DE6944109U - DEVICE FOR WINDING UP A RUNNING TAPE. - Google Patents

Description

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Dr. A. Msntzel ipUne

Godparents i - * "** hey

Refrath near Cologne

Frenkenfors »137

November 13, 1969 Hg / ho

A. Ahlstrbm Osakeyhtio * Varkaus, Finland

• "Device sum Äufwicfeela eise εlauf ^ adea Basdes"

The invention relates to a device for winding a running tape into a cylindrical winding roll.

In the production of running binders, for example in the paper and foil industries, but also in the textile industry » Industry, it is common to use the produced paper or pollexibah

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Wind up ηβη or fabric webs into cylindrical Wiokel rolls, because these screen leioht pack, conveniently transport and can be stacked and used particularly advantageously in the processing machines. If they enable continuous work without interrupting operations when using a new winding roll after the previously used winding roll has been used up.

Trouble-free work with single Wiokel rolls is required at the high working speeds of modern machines Processing machines a very careful curling, especially one across the width of the strip as well as from layer to layer even winding hardness.

Various devices are known for winding a running tape into a cylindrical winding roll. Many of these devices have a winding body that is used to generate the winding hardness, via which the tape is deflected from the feed direction, which may for example come from the manufacturing machine, into the direction tangential to the outer surface of the winding roll (UP 844 702). A widely used design of such Bandaufwiokelvorrichtungen is the so-called two-drum winders (SF 902,456), wherein the web bar / s by means of two equally large, horizontally on a serving as a core cylindrical winding :, with ge "; next to each other rotatably gelag rter lngea Abstanl in the machine frame Support rollers

694410

wound wii'ft _e while a third "to the parallel Cragwalaen © .'aliS6 _s called Belastun £ swclze _s serücrocht ü" over the "two T? agv / £ -Laen located höhenveraoliieblioh in their veäUcaler Syiometrieebene and so complained * that they ickelrolle during dea Aufwiokelns the v / is against the Tragwal 2s presses _o It also "known s suspend the loading roll of cables and each cable directly or through au a disc loaded into a Sohlaufe -eilrolle to the piston rod of a pressure cylinder mount (U.S. Patent 3 232 549 or »DAS 1 123 552)" By changing the Di-uoke in the pressure cylinder, the Uickel hardness is influenced. / It is also known to bring about the Axis of the loading roll adapts itself to the .sighting of the surface line of the winding roll in the support point _& around with different thicknesses at the web edges, the conical V, ^y c kelrollen led a over the web width sjanähernd uniform 'winding hardness to obtain _u

! Crotz this near-measure is only in relation to the outdoor Durohuessersohaalen ./ickel rollers to achieve a reasonably satisfactory uniformity in / ickel hardness, especially with wide .. winding rolls is in the known tape on winding devices despite all the attentiveness of the operating staff

the G-Ie ¹ -.haäßr.gkeit ^ r .Hebe '.' arte ao '/ ohl uler die Beh: .- "width k

as well as ^ c ι Lege 11 La ^ e unsatisfied.ad _o

44109

The object of the invention is to improve the uniformity of the winding hardness of winding rolls across the width of the web as well as from layer to layer by exerting uniform compressive forces against the outer surface of the winding roll in the winding gap and to make it independent of the attention of the operating staff.

This object is achieved according to the invention in such a way that, in order to exert compressive forces against the outer surface of the winding roll, a winding body with a meridian line that can be set in a known manner, which is in contact with this surface essentially along a meridian line extending over the length of the winding roll, is used, the meridian line in the winding gap in the form of a Straight lines are set and, if necessary, the location of this straight meridian line with the position of the Vfickelspalt which changes during the winding process is brought into consideration and that finally on the winding roll along a further meridian line at least diametrically opposite the V / ICML body in a known V / eise according to the amount variable load applied and their Betras is changed according to the increasing weight of the winding roll, so that the effective between the winding roller and the winding body contact force during the winding operation remains the same o £ - ~ In ~ ise vorbestimaiter VT is changed.

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In order to carry out this soldering operation in practice, according to the invention, a tape winding device which continuously winds a tape at the point where a paper or sheet of paper is used is arranged with a perpendicular to the belt flange direction Winding core ssur receiving the tape to be wound up on a cylindrical winding roll and with one with the outer surface of the Winding roll in Bruckbertthrung along a meridian line, serving to generate the winding hardness, over which the tape ans the feed direction in the to the jacket surface the winding roll is deflected in the tangential direction. In such a tape winding device, according to a further idea of the invention, at least the tape on the winding * Roll applying winding body, standing with the outer surface of the winding roll in pressure contact along a meridian line, as an approaching winding roller with in a manner known per se adjustable meridian line formed and the meridian line of the winding roller set in a straight line regardless of the external load in the area of pressure contact with the winding roller.

There are known many types of rollers <■ It Heridianlinie adjustable. As a rule, such rolls are used in roll presses for machines for the production or processing of strip-shaped materials, such as paper, foils and textile webs, but also Metairbands are used in which the curvature of the roll axis under the influence of its own weight and the external load in the area of the roll gap must be compensated «

Ifen has known for the ο en purpose since Iszigeu, da ^. On the outer surface of the "JaI ze" IIier "at the ./e knife along the meridic line at each point, among other things, an amount corresponding to the deflection evaluated there is listed greater than the ./elzenhalbmeaser at the .alzer end _c below the predetermined load then passes the meridian line of the ..alze alzen gap in the region of. "exactly straight ₀ A α oil ah era L5ec crown roll provides, however, only for the Boiobierungakurve underlying Bel & 3tun £ exactly the desired straight meridian line in .VaI ζ ens pal ta in When the load changes, the 1-lane line deviates from the straight line in the ./alzensp&lt _o

It iot ε-uoli known to form such ./alzen hollow and expand by introducing ^ JUcL-jedium into the cavity in an outer shape increasing from the ends to the middle (US Patoi 3,019,511) o through _; , ahl a suitable internal pressure; vird _s reaches the external load at the DEI ..Xilae UEI idicnlinie in 3ereioh de "./alzenspalteo prektiaoh runs straight" By adjusting the internal pressure to the external load can be suitable straight course in the meridian line. .clzenspolt achieve with all occurring external loads ,? Such an execution, however, requires the use of very high pressures in the cavity of the socket body

In another known construction of such ./alzen with one

αϊ ell bar G Ueridic.nl ir.ie iB. ^ eirc ^ aii j- *; den del i: i ^ eei ^ -st ^ r .'eiste ve-Ί'ά. evaluate u'ra ^ zapfeii dei · .. '£.! ac in aw ei ■ cocidl disconnected lr.geru _{t of} those ei-ieu firmly supported _v while r.uf the other a counterforce adjustable in its size is exerted (Uo-Pat ent 3 273 4 92) ^ 3c ^ A bending area produced by means of Lscerki-cft and Gegenkx-aft is less like üielir odex "

the Lastbiegemomont f.us and prevents dcduieli the Durchder ./rlze in wr

At sudGrer. known construction modes of such boMbic-ixaiiigex · ..olsen iüt der; clze2iniJitel designed as a hollow cylinder In the Hohlrciuia dec 7ßlzenaantelß extends parallel to this a serving to absorb the victory moments ^ protruding over the two end faces of the roll shell and with the protruding lands ic 'uaachinengeatell Supporting beam _o On the side of the external load dea ./alzeui^antelu facilities for applying counterforces to this inner surface are provided between the inner surface and the supporting beam you can balance the external load on the "Jalaenmantels" with the opposing forces

In a construction of such a deflection-free hollow roller which is very suitable for the purposes of the present invention

(DAS 1,026,609) is on Deraa "bolasteter side arranged a of the nlohtmalaufeiaie ^. Stringers begrengtar _w windksaselartig auügebildeter Druokraun for receiving vou pressure oil The üldruok erceugt one on the Vialaenlünge uniformly distributed" the Außenlaet auegleiohende counter load _o To la Y / alzen cleaving a Straight line Ileridiaallle with all occurring external loads must have only the oil pressure of the respective external load. ₃ Even with an externally variable load on the v / alaenia jacket, this construction has advantages by virtue of the twisting of the supporting beam around the ttalaenlängsachao enables the reduction of the counter-load with the reduction of the external load in Deokung bu.

The invention is described and described below with reference to the explanations shown in the accompanying drawings explained in more detail »In the drawing 2eigt

FIG. ₀ 1 shows a Do> -pel carrier roller roller designed according to the invention, in cross section in the same representation;

Pig ο 2 a cross-section through a see Pig ο 1 associated control valve

Figo 3 shows a different design of a double-sided roller roller »also in a similar bar-

position, with hydraulic control of the winding process ;

Pig. 4 shows a further design of a deviating from the exemplary embodiments according to FIGS. 1 and 3 Double support roller, also in a schematic position with hydraulic control the winding process;

FIG. 5 shows an enlarged illustration of the device for simultaneous, opposing adjustment of the supporting beams of the spans;

6 shows a schematic partial cross section through the Device according to Figure 5 length of the line YI-TI;

FIG. 7 shows a schematic diagram corresponding to FIG. 6 shown partial cross-section for another Formation of the device according to FIG. 5 J

Fig. 8 shows a further, from the Ausführungsbeiepielen according to Fig. 3 and 4 I ₉ deviating formation of a two drum winder, also in view scheoatiscner!

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Figo 9 shows a Andore type of Belastungswalzenauf "· hanging in Aueführung after Figo 8 _O

The same or corresponding ropes are provided with the same reference lines in the figures and in the description

On the two, in the machine frame, not shown, horizontally spaced apart and rotatably mounted support rollers 1O ₄ 12 of the Auaführuagsbeispieles after Pig.i runs a winding roll H of an endless paper web 16 to _u The beginning of this paper web is on one of the core of the winding roll forming Wiokelstange 15 wound up "One of the support rollers 10" 12 is provided with a drive not shown vertically above the support rollers is a loadav / alae i8 with a new additional load weight 20 in the vertical direction as a machine frame and on a cable at each end (suspended o the cable can with rope * a chain * a belt, a band or the like 22 may be formed "on which the Belastungewalze 18 depends _k and is guided over a rotatably mounted in the upper part of the machine frame guide roller 24 ·. the free end is connected via a another deflection roller 25 out and fixed in the upper part of the machine frame »Die Umle nkrolle 25 is at the upper end of the piston rod 26 of a laterally rubbing the iiragv / alzen 10, 12 in the machine frame angöoi-üneten printing cylinder 2C drehl "ar mounted * By changing the oil pressure in JJruül: - cylinder 23 is ler Betrüg that of DEI relcstu ^ gay / al-d'8 ait

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the Belastungsgewioht reduced exerted on ai © winding roll H Laat 20 corresponding to your Beisa Wi ekel operation increasing weight of the winding roll, thereby achieving _e that the awicchen serving as Wiokelwalse Sragwalae 10 and the 'rfiokärolle 14 in the V / iokelspalt acting force during geaam "th The wrapping process is kept the same size or changed in a predetermined amount

Eiae new! I · Method ο of the load roll-up and BelaGtungsgev / light suspension shown in Figure 8 ", The load roll 18 with the additional load weight 20 is guided in a vertical or slightly inclined direction (^ 30 °) in the lviasohinea frame and on a spindle 177 _ς on both l ^ acchinenseiten EBfg-r ^ ängto between the spindles 177 and the Belastungseinhelt 18 20 are the Kraftsoßdosen i26und the Peder elements 1? 8 _O Am Stuhlungsobei.eil ^ ind stored as spindle nuts worm wheels running 179 _v which in turn over Schnekken with the torque-adjustable Blelcbro «air or hydraulic motors 180 are engaged. By iindermig Drehmomentas of the motors 180 of the amount of force exerted by the La9t Belastungöeinheit 18 _S 20 onto the winding roller 14 in accordance with your _t when v / ickelvorgang increasing weight of the winding roll ,, verhindertο

Each 5IiO ^ ..- as IG, 12 v / eist fi ^ .nen dumbbell 30 ,, 12 vciö. an I; o SKio-1 sum '. .Uii;, el major-o'ü. dieaen hi iuroligöl:. ien. üo n: diu "both and en des Llarri? la protruding trag üai ken 34 _{ . 36 aufi der - \ 1τ

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its protruding over the ends of the associated jacket, designed as pins 38, 40 parts in the machine frame in Bearings 50, 52 is pivotably mounted «on the axially outer One end of a lever 42, 44 is attached to the end of each pin 38, 40, to the other end of which a link 46, 48 is connected.

You support beams 34, 36 are by a cranesbill-like The gear is pivoted in the bearings 50, 52 in accordance with the Surohmesser of the winding roll 14 growing during the winding process, so that the Sruok of the prevailing on the inside of the roll shell in the pressure chamber 54, 56 closed off by the associated supporting beam in this area acting on the outer surface of the roll shell in the winding gap load keeps the balance. The meridian line of the roll shell in the winding gap is therefore a straight line and remains as such from the first to the last layer of the winding roll, because the support beam 34, 36, according to the Migration of the winding gap is pivoted on the circumference of the support roller.

The transmission consists of four articulated, rods of equal length 58, 60, 62, 64 · The two lowest rods 62, 64 of this transmission are with their common joint 68 on

I-Iasßhinengestell arge

iea fixed joint 63 diagonally opposite joint 66,

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carries a pulley 70 for a rope 72, one of which is satellite 74 at the loading court 20 or at the loading whale 18, whose j other end 76 attached to the upper part of the Masohinengestellee is. This rope 72 adjusts the Storohsohnabol gear according to the Darohmesseraunahme of the winding roll 14: wherein the lower rods 62, 64 are rotated about the fixed joint 68 na ^ above. On each of these lower bars 62, 64 1st at the same distance from the joint 68 the fiide of the handlebar 46, 48 hinged. With an appropriate selection of the dimensions of its parts, this gear causes a substantial adaptation of the resultant of the pressure forces exerted in the pressure chamber 54, 56 on the inner surface of the support roller jacket 30, 32 to the direction of the The contact pressure of the winding roll 14 acting on the outer surface of the support roller jacket 30, 32. The meridian line of the outer surface The orphan's coat remains straight when the magnitude of the pressure forces in the pressure space just balances the external pressure.

In order to achieve this, the size of the load roll 18 including load weight 20 on the winding roll exerted force by regulating the oil pressure in the pressure cylinder so according to the dish with the Dareameör ~ r of the winding roller 14 is reduced, so that the contact pressure between the winding roller 14 and the support roller 10 assumes the predetermined value at every instant, for example remains the same. One can Then wrap it so that the core is harder than the outer layers or vice versa. This adaptation of the oil druoke in the pressure cylinder

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the 28 happens through the pressure oil valve 78, its to each other moving parts (housing and valve body) are connected to the pantograph gear, for example in such a way that the housing 82 is attached to the housing frame and the valve body 84 with one of the rods 62, 64 rotatably and axially immovable is connected, as Figure 2 shows.

On a bracket 80 of the machine frame, in which the joint 68 of the two lower rods 62, 64 is held, the valve housing 82 is fastened, which is provided with line connectors 86, 88, 90 is provided «Through line 90 pressure medium, for example pressure oil, is supplied from a source not shown. hit The valve body 84, which has a bore 94 connecting the lines 86 and 90, is connected non-rotatably to the pivot pin 92. In addition, lines 88 and 90 are in communication via cavity 96. The overflow openings 98, 100, which are variable in terms of their flow cross-section when the valve body 84 in the housing 82 is pivoted, are shaped in accordance with the flow rate of the pressure medium required in each position, so that at the beginning of the wokel process, the pressure medium flows into the upper cylinder space of the pressure cylinder 28 with little pressure leading line 88 enters because the line 88 leading to the drain line 86 enters because the to the drain line 86 leading flow opening 98 is wide open. This flow opening 98 and also flow opening 100 are closed more and more as the diameter of the winding roll 14 increases, the former around the bridge in bore 94 »cavity 96, line

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and thus in the upper cylinder space of the pressure cylinder 28 to increase, the latter in order to reduce the flow rate in line 88 at the same time.

The winding hardness, which remains constant from layer to layer, can be kept constant by the oil pressure in the pressure chambers 54, 56 of the Prague rollers 10, 12 be held, since in this case the pressing force between the support roller shells 30, 32 and the winding roll 14 in the winding gap by the described control of the loading roller 18 remains consistent.

This no longer applies if the winding hardness is to be changed from layer to layer in the prescribed manner. Then he must too Oil pressure of the pressure medium in the pressure chambers 54, 56 accordingly the changing winding hardness can be controlled by means of a valve similar to valve 78. For this purpose one can use the Provide connections for two further lines 102, 104 for valve housing 82 of valve 78. Corresponding flow openings 106, 108 are provided in the valve body 84, with the aid of which the oil pressure in the line 104 leading to the pressure chambers 54 »56 can be influenced in a similar manner as in the above Line 88 is described.

In the embodiment according to Pig. 3 is, as well as with Figure 1, a double support roller for winding the running paper tape 16 by means of a Wiokeletange 15 to a

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Winding roller 14 is provided by means of the two drivable drag rollers 10, 12, each of which has a support roller shell 30, 32 and has a supporting beam 34, 36 extending through it in the longitudinal direction coaxially to the jacket. Every girder is against the inner surface of the associated support roller shell sealed, so that between the support beam and the support roller shell on the Attack on the outer load-facing side a pressure chamber 54 * 56 is formed, which is connected to a pressure oil pump 10 by lines 112, 114.

The parts of the respective support beam 34, which protrude beyond the ends of each support roller jacket and are designed as pegs 38, 40 36 are pivotably mounted in bearings 50, 52 of the machine frame and are provided with levers 42, 44 on the axially outer side. The other ends of these levers are by means of the handlebars 46, 48 hinged to the piston rod 118 of the pressure cylinder 116, the two pressure chambers of which pressurized oil through one of the line 112 branched line 120 is supplied via the reversing valve 122. The actuation of the reversing valve 122 will be later described.

Vertically above the support rollers 10, 12 in their line of symmetry is a loading roller 18 resting on top of the winding roller 14 with an additional loading weight 20 by means of each one at each end of the loading roller 18 acting cable is suspended, the cable 22 (chain, belt, tape or the like)

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Via a pivoting roller 24 rotatably mounted in the upper part of the machine frame and from there via a further, aa outer end of the piston rod 26 on the side next to the support rollers 10, 12 guided in the hashine frame pivotably arranged pressure cylinder 28 rotatably mounted deflection roller 25 and with its end is connected to the machine frame.

To achieve a uniform over the entire width as well as from position to position of the same hardness or in predetermined ones In terms of the hardness of the winding roll, three variables are dependent on during the winding process · » Ability to control the increasing diameter of the winding roll 14, namely the direction of the support beams 34, 36 via the pressure cylinders 116, the level of pressure in the bruises 54 · 56 of the support rollers 10 »12 and the size of the effective load duroh the pressure cylinder 28. The diameter of the winding roller is over the stroke of the loading roller 18 duroh this corresponding rotation of the deflection roller 24 is input to a Mefigerät 124 coupled to this and fed to a computing relay 136, in which from the respective durometer the in formation understood winding roll 14 and the specific Sewittht of the tape to be wound 16 a binding guide signal fmr dl · closed controls is formed.

That depends on the piston force in the Bruoksylimder 28 changing, momentarily effective weight force of the

594410a

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Stungswalze 18 arranged in the support of the TJmlenkrol-Ie 24 force measuring device _B ", for example, a pressure measuring cell 126, is determined and fed via an amplifier 128 to the computing relay 130. From this measured variable there is susami & en with the diameter signal converted in the computer 132 the control pulse for the Controller 134 is formed, which controls the piston force in the pressure cylinder 28 and is fed to the pressure oil from the pressure oil pump 110 via the line 138. This control circuit thus realizes the requirement for a line pressure to be set in the winding gap between the support rollers 10 in a predetermined manner, depending on the durometer of the winding roll 14 _f 12 and the winding roll 14 "according to the amount _o TJm also the direction of the line pressure prevailing in the pressure chambers 54" 56 of the support rollers 10g 12 "the line pressure in the Wiclcelapalt keeping the balance with the direction of this line pressure in congruence with the arithmetic relay 136 guide signal i formed m Reohenrelais 140 converted into a signal describing the rotation of the support beams and fed to the reversing valve 122 _{v to} bring the piston rod 118 into the position corresponding to the respective diameter of the winding roller 14 _o

In the case of very bumpy machines, the thermosetting bending of the support rollers 10, 12 under their own weight is not negligible. Therefore, the internal pressure in the druola rooms 54 1 56 of the lag \ 1- zen 1O ₉ 12 must be adjusted to compensate for the weight at Betriig kc .. = - whose value also depends on the jewel. Igen λ> -Archiesser of the winding roll 14 depends _o Therefore sris α · - · κ ^ osi ile-

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ohenrelaie 136 in the computing relay 150 a the dependence of this pressure correction on the Surcia knife A signal is formed and passed to the pressure regulator 142.

Finally, it is nooh necessary to change the basic setting of the the internal pressure compensating for the line pressure in the winding gap in the pressure spaces 54 »56 of the support rollers 10, 12 as the initial value set according to the initial test. this happens duroh inclusion of a weight taken from the amplifier 128, which is also included in the computing relay IbO is entered «,

In order to be able to use the device in such cases, in r * nen the thickness of the paper web across the width of which is greater or less at the edges than in the middle, and A relay that can be operated by hand is used to obtain the specified winding hardness across the width of the web and from age to layer 144 envisaged, by walches a corresponding: de Korcäctur is attached to the signal formed in the arithmetic relay 150 for the actuation of the controller 142.

The devices used in this control device according to Pig, 3 (Reohenreleis 130, 136, 140, manually operated relay 144, Reelr; r 13- <? T ^ reo ^ - ^ ker lä <.are eivmso wio & ± <3- Segl ·. ^ 134 _f Uinsteι- 3λ / enl-il 122 i?; ^. D D2fucJn? Egles 142 In ü.ev Hegel'baciaailE known l..BLJ-Chtungön? E &erü.br?; C sich ^ r-Sr, the ^ e be

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known facilities to be described here exactly · For the actuation of the desire 134 »reversing valves 122 and pressure regulators 142 so-called plunger coil drives have proven to be particularly suitable.

In addition to the two support rollers, the load roller can also be used provided with a device for setting the meridian line in the pre-gap and its control in one of the systems according to FIGS. 1 and 2 or according to FIG. 3 according to one of the ways described there for the control of the support rollers be involved.

The embodiment according to FIG. 4 differs from the embodiment according to FIG. 3 by the different design of the adjustment drive for the support beams 34 »36 of the support rollers 10, 12. Furthermore, the automatic device for achieving a uniform over the entire width of the wound paper web wound as well as equally hard from layer to layer or with regard to the winding hardness variable in a predetermined manner additionally provided with a device in order to take into account the influence of the web tension of the endless paper web 16 running onto the support roller 10. Such an additional device can of course also be provided in the exemplary embodiments 73aG FIG. 1 or 3 .

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In the embodiment according to FIG. 4, too, the paper web 16 is turned into a winding roll 14 by means of a winding bar 15 with the aid of the drivable support rollers 10, 12. Each of the support rollers 10, 12 has a support roller shell 30, 32 and a support beam 34, 36 extending through the shell in the longitudinal direction coaxially to the shell. Each support beam 34, 36 is pivotably mounted in the machine frame with its parts, which protrude beyond the ends of the associated casing 30, 32 and are designed as pegs 38, 40 Radius is smaller than half the distance between the axes of rotation of the support rollers 10, 12, so that the two segments are arranged symmetrically to one another and opposite one another. The pair of segments 152, 154 are coupled by two crossing straps 156, 158 according to FIGS. 5 and 6 or by two crossing cables 160, 162 according to FIG. 7. One end of the band 156 or rope 160 is attached to the upper hand of the segment 152 and the other end to the lower band of the segment 154 in a slightly tensioned state. The other band 158 or rope 162 is attached with one end to the upper band of the segment 154 and with its other end to the lower hand of the segment 152 also in a slightly tensioned state. It can be attached, for example, by screws. According to FIGS. 5 and 7, the two bands 156, 158 and

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Lay the ropes 160, 162 a short distance apart! the cylindrical outer surface of the segments 152, 154. When rotating one of the segments, for example segment 152, by means of the hydraulic adjustment drive with parts 116, 118 and 164 that engages the eye of this segment the other segment 154 is rotated in the opposite direction by the same angular amount.

The degree of rotation of the support beams 34, 36 depends on the respective diameter of the winding roll 14. The force transmitted by the winding roll 14 to the support rollers 10, 12 in the winding gap, and thus the winding hardness eb «TJm, depend on the diameter of the winding roll 14, which is constant or arbitrary from position to position, independent of the respective weight of the tail of the paper web that has already been wound up To obtain adjustable BickelhUrte, one uses a load roller 18 suspended vertically above the axis of rotation of the roller 14, which can also be provided with additional load weights 20. This loading roller 18 with the loading weights 20 int attached to it, as in the exemplary embodiments according to FIG. Each rope V>; w. Chain 22 is - as in the Ausführungebeispielen of Figure 1 _e and 3 - first vertically

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above _s then via a guide roller 24 rotatably supported in the machine frame? from this down again and around another deflecting roller 25 rotatably mounted at the end of the piston rod 26 of a hydraulic pressure cylinder 28 - and then again to the top and finally attached to the machine frame with the free end. As in the above-described examples according to FIGS. 1 and 3, the lower end of the hydraulic pressure cylinder 26 is pivotably mounted in the machine frame; so that it is able to follow the movements of the deflection roller 25, and is provided with equipment for supplying pressure medium to the pressure chambers. By changing the pressure in the pressure cylinder 28, the amount of the load exerted by the loading roller 18 together with the loading weight 20 on the winding roller 34 is reduced in accordance with the self-weight of the winding roller 14, which increases during the winding process, and is achieved by the fact that the load from the winding roller 14 onto the support roller 10 transmitted, the winding hardness determining force has the desired value during the entire winding process.

In order to achieve a winding roll that is uniform over the entire width, as well as being equally hard from layer to layer or variable in terms of hardness in a predetermined manner, three variables are required during the winding process, depending on the increasing diameter of the winding roll

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14 to control, namely the direction of the support beams 34, 36 via Druckz.ylinu.er 116 _p the level of pressure in the Dructeiäume 54, 56 of the support whales 10, 12 and the size of the effective load by the pressure cylinder 28. The device provided for this purpose corresponds in all details to the device described in the exemplary embodiment according to FIG. 3, so that reference can be made to the description given in this regard.

To also the influence of the tension of the circulating paper web to be taken into account, which is particularly important for wide webs can be significant, a guide roller 158 is arranged in front of the support roller 10 receiving the incoming paper web, in their support 170, as well as in the bearing of the TJm onkwalze 124, a pressure cell 172 is arranged. The tension prevailing in the paper web 16 is determined by this pressure cell determined and via the amplifier 174 a Reohenrelais 176, which in turn sends the transformed signal to the control regulator 178. This increases the pressure in the print room 56 of the support roller 12 adjusted according to the paper tension.

The exemplary embodiment Fig. 8 differs from the example Fig. 4 only in the different design of the loading roller suspension and the unloading drive a.

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The loading roller 18 with the additional loading weight 20 that may be required is vertical or light inclined direction (* 30 °) in the machine frame and on one spindle 177 each hung on both sides of the machine. Between spindles 177 and load unit 18, 20 are calibration force measuring units 126 and spring elements 178, which are with are equipped with very flat spring constants (air springs, disc springs or others). On the machine frame top are tendon gears 179 designed as locker nuts, which in turn mesh with the torque-adjustable electric-air or hydraulic servo motors 180 via worms stand.

The number of revolutions of the worm is also a factor for changing the diameter of the winding roll 14, so the measuring device 124 is coupled to one of the screws.

The momentarily effective load weight of the load unit 18, 20, which varies as a function of the torque of the motors 180, is determined by the load cells 126 (strain gauges or other measuring units are also possible) and fed to the computing relay via an amplifier 128. From this measured variable , the control pulse for desire 134, which dictates the torque of servo motors 180, is formed there, using the diameter signal converted in computer 132.

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ι »η- * * · »F he

Ii t · »(^ ι ι · f

■ Il «« ι ι t frr -

«•« »•« ■ et 11 t β »· - ■" · ■> ·> »R ·»

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A hydraulic control is shown, "when used of air or electric motors are the units 150 and 134 choose differently accordingly.

When using an additional weight 20 (normally a carriage traverse) can be via the spindles 177 and the Worm drive 179 by the motors 180 the load roller 18 are also additionally pressed, which the construction simplified and cheaper, ihne the puncture, the line pressure between the winding roll 14 and the support rollers 10, 12 to keep constant, to impair.

Pig. 9 shows an exemplary embodiment in which with a heavy Schiitteatraverse 20 is worked, and therefore A controllable discharge is necessary for "

In addition to the loading rollers shown in Pignr 1, 3 and 8, there is the possibility, instead of the spindle-worm drive motor shown in Pigur 8, to drive 177, 179, 180 the printing cylinders shown in Pigur 1 and 3 28 to connect the measuring unit 126 (Pig. 8) to the loading roller directly via the Peder element 178 _U ra, dispensing with the rope, chain or belt pull 22 (Pig «I or 3) *

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Instead of the and The construction of the support rollers described with an adjustable meridian line in the winding gap can also be any other known construction of such rollers, both in the case of the support rollers as well as with the loading roller »

Claims (1)

• ·· »Iff ··?« « lit ·· · β »· ■■ ·· · · - 28 - Protection claims 1. Device for winding a running tape into a cylindrical winding roll with a uniform over the belt width as well as from position to position of the winding roll Winding hardness by exerting even compressive forces against the outer surface of the winding roll in the Winding gap, with a tape, for example a paper or film web, being fed continuously, with a The winding core arranged perpendicular to the direction of travel of the tape to accommodate the cylindrical winding roll to be wound up and with one with the lateral surface of the winding roll in pressure contact along a meridian line standing bobbin, which is used to generate the winding hardness, over which the tape moves from the feed direction in the direction tangential to the outer surface of the winding roll is deflected, marked thereby net that at least the tape (16) on the winding roll (i4) applying, with the outer surface of the winding roll winding body (10) standing in pressure contact along a meridional line as a revolving roller with in on known manner adjustable Meriaianlinie formed «Mä the meridian line of the winding roller independently from the external load in the area of the bridge contact ί is set in a straight line with the winding roll. 6 £ 44 109 tf · · - 29 - 2. BandaafWlckelTorriohtung according to claim 1, isdareh GEK _"f iiaielohBit that the ale Wals · eusgefeil * date winding body" it a separable lieridianllnie a d «c Sragwalsen two (10, 12) of a calibrated to let known Doppsltragwalsenrollers · 3. BftndacLfwiokexYorrlchtiiBg according to claim 2, characterized gekennieicb.net that the other fragwaxse of the Doppeltragwalaenroller is also educated as an orphan of old Iferldianlini 4. Bandaufwicke lvoriohtung according to claim 2 or 3 t characterized in that a · perpendicular arranged above the winding roll (U), with its outer surface in pressure contact along a Meridlan line standing burden whale (18) also as an orphan with adjustable Meridianllnie formed and irf.t a gate direction sum adjustment of the effective load connected 1st. 5 · Band Aufwlckelvorriohtung according to An *, ruch 1 to 4, characterized in that the winding body in a well-known manner as one aside over the bandwidth protruding hollow cylinder (30) bit over a one extending through it its two end faces protruding and with the over- - 30 - 6644109 cantilevered ends in the machine frame pivotably mounted support beam (34) eats against which the ends of the Hollow cylinder supported and sealed; are that, furthermore, the supporting beam is perpendicular in the area of the transverse diameter is sealed to the direction of pressure contact against the inner surface of the hollow cylinder, so that a between the supporting beam and the part of the shell of the hollow cylinder exposed to pressure contact with the winding roll (H) extending pressure chamber (54) connected to a pressure source is formed, and finally the pivotably mounted support beam with a device for pivoting the support beam relative to the machine frame in one of the respective directions of the pressure contact between the winding roll and the hollow cylinder corresponding Location is connected. 6. Tape winding device according to claim 5, characterized in that a device for adjusting the pressure in the pressure chamber (54) of the support roller (10) is also provided. 7. Tape winding device according to claim 6, characterized in that the pivoting device for the support beam (34) is in operative connection with the loading roller (18) for the purpose of adapting the setting angle of the support beam to the diameter of the winding roll (14). C β β I O 8- tape winding device according to Aasprucli 7 »characterized in that a reduction gear connected to the loading roller (18) is provided, for example one which is symmetrical to the support rollers (10, 12) and consists of four rods of equal length (38, 60, 62, 64) formed joint square, and that located in the plane of symmetry of the support rollers, the loading roller facing joint (66) is rotatably arranged a pulley (70) over which a rope (72) or the like. one end of the rope is attached to the machine frame and the other to the load roller (18) or the load weight (20) connected to it, and that the joint (68) of the four-bar linkage diagonally opposite the deflection roller is also supported on the machine frame and that finally a pivot lever (42, 44) attached to the associated support beam (34 or 36) in a rotationally fixed manner is articulated on the reduction gear, for example on each rod (62, 64) of the quadrangular articulation adjacent to a support roller. 9. B; 4idaufwickelvorrichtung according to claim 6 to 8, characterized in that a throttle valve for adjusting the pressure in the pressure chamber (54) of the ale winding roller serving hollow support roller jacket (30) is provided, that further the housing (82) of the throttle valve at one of two movable relative to each other 6C44109 - 32 - if- ι Parts of the reduction gear, for example on the fixed bracket (80), and the valve body (84) on the other of these two parts, for example on the neighboring one Rod (64) of the four-bar linkage is fixed in such a way that when the loading roller (18) is moved under the influence the increasing diameter of the winding roll (14), the flow cross-section for the pressure medium in the throttle valve increases. 10. Tape winding device η ch claim 4 to 9, characterized in that the loading roller (18) is connected in a manner known per se to the piston rod (26) of a pressure cylinder (28) for applying an adjustable counterforce through which cer of the loading roller the line pressure exerted on the winding roll (H) is reduced as the diameter of the winding roll increases. 11. Tape winding device according to claim 4 to 9 »characterized in that the loading roller (18) in a previously unknown manner by means of spin deln (177) and worm drives (179) by torque-controlled motors (180) exerts a line pressure on the winding roller (14) , which is reduced as the diameter of the winding roll increases, preferably ao that the idni pressure between the support rollers (10, 12) and the winding roll remain constant during the entire winding process. 6S44109