US3185010A - Slitting mechanism for endless web material - Google Patents

Description

SLITTING MECHANISM FOR ENDLESS WEB MATERIAL 3 Sheets-Sheet 1 Filed June 5, 1963 UN 5m WM: win 6x c gm fun Ma m A W\ Mw m -\m m. m o. u in |MJ m y 25, 1965 w. G. PRINTZ ETAL 3,185,010

SLITTING MECHANISM FOR ENDLESS WEB MATERIAL Filed June 3, 1963 3 Sheets-Sheet 2 INVENTORS, IVA/WE/VGPe/NTZ D/M/TE/JS UBE/V/5 MAL/4M [/THGO MEL b0 Y-Ioczs "MOIQNEY 1965 w. s. PRINTZ ETAL 3,185,010

SLITTING MECHANISM FOR ENDLESS WEB MATERIAL Filed June 3, 1963 Sheets-Sheet 3 I m 84 4% a 1os- 1 m 4- 10awe, 5: as gas \40 F 6 5 V56) I l '10 P w 5615 '4 use x x I65 v14, A60

as n4 m1 INVENTORS,

MEEE/V 6. Fem/r2 DIM/TEA/S Fuse/W5 MLL MM 1/77/60 BY MEL U). FLOCKS ATTORNEY United States Patent 3,185,010 SLITTING MECHANISM FOR ENDLESS WEB MATERIAL Warren G. Printz, Middletow-n, Dimitrijs Rubenis,

Monroe, and William Lithgo, Middletown, Ohio, as-

signors to Diamond International Corporation, a corporation of Delaware Filed .l'une 3, 1963, Ser. No. 284,915 14 Claims. (Cl. 83-482) The present invention relates generally to slitting apparatus, and more particularly, to the type of slitting apparatus of the character disclosed, for example, in Us. Letters Patent to Clem No. 2,571,20l, issued October 16, 195 1, employed in the slitting of webs of paper webs.

The improved slitting apparatus of this invention is of the narrow-cut, shear type such as that used to trim and cut web material on web winding machines, for example.

This type of slitting apparatus is generally in the form of a thin steel disc of about 6 to 8 inches in diameter, manufactured from hardened and tempered tool steel, and peripherally ground to obtain a sharp edge in order to form a circular knife. The steel disc cooperates with an underlying driven cutter disc or drum, and will be kept in rotating contact, i.e., by overlapping and engaging the side of the drum, and the plane of the axis of rotation thereof will be at a slight angle with respect to the axis, of rotation of the cooperating drum to form a shear angle similar in effect to the angle of contact of two cooperating and overlapping blades of a pair of scissors. Just as in a pair of scissors, the blade and drum, while rotating together, must be maintained in contact at an optimum amount of pressure in order to sever a web of material with a consistently clean cut.

The necessity for maintaining the optimum shear angle and optimum pressure is well recognized by the prior art, and various means have been devised, the more common of which being through the utilization of a spring pressure.

A primary object of the present invention is to use fluid pressure, preferably pneumatic pressure, in conjunction with means whereby the pressure may be readily controlled at a remote control console, and this pressure may be readily adjusted to suit slitting requirements for different grades of material being processed.

A further object of the present invention is to provide improved web slitting apparatus which includes means for applying pressure to normally retain an upper cutter disc and bottom cutting drum in spaced relation; which utilizes fluid pressure to force the blades in engagement by means of a compound movement whereby engagement and disengagement of the cooperating cutting blades is such a movement that substantially obviates damage to the blades when they are engaging and disengaging; which affords a cam control action whereby an upper slitter blade is moved first vertically and then horizontally into engagement with a lower slitter blade, and in which such movement is reversed; in which disengagement between the cooperating cutter blades is substantially instantaneous; in which the apparatus may be readily moved on a rigid support beam and adjusted along the length thereof without disturbing the previously adjusted shearing angle, overlap, and position relationship; and in which means are provided to readily adjust various angular re lationships between a pair of cooperating cutter discs in order to obtain and maintain an optimum shearing relationship.

, Other objects and the nature and advantages of the instant invention will be apparent from the following Patented May 25, 1965 of the upper slitter disc with a lower cutting drum;

FIG. 3 is an end elevation looking from left to right at FIG. 2, and showing by means of phantom lines the normal angular disposition of the upper slitter disc with respect to the cooperating edge of the lower slitter drum,

and showing by means of solid lines the normal cooperating cutting position between the slitter disc and slitter drum;

FIG. 4 is a view similar to FIG. 2, with portions broken away and shown in section for purposes of clarity to illustrate structural details;

FIG. 5 is an enlarged vertical section taken substantially on the plane of line 55 of FIG. 4;

FIG. 6 is an enlarged bottom plan view taken substantially on the plane of line 6--6 of FIG. 4;

FIG. 7 is an enlarged section taken substantially on the plane of line 7-7 of FIG. 4; and

FIG. 8 is a further enlarged vertical section through the upper slitting disc showing details thereof.

Referring to the drawings in detail, and first considering FIG. 1, a horizontally extending support beam or mounting bar is indicated generally at 1%, and conveniently has a dove tail cross section. The support beam will be of sufficient rigidity and strength to resist the effect of bending and torsional forces when a plurality of slitting apparatus such as that indicated generally at 12 is mounted thereon. Rotatably mounted on a suitable support shaft below the slitting apparatus 12 is a driven slitting drum or disc 14 which preferably has suitable ground cutting edges 16 and 18 at opposite sides of an annular circumferential rim. The two cutting edges 16 and 18 permit left or right hand installations of the upper slitting disc, and the slitting apparatus 12 includes means for adjusting or controlling the compound movement thereof for orientation from right to left as shown in FIGS. 3 and 5, for example, or alternatively, in opposite direction, i.e., from left to right (not shown), as will subsequently be described in detail.

The apparatus 12 comprises a substantially rectangular body member 20 including cored pocket 22 at what will be conveniently described the rear portion thereof, and has extending vertically therethrough a bore portion 24; see FIG. 4. The bore portion 24 receives therethrough a bolt 26 which has fixedly secured at the lower end thereof by means of welding 23, for example, a lower clamp block 30. It will be noted that the clamp block 30 has an angled lip 32 engaging a complementary portion of the mounting bar 10. The body member 20 has secured by means of machine screws 34 (only one shown) a mounting lip 36 having an angled edge 38 engaging on an upper complementary portion of the dove tailed mounting bar It The upper end of the bolt 26 is threaded as indicated at 40 and receives thereon a washer 42 and clamp nut 44 which cooperates with the clamp lock 30 to retain the apparatus 12 in various positions of adjustment longitudinally of the support member 10 (a plurality of units 12 can be mounted on member 10).

The body member 20 has extending therethrough a vertical bore 46 which reciprocably receives therein a guide plunger 43 preferably produced from a bronze or some other similar bearing-type material.

Fixedly secured in overlying relationship to the bore portion 46 is a single-acting or double-acting fluid motor or cylinder 50 operatively connected to a source of fluid pressure 52.

Specific details of the fluid motor 50 are not illustrated, however, the piston (not shown) will generally be of the single-acting, spring-return type or double-acting type, as is conventional.

A piston rod 54 projects from the fluid motor 50 into the bore portion 46 and includes a lowerthreaded portion 56 and engaged in a suitably threaded bore portion 58 of the guide plunger. In order to relieve the accumulation of internal pressure within the bore portion 46 above the plunger 58, a suitable relief orifice 60 is provided to communicate atmospheric pressure with the bore portion '46.

The body member 20 includes vertical guide slots 62 and 64 opening from opposite sides of the bore portion 46, and the plunger 48 has extending transversely therethrough a bore portion 66 which rotatably receives therein a mounting shaft 68, The shaft 68has journaled thereon a carriage yoke indicated generally at 70 which comprises a cam plate 72 suitably apertured at 74 to receive the left hand end of shaft 68 therethrough; see FIG. 4. Secured by means of suitable machine screws 76'to the cam plate 72 is a mounting collar element 78 to subsequently be described in detail. The mounting collar 78 includes a recess 80 which receives the enlarged complementary end 84=of the shaft 68 therein.

The shaft '68 is suitably apertured at 86 and fixedly secured therein a mounting stud 88 projecting through the slot 62 and receiving thereon a washer-spring assembly 90, and retaining nuts 92.

Operation of the fluid motor 56 results in vertical re ciprocation of the guide plunger 43, and comparable vertical movement of the shaft 68 in guide slots 62 and 64. However, it will be noted that the cam plate 72, mount- .ing collar 78 and shaft 68 are free to rotate in the bore portion '66.

Itwill be noted that the support shaft 68 defines the maintains the vertical path of movement of the cutter assembly 94 as has been previously described and as is readily apparent from FIG. 4.

In order to obtain controlled oscillation of the cutter assembly 94- about the shaft 68, cam means indicated generally at 96 is provided.

The cam or control means 96 comprises a mounting block 98 secured in overlying relationship below the bore portion 46 of the body member 20 and is retained thereon by means of machine screws 1063; see FIGS. 4 and 6, for example. The mounting block 98, as clearly seen in FIG. 4, includes a bore or orifice portion 102 therethrough which communicates with the lower end of the bore portion 46 in which the plunger 48 reciprocates to relieve the accumulation of pressure beneath the plunger 48.

The cam plate 72; see FIG. 5, for example, includes at opposite lower end portions thereof slightly downwardly angled cam surfaces 164 and 106 which terminate in inwardly disposed arcuate portions 108 and 110, respectively. When the apparatus is in operation, only one of the cam surfacesis used, depending upon whether the cutting edge 18 of the cutting drum 14 is being used, or if the installation is reversed and the cutting edge 16 is being used. This will be readily apparent to those skilled in the art, in view of the structure to subsequently be described in detail.

Formed on the inner surface of the cam plate 72 facing the adjacent surface of the mounting block 98 is downwardly opening guide recess 112; see FIGS. 4-6, for example. The mounting block 98 has extending transversely therethrough a bore portion 114 having disposed in one end thereof a retaining ring 116 and circular sealing plate 117 and have reciprocably supported therein a guide plunger 118 subject to the force of a compression spring 120 retained in the bore portion 114 bymeans of a second retainer plate 121 and, retaining ring 122.

The mounting block 98 has communicating with the bore portion 114 a guide slot 124,- and the plunger 118 has mounted therein and extending through' the guide slot 124 a threaded mountingshaft portion 126 upon which a rotatable cam follower element 128 is'mounted. Suitably mounted on a shaft. 130 is a cam follower 132 which will engage the cam edge 104 of the cam plate 72 and move toward the arcuate portion 108 when thecutter assemby 94 is in its lower-most of solid line position shown in'FIGS. 2 and 3; it will be noted that thefollower 132 does not engage thearcuate portion 198 and thus permits a range of adjustment of pressure between cooperating cutting edges,

When, the cutter assembly 94 is inthe phantom line position, the spring 120'will react against the plunger 118 which, "in turn, will react through the cam follower 124 on thegroove 112 on the inner surface of the cam plate "to accordingly urge the campla te and cutter assembly into outwardly extending angular relation as clearly shown in FIG. 3.

When the fluid motor 50 is activated, and the cutter assembly 94 is lowered, the camfollower 132 will engage the cam edge 104 accordingly causing the plate 72, i.e., the cutter assembly, to move to the left or the solid line position shown in'FIG. 3, after the blade cutting edges overlap, and the apparatus will be in condition for slitting webs, trimming the edge of the web, etc.

Upon relief of pressure in the fluid motor 50, which was described as being one-way acting fluid motor which is spring urged to an inoperative position; as the guide piston 48 moves to theupper phantom line position of FIG. 2, for example, the spring12t will be effective to immediately move the disc cutter away from the cooperating cutting edge 18 A double-acting fluid motor could be used to control movements in both an operative and inoperative-position.

It will be noted in FIG. 5, for example,-that the mounting block 98 includes an aperture 134 in which the shaft 130 of the cam follower 132 may be mounted foralternatively' utilizing the cutting edge 16 of the cutter drum 14 as mentioned above. The springv 120 would be in engagement with the opposite end of the guide plunger 118-for attaining the reverse movement mentioned, and substantially instantaneous outward movement of the cutter assembly is aifordedwhen the fluid motor 50 is not being activated.

The range of movement is relatively slight, i.e., the

slitter blade of the cutter assembly moving approximately A; of an inch away from the cooperating cutting edge or" the lower slitter drum.

The showing in FIG, 3 has been exaggerated in order to emphasizepthe range of movement which. occurs when the cutter assembly 94 reaches its lowermost position.

As previously mentioned above, the carriage yoke 70 is retained on the cam plate 72 by means of screws 76, and the yoke 78 of the carriage yoke assembly is substantially G-shaped in cross-section; see FIG. 7, for exarnple, and includes a leg 136 secured in juxtaposed relation on the cam plate 72, a transverse leg 138 substantially parallel to the plane of .the slitter disc to be described, and a leg 140 parallel to leg 136.

The transverse leg 138 includes a transverse aperture 142 which has extending therethrougha mounting nutand-bolt assembly 144 including a headed bolt 146,,wash er 148 and clamp nut i150 receiving the threaded end of the bolt 146.

Mounted on the assembly 144 is an elongated mount ing post or bar 152, which preferably has a rectangular cross section as seen in FIG. 7. The bar or post 152 includes an intermediate vertically extending slot 154 in which a suitably conformed end 156 of the nut 150 projects.

The post 152 includes a horizontally extending lug portion 157 in which is threadedly received a knurled abutment screw 158, the lower end of which engages the upper surface of the substantially rectangular clamping nut 150; see FIGS, 1-4.

When the clamp nut and bolt assembly 144 is in a loosened condition, the screw 158 may be rotated to vertically adjust the mounting bar or post 152 with respect to the yoke 78. This adjustment will control the amount of overlap between the cutter drum 14 and the cutter disc mounted" on the lower end of the post 152 and to be presently described.

The mounting :bar or post 152 is transversely apertured at 160 adjacent the lower end thereof, and has mounted thereon a slitter disc assembly indicated generally at 162. The slitter disc assembly 162 comprises a mounting hub 164 including a transverse recess 166 receiving therein roller bearing assemblies 168 which r-otatably support a mounting shaft 170; see FIG. 8. A cover plate 172 is retained in overlying relationship to the recess 166 'by means of machine screws 174 or the ike.

The shaft 170 is retained against rotation with respect to the mounting bar 152 by means of a suitable key 176, and an abutment collar 178 is disposed opposite a clamp nut 180 threadedly engaged on the terminal end of the mounting shaft 170; which shaft projects through the transverse aperture 160 at the lower end of the mounting bar.

The hub 164 includes an annular mounting flange 182 and has oircum-posed thereabout a suitably circular slitter disc 184 retained on the flange 182 in juxtaposed relation thereto by means of machine screws 186.

The peripheral cutting edge 1% of the cutter disc 184 will be in overlapped relationship with respect to the cutting edge 18 or 16, and due to resharpening, though the diameter of the cutting disc 184 may be reduced, the vertical adjustment provided by means of the screw 158 will compensate for regrinding of the disc. Further, the disc 184 may be readily removed from the mounting hub 164 by removal of the screws 186, for example.

The plane of the disc 184 is disposed at a slight angle with respect to a plane passing through the cooperating cutting edge 18 of the drum 14. Further, the axes of rotation of the cutting drum 14 and disc 184 are not in exact alignment, i.e., the axis of rotation of the cutting disc 184 slightly being advanced or leading with respect to that of the axis of rotation of the drum; see for example FIG. 2.

The so-called lead angle just mentioned is attained by means of structure to be presently described in detail.

The leg 136 of the yoke 78; see FIG. 7, has fixed thereon a hemispherical abutment element 1% engageable with the edge 192 of the mounting bar 152.

Disposed vertically above and below a point of engagement between the hemispherical abutment element 190 and the edge 192 of the mounting bar, and mounted on the leg 140 of the yoke, is a pair of abutment screws 194 and 196, the terminal ends thereof respectively engaging the edge 198 of the mounting bar 152.

Accordingly, when one of the screws 194 or 196 is backed off the other may be tightened, and the longitudinal axis of the mounting bar upon which the cutting disc 184 is mounted may be adjusted angularly with respect to the abut-ment element 190 which is, in a limited sense, a pivotal abutment element. In this manner, the angular lead angle of the cutter disc 184 may be adjusted with respect to that of the cutter drum 14; this adjustment is further made apparent when considering FIGS. l-4.

In order to adjust the shear-angle relationship of the slitter disc 184 with respect to a plane passing through the cutting edge 18, for example, the leg 138 of the yoke 78 has mounted thereon, in offset relationship with respect to the longitudinal axis of the mounting bar 152 which passes through the axis of rotation of the slitter disc 184, a pair of abutment elements having hemispherical heads 2%, see FIG. 7, in engagement with the adjacent surf-ace 262 of the mounting bar 152. The 'leg 13 8 of the yoke has a pair of threaded transverse bores 204 which receive therein set screws 206 having hemispherical terminal ends 208 in abutting engagement with the surface 202 in spaced relation on the opposite side of the longitudinal axis of the mounting bar 152. 'It will be noted that the aperture 142 is substantially larger than the diameter of the bolt 146 and thus when the nut and bolt assembly 144 is loosened or backed off, the set screws 206 may be adjusted to provide the required shear angle or angular relationship between the plane of the slitter disc and the effective cutting edge 18 or alternatively 16 depending upon which type of installation is being utilized.

The adjustments referred to above, are in the nature of hundredths or thousandths of an inch, and accordingly are relatively minute. However, this slitter apparatus will afford an extremely accurate and adjustable out which is of the critical character required when slitting or trimming huge rolls of :a continuous web of paper for newsprint, bond paper for stationery etc.

Although only one installation of a slitter apparatus has been described in detail, for example that used to trim the edge of a continuous web of paper, or paper product material, it will be readily understood that a plurality of these units may be readily adjusted longitudinally of the mounting bar 10. Once the apparatus 12 has been positioned on the mounting bar 10, the adjustment afforded by the screw 158, screws 194, 196 and set screws 206 are accomplished. In the event the cutter disc 184 has to be removed and regr-ound, this may be accomplished in a relatively simple and expeditious manner. 'After regrinding, the adjustment screw 158 may be used to lower the cutting disc 184 the necessary amount to compensate for that material which has been ground off during the resharpening. However, the shear angle and lead angle will be maintained, and further adjustments thereof are independently made as required.

Additionally, by controlling the amount of pressure applied via the fluid motor 50, which accordingly controls vertical and subsequent horizontal movement of the slitter assembly 94, i.e., movement of the mounting bar 152 etc., the extent of horizontal movement controls the pressure between the slitter drum 14 and cutting edge 18. The movement and slitting pressure of the slitter disc will be readily determined by means of suitable pressure gauges provided at a remote console to control the fluid motor 50. The slitter disc 184 is rotated due to frictional engagement between the slitter drum 14 and the peripheral edge of the slitter disc 184, the drum 14 (it being understood that there are a plurality of these drums disposed on a suitable drive shaft) will be power rotated.

Briefly in review, the apparatus just described avoids the possibility of damage to the cutting edges or blades while engaging and disengaging as follows:

(a) When disengaged, the slitter disc 184 is retained in its uppermost position in the phantom line position shown in FIG. 2, and slightly to one side by virtue of the eifect of the spring (b) The fluid motor 50, which is used to force the slitter disc 184 downwardly, will not cause the cutter edge 188 to engage on the outer surface of the slitter drum 14 inasmuch as the spring 129 continues to hold the disc in the phantom line position shown in FIG. 3 until the cutting edge 188 extends below the outer surface of the drum 14;

(0) At the end of the downward stroke or movement of the cam plate 72, the cam follower 132, which engages the cam edge 194, is effective to draw the slitter disc 184 into its adjusted shear angle relationship with respect to the cutting edge 18 as illustrated by solid lines in FIG. 3 and the extent of horizontal movement may be controlled;

lieved in the fluid motor 50, the slitter disc first moves horizontally to the phantom line position shown in FIG. 3, and then. the assembly moves vertically back to the phantom line position shown in FIG. 2;

(2) Means are provided for adjustment of the most effective shear angle, most effective lead angle, the most effective amount of pressure contact in overlap be tween the cooperating cutting edges, and means are provided to compensate for the reduction of the slitter disc diameter due to the regrinding;

(f) The amount of contact pressure between the cutting edges of the upper slitter disc and the lower slitter drum canbe adjusted through a range of anywhere from 2 to pounds, forexample, by means of a suitable pressure regulator in remote console which will be operatively connected to thefluid line 52.

It will be obvious to those skilled in the art that various changes may be made without departing from the scope of the invention and therefore the invention is not limited to what is shown in the drawings and described in the specification but only as indicated in the appended claims.

What is claimed is:

1. Apparatus for slitting a continuous web of material comprising a support member, a body member mounted on said support member, first cutter means having a circular cutting edge and mounted below said body member, a slitter assembly including a depending second cutter means having a circular cutting edge and journaled on said slitter assembly on a fixed axis of rotation for driving,

shear-angle engagement with said first cutter means, said slitter assemblyand body member including means pivotally and reciprocably mounting said slitter assembly on said body member on an axis of rotation above and substantially normal to the axis of rotation ofsaid first cutter means, fluid motor means on said body member operatively connected to .said slitter assembly for reciprocating said slitter assembly at said means pivotally and reciprocably mountingsaid slitter assembly and moving said second cutter means edge toward said first cutter.

means edge, means on said slitter assembly normally urging said second cutter means edge away from first cutter means edge and cam means on said body member and said slitter assembly and including camming portions for pivoting said slitter assembly and said second cutter means edge bodily toward and away from said first cutter means edge during reciprocable movement of said slitter assembly during operation of said fiuid motor means.

2. The apparatus of claim 1 in which said slitter assembly includes mounting means thereon for adjusting the relative overlap between the cutting edges of said first and second cutter means.

3. The apparatus of claim 1 in which said slitter assembly includes means adjustably mounting and rotating said second cutter means on an axis substantially normal to the axis of rotation of said second cutter means for adjusting and maintaining the optimum shear-angle between the cutting edges of said cutter means.

4. The apparatus of claim 1 in which said slitter assembly includes adjusting means for orienting the axis of rotation of said second cutter means out of vertical alignment with the axis of rotation of said first cutter means.

5. The apparatus of claim 1 in which said body member includes a guide element connected to said fluid motor means and reciprocably mounted therein, said guide element including a shaft journaled therein and extending transversely of said body member, said shaft element being terminally and pivotally connected to said slitter assembly.

6. The structure of claim 1 in which said slitter assembly includes a cam plate disposed at one side of said body member, said cam means comprising a cam element on said body member, projecting laterally from said one &

side of'said body member at which said cam plateis dis posed, said cam plate including a cam edge portion engageable with said cam follower element during recipro- Cation of said slitter assembly and controlling relative horizontal movement of said cutter means with respect to each other.

7. The apparatus of claim 6 in which saidbody member includes spring means operatively connected to said cam plate and normally urging said cam edge portion out of engagement'with said cam follower.

8. The apparatus of claim 7 in which said spring means comprises a guide element pivotally supported on said body memberv for movement in thesame'direction toward which the axis of rotation of said second cutter member extends, and abutment element mounted on said guide element and projecting laterally from said body member toward said cam plate, said cam plate including a guide portion displaceably engaged I on said abutment element.

9. The apparatus as set forth in claim 1 in which said slitter. assembly comprises a carriage-yoke member connected to said means pivotally and reciprocably mounting said slitter assembly on said body member, a mounting post mounted on said carriage-yoke member and depending therefrom, said second cutter means being journaled on a lower end portion of-said mounting post.

10. The apparatus as set forth in claim 9 in which said carriage-yoke member includes releasable fastening means extending transversely throughsaid mounting-post for' adjustably'retaining said mounting-post thereon.

11. The apparatus as set forth in claim 10 in which said fastening means extends transversely through said mounting-post forming an axis of rotation thereat parallel to the axis of rotationof said second cutting means.

12; The apparatus as set forth in claim 11 in which said carriage-yoke member includes. adjustable abutment means engaging one portion of said mounting-post membet, and fixed abutment means disposed at an opposed portion of said mounting-post for pivotally adjusting said mounting-post in angular relationship with respect to the axis of rotation of said first cutter means.

13. The apparatus as set forthin claim 9 in whichsaid carriage-yoke member includes a fixed abutment engaging one side of said mounting-post in spaced relation from the longitudinal axis thereof, and an adjustable abutment attain controlled cutting edge overlap.

References Cited by the Examiner UNITED STATES PATENTS 6/36 Thibedeau 83-482 2,212,457 8/40 Schrier 83-482 2,571,201 10/51 Clenr 83-482 2,897,893 8/59 Rockstrom 83-482 3,041,907 7/62 'Gallagher 83-504 X 3,091,146 0 5/63 Bulk 83-482 X,

FOREIGN PATENTS 1,024,341 2/58 Germany.

ANDREW. R. JUHASZ, Primary Examiner.

Claims (1)

1. APPARATUS FOR SLITTING A CONTINUOUS WEB OF MATERIAL COMPRISING A SUPPORT MEMBER, A BODY MEMBER MOUNTED ON SAID SUPPORT MEMBER, FIRST CUTTER MEANS HAVING A CIRCULAR CUTTING EDGE AND MOUNTED BELOW SAID BODY MEMBER, A SLITTER ASSEMBLY INCLUDING A DEPENDING SECOND CUTTER MEANS HAVING A CIRCULAR CUTTING EDGE AND JOURNALED ON SAID SLITTER ASSEMBLY ON A FIXED AXIS OF ROTATION FOR DRIVING, SHEAR-ANGLE ENGAGEMENT WITH SAID FIRST CUTTER MEANS, SAID SLITTER ASSEMBLY AND BODY MEMBER INCLUDING MEANS PIVOTALLY AND RECIPROCABLY MOUNTING SAID SALITTER ASSEMBLY ON SAID BODY MEMBER ON AN AXIS OF ROTATION OF SAID FIRST SUBSTANTIALLY NORMAL TO THE AXIS OF ROTATION OF SAID FIRST CUTTER MEANS, FLUID MOTOR MEANS ON SAID BODY MEMBER OPERATIVELY CONNECTED TO SAID SLITTER ASSEMBLY FOR CECIPROCATING SAID SLITTER ASSEMBLY AT SAID MEANS PIVOTALLY AND RECIPROCABLY MOUNTING SAID SLITTER ASSEMBLY NORMALLY URGSAID SECOND CUTTER MEANS EDGE TOWARD SAID FIRST CUTTER MEANS EDGE, MEANS ON SAID SLITTER ASSEMBLY NORMALLY URGING SAID SECOND CUTTER MEANS EDGE AWAY FROM FIRST CUTTER MEANS EDGE AND CAM MEANS ON SAID BODY MEMBER AND SAID SLITTER ASSEMBLY AND INCLUDING CAMMING PORTIONS FOR PIVOTING SAID SLITTER ASSEMBLY AND SAID SECOND CUTTER MEANS EDGE BODILY TOWARD AND AWAY FROM SAID FIRST CUTTER MEANS EDGE DURING RECIPROCABLE MOVEMENT OF SAID SITTER ASSEMBLY DURING OPERATION OF SAID FLUID MOTOR MEANS.

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