US3185008A

US3185008A - Postal meter having means for selectively controlling magnitude op work peed increment

Info

Publication number: US3185008A
Authority: US
Publication date: 1965-05-25
Anticipated expiration: 1982-05-25

Description

May 25, 1965 c. s. BALAZ ETAL 3,185,008

POSTAL METER HAVING MEANS FOR SELECTIVELY CONTROLLING MAGNITUDE OF WORK FEED INCREMENT Filed Nov. 30, 1962 6 Sheets-Sheet l FIE l y 5, 1965 c. BALAZ ETAL 3,185,008

POSTAL METER HAVING ANS FOR SELECTIVELY CONTROLLING MAGNITUDE OF WORK FEED INCREMENT Filed Nov. 50, 1962 6 Sheets-Sheet 2 FIEI E May 25, 1965 c. s. BALAZ' ETAL 3,185,008

POSTAL METER HAVING MEANS FOR SELECTIVELY CONTROLLING MAGNI'IUDE OF WORK FEED INCREMENT 6 Sheets-Sheet 3 Filed Nov. 30, 1962 May 25, 1965 c. s. BALAZ ETAL POSTAL METER HAVING MEANS FOR SELECTIVELY CONTROLLING MAGNITUDE OF WORK FEED INCREMENT 6 Sheets-Sheet 4 Filed NOV. 30, 1962 y 1965 c. s. BALAZ ETAL 3,185,008

POSTAL METER HAVING MEANS FOR SELECTIVELY CONTROLLING MAGNITUDE OF WORK FEED INCREMENT 6 SheetsSheet 5 Filed NOV. 30, 1962 y 25, 1965 c. s. BALAZ ETAL 3,

POSTAL METER HAVING MEANS FOR SELECTIVELY CONTROLLING MAGNITUDE OF WORK FEED INCREMENT- Filed Nov. 30, 1962 6 Sheets-Sheet 6 United States Patent 3,185,008 POSTAL METER HAVING MEANS FOR SELEC- TIVELY CONTROLLING MAGNITUDE OF WORK FEED INCREMENT Charles S. Balaz, Hayward, and lngemar H. Lundquist, Oakland, Calif, assignors, by mesne assignments, to Friden, inc, San Leandro, Calif, a corporation of Delaware Filed Nov. 30, 1962, Ser. No. 241,395 Claims. (Cl. 83-=-224) This invention relates to a tape unit control device for a postage metering machine. More specifically, the invention is an improvement of a tape feed device of the type illustrated and described in the patent of Lundquist et al., No. 3,062,133, issued November 6, 1962.

It is an object of the present invention to provide an improved tape feed mechanism for a tape control device.

Another object of the present invention is to provide an improved means for selectively controlling the feeding and severing of tape strips of predetermined lengths.

A further object of the present invention is to provide an improved tape feed mechanism selectively controlled for the dispensing of tape strips of each of a plurality of lengths.

Other objects and advantages will become apparent from the following description of a preferred embodiment of the invention as illustrated in the accompanying drawings in which:

FIG. 1 is a front elevational view of the postage metering machine with a portion of the base cover broken away to show the tape feed unit;

FIG. 2 is an isometric view showing the selective control for the tape feed mechanism and the main drive clutch control mechanism;

FIG. 3 is a fragmentary frontal elevational view of the base portion of the machine with the cover partially broken away to more clearly show the power-driven actuator for the tape feed drive mechanism;

FIG. 4 is a plan view of the tape feed mechanism;

FIG. 5 is a plan view of the print drum bearing the dater die and slogan die plate;

FIG. 6 is a fragmentary sectional elevational view of the tape feed mechanism showing the normal inactive position of the parts for controlling angular rotation of the tape feed roller, the view being taken on the plane indicated by line 66 in FIG. 4;

FIG. 7 is a fragmentary sectional elevational view of the mechanism for determining the angular rotation of the feed roller, the view being taken on the planes indicated by the lines 77 in FIG. 4; and

FIG. 8 is a fragmentary transverse elevational view of the tape feed mechanism, the view being taken on the plane indicated by the line 88 in FIG. 4.

Referring to FIG. 1 the tape control unit 10 of which the invention is a part is preferably shown as embodied in a postage metering machine of the type disclosed in the patent of Ingemar H. Lundquist, No. 3,107,854, issued October 22, 1963. Only so much of the postage metering machine will be described as is believed necessary for an understanding of the control of the tape control unit 10. Such machine comprises generally the base portion 12, the housing for the cyclic clutch-controlled power unit and the postage meter unit 20.

The tape control unit 10 (FIG. 1) is removably supported on the base plate 21 of the base portion 12 within the cover 22. Also enclosed within the cover 22 is an electric motor (not shown) which serves, upon energization thereof, to effect a continuous operation of the endless belt 23, the upper run of which moves to the right in FIG. 1 in a plane parallel to and above the top surface of the cover 22. In addition to controlling the operation ice of the belt 23, the electric motor also serves, by means of timing belt 24 (FIG. 2), to control the operation of the cyclic clutch 25, enclosed within the power unit housing 15. Upon engagement of the clutch 25, a clutchdriven mechanism (not shown) functions in a conventional manner to impart a synchronous cyclic rotation to the rotary printing drums, one of which is generally indicated at 26 (FIG. 1) and is suitably journalled in the power unit housing 15 and the other of which is generally indicated at 27, suitably journalled within the framework of the postage meter unit 29.

The rotary printing drum 26 (FIGS. 1 and 5) carries the town circle die 28, dater die wheels 29, bulk rate die 3t and the removable slogan die plate 31, while the printing drum 27 carries the postage indicia die. The dater die wheels 29 and bulk rate die 30 are each selectively adjustable to print or nonprint position under the control of the knurled knob 32 and, in a like manner, the slogan die plate 31 may be selectively adjusted from a print to a nonprint position by manipulation of the knurled knob 33.

Knurled knobs

32 and 33 are freely mounted for independent manipulation on the outer extended end of the shaft 34, upon which the rotary printing drum 26 is secured. The axes of the printing drum 26 and the postage indicia printing drum 27 are parallel and the axial spacing of the drums is such that the impression made by each of the printing drums on a tape forms a complete postmark thereon. Each of the

rotary printing drums

26 and 27 is provided with a similar roller 35 which, in the full cycle position of the drums, is in rolling contact with the upper running surface of the endless belt 23 and is positioned directly above respective impression rollers, or platens, 36 and 37, which are normally spring-urged upwardly into rolling contact with the underside of the belt 23.

The endless belt 23 (FIGS. 1 and 3) is carried by pulley 42 secured on shaft 41 and similar pulley 44 secured on shaft 43, each of the shafts being suitably journalled in axially parallel relationship within the framework of the base portion 12. In order to drive the endless belt 23, gear 45 secured on drive shaft 46 rotating continuously in a clockwise direction, upon energization of the motor, is enmeshed with gear 47 which, in turn, is enmeshed with gear 48 secured on pulley shaft 41, causing movement of the upper run of the belt 23 to the right. Pulley 42 is normally urged upwardly to resiliently maintain belt 23 in engagement with pressure roller 49 suitably supported within the framework of the power unit housing 15. Similarly, pulley 44 is normally urged upwardly to resiliently maintain belt 23 in engagement with pressure roller 50 suitably supported within the meter unit 24). Thus, tape, in passing between the belt 23 and pressure rollers 49, 35 and 5b, is maintained in frictional engagement with the belt for discharge at the right end thereof.

Referring to FIG. 2 and as explained above, the cyclic clutch 25 becomes effective, upon engagement thereof, to cause a synchronous cyclic rotation of the

rotary printing drums

26 and 27, the peripheral speed of which is in timed relation to the surface speed of the belt 23. Clutch 25 is of a well-known construction and is normally retained in its full-cycle, or disengaged condition, by clutch control member 54. Control member 54 is normally urged counter-clockwise intov the clutch-disengaging position by means of spring 55, which also serves to resiliently maintain a shoulder formed in the lower edge of clutch control link 56 in engagement with the ear 57 formed at a right angle to the upwardly extended arm of control member 54. At its right end, link 56 is pivotally mounted at 53 on arm 59 secured on shaft 6t suitably journalled in the framework of the machine and within the housing 15. Thus, it can be seen that upon clockwise rocking movement of ansaoos shaft 60, clutch control member 54 is likewise rocked to effect engagement of clutch 25 for a single cycle of operation as described in the afore-mentioned patent, No.

Although the invention is shown and described as an improvement of the tape control device disclosed in the aforementioned patent, No. 3,062,133, it will be understood that the invention'is adaptable for use in any type of tape control mechanism which operates to feed the tape from a roll, or source of supply, to a position Where it is severed to form strips of selected lengths. As shown, the tape feed and cutting mechanism is adapted to be detachably mounted. as a unit within the machine and, when ro erl mounted for o era-tion, it is in a osition such that each severed strip of tape, or web, will thereafter be advanced to the printing station for animpression by each between the vertically disposed parallel walls of the

respective guideway blocks

67 and 68 toprevent inaccurate alignment of the tape feed mechanism and the control mechanism therefor, as will be hereinafter described. Following the sliding movement of the base 64 and the mechanism mounted thereon into operative position with- 1 in the machine, thebase, and the mechanism carried thereby, is moved upwardly and becomes locked in the raised position against movement in either direction by therocking of handle 69 to the position shown in FIGS. 1 and 4;

The base plate 64 of the tape control unit serves to mount the roll of tape, or webbing 7 0, mechanism for feed-.

Base plate 64 is substantially rectangular in shape and is of a length sufiiciently less than the spacing 1 gear 92 enmeshed with gear 91 and, therefore, roller 79 in frictional contact with feed roller. 80, :U-shaped bracket 86 is resiliently urged to the position shown in FIG. 6 by means of the relatively strong spring 94.- The peripheral surface of roller 79 is preferably'covered with a cylinder of rubber similar to feed roller 80 and, in'operation, the strength of the spring 94 is such. that sufficient pressure is applied by roller 79 to ensure uninterrupted feeding of the tape T from the source of supply 70. The degree of contact pressure of roller 79 and feed roller 80 with the respective surfaces of the tape T is determined by the pitch diameter of the enmeshed

gears

92 and 91. The pitch diameter of each gear. 91 and 92 is only slightly less than the outside diameter of the respective feed roller 80 and roller 79 and is such that the peripheral speed of the roller 79 is substantially equal to that of feed-roller 80.

Following energization of theelectric motor and, thus, the initiation of anoperation ofthe endless belt 23 by manipulation of control button 95 (FIG. 1), a depression of control key 96 will effect rotation of feed roller 80 (FIG. 8) to move tapeT across a rotary cutter device, generally indicated at 97 (FIG. 4). From the cutter device 97, the leading en-dof the tape is advanced to a position wherein it is frictionally grasped by, feed belt 23' 7 between the belt and pressurerollen49 (FIG. '1). As the leading end of tape T is moved into the nip of belt 23 and pressure roller 49, engagement of clutch 25 is effected to cause a synchronous cyclic rotation of each of the printing drums .26 and 27. Following-reither 180 rotation or a complete revolution of the feed. roller 80, the rotary cutter device 97 becomes effective to sever the tape, thereby providing a strip of predetermined length which is I thereafter advanced by the feed belt 23 to the printing ing a predetermined length of tape and a cutting knife effective to thereafter sever the tape,.forming a strip of either of two predetermined lengths.

The tape feed and cutting mechanisms are supported in spaced parallel frame 1 posed peg 76 secured on base 64, beneath and in contact with roller 77 (FIGS. 4 and 6) rotatably mounted on shaft 78 journalled in frame members 72 and 73., The advancemaintain plate 106 in spaced parallel relationship to.

men-t of tape T is upwardly from roller 77 and is effected by means of the pair of power-driven feed rollers 79 and 80 (FIGS. 4, 6 and 8),. coacting one with the other to move the tape to the cutting station where it is severed to form strips of predetermined lengths.

Roller 77 is rotatably mounted on shaft 78 and is positioned between the parallel legs $4 and 85 of the substantially U-shaped bracket 86. Each of the

legs

84 and 85 is keyed to the shaft 78 so that a rocking of the bracket 86, counter-clockwise from the position shown in FIG. 6, will rock shaft '78. The rocking functionof the bracket 86 is not considered to be pertinent to the invention and will not, therefore, be described herein. However, for a complete description of this mechanism, reference is to be had to the afore-mentioned patent, No. 3,062,133.

As stated above, the tape T, in its path of movement from roller 77, passes between feed rollers 79 and $9, the cooperation of the

feed rollers

79 and 80 serving to frictionally control intermittent movement of the tape. Feed nalled in suitable bearing bushings in each of frame memsurface of which is encompassed by a suitable frictional material, such as rubber.

85 of U-shaped bracket 86.

roller is secured on shaft 90 (FIGS. 6, 7 and 8) jourstation for a postmark impression drums 26 and 27. Referring nowto FIGS. 6 and 8, the rotationof feed roller 80 is under the control of a pair of similar pinion gears 102. and 10.3 and a rack and

pinion

104 and 105. Rack 104, enmeshed withpinion 105, is secured on a plate 106- suitably mounted for selective differential reciprocatory movement on

studs

107, 108 and 109 on frame member 73. Each of thestuds 107; and 108 serves to by each of printing frame member 73 by the engagement of the reduced diametral end portion of each stud in respective elongated parallel slots 110 and 111 in plate'106. The slots 11%) and 111 are likewise disposed in parallel relationship to the rack 104. In addition to the pin-and-

slot connections

107, 110 and 108,111, plate 106 is further guided in its reciprocatory movement parallelto frame member 73 by the engagement of the upper edge of the plate in an annular slot in stud 109. .Normally, plate 106 is biased to the right-hand position shown in FIG. 6 by'means of a relatively strong spring 115 (FIGS. 1, 4 and 8), secured at. its one end on a stud 116cm frame member 73 and at its other end on a stud 117 secured on plate 106 and extending through an elongated slot 118 in frame me1nber 73.

Upon reciprocation of plate 106, rack 104, enmeshed with pinion-105 secured .on and concentric with pinion 102, imparts rotation to pinion 102. Pinions' 102, 105 are rotatably' mounted on a stub shaft. 119 secured on frame member 73. Pinion 102 is enmeshed with pinion 103 secured on one end of a hub 120 'rotatably mounted on shaft 90 so that, upon rotation of pinion 102, a similar angular rotation is irnpartedto pinion 103. The hub 120 of pinion 103 extends through an elongated slot 121 in plate 106, the width of the slot being such that there is sufiicient clearance to permit reciprocation of plate 106-. Uponmovernent of plate 106 and rack 104 'to the left from the normally inactive posit-ion shown in FIG. 6

' under control of an actuating mechanism, generally indicated at-122 (FIG. '3) and to be described hereinafter, pinion 103 is rotated in a clockwise direction (FIG. 6)

to impart a similar clockwise rotation to shaft 90 and feed roller 80.

The clockwise rotation of pinion 103 (FIG. 6) is transmitted to shaft 90 by means of a coil spring-type clutch 125, an actuating disk 126 and a driven disk 127 (FIGS. 7 and 8). Each of the

disks

126 and 127 is cup-shaped with the outside diameter of the cup portion of the disk 126 being sufiiciently less than the inside diameter of the cup portion of disk 127 so that the cup portion of disk 126 may be inserted for free turning movement within the cup portion of disk 127 to enable the positioning of the disk, one adjacent the other, on shaft 90. The actuating, or driving, disk 126 and driven disk 127 are of equal diameter and each is provided with a pair of similar substantially V-shaped

notches

128, 129 and 130, 131, respectively, in the peripheral surface thereof (FIGS. 6 and 7).

Notches

128, 129 and 130, 131 of

respective disks

126 and 127 are diametrically opposed and, as will be described hereinafter, the

notches

128 and 129 in disk 126 cooperate with respective notches 130 anad 131 in disk 127 to efiect operation of the cutter mechanism 97 in either of two angularly rotated positions of the disks. Driven disk 127 is provided with a hub 132 pinned on shaft 90, whereas driving disk 126 is carried by a hub 133 rotatable on shaft 90 with the end of the hub 133 abutting the end of pinion hub 120, intermediate the axial length of the spring 125. As stated above, rotation of pinion 103 is transmitted to disk 126 by the spring-clutch 125 which is tightly coiled in a clockwise direction, as viewed from the right in FIG. 8, and is supported on the hub 133 of disk 126 and on the hub 120 of pinion 103. The diameter of the hubs 120 and 133 is substantially that of the inside diameter of the coiled spring 125. For substantially half of its axial length, spring 125 is positioned within the cup portion of the disk 126, with the end of the spring in abutting relationship to the inner surface of the cup portion of the disk. At its other end, spring 125 abuts the surface of a flange 134 integrally formed on hub 120, intermediate the end of the hub and pinion 103. Thus, it becomes apparent that upon clockwise rotation of pinion 103 (FIG. 6), coil spring 125 is tightened to provide a frictional bond between the spring and hub 120 of the pinion 103 and hub 133 of disk 126, thereby effecting a similar rotation of disk 126. However, inasmuch as spring 125 is coiled in a clockwise direction, pinion 103 may be rotated counter-clockwise (FIG. 6) independently of disk 126 for a purpose to be explained later.

A driving connection is provided between

disks

126 and 127 to enable a clockwise rotation of feed roller 80, as viewed from the right in FIG. 8, upon rotation of pinion 103 by rack 104 as plate 106 is differentially moved selectively from its normally inactive position. For this purpose, a pin 138 (FIGS. 7 and 8), projecting outwardly from the inner face of the disk 126, is engaged in an arcuate slot 139 in the juxtapositioned driven disk 127. In the normal at rest position of the tape feed mechanism, pin 138 on driving disk 126 abuts the counterclockwise end of the arcuate slot 139 in driven disk 127, as seen in FIG. 7. It will be noted that with the pin 138 so positioned in slot 139, the

notches

128 and 129 of disk 126 are aligned with the corresponding

notches

130 and 131 of disk 127. Immediately, upon clockwise rotation of pinion 103, disk 126 is likewise rotated and, following a lost motion of approximately 35 in the rotation of disk 126, pin 138 carried thereby engages the clockwise end of the slot 139 (FIG. 7) to immediately, thereafter, effect a clockwise rotation of driven disk 127, shaft 90 and tape feed roller 80. Continued clockwise rotation of pinion 103, disk 126 and disk 127 will selectively move the V-notch 128 of disk 126 to either an angularly rotated position approximately 215 or 395 displaced from the position thereof shown in FIG. 7. At the same time, the V-notch 130 in disk 127, corresponding to V-notch 128 in disk 126, will either be moved to an angularly rotated position approximately 180 or 360 from the position thereof, likewise shown in FIG. 7. Fol lowing the selective 180 or 360 rotation of the disk 127 and feed roller 80, rotation of the feed roller will be terminated and rack 104 will be released to be returned to its normally inactive position (FiGS. 3 and 6) under the influence of spring 115, as will be described hereinafter.

As stated hereinbefore, the control of the tape feed mechanism is enabled by the manipulation of control key 96 (FIG. 1), which operates in a conventional manner to initiate operation of the power-driven actuating mechanism 122 (FIG. 3). Referring now to FIGS. 1, 3 and 6, following the sliding movement of the base 64 and the tape feed mechanism 10 thereon into its operative posi tion within the machine, the base 64 is locked in place by adjustment of handle 69 to the position shown in FIG. 1. Upon locking base 64 in its operative position, the tape feed roller is accurately positioned for cooperation with feed belt 23, and a stud 140, secured on plate 106 adjacent the right end thereof, is aligned with rack slide 141 of the power-driven actuating mechanism 122. The rack slide 141 is positioned adjacent bracket 142 and is supported for endwise movement thereon by means of

pins

143 and 144 engaged in respective elongated slots 145 and 146 in slide 141. Bracket 142 is secured on frame member 147 in parallel spaced relationship thereto to maintain rack slide 141 in the plane of gear 148 secured to gear 45 carried by drive shaft 46. Each of the

pins

143 and 144 is of similar diameter. However, slot 146 is wider than slot 145, thereby enabling oscillatory movement of rack slide 141 about pin 143 to effect an engagement or disengagement of the rack teeth 149 with the gear 148.

Normally, rack slide 141 is resiliently maintained in the inactive position shown in FIG. 3 by means of the relatively strong spring 153, wherein car 154 on slide 141 abuts limit stop 155 which is preferably of rubber and is supported on bracket 142. The influence of spring 153 is such that rack slide 141 is not only urged to the right in FIG. 3, but is also urged clockwise about pin 143 to engage the upper edge and left end surface of slot 146 with pin 144, thereby maintaining rack teeth 149 out of engagement with the teeth of gear 148.

It will be remembered that upon energization of the motor drive means, drive shaft 46 rotates continuously to effect a continuous operation of feed belt 23. At any time during the continuous rotation of drive shaft 46, a depression of control key 96 will effect a rocking movement of the slide 141 counter-clockwise to engage the rack teeth 149 with the gear 148 (FIG. 3). Immediately upon engagement of the rack teeth 149 with the teeth of gear 148, slide 141 is moved to the left, as viewed in FIG. 3, when, following an initial predetermined lineal motion of the slide 141, a shoulder 156 formed in the left end portion of the slide 141 engages stud 140 secured on the rack supporting plate 106 to effect rotation of tape feed roller 80. To control the engagement of the rack teeth 149 with gear 148, rocker plate 158, pivotally mounted at 159 on and adjacent frame member 147, carries a pair of diametrically opposed rollers 160 and 161. The plate 158 may be rocked from the normal inactive position shown in FIG. 3 counter-clockwise to its active position and is resiliently retained in either the inactive or active position thereof by means of toggle spring 162. Each position of the plate is determined by the engagement of one shoulder or the other formed by the arcuate recess 163 in the defining edge of the plate 158 with pin 164 on frame member 147.

In the normally inactive position of the rocker plate 158, the ear 165, formed at a right angle thereto, is substantially perpendicularly disposed, having its upper edge portion engaged in recess 166 formed in the lower edge of the horizontally disposed link 167. At its right-hand end (FIG. 3), link 167 is connected by suitable linkage (not shown) to control key 96 (FIG. 1) and becomes effective,

7 7 v in a well-known manner, upon depression of control key 96, to move link 167 to the right. end, link 167 is supported for reciprocatory movement in a vertical slot in the angularly disposed right angle pro- I jection 168 of lever 169 pivotaliy mounted on frame member 147.

Normally, link 167 is urged to the left (FIG. 3) by spring 172. In the inactive position of the link 167 and rocker plate 158, the bottom of the recess 166 in link 167 rests on the upper edge of the ear 165 and the lefthand shoulder formed by the recess abuts the face of the ear 165. Upon depression of control key 96, link 1167 is moved to the right (FIG. 3) and the left-hand shoulder of the recess portion 166 of the link, by virtue of its engagement with car 165, effects a counter-clockwise rocking movement of the rocker plate 158 from its normally inactive to its active position. As the rocker plate 168 is adjusted to its active position, roller 160 engages the lower edge of the rack slide ldL'rocking the slide counterclockwise about pm 143 to engage the rack teeth 149 with the continuously running gear 1423. Thereafter, rocker plate 158 is resiliently maintained in its active, or rackengaging, position by means of the toggle spring 162, and the diametrically opposed rollers 160 and 161 are positioned and retained in a horizontal plane parallel to the path of travel of the rack slide 141.

As the teeth 149 of the slide 141 are moved into en- 1 on roller 161, while the lower edge of the slide 1141 continues to ride on roller 160. Following a lost motion of the rack slide 141, equivalent to approximately one-half the extent of its travel, shoulder 156 engage pin 146- on plate 106. Thereafter, continued movement of the rack slide 141 to the left'causes rack 104 to become effective to impart 180 clockwise rotation to tape feed roller 80,

moving the leading end of tape T into engagement with a feed belt 23.

As rack slide 141 nears the completion of its leftward travel, the downwardly inclined leading edge 174 of a depending portion of the slide 141 moves into engagement with roller 160 and becomes effective, upon further movement of the slide, to rock plate 158 clockwise. As roller 160 moves downwardly along the inclined surface 174, roller 161 moves upwardly along the beveled right-hand end surface of cam bar 173. Immediately upon movement of roller 161 beyond the end of the cam bar 173, toggle spring 162 becomes effective to restore rocker plate .158 to its inactive position. During the return of the plate 158 to its inactive position, roller 160 engages the horizontally disposed upper edge surface 175 of the depending portion of slide 141 which, together with the biasing effect of the spring 153, causes disengagement of the rack teeth 149 from the teeth of gear 14-8 and return of the slide 141 to the inactive position shown in FIG. '3. Simultaneously therewith, plate 1&6 and, therefore, rack 104 are restored to the inactive position under the influence of spring 115.

I There are certain conditions under which the link 167 is rendered inoperative to effect engagement of the rack 149 with gear 148 for an operation of the tape feed roller 80; One such condition is that of the exhaustion of the tape supply 70, another being the condition wherein the tape is improperly threaded, and the third being the condition wherein the tape feed unit is removed from the machine. However, the mechanism for controlling the disablement of the link 167 under these conditions is not considered pertinent to the invention and will, therefore, not be described herein. For a description of this Adjacent its other mechanism, as well as a more. complete disclosure of the tape feedactuating mechanism 122,v reference is to be had to the afore-mentioned patent, No. 3,062,133.

In the embodiment shown, the rotary-cutter employed is preferablyof the type, the two members of which have intermeshing'serrated edges andcomprise a cutter rod 176, one end portion of which is provided with a series of circumferential serrations, as at 177, and the other end portion of which is of a reduced diameter and serves to journal the cutter rod 176 in suitable bearings in each of "

frame members

72 and 73; At its outer end, the serrated portion 177 is cradled in a semicircular notch in the upwardly inclined edge of frame member 71, providing additional support for cutter rod176. In order to provide a cutting edge, the serrated portion 177 of rod 176 is cut away, providing a fiat surface extending axially the length of the serrated portion 177. In operation, the teeth of the serrated portion 177 of rod 176 are adapted to intermesh with a series of similar serrations provided along the edge of cutting blade 178 extending transversely of feed roller between

frame members

71 and 72. A portion of the lowersurface of the cutting blade 178 is cut away, providing a channelof sufficient length and depth to permit the passage of the tape therethrough during a tape feeding operation.

In the normally inactive position of the plate 106 and disks. 126 and 127 (FIGS. 6 and 7 wherein the notches 128 and .129 of disk 126 are aligned with the corresponding notches 130 and 1310f disk 127, the cutting edge of the serrated portion 177 of the rotary cutter 97 is in the actuated position'relative to the teeth of the cutter blade. 17%}, Thus, the tape passageway provided in the cutting blade 178 is closed. However, upon engagement of shoulder156 of rack slide 141 with stud on plate 1t96-and the subsequent movement of the plate 106, to the left as viewed in FIG. ,6, the initial 35 rotation of disk 126 becomes effective to rock cutter shaft 1'76 counter-clockwise (FIGS. 6 and 7).: The toothed portion 177 of the cutter shaft 176 is, therefore, rocked out of active engagement with the teeth of the cutting blade 178, thereby enabling the, tape T to pass over the flat surface of the toothed portion 177. To control the rocking of the cutter shaft 176, arm 132 (FIGS. 4, 6 and 7), secured on shaft 176

intermediate frame members

72 and 73, is provided with the nose portion 183 which is normally urged under the influence of the relatively strong spring 184 into either the aligned

notches

12S and 130 or 129 and 131 of

respective disks

126 and 127. Arm 182 is of a thickness equivalent to the combined thicknesses of the

disks

126 and 127 so that, uponan angular displacement of the notch 128 or 12.9 in disk 126 relative to the corresponding .notch'130 or 131 in disk 127,'the nose 183 of arm 182 will ride on the periphery of one disk or the other, or both, thereby maintaining-the cutter portion 177 in its inactive position.

As explained hereinbefore, immediately upon actuation of rack 104 to the left from the inactive position shown in FIG. 6, disk 126 receives an initial angular rotation of approximately 35 in a clockwise direction, whereupon pin 133 (FIG. 7) on disk 126 is moved into engagement with the upper end of the slot 139 in disk'127. During this initial rotation of disk 126, the formed camrning edge of either the

notch

128 or 129 therein becomes effective to rock arm 132 counter-clockwise thereby rendering the cutter device inactive. Thereafter, both

disks

126 and 127 rotate together in a clockwise direction as the rack 10d continues its movement to the left under the control of actuator rack slide 141.

During this phase of the operation, disk 126 receives an angular rotation of 215, while disk 127 and, therefore, tape feed roller 80 receive an angular rotation of thereby moving the leading end of the tape T across the flat surface of the serrated portion 177 of the cutter 97 and into frictional contact with belt 23 between the belt and pressure roller 4%., Also, during this phase of the operation, the nose 183 of arm 182 (FIG. 7) rides on the peripheral edge of the

disks

126 and 127, maintaining the cutting edge of the serrated portion 177 in its inactive position relative to cutter blade 178. At the same time, the

notches

128 and 129 of disk 126 assume a position wherein the notches are advanced 35 clockwise from the corresponding

notches

130 and 131 of disk 127. This 35 clockwise rotation of disk 126 is not sufiicient to cause the disk to completely overlie the notches in disk 127. Thus, the axial alignment of the corresponding notches in the respective disks is restricted so that only a small portion of the left-hand surface of either notch 128 or 129 is exposed for engagement by the nose of arm 182 following the 180' rotation of disk 127. As disk 127 and feed roller 80 complete 180 of rotation, the nose of the arm 182, under the influence of the relatively strong spring 184, engages the exposed surface of either notch 128 or 129 of disk 126 to return the disk counter-clockwise until pin 138 engages the lower end of the slot 139 in disk 127 The corresponding notches in the respective disks are thus realigned and simultaneously therewith, spring 115 becomes effective to return the plate 106 and, therefore, rack 104 to the normally inactive position. Upon engagement of the nose 183 of arm 182 in the aligned notches of the

disks

126 and 127, rotation of the disks and feed roller 80 is terminated and the force exerted by the spring 184 is sufficient to cause the serrated edge of the toothed portion 177 of cutter device 97 to sever the tape, forming a short strip. Thereafter, the severed strip is carried by means of belt 23 to and beyond the printing station for an impression by each of printing heads 26 and 27. Following the termination of rotation of

disks

126, 127 and feed roller 80, pinion 103 (FIG. 6) will continue to rotate freely counterclockwise on shaft 90 thereby enabling rack 104 to continue its return to the inactive position shown.

Following the 180 rotation of feed roller 80, and the re-engagement of the nose 183 of arm 182 in either pair of aligned

notches

128 and 130 or 129 and 131 of the

disks

126 and 127, a short tape is provided which, upon advancement by belt 23 through the printing station, will receive a postage impression from print drum 26 and the indicia print drum 27. A differential actuation of rack 104 may be utilized, when desired, to enable the operation of the tape feed mechanism for the provision of a long tape which, upon severance thereof, is advanced by the belt 23 through the printing station to receive a slogan impression from print drum 26 in addition to the postage impression from each of the print drums 26 and 27.

In order to provide a long tape, disk 126 is revolved 395 to effect one complete 360 rotation of disk 127 and, therefore, feed roller 80. For this purpose, a pin 185 is slidably mounted for axial movement (FIGS. 3, 4 and 6) within a suitable bushing 186 secured on plate 106, below and to the right of pin 140. Pin 185 is axially parallel to pin 140 and is normally retained in an endwise adjusted position such that its one end is flush with the outer surface of plate 106. At its other end, pin 185 is provided with a circular head 187, disposed between the head of a pin 188 carried by an car 189 and the surface of the ear 189 which is formed at a right angle to a bar 190 suitably supported for endwise movement in rectangular apertures in each of

frame members

71 and 72. The bar 190 is normally urged to the position shown in FIG. 4 by a spring 191 secured at its one end on a pin carried on bar 190 and at its other end on an extended ear of frame member 71. In this normally inactive position of the bar 190, determined by the engagement of a pin 192 on the bar with frame member 71, the outer end surface of the pin 185 is flush with the face of plate 106. Upon movement of bar 190 downwardly, as viewed in FIG. 4, against the urgency of spring 191, or to the right as viewed in FIG. 8, the end portion of the pin 185 is moved outwardly beyond the face of plate 106 into the plane of movement of rack slide 141 for engagement by the arcuate end 193 thereof. In the normally inactive position of the plate 106 (FIGS. 3 and 6), the position of the extended pin 185 relative to the arcuate end 193 of slide 141 is such that the gear-driven actuation of slide 141 for a tape feed operation will impart twice the movement to plate 106 as that effected by the engagement of the shoulder 156 of slide 141 with stud on plate 106.

Upon initiation of a tape feed operation by the depression of control key 96 (FIG. 1), the initial movement imparted to plate 106 by the engagement of the arcuate end of rack slide 141 with pin 185- rotates disk 126 approximately 35 in a clockwise direction (FIG. 7) as described above. It will be remembered that this initial rotation of disk 126 effects a rocking movement of arm 182 to rock the serrated portion 177 of the cutter rod 176 to its inactive position. At the same time, pin 138 moves into engagement with the upper end of slot 139 and each of the

notches

128 and 129 in disk 126 move out of alignment with the corresponding

notches

130 and 131 of disk 127 and remain out of alignment until after a complete 360 rotation of disk 127 Following the initial rotation of disk 126 and the subsequent rotation of both

disks

126 and 127, the nose 183 of arm 182 rides on the peripheral surface of the disks to maintain cutter 97 disabled. Due to the displacement of the notches in one disk relative to the notches in the other disk, the nose of the arm 182 will ride on the peripheral surface of the disk 126 through the angular rotation of disk 127. As the disk 127 completes a full revolution and the teeth of rack slide 141 become disengaged from the teeth of gear 148, slide 141 is retracted to its inactive position and rack 104 returns to its inactive position. During the initial phase of the return movement of rack 104, arm 182, under the influence of spring 184, returns disk 126 an angular increment of 35 counter-clockwise to move pin 138 into engagement with the lower end of slot 139 in disk 127, thereby aligning the notches in disk 126 with the notches in disk 127. Whereupon, the actively positioned pair of corresponding notches become engaged immediately by the nose 183 of arm 182 under the urgency of the spring 184 to terminate rotation of feed roller 80 and to rock cutter rod 176, thereby severing the tape. Thereafter, rack 104 continues its return movement to the inactive position and the severed strip of long tape, which is twice the length of the short tape, is carried by the belt 23 through the printing station.

The selective adjustment of pin 185, from its inactive to its active position, is under the control of the manipulative knob 33 (FIG. 5), which operates in a well-known manner to control the adjustment of the slogan die plate 31 to either the print or nonprint position on printing drum 26. As fully described in the afore-mentioned patent, No. 3,062,133, the die block 201, upon which the slogan die plate 31 is removably mounted, is supported for radial movement on stud 202 secured on one leg of the U-shaped bracket 203 supported between each of circular end frames 204 and 205 which, in turn, are secured on shaft 34 for rotation therewith. Normally, die block 201 and the slogan plate 31 thereon are urged to the retracted, or nonprint, position by means of compression spring 206. To enable the retraction of the die block 201, the channel member 207, slidably supported on one leg of the U-shaped bracket 203, assumes a position to the right of the position shown in FIG. 5 under the urgency of spring 208. The movement of the channel member 207 is parallel to the axis of shaft 34 and, upon manipulation of knob 33, is moved to the position shown in FIG. 5, whereby die block 201 is cammed radially to adjust the die plate 31 to the print position. Upon adjustment of the die plate 31 to the print position, a pin 209 carried by channel member 287 for movement therewith becomes effective to cause an axial translation of pin 185 to its active position (FIGS. 5 and 6), as will now be described.

Referring to FIGS. 2, 4, 5, 6 and 8, pin 209 at its outer end is formed to provide a diametral rib which is eni t t1 gaged in a suitable groove 216 in shaft 34. The groove 21ft extends longitudinally of the shaft 34 parallel to the axis thereof and serves to confine rod 211, one end of which abuts the rib portion of pin 269 and the other end of which abuts collar 215 slidably mounted on shaft 34. The respective ends of the rod 211 are maintained in engagement with the rib on pin 269 and with collar 215 by Ineansof compression spring 216 positioned on shaft 54 between collar 215 and disk 217 secured on shaft 34.

Thus, it can be seen that, upon movement of the channel member 2d7 fromits right-hand, or inactive, position to the active position shown in FIG. 5 for'the adjustment of the die plate 31 to its print position, pin 269 becomes effective to move rod 211 axially of the shaft 34, thereby imparting a sliding movement to collar 215 on shaft 34, compressing spring 216. The control of the adjustment of die plate 31 from its nonprint to print position and the axial translation of rod 211is conventional. It is, therefore,-believed that the foregoing description will sufiice for an understanding of this mechanism. However, for

a more complete disclosure, reference is to be had to the afore-mentioned patent, No. 3,062,133.'

As the collar 215 is moved to the right in FIG. 2, means become effective to move pin 185 axially from its normally inactive toits active position. For this purpose, a shaft 218 (FIGS. 2, 6 and 8) is suitably supported adjacent its one end in a bracket 219 secured on frame member 220 and is journalled adjacent its other end in crossframe member 221. At its respective ends, shaft 213 car- 'ries a vertically disposed arm 222 and a depending-arm 223 secured thereon. The upwardly extended laterally oifsetend of arm 222 is provided with an ear 224 formed at a right angle thereto and positioned between the collar 215 and the face of the disk 217 with its left-hand edge in contact with the flange on collar 215. As stated above, the compression spring 216 normally urges collar 215 vto the left (FIG. 2) and the spacing thereby provided between collar 215 and disk 217 is sufficiently greater than the width of the ear 224 on arm 222 to permit'the adjustment of the die plate 31 from the nonprint to the print position and the rocking of the arm 222. At its lower extremity, the depending arm 223 is provided with car 225, extending laterally at a right angle thereto for engagement with the arcual end of the bar 199. Thus, upon movement of die plate 31 to its print position and the movement of thecollar 215 to the right in FIG. 2, bar 1% is moved to the right in FIG. 8 to actively position the outer end portion of pin 185 in the path of travelof rack slide 141. Pin 185 will remain in its active position so long as slogan die plate 31 remains in its print adjusted position.

Itwill be recalled that a clockwise rotation of clutch control shaft 6t as viewed from the lower end thereof in FIG. 2, serves, in a well known manner, to effect an engagement of the cyclic clutch for the control of a synchronous cyclic rotation of the print drums 26 and 27 in timed relation to the surface speed of the belt 25. It will be noted also that a disengagement of clutch 25 is effected in a conventional manner following each cyclic operation of the print drums 26 and 27. In order to effect engagement of clutch 25 and the operation, therefore, of the

drums

26 and 27 in timed relation to the feeding of the tape T, a-laterally extended pin' 230 (FIGS. 6, 7 and 8) is secured on rack supporting plate 106 for movement therewith. Pin 230 is engaged in a bifurcation 231 in an position, the laterally extended pin 236 secured on the free end of arm 235 is angularly displaced a predeter mined distance from the upper edge surface of the laterally extended end portion 2370f the slide 238, the extension 237 lying in the arcual path of the pin 236 for engagement thereby, upon clockwise rocking movement of arm 2355. Slide 233 is mounted for .vertical endwise movement by the engagement ofeach ofpins 239 on the laterally offset extension 240 of bracket 241 in suitable elongated slots in slide 238. Bracket-241 is secured on frame member 229 and the laterally extended offset portion 24% thereof is provided with recess 242'. A similar recessis provided in slide 238 corresponding to recess 242 and within the recesses in slide 238 and the offset extension 240, spring 243 is disposed; At its upper end, spring 243 is supported in anaperture in the offset extension 245) and at its lower end is supported in an aperture in slide 233, spring 243normally serving to urge. slide 238 upwardly itO the inactive position shown in FIG. 2.

Upon downward movement of the slide 238 from its inactive'position, shaft 68 is rocked to effect engagement of the clutch 25. For this purpose, shaft 60 carries arm 248- which, at its free end, isprovided with pin 249 engaged in the vertically disposed .slot 250 in the upper end of slide 238. Normally, pin249 is in contact with iihB upper end of the slot 250, which is of a length sufficient to enable the rocking of clutch control shaft 69 by the rocking of trip member 251 (FIG. 3), upon passage of other mail matter, such as envelopes, into the metering device. It can be seen, however, that upon actuation of the rack supporting plate 106 (to the left in FIG. 6) by virtue of the engagement ofactuator slide Mil witheither pin 14% or the initial. part ofthe movement will cause arm 235 to be rocked clockwise (FIG. 2) to engage pin 236 with the upper edge surface of the extension 237 of slide 238.- Upon further movement of the plate 1% to the left for the limited extent of its travel, the-rocking of arm 235 moves slide 238 downwardly, thereby imparting a clockwise rotation to the clutch control shaft 6% to effect engagement of the cyclic clutch 25. The extent of the lost motion of pin 23 5, prior to its engagement with the upper edge surface of the extension 237, is suiiicien-t to enable the tape feed roller 86' to move the leading edge of the tape T into frictional engagement with the surface of the feed belt 23,

between the belt and pressure roller 49. Thereafter, tape T is severed to selectively form either a short or long tape strip which is advanced by belt 23 to the printing station in proper timed relation to the rotation of the printing drums 26 and 27 for a postage impression thereon. 1 Following the actuation of" the rack supporting plate 166 to provide-either a short or a long tape and, upon termination of the rotation of the feedrollerfitl by the engagement of the nose 183; of arm 182 in either the notch-.128 or 129 and the corresponding notches 136 or 131 ofthe

respective disks

126 and 127, the impact of the nose 183 with the left-hand surface of the actively positioned notches would normally be 'sufiicient, under the influence of spring 184, to cause an angular counterclockwise rotation of the disks. Such backlash of the disks 1% and 12'? and, therefore, feed roller'Sd, would effect a retraction of the serrated end of the tape T from the cutting edge ofithe toothed portion 177 of cutter rod 176." Thus, a subsequent actuation of rack support ing plate 106 would either beinsuflicient'to move the leading end of theltape into frictional engagement with the feed belt 23, or the severed strip of tape'would be shorter than the desired length. such a condition, conventional means are provided for locking the feed roller 86 against rotation asthe nose 183 of arm 182 is urged into the aligned active notches of the

disks

126 and 127. I Referring to FIG. 1, arm 252 is carried by a hub secured on the outer end of cutter rod 176. At:itS lower In order to prevent end, arm 252 carries pin 253 extending to either side of the arm and secured in position by any suitable means, such as a threaded nut. The inwardly extended portion of pin 253 carries a roller which becomes effective, upon a predetermined angular counter-clockwise rocking movement of the arm 253, to engage the vertically disposed edge of arm 254 freely mounted for independent movement in an annular groove in the hub of arm 252 and positioned adjacent thereto. At its lower extremity, arm 254 is provided with the laterally projecting ear 255 adapted for engagement in either of the pair of diametrically opposed notches 256 in disk 257 secured on the end of feed roller shaft 90.

It will be recalled that upon the initial actuation of rack supporting plate 106, the disk 126 (FIG. 7) becomes effective to rock arm 182 and, therefore, cutter rod 176 counterclockwise to the inactive position thereof. Immediately prior to the disengagement of the nose 183 of arm 182 from the aligned actively positioned notches in

disks

126 and 127, a roller on the inward extension of pin 253 on arm 252 engages arm 254 to disengage ear 255 from the aligned notch 256 in disk 257, thereby enabling rotation of shaft 90 upon continued actuation of the plate 106. Following either 180 or 360 rotation of the disk 127 and feed roller 80 and the movement of the aligned notches into position for re-engagement by the nose 183 of arm 182, the clockwise rocking of the arm 182 and shaft 176 imparts a similar movement to arm 252. Thereupon, spring 258, supported at its one end on the outwardly extended portion of pin 253 on arm 252 and at its other end on arm 254, causes the arm 254 to be rocked clockwise, moving ear 255 into the aligned notch 256 of disk 257. Thus, further rotation of shaft 90 and feed roller 80 is precluded immediately prior to the abutment of the nose 183 of arm 182 with the left-hand surface of the aligned active notches in the

disks

126 and 127.

Conventional mechanism is provided for facilitating the threading of a new tape between

feed rollers

79 and 80, upon depletion of the tape supply roll 70. For this purpose, U-shaped bracket 86 (FIGS. 1, 4 and 6), keyed on shaft 78, is rocked counter-clockwise to, and is locked in, its inactive position by the engagement of pin 262 in notch 263 of latch lever 264. Thus, the feed roller 79 is moved out of engagement with feed roller 80. At the same time the rocking of shaft 78 becomes effective to rock the cutting portion 177 of cutter shaft 176 to its inactive position by means of arm 265 secured thereon

intermediate frame members

72 and 73. The rounded nose formed at the free end of arm 265 underlies ear 266 projecting laterally from the end portion of the substantially horizontally disposed arm of lever 267 secured on the end of shaft 268 suitably journalled for rocking movement in

frame members

71 and 72. Thus, it can be seen that upon movement of bracket 86 to its inactive position, the arm 265 rocks lever 267 clockwise (FIGS. 6 and 7) which, by virtue of the engagement of the bifurcation 269 in the end of the upwardly extended arm of lever 267 with the pin 270 on arm 182, imparts a counter-clockwise movement to the arm 182. The nose 183 of arm 182 is thereby removed from its engagement in the aligned notches of the

disks

126 and 127 and the cutter device 97 is disabled.

It will be recalled that upon removal of the nose 183 of arm 182 from active engagement with the aligned active notches in

disks

126 and 127, cutter rod 176 is angularly rotated to disable cutter device 97 and to also remove the ear 255 on arm 254 from its engagement with the actively positioned one of the notches 256 in disk 257 (FIG. 1). Thus, upon release of each of these locking means, tape feed roller 80 may be freely rotated. However, means are provided for preventing inadvertent rotation of tape feed roller 80 while U-shaped bracket 86 is in its inactive position, thereby ensuring retention of the alignment of the corresponding notches in the disks 14 126 and 127 and the alignment of notch 256 in disk 257 for re-engagernent by the nose of arm 182 and the ear 255 of arm 254, respectively. In order to lock roller against rotation at this time, a pair of diametrically op-' posed concave indentations, similar to 271 in FIG. 6, is provided in the peripheral edge of the disk 272 concentric with and secured on one end of the feed roller 80 (FIG. 8). Following each rotation of feed roller 80, or after each complete revolution thereof, one or the other of the indentations 271 will be in position to receive the arcuate edge 273 on the depending portion of leg 84 of U-shaped bracket 86, upon rocking movement of the bracket to its inactive position. Following the tape threading operation, latch lever 264 is depressed, releasing the U-shaped bracket 86 to the influence of spring 94, thereby restoring roller 79 into its active position relative to feed roller 80 and enabling the return of the nose 183 of arm 182 into the aligned active notches in

disks

126 and 127.

We claim:

1. In a tape feeding device, the combination of a source of tape supply, a feed roller for advancing the tape from said source of supply, a disk associated with said feed roller for rotation therewith having a series of peripheral notches therein, each notch representative of an angularly rotated position of said feed roller, a cutting means for severing the advanced portion of the tape to form a strip of a selected length, means engageable selectively in one of the series of notches in said disk operable to terminate the rotation of said feed roller in a predetermined angularly rotated position thereof and to effect operation of said cutting means, an actuating means for driving said disk movable differentially to control the angular rotation of said feed roller, means operable to control operation of said engageable mean subsequent to the operation of said actuating means, a power-operated means for effecting differential movement of said actuating means, and means settable to control the differential movement of said actuating means by said power-operated means.

2. In a tape feeding device, the combination of a source of tape supply, a feed roller rotatable to advance the tape from said source of supply, a first disk and a second disk, said first disk being associated with said feed roller for rotation therewith, said second disk having a lost motion connection with said first disk, each of said disks having a plurality of corresponding equiangularly spaced notches in the periphery thereof, the said notches in said second disk normally aligned axially of the disks with the corresponding notches in said first disk, and actuating means effective upon selective differential operation thereof to drive said second disk in one direction relative to said first disk through the lost motion connection therebetween and operable thereafter to effect rotation of said first disk by said second disk, a cutter for severing the advanced portion of the tape to form strips of each of a plurality of predetermined lengths, a power-operated means enabled by said first and said second disks and operable to lock said disks to retain said feed roller in each angularly rotated position thereof and to operate said cutter subsequent to the operation of said actuating means, a power-driven means for driving said actuating means, and means adjustable to determine the differential operation of said actuating means by said powerdriven means.

3. In the apparatus of claim 2, said actuating means comprising a gear means, a unidirectional clutch operable upon operation of said gear means to effect operation of said second disk and the rotation of said first disk, a rack means for driving said gear means operable upon differential movement from a normally inactive position to control angular rotation of said feed roller and operation of said power-operated means, and a restore means operable subsequent to the operation of said power-driven means and said power-operated means to restore said rack means to the inactive position.

4.,In the apparatus of claim 3, said power-operated means comprising a resilient means, and a detent means for operating said cutter rendered operable by said resili nt means for engagement in the aligned selective ones of the corresponding notches in said first and said second disks as determined by the differential movement of said rack means in accordance with the adjustment of said adjustable means,

5. In the apparatus of claim 4, wherein said rack means includes a plurality of pins selectively engageable by said power-driven means to control the differential movement of said rack means, one of said pins being normally ac ively engaged by said power-driven means and the otner of said pins being adjustable selectively by said ad 16 justable means from an inactive toan active position, and a manipulative means for controlling adjustment of said adjustable means.

References Cited by theExaminer,

UNITED STATES PATENTS 1,169,767 2/16' Bresnan 2 83244 X 7 1,504,419 8/24v Berkley 83241 X 1,748,940 3/30 Beach 83649 X 1,782,362 11/30 McArthur 83241 X 1,789,688 1/31 Rast et a1. 83242 X 2,220,256 11/ 40 Martindale 83'24'1 X 2,838,113 6/58 Cronell 83244 X 3,063,322 11/62' Thomas 83587 ANDREW R. JUHASZ, Primary Examiner.

Claims

1. IN A TAPE FEEDING DEVICE, THE COMBINATION OF A SOURCE OF TAPE SUPPLY, A FEED ROLLER FOR ADVANCING THE TAPE FROM SAID SOURCE OF SUPPLY, A DISK ASSOCIATED WITH SAID FEED ROLLER FOR ROTATION THEREWITH HAVING A SERIES OF PERIPHERAL NOTCHES, THEREIN, EACH NOTCH REPRESENTATIVE OF AN ANGULARLY ROTATED POSITION OF FEED ROLLER, A CUTTING MEANS FOR SEVERING THE ADVANCED PORTION OF THE TAPE TO FORM A STRIP OF A SELECTED LENGTH, MEANS ENGAGEABLE SELECTIVELY IN ONE OF THE SERIES OIF NOTCHES IN SAID DISK OPERABLE TO TERMINATE THE ROTATION OIF SAID REED ROLLER IN A PREDETERMINED ANGULARLY ROTATED POSITION THEREOF AND TO EFFECT OPERATION OF SAID CUTTING MEANS, AN ACTUATING MEANS FOR DRIVING SAID DISK MOVABLE DIFFERENTIALLY TO CONTROL THE ANGULAR ROTATION OF SAID FEED ROLLER, MEANS OPERABLE TO CONTROL OPERATION OF SAID ENGAGEABLE MEANS SUBSEQUENT TO THE OPERATION OF SAID ACTUATING MEANS, A POWER-OPERATED MEANS FOR EFFECTING DIFFERENTIAL MOVEMENT OF SAID ACTUATING MEANS, AND MEANS SETTABLE TO CONTROL THE DIFFERENTIAL MOVEMENT OF SAID ACTUATING MEANS BY SAID POWER-OPERATED MEANS.