US2872126A - Rewinding machine - Google Patents

Rewinding machine Download PDF

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Publication number
US2872126A
US2872126A US498809A US49880955A US2872126A US 2872126 A US2872126 A US 2872126A US 498809 A US498809 A US 498809A US 49880955 A US49880955 A US 49880955A US 2872126 A US2872126 A US 2872126A
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Prior art keywords
rewind
shaft
arm
roll
axis
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US498809A
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English (en)
Inventor
Rockstrom Leonard
Aaron Charles
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Cameron Machine Co
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Cameron Machine Co
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Priority to BE546676D priority Critical patent/BE546676A/xx
Application filed by Cameron Machine Co filed Critical Cameron Machine Co
Priority to US498809A priority patent/US2872126A/en
Priority to FR1153110D priority patent/FR1153110A/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H18/00—Winding webs
    • B65H18/08—Web-winding mechanisms
    • B65H18/26—Mechanisms for controlling contact pressure on winding-web package, e.g. for regulating the quantity of air between web layers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H19/00—Changing the web roll
    • B65H19/22—Changing the web roll in winding mechanisms or in connection with winding operations
    • B65H19/2238—The web roll being driven by a winding mechanism of the nip or tangential drive type
    • B65H19/2253—The web roll being driven by a winding mechanism of the nip or tangential drive type and the roll being displaced during the winding operation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2301/00—Handling processes for sheets or webs
    • B65H2301/40—Type of handling process
    • B65H2301/41—Winding, unwinding
    • B65H2301/414—Winding
    • B65H2301/4148—Winding slitting
    • B65H2301/41486—Winding slitting winding on two or more winding shafts simultaneously

Definitions

  • This invention relates to improvements in rewinding machines, and more particularly to improvementsin control means for slittingand rewinding machines.
  • the invention is shown, by way of illustration, asembodied in a slitting and rewinding machine employing two shafts for supporting two groups of rewound or rewind rolls, such a machine being referred to in the art as of the duplex type.
  • a slitting and rewinding machine employing two shafts for supporting two groups of rewound or rewind rolls, such a machine being referred to in the art as of the duplex type.
  • certain features of-the invention are useful in machines of other types.
  • the mill web passes around a constant speed roll, known as a contact drum, or a platen drum against which the slitters or cuttersoperate to cut the web-into a pluralityv of smaller rewind widths, although slitting may be done at other locations.
  • a contact drum or a platen drum against which the slitters or cuttersoperate to cut the web-into a pluralityv of smaller rewind widths, although slitting may be done at other locations.
  • These smaller widths pass to the rewind rolls which rest against the driven contact drum, the several rewind rolls being wound upon rewind shafts.
  • apparatus of this class has not been able to control adequately the pressure between the rewind rolls and such contact drum nor have such prior art machines been adequately equipped for the purpose of permitting anoperator. so to control the pressure between the rewind rolls and contact drum, such pressure being herein sometimes referred to as roll-contact drum pressure or contact pressure.
  • One of the objects of the present invention is to provide novel means for controlling such contact pressure where- 'by a superior quality control of the end product is. at-
  • Another object is to, provide a slitting and rewinding
  • Still another object is toprovide asingle apparatus ofthis characterh the versatility of which i sisuclith capable ofslitting and winding; lightheaiyf, stre h relatively stiff plastics, and Ianiinatesofall type wax d' r oate ati ekr ft Q hndr l'sj t dth CS d othermaterials.
  • i Another object is to provide an apparatus of' this char: acter whichcan provide easily and completely 'con'trol lable rewind roll quality wherein there is provided, an automatic rewind d nsity.
  • Control means whichf'isfad ⁇ justable while the apparatus is running: and wherein the rewind tension is positively isolated frorn the unwind en; sion,' th at is, the web tension in the region of the. tiflf Wind, pat n r l nd here e. nw h fw h ls bn prevented from building up in the rewind 'regionofthe ppar t s St uhhothe object to, r d a parat h h character wherein roll density can be commitments,- matigally with high precision between substantial" limits whe eby. he W1 an h r. of sof hr r chhsist y Still a further.
  • object is to provide noveljm'eanstor antorna tically balancing the torque. which acts jupohtne I PPQIi IE ai s for he w nsi shaft, sh h w qhe e due to the pull Qtthh Web. bein l l d- P0 l
  • Another object is to provide novel connterbalan ng means for automatically counterbalancingf the static Weigh o he wi h ma ia as it hui dhh i he rew n
  • still a further object is to prov fe h' thal i s e e h tst was t supporting arms .for the rewind.
  • Fig. 1 is a sehematic diagram illustrating one form of apparatus embodying the presentinvent n w' particular reference to the interconnections fir a'ph nj a 'c ysterhhmp y d th r y; i
  • F ig; 2 is a side elevationof one form ofapparatu semperbodying the present invention and in particular illiistrating the rewind rolls and their supporting shaftsfin association with cam control means which in turn govern p ma ntc a ah m an o cou terhalah cih the static weight of the rewind rolls as, theyhuildgup in i me e Fig.
  • 3 is a front elevation of the rear pivot'shaftrto which is secured two supportingarmsfon the-rear rewind f u h figure l a n r in o r sp ing; mean mploy d ou lan h e s icweight ttsuch arms and rewind shaft; 4
  • Fig. 4 is a sectional view-takqn substantiallyon line 4 4 of Fig. 3;
  • Fig. 5 isa frontelevation'of'a couuterbalancing-mechanism for the front rewind arms and frontjrewindtshaft employed in the apparatus and shows a pair of coil springs wound about a central shaftfor this purpose;
  • Fig. 6 is a sectional view taken substantially on line 6 6 of Fig.
  • Fig. 7 is a sectionalview taken substantially along line 77 of Fig. 5;
  • Fig. 8 is a side view of a rewind roll counterbalance valve means employed in the invention, including a sliding cam device which is adjustable in terms of the number of inches of the width of the web material wound on the pertinent rewind shaft;
  • Fig. 9 is a front elevation of the parts shown in Fig. 8.
  • Fig. 10 is a side elevation of the novel apparatus showing the latter on the opposite side thereof with respect to that shown in Fig. 2 and in particular illustrating an offset drive pulley construction wherein the axis ofeach of the respective drive pulleys for the respective rewind shafts is offset with respect to the pivot axis of its respective rewind arms, for the purpose of counterbalancing the pull of the web acting upon the respective support ing arms; 1
  • Fig. 11 is a schematic view on a somewhat enlarged scale as compared to Fig. 10 and illustrating in greater detail the offset of the axis of the drive pulley for each rewind shaft with respect to the pivot axis of the sup porting arms for such shaft and also illustrating schematically the several moment arms and moments which are created in the counterbalancing of the web pull;
  • Fig. 110 is a schematic showing of certain parts of Fig. 11 in an intermediate position and also illustrating schematically certain of the moments and moment arms instantaneously occurring;
  • Fig. 11b is a schematic showing in side elevation of counterbalancing means which performs a function analogous .to that of the means shown in Fig. 11.
  • Fig. 12 is a graphical showing of the relationship of two of the opposing moments which act about the axis of the front rewind roll supporting arms.
  • the apparatus comprises a slitting and rewind device generally designated 20 which includes a pair of rewind shafts 21 and 22 which are respectively the front. and rear rewind shafts.
  • the front rewind shaft is supported by a pair of rewind arms 23 and 24 which at the inner ends thereof, that is, the lower ends as viewed in this figure, are mounted for angular move-' ment about a fixed or primary axis, such inner ends of the arms thus being mounted upon a pivot shaft 25 which is journaled for angular movement in the frame of the apparatus.
  • the rewind shaft 22 in turn is supported by a pair of rewind arms 26 and 27 which, at the inner ends thereof, are mounted upon a pivot shaft 28 which also is mounted for angular movement in suitable journals in the frame of the apparatus whereby said rewind arms 26 and 27 also are adapted for angular movement about a primary axis, namely, that of the shaft 28.
  • the shafts 21 and 22 are shown in raised or spaced relationship with respect to a contact drum 29, partially about which there passes the web material which is slit and thereafter wound into rolls upon the rewind shafts 21 and 22.
  • the slitting devices comprising a plurality of wheel- .like knives for pressing against the contact drum 29, are
  • I -Th'e co ntact drum 29, as aforementioned, is driven at a constant speed by any suitable means (not shown) and the rewind shafts 21 and 22 are driven at variable speeds,
  • the drive and speed control means for said 4 drum 29 and shafts 21 and 22 may be similar to that shown and described in U. S. Patent No. 2,650,039, granted August 25, 1953, to Thomas N. Carter.
  • Fig. 1 there is schematically shown a pair of coil springs 30, 31 which respectively are coiled about the front pivot shaft 25.
  • Such coil springs at the inner extremities thereof are relatively fixed whereas the outer extremities thereof are secured to the respective rewind shaft support arms 23, 24 in such a manner that as such support arms shift angularly in a counterclockwise direction towards the contact drum 29, the coils thereof are wound up thereby increasing the force exerted upon the support arms 23, 24 to counterbalance the static weight thereof, together with the weight of the rewind shafts 21.
  • justable arm 35 is prevented from shifting angularly thereby anchoring theaforementioned spring extremity 30a.
  • the opposite extremity of the spring 30 at 3% (Fig. 5) is rigidly secured to the shaft 32 by means of a clamp 36 which is analogous to the clamp 33.
  • the opposite extremities of the spring 31 are analogously secured to aspring collar, such as 37, analogous to collar 34, and to aclamp 38 which is analogous to the clamp 36.
  • the aforementioned linkage which operatively interconnects the shaft 32 to the pivot shaft 25 is partially shown in Fig. 6 and comprises a lever arm 39 and a rod 40 which is pivoted at 41 to one extremity of the lever arm 39, the opposite extremity of the rod 4% being pivotally secured to another lever arm (not shown) which in turn is attached suitably to the pivot shaft 25.
  • FIG. 3 the counterbalance system for the rear shaft will be described which differs somewhat from that of Fig. 5 by virtue of the fact that the two opposite counterbalance coil springs 42 and 4-3 are associated at the inner ends thereof by means of two spring control sleeves 44 which are similar but of opposite hand.
  • the spring 42 is operatively connected'to the system as follows: The outer extremity thereof at 4211 is secured by means of a clamp 45 to a collar-46 which is secured to the frame of the apparatus, whereas outer extremity 42b of the spring 42 is secured by means of a spring clamp 47 to a flange 44a of the lefthand sleeve 44.
  • an adjustment lug 50d having a here through which passes the aforementioned bolt Stla and which further is provided with trunnions 50a and 56 which respectively engage suitable bores in the sleeve flanges 44c and 440.
  • trunnions 50a and 56 which respectively engage suitable bores in the sleeve flanges 44c and 440.
  • the pair of power devices for such rear shaft comprise pneumatic power cylinders respectively designated 53 and 54 which are respectively drivably connected with the support arms 26 and 27.
  • the pneumatic devices 53 and 54 are respectively provided with pistons 55 and 56 which are interconnected with their supporting arms 26 and 27 by means of piston rods 57 and 58.
  • Fluid under pressure preferably air
  • a control valve 59 which in turn is under the influence of two different factors: (a) the angular position of the arms 26 and 27,; and ('0) the sum in inches of the rewind roll widths on the given rewind shaft, that is, the weight of the rewind rolls in terms of the widths thereof.
  • the latter factor comprises a prorated share of the weight of the parent roll which is wound upon the rewind shaft. That is, the total weight of a parent roll, for example, of sixty inches in width, is known and if the slitters are so adjusted, for example, to rewind a total of thirty inches of such width of the parent roll upon a rewind shaft, then the latter factor (b) is 5 adjusted in such a way that it reflects the rewinding of thirty inches of the parent roll.
  • the total weight of the parent roll need not be known.
  • the adjustment for the factor (b) above mentioned is made upon the apparatus, as will be set forth below, for both the front and the rear rewind shafts in such a way that both adjustments reflect the total width of the parent roll in inches (or whatever suitable term is desired) and consequently an adequate adjustment is made for the prorated share of the parent roll which is ultimately to be wound upon the rewind shaft.
  • valve 59 by means of a control rod 6! is placed under the influence of a control cam 61 which is angularly shiftable in response to angular movement of the support arms 26, 27, such cam being suitably operatively interconnected thereto, for example, to the pertinent pivot shaft 28.
  • the cam 6i by angularly shifting upon its axis 62, is capable of shifting, in the direction of the arrow 63, a ramp element 64 which is adjusted in slope in response to the aforementioned factor (b) in accordance with the sum of the rewind roll widths in inches,. reference being had for this purpose to a suitably graduated scale at 65, the adjustment being made with theaid of a pointer 66.
  • the aforementioned ramp element 64 is retricted to move in the direction of the arrow 63 by a carriage 67 which, as is well shown in Fig. 9, is restricted in move .ment in a vertical direction by means of guides 68 and 69 which move in vertical grooves 70 and 71, respectively,
  • the carriage 67 is urged upwardly by means of a coil spring '74 (Fig. 9) which provides the driving power for the carriage 67 and hence for the ramp 64, the angular movement of the cam 61 distorting the spring 74 in response to the angular position of the support arms 26, 2'7.
  • a coil spring '74 (Fig. 9) which provides the driving power for the carriage 67 and hence for the ramp 64, the angular movement of the cam 61 distorting the spring 74 in response to the angular position of the support arms 26, 2'7.
  • the ramp 64 thus can be adjusted in its angular position about an adjustment shaft '75 thereby to control the slope of such ramp and henceto superimpose the correction or compensating factor for the sum of the rewind roll widths upon the correction factor for the angle of move ment of the support shafts 2'6, 27.
  • Shaft 75 is mounted for angular movement upon arms 75a of the carriage 67.
  • a cam follower 64a (Fig. 8) in the form of a roller rides upon the ramp 64, such follower being mounted for rotation upon an arm 64b which is angularly shiftable about a fixed pivot 64c.
  • the roller 64a is coaxial with shaft 75 when cam 61 is in its zero or no correction position.
  • the shaft 75 which supports the ramp 64 can be frictionally held in a desired angular position after it has been suitably adjusted by well known clamp means.
  • the graduations 65 are formed upon a suitable plate 76 which may be secured to the guidepost 73.
  • the fluid pressure which is under the influence of the control valve 59, is directed to both of the pneumatic cylinders 53 and 54 in a manner to be more fully described herebelow.
  • Such air under pressure is conducted to the pneumatic cylinders'53 and 54 for the purpose of either raising or lowering the rewind shaft 22 by means of a four-way main valve 81 which is controlled by means of a hand lever 82, the latter being adjustable in position to the position shown in broken lines respectively at the right and left for raise and lower, or alternatively to a central position, as shown in solid lines for run as will appear more fully hereinafter.
  • the main valve 81 is interconnected to the conduit 80 by means of a conduit 82a, and is respectively connected to the raise sides of the pneumatic cylinders 53 and 54 by means of a conduit 83 which is directed to a check valve 84, the latter having a bypass restriction.
  • the check valve 8- is provided with a ball check 84a which will permit the pas sage of air towards the cylinders 53 and'54 but not away therefrom, and is also provided with a bypass restriction 84b for a purpose that will appear hereinafter.
  • the check valve 84 by means of a conduit 85, in turn is connected to a conduit junction 86 from which emanate conduits 87 and 88 respectively connected to the raise sides ofthe pneumatic cylinders 53 and 54. That is, the conduits 87 and 88 are connected to the cylinder chambers which are in Fig. l to the right of the pistons 55 and 56 and thus on the side thereof to which fluid is directed for the purpose of raising the support arms 26, 27.
  • the main valve 81 is connected to the lower sides of the aforementioned cylinders 53 and 54 by an analogous conduit system as follows:
  • a conduit 89 interconnects the main valve 81 to a check valve 90 having a ball check device and a bypass restriction therein analogous to 84a and 84b, that is, fluid is permitted to pass toward the pneumatic cylinders, not away therefrom, by such ball check and the bypass restriction is provided therein also for a purpose to appear hereinafter.
  • the check valve 90 is in turn, by means of a conduit 91, connected to a conduit junction 92 which is respectively connected to the pneumatic cylinders 53 and 54 by means of conduits 93 and 94, the latter conduits being connected to the aforementioned lower sides of their respective cylinders.
  • main valve handle 82 is moved to the righthand position (Fig. l) which conducts fluid to the cylinders 53 and 54 by means of the following path: conduit 82a, valve 81, conduit 83, check valve 84, conduit 85 and the conduits 87 and 88.
  • the air under pressure thus urges the pistons 55 and 56 to the left, as shown in Fig. 1, thereby raising the support arms 26, 27.
  • This pressure is prevented from slamming the support arms 26, 27 against their limit-stops (not shown) by means of the back pressure existing in the lefthand chambers of said cylinders which escapes via the following path: conduits 93, 94, conduit 91, the check valve 90 (via the bypass restriction therein), the conduit 89 and an exhaust port in the main valve 81.
  • the handle 82 When the support arms 26 and 27 are in their raised position and it is desired to lower same to an operating position adjacent the contact drum 29, the handle 82 is shifted from its righthand or raise position to its lefthand or lower position, as shown in Fig. 1, thereby directing air under pressure to the lefthand chambers of the cylinders 53, 54 via the following path: 82a, 81, 89, 9t), 91 and 93, 94.
  • the support arms 26, 27 are again prevented from slamming against their lower limit-stops (not shown) by means of an analogous air cusioning which is bled from the righthand chambers of their respective cylinders via the bypass restriction 84b of the check valve 84 and a suitable exhaust port in the main valve 31.
  • the conduit 96 is divided into two portions, namely, 96a, which interconnects the valve 59 to the poppet valve 97, and a portion 9611 which interconnects said valve 97 to the conduit 85.
  • 96a which interconnects the valve 59 to the poppet valve 97
  • a portion 9611 which interconnects said valve 97 to the conduit 85.
  • the poppet valve 97 is opened by a suitable pilot valve 98 which is responsive to the plating of the handle 82 in the central position, as shown in Fig. l in solid lines.
  • the poppet valve 97 is closed when the handle 82 is in either the raise or lower position by virtue of fluid under pressure conducted thereto via a conduit 99 in which the pilot valve 98 is interposed.
  • the aforementioned cam-controlled valve 59 is isolated from the fluid infeed system when the handle 82 is in said raise or lower position.
  • the pilot valve 98 is actuated in such a way that the pressure normally acting upon the poppet valve 97 is bled therefrom and the fluid under pressure from conduits 95, 96 is allowed to pass to the cylinders 53, 54 via the cam control valve 59, the poppet valve 97 then being open.
  • main valve 81 is in a closed condition when the handle 82 is in the central position thereby insuring that the full fluid pressure in conduits 95, 96 suffers no leakage and is directed to the pistons 53, 54.
  • a hand controlled in-pressure regulating valve 100 is provided for controlling the flow of air under pressure to the lefthand chambers of the cylinders 53, 54.
  • Such in-pressure is conducted to the cylinders 53, 54 by means of a conduit 101, which interconnects the regulating valve with the main air line 80, a conduit 102 which interconnects the valve 100 to the aforedescribed conduit 91, there being interposed in the latter conduit a pressure-controlled poppet valve 103 which is under the influence of the pilot valve 98, being also connected for its control to the conduit 99, as shown in Fig. 1.
  • the conduit 102 is also divided into two portions, namely, a portion 102a which is interposed between the valve 100 and the poppet 103, and the portion 102b which interconnects the poppet valve 103 with the conduit 91.
  • the in-pressure regulating valve 100 is provided with a suitable manually adjustable knob 100a by which the inpressure or back pressure can be controlled which acts against the fluid under pressure coming via the cam controlled valve 59.
  • one of the principal objects of the present invention is to provide novel means for maintaining a minimum uniform contact pressure (rewind roll vs. contact drum pressure) during the build-up of the rewind roll, such pressure sometimes being referred to as kiss pressure, such uniform minimum pressure is normally applicable for the rewinding of relatively light, thin and stretchy web material.
  • a minimum uniform contact pressure rewind roll vs. contact drum pressure
  • kiss pressure such uniform minimum pressure is normally applicable for the rewinding of relatively light, thin and stretchy web material.
  • the poppet valve 103 is analogous in operation to the poppet valve 97 and blocks off or isolates the in-pressure regulating valve 1% whenever the handle 82 is' moved away from its central or run position.
  • the extent of the aforementioned in-pressure controlled by the regulating valve 100 can be determined by observing a gauge 104 which is in communication with the conduit 91. 1
  • a pressure sleeve 105 is employed which is urged to the left by means of a piston rod 166 which is under the influence of air pressure within a cylinder 107 in a Well known way.
  • Such pressure is conducted to the sleeve 105 by means of a crank 108 which presses against a rod 109 and thence upon an intervening plate 110.
  • Air under pressure is conducted to the cylinder 107 by means of a conduit 111 which is in communication with the main fluid supply cylinder 80.
  • a hand-controlled pressure adjusting valve 112 interposed in the conduit 111, the pressure being adjustable by observing a gauge 113.
  • the contact drum is driven, in the embodiment shown, at a constant speed and each rewind shaft is driven at a gradually diminishing speed, such speed control being accomplished by means shown in the aforementioned patent to T. N. Carter No. 2,650,039.
  • the invention is not necessarily l'imitedto this particular type of speed control but we have found it to be advantageously adapted to this invention.
  • the invention is not limited to the driving of the contact drum at a constant speed with the rewind shaft being driven at a gradually diminishing speed.
  • the present apparatus employs what is known in the art as center rewind and contact rewind, that is the rewind torques are respectively attributable to: a driving torque exerted on the rewind shaft per se, and a torque occurring because of the peripheral contact between the rewind roll and the driven contact drum.
  • center rewind that is, a direct driving of the rewind shaft
  • the web inescapably is placed under a tension because of the torque acting upon the rewind shaft. Such tension produces; a reaction.
  • a counterbalancing torque is automatically exerted upon the supportv arms about the axis of their pivot shaft, whichcounterbalancing torque differs onlyto a negligible degreeor not a t-all with the torque acting uponsaid arms attributable to the web pull.
  • the, rewind shaft 21 is preferably driven by means of endless band means, such as. an endlessbelt ll lwhich respectively passes over: a rewind shaft pulley 115 secured to and coaxial with the rewind shaft21, and'o'ver a drive pulley 116.
  • endless band means such as. an endlessbelt ll l which respectively passes over: a rewind shaft pulley 115 secured to and coaxial with the rewind shaft21, and'o'ver a drive pulley 116.
  • the direction and extent of offset of the axis or pivot of the latter pulley results in the counterbalancing ofweb pull as herein set forth;
  • the belt 114 it advantageous, but not mandatory, for the belt 114 to be of flexibiematerial, for example, oftough steel wire bonded together'with or impregnated by a rubber-like material,
  • the belt having formed on the inner surfaces thereof a plurality of parallel transversely extending ridges 114a (Fig. 10) which are uniformly spaced and designed for meshing with complementary ridges or teeth upon the peripheries of. the pulleys 115 and 116. A positive drive thereby isattained.
  • the pivotaxis (or primary axis) of the front supporting,arrns 23, 24 is indicated'by 117, whereas the pivot axis of the drive pulley 116 isindicated at118 and is offset therefrom in a direction and by. an amount' as hereinafter set forth.
  • suitable slack take-up means must be employed for the belt 114.
  • Such means comprise a slack take-up roll 119 (Fig. mounted upon a lever arm 120 which is mounted for pivotal movement upon a pivot shaft 121 and which lever arm is resiliently urged against the inner run of the belt 114 by suitable means, such as a pneumatic power cylinder 120a.
  • slack take-up means preferably should engage the belt on the run thereof which is opposite to the run which effects the belt tension reaction for balancing the web pull.
  • the web of material to be slit and rewound is first unwound from a parent roll 122, such web being designated 123, and passes over the several rolls as shown through a tension control device 124 and thence via a roll 125 onto the contact drum 29 against which the slitting is effected by means of a plurality of slitter wheels, one of which is shown at 126.
  • Each of such wheels is mounted upon suitable supporting arms, one end of which is angularly shiftable about a fixed pivot and the other end of which is urged toward the contact drum by means of a pneumatic power cylinder 127 which receives air under pressure via a conduit 128.
  • the rear rewind shaft 22 is driven in a manner analogous to the front shaft 21, by means of an endless belt 129 of similar construction and in which the slack is taken up by a slack take-up device 130 which is urged against the outer run of the belt by means of a pneumatic cylinder power device 131.
  • W Web tangent moment arm acting about the arm pivot 117, i. e., the perpendicular distance from the arm pivot axis 117 to a line tangent to the rewind roll (contact drum) at the point of contact between such roll and drum.
  • Such tangents are shown at 117a and 117b (for minimum and maximum values of rewind roll diameter).
  • T Belt tension (pull on drive belt), acts in a given direction about the arm pivot, i. e., acts in the direction of the tangent described in connection with B.
  • P Web tension reaction (must produce a moment opposed to that of T), acts in the direction of the tangent described in connection with W.
  • d' Diameter of drive pulley 116.
  • d Diameter of rewind shaft pulley (e. g. 4.186") (Note:d and d are equal .in the form shown but can be unequal.)
  • X Distance between arm pivot 117 (primary axis about which rewind shaft support armspivot) and drive pulley axis 118.
  • A Angle between points 1' and 1' as measured from the center ofthe constant drum, that is, the angle between the two points of tang' ency between the rewind roll and contact drum with R-at its minimum and maximum values respectively.
  • M The radius of the supporting arm for the rewind shaft.
  • the direction of offset (45) and extent of offset (X) of the axis of the drive pulley is selected to bring about the above equation as closely as possible as R builds up.
  • TB is substantially balanced by dTW B is so balanced by (as R varies between its limits, e. g. 3 /2 to 20"), then X and are determined.
  • R varies between its limits, e. g. 3 /2 to 20
  • X and g5 are selected to bring about the aforementioned balance or substantial balance as R varies.
  • W 4.l8 6 X I Rewind diameter and belt tension .moment BxT, the following table of moments is arrived at,.assuming that the rewind pulley diameter is, for example, 4.186" and that the FRONT ARM WEB lVIQMIlNT-TORQUE IVIOMEN'I and the drive pulley ANALYSIS Towards Contact Drum Away from Contact Drum (W) Web Tension Belt Rewind Web Tangent Moment in Moment Belt Ten. Dia., Mom. Arm Terms of Belt Arm (B), Mom. inches A bout Arm Tension T inches Pivot, inches 3% 1.08 1. 3T 1. 05 1. 05T 5 1. 3 1.09T 1.0 1. OT 7 1. 48 885'! 95 95'1 9 1. 82 848T 90 90'1 12 2.
  • the drive pulley pivot is positioned to produce a diminishing value of B as R increases, that is, the rewind roll diameter increases.
  • the length of arm M (Fig. 11) is about equal to the distance between axis 117 and the axis of drum 29.
  • the location of drive pulley pivot axis' is selectedin such awaythat the value of B diminishes, for example, by approximately 25% with respect to thefront arm system; With respect to the rear arm, the decrease is, in that example, somewhat greater,'the conditions, however, being somewhat different with respectthereto.
  • the novel apparatus being capable of reaching speeds up to 2,000 7 ft. per minute depending upon the widthof the web and its character.
  • the novel apparatus provides in a single machine heretofore unattained versatility 'in that itsis capable of slitting and :rewinding the following" types of web material: light, heavy, stretchy, rigid, laminates, waxed and coated papers, kraft, foil, impregnated fabrics., Rewind rolls produced .on this apparatus provide the precise degree of softness or hardness which may be required for'shipping, storage and subsequent end use.
  • the automatic rewind density control herein described is adjustable while-running, for example, by adjustment of the in-pressure control valve and/or'lfiilb, and
  • rewind tension that is, the tension of the web as it leaves the contact drum
  • unwind tension namely, the tension of the web as it is unwound'from the-parent roll
  • the slitting of the web can be accomplished by any one of the several'well known means, one of which'is shown in the aforementioned patent to" N. Carter
  • the consistently accurate means for controlling the aforementioned rewind roll vs. the contact drum pressure substantially eliminates operator guesswork during the operation of the apparatus. Also rewind rolls of unvarying quality are assured.
  • the setting or adjustments of the apparatus permit perfect reproduction of such satisfactory run and the pressure, sensitivity and wide range of control means provides optimum running conditions for a heretofore unattained variety of materials.
  • the present invention employs a combination surface and center rewind principle, that is, the rewinding of the rewind rolls is effected by driving the rewind shaft (center rewind) and also by driving the contact drum, the latter being rotated at a constant angular velocity (surface rewind).
  • the rewind rolls are rewound in twoseparate groups, as is well known in the art, one group being on the front rewind shaft and the other group on the rear rewind shaft, the individual rewind rolls being staggered on the separate shafts and well separated, thus effecting a positive roll separation.
  • a mechanical counterbalancing of this type may be employed, including a counterweight, which may be shiftable along a scale beam by, for example, electrical means in response to the angular movement of a given pair of support arms or to the extent of movement of the axis of the rewind (or roll) shaft from a norm position as in the embodiment of Fig. 1.
  • the countermoment for counterbalancing the static weight of the rolls can be efiected in other embodi ments by means which can be actuated in response to movement of the axis of the rewind shaft from some norm and employing, of course, the density of the material as one of the governing factors.
  • a gear train linkage from a suitable power source, such as a motor, operatively connected to the rewind shaft.
  • FIG. 11b an example of such a linkage is shown designated by the numeral 132. Only one of such linkages will be described for one of such support arms, it being understood that a similar gear train may be employed for the other support arm of a given pair.
  • a support arm 133 rotatably supports a rewind shaft 134 at its upper extremity and is pivotally mounted at its lower extremity 135.
  • the rewind shaft has secured thereto a gear 136 which is operatively connected to a motor 137 through the intermediary of the gear train shown which comprises six toothed consecutively meshing gears 138-143, inclusive, the pivot shafts of which are'mounted upon the support arm 133.
  • the feature of the modification of Fig. 11b which is analogous to the offset pivot feature of Fig.
  • a driving gear 144 (analogous to drive pulley 116), the axis 145 of which is offset from the pivot arm axis in a manner analogous to the offsetting of the axis of the drive pulley pivot, as shown in Fig. 11.
  • the driving gear 144 is drivably connected to the gear train 138143 through the intermediary of gears 146 and 147 which are mounted upon a lever arm 148.
  • lever arm 148 is pivotally secured to the arm 133 at 143a lever arm 148 is pivotally secured to the arm 133 at 143a, comprising the axis of the gear 143, and at the opposite extremity of the arm 148 the gear 147 is rotatably mounted about an axis 147:: comprising the pivot axis of the gear 147.
  • a supplementary arm 149 is pivotally mounted at one extremity at 147a and at the opposite extremity at the pivot and is able angularly to shift about the latter pivot which is fixed.
  • the pivot 135 also is fixed.
  • rewind shaft in lieu of mounting the rewind shaft upon support arms, such as 23, 24, such arms may be dispensed with and the opposite extremities of the rewind shaft, e. g. 21, can be supported in suitable tracks formed, for example, in either straight or curved parallel slotted or grooved members, suitable means being provided, of course, to prevent the rewind shaft from becoming askew or canted with respect to such slotted members.
  • Such members are provided with said tracks for receiving the opposite extremities of such a rewind shaft and for guiding same, for example, in substantially the same curved path as shown in Fig. 11 although such curved path may be straight.
  • rewind arm means a rewind shaft
  • means for pivotally supporting said arms at one end thereof for angular movement about a primary axis said arms being adapted to support said rewind shaft at the other end thereof for angular movement therewith about such axis, and on which shaft web material is to be wound into one or more rewind rolls
  • a contact drum mounted for rotation in the path of such angular movement of such rewind shaft
  • rewind arm means 'pivotally supported at one end thereof for angular movement about a primary axis, and adapted to support a rewind shaft at the other end thereof, on which shaft web material is to be wound into one or more rewind rolls
  • a contact drum mounted for rotation about a stationary axis and positioned in the path of movement of the axis of rotation of said first-mentioned shaft, such angular movement occurring about the aforementioned primary axis, whereby web material passing at least partly around said contact drum is wound upon such rewind shaft
  • power means operatively connected to such rewind shaft for winding such web of sheet material thereupon, thereby ,to create the aforementioned rewind rolls, the winding of such rolls upon such rewind shaft creating web tension moments about the aforementioned primary axis
  • rewind arm means pivotally supported at one end thereof for angular movement about a primary axis, and adapted to support ,a rewind .shaft at the other end-thereof, which shaft is. adapted in turn for the winding thereupon of web material in Qneior more rewind rolls; a contact drum mounted for rotation about a stationary axis parallel to the aforementioned primary axis and to the axis of rotation of said rewind shaft; spring means operatively connected with said arm means for counterbalancing the static weight of said arm means including that of said rewind shaft; means responsive to angular movement of said arm means from a' norm position for exerting a torque on said arm means as a function of such angular movement thereby to counterbalance the static weight of the web material wound upon said rewind shaft, said arm means angularly moving in response to the build .up of web material upon said rewind shaft; driving means for said rewind shaft comprising an endless band passing over
  • rewind arm means pivotally supported at one end thereof for angular movement about a primary axis, and adapted to support a rewind shaft at the other end thereof, which shaft is adapted in turn for the winding thereupon of web material in one or more rewind rolls; a contact drum mounted for rotation about an axis parallel to the aforementioned primary axis and to the axis of rotation of said rewind shaft; driving means for said rewind shaft comprising an endless band passing over a rewind shaft pulley connected to said rewind shaft and positioned near the outer end of said arm means, said band also passing over a drive pulley, the axis of rotation of the latter pulley being positioned near to but offset from said primary axis by a selected distance in a selected direction therefrom responsive to the variation of B as compared to the variation of where: B is the belt moment arm about the aforementioned primary axis, that is, the perpendicular distance from such axis to a line
  • rewind arm means pivotally supported at one end thereof for angular movement about 'a primary axis; a rewind shaft supported at the other end of such arm means for rotation about an axis which is parallel to said primary axis, said rewind shaft being adapted for the winding of web material 'therearound in one or more rewind rolls; a contact drum mounted for rotation about an axis parallel to the aforementioned primary axis and to the axis of rotation of said rewind shaft, said rewind rolls and drum being in peripheral contact when the machine is in operation; and means for selectively controlling the pressure of such contact independent of the static weight of such arm means, shaft, rolls, and of a web reaction torque set forth below, such means including: means operatively connected with said arm means for counterbalancing the static Weight thereof including the static weight of said rewind shaft, means responsive to the extent of angular movement of said arm means about said primary axis for exerting a torque upon said arm means acting about said primary axis
  • arm means pivotally supported at one end thereof for angular movement about a primary axis, a driven shaft supported at the other end of such arm means for rotation about an axis which is parallel to said primary axis, said shaft being adapted for the winding of web material therearound in one or more rolls; the driving of said shaft producing a web reaction torque acting on said arm means, and means for balancing said web reaction torque.
  • a rewind arm device pivotally supported at one end thereof for angular movement about a primary axis; a rewind shaft mounted for rotation at the other end of such rewind arm device, such rewind shaft being driven and being positioned for rotation about an axis parallel to such primary axis and being adapted for the winding of web material thereon in one or more rewind rolls; a contact drum mounted for rotation about an axis parallel to the aforementioned axes, said rewind rolls and drum being in peripheral contact when the'machine is in operation; and means for making the pressure of such contact independent of the static weight of such rewind arm device, rewind shaft, rewind rolls and of a web reaction torque set forth below, such means including: means operatively connected with said arm device for counterbalancing the static weight thereof including the static weight of the rewind shaft mounted thereupon, power means for exerting torque upon said arm device, and means for controlling said power means in response to the angular displacement of said arm device from
  • such angular displacement being in turn responsive to change in diameter of such rolls whereby the static Weight of web material wound upon said rewind shaft is counterbalanced, the aforementioned web material passing at least partially around said contact drum and thence being Wound upon said rewind shaft and exerting a torque upon said arm device about said primary axis attributable to web tension reaction resulting from such shaft being driven as aforesaid; driving means for driving same as aforementioned and this for said rewind shaft for applying a driving torque thereto, and means for mounting said driving means for producing a torque for substantiaily counterbalancing said web reaction torque.
  • a rewind arm device i pivot- "20 ally supported at one end thereof for angular movement about a primary axis, a rewind shaft mounted for rotation in'the other end of said rewind arm device about an axis which is parallel to said primary axis, said rewind shaft having a torque directly applied thereto for the winding of web material thereupon in one or more rewind rolls out from a parent roll; a contact drum mounted for rotation about an axis parallel to the aforementioned axes, said rewind rolls and drum being in peripheral contact when the machine is in operation; primary counterbalancing means operatively connected with said arm device for counterbalancing the static weight thereof including the weight of the rewind shaft mounted thereupon; said primary counterbalancing means comprising spring means operatively connected with said arm device for deformation in response to angular movement of said.
  • a winding machine including: a pair of rewind arms pivotally supported at one end thereof for angular movement about a primary axis, a rewind shaft mounted upon the other ends of said rewind arms and positioned there for rotation about an axis which is parallel to said primary axis, said rewind shaft being adapted for the winding thereupon of web material in one or more rewind rolls; a contact drum mounted for rotation about an axis parallel to the aforementioned axes, said web material passing at least partially around said contact drum and onto said rewind rolls upon said rewind shaft, said rewind rolls and drum being in peripheral contact; the static weight of said rewind shaft and rewind arms exerting a moment about the aforementioned primary axis, primary counterbalancing means for exerting a primary torque upon said rewind arms thereby to counterbalance the aforementioned static weight, such primary torque being a function of the extent of angular movement of said rewind arms from a selected primary norm position; a
  • a contact drum a roll shaft on which sheet material is to be wound in one or more rolls
  • drive means connected to said roll shaft for rotating same thereby to wind such sheet material thereupon
  • the axes of said roll shaft and contact drum being so disposed with the Web of sheet material being Wound upon the roll shaft under tension and exerting a force upon such roll shaft tending to cause relative movement of the axis of such shaft with respect to that of the contact drum, and means for counterbalancing such force.
  • a driven roll shaft adapted for the winding thereon of web material in the form of a roll, a contact drum, the force of gravity acting upon said roll shaft due to the mass thereof, such force of gravity also acting upon the sheet material Wound thereupon in the form of such roll, a further force acting upon said rewind shaft attributable to the tension of the sheet material as it is wound upon the roll shaft by virtue of the fact that such shaft is driven as aforementioned, such forces tending to cause relative movement of the axis of such roll shaft and the axis of such contact drum, such contact drum and material rolled upon the roll shaft being peripherally in engagement during the winding of the web material thereon, and means for respectively neutralizing such forces during the driving of such roll shaft and thus as the distance changes between the axis of said contact drum and the axis of said roll shaft.
  • a roll shaft adapted for the winding thereon of web material in the form of .a roll, a contact drum, power means connected to said shaft for exerting a driving torque thereon for driving same and thereby winding such material thereon, the force of gravity acting upon said roll shaft due to the mass thereof, such force of gravity also acting upon the sheet material Wound thereupon in the form of such roll, a further force acting upon said rewind shaft attributable to the tension of the sheet material as it is Wound upon such roll shaft by virtue of the fact that such shaft is driven as aforementioned, such forces tending to move the axis of such roll shaft with respect to the axis of such contact drum, means for respectively neutralizing such forces during the driving of such roll shaft and thus as the distance changes between the axis of said contact drum and the axis of said roll shaft, such contact drum and material rolled upon the roll shaft being peripherally in engagement, and means for exerting a controlledlforce for urging said axes toward one another.

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FR1153110D FR1153110A (fr) 1955-04-04 1956-04-04 Machine de rebobinage

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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2985398A (en) * 1956-10-11 1961-05-23 Cameron Machine Co Roll rewinding device
US3122335A (en) * 1961-05-02 1964-02-25 John Dusenbery Company Inc Web slitter-rewinder
US3179349A (en) * 1960-03-02 1965-04-20 Cameron Machine Co Rewind machines
US3198453A (en) * 1963-05-15 1965-08-03 Cameron Machine Co Automatic variable speed rewind drive
US3357651A (en) * 1966-03-04 1967-12-12 Flexipak Inc Take-up mechanism for sheet-feeding apparatus
DE2541945A1 (de) * 1975-08-08 1977-02-17 Hiroshi Kataoka Verfahren und vorrichtung zum steuern des beruehrungsdrucks der kontaktwalze einer haspel zum aufwickeln von bahnmaterial
US4150797A (en) * 1975-08-08 1979-04-24 Hiroshi Kataoka Method and device for controlling contact pressure on touch roller in sheet winder
WO1993014013A2 (fr) * 1992-01-21 1993-07-22 Minnesota Mining And Manufacturing Company Appareil d'enroulement d'une bande
US5346150A (en) * 1992-01-21 1994-09-13 Minnesota Mining And Manufacturing Company Tail gap winder
US5379962A (en) * 1992-01-21 1995-01-10 Minnesota Mining And Manufacturing Company Heated web knife
US5632849A (en) * 1992-01-21 1997-05-27 Minnesota Mining And Manufacturing And Company Tab applicator for log roll winders
US6145777A (en) * 1999-04-28 2000-11-14 3M Innovative Properties Company Single station continuous log roll winder

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB190813782A (en) * 1908-06-29 1909-05-06 Jean Goebel Improvements relating to the Winding and Unwinding of Rolls of Paper and the like.
US1267080A (en) * 1916-10-31 1918-05-21 Oscar I Judelshon Strip-winding machine.
US1964076A (en) * 1930-12-04 1934-06-26 Celluloid Corp Winding machine
US2190106A (en) * 1938-01-07 1940-02-13 Barber Colman Co Winder
US2196000A (en) * 1938-06-01 1940-04-02 Gen Electric Beam drive
US2609157A (en) * 1947-11-12 1952-09-02 Marathon Corp Winding apparatus
US2650039A (en) * 1950-11-28 1953-08-25 Cameron Machine Co Rewinding machine

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB190813782A (en) * 1908-06-29 1909-05-06 Jean Goebel Improvements relating to the Winding and Unwinding of Rolls of Paper and the like.
US1267080A (en) * 1916-10-31 1918-05-21 Oscar I Judelshon Strip-winding machine.
US1964076A (en) * 1930-12-04 1934-06-26 Celluloid Corp Winding machine
US2190106A (en) * 1938-01-07 1940-02-13 Barber Colman Co Winder
US2196000A (en) * 1938-06-01 1940-04-02 Gen Electric Beam drive
US2609157A (en) * 1947-11-12 1952-09-02 Marathon Corp Winding apparatus
US2650039A (en) * 1950-11-28 1953-08-25 Cameron Machine Co Rewinding machine

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2985398A (en) * 1956-10-11 1961-05-23 Cameron Machine Co Roll rewinding device
US3179349A (en) * 1960-03-02 1965-04-20 Cameron Machine Co Rewind machines
US3122335A (en) * 1961-05-02 1964-02-25 John Dusenbery Company Inc Web slitter-rewinder
US3198453A (en) * 1963-05-15 1965-08-03 Cameron Machine Co Automatic variable speed rewind drive
US3357651A (en) * 1966-03-04 1967-12-12 Flexipak Inc Take-up mechanism for sheet-feeding apparatus
US4150797A (en) * 1975-08-08 1979-04-24 Hiroshi Kataoka Method and device for controlling contact pressure on touch roller in sheet winder
DE2541945A1 (de) * 1975-08-08 1977-02-17 Hiroshi Kataoka Verfahren und vorrichtung zum steuern des beruehrungsdrucks der kontaktwalze einer haspel zum aufwickeln von bahnmaterial
WO1993014013A2 (fr) * 1992-01-21 1993-07-22 Minnesota Mining And Manufacturing Company Appareil d'enroulement d'une bande
WO1993014013A3 (fr) * 1992-01-21 1994-01-06 Minnesota Mining & Mfg Appareil d'enroulement d'une bande
US5346150A (en) * 1992-01-21 1994-09-13 Minnesota Mining And Manufacturing Company Tail gap winder
US5379962A (en) * 1992-01-21 1995-01-10 Minnesota Mining And Manufacturing Company Heated web knife
US5632849A (en) * 1992-01-21 1997-05-27 Minnesota Mining And Manufacturing And Company Tab applicator for log roll winders
AU681833B2 (en) * 1992-01-21 1997-09-04 Minnesota Mining And Manufacturing Company Web winding system
US6145777A (en) * 1999-04-28 2000-11-14 3M Innovative Properties Company Single station continuous log roll winder

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FR1153110A (fr) 1958-03-03
BE546676A (fr)

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