US2345411A - Method and machine for operating on sheet material - Google Patents

Description

March 28, 1944.

i U uni-6 C. A. MOELLER METHOD AND MACHINE FOR OPERATING ON SHEET MATERIAL Filed Feb. 18, 1941 1.? in In II III 52 l R 4:11 11:: l:

8 Sheets-Sheet 1 Fa". II II kw d l-EZNCH KOUH! March 28, 1944. c. A. MOELLER 2,345,411

METHOD AND MACHINE FOR OPERATING ON SHEET MATERIAL mm m. 18, 1941 8 Sheets-Sheet 3 OCGWH NCOF'F vv- ||u l-H mnmu. nu i U 4 Search Room 5 8 2 March 28, 1944. Q A MOELLER 2,345,411

METHOD CHINE FOR OPERATING 0N SHEET KAI'BRIAL Find an. 18. 1941 a Sheets-Sheet 4 March 28, 1944. c. A. MOELLER METHOD AND MACHINE FOR OPERATING ON SHEET MATERIAL Filed Fob. 18. 1941 8 Sheets-Shoot 5 050mm Hu warm K00 March 28, 1944.' c. A. MOELLER 2,345,411

METHOD AND CHINE FOR OPERATING 0N SHEET MATERIAL Filed Feb. 18, 1941 8 Sheets-Sheet 6 March 28, 1944. Q MOELLER 2,345,411

METHOD AND MACHINE FOR OPERATING ON snns'r MATERIAL Filod Feb. 18, 1941 8 Sheets-Sheet 7 cooooooo Q; 2000 I 322 r A? March 28, 1944.

METHOD AND MACHINE FOR OPERATING ON SHEET MATERIAL C. A. MOELLER Filed Feb. 18, 1941 uuuiuil 8 Sheets-Sheet 8 40 fig/31 40 111% 381 I 30 42/ J6 38 42) M W l f@-22 ,a l u 5v? @Z-L 389%? 1 1 24 I L E 1: 4M.

WimesJ WM WW Patented Mar; 28, 1944 METHOD AND MACHINE-FOR OPERATING ON SHEET MATERIAL Carl A. Moellcr, Randolph; Masa, asslgnor to'No'r.

The present inven ion relates to methods and machines for operatl-g on sheet material, particularly a web of paper'or the like, and is primarily but by no means exclusively concerned nearlythat of the web itself, to avoid buckling or tearing of the material. If, in addition, a number of different operations are to be permaterial.

folk Paper 00., Inc., Randolph, l VIass a corporation of Massachusetts Application February 18,1941, vseriaiiixia.:iiaaaz 1 22 Claims. (01. ee -5&2)

ing 7 the operation .of'. the mechanisms .on. said.

Another object of the invention is .toprovide a method and a .machine for forming box: blanks at with machines for makingblanks which are sub- 5 high speed from .a continuously advancingweb sequently to be formed into boxes. of material, .particularlymdapted :for producing To attain the high production rate necessary accurately formed blanksiof variouszshapesand for economical manufacture of box blanks,-it is sizes. 4 a T': 3

essential that the various blank forming opera- Still anotherobject of athe'inventionlis to protions be performed at high speeds and as nearly 10' vide a machine'havingnovel and improvedzcutas possible automatically from start to finish. off mechanism, wherebysuccessive-sheets, of me- "While many of the machines heretofore devised determined length maybe rapidly and-accurately have been so arranged that the material, either -cut from a continuously advancing-web of matein web form or in individual sheets, is stopped at rial. 'j 1' I =one-or more of the various stations-at which the i5 rMore specifically, itlis =an obiect. of. the invenblank forming operations are performed, true tion toprovide in 'a machine employing a;rotathigh speed operationrequires that the material ing member for.operatinglperiodically; upon a pass through the machine continuously, either moving web of material,-novel mechanism for aca'succession of individual sheets, but prefer-- tu'ating said memberltooperateion the material ably in web form. Where the entire output of a at'adiustable predetermined intervals whilelcausmachine can be devoted to but one size of blank, ing the peripheral speed of themembenthrougha continuous feed type of machine may be devised out the period of operation onthe materiahto be without undue diiliculty. If, however, a machine substantially equal to the linear. speed 'of:the web. is to be capable of forming blanks of various sizes In accordance with these-and other objects as and still operate at high speeds, then serious willher'einafter appear,.a featureoftthe present problems are presented which have heretofore invention involves the-provisiomof amachinefor not been satisfactorily solved. The difficulties in forming box blanksfrom a continuously advancproviding such a machine willbecome apparent ing web of material,:the machine havinga plufrom the following considerations. a ty o Op a Stations for Operating P If sheets of various lengths are to be cut from 80 the materialas itpasses, rotating devicesat the "'-a continuously advancing web of material, or it stations for operation -upon -the material, and any given operation in theweb is to berepeated mean f rivi e rot in evic omp isat either longer or shorter intervals along the ins niformly rotatinsm a s' a t a d P webythen the frequency at which the operation cally to synchronize-the speed of ithe operating "is repeated must beadjustable, more often for rnember Wlththe peed 01' he Web ur ll the shorter lengths or spacing and less often for tim he members p a iv e e he we -longer lengths or spacing. In any case, however, As another feature. the invention comprises a. the speed of the web-engaging portion of the machine having mechanism'for' cutting off sheets operating device, during the period of operation of pre ete ed le l ffi ntin us y upon the web, must be so adjusted as to be very 4o vancing webof material the cut-ofi means-comprising a rotating blade driven by a worm .uniformly rotated at a speed such that the desired length of web is fedlbetween successive. cuts, the

' formed successively-onthe material, then besides worm being m d bodily during the cutting the adjustments above specified the spacing be 45 operation to synchronize-theperiphe l Speed 01 5c; tween the various operating stations must be adthe cutting blade with the linear speed'of the web. ii iustable longitudinally of the direction of feed of Other features ofthe invention include -n ove1 s the material. mechanism for forming slots in the advancing The present invention has as an object, therematerial transversely of the direction of feed, fore, to provide a method and a machine for per- 5 novel cieasingmechanism.forforming transverse forming a plurality of operations upon continufold lines inthe advancing .materiaLand other ously advancing sheet material, wherein the spacing-between, operations on the material may .beu'eadily adjusted Whi18, nevertheless-the movement of the operating mechanisms may be synzchronized with the advance of the material dill? I constructions and arrangements hereinafter described.

5 and rr n ed mroduc bQxJbIanksof-the type shown in United States Letters Patent No. 2,166,287 of C. Lloyd Clafl, although the machine may be so adjusted and arranged as to produce a wide variety of types of blanks, while in addition certain mechanisms of the machine are well adapted for use in many difierent types of machines which are required to operate upon moving material.

In the accompanying drawings illustrating the invention, Fig. 1 is a top plan view and Fig. 2 a side elevation of the complete machine; Fig, 3 is a top plan view of the web of material showing the effect of the various operations as the material passes through the machine; Fig. 4 is a side elevation, partly in section, on an enlarged scale, of a portion of the machine midway its ends; Fig. 5 is a longitudinal sectional view of the end or deliveryportion of the machine; Fig. 6 is a perspective of one pair of rolls for forming the longitudinal creases in the web; Fig. 7 is a perspective of the cutting mechanism for severing the individual blanks from the web; Fig. 8 shows in vertical, transverse section a pair of slotting or punching reels for cutting the transverse slots extending inwardly from the margin of the web, and Fig. 9 shows the same, partly in vertical longitudinal section, and at right angles; Fig. 10 is a perspective, with parts broken away, of one of the reels; Fig. 11 shows in transverse sectional view a pair of transverse creasing reels, and Fig. 12 is a longitudinal view, partly in section, of the same; Fig. 13 is a perspective view, with parts cut away, of one of the creasing reels; Fig. 14 is a perspective view of the driving mechanism for the various feeding and operating stations; Fig. 15 is a detail view, partly in section, of a portion of such mechanism; Fig. 16 is a view in elevation of one set of punching or slotting reels and a portion of the driving mechanism therefor; Fig. 17 is a detail sectional view of another portion of the driving mechanism; Fig. 18 is a top plan view of the positioning mechanism for adjusting one of the operating stations longitudinally of the machine frame; and Figs. 19 to 27 show a portion or section of the web as it appears at different stages in its progress through the machine.

The machine embodying the invention is arranged to form finished box blanks of the type described in the aforesaid patent in a continuous process from box blank materials supplied to the machine in web form from large rolls. The machine is made up of a number of stations, at certain of which the various blank-forming operations are performed, while at others the material is merely fed or guided. In the views of the complete machine, Figures 1 and 2, the various stations are identified as follows:

F-slotter for cutting second set of marginal slots.

G-feed rolls. H-creaser for transverse creases. I-creaser for first pair of longitudinal creases.

J-creaser for second pair of longitudinal creases.

K-feed rolls. L-cut-ofl for severing completed blanks. Mconveyer belt for removing severed blanks.

The various operations in the production of blanks like those of Patent No. 2,166,287 above referred to, as performed by the machine at diiferent stages in the passage of the materials therethrough, are illustrated in Figure 3 and on a larger scale in the detail views Figures 19-27 inclusive. The web of cardboard indicated at 30 is drawn from a supply 32 and is of a width equal to the desired length of finished blank which in cludes end wings and end wing extensions 34 and 36 respectively (see Figure 27). At station C slots 38 are cut in the margin of the cardboard, these being the slots for reducing the height of the corner laps 40 to provide flush sides and ends when the blank is set-up, as disclosed in the aforesaid patent.

At station D, reenforcing tapes 42 from rolls 44 are first applied along the edges of the cardboard over the slots 38 (Figure 21), and then cover pa per 46 from the web 41 is assembled with the tapes and cardboard (Figure 22), adhesive being applied to the tapes and cover paper by rolls 48 as the materials are drawn from the supply rolls. Next are cut the slots 50 through the assembly (Figure 23) to separate the corner laps 40 from the end wings 34, this being done at station F.

Transverse creases 52, which form the longitudinal fold lines for the side walls of the box, are produced in the assembly at station H, these creases being aligned with the marginal slots 38 and 50 (see Figure 24). Creases 54 and 56 for the end wing extensions and end wings are produced by longitudinal creasing rolls at stations I and J, while finished blanks (Figure 27) are severed from the web by the cut-off mechanism at station L and carried away by the conveyor belt at station M. Having indicated the nature and sequence of the various operations in the formation of one type of box blank, the machine itself will now be considered, the individual stations being treated in detail.

The mechanisms which make up the various stations are carried on side rails 60 which extend the full length of the machine, thus providing accurate alignment and spacing of the devices. The web is advanced through the machine of pairs of feed rolls 62 at stations D, G, and K, the roll shafts 64 being supported on pedestals 66 secured to the frame 60, with the upper rolls journalled in bearing blocks 68 urged downwardly under the pressure of springs 16 adjustable by stud 12 (see Figure 4). Intermeshing gears 14 connect the upper and lower roll shafts (see Figure 5), the lower shafts being driven in unison through gear boxes 16 from a feed roll shaft 18 extending along the side of the machine (see Figure 1). As illustrated at station K (Figure 5), the feed rolls may be separated slightly by means of a hook engaging the shaft and adapted to be raised by hand lever 82 acting through eccentric bearing 84 on pivot shaft 86.

The material is supported and guided in its passage to the first slotter, station C, and to the second slotter, station F, by means of channel members or guides 88 at stations B and E. The members 88 are moved inwardly or outwardly to accommodate various widths of web material while maintaining the web centrally positioned in the machine. For this purpose, cross rods 88 journalled in pedestals 92 (see Figure 4) are provided with left and right hand threads on opposite sides of the center line, with correspondingly threaded bearing blocks 94 carried by the rods and having the channel members secured thereto. Rotation of one rod of each pair by handwheel 88 simultaneously adjusts the other through sprockets 88 and connecting chain I00, insuring that the channel members 88 are always parallel and equidstant from the center line of the machine.

The creasing of the assembled web of cardboard, tapes, and cover material for the fold lines 54 and 56 is performed at stations I and J and is continuous along the web. The principal adjustment is therefore the positioning of the crease lines transversely of the direction of web advance. The creasing mechanism, best illustrated in Figures 5 and 6, comprises cooperating pairs of creasing rolls freely rotatable on cross shafts I02, the upper shaft being urged downwardly by springs and adjusting screws in the same manner as the feed rolls. The upper rolls I04 are formed with a bead or rib I06, while the lower rolls I08 have a complementary groove IIO into which the assembled blank materials may be forced by the rib I06 as the web assembly is fed between the rolls.

The rolls are adjusted transversely by means of rods II2 threaded in right hand direction on one side of the center line and in left hand di rection on the other side like the rods 90 for the web guides. The rods carry threaded nuts II4 to which are secured U-shaped members II6 between the arms of which the creasing rolls are axially positioned although freely rotatable. The nuts likewise have secured thereto extensions II8 which engage the rod at points spaced from the nuts to prevent twisting and binding of the nuts on the rods. The upper and lower rods of each unit are adjusted simultaneously by means of a hand crank I20 on the upper rod, which rotates the lower rod through gears I22 and idler I24.

The slotting operations which are carried out at stations and F are performed by slotting reels best illustrated in Figures 8, 9, and 10. Except for adjustment for different slot spacings, the slotting reels at the two stations are similar, those illustrated being adjusted to cut the slots 38, which, being nearest the longitudinal edges of the finished blanks, are more closely spaced in the continuous web. The upper reel, indicated generally at I30, is provided with knife blades I32 having serrated cutting edges I34, while the lower reel I36 carries shear plates or members I38 between which the blades enter during the slotting operation.

The slotting blades are carried on cross bars I40 secured at their ends to segments I42. The segments are provided with arcuate ribs I=44 which fit within annular channels I46 formed in the inner faces of the reel head I48. By loosening clamping screws I50 which pass through the arcuate slots II in the heads, the segments, and thus the slotting blades and cooperating shear plates may be readily adjusted about the periphery of the reel to change the position of the slots in the web. The reels are likewise bodily adjustable along their supporting shafts I52, long keys I54 maintaining the reels in fixed angular position on the shafts while set screws I56 secure the parts in adjusted position.

The blades are supported radially against the thrust of the operation through the provision on the cross bar I40 of shoulders I62 against which the inner edges of the blades rest. To permit the blades to rock slightly relative to their supporting bars I40 so that the blades may enter and withdraw from the shear plates I38 without catching or binding thereon, yielding connections are provided in the form of compression springs I64 between the heads of the securing bolts I68 and the blades I32. In normal position, with the blades in contact with the cross bars, the blades are not radially directed, but are inclined slightly (see dot and dash line I68 in Figure 8) in order that, on entering the work, the blades may be more nearly normal thereto. As the blades pass through the web assembly and enter between the shear plates I38, they are drawn away from their supporting bars against the force of springs I64, by reason of the greater radius of the path taken by the point of contact of the blades with the shear plates, as compared with the radius of the shear plates. Since both wheels rotate at the same rate, the outer portion of the slotting blades is retarded from its normal peripheral speed, the retardation accordingly increasing until the blades are fully withdrawn, whereupon they snap back to normal position against the cross bars preparatory to the next cut. Such arrangement, coupled with the fact that the shear plates I38 are shaped as at I10 to provide clearance back of their shearing edges within which the blades may rock, provides a smoothly running mechanism by which the slots may be accurately positioned and cleanly cut.

During the slotting operation, the central portion of the web of material is gripped by rolls I12 and I14 mounted on the shafts I52 between the slotting reels. The lower roll I14 is shown as cylindrical, while the upper roll I12 is provided with lands I16 which occupy arcs of a length somewhat greater than that of each pair of slotting blades. The radius of the lands is such that the material is gripped between the lower roll I14 and the lands I16 of the upper roll while the slotting is taking place, thus insuring synchronism between the peripheral speed of the slotting blades and the linear speed of the web, as will more fully be described hereinafter.

The creasing reels, for producing in the assembled materials the transverse creases which in the finished blanks are the longitudinal fold lines 52, are carried on supporting shafts I at station H. The reels, best illustrated in Figures 11, 12, and 1.3, are provided with circular heads I82 like those of the slotting reels. The heads I82 are keyed to the shafts and have formed in their inner faces annular grooves I83 to receive arcuate, bosses I84 formed in the ends of cross bars I86 having a segmental shape of section. The bars of the upper reel are formed with a transverse projecting bead I88, while the bars of the lower reel have a complementary groove I80 into which the blank forming materials are pressed by the bead. Like the slotting blades, the creasing bars are adjustable around the reels to provide the desired spacing of the creases, screws I92 passing through arcuate slots I93 in the heads serving to secure the bars in adjusted Position.

The cut-off mechanism (station L and Figures 5 and 7) employs a fixed cutter bar and a rotating cutter reel. The cutter bar, indicated at 200, is carried by a cross member 202 vertically adjustable in pedestals 204 by means of screws 206. The cutter reel comprises knife blades 2I0 secured to reel heads 2I2 which are keyed and clamped to the shaft 2I4 journalled in the pedestals.

The blanks, after being severed from the web by the cut off mechanism, slide onto an endless 'belt conveyer 2 I 6 driven by chain 2 I 8 and sprockets 220 from the lower feed roll shaft 64 of station K and are thus carried from the machine as fast as produced.

In order to permit adjustment of the spacing between the various operations which require positioning longitudinally of the web, such as the slotting, transverse creasing, and cut-oil, it is necessary that the stations themselves be bodily adjustable toward and from one another along the machine. Accordin y, while one station, in the case of the illustrative embodiment the first slotter, station C, may be fixed, the stations at F, H, and L are arranged to be movable bodily along the side rails 60 of the machine frame.

To this end, the pedestals for the operating mechanisms of -,the movable stations are formed on their under sides with guideways which fit over ways 224 mounted on the side rails 60 (see Figures 5, 7, and 18). A cross shaft 226 journalled in the lower portion of the pedestals carries gears 228 which mesh with racks 230 secured to the rails 60, so that upon rotation of the shaft by hand crank 232 the station mechanism may be moved as a unit along the rails. After the proper setting is obtained by reference to scale 234 and cooperating pointer 286, the pedestals may be positively clamped to the rails by studs 238.

The slotting, creasing, and cut-01f mechanisms at stations C, F, H and L are driven from a common shaft 240 extending along the right hand side of the machine as viewed in Figures 14 and 16. Worms 242 keyed to the shaft 248 (see Figure 4) mesh with gears 244 on the lower shafts of the operating devices at each station, the upper shaft being rotated by intermeshing gears 246.

The main or longitudinal drive shafts 18 and 240 are rotated from a common source of power, such as the electric motor 250, through variable speed driving mechanisms (shown in Figure 14) by which the speed of both shafts may be varied together, thus increasing or decreasing the speed of the machine as a whole, or the speed of drive shaft 240 varied relative to that of the feed r011 shaft 18, to increase or decrease the frequency of operations in relation to web travel, and thus change the blank width. The feed roll drive shaft 18 is driven by multiple V belt 252 from a countershaft 254 journalled in bearings 256, the countershaft in turn being connected by clutch 258 through a Reeves" type variable speed transmission to the driving motor 250. The transmission comprises countershaft pulley 260, V belt 262, and motor pulley 264, the latter having one fixed and one spring pressed, axially movable flange. The motor is raised or lowered to increase or decrease the radius of rotation of the belt around the motor pulley by means of hand wheel 266 which rotates screw 268 to advance or retract block 210, rocking motor platform 212 about its pivot 214 through links 216.

The drive shaft 240 on the right hand side of the machine is actuated through a second "Reeves" type variable speed transmission, the adjustable pulley 218 being carried on countershaft 254 and driving through V belt 288 a pulley 282 on a second countershaft 284 connected to the shaft 240 by multiple V belt 286. The speed of shaft 240 is controlled by hand wheel 288 which rotates threaded rod 290 (see Fig. to raise or lower arm 292 on which is mounted an idler pulley 284, thus decreasing or increasing the radius of operation of the belt 280 in the self-adjusting pulley 218.

In setting up the machine for the production of any given size of blank, the first variable speed transmission is adjusted to provide the desired speed of web travel, which determines the rate of production. Next the speed of drive shaft 240 is adjusted relative to the feed roll driving shaft 18 so that the desired spacing between successive operations of any one station is obtained, a decrease in blank size being obtained by increasing the shaft speed to permit less material to pass the station between successive operations thereof, while larger blank sizes are obtained by slowing down the frequency of operations. Having obtained the correct shaft peed, the stations whose devices are driven from the shaft 240 are adjusted along the machine frame as heretofore described so that the later operations in the blank forming sequence occur at the proper points on the web relative to the earlier-performed operations.

If it happens that the desired blank size is such that the spacing between successive operations is exactly equal to a semi-circumference of the various operating devices or reels, the devices will be rotated at a speed such that the peripheral speed of the operating devices is equal to the linear speed of the web, and the devices need merely be rotated at this uniform speed from shaft 248. In the majority of cases, however, the blank width will not be equal to a semi-circumference of the operating reels, and the reels will be turning at a rate such that their surface speed may be either faster or slower than the speed of the web. Accordingly, if the operations are to be performed without tearing or buckling the web, the speed of the devices must be altered so that, while each operation is being performed, the peripheral speed of the devices is made substantially equal to the linear speed of the web.

In view of the fact that certain of the operating devices, for example the slotters and the transverse creaser, require an appreciable portion of each half-revolution of the devices to complete an operation on the web, it is neces sary not only that actual synchronism be established but also that it be maintained for the duration of the operation. As a consequence, arrangements such as employed in simple cutting off mechanisms or flying shears wherein an operating device is constantly accelerated and decelerated, the operation being performed at that instant in the cycle of continually changing speed when the speed of the device and that of the material are equal, are of no value in the present machine, since synchronism cannot be maintained throughout the periods of operative engagement of the blank forming devices with the web.

In the machine of the present invention, mechanisms are provided which are adjustable, independently of either the longitudinal position of the operating stations or the speed at which they are driven by drive shaft 240, to cause the peripheral speed of the devices to be substantially equal to the linear speed of the web throughout the time interval during which each operation is taking place. During the period of time between operations, when the devices are out of engagement with the web, the speed of the devices is altered in the reverse manner, so that the actual frequency of operations, or number of revolutions per unti of time, is dependent solely on the speed or drive shaft 248, as determined by the second "Reeves transmission between counter-shaft 254 and shaft 240.

Periodic alteration in the speed of the blank forming devices is effected by moving the worms 242 bodily in an axial direction along the shaft 248, long keyways permitting movement of the keys 302 along with the worms so as to rotatably connect the worms to the shaft over a substantial range of axial movement. The worms, during their axial movement, operate in the manner of a rack, the rotative movement which they thus impart to the gears 244 during their axial movement being either additive or subtractive with reference to the rotation independently imparted thereto through rotation of the worms. In the present machine, the worms are given a reciprocatory movement axially, the major portion of the reciprocation being at a substantially uniform but adjustable rate and in timed relation to the rotation of the operating devices.

The worms are reciprocated in unison by a longitudinally movable connecting rod 304, which may be a hollow pipe or sleeve for lightness and hence reduced inertia. The rod extends substantially the length of th machine below and parallel to the drive shaft 240 on which the worms 242 are slidably arranged. The ends of the worms are engaged, with intervening thrust bearings 308, by sleeves 308 (see Figures 4 and 17) surrounding the driving shaft and within which the shaft is journalled, the sleeves being axially slidable relative to the shaft and to the worm and gear housing 3I0 carried by the pedestals of the operating stations. The outer ends of the sleeves are clamped in the upper ends of arms 3I2, the arm ends being bored and split for this purpose. The lower ends of the arms 3I2 are similarly arranged for securing to th connecting rod 384. A spacing rod 3I4 provided with reduced end portions 3I8 and clamping nuts 3I8 stiflens the assembly and prevents spreading of the sleeves 308.

To prevent the escape of lubricant from the gear housing along the keyways- 300, half-thickness or flush keys 328 are provided which extend beyond the ends of sleeves 308. The keys are secured to collars 322 which are in turn clamped to the drive shaft by set screws 324, sufficient spacing being left between the inner end of the keys to permit reciprocations of worms 242 and worm keys 302.

The connecting rod 304 is reciprocated longitudinally to shift the worms axially by cam actuated connections which are adjustable to vary both the magnitude and the direction of the alteration in speed. These connections comprise a cam disc 330 mounted on a cross shaft 332 which is driven from the lower shaft I52 of the first slotting station C, at twice the speed thereof, by chain 334 and sprockets 338 and 338 on shafts I52 and332 respectively (see Figure 16). The cam disc is provided with a cam groove 348 on one face thereof, which is engaged by a follower on a cam lever 342 secured to a rock shaft 344 (see Figures 4 and 16 carried in supporting bearings 348 and 348. At its outer end the rock shaft is provided with an arm 358 having a slot 352 extending from one end across the cen ter line of the rock shaft to the other arm end.

Mounted adjacent arm 350 is a cross head member 354 slidably mounted on upper and lower guide rods 356 and having secured in split sleeve 358 one end of the connecting rod 304,

UCQI DH The cross head member is provided with a vertical slot 388 within which is adiustably clamped a pin 382 provided with a roller 384 received within the slot 352 in the arm 350. By raising or lowering the connecting pin 382 in the slot, not only may the speed of the reciprocating stroke be altered, but its direction may be reversed, by moving the pin to the other side of the center line of rock shaft 344.

The cam groove 348 is shaped to provide a substantially uniform rise and fall throughout the major portions of its operating faces, in order that the worms may be moved at substantially uniform speed throughout substantially the duration of the reciprocating stroke. By reason of the fact that the cam disc turns one revolution for every half-revolution of the operating device, for example, of the slotting rolls shown in Figure 4, one portion of the cam groove, the rise" 338, is traversed by the follower when the slotting blades I32 and lands I18 are in engagement with the work, while the fall ass of the cam groove is traversed when the operating parts are out of engagement with the work. The rise portion of the groove occupies less than one-half a revolution of the cam disc for the reason that a pair of slotting blades and corresponding land engage the web for less than a quarter revolution of rotation, the inoperative or idle portions of each revolution being occupied by rotation of the device at a rate altered from the constant value condition in the opposit direction from that of the operative portion.

To relieve the cam and other parts of the worm reciprocating mechanism of the axial thrust developed in driving the operating devices by rotation of the worms, means are provided at each station to substantially offset the normal thrust of the worm. As shown in Figure 4, each gear housing 3I8 has secured to its under side a thrust sleeve 318 through which slides the spacing rod 3. The spring 312 sliding on said rod and bearing at one end against the sleeve 310 and at the other end against a nut 314 urges the sleeves 308 to the left with a force which may be adjusted so as approximately to balance the axial thrust of the worm to the right at the particular speed of rotation of drive shaft 240. Since each station is similarly equipped, as shown in Figure 2, the connecting rod 384 and its actuating mechanism need only withstand the forces involved in changing the speed of the devices.

In the design of the machine, the radius of such operating devices as the cut-off reel and the creasing and slotting reels is preferably chosen so that blanks of average or intermediate size are produced when the operating devices are running at constant speed with their peripheral speed equal to the linear speed of the web. If blanks are to be produced of larger size than this so-called average or intermediate size, then, for the same speed of web travel, there must be longer intervals or time between operations, and the spacing between stations must be increased. Also, since longer intervals of time between operations means slower rotation of the devices, the speed of the rotating devices must be increased for the duration of each operation. Accordingly, the connecting pin 382 will be moved from its "zero position in align ment with rock shaft 344 upwardly an amount depending on how much the blank size is to be increased.

Conversely, where the blank size is to be decreased, below that of the average or intermediate size, the spacing between stations will be decreased, and the drive shaft 240 speeded up so that each operation will occur more often, which means at more closely spaced intervals along the web. Since, however, the peripheral speed of the operating devices is now greater than the linear speed of the web, the connecting pin 362 will have to be moved to a position below the center of rock shaft 3, with the result that the devices are slowed down for the duration of each operation, and speeded up above normal for the remainder of the time.

As shown in Figures 1, 2, and 3, those stations which carry out on the material the actual blank forming operations are spaced, of necessity, several operations apart along the web. By so doing, however, a wide range of blank sizes can be produced without requiring extreme changes in the positions of the stations performing the later operations in the sequence. By having the stations spaced at some multiple of the spacing between operations, changes in size can be adjusted for by moving the individual stations to the nearest point where the operation is to be performed for the new size blank. It has been found in practice that the desired range in blank sizes may readily be obtained with but relatively short rangesof longitudinal adjustment for the individual stations, so that in many cases changes in the position of the stations do not require corresponding changes in the position of arms 3|! on connecting rod 304 by which the worms are reciprocated.

While the invention has been illustrated and described as embodied in a box blank machine of particular construction and arrangement, adapted for the production of one type of box blank, the invention is not so limited, but may be embodied in machines arranged to form blanks of other types and to carry out blank fonning operations according to various sequences of steps. Neither is the invention limited to a machine for operating on paper or like materials, since certain mechanisms of the machine are well adapted for performing other types of operations upon many different kinds of moving material.

Having thus described the invention, what is claimed is:

1. A machine for operating on continuously advancing sheet material, comprising a rotatable device adapted to perform an operation on the material, mechanism for rotating the device, comprising a worm rotated at uniform speed to space the operations of the device along the material, and means under control of the device-rotating mechanism for moving the worm axially during operation of the device on the material to synchronize temporarily the peripheral speed of the device with the linear speed of the material.

2. A machine for operating on continuously advancing sheet material, comprising a rotatable device adapted to perform an operation on the material, mechanism for rotating the device, comprising a member adapted to be rotated at a uniform rate to space the operations of the device along the material, and means actuated periodically by the device-rotating mechanism during successive operations of the device on the material for moving the member axially at a uniform rate to synchronize the peripheral speed of the device with the linear speed of the material for the duration of each operation.

3. A machine for operating on continuously advancing sheet material, comprising a rotatable device adapted to perform an operation on the material, mechanism for rotating the device,

5 comprising a worm rotated at a uniform rate to space the operations along the material, and means actuated by the device-rotating mechanism in timed relation to the rotation of the de vice for reciprocating the worm axially to synchronize the peripheral speed of the device with the linear speed of the material while the device is operating thereon.

4. A machine for operating on continuously advancing sheet material, comprising a rotatable device adapted to perform an operation on the material, mechanism for rotating the device, comprising a, worm, and means for periodically changing the rate of rotation of the device, said means comprising a cam and connections actuated therefrom for reciprocating the worm axially.

5. A machine for operating on continuously advancing sheet material, comprising a rotatable device adapted to perform an operation on the material, mechanism for rotating the device, comprising a worm, and means for periodically changing the rate of rotation of the device, said means comprising a cam and connections actuated therefrom for reciprocating the worm axially, said connections comprising a rocking member, a reciprocating member, and connections between the rocking member and the reciprocating member adjustable towards and from the pivotal center of the rocking member to regulate the axial movement imparted to the worm.

6. A machine for operating on continuously advancing sheet material, comprising a rotatable device adapted to perform an operation on the material, mechanism for rotating the device, comprising a worm, a driving shaft for rotating the worm at a uniform rate, means for reciprocating the worm in an axial direction along the driving shaft to change the rate of rotation of the device, and resilient means for supporting 45 the reciprocating means against the axial thrust of the worm through rotation thereof.

7. A machine for operating on a continuously advancing, web of sheet material, comprising a plurality of operating stations spaced longitudinally of the direction of the web advance, rotatable devices at certain of the stations adapted to perform repetitious operations at spaced intervals along the web, mechanism for operating said devices comprising a worm at each of said stations, a common shaft for rotating the worms at uniform speed, and means for reciprocating the worms axially during operation of the devices on the web to temporarily change the speed of the devices to effect substantial synchronism between the peripheral speed of the devices and the linear speed of the web.

8. A machine for operating on a web of continuously advancing sheet material, comprising a plurality of operating stations arranged longitudinally of the direction of web advance, and having rotatable devices adapted to perform repetitious operations at spaced intervals along the web, said stations being adjustable longitudinally of the direction of web feed to change the spacing between operations, means including a worm at each station and variable speed driving mechanism therefor for spacing successive operations of each station at predetermined intervals along the web, and synchronizing means for effecting, 5 during the period of operation of the devices on the web, substantial synchronization of the peripheral speed of the devices with the linear speed of the web, said synchronizing means comprising means for bodily moving the worms in an axial direction during said operating period.

9. A machine for operating on sheet material, comprising feed rolls adapted to be rotated to advance the material, a device adapted to be rotated to perform an operation on the material, means for rotating the feed rolls, means including a rotating worm for rotating the operating device, speed controlling means comprising mechanism for changing the speed of the feed rolls, mechanism for changing the speed of rotation of the worm to vary the rate of rotation of the rotating operating device relative to the feed rolls and thereby change the distance along the material between successive operations of the device, and mechanism operative on the worm to move the same in an axial direction during operation on the device on the material to cause the worm to drive the device temporarily at synchronous speed relative to the linear speed of the material.

10. In a machine for operating on moving sheet material, mechanism for creasing the material transversely of its direction of movement, comprising cooperating rotatable creasing reels adapted to engage opposite sides of the material, said reels comprising head members and transversely arranged creasing bars, the head members having annular channels formed in the inner faces thereof, arcuate bosses on the ends of the creasing bars fitting within the annular channels in the head members, and means for securing the bars to the head members in peripherally adjusted position.

11. In a machine for operating on moving sheet material, mechanism for slotting the material transversely of its direction of movement comprising cooperating rotating Weds adapted to engage opposite sides of the material, one of said reels comprising head members, crossbars carried thereby, slotting blades carried by the cross-bars, means or r1 y supporting said blades against radially directed thrust, and connections for securing the blades to the crossbars arranged to permit slight yielding movement of the blades peripherally of the reel.

12. In a machine for operating on moving sheet material, mechanism for slotting th material transversely of its direction of movement at ad justably predetermined intervals, comprising rotatable cooperating creasing reels arranged on opposite sides of th a a, a slotting blade and cooperating shear blades carried by the reels, means for rotating the reels at a rate to space the slots along the material, means for altering the speed of the reels during a portion of each revolution thereof to substantially synchronize the peripheral speed of the reels with the linear speed of the material, and means rotating with the reels adapted, during such times, to engage the material to aid in maintaining synchronism between the reels and the material.

13. The method of operating upon a Web of box material continuously advancing at a uniform rate to form varying sizes of box blanks by means of a series of continuously rotating blank forming devices, which method consists in varying the spacings of the devices longitudinally of the said advancing web in accordance with such blank sizes, and temporarily altering such normal rate of rotation to synchronize the peripheral speed of the devices with the linear speed 76 of the web while said devices are operating upon the web.

14. A machine for operating on sheet material comprising a plurality of feed rolls, means for rotating the rolls to advance the. material at a uniform rate, a plurality of stations having operating devices adapted to be rotated to perform operations on the moving material, mechanism rotating at a uniform rate for rotating the operating devices, means for periodically reciprocating said mechanism axially to alter simultaneously the speed of the rotating devices to synchronize their peripheral speed with the linear speed of the material during operation of the devices thereon, and speed control means including mechanism for adjusting the speed of rotation of the feed rolls, mechanism for adjusting the speed of rotation of the mechanism rotating the operating devices at a uniform rate to change the spacing between successive operations on the moving material, and means for adjusting the velocity of reciprocation of said rotating mechanism to vary the magnitude of periodical alteration in speed of the operating devices.

15. A machine for operating on a web of sheet material, comprising a plurality of feed rolls for advancing the material at a uniform rate, a plurality of operating stations arranged longitudinally of the direction of web feed and having rotatable devices for performing repetitious operations on the moving material, said stations being adjustable longitudinally of the direction of web feed to change the spacing between operations, mechanism rotating at an adjustable uniform rate for operating the rotating devices at a speed to space successive operations of each station at predetermined intervals along the material, said mechanism including driving connections to the rotating devices arranged to permit independent longitudinal adjustment of the individual stations without change in relative angular position of said devices, and means operating periodically through said driving connections to alter in unison the speed of the rotating devices during operation on the material to synchronize their peripheral speed with the linear speed of the web.

16. The method of operating upon a web of sheet material continuously advancing at a uniform rate by means of a plurality of continuously rotating devices, which method consists in imparting to said devices a normal rate of rotation to space successive operations of each device on the web a predetermined distance, spacing the different devices longitudinally of the direction of web advance in accordance with the spacing between successive operations of a single station to effect registration of the different operations on the web, and temporarily altering such normal rate of rotation of the devices to a value synchronizing the peripheral speed of the devices with the linear speed of the web while said devices are operating on the web.

17. A machine for operating upon a web of sheet material, comprising a plurality of feed rolls for advancing the material at a uniform rate, a plurality of operating stations arranged longitudinally of the direction of feed of the material and having rotatable devices for performing repetitious operations on the moving web, driving means for rotating the devices at an adjustable uniform rate to space successive operations of each device along the web of moving material, said operating stations being adjustable longitudinally of the direction of web feed to change the spacing between operations of the different cm li'OOll devices in accordance with the spacing between successive operations of a single device, and supplementary means for temporarily varying the rate of rotation of said devices to synchronize the peripheral speed of such rotating devices with the linear speed of the advancing web material while the devices are operating thereon.

18. A machine for operating upon continuously advancing sheet material, comprising a rotatable device adapted to perform an operation on the material, mechanism for rotating the device including a worm, a gear driven by said worm and connected with the rotatable device, a shaft for supporting the worm, means for rotating the worm at a uniform speed independently of axial movement thereof, and means engaging the worm and actuated by the deviceu'otating mechanism to impart reciprocating movement to the worm in an axial direction in timed relation to the rotation of the device independently of the rotation thereof.

19. A machine for operating upon continuously advancing sheet material, comprising a rotatable device adapted to perform an operation on the material, mechanism for rotating the device including a worm, a gear driven by the worm and connected with the rotatable device, a shaft on which the worm is mounted in rotatably connected but axially slidable relation, driving means for rotating the shaft at a uniform speed, and means actuated by the device-rotating mechanism for periodically moving the worm axially along the shaft in timed relation to the rotation of the device to modify temporarily the speed of rotation of the device, said means including connections engaging the worm in relatively rotatable but axially fixed relation.

20. A machine for operating upon a web of continuously advancing sheet material, comprising a plurality of operating stations arranged longitudinally of the direction of web advance and having rotatable devices for performing repetitious operations on the moving material, a shaft extending in the direction of web advance, a worm gear on the shaft at each operating station, gears driven by the worms and connected with the rotatable devices, said worms being mounted on the shaft in rotatably connected but axially slidable relation, driving means for rotating the shaft at a uniform speed, and means for moving the worms axially to modify temporarily the speed of rotation of the devices, said means comprising a member arranged in parallel relation to the worm-supporting shaft, connections between the member and the individual worms for axially positioning the worms on the shaft, and means operating in time-controlled'relation to the rotation of the devices for actuating the member to move the worms simultaneously along the shaft.

21. In a machine for operating on moving sheet material, mechanism for slotting the material transversely of its direction of movement comprising cooperating rotatable slotting reels, one of said reels being provided with slotting blades and the other reel being provided with shear plates, between which plates the slotting blades are adapted to enter and withdraw, the former reel being provided with blade supporting bars each having a shoulder to receive the radial thrust of the blade, headed studs passing loosely through the blade and fixed in the bars, and spring members interposed between the headed studs and the blades for yieldingly holding the blade against the bar to permit slight angular movement of the blade upon its supporting shoulder as the blade enters and withdraws from its cooperating shear blades.

22. The method of periodically synchronizing the peripheral speed of an operating device driven by gear and uniformly rotating worm with the linear speed of continuously advancing material upon which the device operates periodically, which consists in automatically imparting to the worm, in timed relation to the periodicity of operations of the device, axial movements of such direction and velocity that the resultant rotation of the gear drives the operating device periodically at peripherally synchronous speed with respect to the advancing material.

CARL A. MOELLER.

CERTIFICATE OF CORRECTION Patent No. 2515,1 11. March 28, 191i.

CARL A. MoELLER.

" It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows: Page 2, second column, line 1+7, for "or" first occurrence, read "by"; page 3, first column, line 5, for "equidstant' read --equidistant-; page 5, first column, line 28, for "guides read -guides 88"; and second column, line 16, for "wheels' read --reels--; and that the said Letters Patent should be read with this correction therein that the same may conform tothe record of the case in the Patent Office.

Signed and sealed this 50th day of Ma A. D. 192 1;.

. Leslie Frazer (Seal) Acting Commissioner of Patents.

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