US2289394A

US2289394A - Cutting apparatus

Info

Publication number: US2289394A
Authority: US
Inventors: Gustave A Ungar
Original assignee: S&S Corrugated Paper Machinery Co Inc
Current assignee: S&S Corrugated Paper Machinery Co Inc
Priority date: 1937-06-18
Filing date: 1940-07-13
Publication date: 1942-07-14
Anticipated expiration: 1959-07-14

Description

July 14,1942. "G. A. UNG AR CUTTING APPARATUS Original Filed June 18, 1937 6 Sheets-Sheet l INVENTOR. gusfav'ca. Llgyar ATTORNEY.

"J1ilyl4',1 942." G. A.'U NGAR 2,239,394

, v I CUTTING APPARATUS Original Filed June 18, 1937 6 Sheets-Sheet 2 INVENTOR.

quslav'e a.

July 14,- 1942. cs. A. UNGAR CUTTING APPARATUS Original Filed June 18, 1937 6 Sheets-Sheet 3 INVKNTUK. gusl'are a. W r BY Q July 14, 1942". A A, UN AR 2,2891394 ,CUTTING APPARATUS Original Filed Ju ne 18, 1937 6 Sheets-Sheet 5 Fig: 1'7 INVENTOR.

gust-ave a. a gal BY ATTORXEY.

"J l 14, 1942. a A, UNGAR 2,289,394

\ CUTTING APPARATUS Original Filed June 18, 1957 6 Sheets-Sheet 6 INVENTOR.

gusf'ave 0.?11war ATTORNEY.

Patented July 14, 1942 CUTTING APPARATUS I Gustave A. Ungar, Pelham Manor, N. Y., assignor to S. & S. Corrugated Paper Machinery Co.,

Inc., Brooklyn, N. Y., a corporation of New York Original application June 18, 1937, Serial No. 148,892, now Patent No. 2,208,350, dated July 16, 1940. Divided and this application July 13, 1940, Serial No. 345,315

v11 Claims.

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 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 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 during 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 have been considerably improved upon by hydraulic transmission and other forms of drives.

In general, however, these systems are expensive andlack 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 interval 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 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.

A further object of my invention is to pro vide an interlocking pin and slot drive connection for obtaining variable speeds during a single cycle to insure synchronism during the cutting interval.

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 cut while insuring synchronism during the cutting interval.

Still another object of my invention is to provide 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 therebetween in a cycle.

There are other objects of 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 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 taken on line 33 of Figure 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 different 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 oi 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 ll comprising the cones I2 and I3 joined by the continuous belt M. The cone I3 is mounted on the main drive shaft l5 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 I! which in turn rotates sprocket wheel l8 mounted on the shaft [9 which carries thereon the feed roll 20 cooperating with the upper feed roll 2L web 22 is advanced forward in the direction inthe knives 23 and 24 mounted on drums 25 and 26 respectively.

Between the feed rolls 2!] and 2| the I The cone I2 is mounted on and drives the shaft 3| which carries on its end a sprocket wheel 32 carrying the sprocket chain 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 crank 4|. To one end of the crank 4| and extending substantially at right angles from the plane thereof a pin 42 issecured and is ar ranged to drive the bifurcated crank 43 in which it is slidably positioned. The 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. As the Reeves drive transmits power over the shaft 3| the gear 38 is rotated, in turn driving the shaft 39 and the crank attached thereto 4| together with the pin 42 about the axis of shaft 39 as a center. As the pin 42 rotates about the shaft 39 as its center it will drive the bifurcated crank 43. In the specific adjustment shown in Fig. 4, where the shaft 39 lies below shaft 44, the pin 42 is sliding toward and away from shaft 44 in aplane at right angles to its axis during each revolution by reason of its fixed relation with respect to shaft 39.

Assuming for the purpose of the present illustration that the shaft 39, which, as will be explained hereinafter, is adjustable with respect to the fixed knife shaft 44, is below the shaft 44 as in the present case; it will be obvious that angular velocity of the shaft 39, when the crank 4| and the pin 42 reach the position 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 T0 of shaft 44 which is greater than the angular velocity 0 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.

0=angular velocity of shaft 39 r=actingradius of shaft 39+acting radius of shaft 44 r0=angular velocity of shaft 44 It will be obvious that in every position of crank 4| and pin 42 within the bifurcated mem ber 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 44.

Thus, when the pin 42, in the course of its revolution, has turned 45 from the position illustrated in Fig. 4, it will 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 0 of shaft 44 will be 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 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 velocity M of shaft 44 will be less than the angular velocity of shaft 39.

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.

When now it is desired to change the length of the cuts (and to this end the Reeves drive is changed for either decreasing or increasing the R. P. M. of the knife drums 25 and 26), the relative 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 be noted that the 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| there is secured a link 62, the other end of which is secured through a pin 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 idler 31 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.

When the handle 53 is rotated the bifurcated member 5| moves the belt l4 to either increase 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. Depending 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 angles 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 of feet or 1200 inches per minute. It is further assumed that the size of sheets desired to be cut is 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 assumed that the permanent ratio selected betweenshafts 3| and 39 is five to one; therefore, to produce R. P. M. on the knife drums. an output speedof 50 R. P. M. is required on shaft 3| of the Reeves drive.

It is obvious, however, that with 10R. P. M. of the knife drums whose circumference is 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 wili tend to rip or tear the paper and that they will not make a clean out.

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:

as previously described: and making the proper substitutions forthe symbols, the angular velocity of shaft 44 at the knife edge circumference of the knife drum will be 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 averagespeeds 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 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 of the 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 120 inches, it became necessary as previously explained to decrease the average speed of the knife drums to 10 R. P. M. or one fourth of the speed of the paper. Therefore, in order to bring 3 the knife speed to the speed of the paper at the time of cutoff it was necessary duringthis period to obtain a speed on the knife drum quadruple 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 remaining the 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-tocenter 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 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 40 R. P. M. imparted by shaft 39 is 900 inches per minute.

Thus, again applying the formulae previously set forth,

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

In this instance again, the shaft 30, in order to produce cuts longer than 30 inches must be 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 40 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 Accordingly a ratio of one to one 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 44 in 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 3| 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 eachspecific size to be out.

It will further be obvious that, in the illustration given, in order to obtain cuts shorter than inches in length, 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 a limitation 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 44 for every desired size of sheet to be cut by the knives 23 and 24. In order to effect 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 68, the adjustments of the lever 68 being greater than the proportionate change of the Reeves drive for one size cutoff 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 100 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 turns necessary for the Reeves control screw at the higher speeds I have provided the cammed slot 65 in which the roller 66 moves for increasing the ratio of linear movement of the shaft 39 for every turn of the Reeves control screw at the higher speeds.

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 Fig. 4 a Reeves drive III is employed comprising the cones H2 and H3 mounted on their respective shafts H5 and I3I and having the drive belt H4. As in the previous illustration the roll I2I of feed-rolls I20 and I2I is driven from the sprocket H6, sprocket chain H1, sprocket wheel H8 and the shaft H9 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 I53 rotates the screw I52 on which is mounted for axial movement the bifurcated link I'-5I which engages and moves the belt H4. A second adjusting handle I29 rotates the screw I28 which axially moves the nut I55 and through a pin I56 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 I39. 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 HI and the crank arm I13 which is adjustably'secured to the knife shaft I44 through an adjusting mechanism I14 shown in greater detail in Figs. 2 and 3 to be described her inafter.

In this case as in Fig. 4 rotation of the Reeves control screw through handle I53 will produce changes in the R. P. M. of the drive shaft I39 which, through the cranks HI and I13 and link I12 drives the knife shaft I44. At the same time rotation of the handle I29 drives the lever and link I6I 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 illustrated in Fig. 7, this maximum distance being determined of course by the cranks and levers I1I, I12 and I13. It will be understood, of course, that the first limit mentioned, that of the coaxial position of shaft I39 and I44 may be even further extended so that even shorter pieces of the web will be cut simply by raising shaft I39 above the shaft I44 and thus beyond the coaxial previously mentioned. As in the case of Fig. 4 when the shaft I39 is co-axial with shaft I44 a one to one ratio between the R. P. M. of shaft I39 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 I20 and I2I. This is a condition obtained in Fig. 13 in which the shaft I39 and the shaft I44 are in co-axial relation and the crank III is shown extending to the pin I21 connecting this crank "I to the link I12 and the 1 link I12tisshown extending to the pin lllconnecting thexlink withlthe crank I 13. Atthis. position the knives: I 23 and I24 are in their cutting I position andr the ;cutting operations begin. For cutoffs l2oxin'cheslong and assumingall the i I conditions assumed. in" connection with. Fig. =4,

that is a movement tof thexpaper of 100 feetor 1200. inchesrpenminute =a circumference of: the knife drum of 30 inchesxtheaverage R. P. M. of the shaft 139 will be one-fourth of the speed assumed in the first. condition illustrated in Fig. 313. "Therefore during the cutoff period the ratio I of four to onegin :order that ;the' shaft I44; may

move at. an angular: speed *which will produce 'a linear :movementx synchronous with the linear movement of" the paperbeing out. To this end at thexinstant'of: cutoflx-the center distance from shaft I39 to pin I12'wand1of shaft I44to the center of. pin I12'1must beIin the ratio of IfOuI' tO one at theperiodxoffcutofi orzat the periodwhen theknives 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 I 39tand I44 and the pinI 12.must be'two tonne atthe period of. cutoff as illustrated .in

.1 Fig-9,: and'for cutting-40inchulengths the ratio between therespective shafts139 and I44 and .pin I'IZ'IJmustbe fouroto three I at the period of I cutoff 1 as lillustrated in' Fig. 11.

It will benotedrhowever, .thatdue to the link and crankconstruction here employed .the angular position of the cutting. knives, which is determinedxby the angularpositions in turn of the Ilinks "I12 and I13 at the pin I15, isdifferent for eachvparticular'size ofmaterial being cut so that it becomes necessaryrnot only to adjust the shaft I39 to'obtain thedifferent ratios between the speed of the shaft I39 and the. knife shaft I44 at cutoff but it also ibecomes necessary to angularly adjust the knives so that they will be in a cutting position at the \new' angular position I assumed by the crank I13 and-link I12 at the pin I15 for, thenew cutoif length. To explainthis further; assuming that the knives areadjusted on the-drum so that cutoflf takes place when the .pin I15 and the crank I 13 is in they position shown inFig. 13, it .willbe obvious that in the opposite I extreme-position shown in Fig. 7 the knives are not in 'cuttingposition at the time of thedesired speed .of shaft I44. It is "however at this particularposition of thepin I15 of Fig. 7 that the desired speed ratio between the driving drum I39 and the knifedrum I 44 obtains and therefore it I is necessary to obtaina further adjustment of the knives so that they'willbe cutting 'when 'this proper ratio obtains. To this end I provide a further angular. adjustment of the knives in relation to thecrank I13 by means of the mechanism I14 shown in greater detail in Fig. 2 I Crank I13-as shown .inIFig. 2 is keyed to a shaft I 8|" which has an extension I82 provided with aplurality of grooves I83 mounted on sha I 44. His slidably connected; the coupling piece "I85 having-mountedat its extreme anda plurality of rollers I86 mounted on pinsl81. Courpling I85 is also--provided witha groove I88 in which it engagesa fork I89 which is rotated by 1means of shafts I90.

When the shaft I58 is rotatedin themanner described above the crank 'I9I rotates and moves :andin turnmoves the link I92 connected at its .1 other end through the crank I93 tothe shaft I 90. 'iShaft I96 is thus rotated so it will be imparting an axial movement to coupling I85 ducingctherproper adjustment of' shaft I39 through :the. fork I89 by I appropriate curvature .oflthe camgrooves I83. {I'hepins I81 turn shaft I44in relationto shaftIBLand in turn .with relationtto: crank: I 13 thus providing I am angulanadiustment of the kniveszwith respect tothercrank I13 suflicient. to compensate orcorrectfor-the angular adjustment necessary as indicated in comparing Figs. 7, 9,. 11, and 13.

'It' will be understood by those'skilledin the art that as crank I13 and link I12;arestraightened this angular adjustment of r the kniferin relation .to the position of i pin I15 rbecome's smaller and smaller .untilatwagproper ,anglerbetweencrank I13 and .link I 12-substantially-no correctionisnecessary.

In view of the fact that .theJReeves-control screw is'separate from .thep'adjustment of the shaft I39 obtained through the adjustinghan'dle I29 a definite relationbetween therrotation of handle I53 and I29wmust be obtained. 1 provided by the twoindicator andscale combinations I94 and I95. These are so calibrated that for a predetermined rotation of handle I53 as indicated by the indicator I94 a correspondingrotation oflhandle I29 is necessary as in turn indicated by the indicator I95 for profor any operationv of the Reeves drive.

The different sheet lengths are marked on the Ydial" by calibration. It is'merely necessary to bring the two indicators to the corresponding-p0 0 sitions on their dials.

In Figure 51 have shown a further modified form of myinvention in which the Reeves drive 3 comprises the conesl3I3 and 3I4, connected by the belt 3I2. The :cone 3I3 mounted on and rotating the shaft 3I5 operates the feed rollers .320 and' 32I for feeding the paper totheknives or

cutters

323 and 324; The cone 3I8Lsecured to and driving the shaft 33I rotates the sprocket wheel 332 keyed to the shaft 33L A continuous sprocket chain 333 driven by thewsprocket wheel 332 meshes at its oppositeend with the teeth of sprocket-wheel 334. Sprocketwheel 334isikeyed toand drives the shaft 335 at the opposite end of which is secured the worm'gear 3336 which meshes with the worm 331.mounted on the shaft .333. ISecured to the side of and rotatedbygear ly broken away for clarity.)

336 is the .pin 34I which extends from gear 336 to the wheel 342 which iscdriven by the gear 336 through the pin 34 I. (Pin 34I being shown part- Wheel3'42 is suitably supported in hearings on the shaft. 344. Pin

34I also carries the

cranklevers

345 and 346 to .which is secured the ends of the knife,323 in any suitable manner as by rivets 341. As gear through shaft 338, having :secured atits lower end the worm 35I whichmeshes with a worm gear 352 towhich is secured the pin 353 carrying at its 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 meshing with the bevel gear 364 which in turn is secured to and rotates the shaft 365 and through this drivesthe bevel gear 366 meshing withbevelgear 361 for turning the screw 368. As screw-368 rotates, it moves the fork member III axially and adjusts the belt III for changing the R. P. M. of the output of the Reeves drive at shaft III to vary the cycle of the knives III and I24 for varying the also of cuts as explained hereinbe-' fore. Secured to the shaft III are the worms Ill and I1! which mesh with the worm gears "I and I14 respectively mounted on shafts I15 and I10. Secured to and driven by the shaft I" is the crank arm I11 and the crank arm I10 which are connected through pins to their respective links I19, the opposite ends of which are a connected through pins to the crank arms I45 and I4I respectively.

when the adjusting handle III is rotated it will, as will now be obvious move the belt I12 for adjusting thespeed output of the Reeves drive and at the same time will adjust the position of the knives III and I24 so that the cutting action will occur at that point in the cycle atwhich 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 knives in 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 pin I4l driven by gear III and a modification of that circumferential movement affected by the crank and-link connections I11 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 are so designed and the adjustments so made as to increase the-speed of the knife over the speed obtained at the gear III 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 be ns Provided by the action of the crank and links I11 and I19.

Similarly for a further adjustment of the output speed of the Reeves drive, an entirely different path of the knives will be effected by a new to the Reeves drive), so that the knives 4l4 and-" adjustment obtained along the shaft I15, as illustrated in. Figure 21 in the paths III and I84. 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 with the paper at the time when they meet for the cutting operation.

In Fig. 17, I have illustrated this same prin-- ciple in connection with knives mounted on crank Here, as in the previous illustration. discs 40l 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 pins 40I and 404 respectively secured to the cranks 400 and 400 will normally tend to rotate these members in a circumferential path.

Crank 405 is connected by connecting rods 401, 400 and 400 to crank 4l0. Crank 0 is in turn mounted on disk 4 by pin 4I2. It will thus be obvious that any rotation of disk 40! which through pin 40I imparts a corresponding circular movement to crank 405 will also, through the connecting

rods

401, 408 and 409, impart exactly the same movement to crank 4l0 causing it to move on its pin 4l2 which will be caused to rotate about the disc 4. Thus disc 4 will be caused to rotate in exactly the same manner as disc 40! and the two cranks 405 and 0 will move synchronously. Although it is thus not essential, a drive belt 413 is mounted from disk 40l to disk 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 0 as disk 40l exerts upon crank 405.

The knife 414 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 414 will, at all m thus insuring a uniform power distribution over the edge of the knife 4 I 4.

In the same manner, crank 40I,,-attached by pin 404 to disk 402, is connected by connecting rods I, I and 4" to crank 4|8. Crank 4 is in turn mounted on disk 4l9 by pin 420.

Disks

402 and 419 are also connected, in the manner previously described and for the same reasons, by a drive belt 42l;

Th knife 422 is mounted upon connecting rod 4" and in a plane at right angles to that of connecting rod 1 producing the uniform power distribution over the edges of the knife 422 in'the manner previously described.

The action ofdisks m and m and their 06- operating members is intended to be synchronous (since they are connected in the same manner 422 will cooperate with each other for the cutting operation, and will move in exactly homologous paths at all times.

A Reeves drive adjusting handle 4Il secured to the shaft 482 drives the bevel gear 483 meshing with the bevel gear 4I4 which in turn is secured to and rotates the shaft 4|I 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 4 I 4 and 422.

Secured to the shaft 402 are the worms 4H and 412 which mesh respectively with the

gears

413 and 414 respectively mounted on shafts 415 and "I. Secured to and driven by the shaft 415 is the crank arm 411 which is connected through a pin to th link 419. Similarly secured to and driven by the shaft 416 is the crank arm 419 which is connected through a pin to link 480. The opposite ends of

links

419 and 480 are respctively connected by appropriate pins to their appropriate crank

arms

405 and 406.

When the adjusting handle 4Il is rotated it will, as has been explained, adjust the output i aaeaeoa speed of the Reeves drive and at the same time,

in thesame manner as explained inconnection with Figure 6, will adjust the .positionof the knives Ill and .463 so that the cutting action will occur-at thatpoint in the cycle at which the knives are moving, in ,synchronism with the paper.

In Figures and 16, I have again illustrated the same principle in connection with a different adaptation of the crank and link members previously described. In these flgures, the parts 561, 562, 566, 665, 51l, 512; 613, 514, 515, 516, are exactly homologous to. and act in the same manner as the parts in Figures 18 and l9-which are numbered36i, 362, 363,364, 365, 311, 312, 313, 316, 315, and 316. I

The disks 661 and 662 are driven through the Reeves drive in a manner which will now be understood. Attached to the sides of said disks are pins 663'and 664 respectively which in turn carry cranks 665 and 666 respectively. Crank 665 carries knife 661 which inturn cooperated with knife ens carried by crank ens.

- speed of said shaft for changing the size of sheets.

is moved through an arcuate path; a pivot on said shaft for said link: means for changing the speed of said shaft for changing the size of sheets and means for changing the'path of said knife carrier, I

3. A source of power; a shaft; a knife carrier; a link connecting said shaft and knife carrier whereby, as said shaft rotates, said knife carrier is moved through an arcuate path; a, pivot on said shaft for said link; means for changing the and means for continuouslychanging the'pivot of said link for varying thespeed'of 's'aid knife dur Crank arm 669 iskeyedto shaft 515 and car-- ties at its otherend'pin .616 whichis adapted to slidein slot 6| 1 in the crank 665. Similarly crank arm H2 is keyed to shaft 516 and carries at its other end pin 613 which is adapted to slide in slot 6 in the crank 616.

It will be obvious that the crank arm 669 will have an action similar to that of crank arm 611 of Figure 17, but that in place of thelink 319 of Figures 18 and 19 there is substituted the length of the stroke of pin 616 in slot 6 of crank 665; the lower terminal of such stroke corresponding to the pin which connects crank arm 311 and link 319 of Figures 18 and 19 and the other terminal of such stroke corresponding tothe pin which connects link 319 with crank 365 of Figures 18 and 19. V

Similarly, crank arm 6|! has an action like that of crank arm 318 of Figures 18 and 19; but in place of link 366 of Figures 18 and 19, there is substituted the length of the stroke of pin 613 in slot 614 of crank 666;

,When the adjusting handle 561 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 661 and 666 so that cutting action will occur 'at that point in the cycle at which the knives are moving'in synchronism with the paper.

This application is a division of my Patent No. 2,208,350, issued July 16, 1940.

Although I have described my invention in detail, it will be apparent that I have chosen spe cific 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: I

1. A source of power; a shaft;.a knife drum; a crank on said shaft and a crank on said'knife drum; a link connecting the ends of said cranks on said shaft and knife drum whereby, as said shaft rotates, said knife drum is rotated through an arcuate path; means for changing the speed of said shaft for changing the size of sheets and means for continuously changing the pivot of said link by rotation of said shaft for varying the speed of said knife during each cycle of said shaft.

2. A source of power; a shaft; a knife carrier; a link connecting said shaft andknife carrier ing each cycle of said shaft and means for changing therpath of said knife carrier. I

4. A source of power; a shaft; a knife carrier; a link connecting said shaft and knife carrier whereby, as said shaft rotates, said knife carrier is moved through an arcuate path and means for changing the path of said knife carrier comprising amovable pivot for said link on said shaft.

5. A source of power; a shaft; a knife carrier;

a link connecting said shaft and knife carrier.

whereby, as said shaft rotates said knife carrier is moved through an arcuate path; a pivot on saidshaft for said link and means for continuously changing the pivot of said link for varying the speed of said knife during each cycle of said shaft.

6. In apparatus for cutting sheets from a continuously moving web: a source of power, a shaft, a knife carrier, a link connecting said shaft and said knife carrier, said link being pivotally' connected to and oscillatable by said shaft; adjustable-means pivotally connected to said link for defining and limiting the path of movement thereof while the same oscillates, means for changing the size of sheets to be cut and means for changing said adjustable means for varying the speed of movement of said knife during each cycle.

7. In apparatus for cutting sheets from a continuously moving web: a source of power, a shaft, a knife carrier, 8. link connecting said shaft and said knife carrier, said link being pivotally connected to and oscillatable .by said shaft; said knife being rigidly connected to said knife carrieri adjustable means pivotally connected to said link for defining and limiting the path of movement thereof while the same oscillates; means for changing the size of sheets to be cut and means for changing said adjustable means for varying the sp. ad of movement of said knife during each cycle.

8. In apparatus for cutting sheets from a continuously moving web: a source of power, a shaft, a knife carrier, a link connecting said shaft and said knife carrier, said link being pivotally connected to and oscillatable by said shaft;

movement thereof while the same oscillates;

means for changing the size of sheets to be cut and means for changing said adjustable means for varying the speed of movement of said knife during each cycle, said adjustable means comprising a second link pivotally connected at one end to said first link intermediate the ends of said first link and pivotally connected at the other end to a third link, said third link being pivotal on a fixed pivot,

9. In apparatus for cutting sheets from a continuously moving web: a source of power, a

1, my I'm".

whereby. as said shaft rotates, said knife carrier means for changing the size of sheets to bevcut and means for changing-z saidz-adjustable' means for varying the speed of .movement of said knifeduring each cycle, said adjustable"meansrcoml prising'a second link-pivotally connected at: one

end to'said. first link intermediate.:the ends. of said first.-link;rand pivotally" connected at ;.the other end'to a third link; said: third link being pivotal on a fixed pivot, and means. for changing thesetting of s'aid'fixed pivot for-changing the variation in the speed-of movement of said knife during each cycle.

10. In apparatus for cutting :sheets from a continuously moving 'web: a source of power, a shaft, a'knife carrier, 9. link connecting said 1 shaft andlsaidsknife carrier; said: link :being pivotally connected to and oscillatable by said shaft;

2 said knife beingflrigidly connected tmsaid' knife carrier: adjustable meanspivotally connected to said linkfor defining andilimiting theipatn of movement thereof 'w'hile the same oscillates; means for changing the size of sheets'to bexcut and means-for changing said adjustable means for varying the speed of movement of said knife during each" cycle, said adjustable means comprising a secondlink' slidably connected atone end to saidxfirst link and slidable intermediate thesends of said first'link; .saidisecond-linkbeing pivotalron a fixed pivot.

.11. In apparatuszfor cutting :sheets from a continuously moving web: a-rsourceof power, a shaft, a knife carrier, a link connecting-said shaft'andsaid knife carrier, .said link being piviotally connected to and oscillatable by said shaft;

.. said .Jknifa being rigidly connected to said knife .1 carrier; adjustable means pivotally connected to said link for'definingwand limiting the path of rnmovementv thereof while the-same :osoillates; umeans for changing thersize of' sheetsto be :cut 5 and means for changingsaidadjustable means for varying the speed of movement of :said knife during each cycle, said adjustableumeans comprising a'second link slidablycconnected Vat-one endzto said first link and slidably intermediate thesends of said first linkysaidsecond linkbeing pivotal'on a fixed pivot, and'means'for changing theset'ting .of said fixed pivot forzchanging the variation inthe speed of movement ofsaidknife during each cycle.

' GUSTAVE UNG'AR.