for causing a single line space of the ticket strip.

Fig. 23 is a. detail view of the clutch arm and cam for causing a multiple line feed of the ticket strip.

Fig. 24 shows a single item ticket.

Fig. 25 shows a multiple item ticket.

Fig. 26 shows three tickets bearing prints of the individual clerks totals.

GENERAL DESCRIPTION The machine to which the present invention is shown as applied, by way of example only, has five rows of amount keys for recording amounts up to 9.19.11%d., to the left of which are four function control keys, three of which are for recording entries in respect of individual clerks, and the fourth of which is a total key, which is used to control the wider spacing of total prints on the ticket strip.

The machine has a single cash drawer, although it can, if desired, be provided with a separate cash drawer for each clerk.

To the left of the function control keys are an on and off control lever for the ticket printing and feeding mechanisms, a ticket chute, and a window through which the usual audit strip is visible.

Located beneath the amount keyboard is a window 3 through which the individual clerks totalizer wheels can be read.

The function control keys are all motorized keys; that is, upon being depressed, they will release the machine for operation by the usual electric motor. An operating handle is provided for operating the machine manually when desired. The clerks keys also select individual clerks totalizers.

The usual front and rear indicators are provided, and the machine is equipped with a control lock, which can be turned by means of a key in the possession of an authorized person, so as to completely lock the machine when desired, to enable an obscuring shutter to be removed from the totalizer window, and to permit the totalizers to be reset.

Amount diflerential mechanism The amount keys 1 (Figs. 1, 2, and 3) are mounted on a key frame, which is supported on cross shafts 2 and 3 (Figs. 2 and 3) extending between side frames of the machine, one of which, 4, is shown in Figs. 4, 5, 6, 7, and 8, and the other of which, 5, is shown in Fig. 9.

Each amount key 1 (Figs. 1, 2, and 3) carries a stud 6 (Figs. 2 and 3), which is guided by slots 7 (Fig. 2) in a combined guiding and aligning plate 8, forming part of the key frame.

A slide 9 (Figs. 2 and 3) is suitably supported for reciprocating movement by slots, such as 10 (Fig. 3), therein, which are guided on studs 11 in the key frame, the slide 9 having a series of cam slots 12 (Figs. 2 and 3), one for each of the studs 6, by which means the slide 9 is moved upwardly when any amount key 1 is depressed.

A spring 13 (Fig. 2), anchored between a stud on the slide 9 and a stud secured to the key frame, tends to maintain the slide 9 in the position shown in Fig. 2.

On the front lower end of the slide 9 is a lug 14 (Figs. 2 and 3), which cooperates, when the parts are in the home position, as shown in Fig. 2, with a surface 15 (Figs. 2 and 3) on a zero stop 16, which is pivotally supported by a stud '7 secured to the key frame.

Secured to a shaft 18, extending across the bottom of the key banks, is a finger 19, which is adapted to cooperate with a stud in the lower end of the zero stop 16 to release depressed keys.

The upper end of the zero stop 16 carries a stud 21, which is adapted to cooperate with a finger 22 on a latch 23 pivoted on a stud 24 on a differential arm 25 loosely mounted on a main shaft 26.

Also pivoted on another stud 27 on the differential arm 25 is a coupling pawl 28. A spring 29, connected between a stud 30 on the latch 23 and a stud 31 on the coupling pawl 28, normally maintains a surface 32 on the latch 23 against a surface 33 of the coupling pawl 28. Clockwise movement of the latch 23 is limited by a stud 34 thereon, which contacts the upper surface of the differential arm 25.

In the home position of the parts, as shown in Fig. 2, a surface 35 on the coupling pawl 28 overlies the arcuate path of a rod 36, which is common to the coupling pawls of all of the key banks and is carried by a pair of arms 37 (only one of which is shown) loose on the main shaft 26 of the machine.

Referring to Fig. 9, the main shaft 26 has secured thereto a gear 38 meshing with a gear 39 loose on a stud 40 secured to the right side frame 5. Also meshing with the gear 39 is a gear 41 loose on a stud 42 secured to the frame 5. A gear 43 is secured to a shaft 44 for actuating a knOWn tens transfer mechanism for the totalizers, which totalizers will be described later.

Secured to a hand crank 46 is a gear 45, which meshes with the gear 39.

Upon rotation of the hand crank 46, the main shaft 26 will be rotated through one complete clockwise rotation, as seen in Fig. 9. The shaft 26 may also be driven from the usual electric motor in a manner described later through a series of gears which mesh with a gear similar to the gear 38 and fast on the other end of the main shaft 26.

The gear 43 has secured thereto a plate 47, carrying a stud 48, which is adapted to cooperate with the left arm 49 of a lever 50 loose on the stud 42. The upper end of the lever 50 is bifurcated to embrace a stud 51, secured to a lever 52 fast on the right-hand end of the zero stop shaft 18 (see also Figs. 2 and 3).

Near the end of a machine operation, the stud 48 engages the arm 49 of the lever 50, rocking the latter a short distance clockwise, thus tensioning a spring 53, attached to a right arm 54 of the lever 50 and to a stud 55, secured to the frame 5. Upon the clockwise move ment of the lever 50, the lever 52 and consequently the shaft 18 and the fingers 19 are rocked slightly counterclockwise for a purpose to be described later. As the stud 48 is disengaged from the arm 49 of the lever 50, the spring 53 will restore the parts to the position shown in Fig. 9.

The arm 37 (Fig. 2) has pivotally connected thereto, by means of a stud 56, one end of a link 57, the other end of which is connected, through a stud 58, to a beam 59 loosely supported on a shaft 60 extending between the side frames 4 (Figs. 4, 5, and 6) and 5 (Fig. 9). The other end of the beam 59 (Fig. 2) is pivoted to a pitman 61 by a stud 621. The pitman 61 has therein an enlarged opening 62, which embraces a hub 63 on the main shaft 26, thus guiding the pitman 61 in it movements.

The pitman 61 carries two rollers, 64 and 65, which cooperate, respectively, with a pair of companion earns 66 and 67, fast on the shaft 26.

Mounted on the ,shaft 60 is an indicator setting segment 68 having teeth which mesh with a gear 69 secured to an indicator drum 7 0 bearing numerals.

The indicator setting segment 68 has pivoted thereto a link 71 (Figs. 2 and 3) connected by a stud 72 (Fig. 3) to a beam '73 pivoted on a stud 74 on the lower end of the differential arm 25. An inner arcuate surface 75 of the beam 73 is adapted to cooperate with a hub 76 on the differential arm 25.

The lower end of the differential arm 25 is connected by a stud 77 to a link 78 pivotally connected at its other end by a stud 79 to a totalizer setting segment 80 having teeth 82, which can be brought into and out of mesh with an intermediate gear 81, said gear 81 in turn meshing with a gear 160, described later. The segments 88 are mounted in a rockable frame, to be described later.

The forward side of the differential arm 25 carries teeth 84, which mesh with a type setting gear 85, which will be further described later.

A cam 86 (Fig. 3) is fast on the main shaft 26 and cooperates with a roller 87 mounted on an arm 83 fast on a shaft 89 journaled in the side frames 4 (Figs. 4, 5, and 6) and 5 (Fig. 9) of the machine. Also fast on the shaft 89 is another arm 90, carrying a roller 91, which cooperates with a rear surface of the beam 73.

Assuming that an amount key 1 to the value of 7 has been depressed, the operation of the amount differential mechanism is as follows:

Depression of the key 1, as shown in Fig. 3, through the cooperation of its stud 6 with the related cam slot 12 in the slide 9, shifts the latter upwardly, removing the lug 14 (see also Fig. 2) from the path of the surface 15 of the zero stop 16, whereupon a spring (not shown) rocks the zero stop 16 counter-clockwise to remove the stud 21 (Fig. 2) from the path of the finger 22 of the latch 23. The counter-clockwise movement of the zero stop 16 positions a locking surface 92 (Fig. 3) thereon under the lug 14 of the slide 9, thereby preventing return movement of the latter, so as to lock the depressed key 1 in depressed position.

The high portions of the slide 9, between the cam slots 12, are moved beneath the studs 6 on the remaining amount keys 1 to prevent their depression at this time.

When the main shaft 26 rotates counter-clockwise, as above described, the cams 66 and 67 (Fig. 2), cooperating wit-h their related rollers 64 and 65 on the pitman 61, move the latter to the left, as-seen in Fig. 2, rocking the beam 59 clockwise, so that the link 57 rotates the driving arm 37 clockwise.

As the arm 37 rotates clockwise, the rod 36 engages the overlying surface 35 of the couplingpawl 28. Since the coupling pawl 28 and the latch 23 can perform no relative movement at this time, as mentioned previously, the differential arm will be rotated clockwise.

The difl erential arm 25 continues its clockwise moveinent, underthe influence of the driving rod 36, until the finger 22 on the latch 23 strikes the stud 6 on the depressed key 1, as shown in Fig. 3.

Further clockwise movement of the differential arm 25 will now cause the latch 23 to rock counter-clockwise about its pivot 24, tensioning the spring 29, until the surface on the said latch passes beyond the surface 33 on the coupling pawl 28, whereupon the combined pressure of the driving rod 36 and the pull of the spring 29 cause the coupling pawl 28 to rock counterclockwise on its pivot 27 until an abrupt surface 93 (Fig. 2) snaps under an abrupt surface 94 on the latch 23.

The counter-clockwise movement of the latch 23, when it contacts the stud ti or" the depressed key 1, causes the stud 34 (Fig. 3) to engage in a related one of a series of aligning notches 95 in the plate 8 (Figs. 2 and 3). The cooperation of the surfaces 93 (Fig. v2) and 94 causes the latch 23, and therefore the differential arm 25, to be locked in adiustcd position, as shown in Fig.

Counter-clockwise movement of the coupling pawl 28 removes its surface from the path of the driving rod 36, and the latter now continues its clockwise movement until it reaches the position shown in Fig. 3.

If the previous setting was to ahigher value than the current one, the clockwise setting movement of the differential arm 25, until it has been arrested by the depressed key 1, causes the beam 73 (Fig. 3) to rock counter-clockwise on its pivot 74. The cam 86 is so formed that, after the differential arm 25 has been set under control of the depressed key 1, it cooperates with the roller 87 and rocks the arms 88 and 90 counter-clockwise, whereupon the roller 91 engages the rear. side of the beam 73 and moves the latter counter-clockwise on its pivot 74, until the inner surface 75 of the beam 73 strikes against the hub 76 on the differential arm 25. Since the indicator setting segment 68 is coupled to the beam 7.3, it will be set to a position corresponding to the extent of travel of said beam, so as to set the indicator drum 70 through the ear 69.

During the setting movement of the differential arm 25, the teeth 04 on its front edge, cooperating with the gear 85, set the appropriate type wheel.

if the previous setting of the differential arm 25 was to a lower value than the present setting, then, as the differential arm 25 moves clockwise, the beam 73 will pivot clockwise about the hub 76, causing the link 71 to rock the indicator setting segment 63 clockwise, and move the indicator drum '70 to the 7 position. 7

After the differential arm 25, the indicator drum 70, and the type setting gear 85 have been set, as above described, continued clockwise movement of the main shaft 26 permits the arms 88 and 90 to be restored clockwise by a spring (not shown) to their original positions, as the roller 87 follows the contour of the cam 86.

During the said continued movement of the main shaft 26, the earns 66 and 67 (Fig. 2) restore the pitman 61 to the right, to the position shown in this figure, the rod 36 being thereby moved counter-clockwise, so that it contacts the lower part of the surface 35 on the coupling pawl 28, but at this time the latch 23 is still locked against any clockwise movement by reason of its engagement with the stud 6 (Fig. 3). However, the continued movement of the driving rod 36 causesthedifferential arm 25 to commence. its counter-clockwise restoring movement, removing the latch 23 from the restraint of the stud 6. Immediately thereafter, the coupling pawl 28 is rocked clockwise by the pressure of the rod 36 on the lower surface 35, moving the abrupt surface 93 on the coupling. pawl 28 out of engagement with the abrupt surface 94 on the latch 23, and tensioning the spring 29. As soon. as the said abrupt surfaces leave one another, the latch 23, which is now freed from the stud 6,v as just mentioned, is rocked clockwise by the spring29 to the position shown in Fig. 2, whereupon the surface 32 again interlocks with the surface 33 on the coupling pawl 28. Continued counter-clockwise movement of the rod 36 now restores the differential arm 25 to its home position, as shownin'this figure.

During the restoring movement of the differential arm 2S, the beam '73 pivots idly counter-clockwise on the stud 72, leaving the indicator drum 70 in the position to which it has been set.

Near the end of the cycle of machine operation, the

shaft 18 (Fig. 9) is rocked first counter-clockwise and then clockwise, as previously described, by means of the lever 50. Upon the counter-clockwise movement ofthe shaft 13, the finger 19 (Figs. 2. and 3) is similarly moved, rocking the zero stop 16 clockwise back to its home position, removing the surface 92 (Fig. 3) thereon from the path of the lug 14 on the slide 9, releasing the 'latter to the action of the spring 13 (Fig. 2), which restores the slide 9 downwardly to its home position, releasing the depressed key 1, so that it will be restored upwardly by the usual restoring spring (not shown).

As the slide 9 moves downwardly, the lug 14 thereon is positioned in front ofthe surface 15* of the zerostop 16. Upon the clockwise return movement of the finger 19, it is removed from contact with the stud 20 on the Zero stop 16, whereupon the latter is rocked slightly counterclockwise by its spring until the surface 15 on the zero stop 16 contacts the lug 14 on the slide 9 and maintains the said zero pawl in its normal home position, as shown in Fig. 2.

Just prior to the clockwise movement of the driving rod .36, the setting segments are rocked into engagement with the intermediate gears 81, as will be described later, so that, during the clockwise movement of the differential arm 25, the setting of the segment 80 by the link 78 will transmit an amount corresponding to the depressed amount key 1 to the totalizer wheel 83.

If none of the keys 1 has been depressed, the zero stop 16 will remain in the position shown in Fig. 2, so that, when the differential arm 25 commences its clockwise movement, the stud 21 on the zero stop 16 will engage the finger 22 on the latch 23, causing the latter to be rocked counter-clockwise, whereupon the coupling pawl 28 will be disengaged from the driving rod 36, as previously described, the remainder of the machine operation then continuing exactly as described above, to position the indicator drum 70 and the type setting gear at zero, the totalizer wheel 83 remaining in its previously set position, as no movement is transmitted to the. segment 80 through the link 78 at this time.

Machine driving mechanism An armature shaft 97 (Fig. 14) of an electric motor 98 is provided with a worm gear 99, made of insulating material and meshing with a worm gear 100 on a shaft 101 mounted in bearings in the motor frame. The shaft 101 is connected to a shaft 102 by an insulating coupling, and the shaft 102 carries a spur gear 103 in mesh with a crown gear 104 (see also Fig. 15). The shaft 102 is rotatably mounted in bearings 105 and 106 carried .by a bracket 107 supported in the left side frame 4 by screws 108.

The crown gear 104 (Fig. is secured to a ratchet wheel 109, and the assembly, including the gear 104 and the ratchet wheel 109, is rotatably mounted on a stud 110, carried in the frame 4 (Fig. 14). Also mounted on the stud (Fig. 15) is a disc 111, carrying a clutch pawl 112 pivotally mounted on a stud 113.

A spring 114, connected to one end of the clutch pawl 112 and to a stud carried by the disc 111, normally tends to move the clutch pawl 112 into engagement with the ratchet wheel 109. When the machine is at rest, however, a stop arm 115, described later, lies in the path of an upstanding arm 116 of the clutch pawl 112, keeping it away from the ratchet 109, and the arm 116 engages a stud 117 on the disc 111.

When the machine is released for operation, in a manner described hereinafter, the stop arm is raised out of engagement with the arm 116, thus permitting the spring 114 to move the clutch pawl 112 into engagement with the ratchet wheel 109, which at this time is being rotated by the motor 98. When the clutch pawl 112 drops behind a tooth of the ratchet wheel 109, the ratchet wheel 109 carries the pawl, together with the disc 111, counter-clockwise. As the upstanding arm 116 again approaches home position, the arm 115 is again I lowered, in a manner described hereinafter, into its path, thus forcing the upstanding arm 116 against the stud 117, thereby arresting the disc 111 after the main shaft 26 has completed one complete clockwise rotation. Also secured to the disc 111 is a gear 118, meshing with a gear 119, secured to the main shaft 26. Therefore, when the disc 111 is arrested, the gears 118 and 119 and the main shaft 26 are arrested after the latter has made one complete rotation. The ratio between the gears 118 and 119 is l to 1, so that one complete rotation of the gear 118 causes one complete rotation of the gear 119 and the main shaft 26.

Machine release mechanism After the amount has been set upon the amount keys 1 (Figs. 1, 2, and 3), the machine may be released by depression of any one of four release keys. Three of these keys, numbered 120 (Figs. 1, l0, and 13), are clerks keys, which also select a related totalizer for actuation, and the other key, numbered 121, is a total key, which releases the machine for operation and also controls a ticket feeding mechanism in a manner which will be described later.

The keys 120 and 121 are of the insertable type; that is, each key is inserted into a lock cylinder 122 (Fig. 13). Removal of the key from its lock, of course, prevents any unauthorized actuation of the machine for the particular function assigned to that key.

Insertion of a key 120 or 121 into a cylinder 122 and further depression thereof move a stud 123, on the lower end of the key cylinder, into a slot 124 in a seg ment 125, loosely mounted on the shaft 26. The cam slot 124 is so formed that entry of the stud 123 therein rocks the segment 125 clockwise.

The segment 125 is provided with a downwardly extending arm 126 having a stud 127 projecting into the bifurcated end of an arm 128 pinned to a shaft 129 supported between the frames 4 (Figs. 4, 5, 6, 7, and 8) and 5 (Figs. 9 and 13). The bifurcated arm 123 (Fig. 13) is located near the frame 4. Also secured to the shaft 129, adjacent the right frame 5, is an arm 130, which, together with an extension on the arm 128, supports a restoring rod 131. The shaft 129 projects through the right side frame 5, where it supports an arm 132, which is provided with a flange 133 at its upper end. The flange 133 normally lies in the path of a surface 134 of a three-armed lever 135, pivoted on a stud 136 on the right side frame 5. A spring 137 normally maintains the surface 134 in contact with the flange 133. A rearwardly-extending arm 138 of the three-armed lever is bifurcated to engage a stud 139 on an arm 140, secured to a shaft 141. The

before-mentioned stop arm 115 (see also Figs. 14 and 15) is pinned to the shaft 141. Also secured on the shaft 141 is an arm 142 (Figs. 13 and 16) normally engaging a switch operating arm 143 pivoted on a stud 144 carried by a flange on a motor bracket 145. The switch arm 143 is made of an insulating material and is normally in contact with a switch blade 146 carried by a bracket 147 mounted on the motor 98 (Fig. 14). The bracket 147 (Figure 16) also has thereon a switch blade 148, with which the switch blade 146 comes into contact to close the circuit through the motor 98 (Fig. 14).

Through the above-described mechanism, upon depression of a key 120 or 121 (Fig. 13), the segment 125, acting through the arm 128, the shaft 129, and the arm 132, withdraws the flange 133 from beneath the surface 134 to release the three-armed lever 135 to the action of the spring 137, to rock the three-armed lever counterclockwise. Counter-clockwise movement of the three-armed lever 135 rocks the arm and the shaft 141 clockwise, which rocks the arm 142 clockwise (Fig. 13) to lower the switch arm 143 ((Fig. 16) to move the switch blade 146 into contact with the stationary switch blade 148, to start the motor in operation. When the motor operates, the ratchet wheel 109 (Fig. 15) is rotated. When the shaft 141 is rocked clockwise, the arm 115 is rocked therewith to withdraw its left end from the path of the upstanding arm 116 to release the clutch pawl .112 to the action of its spring 114. This causes the clutch pawl 112 to engage a tooth of the ratchet wheel 109, whereupon the ratchet wheel, acting through the pawl 112, rotates the disc 111 and, through the gears 118 and 119, the main shaft 26 clockwise, as hereinbefore stated. Near the end of the machine operation, a stud 149 (Fig. 13), on a gear 150 secured to the main shaft 26, engages a nose 151 on the forward end of the three-armed lever 135 and returns the latter clockwise to its home position. When the three-armed lever 135 is thus restored, the flange 133 is again rocked beneath the surface 134 by a spring 152, one end of which is connected to the rod 131 and the other end of which is connected to a flange 153 on a bracket 154 for supporting the frames 4 and 5. Return movement of the arm 132 and the shaft 129 to their normal positions by the spring 152 restores the segment 125 to its home position. The segment 125, acting through the cam slot 124, restores the depressed key 120 or 121. This restoring movement is assisted by the action of a spring 155, coiled around the lock cylinder 122 of the key.

A means is provided to prevent a second release of the motor before the depressed key 120 or 121 is again released to the action of the spring 155 at the end of the machine operation. This means includes a pawl 156 pivoted on the forward end of the lower arm of the threearmed lever 135. A spring 157 normally maintains the pawl 156 in contact with a stud 158 on an upper extension of the lower arm of the three-armed lever 135. When the pawl 156 is held against the stud 158, a surface 159 thereof lies out of the path of movement: of the flange 133 of the arm 132. When the machine is released for operation by depression of a key 120 or 121 and the flange 133 is rocked from beneath the surface 134, the flange 133 moves beyond the surface 159 of the pawl 156. When the three-armed lever is rocked counter-clockwise by the spring 137, the pawl 156 moves in front of the flange 133. If, at the end of the machine operation, the operator should maintain the key 120 or 121 depressed, the arm 132 is held in moved position, wherein the flange 133 lies in the path of movement of the surface 159. Thereafter, when the three-armed lever is restored clockwise by the stud 149, the surface 159 comes to rest on top of the flange 133 and holds the stop arm 115 in moved position, thus preventing a second release of the motor until after the pressure is taken from the key 120 or 121. When the operator removes the pressure from the key 120 or 121, the segment 125, the arm 128, the

shaft 129, and the arm 132 arerestored. to home, positions to again move the flange. 133 beneath the surface, 134. As the flange 133 moves from beyond the surface 159 of the pawl 156, the three-armed lever 135 is restored into its home position by the spring 137, whereupon the surface 134 comes to rest on top of the flange 133.

In the normal operation of the machine, when the key 120 or 121 is free to be released at the end. of the operation of the machine, the spring 152 restoresthe arm 132 into its home position at the end of the machine operation. During this operation, the pawl 156 performs no function, and the machine comes to rest in the, position shown in Fig. 13, in the manner described above.

Totalizers 841 are mounted on a sleeve 161, which supports the three totalizer wheels 33 for each denomination of the interspersed totalizers.

The totalizer wheels 83 are displayed in a viewing aperture 162 (Fig. 1) and are concealed or exposed by means of a shutter controlled by a control lock, as will be described later.

The totalizer wheels 83 are loosely rotatable on the sleeve 161 and may be selectively coupled thereto by means of coupling members 163, one of whichis provided for each denominational order of the totalizers. The coupling members 163are supported on a shaft 164 within annular grooves 165 therein. The shaft 164' is shifted endwise under control of the" clerks keys 120 (Figs. 1, 10, and 13), as will be described later, so as to shift the coupling members 163 to select the appropriate totalizer wheels 33.

The totalizer wheels 83 are provided with internal teeth 166 (Figs. 11 and 19), and the coupling members 163 are moved into engagementwith the internal teeth by the shifting. movement of the shaft 64, thereby to couple a selected one of the sets of'tota1izerwhee1s 8'3 with the totalizer pinion 160.

The coupling member 163 is shown in Fig, 11- in its home position, in which it is aligned with the No. 1 clerks totalizer wheels 83.

When the coupling members 163 are shifted ,to select theproper totalizer and the machine isoperated with the amount keys 1 (Figs. 1, 2, and 3;) depressed, then, at the commencement of the machine operation, after the setting segments 80 have been engaged with the intermediate wheels 81, as will be described later, whenthe gear 160 receives its diiferential movementcommensurate with the amount key depressed, it will, through the. sleeve 161 and the coupling members 163, rotate the corresponding totalizer wheels 83 to an appropriateextent.

Each gear 160. and sleeve 161 .is mounted for independent rotation between plates 167, supported by the frames 4 (Figs. 4, 5, 6, 7, 8, and 14,) and (Figs; 9 and 13), by means of shafts 168 and 169 (Fig. 11).

The totalizers are equipped with a well-known type of tens transfer mechanism, which will not be described here.

Totalize-r selecting mechanism Each of the keys 120 and 121 (Figs. 1, 10, and 13) has a stud 170, which is adapted to cooperate with a notch 171 (Fig. in a slide 172, slidablyzmounted on the studs 11. A spring 173 (Fig. 10) normally.maintains the slide 172 in its downward position, as'shown in this figure.

Each of the notches 171-associated: with, the three 1'0 clerks keys is formed with a cam face whereby, upon depression of one of said keys, the slide 172 will be shifted upwardly. It wiil be seen, however, that the total key .121 has its notch 171 so shaped that, when this particular key is depressed, the slide 172 will remain in its normal position.

The lower end of the slide 172 has a lug 174, which cooperates with a zero stop 175 in exactly the same manner as the amount key slide 9 (Fig. 3), previously described. V

Associated with the clerks keys is a setting segment 176 (Fig. 10) pivotally mounted. on the main shaft 26 and cooperating with the studs 170 in exactly the same manner as the amount setting arms 25 (Figs. 2 and 3) cooperate with the studs 6 of thedepressed amount keys 1. Therefore a detailed description of the differential mechanism for the clerks key bank is considered to be unnecessary.

The segment 176 has teeth 177 cooperating with a gear wheel 178 to set a printing wheel in a manner similar to the setting of the amount printing wheels which will be described later.

Pivotally connected to the lower end of the setting segment 176 by a stud 179 is a link 1811, pivotally connected at its other end to an arm 181 secured to a shaft 182, to which is also secured a gear 183. The gear 183 meshes with a gear 184 connected to a drum cam 185 by a sleeve 186 mounted ona shaft 187.

The drum cam 185 is provided with a cam race 188 (Fig. 12), into which projects a roller 1S9 carried by a slide 190 engaging over studs 191' carried by a bracket 192 supported by the frame 4. The slide 1% is provided with a notch into which projects an end of a plate 193 (Fig. 10), having a bifurcation 194 engaging the annular groove 165 (Fig. 11) in the left end of the shaft 164.

From the foregoing it will be seen that, when the setting segment 176' (Fig. 10') is positioned under control of the depressed clerks key 120, the gear 183 cooperates with the gear 184 to rotate the cam drum 1.85 to shift the'slide 190 endwise. The endwise shifting of the slide 190, through the plate 193 engaging the annular groove 165 (Fig. 11) in the shaft 164, shifts the latter endwise to position the coupling members 163 so as to engage the inner teeth 166 of totalizer wheels 83 corresponding to the key 120 which has been depressed.

To prevent the totali-zer wheels 83 which are not selected for operation from being accidentally rotated during the machine operation, a locking shaft 1194 (Figs. 11 and 19) is provided and engages between the teeth of reset gears, which will be later described and which mesh constantly with the totalizer wheels 83. The shaft 1194 has appropriate notches to permit rotation of selected reset gears and is connected to the shifting plate 193, so that, when the drum cam 1S5 (Figs. 10 and 12) shifts the plate 193 to move the coupling members 163 (Fig. 11) for selecting a totalizer for operation, the shaft 1194 (Figs. 11 and 19) is also shifted properly to position the notches opposite the reset gears for the selected totalizer wheels 83.

Engagement of amount setting segments Immediately prior to the clockwise movement of the amount differential arms 25 (Figs. 2 and '3) under control of the driving rod 36, the setting segments 80 are engaged with the intermediate gears 81, so that the amount set up on :the amount keys 1 may be transmitted to the totalizer gears 1.60 and the totalizer wheels 83. The mechanism for engaging the segments 31) with, and disengaging them from, theinterrnediate gears 31 will now be described.

Alltof the amount setting segments 80 are loosely mounted on a rod- 195 (Fig. .17). in proper spaced-relationship. The rod 195 is supported by a plurality of arms 196 (only one shown) loose on a shaft 197 jour- 11 naled in the side frames 4 (Figs. 4, 5, 6, 7, 8, and 14) and (Figs. 9 and 13).

The arms 196 (Fig. 17) are held in rigid relation to each other by the rod 195, and the entire assembly forms a rockable frame adapted to rock the teeth 82 (see also Fig. 3) of the segments 80 into engagement with the teeth of the corresponding intermediate gears 81 (Figs. 2 and 3).

Each mm 196 (Fig. 17) carries a pair of rollers 198 and 199 adapted to cooperate with respective plate cams 200 and 201 fast on the main shaft 26. Initial movement of the shaft 26 in a clockwise direction causes the cams 200 and 201, in cooperation with the rollers 198 and 199, to rock the framework composed of the arms 196 counter-clockwise to engage the teeth 82 of the segments 80 with the teeth of the intermediate gears 81.

After the teeth 82 have been engaged with the teeth of the intermediate gears 81, the cams 66 and 67 (Fig. 2) actuate the pitman 61 to cause the arms 37 and the driving rod 36 to drive the differential setting arms 25 to their set positions as determined by depressed amount keys 1 or the zero stops 16. Consequently, at this time, the setting segments 80 transmit the setting of the differential arms 25 to the totalizer wheels 83.

Prior to the return movement in a counter-clockwise direction of the differential arms 25, the cams 200 and 201 (Fig. 17) rock the arms 196 clockwise to disengage the teeth 82 of the segments 80 from the associated intermediate gears 81.

Type wheel setting The lowest order type setting gear 85 (Figs. 2 and 3) is secured on a shaft 202 (see also Figs. 4, 5, and 7), journaled in the side frames 4 (Figs. 4, 5, 6, 7, 8, and 14) and 5 (Figs. 9 and 13). A corresponding type wheel drive gear 203 (Figs. 4 and 7) is also secured on the shaft 202, while the higher order drive gears 85 (Figs. 2 and 3) are connected by corresponding nested tubes 204 (Figs. 4 and 5), supported by the shaft 202, to their corresponding type wheel drive gears 203 (Figs. 4 and 7). The type wheel drive gears 203 mesh with corresponding amount type wheels 205 of the upper or receipt type wheel line and with the corresponding amount type wheels of: a lower or detail strip type wheel line, not described herein. The receipt type wheels 205 are rotatably mounted on a stud 206 (Fig. 7) secured to the frame 4.

It is therefore obvious from the foregoing description that the positioning of the amount differential arms 25 (Figs. 2 and 3) also correspondingly positions the corresponding type wheels 205.

The extreme left-hand drive gear 203 (Fig. 4) is connected to the drive gear 178 (Fig. for the clerk's key bank, and thereby sets a type Wheel 207 (Fig. 4) for printing a numeral or a letter identifying the particular key 120 (Figs. 10 and 13) depressed. The setting of the clerks drive gear 203 (Fig. 4) under control of the total key 121 (Figs. 10 and 13) will set the type wheel 207 (Fig. 4) so as to print the letter T to identify a total. A so-callcd total operation, which is actually an amount entering operation, will be referred to more fully later.

Consecutive number drive gears 208 (Figs. 4 and 5) set corresponding consecutive number type Wheels 209. The lowest order drive gear 208 is advanced one step at each machine operation in well-known manner.

Control lock The machine of the present invention is provided with a control lock 210 (Fig. 13), which controls the operations of the machine; that is, the operations of disabling the concealing shutter for the totalizer Wheels and locking the machine. The lock has three positions of adjustment. When the key in the lock is in an intermediate, or normal, position, shown in Fig. 13, the machine can be operated for entering items. When the lock is turned ninety degrees clockwise from the intermediate position, the shutter is disabled, and the totalizers can be reset to zero. When the lock is turned counter-clockwise ninety degrees from the intermediate position, shown in Fig. 13, to the position shown in Fig. 18, the machine is locked against any operation.

The control lock 210 is mounted in a bracket 211 on the right side frame 5. An insertible key 212 controls the various machine functions described above. When the key 212 is in its horizontal position, as shown in Fig. 13, the machine can be operated for item-entering operations. When the key 212 is turned counter-clockwise to the position shown in Fig. 18, the following mechanisms are operated:

Counter-clockwise rotation of the lock by the key 212 moves a pin 213 thereon into the position shown in full lines in Fig. 18. The pin 213 projects into a slot 214 of a lever 215 pivoted on a stud 216 carried by the right side frame 5 (Figs. 9 and 13). Counter-clockwise rotation of the lock 210 (Fig. 13) into the position shown in Fig. 18 moves the lever 215 (Fig. 18) from the dottedline position into the full-line position shown in this figure. When the lever 215 is moved into its full-line position, a stud 217 thereon comes into engagement with a shoulder 218 on the three-armed lever 135, thus preventing any releasing movement thereof. Therefore, when a machine release key or 121 (Fig. 13) is depressed to withdraw the flange 133 from the surface 134 of the three-armed lever 135, the lever is arrested against movement, therefore preventing release of the machine. When the operator removes his finger from the key 120 or 121, with the machine in the above-described locked condition, the depressed key is not latched in de pressed position, and therefore the spring immediately restores the depressed key into its undepressed position.

The pin 213 on the lock 210 also projects into a slot 219 (Fig. 18) of a bell crank 220 pivoted on a stud 221, carried by the right frame 5. The downwardly-extending arm of the bell crank 220 has pivoted thereon a link 222, the other end of which is pivoted to a pin 223 on a cam 224, later to be described, loose on the shaft 44. Also pivoted to the pin 223 is a link 225, pivoted at its other end to a cam plate 226 loose on a shaft 227 supported by the totalizer plates 167 (see also Fig. 11). The cam plate 226 (Fig. 18) cooperates with a stud 228 on one of a pair of arms 229 (only one shown) of a totalizerobscuring shutter 230, freely mounted on the shaft 164 supporting the totalizer wheels 83. A spring 231 normally maintains the stud 228 in the position against the plate 226 shown in this figure.

When the key 212 (Fig. 13) is turned clockwise from the intermediate position, the plate 226 (Fig. 18) moves clockwise, cooperating with the stud 228 to permit the spring 231 to rock the arms 229 and the shutter 230 counter-clockwise, so that the totalizer wheels 83 arc visible through the aperture 162 (Fig. 1). When the key 212 (Fig. 13) is returned counter-clockwise to its intermediate position, the plate 226, engaging stud 228, (Fig. 18) rocks the arms 229 clockwise, so that the shutter 230 again obscures the totalizer wheels 83.

Resetting the totalizers As already stated, the setting segments 80 (Figs. 2 and 3) are engaged with the intermediate gears 81 immediately prior to the clockwise movement of the ditferen tial. setting arms 25.

In the present machine, the engaging and disengaging movements of the setting segments 80 remain the same for totalizer resetting operations as for adding operations. During resetting operations, the zero stops 16 remain ef fective, since no amount keys are depressed, and therefore the differential arms 25 remain in their zero positions at this time. Thus, the said engaging movement of the setting segments 80 is merely an idle one, and the type wheels 205 (Fig. 4) remain in zero positions. By means of a manual control lever, to be described later, a ticket printing mechanism can be disabled and therefore no print will be made from the said type wheels on a ticket during the resetting operation.

As will be described later a print of the three totals can be obtained by entering the totals on the three totalizers through the machine keyboard.

There is a simple automatic resetting mechanism for the. totalizers which operates independently of the engaging and disengaging movements of the setting segments 8%) (Figs. Z and 3) and which becomes effective after the disengaging movement has taken place.

This automatic totalizer resetting mechanism will now be described.

A reset shaft 232 (Figs. 11, 1'8, and 19) is connected to the plate 193 (Fig. 10) and is slidably supported in the totalizer plates 167 (Fig. 11), so as to shift laterally with the plate 193, for the selection of the totalizers to be reset.

The shaft 232 is provided with a notch 233 (Figs. 11 and 19) for each denominational order of the totalizer wheels 83, and the notches are in alignment with the coupling members 163 on the shaft 164. When the shaft 164 is shifted endwise under control of the depressed clerks selecting keyslZl) (Figs. 1, 10, and 13) to select a totalizer with which the coupling member 163 is to engage, the notches 233 are moved into the path of reset pawls 234 pivotally mounted within the hollow portions of reset gears 235 freely mounted on the shaft 232 and each meshing with a related one of the totalizer wheels 83, as can be clearly seen in Fig. 19. Springs 236, mounted on studs 237 within the hollow portions of the gears 235, engage the pawls 234 and normally tend to hold them in engagement with the notches 233.

The shaft 1194 (Figs. 11 and 19) has notches 238, which are aligned opposite selected reset gears 235 and permit their rotation. All unselected gears 235 are held against rotation by full portions of the shaft 1194, as can be seen from Fig. 11.

As amounts are entered into the totalizer wheels 83, the corresponding reset gears 235 are rotated counterclockwise. When a totalizer wheel 83 is moved out of zero position, the reset pawl 234, moving with the reset gear 235, is moved out of engagement with the notch 233 a distance corresponding to the value set on the totalizer wheel 83.

The reset shaft 232 is rotated to reset the selected set of totalizer wheels, during a machine operation initiated by depression of the appropriate clerks key 120 (Figs. 1, 10, and 13), in which the shafts 164 and 232 have been shifted axially to the appropriate positions, by means of the following mechanism.

Constantly meshing with a gear 239 (Fig. 11) keyed to the shaft 232 is a gear 240 free on a stud 241 secured to the extreme right-hand totalizer, plate 167. Integral with the gear 240 is a smaller gear 232 (Figs. 11, 20, and 21), to the right side of which is secured a cam 243, located With 11S nose lying in approximately the center of a non-toothed portion of the gear 242.

Fast on the shaft 44 (Figs. 9, 11, 20, and 21) is a partially-toothed gear 244 (Figs. 11, 20, and 21), which receives one complete counter-clockwise rotation, as seen in Figs. 20 and 21, at each machine operation.

The cam 224 (Figs. 11, 18, 20, and 21) is loosely mounted on the shaft 44 to the left of the gear 244 and is held in position by a spacing collar 245 (Fig. 11), fixedly mounted on the shaft 44.

Pivotally mounted on a stud 246 (Figs. 20 and 21) on the right side of the gear 244 is a pawl 2 17 (Figs. 11, 20, and 21), carrying a roller 248, which projects through an enlarged aperture 249, (Figs. 20 and 21) in the gear 244. The roller 248 is held in engagement with a sur- 14 face of the cam 224 by means of a spring 250, secured to the pawl 247 and to a stud 251 on the gear 244.

A nose 252 of the pawl 247 and the nose of the cam 243 lie in the same rotational planes.

When the key 212 (Fig. 13,) is in its normal position, as shown in this figure, 'the cam 224 assumes the position shown in Figs. 18 and 21. Now, upon counter-clockwise rotation of the shaft 44 (Figs. 9, 20, and 21), and similar rotation of the gear 244, the roller 248, riding on the surface of the cam 224, will cause the pawl 247, after about 180 degrees of rotation of the shaft 44, to be rocked counter-clockwise onthe pivot stud 246 until its nose 252 assumes the position shown in Fig. 20, wherein it is beneath the nose of the cam 243. Consequently, as the gear 244 continues its counter-clockwise movement, the nose 252 passes freely under the nose of the cam 243, permitting the gear 242 to remain in the position shown in Fig. 20, in which the teeth of the gear 244 pass along the gap in the teeth of the gear 242 without imparting any rotation to the latter. Therefore, during adding operations, the reset shaft 232 is not rotated.

However, when the key 212 (Fig. 13) is turned clockwise to the reset position, the lever 220 (Fig. 18) is rocked counter-clockwise, whereupon the link 22 rotates the cam 224 slightly clockwise, bringing it to the position shown in Fig. 20.

Now, after about 180 degrees of rotation of the gear 244, the roller 248, following the contour of the cam 224, causes the pawl 247 to be so positioned that its nose 252 lies in the plane of the nose of the cam 243, as shown in Fig. 21.

Upon the continued counter-clockwise rotation of the gear 244, the nose 252 of the pawl 247 will, through its cooperation with the nose of the cam 243, rotate the gear 242 slightly clockwise, bringing its teeth into the path of the teeth of the gear 244, which now imparts one complete clockwise revolution during the machine operation.

Since the gear 240 constantly meshes with the gear 239 (Fig. 11), keyed on the reset shaft 232, the latter, which has been shifted so that the notches 233 cooperate with the appropriate reset pawls 234 (Fig. 19), will be rotated through one complete counter-clockwise revolution, the noses of the pawls 234, by their engagement with the notches 233, rotating the related reset gears 2335 (Figs. 11 and 19) to zero positions, and thereby correspondingly rotating the related totalizer Wheels 83 also to the zero positions.

By the successive depression of each of the clerks keys (Figs. 1, 10, and 13) and operation of the machine with the control lock key 212 (Fig. 13) in the extreme clockwise position, each of the clerks totalizers 83 will be reset tozero, ready for a new series of adding operations.

When the control lock 21% (Fig. 13) is restored counter-clockwise to its normal, or amount-entering, position, the link 222 (Fig. 18) will rock the cam 224 slightly counter-clockwise until it reaches its normal position again, as shown in this figure.

During the next adding operation of the machine, the pawl 247 will be rocked counter-clockwise by the cam 224, so "that its nose 252 will occupy the position shown in Fig. 20, as the gear 244 rotates counter-clockwise, in which it passes below the nose of the earn 243, and consequently neither the gear 240, nor the gear 239, nor

the reset shaft 232 will be rotated at this time.

Ticket printing and feeding mechanism The mechanism by means of which a ticket strip will be printed and given a line'space at each machine operation controlled by depression of a clerks key will now be described.

The ticket strip 253 (Fig. 7) is fed from a supply roll (not shown), between a cylindrical platen 254 (Figs. 7 and 8) and an electro roller 255 (Figs. 6, 7, and 8),

thence between a platen 256 (Fig. 7) and the type wheels 205, and finally between upper and lower rollers, described later, and out of the machine through a ticket chute 257 (Figs. 1, 5, and 7), where the issued portion of the ticket can be torn off against a stationary serrated knife edge 258 (Fig. A usual ink ribbon (not shown) islocated between the type wheels 205 (Fig. 7) and the platen 256.

A printing hammer 259 (Figs. 4, 5, and 7) is notched to receive the forward end of an arm 26!]: (Figs. 4, 5, 7, and 8), which is pivoted to the hammer 259, and is pivoted on a stud 261, carried by the left frame 4.

The arm 260 has a stud 262 (Figs. 5 and 7), which is embraced by the bifurcated end of a slide 263 (Figs. 5 and 8), the other end of which is bifurcated also and is guided in an annular slot in a sleeve 264 (Figs. 5 and 7), surrounding the stud 261. As can be seen from Fig. 8, the upper arm of the bifurcation is longer than the lower arm. A stud 265 (Figs. 7 and 8) on the slide 263 is embraced by the bifurcated end of an arm 266 (Fig. 8) fast on a sleeve 267 surrounding a stud 268 (Figs. 4, 5, 6, 7, and 8), secured to the left side frame 4.

Also received within the bifurcation in the forward end of the slide 263 is a stud 269 (Figs. 5, 7, and 8), secured in a hammer-actuating lever 270, pivoted on the stud 261. Secured to the other end of the sleeve 267 is a manually-operable on and o lever 271 (Figs. 1 and 8). The lever 270 (Figs. 5, 7, and 8) is urged counter-clockwise, as seen in Figs. 7 and 8, by a spring (not shown), so that a roller 272 thereon cooperates with the surface of a cam 273, secured on the main cam shaft 26 (Figs. 6, 7, and 8).

As the main cam shaft 26 rotates counter-clockwise, as seen in Figs. 7 and 8, the cam 273, cooperating with the roller 272, rocks the lever 270 clockwise. If the slide 263 has both arms of the forward bifurcation embracing the stud 269 on the lever 270 at this time, the hammer-actuating arm 260 will be rocked clockwise, so that the platen 256 takes an impression from the type wheels 265. if, however, the manual lever 2'71 (Figs. 1 and 8) has been moved forwardly to off position prior to a machine operation, the arm 266 (Fig. 8), cooperating with the stud 265, will have moved the slide 263 rearwardly, so that the lower short arm of the forward .bifurcation in said slide is out of the path of downward movement of the stud 269 on the lever 270. Thus the lever 270 will make its clockwise movement independently of the slide 263, and the hammer 259 will not be actuated at this time.

When the manual lever 271 is in its rear or on position, the lever 270, when returned by its spring, will, through the cooperation of the stud 269 with the slide 263, also return the hammer 259 upwardly to normal position.

In a total operation, after the ticket strip 253 (Fig. 7) has been printed upon by the platen 256, it is fed forwardly into the chute 257 (Figs. 1, 5, and 7), and, while it is being fed, the electro roller 255 prints various data or other information of a descriptive or advertising nature on the face of the succeeding receipt.

The feeding mechanism for the ticket will now be described.

Secured to the cam 273 (Fig. 7) is a partial gear 274, the teeth of which cooperate with the teeth of a gear 275 (Figs. 6, 7, and 22) loose on a stud 276 supporting the electro roller 255. The gear 275 meshes with a gear 277 (Fig. 7) loose on the stud 206. The gear 277 meshes with a gear 278 secured to a feeding roller 279 rotatably mounted on a shaft 280 secured between the left side frame 4 and a printer side frame (not shown).

A pressure roller 281 (Figs. 4, 7, and 8) is rotatably mounted on a plate 282 pivoted on a stud 283 (Fig. 8) secured in the left side frame 4. A link 284 (Figs. 4, 5, 6, 7, and 8) is pivotally connected at one end to the plate 282. The link 284 is mounted, near its other end,

16 by means of an elongated slot, on a stud 285 (Figs. 6, 7, and 8) secured in the upper end of an upwardly-extending arm 286 (Figs. 7 and 8) of a yoke 287 pivoted on a shaft 288 rotatably supported in the left side frame 4.

A spring 289 is anchored between a stud 290 on the rear end of the link 284 and the stud 285. The flexible coupling constituted by the elongated slot in the link 284 and the spring 289 enables the pressure roller 281 to accommodate itself to any uneven thicknesses in the ticket strip 253 (Fig. 7), so as to maintain a proper feed of the strip.

A forwardly-extending arm 291 (Figs. 7 and 8) of a yoke (Fig. 5) fast on the shaft 288 and bearing against a cross piece of the yoke 287 under the influence of a fiat spring 292 (Figs. 5 and 6) has thereon a stud 293, which cooperates with either one of a pair of cam notches cut in the lower end of the manual on and off lever 271. (Figs. 1 and 8). A spring (not shown), anchored between the lower end of the lever 271 and the forward end of the yoke 287, normally maintains said yoke in an upward position in which the electro pressure roller 254 (Figs. 7 and 8) is held well away from the electro roller 255, and the pressure roller 281 is disengaged from the feed roller 279. Said electro pressure roller is rotatably mounted on a short shaft 294 supported between the arms of the yoke 287.

When the manual on and off lever 271. (Fig. 8) is moved rearwardly to the on position, one of the cam notches in its lower edge, through the cooperation with the stud 293, will cause the arm 291, and thereby the yoke 287, to be rocked clockwise until the pressure roller 254 is brought nearer to the electro roller 255, so as to be subsequently brought into cooperative relationship therewith for printing during the line-spacing movement of the ticket strip 253 (Fig. 7), as will be explained later.

As the type faces on the electro roller 255 cooperate with the electro pressure roller 254, the arm 291 will pivot slightly counter-clockwise about the shaft 288, so as to prevent the rollers 254 and 255 from binding together.

When the manual on and off lever 271 (Fig. 8) is moved forwardly to the off position, the other cam notch in its lower edge, through its cooperation with the stud 293, will permit the arm 291 and the yoke 287 to be rocked counter-clockwise with the shaft 288, under the influence of the spring secured between the arm 291 and the lever 271, until the shaft 294 (see Fig. 22) is out of the range of a hook 300 on a lever 297. This counter-clockwise movement of the yoke 287 will, through the link 284, rock the plate 282 counter-clockwise to remove the pressure roller 281 from engagement with the feed roller 279.

Thus, during any machine operations, except a total operation, in which the lever 271 is in the off position, no feed will be imparted at all to the ticket strip 253.

Single line feed of ticket strip Secured to the inner face of the mutilated gear 274 (Figs. 7 and 22) is a stud 295, which, shortly after the commencement of the counter-clockwise rotation of said gear 274, contacts a depending arm 296 of the threearmed lever 297 loosely mounted on the stud 276, rocking said lever a short distance clockwise, whereby, through a central arm 298 and a stud 299, a ribbon feeding pawl (not shown) is actuated to feed the printing ribbon one step in the usual manner.

The upwardly-extending arm 300 of the lever 297 is formed as a hook and, upon clockwise movement of the lever 297, engages over the inner end of the shaft 294, carried by the yoke 287 and supporting the electro pressure roller 254, thereby rocking the yoke 287 clockwise to bring the electro pressure roller 254, when the lever 271 (Fig. 8) is in its on" position, into cooperative relationship with the electro roller 255, and also to engage the pressure roller 281 .with the. feed roller 279 through.

theaction of the link 284, for a short timelsufficient to feed the receipt by onev line space.

The teeth on the mutilated gear 274 are so arrangedv that the ticket strip 253 is fed by the feed roller 279 just prior to an actuation of the printing hammer 259,

in the manner previously described, to print the amount.

and other data.

After the printing hammer 259 has beenreturned,

beyond the lower arm 296 of the lever 297, the latter will be returned counter-clockwise by the spring 289 (Fig. 7), removing the electro pressure roller 254 from engagement with the electro roller 255 and disengaging the pressure roller 281 (Fig. 8) from the feed roller 279. Thus the ticket strip 253 will not be advanced during this further clockwise rotation of the electro roller 25.5, and the type faces on the periphery of the latter will merely wipe idly past the under surface of the ticket strip.

Therefore it will be seen that, for all operations of the machine under the control of the clerks keys .120 (Figs. 1, 10, and 13), with the manual on and off lever 271 (Figs. 1 and 8) in its on position, the ticket strip 253 (Fig. 7) will be fed by a single line space just before each printing stroke of the hammer 259.

Multiple line space of the ticket strip.

The means by which the ticket strip 253 .(Fig. 7) receives a multiple line space during a machine operation initiated bydepression of the Total key 121 (Figs. 1, 10, and 13) will now be described.

, The lower end of the lock cylinder 122 (Fig. 8) of the key 121 (Figs. 1, l0, and '13) has a circular dependency 301 (Figs. 8 and 10), which is adapted to cooperate with a lug 302 (Figs. 4, 6, 8, and 23) on a lever 303, loosely mounted on the right-hand end of the shaft 288. The lever 303 carries a lug 304, and spaced therefrom is a member 305 secured to the shaft 288. A spring 306 normally maintains the lever 303 .in a position in which a lower face of the lug 304 is spaced slightly apart from a lower face of the member 305, thus permitting the shaft 288 to make its clockwise and counter-clockwise movements for causing the respective engaging and disengaging movements of the electro pressure roller 254 and the roller 281 without disturbing the position of the lever 303.

Upon depression of the Total key 121 (Figs. 1, 10, and 13), however, with the manual lever 271 (Figs. 1 and 8) in the on position, the dependency 301 (Fig. 8) contacts the lug 302 on the lever 303, rocking the lat ter clockwise as seen in Fig. 8 and counter-clockwise as seen in Fig. 23, whereby a roller 307 (Figs. 6, 8, and t 23) on the lever 303 enters an aperture 308 (Figs. 8 and 23) in a box cam 309 fast on the shaft 26. At this time, the lower face of the lug 304 will lie against the lower face of the member 305.

As soon as the shaft 26 commences to rotate, a face 310 (Fig. 23) of the cam 309, cooperating with the roller.

307, will rock the lever 303 farther clockwise, as seen in Fig. 8, and counterclockwise as seen in Fig; 23, causing the lug 304 and the member 305, by their mutual engagement, to rock the shaft 288 and the arm 291 clockwise, bringing the electropressure roller 254 (Fig. 8) into cooperative relationship with the electro roller 255,-and the pressure roller'281 into engagement with the feed roller I 279 for a longer period of time than in item-entering operations. Now, upon the first short clockwise'rotation of the feed roller 279, the ticketstrip 253 will be advanced by several line spaces priorto the actuation of the printing hammer 259 (Fig. 7), since the roller 307 is still trapped in the box cam 309. Since the shaft 294 has already been moved downwardly, the cooperation of the stud 2'95 (Figs. 7 and 22). with the lower arm 296 of the lever 297 will merely cause an idle clockwise rotation of the latter until its hooked arm 300 abuts against the moved shaft 294.

The shape of the face 310 (Fig. 23) of the box cam 309 is such that the lever 383 will be held in its moved position until after the feed roller 279 (Fig. 8)'has fed the ticket strip farther so as to feed the ticket out of the machine, the electro roller 255 printing on the next ticket during this final feed.

After the feed roller 279 has imparted the final feed to the ticket strip 253 (Fig. 7), the roller 307 (Figs. 8 and 23), under the urgency of the tensioned spring. 306, escapes through the aperture 308 in the box cam 309 and the lever 303 returns counter-clockwise as seen in Fig. 8. vThis frees the member 305 so that the yoke 287 (Fig. 8) can be restored counter-clockwise by its spring, removing the electro pressure roller 254 from engagementwith the electro roller 255, and removing the pressure roller. 281 from engagement with the feed .roller 279, ready for the next machine operation.

Exemplary uses of the invention pressed in order that the ticket may be fed right out of the machine. U

As will be seen, the Total key 121 causes the symbol T to beprinted.

In the ticket shown, the amount of 2/4d. has again been set up and printed with the Total key. 121 depressed. However, it is not necessary to set up the amount again atthis time, and the machine would then print 0.0 against the symbol T. 1

Fig. 25 shows a ticket for a multiple-item sale and its total.

The No. 3 clerks key (Figs. 1, l0, and ,13) is depressed for the registration of each of the four individual items, the ticket being line-spaced before the print of each item, as described hereinbefore.

Since the particular machine used as an example is not equipped with an itemizing totalizer, it'would be necessary for the clerk, after entering the four items, to compute the total of 5/ 8d. mentally, setting it up on the amount keys and then depressing the Total key 1215 By the depression of this key, as can be seen from Fig. 25, the total, 5/ 8d., is spaced apart from the items, so as to be easily distinguishable. 7

Although the total has been computed mentally, the fact that it has been printed on the ticket would enable any disputes as to how much was actually paid by the customer to be settled easily, and in addition, of course,

i the printed figure of the total is available if it is necessa obtain a daily, or other periodic, printed record of the amounts on the three individual clerks totalizers.

in this case, he turns the control key 212 (Fig. 13) clockwise to total reset position, thus causingthe shutter .230 (Fig. 18) tobe moved away from the t-otalizer wheels 83. Assuming that the amount of 5.l4.11d. is standing on the totalizer for clerk No. l, the machine is first operated with only the No. 1 clerks key depressed. This.

will cause the clerks number-i. e., l-to be printed on the ticket, together with. 0.0. This identifies the

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