US2208350A - Cutting apparatus - Google Patents

Description

July 16, 1940.

I G. A. UNGAR CUTTING APPARATUS Filed June 18, 1937 6 Sheets-Sheet 1 1N VENT OR. gusl'azrca. Lima ATTORNEY.

y 6, 1940. G. A. UNGAYR 2,208,350

CUTTING APPARATUS Filed June 18, 1937 6 Sheets-Sheet 2 Fig: 4

July 16, 1940.

G. A. UN GAR CUTTING APPARATUS Filed June 18, 1937 6 Sheets-Sheet 5 INVENT OR. gusl'are a. War

i ATTORNEY.

July 16,1940 5,- UNGAR 2,208,350

- 'v CUTTING APPARATUS Filed June 18, 1937 6 Sheets-Sheet 5 I J61 $5 v I 3 1 v INVENTOR.

' gustav'e a. urge!" BY 4 4v ATTORNEY.

July1'6, 1940. QAUNGAR 2, zos,350

CUTTING, APPARATUS Filed June 18, 1-937 6 Sheets-Sheet 6 IN VENT OR. gztsl'a re a. Ilwar BY I V ATTQRNEY.

Patented July 16, 1940 UNITED STATES PATENT OFFICE.

CUTTING APPARATUS York Application June 18, 1937, Serial No. 148,892

9 Claims. (Cl. 164-68) My invention relates to novel means of and apparatus for cutting corrugated board or sheet material and more particularly to continuously operating knives arranged to be driven in synchronous speed with the sheet material during the cutting operation.

In cutting corrugated board, for instance, as it is being fed from the corrugator it is necessary, where continuously driven knives are to be employed, that provision be made for varying the speed of the knives during the cutting period as the cycle of the knives are changed for different sizes of sheets to be cut. Thus, for example, if

the knife drums are rotating at a speed which 15 will produce synchronism between the knife and the paper for one size length of sheets to be cut, it will be obvious that for another size the necessary changes in the period of the cycle of the knife drum will, unless there is a change within 20 the cycle itself, result in a non-synchronous condition between the knife and the moving sheet.

In order to overcome this, it has been proposed that involved elliptical gears be employed which can be shifted angularly so that the speed dur- 25 ing a single cycle is varied, always resulting in a synchronous speed or at least an approximate synchronous speed during the cutting period.

More recently such elliptical gears arrangement has been considerably improved upon by hydraulic transmission and other forms of drives.

In general, however, these systems are expensive and lack the positive operation which is desirable in these machines. I have discovered that, by the proper interlinkage between the drive and the driven member, which links are adjustable, I may change the speed during a cycle for producing synchronism during the cutting in- .terval without sacrificing any positive action in the drive connection.

Attempts to accomplish this heretofore have not only been complicated and costly but failed to provide corresponding adjustment for insuring synchronous speed between the knives and 45 sheet material during cutting for all sizes of material.

Accordingly an object of my invention is to provide a novel apparatus for and method. of cutting corrugated board.

50 A further object of my invention is to provide an interlocking pin and slot drive connection for obtaining variable speeds during a single cycle.

to insure. synchronism during the cutting inter val. 55 Still a further object of my invention is to provide a wide range of adjustments which will enable any desired length of material to be out while insuring synchronism during the cutting interval.

Still another object of my invention is to pro- 5 vide a novel speed adjustment between a driving and driven shaft.

Another object of my invention is to provide means for adjusting the axial relation between two shafts for obtaining speed variations there-. between in a cycle.

There are other objects to my invention which, together with the foregoing, will appear in the detailed description which is to follow in connection with the drawings in which:

Fig. 1 is a perspective view of one form of I my invention employing a link connection.

Fig. 2 is a cross-section through 2-2 of Fig. 1.

Fig. 3 is a detail of Fig. 2.

Fig. 4 is a perspective view of another form of my invention employing a pin operating in a slot.

Fig. 5 is a perspective view of another form of my invention.

Figs. 6 to 13 are illustrations showing the link and slot operations for difierent adjustments of Figs. 1 and 4.

Fig. 14 is a set of curves showing the relation between the movement of the control member of the variable speed transmission and the axial movements of the drive shafts.

Figs. 15 to 19 are schematic illustrations of other methods for obtaining synchronism between the knife and paper in a continuous knifecutting machine.

Figs. 20 and 21 are schematic illustrations showing the movements of the knives for the construction shown in Figs. 18 and 19.

Referring now more specifically to Fig. 4, I have disclosed the usual Reeves drive II comprising the cones l2 and 13 joined by the continuous belt It. The cone I3 is mounted on the main drive shaft I5 from which power for operating the mechanism to be described is obtained. Secured to and rotatable with the shaft I5 is a sprocket I6 which engages the sprocket chain I1 which in turn rotates sprocket wheel I8 mounted on the shaft I9 which carries thereon the feed roll 20 cooperating with the upper feed roll 2|. Between the feed rolls 20 and 2| the web 22 is advanced forward in the direction indicated to be cut in predetermined lengths by the knives 23 and 24 mounted on drums 25 and 26 respectively. v

The cone I2 is mounted on and drives the shaft 3| which carries on its end a sprocket wheel 32 carrying the sprocketchain 33 the opposite end of which meshes with the sprocket wheel 34. Sprocket wheel 34 in turn is keyed to shaft 35 which carries at one end thereof gear 36 which through the idler gear 31 with which it meshes drives the gear 38. The gear 38 is keyed to the shaft 39 one end of which carries a To one end of the crank 4! and excrank 4|. tending substantially at right. angles from the plane thereof a pin 42 is secured and is arranged to drive the bifurcated crank 43 in which it is I slidably positioned. 'I'he bifurcated crank 43 in turn is keyed to the shaft 44 which carries at the other end thereof the knife drum 26 bearing the knife 24. A gear 44' also keyed to shaft 44 meshes with and drives a gear 45 which is keyed to the shaft 46 which carries rotatably therewith the drum 25 of the knife 23.

From the above, the normal operation of the machine, without taking note of the adjustments hereinafter described, will be clear.

the gear 38 is rotated, in turn driving the shaft 39 and the crank attached thereto 4| together with the pm 42 about the axis of shaft 39 as a center. As the pin 42 rotates about the shaft plained hereinafter, is adjustable with respect to the fixed knife shaft, is below the shaft 44 as in the present case; it will be obvious that angular velocity e'of the shaft 39, when the crank 4| and the pin 42 reach theposition shown in Fig.

4 with the pin 42"just above the shaft 44 and at its closest approach to shaft 44, will produce an angular velocity T9 of shaft 44 which is greater than theangular velocity 6 of shaft 39 due to the fact that the driven shaft 44 has a smaller.

acting radius than the driving shaft 39 in the position shown, the relationship between the angular velocities of the shafts 39 and 44 being in fact a ratio r of the acting radii.

9=angular velocity of shaft 39. r=acting radius of shaft 39 acting radius of shaft 44. re=angular velocity of shaft 44.

It will be obvious that in every position of crank 4| and pin 42 within the bifurcated member 43,

the relationship between the angular "velocities of shafts 39 and 44 will be a function of the ratio 1' between the acting radii of shafts 39 and I Thus, when the pin 42,inthe course of its revolution, has turned 45 from the position illustrated in Fig. 4, itwill be obvious that the said pin 42 will have slid outwardly in the slot of the bifurcated member 43 and away from the'shaft 44, and the acting radius of shaft 44 will increase approaching the acting radius of shaft 39 so that the ratio r between the acting radii will become smaller and the angular velocity re of shaft 44 willbe reduced.

Finally, when the pin 42 has turned to a position beneath the shaft 44, the pin 42 will have slid in the slot of bifurcated member 43 toward its outermost position and away from the shaft As the Reeves drive transmits powerover the shaft 3| 44, and the acting radius of shaft 44 will have increased so that it will be greater than the acting radius of shaft 39 so that the ratio r between the acting radii of shafts 39 and 44 will be less than a unit, and the angular velocityv T6 of shaft 44 will be less than the angular velocity of I shaft39.

In this manner the angular velocity of the rotation of the shaft 44 throughout a Single revolution is changed and the particular position of the shaft 44 at which it is rotating in synchronism with the paper may be predetermined in order to set the knives for cutting during this period. c

When now it is desired to change the length of the cuts (and to this end the Reeves drive is changed for either decreasing orincreasing the R. P. M. of the knife drums 25 and26), therelative position of the pin 42 within the slot of the bifurcated member 43 at the cutting period is correspondingly changed by shifting or adjusting the position of the shaft 39 (about which pin 42 rotates) with respect to the'shaft 44. That adjustment will now be described with reference to the Reeves drive.

It will benoted thatthe bifurcated member 5| is mounted for axial movement on the screw 52 which is manually driven through the handle 53. The screw 52 is part of shaft 52' which carries at its opposite end a screw 54 on which a nut 55 is arranged for axial movement. Extending from the nut 55 is pin 56 extending in the slot formed by the bifurcated member 51 which is carried on the shaft '58 suitably supported in a bearing 59. The shaft 58 carries a crank 6| rotatable therewith: to the opposite end of crank 6| thereis'secured a link 62, the other end of which is secured through a pinv 63 on the slidable frame 64 which is adapted to slide in the channel 64'. Frame 64 has a curved slot 65 in which there is slidably mounted a roller follower 66 connected through a pin 61 to the lever 68 which rotatably carries the shaft 69 on which is secured the idler3'l and which lever may also turn about the shaft 69 as a fulcrum. At the other end of the lever 68 the shaft 39 is rotatably mounted. I

When the handle 53 is rotated the bifurcated or decrease the R. P. M. of the knife drums in a manner now known in the art. Simultaneously the screw at the opposite end 54 will, move the nut 55 axially and through the bifurcated member 51 cause the link 62 to move block 64. De-

pending upon the direction in which block 64 is moved, the roller follower 66 will be raised or dropped by reason of the curvature-of the slot 65 and will move .the lever 68 about 69 as a pivot causing a movement of the shaft 39 toward or away from the shaft 44 in a plane at right anles to the axes of such-shafts, the said axes,

however, remaining parallel to each other.

It is now assumed that the knife drums are approximately 9.5 inches in diameter when measured on a line running from the knife edge through the axis, or that they are thus exactly 30 inches in circumference; and that the paper moves past the knives at the rate oflOO feet or 1200 inches per minute. It isfurther assumed that the size of sheets desiredto be cut is 126 inches. It is obvious that the knife drums should revolve at the rate of 10 R. P. M. so that the knives will perform ten cutting operations per minute. It is further assumedthat the perma nent' ratio selected between shafts 3| and 39 is "five to one; therefore, to produce 10 R. P. M. on

the knife drums, an output speed of 50 R. P. M. is required on shaft 3| of the Reeves drive.

It is obvious, however, that with 10 R. P. M. of the knife drums whose circumference is 30 inches, the average angular velocity at the circumference of the drums where the knives are located is only 300 inches per minute or exactly one fourth of the speed of the paper. Unless the speed of the knife drums can be increased to the speed of the paper at the time of cutting it will be apparent that the knives will tend to rip or tear. the paper and that they will not make a clean cut.

The means for varying the speed of rotation of shaft 44 previously described are now applicable here. In Figs. 6, 8, 10 and 12, I have disclosed these movements of the shaft 39 which are effected by the adjustments made through the screw 54. When, as shown in Fig. 6, the shaft 39 is adjusted for its maximum position away from shaft 44, the ratio between the acting radii of shafts 39 and 44 at the moment when pin '42 is intended to be directly above shaft 44 will be four to one.

At that moment the angular velocity of the shaft 44 will be: 119 as previously described; and making the proper substitutions for the symbols, the angular velocity of shaft 44 at the knife edge circumference of the knife drum will be 4x 300, or 1200 inches per minute. .It will be obvious I that G can also represent merely the rate of revolutions per minute at a given moment so that taking 9 as we would get a rate of 40 R. P. M. of shaft 94 at the moment when pin 42 is directly above shaft 44 and thus arrive at the angular velocity of 1200 inches or 100 feet per minute in the same manner.

As the position of pin 42 relative'to the axis of shaft 44 changes during a single revolution, the speed of the knife drum decreases as the acting radius 44-42 increases due to the sliding movement of the pin 42 in the slot formed by the bifurcated member 43. Therefore, for each revolution, the average speeds of shafts 39 and 44 are equal.

In the illustration given, with the assumption of the paper moving at the rate of 100 feet or 1200 inches per minute, it is obvious that 40 R. P. M. of the knife drum will produce 30 inch lengths. If, however, the knife drum is 30 inches in diameter, then at 40 R. P. M., the average velocity of the circumference ofthe knife drum is the same as that of the paper so that no variations in the speed of shaft 44 will be required and it need only revolve (as hereinafter explained) in the same manner as the shaft 39 which will be adjusted by the Reeves drive to turn at .40 R. P. M.

Inasmuch as the cutoff lengths assumed in the previously detailed example however were to be the knife speed to the speed of the paper at the time of cutoff it was necessary during this period to obtain a speed on the knife drumouadruple the speed of shaft 39. Thus, the knife drums are arranged for their cutting operation when the shafts 44 and 39 and. the pin 42 are in the relative positions shown in Fig. 6.

When the Reeves drive is adjusted to obtain cutoffs of, let us say, 60 inch lengths, it will be obvious that with the speed of the paper remainthe same, the knife drums must revolve at an average rate of 20 R. P. M. in order to produce twenty cutting operations per minute. Thus the angular velocity of the knife drums previously described will be, at their circumference, just half the speed of the paper. The screw 54 is so designed for this adjustment of the Reeves drive that through a movement of the link 62, a corresponding rotation of the lever 68 about the shaft 69 is obtained moving the pin 42 to the position shown in Fig. 8 for the period of cutoff. In this position of the pin 42 and shafts 39 and 44, the necessary ratio between center-to-center position of shaft 39 and pin 42 on the one hand and shaft 44 and pin 42 on the other hand must be two to one.

Applying the formulae previously set forth,

or a speed of 1200 inches per minute, the exact speed of the paper.

And, apart from the formulae, for 60 inch lengths, the shaft 39 must be rotated at half the speed at which it would rotate for 30 inch lengths, so that the speed of the knife drums must be double the average speed of shaft 39 at the cutoff interval. This condition obtains due to the above ratio of two to one as described.

When, for example, it is desired to cut off 40 inch lengths, the adjustments obtained through the screw 54 and link62 for rotating the lever 99, is such as to position the pin 42 as shown in Figure 10 in which the center-to-center positions from shaft 39 to pin 42 and shaft 44 to pin 42 is in the ratio of four to three. It will be obvious, that with the speed of the paper still remaining the same, the knife drums must nevertheless rotate at an average R. P. M. of 30, so that their average angular velocity at the circumference by reason of the 30 R. P. M imparted by shaft 39 is 900 inches per minute.

Thus, again applying the formulae previously set forth,

driven so that average speed or angular velocity of the circumference of the knife drums is slower than the speed of the paper and accordingly a radial ratio of four to three as shown in Fig. 10 must be obtained at the instant of cutoff.

The limit or normal condition is obtained for 30 inch cutoffs. Here it is obvious that 4 0 R. P. M. of the knife drums will produce the proper sizes. But since the circumference of the knife drums is 30 inches, the angular velocity of the knife drums produced by shaft 39 is 0:1200. Accordingly. a ratio of one toone at all times between the speeds of shafts 39 and 44 are required, and

this is obtained as illustrated In Fig. 12 by placing the shafts 39 and 44in coaxial relationship. In this condition, the radius from the center of shaft 44 to the center of pin 42 remains constant throughout the entire revolution of the shafts.

It will be obvious that the ratio selected between shafts 3I and 39, that of five to one, is not an essential ratio: and that it may be any other ratio which will make possible various adjustments of the Reeves drive to produce a desired speed on shaft 39; it being obvious however that for different ratios between shafts 3I and 39, different curvatures of the slot 65 may be necessary. However, for any specific dimension of the knife drums and any specific speed of the paper, the radial ratios between 39-42 and 44-42 must be specific and definite for each specific size to be cut.

It will further be obvious that, in the illustration given, in order to obtain cuts shorter than 30 inches inlength, it will be necessary to increase the speed of shaft 39 and to correspondingly raise the said shaft 39 to a position even above shaft 44 so that it will be higher than in the position shown in Fig. 12.

The specific dimensional limitations hereinbefore described are of course illustrative and are not intended to constitute alimitation upon the operation of my knife-cutting machine.

Adjustments of the connections from screw 54' to the lever 68 can be obtained for properly positioning the shaft 39 with respect to the shaft for every desired size of sheet to be cut by the knives 23 ,and 24. In order to efiect this I have found that corresponding changes in the Reeves drive for producing different sizes of cutoff sheets do not require the same corresponding adjustments of the lever 88, the adjustments of the lever 68 being greater than the proportionate change of theReeves drive for one size cutoif than for another.

In Fig. 14 I have shown a set of curves which illustrates this. As shown in the curves, for doubling the speed of the Reeves drive from 50 R. P. M to R. P. M. it 'is necessary to turn the handle 53 through approximately seventeen revolutions whereas for increasing the speed of the Reeves drive from 100 R. P. M. to 200 R. P. M. .it is necessary to turn the handle or Reeves control screw through approximately 10 revolutions. From the above description however, it will be noted that for each doubling of the output of the speed of the Reeves drive a corresponding constant linear movement of the pin 42 is necessary. Thus for example, in" changing the Reeves drive from 50 R. P. M. to 100 R. P. M. a distance L linear adjustment of the shaft 39 was necessary. In changing the Reeves drive from 100 R. P. M. to 200 R. P. M. an additional distance of 2L movement of the shaft 39 is necessary as indicated in Fig. 12. In order, therefore; to

maintain the proper linear movement of the shaft 39. in spite of the'decreased number of turnsnecessary for the Reeves control screw at the higher speeds I have provided the cammed slot 65 in which the roller 65 moves for increasing the ratio of linear movement of the shaft 39 for every turn of the Reeves control screw at the higher speeds. r

In Fig. 1 I have illustrated a modified form of the-principle enunciated in connection with Fig. 4, the main distinction being in the use of a link connection between the driving shaft I39 and the knife drum shaft I44. As in the case of 4 a Reeves drive III is employed comprising t e cones H2 and I I3 mountedon their respective shafts H5 and I3I and having the drive belt H4. As in the previous illustration the roll I 2I of feedrolls I20 and I2I is driven from the sprocket II Ii, sprocket chain II1, sprocket'wheel H8 and the shaftII9 for feeding the material I22 past the knives I23 and I24. Knives I23 and I24 are mounted on the drums I25 and I26, respectively.

The Reeves shaft I3I carries the sprocket I32 which drives the sprocket chain I33 and through the sprocket wheel I34 mounted on the shaft I35 and driving the pinion I36 through the idler gearing I31 thus driving the gear I38 which is secured to and rotates the shaft I39. A Reeves control screw handle I 53 rotates the screw I52 on which is mounted for axial movement the bifurcated link I 5| which engages and moves the belt H4. A second adjusting handle I29 rotates the screw I28 which axially moves the nutI55 and through a pin I55 attached to nut I55 entering into the slot of the bifurcated pin I51 drives the shaft I58 and through the lever I6I and link I62 which is connected by a universal joint I62 to one end of the lever I68, which has the rotation shaft I69 as to fulcrum, the opposite end of the lever I68 rotatively carries the shaft I 39. Secured to and rotatable with the shaft I39 is the crank arm I1I which carries at its outer extremity a connecting link I12 for connecting-the crank arm III andthe crank arm I13 which is adjustably secured to the knife shaft I 44 through'an adjusting mechanism I14 shown in greater detail in Figs. 2 and 3 to be described hereinafter.

In this case as in Fig. 4 rotation of the Reeves control screw through handle I 53 will produce changes in the R. P. M. of the drive shaft I39 which, through the cranks III and I13, and link I12 drives the knife shaft I44. At the same time rotation of the handle I29 drives the lever and link IBI and I62 to in turn rotate the lever I68 for adjusting the shaft I39 to move its center toward or away from the center of shaft I44, one

limit being that position in which the shafts I39 and I44 are co-axial and the other limit being that position in which the shaft I39 is at its- 'maximum distance away from shaft I44 as illusextended sothat even shorter pieces of the web will be cut simply by raising shaft I 39 above shaft I44 and thus beyond the co-axial previously mentioned. As in the case of-Fig. 4 when the shaft I39 is co-axial with shaft I44 2. one to one ratio between the R. P. M. of shaft I 39 and shaft I44 obtains throughout the revolutions, this being equal to and in synchronism with the paper, it being fed past the knives by the feed rolls I29 and I2I. This is a condition obtained in Fig. 13 in which the shaft I39 and the shaft I 44 are in co-axial relation and thev crank "I is shown extending to the pin I12 connecting,this crank I to the link I12 and the link I 12 is shown extending to the pin I15 connecting the'link with the crank I13. At this position theknives I23 and I24 are in their cutting position and the-cutting operations begin. For cutoifs inches long and asence of the knife drum of 30 inches the average Y R. P. M. of the shaft I39 will be one-fourth df the speed assumed in the first condition illustrated in Fig. 13. Therefore during the cutoff period the ratio of four to one, in order that the shaft I44 may move at an angular speed which will produce a linear movement synchronous with the linear movement of the paper being cut. To this end at the instant of cutoff the center distance from shaft I39 to pin I12 and of shaft I44- to the center of pin I12 must be in the ratio of four to one at the period of cutoff or at the period when the knives are cutting. Similarly, as has been explained in detail in connection with Fig. 4 for cutting strips of material of 60 inch lengths the center-to-center ratios between the respective shafts I39 and I44 and the pin I12 must be two to one at the period of cutoff as illustrated in Fig. 9, and for cutting 40 inch lengths the ratio between-the respective shafts I39 and I44 and pin I12 must be four to three at the period of cutoff as illustrated in Fig. 11.

It will be noted however, that due to the link and crank construction here employed the angular position of the cutting knives, which is determined. by the angular positions in turn of the links I12 and I13 at the pin I15,is different for each particular size of material being cut so that it becomes necessary not only to adjust the shaft I39 to obtain the different ratios between the speed of the shaft I39 and the knife shaft I44 at cutoff but it also becomes necessary to angularly adjust the knives so that they will be in a cutting position at the new angular position assumed by I the crank I13 and link I12 at the pin I15 for the new cutoff length. To explain this further, assuming that the knives are adjusted on the drum so that cutoff takes place when the pin I15 and the crank I13 is in the position shown in Fig. 13, it will be obvious that in the opposite extreme position shown in Fig. '7 the knives are not in cutting position at the time of the desired speed of shaft I44. It is however at this particular position of the pin I15 of Fig. '7 that the desired speed ratio between the driving drum I 39 and the knife drum I44 obtains and therefore it is necessary to obtain a further adjustment of the knives so that they will be cutting when this proper ratio obtains. To this end I provide a further angular adjustment of the knives in relation to the crank I 13 by means of the mechanism I14 shown in greater detail in Fig. 2.

Crank I13 as shown in Fig. 2 is keyed to a shaft I8I which has an extension I82 provided with a plurality of grooves I83 mounted on shaft I44. It is slidably connected, the coupling piece I85 having mounted at its extreme end a plurality of rollers I86 mounted on pins I81. Coupling I85 is also provided with a groove I88 in which it engages a fork I89 which is rotated by means of shafts I96.

When the shaft I58 is rotated in the manner described above the crank I9I rotates and moves and in turn moves the link I92 connected at its other end through the crank I93 to the shaft I96. Shaft I98 is thus rotated so it will be imparting an axial movement to coupling I85 through the fork I89 by appropriate curvature of the cam grooves I83. The pins I81 turn shaft I44 in relation to shaft I8I and in turn with relation to crank I13 thus providing an angular adjustment of the knives with respect to the crank I13 sufficient to compensate or correct for v the angular adjustment necessary as indicated in comparing Figs. 7, 9, 11, and 13.

It will be understood by those skilled in the art that as crank I13 and link I12 are straightened this angular adjustment of the knife in rela;

In view of the fact that the Reeves control 5 screw is separate from the adjustment of the shaft I39 obtained through the adjusting handle I29 a definite relation between the rotation of handles I53 and I29 must be obtained. This is provided by the two indicator and scale combi- 10 .nations I94 and I95.

These are so calibrated that for a predetermined rotation of handle I53 as indicated by the indicator I94 a corresponding rotation of handle I29 is necessary as in turn indicated by the indicator I95 for producing 15 the proper adjustment of shaft I39 for any operation of the Reeves drive.

The different sheet lengths are marked on the dial by calibration. It is merely necessary to bring the two indicators to the corresponding 20 positions on their dials.

In Figure 5 I have shown a further modified form of my invention in which the Reeves drive 3 comprises the cones 3I3 and 3| 4, connected by the belt 3I2. The cone 3I3 mounted on and 25 rotating the shaft 3I5 operates the feed rollers 320 and 32I for feeding the paper to the knives or cutters 323 and 324. The cone 3I8 secured to and driving the shaft 33I rotates the sprocket wheel 332 keyed to the shaft 33I. A continuous 30 sprocket chain 333 drivenby the sprocket Wheel 332 meshes at its opposite end with the teeth of sprocket wheel 334. Sprocket wheel 334 is keyed to and drives the shaft 335 at the opposite end of which is secured the worm gear meshes with the worm 331 mounted on the shaft 338. Secured to the side of and rotated by gear 336 is the pin 34I which extends from gear 336 to the wheel 342 which is driven by the gear 336 through the pin 34I. 1y broken away for clarity.) Wheel 342 is suitably supported in bearings on the shaft 344. Pin 34I also carries the crank levers 345 and 346 to which is secured the ends of the knife 323 in any suitable manner as by rivets 341. As gear 45 336 rotates it will carry the pin 34I in a path co-axial with the shaft 335 causing through the crank levers 345 and 346 the knife 341 to move from an arcuate to a curved path, as illustrated in greater detail in Figures 18, 19, 20, and 21, to 50 be explained hereinafter. At the same time knife 324 describes the same sort of path driven through shaft 338, having secured at .its lower end the worm 35I which meshes with a worm gear 352 to which is secured the pin 353 carrying at its 55 other end the wheel 354 suitably mounted in bearings on shaft 355 and supporting the crank levers 356 and 351.

A Reeves drive adjusting handle 36I secured to the shaft 362 drives the bevel gear 363'mesh- 0 ing with the bevel gear 364 which in turn is secured to and rotates the shaft 365 and through this drives the bevel gear 366 meshing with bevel gear 361 for turning the screw 368. 'As screw 368 rotates, it moves the fork member 369 axially 65 and adjusts the belt 3I2 for changing the -R. P. M. of the output of the Reeves drive at'shaft 33I to vary the cycle of the knives 323 and .324 for varying the size of cuts as explained hereinbefore. Secured to the shaft 362 are 312 which mesh with the worm gears 313 and 314 respectively mounted on-shafts 315 and 316.

Secured to and driven by the shaft 315 is the crank arm 311 and the crank arm 318 which are connected through pins to their respectivel'inks 75 336 which 35 (Pin 34I being shown part- 40 the worms 31I and 70 through pins to the crank arms 345 and 346 respectively.

When the adjusting handle 36l is rotated it will, as will now beobvious move the belt 3l2 for adjusting the speed output of the Reeves drive and at the same time will adjust the position of the knives 323 and 324 so that the cutting action will occur at that point in the cycle at which the knives are moving in synchronism with the paper.

Referring now more specifically to Figures 18 to 21 which illustrate the paths taken by the knivesin this form of the invention, it will be noted that the movement of the knives is a composite of both the circumferential movement affected by the pin34l driven by gear 336 and a modification of that circumferential movement affected by the crank and link connections 311 and 319. With the particular adjustment of the links affected through rotation of the shaft 315 with the paper at the time upon rotation of the hand wheel 361 the knives 323 and 324 are arranged to makethe elliptical path illustrated in Figure 20 at curves 38| and 382. In taking this path the knives are arranged to be moving in synchronism with the paper at the time when they are in engagement with each other in the position shown in Figure 18. This is determined exactly in the manner already described in connection with the previous figures. Knowing for example, the ratio of the reduced speed to the normal speed at which the knives move in synchronism with the paper throughout their cycle, the link and crank connections areso designed and the adjustments so made as to increase the speed of the knife over the speed obtained at the gear 336 in the same ratio inversely as the gear is rotating less than the speed of the paper so as to bring the knives to synchronism with the paper, this increased speed being provided by the action of the crank and links 311 and 319.

Similarly for afurther adjustment of the output speed of the Reeves drive, an entirely different path of the knives will be efi'ected by a new adjustment obtained along the shaft 315, as illustrated in Figure 21 in the paths 383 and 384. Here again in order to obtain synchronism between the knives and the cutting paper during cutting operation, the crank and link connections are so adjusted that their action on the normal circumferential movement of the knife carrier will be such as to bring the knives into synchronism when they meet for the cutting operation.

In Figure 17, I have illustrated this same principle in connection with knives mounted on crank members but which, however, eliminates the necessity for shaft 315 in Figure 5 and which requires only one set of links similar to 311 and 319 of Figure 5 for eachknife instead of the two sets in Figure 5, and which will insure a uniform distribution of power during the entire cutting operation.

and 402 are driven from the Reeves drive in a manner already described and which will now be clear to those skilled in the art, and through the Crank 405 is connected by connecting rods 401, 408 and 409 to crank 4l0. Crank 4| 0 is in turn mounted'on. disk 4| I by pin 2. It willthus be obvious that any rotation of disk. 40l which Here, as in the previous illustration, discs 4! 2,208,350 319, the opposite ends of which are connected through pin 403 imparts a corresponding circular movement to crank 405 will also, through the connecting rods 401, 408 and 409, impart exactly the same movement tocrank 4I0 causing it to move on its pin 412 which will be caused to rotate about the disc 4| I. Thus, disc 4 will be caused to rotate in exactly the same manner as disc 401 and the two cranks 405 and M0 will move synchronously. Although it is thus not essential, a drive belt 413 is mounted from disk 40I to disc 4 to further assure exactly synchronous movement, and to change disk 4 from a mere idler supporting disk to a power transmitting disk which will exert the same force upon crank 4l0 as disk 40| exerts upon crank 405.

The knife M4 is mounted upon connecting rod 409 and in a plane at right angles to that of connecting rod 409, the faces of the knives being in parallel planes. It will be obvious that every portion of the edge of the knife 4 will, at all times, be equidistant from the pins 403 and 2 through which power is transmitted to the knife 4| 4 thus insuring a uniform power distribution over the edge of the knife 4.

In the same manner, crank'406, attached by pin 404 to disk 402, is connected by connecting rods M5, M6 and M1 to crank 4l8. Crank 418 is in turn mounted on disk 9 by pin 420. Disks 402 and 419 are also connected, in the manner previously'described and for thesame reasons, by a drive belt 42L l The knife 422 is mounted upon connecting rod 411 and in a plane at right angles to that of connecting rod l1 producing the uniform power distribution over the edgesof the knife 422 in the manner previously described.

The action of disks 4!" and 402 andtheir cooperating members is intended to be synchronous (since they are connected in the same manner to the Reeves drive), so that the knives M4 and 422 will cooperate with each other for the cutting operation, and will move in exactly homologous paths at all times. t

A Reeves drive adjusting handle 461 secured to the shaft 462 drives the bevel gear 463 meshing with the bevel gear 464 which in turn is secured to and rotates the shaft4l5 which in turn is connected in the manner described in connection with Figure 5 to adjust the R. P. M. output of the Reeves drive to vary the cycle of' the knives 414 and 422.

Secured to the shaft 462 are the worms 4" and 412 which mesh respectively with the gears 413 and 414 respectively mounted on shafts 415 and 416. Secured to and driven by the shaft 415 is the crank arm 411 which is connected through a pinto the link 419. Similarly secured to and driven by the shaft 416 is the crank arm 418 which is connected through a pin to link 400, The opposite ends of links 419 and 480 arerespectively connected by appropriate pins to their appropriate crank arms 405 and 406.

When the adjusting handle IN is rotated it; will, as has been explained, adjust the output speed of the Reeves drive and at the same time, in the same manner as explained in connection with Figure'5, will adjust the position of the knives 4 will occur at that point in the cycle at which the knives are moving in synchronism with the paper. I

In Figures 15 and 16, I have again illustrated the same principle in connection with a different members prethe parts 561,

and 422 so that-the cutting actionsea, see, see, an, 512, sis, 514, 51s, 51s, are

exactly homologous to and act in the same manner as the parts in Figures 18 and 19 which are numbered 368, 362, 363, 364, 3B5, 31!, 312, 313, 314, 315, and 316.

The disks 6M and 602 are driven through the Reeves drive in amanner which will now be understood. Attached to'the sides of said disks are pins 603 and 604 respectively which in turn carry cranks 605 and 606 respectively. Crank i305 carries knife 60! which in turn cooperates with knife 608 carried by crank 606.

Crank arm 609 is keyed to shaft 515 and carries at its other end pin Blll which is adapted to slide in slot fill in the crank 605. Similarly crank arm M2 is keyed to shaft 516 and carries at its other end pin M3 which is adapted to slide in slot BM in the crank 6H5.

It will be obvious that the crank arm 609 will have an action similar to that of crank arm Ml of Figure 1'7, but that in place of the link 319 of Figures 18 and 19 there is substituted the length of the stroke of pin 6H0 in slot GM of crank 305; the lower terminal of such stroke corresponding .to the pin which connects crank arm 31?! and link 319 of Figures 18 and 19 and the other terminal of such stroke corresponding to the pin which connects link 319 with crank 305 of Figures 18 and 19.

Similarly, crank arm BIZ has an action like that of crank arm 318 of Figures 18 and 19; but in place oflink 380 of Figures 18 and 19, there is substituted the length of the stroke of pin H3 in slot 6M of crank 636.

When the adjusting handle 56! is rotated, it will, as has been explained, adjust the output speed of the Reeves drive and, at the same time, in the same manner as explained in connection with Figures 18 and 19 and Figure 5, will adjust the position of the knives 631 and 60% so that cutting action will ocur at that point in the cycle at which the knives are moving in synchronism with the paper.

Although I have described my invention in detail, it will be apparent that I have chosen specific illustrations for the purpose of showing how to carry out my invention and I do not intend to be limited thereby except as set forth in the appended claims.

I claim:

1. In a power transmission system, a source of power; a drum; a first shaft driven by said source of power; a second shaft connected to and driving said drum; a power transmission connection from said first shaft to said second shaft; means for adjusting the distance of the axis of the first shaft from the second shaft; said power transmission path from said source of power to said drum constituting a positive drive and being the sole transmission path to said drum.

2. In a power transmission system, a source ofpower; a drum; a first shaft driven by said source of power; a second shaft connected to and driving said drum; a power transmission connection from said first shaft to said second shaft including a slideable pin and slotted member in which said pin slides; means for adjusting the axis of the first shaft with respect to the second shaft; said power transmission path from,said source of power to said drum constituting a positive drive and being the'sole transmission path to said drum.

3. In a power transmission system, a source of power; a drum; a first shaft driven by said source of power; a second shaft connected to and driving said drum; a power transmission connection from said first shaft to said second shaft including a slideable pin and slotted member in which said pin slides, said pin being carried by said first shaft and said slotted member being mounted on said second shaft; means for adjusting the axis of the first shaft with respect to the second shaft; said power transmission path from said source of power to said drum constituting a positive drive and being the sole transmission path to said drum.

4. In a power transmission system for driving a knife drum to cut a web in predetermined varying lengths, means for feeding said web at a constant speed, a source of power; a knife drum carrying a knife; a first shaft driven by said' source of power; a second shaft connected to and driving said drum; a power transmission connec- 1 tion from said first shaft to said second shaft; means for adjusting the axis of thefirst shaft with respect to the second shaft; said power transmission path from said source of power to I said drum constituting a positive drive and being the sole transmission path to said drum. I 5. In a power transmission system for driving a knife drum-to cut a web in predetermined varying lengths, means for feeding said web at a constant speed, a source of power; a knife drum carrying a knife; a first shaft driven by said source of power; a second shaft connected to and driving said drum; a power transmission connection from said first shaft to said second shaft including a slideable pin and slotted member in which said pin slides; means for adjusting the axis of the first shaft with respect to the second shaft; said power transmission path from said source of power to said drum constituting a positive drive and being the sole transmission path to said drum. 6. In a power transmission system for driving a knife drum to cut a web in predetermined varying lengths, means for feeding said web at a constant speed, a source of power; a knife drum carrying a knife; a first shaft driven by said source of power; a second shaft connected to and driving said drum; a power transmission connection from said first shaft to said second shaft including a slideable pin and slotted member in which said pin slides; said pin being carried by said first shaft and said slotted member being mounted on said second shaft; means for adjusting the axis of the first shaft with respect to the second shaft; said power transmission path from said source of power to said drum constituting a positive drive and being the sole transmission path to said drum.

'7. In a power transmission system for driving of rotation of said first shaft, said means simultaneously shifting the axis of the first shaft with respect to the second shaft to secure synchronism of speedbetween said knife drum and said web during the period said knife engages and cuts the web.

8. In a power transmission system for driving carrying a knife; a first shaft driven by said" source of power; a second shaft connected to and driving said drum; a power transmission connection from said first shaft to said second shaft including a siideable pin and slotted memher in which said pin slides; said power transmission path from said source of power to said drum constituting a positive drive and being the sole transmission path to said drum; and. means for varying the speed of rotation of said first shaft, said means simultaneously shifting the axis of the first shaft with respect to the second shaft to secure synchronism of speed between said knife drum and said web during the period said knife engages and cuts the web.

9. In a power transmission system for driving a knife drum to cut a web in predetermined vary- 2,208,850 I a ing 1engths,' means for feeding said web at a constant speed, a source of power; a knife drum carrying a knife; a first shaft driven by said source of power; a second shaft connected to and driving said drum; a power transmission connection from said first shaftto said second shaft including a slideable pin and slotted memher in which said pin slides, said pin being carried by said first shaft and said slotted member being mounted on said second shaft; said power transmission path from said source of .power to said drum constituting a positive drive and being the sole transmission path to said drum; and means for varying the speed of rotation of said first shaft, said means simultaneously shifting the'axis of the first shaft with respect to the second shaft to securesynchronism of speed between said knife drum and said web during the period said knife engages and cuts the web.

GUSTAVE ADOLPI-IE UNGAR. 20

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