EP0912435B1 - Procede de bobinage continu d'une bande de materiau et bobineuse correspondante - Google Patents

Procede de bobinage continu d'une bande de materiau et bobineuse correspondante Download PDF

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Publication number
EP0912435B1
EP0912435B1 EP98928270A EP98928270A EP0912435B1 EP 0912435 B1 EP0912435 B1 EP 0912435B1 EP 98928270 A EP98928270 A EP 98928270A EP 98928270 A EP98928270 A EP 98928270A EP 0912435 B1 EP0912435 B1 EP 0912435B1
Authority
EP
European Patent Office
Prior art keywords
winding
drum
spool
transport device
winding machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP98928270A
Other languages
German (de)
English (en)
Other versions
EP0912435A1 (fr
Inventor
Roland Möller
Ralf Preising
Rudolf Beisswanger
Zygmunt Madrzak
Walter Kaipf
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Voith Patent GmbH
Original Assignee
Voith Paper Patent GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19735590A external-priority patent/DE19735590A1/de
Priority claimed from DE1997137709 external-priority patent/DE19737709A1/de
Priority claimed from DE19748995A external-priority patent/DE19748995A1/de
Application filed by Voith Paper Patent GmbH filed Critical Voith Paper Patent GmbH
Priority to EP02010520A priority Critical patent/EP1238933B1/fr
Publication of EP0912435A1 publication Critical patent/EP0912435A1/fr
Application granted granted Critical
Publication of EP0912435B1 publication Critical patent/EP0912435B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H19/00—Changing the web roll
    • B65H19/22—Changing the web roll in winding mechanisms or in connection with winding operations
    • B65H19/2238—The web roll being driven by a winding mechanism of the nip or tangential drive type
    • B65H19/2253—The web roll being driven by a winding mechanism of the nip or tangential drive type and the roll being displaced during the winding operation
    • B65H19/2261—Pope-roller
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H18/00—Winding webs
    • B65H18/08—Web-winding mechanisms
    • B65H18/26—Mechanisms for controlling contact pressure on winding-web package, e.g. for regulating the quantity of air between web layers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2301/00—Handling processes for sheets or webs
    • B65H2301/40—Type of handling process
    • B65H2301/41—Winding, unwinding
    • B65H2301/414—Winding
    • B65H2301/4144—Finishing winding process
    • B65H2301/41441—Finishing winding process and blocking outer layers against falling apart
    • B65H2301/41444—Specified by process phase during which sealing /securing is performed
    • B65H2301/414443—Sealing or securing within the winding station
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2403/00—Power transmission; Driving means
    • B65H2403/50—Driving mechanisms
    • B65H2403/52—Translation screw-thread mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2408/00—Specific machines
    • B65H2408/20—Specific machines for handling web(s)
    • B65H2408/23—Winding machines
    • B65H2408/236—Pope-winders with first winding on an arc of circle and secondary winding along rails
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2408/00—Specific machines
    • B65H2408/20—Specific machines for handling web(s)
    • B65H2408/23—Winding machines
    • B65H2408/2362—Winding machines with two secondary winding spools, e.g. on separate carriages
    • B65H2408/2364—Winding machines with two secondary winding spools, e.g. on separate carriages with additional element for facilitating web roll change
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2511/00—Dimensions; Position; Numbers; Identification; Occurrences
    • B65H2511/10—Size; Dimensions
    • B65H2511/14—Diameter, e.g. of roll or package
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2515/00—Physical entities not provided for in groups B65H2511/00 or B65H2513/00
    • B65H2515/30—Forces; Stresses
    • B65H2515/34—Pressure, e.g. fluid pressure

Definitions

  • the invention relates to a method for continuous Winding a web of material, in particular Paper or cardboard web, according to the preamble of Claim 1 and a winding machine for continuous Winding a web of material, in particular Paper or cardboard web, according to the preamble of the claim 13th
  • a so-called Pope roller is known from US Pat. No. 5,249,758 with a fixed, not relocatable Carrying drum out, over which on a drum material web to be wound up into a winding roll is led.
  • a displaceable drive roller provided with a winding roll during the majority of the winding process forms a winding gap.
  • the Drive roller 32 is only after a certain time the winding of the drum on the wound on it Winding roll with formation of a winding gap created.
  • the disadvantage here is that not in all cases an optimal core winding, which for the quality of the winding roll is important can be.
  • the process is characterized by following steps: The material web is over a relocatable pressure drum performed with the in a secondary conveyor rotatably held Winding roll forms a winding gap, wherein the line force in the winding nip during this winding phase by moving the pressure drum is controlled / regulated.
  • To prepare one Drum change is required when a desired one is reached Winding roll diameter by means of the secondary transport device from the Pressure drum removed so that the material web runs freely from the pressure drum to the winding roll.
  • a new drum rotating at web speed is by means of a primary transport device entered the free web train and into a reel change position brought in the new drum a new winding nip with the pressure drum forms.
  • the line force in Winding gap during the entire winding process exclusively through a relative movement of the Pressure drum set against the winding roll becomes. Because of the greater the weight becoming winding roll relatively light weight of the The pressure drum can be moved quickly. This can cause jumps and fluctuations in line force be compensated very quickly. hereby is an exact, even line force in the winding gap throughout, that is, a complete one Winding process adjustable / controllable so that overall a good winding quality can be achieved can. It is also particularly advantageous that the relatively low weight compared to the winding roll the pressure drum a change of direction Relocation movement of the pressure drum very quickly is feasible.
  • the method provides that when removing the winding roll from the pressure drum the same Winding roll until it reaches a stop follows, and that then the new drum into the Drum change position is brought, before Reel change of reel with the one wound on it Wind the reel from the stop pushes back.
  • This allows a relatively small Control effort is ensured be that the line force during a complete Winding process, i.e. from winding to Finished winding of the winding roll by relocation the pressure drum to a desired value can be set or held exactly can.
  • a variant of the Preferred method which is characterized by that the empty drum into one above a pressure drum brought lying winding position becomes. This is followed by a winding gap between the pressure drum and the empty drum by a relative movement between the pressure drum and drum formed.
  • the arrangement of the empty drum compared to the pressure drum is chosen so that through the winding nip and through the Longitudinal axes of the empty reel and the pressure drum certain contact level compared to an imaginary one Horizontal is inclined by an angle ⁇ , which in a range of 5 ° ⁇ ⁇ ⁇ 40 °, preferably from 10 ° ⁇ ⁇ 35 °, in particular of 15 ° ⁇ ⁇ 30 °.
  • An exemplary embodiment is also preferred the procedure, which is characterized in that after the takeover of a reel by the secondary transport device a compensation of the increase in diameter the winding roll by a preferably horizontal or at least approximate horizontal Relocation of the secondary transport facility he follows.
  • the adjustment of the line force and thus the pressure drum is shifted independently of the balancing movement of the growing Winding roll.
  • the load in the winding gap is therefore very precisely tunable or adjustable.
  • the previously occasionally in the winding nip occurring fluctuations or jumps in the line force are at least largely avoided. hereby can have a defined, even winding hardness can be set, in particular for an exact core winding can be ensured.
  • a winding machine is also used to achieve the stated object proposed that in claim 13 Features mentioned. This stands out characterized in that during the reel from the secondary transport device is led, the increase in diameter the winding roll due to a shift the secondary transport device can be compensated and the line force in the winding gap due to a shift the pressure drum adjustable, preferably are adjustable. It is advantageous that the opposite the winding roll has a relatively low weight the pressure drum is quickly displaceable, so that jumps in the line force in the winding gap very much can be quickly compensated.
  • An embodiment is particularly preferred the winding machine in which the reel change position is provided above the position in which the secondary transport device the new drum takes over.
  • the new winding gap is at an advantageous embodiment during the winding process in a through the longitudinal axes of the empty drum and the pressure drum Contact plane that is opposite to an imaginary horizontal is inclined by an angle .alpha Range of 5 ° ⁇ ⁇ ⁇ 40 °, preferably from 10 ° ⁇ ⁇ ⁇ 35 °, in particular of 15 ° ⁇ ⁇ ⁇ 30 ° lies. This will raise them in the contact plane lying component of the resulting from the dead weight Deflection and the contact pressure resulting deflection at least approximately on.
  • the diameter increase by relocating the secondary transport device equalizable and the line force in the winding gap by moving the pressure drum are adjustable, preferably adjustable, while the winding roll from the secondary transport device to be led.
  • the balance of the growing Winding roll diameter and adjustment the line force are thus separated from two separate ones operable or working from each other Facilities, the secondary transport facility and the pressure drum.
  • relatively light weight of the pressure drum can be relocated quickly and thus jumps and Fluctuations in line force are compensated very quickly become.
  • through the relatively low weight of the pressure drum Change of direction of the displacement movement very much can be carried out quickly by means of the pressing device is. Due to the independent relocation movements the pressure drum and secondary transport device can be - preferably constant - good winding result can be achieved.
  • An embodiment of the is also preferred Winding machine in which the at least one pressing device, with the help of which the pressure drum can be moved is, as - preferably hydraulic - piston and cylinder unit is formed.
  • the maximum stroke of the Piston is less than half the material layer thickness a finished winding roll.
  • the relocatable pressure drum remains up to a few seconds during the drum change practically constantly in contact with the winding roll.
  • the winding machine is characterized by a simple and inexpensive construction.
  • the maximum stroke of the piston at least greater than or equal to the layer thickness of a finished one Winding roll is.
  • an embodiment of the Winding machine preferred, in which the primary and of the secondary transport device only one at a time single drive, preferably center drive, is assigned, with the help of a torque the drum can be applied. That of the primary transport device assigned drive preferably also to accelerate an empty one Drums on the running speed of the material web used.
  • the winding machine described below is generally used for winding a material web.
  • the winding machine can be at the end of a machine for the production or finishing of a material web, for example a paper web to convert the finished material web into a Wind up the winding roll.
  • the winding machine can but also used for rewinding finished winding rolls become. By way of example only, it is assumed that this is a winding machine for Winding a continuous paper web.
  • FIGS 1 to 4 each show a schematic Schematic diagram of a first embodiment a winding machine 1, which is used for winding a following generally referred to as material web 3 Paper web on a drum, winding core or the like serves.
  • the winding machine 1 comprises in this embodiment two secondary transport devices 5 and 7, each one on second rails 9 include movable secondary carriage 11.
  • the Rails 9 are parallel to an imaginary horizontal arranged and on a machine frame 13 attached.
  • the secondary transport facilities 5, 7 are used for rotatable holding and guiding one reel along a second, horizontal extending guideway 14, which in an imaginary Level E lies in dashed lines. This spans a surface that is perpendicular to the Image plane of Figure 1 is.
  • Embodiment of the winding machine 1 is only a single secondary transport device provided whereby the structure of the winding machine is simplified.
  • the winding machine 1 further comprises a means a center drive indicated with a symbol 17 drivable pressure drum 19 which is rotatable held on a slide 21 which is movable on first rails 22. at this embodiment are the rails 9 and 22 arranged parallel to each other. The distance between the longitudinal axis 23 lying in plane E. the pressure drum 19 and the guide rails 15 is constant.
  • the guide carriage 21 is one here as a hydraulic piston and cylinder unit trained pressure device 25 assigned, which is attached to the machine frame 13.
  • the Pressure device 25 has one in a cylinder 27 guided piston 29, which with one on the Guide slide 21 engaging piston rod 31 is firmly connected. When the Piston rod 31 becomes the guide carriage 21 and thus the pressure drum, also known as the support drum 19 in FIG.
  • the pressure drum forms 19 with one wound on a reel 35 Winding roll 37 a winding gap, that is, the pressure drum 19 forms together with the winding roller 37 a nip.
  • the pressure drum 19 touches the winding roll over its entire length their scope.
  • secondary drive 39 indicated by a symbol, which is formed here by a center drive. With the help of the secondary drive 39, a torque on the lying on the guide rails 15 and held by the secondary transport device 5 Drum can be applied.
  • the guide rails 15 are in this way on the machine frame 13 attached that the longitudinal axis 41 of with its journals on the guide rails 15 overlying drums 35 in the same level E lies like the longitudinal axis 23 of the pressure drum 19th
  • the winding machine 1 are the pressure drum 19 and the drum lying on the guide rails 15 arranged at different levels (figures 9, 12, 13), but this does not affect the advantageous Operation of the winding machine 1 has.
  • the material web 3 is on the pressure drum 19th performed and wound on the winding roll 37.
  • the line force in the winding gap is determined by means of the Pressure device 19 assigned to the pressure device 25 controlled, that is, the pressure drum 19 with a defined force on the circumference of the winding roll 37 pressed, creating a desired winding hardness the winding roll or an even one Winding hardness curve can be adjusted.
  • that the line force in the winding gap is regulated is, that is, the pressure device 25 is part a control loop that automatically takes the line force holds at a desired value or established.
  • the line force can also be for example constant value can be kept if there is a fault in the winding process.
  • disruption can be a not entirely precise Procedure of the secondary transport device be so that the position of the pressure drum 19 and the winding roller 37 formed winding gap shifted slightly, or an unbalance the pressure drum and / or the winding roll.
  • the larger diameter of the winding roller 37 is due to a displacement of the winding roller 37 in Balanced in the direction of arrow 33 to the right.
  • the secondary transport device 5 move to the right, causing the Drums 35 and thus the winding roll 37 takes place.
  • a lifting device 43 is provided here, the one threaded spindle driven by a motor 45 47 includes.
  • the pressure drum 19 is one of one primary transport device, not shown, empty drum 49 in a standby position arranged ( Figures 1 and 2).
  • the drum 49 becomes a drum change with the help of the primary transport device from the Standby position in a reel change position relocated to the primary transport facility, their structure in the following is still described, stationary and rotatable is held ( Figure 3).
  • the empty drum 49 is in the reel change position, is caused by a relative movement between the pressure drum 19 and empty drum 49 a winding nip formed, that is, the pressure drum and the empty reels touch each other on their circumference, over their entire length.
  • drum change position empty drum 49 is after the separation of the material web by means of a Not shown, known separation device (symbolically in Figures 8c and 14c represented by an arrow T) the web with her new web start.
  • the primary transport device can the drum 49 along a first guideway from the standby position to and from the drum change position be moved to a finished winding position (figure 4).
  • a finished winding position (figure 4).
  • the first guideway can have a curved, preferably part-circular, and / or have a linear course.
  • the primary transport facility is not shown, also as Primary drive designated center drive for the of this drum held respectively Assigned winding roll, by means of which the reel with a drive and / or braking torque can be.
  • the empty drum 49 is in the drum change position arranged in the after a The new web start is cut onto the Tambour 49 is wound up.
  • the drum 49 forms with the Press drum 19 a winding nip, which in a Contact plane P lies opposite an imaginary one Horizontal is inclined by an angle ⁇ , which in a range of 5 ° ⁇ ⁇ ⁇ 40 °, preferably of 10 ° ⁇ ⁇ ⁇ 35 °, in particular 15 ° ⁇ ⁇ ⁇ 30 °.
  • the angle ⁇ here is approximately by way of example only 32 °. Angles ⁇ have been found to be particularly advantageous highlighted, which are in the range of 15 ° to 30 °.
  • a pressure element provided that in this embodiment of one over the entire width of the winding roll 37 extending, also referred to as a squeeze roller Pressure roller 51 is formed.
  • the drive roller 51 is by means of a not shown Guide to the scope of the with the Pressure drum 19 a winding roll forming a nip pressed.
  • the pressure roller 51 serves to entraining air between the winding layers prevent the winding roll, for example, if the material web 3 in a free train of the Pressure drum to the winding roll runs.
  • the pressure roller 51 can be from a drive, for example Center drive, applied with a torque and accelerated to web speed.
  • the embodiment is the pressure element formed by a stationary pressure brush, the on at least one across the entire width the winding roll extending beams attached is.
  • the Pressure brush placed on the winding roller, whereby the air carried in between the winding layers is practically deleted.
  • the pressure brush has a simplified compared to the pressure roller and therefore less expensive to build on because they not rotating and therefore an additional drive is not needed. This also applies to a so-called Air brush; one over the width of the web extending air blowing nozzle, which is non-contact in the sense of an air squeeze device acts on the winding roll.
  • the material web 3 is on the pressure drum 19th guided and on by the secondary transport device 5 guided winding roll 37 wound ( Figure 1). Before the winding roller 37 its final diameter reached, the pressure roller 51 to the Circumference of the winding roller 37 pressed ( Figure 2). The Material web 3 is thus both through the winding gap between pressure drum 19 and winding roller 37 as well as through the winding gap between the pressure roller 51 and winding roller 37 out.
  • the winding roll 37 For transfer the continuously fed material web 3 on the empty reel 49, the winding roll 37 by means of the secondary transport device 5 along the guide rails 15 in the direction of arrow 33 procedure, causing the distance between the Longitudinal axis 23 of the pressure drum 19 and the Longitudinal axis 41 of the winding roller 37, both in here the plane E, enlarged and between the pressure drum 19 and the winding roller 37 a space 53 is formed ( Figure 3).
  • the material web 3 is in the area of the space 53 in one free train from the pressure drum 19 on the winding roll 37 transferred.
  • the pressure roller 51 is while the secondary transport device 5 with the Winding roller 37 is moved, the winding roller 37 tracked such that the line force in the winding gap between pressure roller 51 and winding roller 37 maintains a desired value until the pressure drum 19 against at least one stop 54 moves.
  • the stop is 54 realized in that the piston 29 of Pressure device 25 on the inner wall of the cylinder 27 triggers, that is, as shown Figure 3- right end position reached, in which Piston 29 abuts the inner wall of the cylinder 27.
  • the pressure drum 19 thus has a fixed Position on.
  • the drum 49 remains in a variable period of time the reel change position, for example until the The winding of the core of the new winding roll has been completed is. Then the one from the primary conveyor rotating drum 49 along the first guideway from the reel change position led into the finished winding position and lowered directly onto the guide rails 15 ( Figure 4).
  • FIG 1 is one below the pressure drum 19th arranged, rotatable on the machine frame 13th attached web guide roller 55 shown.
  • the web of material 3 is one of the web guide roller 55 -in Direction of travel of the material web seen - upstream Unit 57, which here is purely an example
  • Press device 59 is guided to the web guide roller 55 deflected by this and on to the pressure drum 19 headed.
  • the web guide roller 55 of the material web preferably in a peripheral region from 155 ° to 205 °.
  • the wrap angle is at least 150 °, even then, if the pressure drum 19 during the winding process is shifted. This ensures that the line force in the winding gap through a change in the longitudinal tension in the range between the unit 57 and the pressure drum 19 is not affected.
  • the pressing device 59 comprises two press rolls forming a press nip, from which - as shown in Figure 1 - at least one is driven.
  • the material web guide is preferred designed so that the pressure drum 19 by the material web 3 is wrapped around 180 °.
  • a winding gap between the pressure drum 19 and the empty drum is through it realizable that the empty drum along the first Guideway is shifted and against the in the first guide track arranged pressure drum abuts.
  • the winding gap by a shift the pressure drum 19 with the help of the pressure device 25 towards the in the reel change position arranged drum is formed.
  • both the Tambour 49 and also the pressure drum 19 moved towards each other to form a winding nip.
  • sudden fluctuations in line force like them for example at the moment the drum is handed over from the primary transport device to the Secondary transport device occur with the help the displaceable pressure drum compensated respectively be avoided.
  • the line force can that is, continuously exactly at a desired value being held.
  • the pressure drum 19 can, as in Figures 3 and 4, as a deflection adjustment roller 140 are formed, the roll shell 141 by means of a series of support members 142 on a stationary Yoke 143 is supported, creating an arched Outer contour of the pressure drum 19 achieved. Of those acting in the direction of the winding gap Support elements 142 is in the view according to the figures 3 and 4 only one recognizable.
  • the structure of the Deflection adjusting roller 140 is known per se (DE-OS 25 55 677), so that this is not described in detail becomes.
  • the support members 142 are preferred individually, that is, independently of each other controllable, which creates a desired curvature the roll shell 41 can be adjusted.
  • the yoke 143 is about a fixed axis, here the longitudinal axis 23 rotatable. Those cooperating with yoke 143 Support elements 142 are when the Yokes 143 pivoted such that their direction of action follows the traveling movement of the winding gap.
  • the outer contour of the pressure drum can be guided over it Material web - transverse to the running direction of the web seen - defined tension, preferably before the material web runs into the winding nip. This can cause wrinkling on the Prevents the winding roll from being wound and thus the winding result can be improved.
  • the Deflection of the pressure drum is in the longitudinal direction seen in the drum, as described above, preferably adjustable in sections. This allows the desired width extension of the material web vary the outer contour of the pressure drum, preferably be set.
  • the pressure drum 19 part of an active vibration damping system that is the pressure drum capable of oscillation.
  • FIG. 5 shows a schematic diagram of the winding machine according to Figures 1 to 4 with an embodiment a controller. Parts that match those in the figures 1 to 4 match, are with the same reference numerals provided so that in this respect to the description is referred to Figures 1 to 4.
  • a Control unit 61 provided the motor 45 of the Thread spindle depending on the speed the diameter increase of the winding roller 37 controls.
  • the diameter increase of the winding roll 37 is measured by means of a measuring device 63.
  • the Position of the secondary transport device 5 changed so alone, that means exclusively corresponding to the increase in the winding roll diameter.
  • the winding gap is alone, that is to say exclusively by a method of holding the pressure drum 19 Guide carriage 21 determined, preferably by means of a control device 65 regulated.
  • This includes a measuring device 67 for the line force, a controller 69, a setpoint generator 71 and a Control unit 73.
  • the measuring device 67 is over a measuring line 75 connected to the controller 69 or flows into this.
  • the setpoint generator 71 is connected to the controller 69 via a line 75 ' and gives it the desired setpoint.
  • the controller 69 is in turn connected via a line 77 the control unit 73 connected.
  • the controller 69 In the event that the measured by the measuring device 67 Value of the line force in between the pressure drum 19 and the winding roller 37 formed Winding gap from that specified by the setpoint device If the setpoint deviates, the controller 69 outputs the line 77 a signal to the control unit 73. This thereupon changes the pressure in the cylinder 27 of the pressing device 25 such that the measured Line force value approximates the target value. hereby the line force can also be for example constant value can be kept if there is a fault in the winding process. A For example, disruption can be a less than precise one Method of the secondary transport device 5, so that the position of the pressure drum 19 and that of the secondary transport device 5 guided winding roll 37 formed nip shifted slightly.
  • the pressure drum 19 for controlling the Line force regardless of the driving speed the secondary transport device is displaceable. It is also possible that with the secondary transport device interacting lifting device 43, that is, the one driving the threaded spindle 47 Motor 45 is controllable so that the Position of the between the pressure drum 19 and the Winding roll 37 formed nip essentially is constant while the winding roll 37 is on the guide rails 15 rests. Under “constant Position "of the winding nip becomes its position within the winding machine 1 understood, that is, the winding roll 37 is by means of the secondary transport device 5 at a speed in Shifted in the direction of arrow 33, so that only compensates for the diameter increase of the winding roll 37 becomes.
  • that the secondary transport device 5, 7th assigned lifting device 43 can be controlled in such a way that the position of the between the pressure drum 19 and the winding roller 37 formed nip with increasing winding roll diameter during of the winding process, for example in a range from 50 mm to 200 mm.
  • Figure 6 shows a schematic representation of a Another embodiment of the winding machine 1. Parts which correspond to those in FIGS. 1 to 5, are provided with the same reference symbols, so that in this respect to the description of Figures 1 to 5 is referred.
  • Figure 6 is part of a Embodiment of the primary transport device 79 shown. This includes two primary swivel levers 81, of which in this view only one is shown.
  • the primary swivel levers 81, on which the new drum 49 is rotatably held are parallel to the longitudinal axis of the drum 49 extending axis 83 pivotable.
  • the primary swivel levers 81 are inside the winding machine 1 stationary, that is, the axis 83 points - at least during a complete Winding process - a fixed, unchangeable position on the machine frame 13.
  • the primary swivel levers 81 is one on the machine frame, for example 13 attached lifting device 85 assigned the at least one associated with a primary pivot lever -preferably hydraulic- piston and cylinder unit includes.
  • the piston and cylinder unit comprises a piston guided in a cylinder 87 89, with one on at least one of the primary pivot levers 81 engaging piston rod 91 firmly connected is.
  • the lifting device 85 also, for example, two piston and Cylinder units each include a primary pivot lever 81 are assigned.
  • the primary swivel levers 81 as in FIG. 6 shown - the empty reel 49 in the reel change position hold are in this winding phase compared to an imaginary, with a dashed line shown horizontal H inclined by an angle w, which is about 26 ° here.
  • the angle is w adjustable by means of the lifting device 85.
  • a control device 93 provided that a controller 69 ', a setpoint generator 71 'and a measuring device 67' for the detection the position of the primary drive lever 81 includes.
  • the setpoint generator 71 ' is via a signal line 95 with the controller 69 'and the measuring device 67 'via a signal line 97 to the controller 69 'connected.
  • the Setpoint generator 71 By the angle w and thus the location to change the reel position is the Setpoint generator 71 'entered a new setpoint. With the help of the controller 69 'a target / actual comparison is made carried out. In the event of a deviation, the Controller 69 'via a line 77' a signal on hydraulic control valve 99, which then the Flow between a pump 101 and one of the Control valve 99 to the cylinder 87 leading medium line 103 releases.
  • the medium conveyed by the pump for example a hydraulic fluid or a gas, can optionally be in one of the pistons 89 separate subspaces of the cylinder 87 are introduced. If the medium in the in the representation according to FIG.
  • Angle w can be set.
  • the position of the reel change position predetermined before the next drum change can be, for example, a Angle w can be set, which is zero (For example, according to Figure 14c).
  • Figure 7 shows a view of the drum 49 in the shown in Figure 3 winding phase in which the reel 49 is in the reel change position and with the pressure drum 19 a winding nip forms.
  • the direction of view of the Drum 49 marked with an arrow 107.
  • the Force with which in this embodiment Press drum 19 pressed against the circumference of the drum 49 leads to one with a double arrow 109 shown deflection of the drum 49. Die the curvature of the
  • the outer contour of the drum 49 is shown schematically with a Line 111 shown.
  • the in the contact plane P lying component of the own weight of the Drum 49 resulting deflection is with a Double arrow 113 shown. Is schematic with a line 115 the curved outer contour of the unsupported drum.
  • the deflections act in opposite directions, their Amount is at least substantially the same.
  • the Deflections are therefore preferred completely, but at least essentially on it that a uniform line force in the winding gap adjusted across the entire width of the material web can be.
  • Figures 8a to 8e each show a highly schematic Representation of part of the on the basis of previous figures described winding machine 1 in different winding phases. Based on Figures 8a to 8e will already be the above briefly described drum changing process in more detail explained.
  • an empty reel 49 from the stationary winding station namely from the Primary transport device 79
  • the primary pivot lever here 81 includes, adopted ( Figure 8a).
  • the primary pivot levers 81 are opposed clockwise up to that shown in Figure 8a Empty drum takeover position swiveled.
  • the empty drum 49 is by means of Primary drive accelerated to synchronous speed, that is, the peripheral speed of the empty drum 49 corresponds to the running speed the material web 3.
  • the pressure element, here the pressure roller 51 is almost to the circumference of full winding roller 37 pressed. Not the one Secondary transport device shown held and driven by the secondary drive Winding roll 37 is together with the pressure roller 51 in the direction of arrow 33 from the pressure drum 19 removed.
  • the pressure drum 19 is the Wrapping roller 37 tracked to a desired one Maintain line force in the winding gap, until the pressure drum 19 against a stop 117 drives, causing their displacement movement is stopped.
  • the winding roll 37 continues in the direction of arrow 33, creating a free web train between the pressure drum and the winding roll is formed.
  • FIGS. 8a to 8c show the Distance x of the longitudinal axis 23 of the pressure drum 19 to the stationary axis 83 the primary pivot lever 81, which lies on an imaginary vertical V, immediately before changing the reel (Figure 8a) while des. drum change ( Figure 8b) and after Drum change (Figure 8c) shown.
  • the distance x2 is greater than that Distance x3, which is after pushing back the pressure drum through the into the reel change position relocated drum 49 sets. It can also be seen that before the pressure drum against the Stop 117 moves, this a distance x1 to Axis 83 which is smaller than the distance x2.
  • the material web in the area of free move separated and the new beginning of the path the drum 49 performed.
  • the drum 49 is preferably as long held in the reel change position until formation of the winding core of the new, on the reel 49 wound winding roll 119 completed until, for example, the winding roll 119 is one Layer thickness S has from 20 mm to 100 mm.
  • the pressure drum 19 is removed accordingly the diameter increase of the winding roll 119 from the longitudinal axis of the reel 49. From the amount forth corresponds to the displacement of the pressure drum exactly the horizontal component of the radius increase.
  • the full winding roll 37 is braked and from the variable winding station, i.e. the secondary transport device applied. With a preferred one Embodiment in which only one secondary transport device is provided, the Secondary transport device for taking over the the guide rails 15 after the reels 49 shifted left towards the pressure drum.
  • the winding machine in which two secondary transport devices are provided , they become alternating, i.e. alternating used to guide a new winding roll.
  • the two secondary transport devices only carry every second new winding roll.
  • the radius increase the winding roll by a corresponding shift of the reel with the help of the secondary transport device balanced. The amount corresponds the displacement of the drum in the horizontal direction exactly the radius increase.
  • FIGS 9 to 11 each show a side view a part of another embodiment of the Winding machine 1 in different winding phases.
  • the Construction of the winding machine 1 essentially corresponds that described with reference to Figures 1 to 8 Winder. In the differences following discussed in more detail. Same parts are provided with the same reference numerals, so that so far to the description of the previous figures is referred.
  • the piston 27 the pressing device 25 at this moment a distance to the inner wall of the cylinder 29;
  • the piston 27 is therefore not in an end / stop position.
  • the new drum 49 is in its finished winding position represented, that is, this lies with its trunnions on the guide rails 15 on the weight of the reel 49 and the wound on it - not shown - only Support a winding roll that has a few winding layers.
  • the finished winding position (FIG. 11) becomes the pressure drum 19 by means of the pressing device 25 shifted along the straight line G1, so that the line force in the winding nip during the entire transfer is kept at a desired value.
  • the winding roll 37 is in a deployment position arranged in the winding roll by means of known devices from the guide rails 15 lifted and out of the winding machine 1 can be applied.
  • illustrated embodiment of the winding machine 1 is only a single secondary transport device and only one secondary drive 39 is provided. These are already to be adopted in FIG. 11 of the drum 49 from the primary transport device 79 to the left in the direction of the pressure drum 19 relocated.
  • the secondary transport device 5 and the secondary drive 39 can be common or independently of one another in the takeover position be relocated. While the secondary transport device 5 the drum 49 from the primary pivot levers 81 takes over, becomes the secondary drive 39 coupled to the drum 49, so that temporarily both drives 39 and 121 on drum 49 are coupled.
  • FIG. 10 shows a control of the winding machine 1, which comprises a control device 65.
  • a control device 65 to Explanation of the structure and operation of the Control device 65 is used to describe the figure 5 referenced.
  • the pressure drum 19 for controlling the Line force regardless of the driving speed the secondary transport device 5 can be moved is. It is also possible that the secondary transport device 5 assigned lifting device 43, that is, the one driving the threaded spindle 47 Motor 45 is controllable so that the Position of the between the pressure drum 19 and the Winding roll 37 formed nip essentially is constant. Under "constant position" of the Winding nip will be its position within the Understanding winding machine 1.
  • the winding roll 37 is by means of the secondary transport device 5 with only the diameter increase of Winding roll 37 compensating speed in Shifted in the direction of arrow 33.
  • the secondary transport device 5 assigned lifting device 43 can be controlled in such a way that the position of the pressure drum 19 and the winding roll 37 formed winding gap increasing winding roll diameter during the Shifts, for example, in one Range from 50 mm to 200 mm.
  • the winding gap is in a preferred embodiment when winding an empty drum always in the same place, that is, its position inside the winding machine is during a Drum change constant, but at least essentially constant.
  • winding one empty drums always have the same angular relationships, for example the one acting on the drum Contact pressure, before, so that the deflection of the empty Drums calculated and balanced accordingly can be to a desired line force curve set in the winding gap.
  • the reel change position, in which the winding gap is formed becomes; to postpone.
  • Figure 12 shows schematically a side view of a further example of the winding machine 1. Parts that match those of FIGS. 1 through 11 described, have the same reference numerals provided so that in this respect to the description reference is made to Figures 1 to 11.
  • the primary transport device 79 includes this Embodiment one on third rails 123 movable in the direction of a double arrow 125 Holding device 127 in which the empty drum 49 is held stationary and rotatable. The holding device 127 therefore leaves a rotational movement des Tambours 49 and prevents it from translational movement.
  • the reel 49 can from the reel change position (not shown) along the straight first realized by the rails 123 Guideway 14 'shifted to the finished winding position in the Tambour 49 on the guide rails 15 rests.
  • the drum 49 from a higher level (G2) to a lower level Level (G1) shifted or lowered.
  • the third rails 123 are opposite one imagined, shown with dashed line Horizontal H inclined at an angle z, that in the exemplary embodiment shown in FIG is in a range from 45 ° to 90 °.
  • a second embodiment variant continues from FIG a control system for adjustment the line force in the winding gap between the Press drum and a drum or one Winding roll emerges, which differs from that based on the Figure 10 control described thereby distinguishes that the travel speed of the secondary transport device 5 depending on the Position of the piston 29 in the cylinder 27 of the pressing device 25 set or changed becomes.
  • the regulator 73 can control the pressure in the cylinder 27 and thus the line force in the winding gap in Control / regulate dependency of several parameters.
  • the Parameters are those measured with a measuring device 129 Longitudinal tension of the material web 3 (web tension), the diameter D of the winding roller 37 and an angle ⁇ , the position of one of the primary transport 79 guided drums indicates.
  • the Diameter D of the winding roller 37 and the angle ⁇ are calculated and / or determined Figure 12 exemplified - control curve taken.
  • the angle ⁇ becomes the longitudinal axis between one the pressure drum 19 and the empty drum 49 intersecting plane 131 and the straight line G1 measured.
  • the control unit is connected via a signal line 133 61 transmits the position of the piston 29 in the cylinder 27, which drive the threaded spindle 47 Motor 45 of the lifting device 43 controls.
  • FIG. 13 shows a further embodiment of the Winding machine 1 according to the invention with a the controller described in Figures 5 and 10. Same Parts are provided with the same reference symbols, so that in this respect to the description of the previous Figures is referenced.
  • the pressure drum 19 is in a shift by means of the pressure device 25 in the direction of an arrow 135 from one lower level to a higher one Level raised, that means shifted diagonally upwards.
  • the pressure drum 19 only with the winding roller 37, but not with the empty, arranged in reel change position Drum 49 in contact.
  • the weight of the pressure drum 19 is still largely supported by the rails 22, so that a sufficiently precise control of the line force is easily possible in the winding nip.
  • a small proportion of the weight of the pressure drum influences the measuring and / or the setting accuracy the line force, namely only the downhill drive component.
  • Figures 14a to 14e each show a highly schematic Representation of part of the on the basis of previous Figures 1 to 11 and 13 described Winding machine 1 in different winding phases. In the following only the differences in how it works.
  • the new Tambour 49 before changing the drum on the guide rails (not shown) 15 filed.
  • the pressure drum 19 against one Stop 117 ' which is positioned so that when the new drum 49 is inserted into the Drum change position the pressure drum 19 from the stop 117 'is pushed back while the Drum 49 approaches the guide rails 15.
  • the Stroke of the pressure drum i.e. the maximum distance, which moved the pressure drum in one direction can be greater than or equal to the material layer thickness S a finished winding roll. hereby can be on a secondary transport device, which the reel during the finishing process according to the diameter increase of the winding roll be relocated, waived.
  • the winding roll will in this embodiment in two fixed Winding stations wound.
  • a "fixed" winding station " is characterized by the fact that the drum is rotatably held so that both the Increase in diameter of the winding roll wound on it as well as adjusting the line force in the winding gap only by a shift the pressure drum is realized.
  • a firm one Winding station has the advantage that it is a offers optimal rigidity of the drum clamping, so that a forwarding of possibly occurring Vibrations on the winding roller practical can be excluded. Because the relocation route the pressure drum is so large that the Diameter increase can be fully compensated constant drum tracking is not required, thereby building the winding machine can be simplified.
  • All embodiments of the winding machine is common that in preparation for a reel change a gap / gap between the near finished winding roll and the pressure drum formed becomes. This can ensure that the Material web over before the reel change a circumferential area of the drum change position arranged, empty drum is performed. Thereby can guarantee a high level of functional reliability become.
  • the stationary, rotatable holding of the new drum Start of the winding process in the primary transport device, on an actuating device, as in known winding machines is often used, can be dispensed with.
  • This actuator is used by the primary transport device guided reel radially in the direction of the pressure drum to shift to the line force in the winding nip adjust. Because of this advantageous Design can be based on additional control waived for the actuator be so that the cost of the winding machine is reduced are.
  • All embodiments of the winding machine is common that the control / regulation of the line force in the winding nip according to the invention entire winding process exclusively from one single device is executable, namely by a shift of the pressure drum with the help of Pressure device 25.
  • the winding machine can be equipped with a winding core on which one winding tube or several winding tubes attached are. In the latter case, the Winding machine upstream of a slitter his. This cuts the web into several Partial webs, each partial web on a winding sleeve is wound up.

Landscapes

  • Replacement Of Web Rolls (AREA)
  • Winding Of Webs (AREA)

Claims (41)

  1. Procédé d'enroulement continu d'une bande de matériau (3), notamment une bande de papier ou de carton, en formant un rouleau enroulé sur un tambour, caractérisé par les étapes suivantes :
    la bande de matériau (3) est guidée sur un cylindre presseur positionnable (19) qui, avec un rouleau enroulé (37) logé de manière à pouvoir tourner dans un dispositif de transport secondaire (5 ; 7), forme une fente d'enroulement, la force rectiligne dans la fente d'enroulement étant commandée / régulée par un changement de position du cylindre presseur (19) ;
    lorsqu'un diamètre voulu du rouleau enroulé est atteint, le rouleau enroulé (37) est éloigné du cylindre presseur (19) au moyen du dispositif de transport secondaire (5 ; 7) en vue de préparer un changement de tambour de manière à ce que la bande de matériau (3) puisse défiler vers le rouleau enroulé en étant dégagée du cylindre presseur (19) ;
    un nouveau tambour (49) qui tourne à la vitesse de la bande est amené au moyen d'un dispositif de transport primaire (79) dans une position de changement de tambour dans laquelle il forme avec le cylindre presseur (19) une nouvelle fente d'enroulement ;
    la bande de matériau (3) est sectionnée transversalement sur sa largeur et enroulée sur le nouveau tambour (49) avec sa nouvelle amorce de bande, la commande /régulation de la force rectiligne dans la fente d'enroulement entre le cylindre presseur (19) et le nouveau tambour (49) étant ici de nouveau réalisée par un changement de position du cylindre presseur (19) ;
    le dispositif de transport secondaire (5 ; 7) prend en charge le nouveau tambour (49) muni du nouveau rouleau enroulé, la commande / régulation de la force linéaire s'effectuant là encore par un changement de position du cylindre presseur (19).
  2. Procédé selon la revendication 1, caractérisé en ce qu'une compensation de l'augmentation du diamètre du rouleau enroulé est réalisée après la prise en charge d'un tambour par le dispositif de transport secondaire par un changement de position de préférence au moins approximativement horizontal du dispositif de transport secondaire.
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que la fente d'enroulement entre le nouveau tambour et le cylindre presseur est formée par un mouvement relatif du cylindre d'enroulement par rapport au tambour vide.
  4. Procédé selon la revendication 1 ou 2, caractérisé en ce que la fente d'enroulement est formée par un mouvement relatif du tambour vide par rapport au cylindre presseur.
  5. Procédé selon la revendication 4, caractérisé en ce que lors de l'éloignement du rouleau enroulé du cylindre presseur de celui-ci, le rouleau enroulé suit le mouvement jusqu'à atteindre une butée et que le nouveau tambour est ensuite amené dans la position de changement de tambour où il repousse le cylindre presseur de la butée.
  6. Procédé selon l'une des revendications précédentes, caractérisé en ce que la fente d'enroulement est formée au-dessus de la position dans laquelle le dispositif de transport secondaire prend en charge le nouveau tambour.
  7. Procédé selon la revendication 6, caractérisé en ce que la fente d'enroulement est formée dans un plan de pressage défini par les axes longitudinaux du tambour vide et du cylindre presseur, lequel est incliné selon un angle α par rapport à une horizontale imaginaire, angle qui est compris dans une plage de 5° ≤ α ≤ 40°, de préférence de 10° ≤ α ≤ 35°, plus particulièrement de 15° ≤ α ≤ 30°.
  8. Procédé selon l'une des revendications 1 à 5, caractérisé en ce que la position de changement de tambour se situe à l'endroit où le dispositif de transport secondaire prend en charge le nouveau tambour.
  9. Procédé selon l'une des revendications précédentes, caractérisé en ce que pendant que la bande de matériau est guidée vers le rouleau d'entraínement en étant dégagée du cylindre presseur, un élément presseur, de préférence un rouleau de compression, une brosse de compression non rotative ou similaire est pressé sur le pourtour du rouleau d'entraínement.
  10. Procédé selon l'une des revendications précédentes, caractérisé en ce que la bande de matériau est déjà amenée sur une zone de pourtour du nouveau tambour pendant que celui-ci se trouve dans la position de changement de tambour.
  11. Procédé selon l'une des revendications précédentes, caractérisé en ce que le rouleau enroulé guidé par le dispositif de transport secondaire change de position en permanence pour compenser l'augmentation du diamètre.
  12. Procédé selon l'une des revendications précédentes, caractérisé en ce que la vitesse de changement de position du nouveau tambour guidé par le dispositif de transport primaire et du rouleau enroulé guidé par le dispositif de transport secondaire est constante ou varie de préférence à au moins un endroit quelconque.
  13. Enrouleuse pour l'enroulement continu d'une bande de matériau (3), notamment une bande de papier ou de carton, sur un tambour pour former un rouleau enroulé, comprenant un cylindre presseur (19) sur lequel est guidée la bande de matériau (3) et qui forme une fente d'enroulement avec le rouleau enroulé, comprenant au moins un dispositif de transport primaire (79) à l'aide duquel le tambour (35 ; 49) peut être positionné le long d'une première voie de guidage, et comprenant au moins un dispositif de transport secondaire (5 ; 7) qui guide le tambour (35 ; 49) le long d'une deuxième voie de guidage, caractérisée en ce que pour préparer un changement de tambour, le nouveau tambour (35 ; 49) peut être amené dans une position de changement de tambour au moyen du dispositif de transport primaire (79) dans laquelle une nouvelle fente d'enroulement est formée entre le nouveau tambour (35 ; 49) et le cylindre presseur (19), qu'en position de changement de tambour la bande de matériau (3) est guidée sur une zone de pourtour du nouveau tambour (35 ; 49), et que pendant que le tambour (35 ; 49) est guidé par le dispositif de transport secondaire (5 ; 7), l'augmentation de diamètre du rouleau enroulé peut être compensée par un changement de position du dispositif de transport secondaire (5 ; 7) et la force rectiligne dans la fente d'enroulement est réglable, de préférence régulable, par un changement de position du cylindre presseur (19).
  14. Enrouleuse selon la revendication 13, caractérisée en ce que la position de changement de tambour est prévue au-dessus de la position dans laquelle le dispositif de transport secondaire (5 ; 7) prend en charge le nouveau tambour (35 ; 49).
  15. Enrouleuse selon la revendication 13 ou 14, caractérisée en ce que la nouvelle fente d'enroulement se trouve dans un plan de pressage (P) défini par les axes longitudinaux du tambour vide (35 ; 49) et du cylindre presseur (19), lequel est incliné selon un angle α par rapport à une horizontale imaginaire (H), angle qui est compris dans une plage de 5° ≤ α ≤ 40°, de préférence de 10° ≤ α ≤ 35°, plus particulièrement de 15° ≤ α ≤ 30°.
  16. Enrouleuse selon la revendication 13, caractérisée en ce que la position de changement de tambour se trouve à l'endroit où le dispositif de transport secondaire (5 ; 7) prend en charge le nouveau tambour.
  17. Enrouleuse selon l'une des revendications 13 à 16, caractérisée en ce que le cylindre presseur (19) est positionnable à l'aide d'un dispositif de compression (25) et qu'un changement de position du cylindre presseur (19) permet de compenser l'augmentation du diamètre et de commander / réguler la force rectiligne dans la fente d'enroulement pendant que le rouleau enroulé est guidé par le dispositif de transport primaire (79).
  18. Enrouleuse selon l'une des revendications 13 à 17, caractérisée en ce que la fente d'enroulement est formée par un mouvement relatif du nouveau tambour (35 ; 49) par rapport au cylindre presseur (19) et/ou par le mouvement relatif du cylindre presseur (19) par rapport au nouveau tambour (35 ; 49).
  19. Enrouleuse selon l'une des revendications 13 à 18, caractérisée en ce que le cylindre presseur (19) est maintenu sur un chariot de guidage (21) de manière à pouvoir tourner et que le chariot de guidage (21) est mobile sur des premiers rails (22) qui sont disposés parallèlement à une horizontale imaginaire (H) ou inclinés par rapport à celle-ci selon un angle β (figure 13).
  20. Enrouleuse selon l'une des revendications 13 à 18, caractérisée en ce que le cylindre presseur (19) est maintenu de manière à pouvoir tourner sur des leviers pivotants qui peuvent pivoter autour d'un axe parallèle à l'axe longitudinal du tambour.
  21. Enrouleuse selon l'une des revendications 13 à 20, caractérisée en ce qu'un mécanisme d'entraínement, de préférence un entraínement central (17), est associé au cylindre presseur (19).
  22. Enrouleuse selon l'une des revendications 13 à 21, caractérisée en ce que le dispositif de transport secondaire (5 ; 7) comprend un chariot secondaire (11) qui peut se déplacer sur des deuxièmes rails (9), les rails (9) étant disposés parallèlement à une horizontale imaginaire (H) ou inclinés par rapport à l'horizontale imaginaire (H).
  23. Enrouleuse selon l'une des revendications 13 à 21, caractérisée en ce que le dispositif de transport secondaire (5 ; 7) comprend des leviers pivotants secondaires sur lesquels le tambour est maintenu de manière à pouvoir tourner et qui peuvent pivoter autour d'un axe parallèle à l'axe longitudinal du tambour.
  24. Enrouleuse selon l'une des revendications 13 à 23, caractérisée en ce qu'au moins un mécanisme d'entraínement secondaire, de préférence un entraínement central est associé au dispositif de transport secondaire (5 ; 7) pour soumettre le tambour à un couple d'entraínement et/ou de freinage.
  25. Enrouleuse selon l'une des revendications 13 à 24, caractérisée en ce qu'un dispositif de levage (43) est associé au dispositif de transport secondaire (5 ; 7) et que le dispositif de levage (43) peut être commandé / régulé en fonction du diamètre croissant du rouleau enroulé, de préférence indépendamment de la force rectiligne qui agit dans la fente d'enroulement entre le cylindre presseur (19) et le rouleau enroulé.
  26. Enrouleuse selon l'une des revendications 13 à 25, caractérisée en ce que le dispositif de pressage (25) associé au cylindre presseur peut être actionné pour commander / réguler la force-rectiligne indépendamment du dispositif de levage (43) associé au dispositif de transport secondaire (5 ; 7).
  27. Enrouleuse selon l'une des revendications 13 à 26, caractérisée en ce que le dispositif de pressage (25) peut être commandé à l'aide d'un dispositif de régulation (65) de manière à ce que la force rectiligne dans la fente d'enroulement entre le cylindre presseur (19) et le rouleau enroulé corresponde, au moins pour l'essentiel, à une valeur de consigne.
  28. Enrouleuse selon l'une des revendications 13 à 27, caractérisée en ce que la position de la fente d'enroulement formée entre le cylindre presseur (19) et le rouleau enroulé guidé par le dispositif de transport secondaire (5 ; 7) est constante.
  29. Enrouleuse selon l'une des revendications 13 à 27, caractérisée en ce que la position de la fente d'enroulement formée entre le cylindre presseur (19) et le rouleau enroulé guidé par le dispositif de transport secondaire (5 ; 7) se décale pendant le processus d'enroulement, de préférence entre 50 mm et 200 mm, à mesure que le diamètre du rouleau enroulé augmente.
  30. Enrouleuse selon l'une des revendications 13 à 29, caractérisée en ce que le dispositif de pressage (25) est réalisé sous la forme d'un ensemble piston et cylindre, de préférence hydraulique.
  31. Enrouleuse selon la revendication 30, caractérisée en ce que la course maximale du piston (29) est inférieure à la moitié de l'épaisseur de la couche de matériau d'un rouleau enroulé terminé.
  32. Enrouleuse selon l'une des revendications 13 à 31, caractérisée en ce que le cylindre presseur (19) est réalisé à la manière d'un rouleau de réglage du fléchissement dont la chemise de rouleau est soutenue sur un joug fixe au moyen d'une rangée d'éléments supports.
  33. Enrouleuse selon la revendication 32, caractérisée en ce que les éléments supports peuvent être commandés individuellement.
  34. Enrouleuse selon la revendication 32 ou 33, caractérisée en ce que les éléments supports agissent en direction de la fente d'enroulement.
  35. Enrouleuse selon l'une des revendications précédentes, caractérisée en ce que le joug peut être commandé de telle manière que le sens d'action des éléments supports suit le mouvement de déplacement de la fente d'enroulement (de la figure 3 à la figure 4).
  36. Enrouleuse selon l'une des revendications 13 à 35, caractérisée en ce que le dispositif de transport primaire (79) comprend des leviers pivotants primaires (81) sur lesquels le tambour (35 ; 49) est maintenu de manière à pouvoir tourner et qui peuvent pivoter autour d'un axe (83) parallèle à l'axe longitudinal du tambour.
  37. Enrouleuse selon la revendication 36, caractérisée en ce que l'axe (83) des leviers pivotants primaires (81) est fixe à l'intérieur de l'enrouleuse (21).
  38. Enrouleuse selon l'une des revendications 13 à 37, caractérisée en ce que le dispositif de transport primaire (79) comprend un dispositif de maintien qui peut se déplacer sur des troisièmes rails.
  39. Enrouleuse selon la revendication 38, caractérisée en ce que les troisièmes rails sont disposés verticalement ou sont inclinés selon un angle z par rapport à une verticale imaginaire.
  40. Enrouleuse selon l'une des revendications 13 à 39, caractérisée par au moins un élément presseur (rouleau de compression (51)) qui peut être pressé sur le pourtour du rouleau enroulé.
  41. Enrouleuse selon l'une des revendications précédentes 13 à 40, caractérisée en ce que l'angle α (figure 3) est de préférence réglable avant un changement de tambour.
EP98928270A 1997-05-16 1998-05-15 Procede de bobinage continu d'une bande de materiau et bobineuse correspondante Expired - Lifetime EP0912435B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP02010520A EP1238933B1 (fr) 1997-05-16 1998-05-15 Méthode et dispositif pour continuellement enrouler une bande de matériau

Applications Claiming Priority (11)

Application Number Priority Date Filing Date Title
DE19720495 1997-05-16
DE19720495 1997-05-16
DE19725878 1997-06-18
DE19725878 1997-06-18
DE19735590A DE19735590A1 (de) 1997-05-16 1997-08-15 Wickelmaschine zum Aufwickeln einer Materialbahn
DE19735590 1997-08-15
DE19737709 1997-08-29
DE1997137709 DE19737709A1 (de) 1997-08-29 1997-08-29 Wickelmaschine zum kontinuierlichen Aufwickeln einer Materialbahn
DE19748995A DE19748995A1 (de) 1997-11-06 1997-11-06 Verfahren und Wickelmaschine zum kontinuierlichen Aufwickeln einer Materialbahn
DE19748995 1997-11-06
PCT/EP1998/002867 WO1998052858A1 (fr) 1997-05-16 1998-05-15 Procede de bobinage continu d'une bande de materiau et bobineuse correspondante

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EP02010520A Division EP1238933B1 (fr) 1997-05-16 1998-05-15 Méthode et dispositif pour continuellement enrouler une bande de matériau

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EP0912435A1 EP0912435A1 (fr) 1999-05-06
EP0912435B1 true EP0912435B1 (fr) 2003-03-12

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US (1) US6129305A (fr)
EP (1) EP0912435B1 (fr)
JP (1) JP4391600B2 (fr)
AT (2) ATE320996T1 (fr)
BR (1) BR9804919A (fr)
DE (1) DE59813447D1 (fr)
WO (1) WO1998052858A1 (fr)

Cited By (2)

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CN108820976A (zh) * 2018-06-30 2018-11-16 浙江唐艺织物整理有限公司 一种涂层布加工用自动收卷机
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006128972A1 (fr) * 2005-06-02 2006-12-07 Metso Paper, Inc. Procede et dispositif mis en oeuvre dans une enrouleuse de bande de papier
DE102015220611A1 (de) 2015-10-22 2016-09-29 Voith Patent Gmbh Wickelverfahren

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DE59813447D1 (de) 2006-05-11
JP2000514770A (ja) 2000-11-07
JP4391600B2 (ja) 2009-12-24
US6129305A (en) 2000-10-10
EP0912435A1 (fr) 1999-05-06
ATE234254T1 (de) 2003-03-15
ATE320996T1 (de) 2006-04-15
BR9804919A (pt) 1999-08-31
WO1998052858A1 (fr) 1998-11-26

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