US3604649A

US3604649A - Method and apparatus for winding up traveling webs

Info

Publication number: US3604649A
Application number: US824590A
Authority: US
Inventors: Gerhard Walter Dorfel
Original assignee: Ahlstrom Corp
Current assignee: Lenox Machine Co Inc
Priority date: 1968-05-15
Filing date: 1969-05-14
Publication date: 1971-09-14
Anticipated expiration: 1988-09-14
Also published as: CA932315A; FR2008581A1; SE362630B; GB1260004A; DE1913420B2; DE1913420A1

Abstract

This invention relates to a method and apparatus 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. A winding member is in pressure engagement with the generated surface of the wound roll along a meridian line thereof and is operable to produce the aforesaid uniform winding tightness. Positioned approximately diametrically opposite the aforesaid winding member is a loading roller operable to apply a variable force to the wound roll corresponding to the increasing weight of the wound roll such that the contact pressure between the wound roll and the winding member is maintained constant or varies in a predetermined manner in the winding operation.

Description

United States Patent m1 3,604,649

[72] Inventor GerhardWalterDorfel 3,282,526 1l/l966 Daly 242/66 Riittulanmaki, Varkaus, Finland 3,306,547 2/1967 Reid et al.. 242/66 [2l] Appl. No. 824,590 3,377,033 4/l968 Link I'42/66 X [22] Filed May 14, 1969 3,394,897 7/l968 Martin, Sr. 242/66 X [45] Patented Sepl. 14, 1971 FOREIGN PATENTS [73] Assignee A. Ahlstrom Osakeyhtio Noormarkku, Finland 859,421 l0/l952 Germany 242/66 [32] Priority May l5, 1968, June 26, 1968 Primary Examiner-Stanley N. Gilreath [33] Finland Assistant Examiner-Werner H, Schroeder [3l 1363/68 and 1808/68 Atlorneys-Ralph E. Bucknam, Jesse D. Reingold, Robert R.

Strack and Henry A. Marzullo, .lr`

[54] METHOD AND APPARATUS FOR WINDING UP TRAVELING WEBS 13 Claimsnrawing Figs ABSTRACT: This invention relates to a method and apparatus for winding a traveling web to form a cylindrical [52] U.S. Cl 242/66 wound ron having a uniform winding tigntneSs along the web [5l] Int. Cl B65h 17/08 width and between adjacent layers of the wound roll. 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.

{56} References Cited Positioned approximately diametrically opposite the aforesaid winding member ls 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.

PATENTEnsEmIsn 3,604,649

sum a of a Fly.;

METHOD AND APPARATUS FOR WlNDlNG UP TRAVELING WEBS BACKGROUND OF THE INVENTION l Field of the Invention 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.

2. Description of the Prior Art In the production of traveling webs, for instance in the papermaking and foilmaking industries, but also in the textiles industry, it is conventional to wind up the manufactured paper or foil webs, or the fabric web, into cylindrical wound rolls, as such rolls are easy to pack, convenient to transport and stack and can subsequently be utilized very advantageously in converting machines. Furthermore they permit continuous operation without shutdowns, as a fresh wound roll is placed in position after the previous roll has been consumed.

Trouble-free operation with such rolls at the high operational velocities of up-to-date converting machines admittedly requires very careful winding up, particularly a very uniform winding tightness over the width of the web as well as from layer to layer.

Various types of apparatuses for winding up a traveling web into a cylindrical wound roll are prior known in the art. Many of these apparatuses, in order to produce the desired winding tightness, have a winding member over which the web is directed from its oncoming direction, e.g. from the webproducing machine, into a direction tangential with respect to the outer surface of the wound reel (German Pat. 844 702). An extensively used embodiment of such a web-winding apparatus is the so-called double support roller winding machine (German Pat. No. 902 456), in which the web is wound on a cylindrical winding bar, serving as a core, by means of two equally large support rollers, rotatably mounted horizontally with close spacing beside each other on the machine frame, while a third roller, parallel to the support rollers, a so-called loading roller, is mounted movably vertically above the two support rollers in their vertical plane of symmetry, and so loaded that it, during the winding of the roll will press the roll against the support rollers. Further it is prior known to suspend the loading roller from two ropes and to attach each rope directly, or over a rope pulley inserted in a lifting eye, to the piston rod of a pressure cylinder (U.S. Pat. No. 3 232 549 and DAS 1 123 552). 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.

In spite of the above-mentioned measures it is, however, possible to produce satisfactory uniformity of the winding tightness only in wound rolls of relatively narrow width in relation to their outer diameter. Particularly in the case of wide wound rolls the uniformity of the winding tightness, both over the web width and from layer to layer, is unsatisfactory with the prior known web-winding devices, in spite of all care taken by the operating personnel.

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.

For this purpose 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.

It is also prior known to make such rollers hollow, and to expand the roller with an amount increasing from the ends to the center, by introducing a pressurized medium in the roller cavity (U.S. Pat. No. 3 O19 511). By selecting a suitable inner pressure the result can be achieved that, when an outer load is applied to the roller, the meridian line in the zone of the roller nip is practically straight. By adapting the inner pressure to the outer load, a straight meridian line in the roller nip can be achieved in all outer loads met with. Such an arrangement requires, however, the utilization of very high pressure in the roller cavity, for the supply of which a special, very complicated pressure-generating plant must be provided.

In another prior known mode of construction for such rollers with adjustable meridian 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.

In other prior known construction modes for such crownable rollers the roller shell is in the form of a hollow cylinder. In the cavity of the roller shell extends parallelly with the same 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. On the side of the outer load of the roller shell, between the inner shell surface and the supporting beam, means are provided for applying counteracting forces to said inner surface. 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. Thus 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.

According to a mode of construction for such deflectionfree hollow rollers, particularly suitable for the purposes of the present invention (DAS l O26 609), 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. In order to obtain a straight meridian line in the roller nip with all outer loads met with, it is only necessary to adapt the oil pressure to theprevailing outer load. Even in the case where the outer load `on the roller shell is variable as to its direction, 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.

SUMMARY OF THE INVENTION 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. In such a web-winding apparatus, according to a further aspect of the invention, 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.

BRIEF DESCRIPTION OF THE DRAWINGS The invention is described and elucidated in the following with reference to the embodiments illustrated in the accompanying drawing. In the drawing:

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.

Identical or mutually corresponding parts in all Figures and in the description have been provided'with identical reference numbers.

DESCRIPTION OF THE PREFERRED EMBODIMENTS In the embodiment of 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. Vertically above the support rollers there is provided 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. By means of varying the oil pressure in the pressure cylinder 28, 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.

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. Between the spindles 177 and the

loading unit

18, 20 there are provided force-measuring cells 126 and spring elements 178. 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. 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. To each of said lower bars 62, 64, at equal distances from the articulation 68, is attached the end of the link 46, 48. lf the dimensions of the parts of this linkage are suitably selected, it brings forth a substantial adaptation of the resultant of the pressure forces exercised in the

pressure chamber

54, 56 against the interior surface of the

support roller shells

30, 32 to the direction of the contact pressure force of\the wound roll 14 applied in on the outer surface of the

support roller shell

30, 32. The meridian line of the outer surface of the support roller shell is thus maintained straight if the magnitude of the pressure forces in the pressure chamber are exactly equal to the outer contact pressure force.

To achieve this, 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.

0n a bracket 80 belonging to the machine frame, which supports the pivot pin 68 for the two lower bars 62, 64, is attached the valve housing 82 which has connections 86, 88, 90 for oil lines. Through the line 90 is introduced a pressurized fluid, for instance pressurized oil, from a source not shown. 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, the flow cross sections of which vary when the valve body 84 is turned in the housing 82, 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.

This is no more true when the winding tightness from layer to layer is to be varied in the above-described manner. There also the pressure of the pressure medium in the

pressure chambers

54, 56 must be controlled corresponding to the changing winding tightness by means of a valve similar to the valve 78. For this purpose connections for two additional lines 102, 104 can be provided in the valve housing 82 of the valve 78. The valve body 84 has corresponding flow openings 106, 108, by means of which the oil pressure in the line 104 leading to the

pressure chambers

54, 56 can be influenced similarly to that in the line 88.

In the embodiment according to FIG. 3, similarly as in that of FIG. 1, a double support roller winder for winding a moving paper web 16 by means ofa 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.

The portions of 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 operation of the reversing valve 122 will be described later` Vertically above the support rollers l0, l2, in their plane of symmetry there is 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.

In order to produce a wound roll having a winding tightness uniform as well over the entire width as also from layer to layer or a tightness changing in a predetermined manner from layer to layer, three variables must be controlled during the winding operation in dependence of the increasing diameter of the wound roll 14, that is, the position of the supporting

beams

34, 36 by means of the pressure cylinder 116, the amount of pressure in the

pressure chambers

54, 56 of the

support rollers

10, 12, and the magnitude of the effective load, by means of the pressure cylinder 28. For this purpose 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.

In the case of very broad machines 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.

Finally it is also necessary to adjust the basic adjustment of the inner pressure in the

pressure chambers

54, 56 of the

support rollers

10, 12 which compensates for the linear pressure in the winding nip, to a starting value corresponding to the starting load. This is carried out by including a weight signal derived from the amplifier 128 and by introducing the same as an addition to the computing relay 150.

ln order to be able to utilize the apparatus even in cases where the thickness of the paper web over its width is higher or lower at the edges than at the web center, and to be able to achieve the presupposed winding tightness over the web width and from layer to layer, there is provided 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 (the computer relays 130, 136, 140, the manually operated relay 144, the computer 132, the amplifier 128) 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. For the actuation of the controller 134, the reversing valve 120 and the pressure controller 142, the so-called sucking solenoid actuators have proven particularly suitable.

In addition to the two support rollers, also 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.

Also in the embodiment shown in FIG. 4 the paper web 16 is wound up onto a winding core to form a wound roll 14, by means of the two driven

support rollers

10 and 12. 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,

or by means of two overcrossing ropes 160, 162 according to FIG. 7. One band 156 or rope 160 is attached at its one end to the upper edge of the segment 152, and at its other end to the lower edge of the segment 154 in slightly tensioned condition. The attachment can be carried out by any suitable means such as screws. According to FIGS. 6 and 7 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. When one of the segments such as the segment 152, is pivoted by means of the hydraulic displacement drive, engaging the lug of said segment and consisting of the

parts

116, 118 and 164, the other segment 154 will rotate in the opposite direction for an equal angle.

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. In order to obtain a winding tightness that is independent on the weight of the already woundup portion of the paper web, and therefore constant, or from layer to layer by will adjustable, 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. 1 and 3, at each side of the machine suspended from a rope or a chain 22 and guided along a roller track 166. 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. As in the above described embodiments according to FIGS. l and 3 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. By means of varying the pressure in the pressure cylinder 28, the magnitude of the load applied by the loading roller 18 together with the loading weight 20 on the wound roll 14, is decreased corresponding to the increasing own weight of the wound roll 14 during the winding operation, with the result that the force transferred by the wound roll 14 on the support roller 10 and determining the winding tightness, has during the entire winding operation the desired value.

In order to produce a wound reel which is both over the entire width uniformly tight and also from layer to layer equally tight or, with respect to the tightness variable in a predetermined manner, three variables must, as in the embodiments according to FIGS. 1 and 3 be controlled during the winding operation in dependence on the increasing diameter of the wound roll, viz the position of the supporting

beams

34, 36 by means ofthe pressure cylinder 116, the magnitude of the pressure in the

pressure chambers

54, 56 of the support rollers l0, 12 and the magnitude of the effective load, by means of the pressure cylinder 28. The arrangement provided for this purpose corresponds in all its details to that of the embodiment according to FIG. 3 so that it does not need to be described in this connection.

In order to take care of the influence of the tension of the traveling paper web, which particularly with broad webs can be quite substantial, 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.

The embodiment of 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. Between the spindles 177 and the

loading units

18, 20 there are provided force-measuring units 126 and spring elements 178, having very flat spring rates (pneumatic springs, cup springs or the like). On the upper portion of the machine frame are mounted 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 Figures show a hydraulic control circuit, but when pneumatic or electric motors are utilized, the

units

130 and 134 must also be selected correspondingly.

When additional weight 20 (normally a rail girder) is not utilized, 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.

ln addition to the loading roller pressure control devices shown in FIGS. l, 3 and 8, there is the possibility instead of using the spindle-worm gear-motor drive shown in FIG. 8 to connect the motor drives 177, 179, 180, to connect the pressure cylinder 28 shown in FIGS. 1 and 3 directly through the spring element 178 and the measuring unit 126 (FIG. 8) to the loading roller, in which case the rope, chain, or band tackle 22 (FIG. l or 3) is not necessary.

In place of the mode of construction of the support rollers shown and described in the embodiments above, having an adjustable meridian line in the winding nip, any other prior known mode of construction for such rollers can be utilized for the support rollers as well as the loading roller.

I claim:

1. 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.

2. 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.

3. 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.

4. 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.

5. Web-winding apparatus according to claim 4 wherein said winding means comprises two support rollers of a double support roller Winder, said winding roller being one of said two support rollers.

6. Web-winding apparatus according to claim 4 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.

7. Web-winding apparatus according to claim 6 wherein 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.

8. Apparatus according to claim 7 further comprising means for adjusting the pressure in said pressure chamber.

9. Web-winding apparatus according to claim 7 wherein said means for rotating said supporting beam is operably connected to said loading roller thereby providing for adjustment of the angle of said supporting beam relative to the diameter of said wound roll.

l0. Web-winding apparatus according to claim 9 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.

l1. Web-winding apparatus according to claim 8 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.

wound roll, 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.

Claims

2. A method according to claim 1 comprising varying the magnitude of said applied load so that the effective contact pressure force between the wound roll and the winding member is maintained substantially constant during the winding operation.

3. A method according to claim 1 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.

4. Web-winding apparatus to which a web is continuously introduced comprising a winding core positioned on a machine frame 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.

7. Web-winding apparatus according to claim 6 wherein 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.

10. Web-winding apparatus according to claim 9 comprising a pantograph linkage means connected to said loading roller, said linkage means comprising quadrangle links symmetrical with respect to said winding means and consisting of 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.

11. Web-winding apparatus according to claim 8 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.

12. Apparatus according to claim 6 comprising a pressure cylinder having a piston rod connected to said loading roller to thereby produce an adjustable counteracting force whereby the linear pressure applied by the loading roller on the wound roll is decreased as the diameter of the wound roll increases.

13. Apparatus according to claim 6 comprising means for causing said loading roller to apply a linEar pressure on said wound roll, 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.