US3604649A - Method and apparatus for winding up traveling webs - Google Patents

Method and apparatus for winding up traveling webs Download PDF

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Publication number
US3604649A
US3604649A US824590A US3604649DA US3604649A US 3604649 A US3604649 A US 3604649A US 824590 A US824590 A US 824590A US 3604649D A US3604649D A US 3604649DA US 3604649 A US3604649 A US 3604649A
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Prior art keywords
winding
wound roll
pressure
web
roller
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US824590A
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English (en)
Inventor
Gerhard Walter Dorfel
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Lenox Machine Co Inc
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Ahlstrom Corp
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Filing date
Publication date
Priority claimed from FI136368A external-priority patent/FI42773B/fi
Priority claimed from FI180868A external-priority patent/FI46144C/fi
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Publication of US3604649A publication Critical patent/US3604649A/en
Assigned to LENOX MACHINE COMPANY, INC. reassignment LENOX MACHINE COMPANY, INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: A. AHLSTROM OSAKEYHITO
Assigned to LENOX MACHINE COMPANY, INC., A MA CORP. reassignment LENOX MACHINE COMPANY, INC., A MA CORP. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: A. AHLSTROM OSAKEYHTIO
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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
    • B65H18/14—Mechanisms in which power is applied to web roll, e.g. to effect continuous advancement of web
    • B65H18/20—Mechanisms in which power is applied to web roll, e.g. to effect continuous advancement of web the web roll being supported on two parallel rollers at least one of which is driven
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/40—Shafts, cylinders, drums, spindles
    • B65H2404/43—Rider roll construction

Definitions

  • a wind [50] Field of Search 242/55, 65, ing member is in pressure engagement with the generated sur- 66167'167'575'45754675531 117329/110 face of the wound roll along a meridian line thereof and is l 17 operable to produce the aforesaid uniform winding tightness.
  • a loading roller operable to apply a varia- UNITED STATES PATENTS ble force to the wound roll corresponding to the increasing 3,009,666 l l/l96l Moser 242/66 weight of the wound roll such that the contact pressure 3,178,125 4/l965 Greding 242/66 between the wound roll and the winding member is main- 3,232,549 2/l966 Stambaugh 242/66 tained constant or varies in a predetermined manner n the 3,237,877 3/1966 Printz et al 242/66 winding operation.
  • This invention relates to a method and apparatus for winding up a traveling web to form a cylindrical wound roll having a uniform winding tightness over the web width and between adjacent layers of the wound roll; by utilizing uniform pressure forces against the generated surface of the wound roll in the winding nip and a web-winding apparatus for carrying out the method according to the invention.
  • the winding tightness is regulated by changing the pressure in the pressure cylinder. Further it is prior known to provide springs in the suspension devices of the loading roller at each end so as to cause the axis of the loading roller automatically to adjust itself to the direction of the generatrix of the roll being wound, at the pressing zone, in order to produce an approximately uniform winding tightness over the width of the web even when the web thickness is different and varies over the web width.
  • rollers with adjustable meridian line There are various prior known modes of construction for rollers with adjustable meridian line. In general such rollers are utilized in roller presses in machines for producing or converting web-formed materials such as paper, foil and textile webs, but also metal webs, in which presses the deflection of the roller axis under the influence of the own weight of the roller and the outer load in the zone of the roller nip must be compensated for.
  • the so-called crowning of the shell surface of the roller has long been known. This involves that the roller radius at each point of the meridian line is increased by an amount corresponding to the expected deflection at that point, with respect to the roller radius at the roller ends. With a presupposed load the meridian line of the roller in the zone of the roller nip therefore is an exactly straight line. A roller thus crowned produces, however, only with the load that was the basis for the crowning curve, exactly the desired straight meridian line in the roller nip. With load variations the meridian line in the roller nip deviates from a straight line.
  • each of the suitably extended bearing journals of the roller is mounted in two axially spaced bearings, one of which is fixedly supported, while to the other one is applied a counteracting force which is adjustable as to its magnitude (U.S. Pat. No. 3 273 492).
  • the bending moment produced by the bearing force and the counteracting force compensates more or less exactly the load bending moment and thus decreases the deflection of the roller at the roller nip.
  • the roller shell is in the form of a hollow cylinder.
  • a-supporting beam serving to absorb the bending moment, jutting past the two end planes of the roller shell and having the protruding ends mounted on the machine frame.
  • the supporting beam is admittedly stressed by such counteracting forces and correspondingly deflected.
  • the outer load on the roller shell can, however, be compensated by means of said counteracting forces.
  • the meridian line of the roller shell remains uninfluenced by the outer load and consequently a straight line, provided the roller shell is exactly cylindrical.
  • a pressure chamber defined by the nonrotating supporting beam and having the form of an expansion chamber, is provided at the loaded side of the roller and arranged to receive pressurized oil.
  • the oil pressure produces a uniformly over-the-roller-length-distributed-counteracting load which compensates for the outer load.
  • this mode of construction has the advantage that it permits, through rotation of the supporting beam about the roller longitudinal axis, to bring the direction of the counteracting load to coincide with the direction of the outer load.
  • the object of the present invention is to improve the uniformity of the winding tightness of wound rolls over the web width as well as from layer to layer, by the utilization of uniform pressure forces against the generated surface of the wound roll in the winding nip, and to make it independent of the amount of care taken by the operating personnel.
  • Said object of the invention is achieved by virtue of a method in which, according to the invention, pressure forces are applied against the generated surface of the wound roll by means of a winding member being in contact with said generated surface substantially along a meridian line extending over the length of the wound roll, said meridian line being adjustable in a manner prior known per se; the meridian line in the winding nip is adjusted to form a straight line and, when required, the position of said straight meridian line is brought to coincide with the location of the winding nip which is migrating during the winding operation; and finally, onto the wound roll, along another meridian line positioned at least approximately diametrally opposite the winding member, is applied, ina manner prior known per se, a load the magnitude of which is variable and varies corresponding to the increasing weight of the wound roll, so that the contact pressure force applied between the wound roll and thevwinding member is maintained constant during the winding operation, or varies in a predetermined manner.
  • the method is carried out by means of a web-winding apparatus to which is continuously introduced a web, such as a paper or foil web, and which comprises a winding corepositioned transversely with respect to the web traveling direction, for receiving the web to be wound up into a cylindrical wound roll, and a winding member in pressure engagement with the generated surface of thewound roll along a meridian line, for producing the winding tightness, the web being reversed over said winding member from its oncoming direction to a direction tangential with respect to the generated surface of the wound reel.
  • a web such as a paper or foil web
  • At least the winding member which leads the web onto the wound rolls and is in pressure engagement with the wound roll along a meridian line is in the form of an oncoming winding roller with its meridian line adjustable in a manner known per se, and the meridian line of the winding roller is adjusted to form a straight line independently on the outer load in the zone of the pressure engagement with the wound roll.
  • FIG. l shows in cross-sectional and schematical view a double support roller winding apparatus according to one embodiment of the invention
  • FIG. 2 shows a cross section through a control valve shown in FIG. 1,
  • FIG. 3 relates to an alternate embodiment and is a view of a double support roller Winder, also schematically represented, with hydraulic control for the winding operation,
  • FIG. 4 relates to another alternate embodiment and is a view of a double support winder, also schematically represented and with hydraulic control for the winding operation,
  • FIG. 5 is a detail view in enlarged scale of the means for effecting simultaneous, oppositely directed displacement of the supporting beams of the support rollers shown in FIG. 4,
  • F IG. 6 is a schematic, partial cross section through the device of FIG. 5 along the line VI-VI,
  • FIG. 7 is a schematically represented partial cross section corresponding to that of FIG. 6, of another embodiment of the device of FIG. 6,
  • FIG. 8 shows a further embodiment of a double support roller winder deviating from those of FIGS. l, 3 and 4, also schematically represented, and f FIG. 9 shows another mode of the loading roller suspension for the embodiment of FIG. 8.
  • FIG. l there are provided two support rollers 10, l2 positioned horizontally in spaced relation, and mounted on a machine frame (not shown). On said support rollers 10, l2 rotates a wound roll 14 made up of an endless paper web 16. The beginning of said paper web is wound on a winding bar serving as the core 15 of the winding roll.
  • One of the support rollers l0, 12 is driven by drive means not shown.
  • a loading roller 18 having an additional loading weight 20. The roller 18 is guided in the machine frame in the vertical direction and is suspended at each end from a rope tackle.
  • the tackle can consist of a rope, a chain, a belt, a band or the like, from which the loading roller 18 is suspended, and is passed over a reversing pulley 24 mounted rotatably in the upper part of the machine frame. The free end is passed over a further reversing pulley 25 and attached to an upper portion of the machine frame.
  • the reversing pulley 25 is mounted rotatably at the upper end of the piston rod 26 of a pressure cylinder 28 attached laterally beside the support rollers 10, 12 to the machine frame.
  • the magnitude of the load applied by the loading roller 18 with its loading weight 20 against the wound reel 14 is decreased corresponding to the increase during the winding operation of the weight of the winding roll, with the effect that the force exercised between the support roller 10 serving as a winding roller, and the wound roll 14 in the winding nip, will be maintained uniform during the entire winding operation, or will vary in a predetermined manner.
  • FIG. 8 An alternate method for the suspension of the loading roller and the loading weight is shown in FIG. 8.
  • the loading roller 18 together with the additional loading weight 20 is guided in a vertical or a slightly inclined direction (:30) in the machine frame and suspended at each end from a spindle 177 at each side of the machine.
  • At the upper portion of the machine frame there are mounted two worm wheels 179 serving as nuts for the spindles and meshing in their turn with worms coupled to electric, pneumatic or hydraulic motors, adjustable as to their torque.
  • the magnitude of the load applied by the loading unit 18, 20 against the wound roll 14 is decreased corresponding to the increase of the weight of the wound roll during thev winding operation, by means of varying the torque of the motors 180.
  • Each supporting roller l0, 12 has a shell 30, 32 and a supporting beam 34, 36 extending coaxially through the shell past each shell end, and mounted rotatably at its end portions, jut'ting past the ends of the respective shells in the form of journals 38, 40 on the machine frame, in bearings 50, 52.
  • At the outer ends of each journal 38, 40 is attached one end of a lever 42, 44, the other end of which is attached to the end of a link 46, 48.
  • the supporting beams 34 are by means of pantograph linkage turned in the bearings 50, 52 corresponding to the increasing diameter of the wound/reel 14, so that the pressure prevailing at the inner side of the roller shell in the pressure chambers 54, 56v defined .by the respective supporting beams will balance the load applied against the outer surface of the roller shell in the winding nip.
  • T he meridian line of the roller shell in the winding nip is therefore a straight line and is maintained as such from the first to the last position of the wound roll, since the supporting beams 34, 36 are turned corresponding to the migration of the winding nip on the periphery of the support roller.
  • the linkage consist of four bars 58, 60, 62, 64 of equal length, attached pivotingly to each other. Each of the lower bars 62, 64 of this linkage are attached through their common pivot pin 68 to the machine frame.
  • the articulation 66 positioned diagonally opposite the stationary articulation 68 supports a reversing pulley 70 for a rope 72, one end 74 of which is attached to the loading weight or to the loading roller 18, while the other end 76 of the rope is attached to an upper portion of the machine frame.
  • this rope 72 By the action of this rope 72, the pantograph linkage will be displaced corresponding to the increase of the diameter of the wound reel 14, whereby the lower bars 62, 64 will turn around the stationary articulation 68 in an upward direction.
  • the magnitude of the force applied by the loading roller 18 and the loading weight 20 on the wound reel 14 is decreased through adjustment of the oil pressure in pressure cylinder 28, corresponding to the weight of the wound roll 14 increasing with the diameter, so that the contact pressure force between the wound roll 14 and the support roller 10 will at each moment assume the presupposed value, e.g. is maintained constant. It is also possible to wind so as to make the core harder than the outer layers, or the reverse.
  • Said adjustment of the oil pressure in the pressure cylinder 28 is carried out by means of an oil valve 78, the mutually movable parts (housing and valve body) of which are attached to the pantographic linkage, for instance, so that the housing 82 is attached to the machine frame and the valve body 84 is connected to one of the bars 62, 64 fixedly both against rotational and axial movement as shown in FIG. 2.
  • a pressurized fluid for instance pressurized oil
  • the valve body 84 is unrotatably attached to a pivot pin 92.
  • the valve body has a bore 94 connecting the lines 86 and 90.
  • the lines 88 and 90 are further connected through a cavity 96.
  • the flow openings 98, 100 are formed to correspond to the flow rate of the pressurized medium required for each position, so that the medium, in the beginning of the winding operation will enter at a small pressure the line 88 leading to the upper chamber of the pressure cylinder 28, because the flow opening 98 leading to the discharge line 86 is wide open.
  • Said flow opening 98 as well as the flow opening 100 will, as the diameter ofthe wound roll 14 increases, be more and more closed so as to first increase the pressure in the bore 94, in the cavity 96, in the line 88 and therefore then to increase the pressure in the upper chamber of the pressure cylinder 28, thus causing simultaneously a decrease of the flow rate in the line 88.
  • the winding tightness can be maintained uniform from layer to layer by the oil pressure in the pressure chambers 54, 56 of the support rollers 10, 12, since in this case the pressure force between the support roller shells 30, 32 and the wound roll 14 in the winding nip is maintained constant by the described control of the loading roller 18.
  • a double support roller winder for winding a moving paper web 16 by means of a winding bar l5 into a wound roll 14 is provided with two driven support rollers 10, l2, each of which has a support roller shell 30, 32 and a supporting beam 34, 36 extending through the shell'longitudinally and coaxially with the same.
  • Each supporting beam is sealed against the inner surface of the corresponding support roller shell, so that a pressure chamber 54, 56 is formed between the supporting beam and the support roller shell on the side exposed to the outer load, said chamber being connected to a pressure oil pump 10 through lines 112, 114.
  • each supporting beam 34, 36, jutting through the ends of the respective support roller shells and formed as journals 38, 40, are mounted rotatably in bearings 50, 52 on the machine frame and, at their axially open ends are provided with levers 42, 44.
  • the other ends of said levers are connected to the piston rod 118 of the pressure cylinder 116 by means of a link 46.
  • the two pressure chambers of the cylinder 116 are supplied with pressurized oil through a line 120 branching from line 112 and provided with a reversing valve 122.
  • the reversing valve 122 will be described later ⁇
  • a loading roller 18 lying on the wound roll 14 and having attached thereto an additional loading weight 20, suspended by means of a rope tackle at each end of the loading roller 18, the rope 22 (chain, belt, band or the like) of which is passed over a reversing pulley 24 mounted rotatably in an upper portion of the machine frame, and then overanother reversing pulley 25 rotatably mounted on the outer end of the piston rod 26 of a pressure cylinder 28 pivotably mounted on the machine frame laterally beside the support rollers l0, l2, the end of the rope being attached to the machine frame.
  • the diameter of the wound roll is measured by means of the rise of the loading roller 18, through the corresponding rotation of the reversing pulley 24 and a measuring instrument coupledl thereto.
  • the value is introduced into a computing relay 136 which forms, from the momentary value of the diameter of the growing wound roll 14 and from the specific weight of the web 16 being wound up, a suitable control signal for the subsequent control functions.
  • the value of the loading weight of the loading roller 18, varying depending on the piston force in the pressure cylinder 28 but instantaneously effective, is passed through a forcemeasun'ng device, provided at the base of the reversing pulley 24, such as a pressure-measuring cell 126, and introduced through an amplifier 128 into a computing relay 130. From this measuring value will here, together with the modulated diameter signal from the computer 132, be formed a control impulse for the controller 134, which controls the piston force in the pressure cylinder 28 and receives pressurized oil from the oil pump 110 through the line 138.
  • This control circuit thus meets the requirement of adjusting the linear pressure in the winding nips between the support rollers 10, 12 and the wound roll 14, as to its magnitude, depending in a predetermined manner on the diameter of the wound roll 14. ln order to also maintain the direction of the pressure forces in the pressure chambers 54, 56 of the support rollers 10, 12 which balance the linear pressure in the winding nip, coincident with the direction of said linear pressure, the control signal formed by the computing relay 136 is converted in a computing relay 140 into a signal representing the rotational position of the supporting beams, and passed to the reversing valve 122, in order to bring the piston rod 118 into the position corresponding to the diameter of the wound roll 14 at each moment.
  • the deflection of the support rollers 10, 12 under their own weight cannot be left without consideration. Therefore the inner pressure in the pressure chamber 54, 56 of the support rollers 10, 12 must be corrected by an amount compensating for its own weight, the value of which amount also depends on the value of the diameter of the wound roll 14 at each moment. Therefore it is necessary to form from the diameter signal delivered by the computing relay 136, in a computing relay 150, a signal representing the dependency of said pressure correction on the diameter, and to pass this signal to the pressure controller 142.
  • a manually operated relay 144 by means of which a corresponding correction of the signal produced in the computing relay 150, for actuating the controller 142, is brought forth.
  • the devices utilized in the control arrangement according to FIG. 3 are, as also the controller 134, the reversing valve 122, and the pressure controller 142, devices prior known in the controlling field; therefore it is not necessary to describe these conventional devices in detail.
  • the controller 134, the reversing valve 120 and the pressure controller 142 the so-called sucking solenoid actuators have proven particularly suitable.
  • the loading roller can be provided with a device for adjustment of the meridian line in the winding nip, and its control can be arranged according to any of the systems described in FIGS. 1 and 2 or in FIG. 3 with reference to any of the methods for the control of the support rollers.
  • the embodiment shown in FIG. 4 differs from that shown in FIG. 3 in that the device for the displacement of the supporting beams 34, 36 of the support rollers 10, 12 is different. Further the automatic device for the achievement of a wound roll which is both uniformly wound over the entire width of the wound paper web, and also from layer to layer equally tight or with respect to the winding tightness, variable in a predetermined manner, must be additionally provided with a device for taking care of the influence of the web tension in the oncoming endless paper web 16 on the support roller 10. Such an additional device can, of course, also be similar to those in the embodiments of FIG. l to FIG. 3.
  • each of the support rollers 10, l2 has a support roller shell 30, 32 and an, in the longitudinal direction coaxially with the shell through the same extending supporting beam 34, 36.
  • Each supporting beam 34 ⁇ 36 is with its portions jutting over the ends of the corresponding shell 30, 32, formed as journals 38, 40, rotatably mounted on the machine frame.
  • a segment 152, 154 is attached to the axially outer end of each journal 38, 40, the radius of the segment being smaller than half the distance of the drive axes of the support rollers 10, l2, so that both segments are arranged opposite each other and symmetrically.
  • the pair of segments 152, 154 is coupled together by means of two overcrossing bands 156 ⁇ 158 according to FIGS. 5 and 6,
  • both bands 156, 158, respectively both ropes 160, 162 are positioned with a small spacing beside each other on the cylindrical outer surfaces of the segment 152, 154.
  • the magnitude of the rotation of the supporting beams 34, 36 depends on the diameter of the wound roll 14 at each instance. Similarly dependent on the diameter of the wound roll 14 is the force transferred by the same on the support rollers 10, 12in the winding nip, and therefore the winding tightness.
  • this embodiment also utilizes vertically above the rotation axis of the wound roll 14 suspended loading roller 18, which can additionally be provided with further loading weights 20. This loading roller 18 together with the loading weights 20 attached thereto is, as in the embodiments shown in FIGS.
  • Each rope, resp. chain 22 is, as in the embodiments according to the FIGS. l and 3, first passed vertically upward, then over a reversing pulley 24 supported rotatably on the machine frame, therefrom again downward and over another reversing pulley 25 mounted rotatably at the end of the piston rod 26 of the hydraulic pressure cylinder 28, and again upward, and finally attached at its free end to the machine frame.
  • a reversing pulley 24 supported rotatably on the machine frame, therefrom again downward and over another reversing pulley 25 mounted rotatably at the end of the piston rod 26 of the hydraulic pressure cylinder 28, and again upward, and finally attached at its free end to the machine frame.
  • a hydraulic pressure cylinder 28 is at its lower end pivotingly mounted on the machine frame, so that it can follow the movements of the reversing pulley 25, and is also provided with means for introducing pressurized medium into its pressure chambers.
  • a guide roller 168 is provided before the support roller receiving the oncoming paper web 16 to the base 170 of which similarly as in the case of the bearing of the reversing pulley 24, has a pressure-measuring cell 172.
  • the tension of the paper web 16 is detected by means of said pressure-measuring cell and introduced through an amplifier 174 into a computing relay 176, which in its turn passes the converted signal to the controller 148. In this manner the pressure in the pressure chamber 56 of the support roller 12 is adjusted corresponding to the paper web tension.
  • FIG. 8 differs from the embodiment of FIG. 4 only in the different arrangement of the suspension of the loading roller and the release drive.
  • the loading roller 18 together with the possibly necessary additional loading weight 20 is guided in a vertical or slightly inclined direction '30) in the machine frame, and is at each side of the machine suspended from a spindle 177.
  • force-measuring units 126 and spring elements 178 having very flat spring rates (pneumatic springs, cup springs or the like).
  • worm kwheels 179 formed as spindle nuts, which in their turn are coupled through worm gears to torque-adjustable electric, pneumatic or hydraulic servomotors 180.
  • the number of worm gear revolutions gives simultaneously a measure of the diameter increase of the wound reel 14, therefore the measuring device 124 is connected to one of the worm gears.
  • the loading weight of the loading unit 18, 20, variable in dependence on the torque of the motors 180 and instantaneously effective, is determined by the force-measuring cells 126 (extension-measuringstrips or other measuring units can also be used), and introduced through an amplifier 128 to the computing relay. From this measuring value, together with the diameter signal converted in the computer 132, is then produced the control impulse for the controller 134 which controls the torque of the servo meters 180.
  • the loading roller 18 can via the spindles 177 andthe worm gear 179 be additionally pressed with the motors which makes the construction more simple and economic, without impairing its function, that is, to maintain the pressure constant between the wound reel 14 and the support rollers l0,
  • FIG. 9 shows an embodiment utilizing a heavy rail girder 20 which therefore requires only one adjustable release.
  • any other prior known mode of construction for such rollers can be utilized for the support rollers as well as the loading roller.
  • a method for winding a traveling web to form a cylindrical wound roll having a uniform winding tightness along the web width and between adjacent layers of the wound roll comprising applying a pressure against the generated surface of the wound roll, said pressure being applied at a location defining a winding nip by a winding member engaging said generated surface substantially along a meridian line extending over the length of the wound roll, adjusting said meridian line to the form of a straight line whereby the location of said straight meridian line is adapted to be brought to coincide with the location of said winding nip which location varies during the winding operation, and applying a load to said roll along another meridian line approximately diametrically opposite said winding member, the magnitude of said applied load being varied corresponding to the increasing weight of the wound roll.
  • a method according to claim l comprising varying the magnitude of saidapplied load so that the effective contact pressure force between the wound roll and the winding member is maintained substantially constant during the winding operation.
  • a method according to claim l comprising varying the magnitude of said applied load so that the effective contact pressure force between the wound roll and the winding member is varied in a predetermined manner during the winding operation.
  • Web-winding apparatus to which a web is continuously introduced comprising a winding core positioned on a machine frameA transversely with respect to the oncoming direction of the web for receiving said web to be wound to form a cylindrical wound roll, a winding means in pressure engagement with the generated surface of the wound roll along a meridian line thereof and operable to provide uniform winding tightness, said winding means including a winding roller being disposed and arranged such that the web is directed from the oncoming direction to a direction tangential with respect to the generated surface of the wound roll, and means adjusting the meridian line of said winding roller so that said meridian line is adjusted in the form of a straight line independently of the outer load of the zone of pressure engagement.
  • said winding means comprises two support rollers of a double support roller Winder, said winding roller being one of said two support rollers.
  • Web-winding apparatus comprising a loading roller positioned vertically above said wound roll, means for providing pressure engagement of said loading roller with the generated surface of said wound roll along a meridian line thereof, and means for adjusting the meridian line.
  • said winding roller comprises a hollow cylinder, a supporting beam extending through said hollow cylinder and extending over the end surfaces at each end, means for rotatably mounting said/extending ends on said machine frame, means for sealing the ends of the hollow cylinder against said beam ends, means for sealing the supporting'beam in the zone of the cross diameter perpendicular to the direction of the pressure engagement against the inner face of said hollow cylinder, thereby to define a pressure chamber, said pressure chamber extending between said supporting beam and the portion exposed to pressure engagement with the wound roll and the shell or said hollow cylinder, means connecting said pressure chamber to a pressure source; and means for rotating said supporting beam with respect to the machine frame into a position corresponding to the prevailing direction of the pressure engagement between said wound roll and said hollow cylinder.
  • Apparatus according to claim 7 further comprising means for adjusting the pressure in said pressure chamber.
  • Web-winding apparatus comprising a pantograph linkage means connected to said loading roller, said linkage means comprising quadrangle links symmetrical with respect to said winding means and consistingof four equally long bars, a reversing pulley rotatably mounted in the plane of symmetry of said winding means adjacent said loading roller, a rope passing over said pulley, one end of said rope being attached to said machine frame while the other end is attached to said loading roller.
  • Web-winding apparatus comprising a throttle valve for adjusting the pressure in said pressure chamber, said throttle valve having a housing attached to one of two mutually movable parts of said pantograph linkage means, said valve means having a valve body attached to the other of the two parts of said pantograph linkage means in such a manner that as the loading roller moves under the influence of the increasing diameter of said wound roll, the through flow cross section for the pressured medium in the throttle valve increases.
  • said last said means comprising spindles and worm gears driven by torque-adjusted motors whereby said linear pressure decreases as the diameter of said wound roll increases so that a linear pressure between said winding means and the wound roll remains constant during the entire winding operation.

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  • Rolls And Other Rotary Bodies (AREA)
US824590A 1968-05-15 1969-05-14 Method and apparatus for winding up traveling webs Expired - Lifetime US3604649A (en)

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FI136368A FI42773B (enrdf_load_stackoverflow) 1968-05-15 1968-05-15
FI180868A FI46144C (fi) 1968-06-26 1968-06-26 Laite liikkuvan rainan kelaamiseksi.

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CA (1) CA932315A (enrdf_load_stackoverflow)
FR (1) FR2008581A1 (enrdf_load_stackoverflow)
GB (1) GB1260004A (enrdf_load_stackoverflow)
SE (1) SE362630B (enrdf_load_stackoverflow)

Cited By (12)

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US3837593A (en) * 1971-09-24 1974-09-24 Ahlstroem Oy Supporting-roller reeling apparatus
US3977619A (en) * 1972-12-25 1976-08-31 Kanebo, Ltd. Method and apparatus for winding a continuous fabric on a cylinder in a roll form
US3990648A (en) * 1975-11-13 1976-11-09 Beloit Corporation Cable means for controlling internal tension in web rolls, and method
US4146188A (en) * 1977-10-31 1979-03-27 E. Fogarty & Company Limited Method and apparatus for forming a fibrous cylindrical element
US4150797A (en) * 1975-08-08 1979-04-24 Hiroshi Kataoka Method and device for controlling contact pressure on touch roller in sheet winder
US4434949A (en) 1982-03-10 1984-03-06 Beloit Corporation Winder rider roll control
US4458853A (en) * 1980-07-18 1984-07-10 Jagenberg Ag Apparatus for the separate winding of slit webs
US5320299A (en) * 1992-01-27 1994-06-14 Beloit Technologies, Inc. Articulated rider roll system and method
US20030000054A1 (en) * 1999-12-24 2003-01-02 Tiberio Lonati Apparatus and method for controlling the weight of fabric produced by a textile machine, in particular by a circular knitting machine
US20130277489A1 (en) * 2012-04-20 2013-10-24 Metso Paper, Inc. Method and Device for Winding of Fiber Webs, Especially of Partial Paper and Board Webs
CN103832862A (zh) * 2014-03-20 2014-06-04 杭州奥科服装辅料有限公司 一种无纺布染色生产线的多功能成卷装置
CN107269605A (zh) * 2017-06-30 2017-10-20 无锡威奥液压机电设备有限公司 一种无纺布卷料遥控上料机构

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US3009666A (en) * 1958-10-31 1961-11-21 Samuel M Langston Co Roll density control for slitter winders
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US3237877A (en) * 1963-12-05 1966-03-01 Diamond Int Corp Web winding apparatus
US3282526A (en) * 1963-12-06 1966-11-01 Beloit Eastern Corp Drum winder for paper and the like
US3306547A (en) * 1965-04-02 1967-02-28 Keelavite Hydraulics Ltd Winding apparatus
US3377033A (en) * 1966-05-12 1968-04-09 Kimberly Clark Co Papermaking machine
US3394897A (en) * 1966-10-24 1968-07-30 Cutters Machine Co Inc Suspended web roll support

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DE859421C (de) * 1942-09-20 1952-12-15 Alsacienne Constr Meca Bandvereinigungsmaschine od. dgl. mit Wickelvorrichtung
US3009666A (en) * 1958-10-31 1961-11-21 Samuel M Langston Co Roll density control for slitter winders
US3178125A (en) * 1962-03-08 1965-04-13 Dominion Eng Works Ltd Winders and rewinders for paper machines
US3232549A (en) * 1963-05-09 1966-02-01 Beloit Eastern Corp Paper web winder with pneumatic control circuit
US3237877A (en) * 1963-12-05 1966-03-01 Diamond Int Corp Web winding apparatus
US3282526A (en) * 1963-12-06 1966-11-01 Beloit Eastern Corp Drum winder for paper and the like
US3306547A (en) * 1965-04-02 1967-02-28 Keelavite Hydraulics Ltd Winding apparatus
US3377033A (en) * 1966-05-12 1968-04-09 Kimberly Clark Co Papermaking machine
US3394897A (en) * 1966-10-24 1968-07-30 Cutters Machine Co Inc Suspended web roll support

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3837593A (en) * 1971-09-24 1974-09-24 Ahlstroem Oy Supporting-roller reeling apparatus
US3977619A (en) * 1972-12-25 1976-08-31 Kanebo, Ltd. Method and apparatus for winding a continuous fabric on a cylinder in a roll form
US4150797A (en) * 1975-08-08 1979-04-24 Hiroshi Kataoka Method and device for controlling contact pressure on touch roller in sheet winder
US3990648A (en) * 1975-11-13 1976-11-09 Beloit Corporation Cable means for controlling internal tension in web rolls, and method
US4146188A (en) * 1977-10-31 1979-03-27 E. Fogarty & Company Limited Method and apparatus for forming a fibrous cylindrical element
US4458853A (en) * 1980-07-18 1984-07-10 Jagenberg Ag Apparatus for the separate winding of slit webs
US4434949A (en) 1982-03-10 1984-03-06 Beloit Corporation Winder rider roll control
US5320299A (en) * 1992-01-27 1994-06-14 Beloit Technologies, Inc. Articulated rider roll system and method
US20030000054A1 (en) * 1999-12-24 2003-01-02 Tiberio Lonati Apparatus and method for controlling the weight of fabric produced by a textile machine, in particular by a circular knitting machine
US6952939B2 (en) * 1999-12-24 2005-10-11 Santoni, Spa Apparatus and method for controlling the weight of fabric produced by a textile machine, in particular by a circular knitting machine
US20130277489A1 (en) * 2012-04-20 2013-10-24 Metso Paper, Inc. Method and Device for Winding of Fiber Webs, Especially of Partial Paper and Board Webs
US9051146B2 (en) * 2012-04-20 2015-06-09 Valmet Technologies, Inc. Method and device for winding of fiber webs, especially of partial paper and board webs
CN103832862A (zh) * 2014-03-20 2014-06-04 杭州奥科服装辅料有限公司 一种无纺布染色生产线的多功能成卷装置
CN107269605A (zh) * 2017-06-30 2017-10-20 无锡威奥液压机电设备有限公司 一种无纺布卷料遥控上料机构

Also Published As

Publication number Publication date
GB1260004A (en) 1972-01-12
DE1913420A1 (de) 1969-11-27
SE362630B (enrdf_load_stackoverflow) 1973-12-17
FR2008581A1 (enrdf_load_stackoverflow) 1970-01-23
DE1913420B2 (de) 1975-11-20
CA932315A (en) 1973-08-21

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