US1849494A

US1849494A - Variable platen feed mechanism

Info

Publication number: US1849494A
Application number: US122925A
Authority: US
Inventors: Last James
Original assignee: Remington Rand Inc
Current assignee: Remington Rand Inc
Priority date: 1926-07-16
Filing date: 1926-07-16
Publication date: 1932-03-15
Anticipated expiration: 1949-03-15

Description

March l5, 1932. LAST 1,849,494

VARIABLE PLATEN FEED MECHANISM Filed July 16, 1926 6 Sheets-Sheet 2 March 15, 1932. J. LAST 1,849,494

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attenua! Patented Mar. 15, 1932 l UNITED STATES PATENT OFFICE IAMES LAST, 0F KINGSTON, PENNSYLVANIA, A SSIGNOR, BY MESNE ASSIGNMENTS, T0 REMINGTON RAN D INC., 0F NEW YORK, N. Y., A CORPORATION OF DELAWARE VARIABLE PLATEN FEED MECHANISM Application led July 16,

The present invention relates to a paper feed mechanism and more particularly to a variable feed for the platen of such a mechanism.

Some of the objects of the present invention are to provide an improved mechanism for controlling the line spacing of printing and recording mechanisms, such as employed with adding, calculating, tabulating and other machines wherein paper feed takes place for the proper listing of items and totals; to provide a feeding mechanism for a platen whereby periodic changes in the line spacing automatically take place; to provide means for varying the line spacin of a platen at will; to provide a paper ceding mechanism actuated by the release of prestored energy while the degree of feed is determined by the automatic interposition of appropriate stops; to provide an automatic control for line spacing whereby a feed of any selected number of minimum line-spaces takes place between successive printing or recording strokes, such number of selected line-spaces being less than that selected for alternate total strokes; to provide an automatic control for line spacing whereby after the lirst and alternately occurring total strokes a feed of any selected number of line spaces takes place, such number being less than that selected for the other alternate total strokes; to provide an automatic control for line spacing whereby the feed for total strokes, alternating Cwith those last above referred to, have any selected number of line-spaces within the capacity of the apparatus; and to provide other improvements as will hereinafter appear.

In the accompanying drawings, Fig. 1 represents a side elevation, with the left hand pivot plate removed, of one form of the present invention as applied to the platen drive of a tabulating machine; Fig. 2 represents a sectional elevation on line 2-2 of F ig. 1; Fig. 3 represents a part sectional v plan .with the rim cover removed; Fig. 4

represents a section on line 4-4 of Fig. 2; Fig. 5 represents a section on line 5-5 of Fig. 2; Fig. 6 represents a section on line 6 6 of Fig. 2; Fig. 7 represents a section 1926. Serial No. 122,925.

on line 7-7 of Fig. 2; Fig. 8 represents a section on line 8-8 of Fig. 2; and Fig. 9 represents a section on line 9-9 of Fig. 2.

Referring to the drawings, one form of the present invention is shown as applied to the control of line spacing of aplaten 10, (Fig. 2), of a tabulating machine, the platen 10 being mounted upon a platen spindle 11, which latter is controlled in its rotary movement by the mechanism of the present invention.

For actuating the spindle 11, it is provided with a ratchet wheel 12-7 (Figs. 2 and 4), and two

control ratchet wheels

13 and 14, all of said ratchet wheels being keyed or otherwise made fast to the spindle 11. The wheels 12- and 13 are shown pinned together in Figure 2. Motion is transmitted to the ratchet wheel 12 by a pawl 15 mounted upon an arm secured to a side of a pinion 16 which is freely rotatable about the spindle 11 and meshes with a drive gear sector 17, (Figs. 1 and 2), mounted for rocking movement about a pivot 18 supported by the frame or other fixed part. The gear sector 17 is arranged to be rocked on its working stroke by the load of a spring 19 stretched between a xed pin 20 and a pin 21 which is fast to and projects from the side of the sector 17, While the non-working stroke of the gear sector 17 takes place by the engagement of one arm 22 of a bell crank 23 with the pin 21. The bell crank 23 is, preferably, pivoted upon the pivot 18 and has its other arm in the path of movement of a pin 24 projecting from an arm 25 of a bell crank 26 which is keyed or ot-herwise made fast to the main shaft 27 of the machine. The other arm 28 of the bell crank 26 is arranged to transmit motion to certain parts to carry out steps in the cycle of operations as will hereinafter be explained in detail. Since the ratchet wheel 13 serves to locate the stopping position of the ratchet wheel 12, its teeth are arranged opposite with respect to the teeth of the ratchet wheel 12, (Figs. 4, 5 and 6), and a check pawl 3() is pivotally mounted `upon a rod 31 in the plane of the Wheel 13 and with which it is held in engagement by the load of a spring 32, (Fig. y5). .When the ratchet wheel 12 is being operated by the gear sector 17 on the paper feed stroke because of the load of the spring 19, the check pawl 30 is held out of the teeth of the control ratchet wheel 13 but is automatically released so that the platen spindle comes to rest at the end of the predetermined line space or spaces.

. For controlling and varying the travel of the platen spindle 11, a. drum 33, (Figs. 2,6, 7, 8 and 9), is co-axially arranged about the platen spindle 11 being rotatably supported at one end upon a boss 34, (Fig. 2), of a head 35, which is fixed to the frame, and at the other end being connected to a boss 36, which is freely rotatable upon the spindle 11 and carries an arm 37. The drum 33 carries, as parts adjustably connected to it, three cam rings 40, 41 and 42, (Figs. 2, 7, 8 and 9), all of these parts being frictionally clamped together by means of a nut 44 which 1s threaded upon one end of the drum 33. .The opposite end of the drum 33 is also provided with an arm 45, (Figs. 2 and 6), projected radially therefrom and serving a purpose to be presently described. A torsion spring 46 is located within the drum 33 having one end secured to the fixed boss 34 and its opposite end connected to the drum 33, while suitably spaced from this spring 46 is a second torsion spring 47, preferably of lighter construction, one end of which is fast to the boss 34 and the opposite end of which is fast to the boss 36 of the movable arm 37. Considering rst the control of the ratchet wheel 13 for line spacing without regard to total operations, such control takes place through the rotation of the ring 40 and its cam notch 48, (Fig 7). 1n conjunction with the ratchet wheel 43 and the parts controlled thereby. The release of the drum 33 to the action of the torsion spring 46 is effected by a setting pawl 50, (Fig. 6), secured to a short shaft 51 pivotedin the arm 37, and meshing with the control ratchet wheel 14 while its nose 52 is in position to be engaged by a latch 53 pivoted to the arm 45 and held pressed toward the setting pawl by a coil spring 54 stretched between a pin on the latch 53 and an arm keyed to the short shaft 51. The spring 54 urges the setting pawl to rock into the position shown. As long as the nose 52 engages the control ratchet wheel 14, there is no movement of the drum 33, so in order to release the setting pawl 50 for such movement, it is provided with an integral tail piece 55 having a lug 56 which is in the path of movement of a trip finger 57. This finger 57 is pivoted to one arm of a three arm bell crank 58, which is fast to a rock shaft 59 and has another arm which serves to interconnect the trip finger 57 with a coil spring 60, while another coil spring 61 is stretched between the aforesaid arm and a. fixed point 62. The third arm 63 of the bell crank 58 extends into the path of movement of a pin 64 projecting from a bell crank 65, which is pivoted at 66, and has its opposite arm joined to a shoulder screw 67 (Fig. l), by which it is pivotally connected to a link 68, and also to a bar pawl 70. A lever cam 69 is swung from the pivot 66 and connects at its lower extremity to the arm 28 by a pin 71 riding in a cam slot 72, and also carries a laterally disposed pin 73 which is arranged to move in a path to engage the bar pawl so that a shoulder 74 of the4 said bar pawl 70 is removed from a'holding pin 75 to thereby release the pawl 70 to the action of an operating spring 76.

The trip finger 57, (Figs. 5 and 6), is also arranged to control the lifting of the check pawl 30 by the provisionl of a step 77 which co-acts at a predetermined time with a stud 78 on the check pawl 30. Adjacent to the check pawl 30 there is a pivoted check latch 8O under control of a spring 8l and having a notch 82 so positioned as to receive a pin 83 of the pawl 30 when the latter is in its unlatched position. The check latch has an extended tail piece 84 so arranged as to be in the path of movement of the lug 56 upon the setting pawl 50 on the arrival of the ratchet wheel 14 with the setting pawl re-engaged, to effect re-engagement of the check pawl 30 due to the resulting disengagement of the check latch 80. f

For the purpose of bringing the drum 33 to rest in the position determined by the cam notch 48 in the cam ring 40', a cam lever 85, (Fig. 7), is provided, the same being pivoted upon the rod 31 and having its nose 86 arranged to drop into the cam notch 48 because of the load of a spring 87 which is stretched to a fixed pin 88 as will be apparent. This cam lever has a rearwardly disposed tail 90 arranged to transmit its movement through a bridge pin 91 to a limit pawl 92, also pivoted on the rod 3l and having its nose 93 in the plane of the ratchet wheel 43 but in inoperative position being held out of said engagement by the relatively weaker spring 94 also stretched to the pin 88. The cam lever 85 is also provided with a finger 95 and a cam shoulder 96 for purposes respectively to be described. Thus when the drum 33 is released to the action of the torsion spring 46 it can only turn until the cam notch 48 registers with the nose 86 of the cam lever 85 because the latter then swings under the action of the spring 87, and this swinging movement is transmitted by the tail 90 to the bridge pin 91 to swing the limit pawl 92 against the tension of the spring 94 so that the pawl nose 93 engages the ratchet wheel 43 which is fast to the drum 33.

When the automatic action requires a line spacing different from that determined by the cam ring 40, it is necessary to provide a means for holding the cam lever 85 from movement when its nose 86 comes into register with the cam notch 48. This is accomplished by providing an arm 97 fixed to the rock shaft 59 and having a shoulder 98 movable in a path to pick up the finger 95 and thereby rock the cam lever 85 to a position where its cam shoulder 96 falls under the latch 100 of a latch arm 101, which is pivoted to a rod 102 and drawn to latching position by a spring 103. The end of the latch arm 101 is spaced from and terminates in the path of movement of the bridge pin 91 in order that it can move into latching position without displacing the bridge pin 91 and be automatically unlatched at the proper time by the movement of such bridge pin 91 as the pawl 92 engages the ratchet 43 under control of cam rings selected by a tot-al control means.

Under one total taking cycle, variation of .v the line spacing is controlled by the cam ring 41 (Fig.v 8) provided with a cam notch 104 which is located for the proper line spacing by angularly turning the ring 41 so that the notch 104 is spaced the desired angular distance from the notch 48 in the cam ring 40 to give the additional platen travel, and in which position it is locked by the nut 44 as previously explained. l When this cam ring 41 controls the line spacing,-the drum 33 is brought to rest by the limit pawl 92 as before, but in this instance its movement is governed by a cam lever 105 pivoted upon thel rod 31 and having its nose 106 in position to drop into the notch 104 under the action of a spring 107 stretched to the pin 88. This cam lever 105 also hasaprojectingtail piece 108 engarring the lower side of the bridge pin 91, en 1ikewiee ii ie provided with e ieieh shoulder 110 so that it can be held out of engagement with the cam ring 41 by seating back of a latch 111 on a latch arm 112, the latter being pivoted to the rod 102 and pulled to latching position by the spring 113. The latch arm 112 terminates in the path ofmovement of the bridge pin 91 in order that it can be shifted at the proper time to unlock the cam lever 105. The end of the latch arm 112 is spaced from the bridge pin to permit the latch to emerge the latch shoulder 110 without depressing the bridge pin 91. In order to swing the cam lever 105 in the direction to be latched by the arm 112, it carries a pivot screw 114 to form a support for a pawl 115 arranged to be shifted by a spring 116 to operative position but held in inoperative position by means of a latch 117 which is freely movable upon the rock shaft 59. The latch 117 seats in a shoulder 118 of the pawl 115, and is automatically disengaged by a pin 120 projecting from the side of the arm 97 at the proper location. The opposite end of the pawl 115 is provided with a step 121 in order to coact with a stop 122 projecting laterally from the arm 97 whereby latching of the cam lever 105 is achieved by the latch 111 of the latch lever 112 and control of the drum 33 is transferred to Vanother part, in this instance the cam ring 42. The means for operating the arm 97 from the total control shaft 1150 latch the

pawls

85 and 105 will be described ater.

Under total taking cycles alternating with the above mentioned total taking cycle, the cam ring 42, (Fig. 9), automatically comes into action because the two cam rings 40 and 41 have become ineifective through the latching out of their respective cam levers and in consequence a cam notch 123 in the cam ring 42 becomes the controlling factor. This notch 123 is located a greater angular distance from the rotational starting point of the drum 33 than either of the notches 48 and 104, andthe angular distance between the cam notch 123 and the cam notch 104 represents the increase of line spacing over the line spacing as controlled by the cam ring 41. The rest position of the drum 33 is controlled by the cam ring 42 as determined by a third cam lever 124 which has its nose 125 in the plane of the ring 42 and projected toward such ring by a spring 126 stretched to the pin 88 whereby the nose of the"cam lever drops into the notch 123 when the two parts are brought into register. The cam lever 124 is pivoted upon the rodn 31 and has a rearwardly extending tail piece 127 resting against the bridge pin 91. When, therefore, the cam ring 42 reaches the position where the notch 123 is opposite the nos-e 125, the cam lever 124 is rocked by its spring 126 and transmits movement through the bridge pin 91 to the limit pawl 92 which is thus brought into rocking engagement with the ratchet 43 to hold the drum 33 against further movement.

.This movement of the bridge pin 91 lifts the

latch arms

101 and 112 to release the

pawls

85 and 105. l

For bringing the cam rings 41 and 42 into operation during a total taking cycle, the total control shaft 128, (Fig. 1), is provided with a fiXedly mounted arm 130 which carries the holding pin 75, heretofore referred to, and which is in engagement with the shoulder 74 upon the bar pawl 70 whereby the latter is shifted in the direction of the arrow H. When the bar pawl is released from the holding pin by the laterally pushing movement of the pin 73, the bar pawl 70 then l moves in the direction of the arrow F.

For restoring the bar pawl at the end of the out stroke of the main shaft 27, a pin 131 is fixed to the bar pawl 70 in a position to be engaged by the end of an arm 132 of a bell crank 133, which is freely rotatable upon the total shaft 128 and is arranged to be rocked by a pin 134 on the other arm of the bell crank 133, said pin 134 being located in the path of movement of a lug 135 upon the arm 28. i

The relatching of the shoulder 74 with the holding pin 75 is effected at the end of each cycle by the pin 71 coacting with the end of a slot 136 located in the link 68 which is jointed to the bell crank 65 by means of the shoulder screws 67.

The operation of 'v the mechanism is as follows:

The parts are shown, in Fig. 1, in the resting position, and during the out-stroke of the machine, the main shaft 27 rotates so as to rock the bell crank26 in the direction of the arrow C and so to drive by means of the pin 24 the bell crank 23 in the direction of the arrow D so that the arm 22 of the bell crank 23 engages the pin 21 in the drive sector 17 rotating it about the pivot 18, which is common to the sector 17 and the bell crank 23, and thereby extends the spring 19 thus storing the energy required for the subsequent driving of the platen 10. On this stroke also the sector 17 rotates the pinion 16 freely about the spindle 11 of the platen 10 in the direction of the arrow E trailing the drive pawl 15, (Fig. 4), over the ratchet wheel 12 which is rigidly mounted on the platen spindle 11. At the beginning of this same stroke, in addition, the pin 71 in the arm 28 of the bell crank 26 coacts with the cam slot 72 in the arm 68, which is pivoted about the centre 66 of the bell crank 65, so as to disengage, by means of the pin 73, the pawl 70, which is jointed by the shouldered screw 67 to the bell crank 65, from the pin 75 in the arm 130 which is rigidly mounted on the existing total control shaft 128. This disengagement allows the load resulting from the spring 76 to move the pawl 70 in the direction of the arrow F so as to rotate the bell crank 65 about its pivot 66 and further by means of the pin 64 in the bell crank 65 to rotate the bell crank 58, (Figs. 5 and 6), and rock shaft 59 in the direction of the arrow G against the action of the weaker spring 61 and so to cause the trip finger 57 to engage the lug 56 in the setting pawl 50 allowving the latch 53 to be engaged with the nose 52 of the setting pawl 50 retaining it out of engagement with the ratchet wheel 14 in order that the arm 37 which carries the setting pawl 50 and is rigid with the boss 36, (Fig. 2), which is freely mounted on the platen spindle 11, may now be rotated around the spindle 11 by the torsion spring 46 which is anchored at one end to the fixed boss 34 and at the other to the drum 33 which carries the arm 45 bearing the latch 53, relative movement between the arms 45 and being limited by the pin 49 in the arm 45. The rotation of the arm 45 is checked on the arrival of the notch 48 in the cam ring 40, (Fig. 7 which is variably clamped to the drum 33 by the nut 44) at the nose 86 of t-he cam lever 85, the nose 86 thereupon dropping into the notch 48 because of the load of the spring 87, the tail 90 of the lever 85 raising the bridge pin 91 in the limit pawl 92 against the action of the spring 94, engaging the nose 93 of the said limit pawl 92 with the ratchet wheel 43 and so/arresting the rotation of the drum 33 on which the ratchet wheel 43 is rigidly mounted. This partial rotation ofthe drum 33 takes place as a result of the turning moment applied by the spring 46 which is so scaled that the pin 49 (Fig. 6) 1n the arm 45 which is rigid with the drum 33 maintains a pressure against the arm 37 until the engagement of the limit pawl 92 with the wheel 43 as has just been described. At this point the lighter spring 47, which is also anchored at one end to the fixed boss 34 butis anchored to the boss 36 of the arm 37 rotates the arm 37 4and consequently withdraws the setting pawl 50 from the latch 53 on the arm 45 so allowing the offset portion of the nose 52 of the pawl 50 to re-engage with the ratchet wheel 14 fiXedly mounted on the platen spindle 11. The aforesaid torsion springs 46 and 47 are of such dimensions that the above functions are completed before the arrival of the lug 135, (Fig. 1), at the pin 134 in the bell crank 133 which is freely pivoted on the total control shaft 128. The depression of the pin 134 in the bell crank 133 by the lug 135 of the bell crank 26 at the end of the out-stroke of the main shaft 27 is such that the upper end of the arm 132 of the bell crank 133 engages with the pin 131 in the pawl 70 and by drivin the pawl 70 in the direction of the arrow restores the bell crank 65 to the positlon it occupied before the release of the pawl 7 0 from the pin by the co-action of the pin 71 with cam slot 72. This restoration of the bell crank allows the spring 61, (Figs. 5 and 6), to withdraw the trip finger 57 so that its step 77, which at the commencement of the cycle was prevented by the lug 56 from engagement with the stud 78 in the check pawl 30, now engages with the said stud 78 so that on the commencement of the return stroke of the main shaft 27 the lug 135 on withdrawing from the pin 134 again allows the pawl 70 to move in the'direction of the arrow F (the form of the cam slot 72 being such that the shoulder 74 is maintained out of alignment with the pin 75) so that the spring 76, overcoming the spring 6l, through the bell crank 65, the pin 64, the bell crank 58 and the trip finger 57, causes the step 77 to bear against the stud 78 and so to rotate the check pawl 30 about its rod 31 to withdraw its nose from the ratchet wheel 13 which is iXedly mounted on the platen spindle 11, the notch 82 of the check'latch 80 engaging with the pin 83 in the check pawl 30 and retaining the check pawl 30 disengaged from the ratchet wheel 13, the rotation of the arm 37 as previously described having withdrawn the lug 56 from the tail piece 84 of thel check latch 80. leaving it free to function as just set forth. The commencement of the return stroke of the shaft 27 also results in the withdrawal of the pin 24 in the bell crank 26 from the bell crank 23 so that the spring 19 is now free to apply a turning moment through the sector 17, the pinion 16, the pawl 15 and the ratchet Aso wheel 12 to the platen spindle 11. The disengagement of the check pawl 30 from the ratchet wheel 13 in the manner just described allows this turning movement' to operate and rotate the platen spindle 11 in the direction ofthe arrow K until the ratchet wheel 14, iixedl'v mounted thereon, by its engagement with the setting pawl 50 rotates the arm 37 in its return direction as indicated by the arrow K until the lug 56 again engages with the tail piece 84 of the check latch 80 and disengages the notch 82 from the pin 83 so allowing the check pawl 30 to re-engage with the ratchet wheel 1.3, terminating the rotation of the platen spindle 11 in the direction for feeding the paper. Now if before the main shaft 27 commences its out-stroke the total shaft 128 should be partially rotated in the direction of the arrow L (for the purpose of setting the machine to print a total) the pin being engaged with the shoulder 74 of the pawl 70 will move the pawl 70'in the direction of the arrow H, beyond its usual resting position, further extending the spring 76 and withdrawing the pin'64 from the bell crank 58 so that the spring 61 rotates the bell crank 58 and the pivot 59` causing the detent 97 (Fig. 7), to rotate in the direction of the arrow M so as to lift the cam lever 85 from the surface of the cam ring 40 and to cause the cam lever 85 to be latched by the latch 100 in a disengaged position.

The ensuing machine cycle will now cause the parts to function as before with the exception that the limit pawl 92 will be. engaged with the ratchet wheel 43 by its bridge pin 91 being lifted by the tail of the cam lever 105, (Fig. 8) whose co-action with the cam ring 41 is exactly similar to that of the cam lever 85 with the cam ring 40. The increased length of feed is obtained by setting the notch 1404 at an angular distance in the direction of the arrow N from the notch 48 in the cam ring 40. It. should be understood that the engagement of the limit pawl 92 effects the disengagement of all latches such as 100 and therefore, that the increased length of feed is only given when the total control shaft 128 has first been operated. Therefore, the cycles between those before which the total control shaft 128 is operated will only result in the feed controlled by the co-action of the cam ring 40 and cam lever 85.

In order that the total taking cycle, following that total taking cycle in which the feed is controlled by the co-action of the cam ring 41 and the cam lever 105I` may result in a feed of greater'length than that provided by such co-action, the iirst rotation of the pivot 59 in the direction of the arrow M, (Fig. 7), causes the pin 120, (Fig. 8) ,to disengagethelatch117 from the shoulder 118 of the pawl 115 so that the pawl 115 assumes the posit`on shown vby the dott-ed lines, its step 121 p ssing to a position resting against the stud 122 in the detent 97 so that its shoulder 118 passes below the nose of the latch 117 with the result that, on the disengagement of the shoulder 74 in the bar pawl 70 from the pin 7 5, the latch described by the detent 97 and the lever 105 byI the stud 122, the pawl 115 and pivot screw 114. the uplifted position of which, due to the latching of the lever 105, maintaining the pawl 115 sufficiently raised for the latch 117 v to re-engage with the shoulder 118 on the return stroke of the rock shaft 59 cons uent on the disengagement of the shoulder 4 in the bar pawl 7 0 from the pin 75, at the commencement of the out-stroke of the main shaft 27. The engagement of the limit pawl 92 with the ratchet wheel 43 is now effected by the third cam lever 124 which co-acts with the cam ring 42 which is set so as to give a longer feed than either the cam ring 41 or the cam ring 40. The movement of the bridge pin releases the

latch arms

101 and 112 so that on the next ensuing cycle, the line spacing will be controlled by the cam ring 40 if an adding operation is performed, -or by the cam ring 41 if a total taking operation is performed.

The said cam rings are released or clamped simultaneously on the manual operation of the nut 44 and when free may be conveniently rotated to the desired adjustments by finger operation.

The relatching of the shoulder 74 of the bar pawl 70 on the pin 75 is effected at the end of each cycle by the pin 71 co-acting with the end of the slot 136 in the link 137 also jointed to the bell crank 65 by the shoulder screw 67.

It will now be apparent that a complete unitary platen mechanism for feeding paper has been devised wherein the stored energy serves as the actuating medium for advancing the platen step-by-step to give the desired line spacing. By the present invention uniform line spacing can be obtained or periodically the line spacing can be automatically varied as when totals are taken in an adding machine or for any other purpose. Furthermore, the platen feed is under positive control which gives exact spacing and eliminates over-run of the platen. Also by the employment of a plurality of line-spacing controls any desired line-spacing effects can be automatically provided for, and while in the present embodiment of the invention only two such controls are shown, it is to be understood the invention is not limited in this respect.

While only a single form is shown in which this invention may be embodied, it is to be understood that the invention is notI limitedA ating means.

2. A platen feed mechanism comprising a platen, means for actuating said platen to cause predetermined line spacing, and means controlled by the total operating mechanism of an adding machine for causing two different variations of said line spacing.

3. A platen feed mechanism comprising a platen, means for actuating said platen to cause predetermined line spacing, means for causing two different variations of said line spacing, and means controlled by the totalv operating mechanism of an adding machine for selectively operating said causing means.

4. A platen feed mechanism comprising a platen, means for actuating said platen to cause predetermined line spacing, means for causing two diHerent variations of said line spacing, and means controlled by the total operating mechanism of an adding machine for alternately operating said causing means.

5. A platen feed mechanism comprising a platen, means for moving said platen to cause a predetermined line spacing, means periodically operative to automatically increase the movement of said platen to produce a line spacing greater than said predetermined line spacing, and means also periodically operative to automatically increase the movement of said pla-ten to produce a line spacing greater than either of said platen movements.

6. A platen feed mechanism comprising a platen, means for moving said platen to cause apredetermined line spacing, means periodically operative to automatically increase the movement of said platen to produce a line spacing greater than said predetermined line spacing, means valso periodically operative to automatically increase the movement of said platen to produce a line spacing greater than either of said platen movements, and means selectively operating said periodically operating means.

7. In a platen feed mechanism, the combination of a platen, an adding machine shaft, and a total control shaft, means for moving said platen to produce a series of equal line spaces, connections between said adding machine shaft and said control for actuating said moving means, means actuated by said total operating shaft for preventing said moving means from further effecting equal line spacing, and means valso actuated by said total control shaft for causing said moving means to vary said line spacing.

8. In a platen feed mechanism, the combination of a platen, an adding machine shaft,

and a total control shaft, means for moving said platen to produce a series of equal line spaces, connections between said adding machine shaft and said control for actuating said moving'means, means actuated by said total operating shaft for preventing said moving means from further effecting equal line spacing, and means also actuated by said total control shaft for causing said moving means to increase said line spacing.

9. In a platen feed mechanism, the combination of a platen, an adding machine shaft, and a total control shaft, means for moving said platen to produce a series of equal line spaces, connections between said adding machine shaft and said control for actuating said moving means, means actuated by said total operating shaft for preventing said moving means from further effecting equal line spacing, means also actuated by said total control shaft for causing said moving means to increase said line spacing, and means for automatically causing said moving means to resumeeffecting equal line spacing.

10. In a platen feed mechanism, the combination of a platen, an adding machine shaft, and a total controlshaft, means for moving said platen to produce a series of equal line spaces, connections between said adding machine shaft and said control for actuating said moving means, means actuated by said total operating shaft for preventing said moving means from further effecting equal line spacing, means also actuated by said total control shaft for causing said moving means to vary said line spacing, and means for automatically causing said moving means t0 resume effecting equal line spacing.

11. A platen feed mechanismcomprising a platen shaft, devices for moving said shaft a predetermined angular distance to produce uniform line spacing, a ratchet fast to said platen shaft, a drum mounted to move relatively about said platen shaft, -a torsional spring arranged to actuate said drum, means actuated by said drum for controlling the movement of said ratchet, andmeans for automatically varying the throw of said drum.

12. A platen feed mechanism comprising a platen shaft, devices for moving saidshaft a predetermined angular distance to produce uniform line spacing, a ratchet fast to said platen shaft, a drum mounted to move relatively about said platen shaft, a torsional spring arranged to actuate said drum, means 13. A platen feed mechanism comprising a platen shaft, devices for moving said shaft a predetermined angular distance to produce uniform line spacing, a ratchet fast to said platen shaft, a drum mounted to move relatively about said platen shaft, a torsional spring arranged to actuate said drum, means actuated by said drum for controling the movement of said ratchet, separate mechanisms for controlling the throw of said drum, each of said mechanisms producing a different throw and including a settable adjustment for throw variation, and means for automatically selecting said mechanisms.

14. A platen feed mechanism comprising a platen shaft, devices for moving said shaft a predetermined angular distance to produce uniform line spacing, a ratchet fast to said platen shaft, a drum mounted to move relative about said platen shaft, a torsional spring arranged to actuate said drum, means actuated by said drum for controlling the movement of said ratchet, separate mechanisms for controlling the throw of said drum, each of said mechanisms producing a. different throw, and means for causing said mechanisms to function in sequence.

15. A platen feed mechanism comprising a platen shaft, devices for moving said shaft a predetermined angular distance to produce uniform line spacing, a ratchet fast to said platen shaft, a drum mounted to move relatively about said platen shaft, a torsional spring arranged to actuate said drum, means actuated by said drum for controlling the movement of said ratchet, separate mechanisms for controlling the throw of said drum, each of said mechanisms producing a different throw, and means for causing said mechanisms to function periodically.

16. A platen feed mechanism comprising a platen shaft, devices for moving said shaft a predetermined angular distance to produce uniform line spacing, a ratchet fast t0 said platen shaft, a drum mounted to move relatively about said platen shaft, a torsional spring arranged to actuate said drum, means actuated by said drum for controlling the movement of said ratchet, separate'mechanisms for controlling the throw of said drum, each of said mechanism producing a different throw, and means for causing said mechanisms to function periodically and alternately.

17. In a platen feed mechanism, the combination of a platen shaft, an adding machine shaft, and a total control shaft, a ratchet fast to said platen shaft, a drum mounted to rotatel about said platen shaft,` a torsional spring arranged to actuate said drum, means actuated by said drum for controlling the movement of said ratchet, means actuated by said adding machine shaft for controlling the release of said drum, separate mechanisms for controlling the throw of said drum, each of said mechanisms producing a different throw, and means actuated by said total control shaft for automatically selecting said mechanism.

18. In a platen feed mechanism, the combination of a platen shaft, an adding machine shaft, and a total control shaft, a ratchet fast to said platen shaft, a drum mounted to rotate about said platen shaft, a torsional spring arranged to actuate said drum, means actuated bv said drum for controlling the movement of said ratchet, means actuated by said adding machine shaft for controlling the release of said drum, separate mechanisms for controlling the throw of said drum, each of said mechanisms producing a different throw, and means actuated by said total control shaft for causing said mechanisms to function in sequence.

19. In a platen feed mechanism, the combination of a platen shaft, an adding machine shaft, and a total control shaft, a ratchet fast to said platen shaft, a drum mounted to rotate about said platen shaft. a torsional spring arranged to actuate said drum, means actuated by said drum for controlling the movement of said ratchet, means actuated by said adding machine shaft for controlling the release of said drum, separate mechanisms for controlling the throw of said drum, each of said mechanisms producing a different throw, and means actuated by said total control shaft for causing said mechanisms to function periodically.

20. A platen feed mechanism comprising a platen shaft, devices for moving said shaft a predetermined angular distance to produce uniform line spacing, a ratchet fast to said platen shaft, a drum mounted to move relatively about said platen shaft, a torsional spring arranged to actuate said drum, means' actuated byl said drum for controlling the movement of said ratchet, separate mechanisms for controlling the throw of said drum, each of said mechanisms producing a different throw, and including a settable adjustment for throwing variation, and means for causing said mechanisms to function in sequence.

21. A platen feed mechanism comprising a platen shaft, devices for moving said shaft a predetermined angular distance to produce uniform line spacing, a ratchet fast to said platen shaft, a drum mounted to move relatively about said platen shaft, a torsional spring arranged to actuate said drum, means actuated by said drum for controlling the movement of said ratchet, separate mechanisms for controlling the throw ofsaid drum, eachofsaidmechanismsproducing a different throw, and including a settable adjustment for throwing variation, and means for causing said mechanisms to function periodically.

22. A, platen feed mechanism comprising a platen, means for actuating said platen to cause predetermined line spacing, a plurality of controls for respectively varying said line spacing means, and means for automatically making a selection of said controls for causing a predetermined variation of said line spacing.

23. A platen feed mechanism comprising a platen, means operated by stored energy for actuating said platen to cause predetermined line spacing, a plurality of controls for respectively varying said line spacing means, and means for automatically making a selection of said controls for causing a predetermined variation of said line spacing.

24. A platen feed mechanism comprising a platen, means for actuating saidplaten to cause predetermined line spacing, and means automatically adjusted before each platen feeding cycle to register the predetermined dimension of line spacing.

25. A platen feed mechanism comprising a platen, means for actuating said platen to cause predetermined line spacing, means automatically adjusted before each platen feeding cycle to register the predetermined dimension of line spacing, and means positively limiting said adjustment.

26. A platen feed mechanism comprising a platen, means for actuating said platen to cause predetermined line spacing, means automatically adjusted before each platen feeding cycle to register the predetermined dimension of line spacing, means positively limiting said adjustment, and means controlled by said registering means for positively determining the dimension of the ensuing line spacing.

27. A platen feed mechanism comprising a platen, means for actuating said platen to cause predetermined line spacing, means automatically adjusted before each platen feeding cycle to register the predetermined dimension of line spacing, means positively limiting said adjustment, means controlled by said registering means for positively determining the dimension of the ensuing line spacing, and means including a plurality of selective controls for regulating the dimension of such preadjustment.

28. A platen feed mechanism comprising a platen, means for actuating said platen to cause predetermined line spacing, and means selectively automatically operative to cause a plurality of periodic variations of said line spacing.

29. In combination with the paper feeding means of an adding and total taking machine, of means for varying the paper feed after the printing of a total, and means for varying the paper feed dierently after the j printing of the next succeeding total.

30. A platen'feed mechanism comprising line-spacing means for actuating the platen, and controlling means for limiting the action of the line-spacing means to cause spacings of three predetermined widths, the controlling means comprising a device that is moved from an ineective to aneffective position in one operation of the machine and is actuated when it functions in another operation of the machine.

3l. A platen feed mechanism comprising line-spacing means for actuating the platen, and controlling means for limiting the action of the line-spacing means to cause spacings of three predetermined widths, the controlling means comprising a device that is moved to effective position in a total-taking operation and is actuated when it functions in a succeeding operation of the machine.

32. A platen feed mechanism comprising line-spacing means for actuating the platen, and controlling means for limiting the action of the line-spacing means to cause spacings of three predetermined widths, the controlling means comprising mechanism the functional action of which is effected in one operation of the machine and depends on two operations of the machine.

33. A platen feed mechanism comprising 4line-spacing means for actuating the platen, and controlling means for limiting the action of the line-spacing means to cause spacings of three predetermined widths, the controlling means comprising mechanism the functional action of which depends on a total-taking operation and which functions in a succeeding operation of the machine.

34. A platen feed mechanism comprising line-spacing means for actuating the platen, and controlling means for limiting the action ofthe line-spacing means to cause spacings of three predetermined widths each of which is variable, the controlling means comprising mechanism the functional action of which is effected in one operation of the machine and depends on two operations of the machine.

35. A platen feed mechanism comprising line-spacing means for actuating the. platen, and controlling means for limiting the action of the line-spacing means to cause spacings of three predetermined widths, the controlling means comprising two devices, one of which acts on the other and to both of which motion is imparted in each of two operations of the machine and which jointly function in and only in the later operation.

36. A platen feed mechanism comprising line-spacing means for actuating the platen, and controlling means for varying the action ofi-he line-spacing means to cause spacings of different widths, the controlling means comprising mechanism the functional action of which is effected in one operation of the machine and depends on two operations of the machine.

Signed at Philadelphia, county of Philadelphia, State of Pennsylvania, this 14th day