EP1790600A2 - Enrouleuse - Google Patents

Enrouleuse Download PDF

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Publication number
EP1790600A2
EP1790600A2 EP06123332A EP06123332A EP1790600A2 EP 1790600 A2 EP1790600 A2 EP 1790600A2 EP 06123332 A EP06123332 A EP 06123332A EP 06123332 A EP06123332 A EP 06123332A EP 1790600 A2 EP1790600 A2 EP 1790600A2
Authority
EP
European Patent Office
Prior art keywords
roll
winding device
roll winding
winding
roller
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.)
Granted
Application number
EP06123332A
Other languages
German (de)
English (en)
Other versions
EP1790600B1 (fr
EP1790600A3 (fr
Inventor
Rolf Van Haag
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 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 DE200510056748 external-priority patent/DE102005056748A1/de
Priority claimed from DE200610023831 external-priority patent/DE102006023831A1/de
Application filed by Voith Patent GmbH filed Critical Voith Patent GmbH
Publication of EP1790600A2 publication Critical patent/EP1790600A2/fr
Publication of EP1790600A3 publication Critical patent/EP1790600A3/fr
Application granted granted Critical
Publication of EP1790600B1 publication Critical patent/EP1790600B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B65H18/00—Winding webs
    • B65H18/08—Web-winding mechanisms
    • B65H18/14—Mechanisms in which power is applied to web roll, e.g. to effect continuous advancement of web
    • B65H18/20—Mechanisms in which power is applied to web roll, e.g. to effect continuous advancement of web the web roll being supported on two parallel rollers at least one of which is driven
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2301/00—Handling processes for sheets or webs
    • B65H2301/40—Type of handling process
    • B65H2301/41—Winding, unwinding
    • B65H2301/414—Winding
    • B65H2301/4148—Winding slitting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2601/00—Problem to be solved or advantage achieved
    • B65H2601/50—Diminishing, minimizing or reducing
    • B65H2601/52—Diminishing, minimizing or reducing entities relating to handling machine
    • B65H2601/524—Vibration
    • B65H2601/5242—Vibration by using mass damper

Definitions

  • the invention relates to a roll winding device having two support rollers, which form a winding bed, in which a winding roll is arranged during winding.
  • At least one of the two support rollers is driven, thereby displacing the winding roll in rotation.
  • the winding roll pulls a material web on itself. Their diameter increases.
  • Paper webs are produced in a wide range of currently over 10 m and virtually endless. In order to be manageable for a later user, for example a printing company, they must cut to a smaller width in the range of 0.2 to 4.8 m and then into winding rolls with a diameter in the range of 0.5 to 2.5 m be wound up. The winding takes place at speeds of the order of 2,000 to 3,000 m / min. The winding of a roll takes on the order of about 5 to 15 minutes, which, of course, depending on the diameter exceeding or undershooting these times are possible.
  • the invention has for its object to reduce problems when winding webs with a high coefficient of adhesion.
  • This regenerative effect leads to the coincidence of one or the other harmonics of the winding speed with certain natural frequencies of the winding system of support rollers and winding roll to a self-energizing process.
  • this vibration absorber can not prevent the occurrence of vibrations. But it has a positive effect on the Aufschwingvorgang by depriving the vibrations energy. So one will still be able to observe a certain tendency to oscillate. However, the effect of this vibration is then much lower.
  • the vibration absorber has a natural frequency, the is tuned to a frequency in a predetermined range below the second highest contact frequency at the end of the winding process between the support roller and the winding roll.
  • the predetermined range is on the order of about 5 to 10% of the natural frequency.
  • the vibration absorber Since the circumference of the winding roll increases with increasing diameter, however, it is practically impossible to adhere to this condition throughout. However, in most cases it is sufficient to dimension the vibration absorber in such a way that it satisfies this condition for a certain diameter, which is for example at a diameter of 80 to 100% of the final diameter. For the remaining diameter ranges of the vibration damper is still sufficiently able to dampen the resulting vibrations. Since the absorber frequency is below the second highest contact frequency, the absorber does not optimally attenuate, based on a single frequency. But it covers the expected frequency response with increasing diameter of the winding roll better than a Tilgerfrequenz, which is above the second highest contact frequency.
  • the vibration damper has a natural frequency which is above the first free natural bending frequency of the support roller.
  • the "free bending natural frequency” is by definition the natural frequency of the support roller without the influence of an overlying winding mass, such as the winding roll.
  • the vibration absorber may preferably have a natural frequency which is more than 10%, preferably more than 15%, above the first free one Biegeeigenfrequenz the support roller is.
  • the inlet-side support roller on the vibration damper are the most oscillations registered.
  • An attenuation of the first support roller thus leads in many cases already to the fact that the reel winder is attenuated overall to a sufficient extent.
  • both support rollers may each have a vibration absorber. This results in improved vibration damping.
  • Each support roller can then be tuned to its own contact frequency with the winding roll. This is particularly advantageous if the support rollers have different diameters or their contact nip with the winding roller at different heights, based on the direction of gravity, are arranged.
  • the vibration damper is designed as a passive vibration absorber with a damping mass. In this case it is not necessary to supply auxiliary energy from the outside.
  • the vibration damper removes energy from the oscillatory system simply by moving the absorber mass against a damper.
  • the absorber mass is arranged in the support roller.
  • the roller has for this purpose a roller tube or a roll shell, so it is hollow. In this cavity you can accommodate the absorber mass without much additional effort. This has two advantages. On the one hand space is saved outside the carrier roll, because you used an already existing, but so far practically unused space within the roller. On the other hand, the absorber mass can act directly on the support roller, so must not unfold their effect on the detour via any bearings or the like.
  • the absorber mass acts on the inside of a roll shell.
  • the absorber mass attacks the roll shell from the inside. This is a very immediate form of vibration damping. If the Roll winding device vibrates, then these vibrations arise primarily by the interaction of winding roll and roll shell. If you dampen the vibrations directly on the roll shell, then you prevent with high reliability that the vibrations continue to spread.
  • the absorber mass corresponds to at least 5% of the mass of the support roller.
  • the larger the absorber mass the wider the frequency range in which the vibration absorber is effective. Accordingly, one must not exactly hit the frequency to be damped. Conversely, this has the positive effect of basically covering an entire frequency band with the vibration damper, specifically the frequency band that forms as the diameter of the winding roll increases from about 60 or 70% to 100% of the diameter. As already stated above, this frequency band is not too wide anyway.
  • the absorber mass corresponds to at most 10% of the mass of the support roller.
  • the damping effect is the better, the larger the absorber mass.
  • other boundary conditions have to be taken into account in the operation of a reel winder, for example the drive power and the braking power.
  • the vibration absorber is divided into several individual modules, which are distributed over the axial length of the support roller. This then offers the possibility that the vibration absorber or its individual modules can respond better to asymmetries that can occur in practice. Also, the damping over the axial length of the carrier roll is more uniform than when the vibration absorber is concentrated at one position.
  • the individual modules have different natural frequencies. If you divide the vibration damper on different individual modules, it is possible to tune these individual modules to a slightly different frequency from the edge to the center of the carrier roll and of course from the center back to the edge. This can be particularly useful for very wide machines in which the contact own frequencies due to drive elements, such as the coupled mass of a propeller shaft, not exactly the same form on both sides of the machine.
  • the vibration damper is adjustable with respect to its natural frequency. This has several advantages. On the one hand, you can then fine-tune, for example, during commissioning in order to achieve optimum vibration damping. On the other hand, you can then use the same vibration absorber for different applications, which simplifies spare parts inventory and maintenance.
  • the vibration damper has a Tillgungsmassenlagerung having a spring with a non-linear characteristic, wherein the bias of the spring is variable.
  • At least one power-operated adjusting element is provided for changing the bias voltage.
  • an assistant you can use pneumatic, hydraulic or electrical energy. In this case, the adjustment is possible, so to speak remotely controlled. This is relatively comfortable.
  • the vibration damper on at least one piezoelectric element, which is connected to an electrical resonant circuit.
  • an electrical resonant circuit In many cases it is there favorable to use several distributed over the circumference of the roller piezo elements, which are each connected to a separate resonant circuit. You can also connect several piezo elements with a common resonant circuit.
  • the piezoelectric element generates an electric voltage in a roll deformation that occurs at a vibration. This electrical voltage is passed on to the electrical resonant circuit. If the electrical resonant circuit is operated at its resonant frequency, which is tuned to the problem frequency of the mechanical structure, then the electrical voltage acts on the piezo element.
  • the piezoelectric element is excited approximately in the opposite phase to the vibration. Due to the feedback of the oscillating electrical currents, a damping expansion component is introduced into the carrier roll via the expansion of the piezoelements, which causes the same damping effects as purely mechanical absorber modules.
  • the piezoelectric element is designed as a film module.
  • Piezoceramic film modules are commercially available at a reasonable cost. They are easy to handle and connect.
  • the piezo elements are fastened with their direction of action parallel to the direction of greatest elongation of the support roller from the inside to the roll shell.
  • the piezoelectric elements thus act directly on the roll shell.
  • Each piezo element is then operated both as a generator and as a motor, depending on the position where it is currently located.
  • the vibration damper may be formed in a preferred embodiment as an active system having a plurality of electromechanical actuators, in particular piezoelectric elements, which are connected to an electrical control circuit that supplies electrical energy from the outside.
  • the electrical control circuit also has a sensor which determines the deformations caused by the vibration of the support roller.
  • this sensor can also be formed by an electromechanical actuator itself.
  • An active System has the advantage that one can react very flexibly to changing problem frequencies.
  • the vibration damper has at least one roller insertion, which is supported by springs on the inside of the roll shell, wherein a gap between the roll insert and roll shell is filled with a viscous liquid. With the help of the viscous liquid, the damping properties can be adjusted.
  • the springs determine the resonance frequency.
  • the vibration damper has at least one roller insertion, which is supported on the roll shell via rubber spring packages.
  • a rubber spring unites a spring function and a damping function in one component.
  • the vibration damper has at least one roller insertion, which is supported by a spring assembly on the roll shell, wherein a hydraulic piston-cylinder arrangement is arranged in series with or parallel to the spring assembly.
  • the spring is again responsible for the natural frequency, while the piston-cylinder arrangement causes the damping. It is sufficient if the piston-cylinder arrangement displaces a liquid from one chamber to another and in the communication path between the two chambers, a throttle or a similar constriction is provided to withdraw energy from the vibration.
  • At least one roller-shaped insert body is arranged in the roll shell, which is shrunk into an intermediate layer of viscoelastic material.
  • This may be, for example, a rubber or plastic coating. This results, so to speak, one annular support of the roll body in the roll shell, which leads to an all-round damping.
  • a roll winding device 1 has two support rollers 2, 3, which form a winding bed 4, in which a winding roller 5 rests during winding.
  • a material web in the present case, a paper web 6, wound up.
  • the paper web 6, which may have a width of up to 10 m or even beyond in the initial state, passes through a longitudinal cutting device 7 before hitting the feed-side support roll 2, with the aid of which it is cut into its part webs having a width in the range of 0.2 to 4.8 m.
  • the paper web 6 is first attached to a winding tube 8, for example by gluing.
  • the end of the paper web 6 is attached to the circumference of the winding roll 5, for example also by gluing.
  • a cross cutting device 9 is shown only schematically.
  • the loading roller 10 which presses the winding roller 5 into the winding bed 4.
  • the loading roller 10 can also generate a sufficient contact pressure at the beginning of a winding process to increase the winding hardness in the radial interior of the winding roll. Nevertheless, unwanted vibrations occur.
  • This regenerative effect leads to the coincidence of some harmonics of the winding speed with certain natural frequencies of the winding system (support rollers 2, 3 and winding roller 5) to a self-energizing process.
  • These are usually the natural frequencies at which the winding roll itself undergoes a large dynamic deformation, which is basically equated with a spring travel. This is the case, in particular, in the case of the so-called contact own frequencies, in which the support rollers 2, 3 and the winding roller 5 oscillate in an antiphase movement relative to one another.
  • Fig. 2 shows a highly simplified representation of the roll winding device 1, in which all moving masses, so the two support rollers 2, 3, the winding roll 5 and the loading roller 10, each one degree of freedom of movement in the X direction (horizontal direction) and have one in the Y direction (vertical direction).
  • the two support rollers 2, 3, the winding roller 5 and the loading roller 10 are illustrated as mass points connected via springs and dampers (dampers are not shown in FIG. 2 for the sake of simplicity).
  • the individual spring stiffnesses are adjusted so that each mass individually reflects the natural frequency of the associated component in the uncoupled state as accurately as possible.
  • the two support rollers 2, 3 each have a vibration damper 14, 15.
  • Each vibration absorber has a damping mass 16, 17, which is attached via a spring-damper arrangement 18, 19 on the inner wall 20, 21 of the roll shell 22, 23 of the two support rollers 2, 3.
  • a spring-damper arrangement 18, 19 on the inner wall 20, 21 of the roll shell 22, 23 of the two support rollers 2, 3.
  • the spring-damper assembly there are basically two options. For example, one can arrange a spring 24 parallel to a damper 25. It is also possible to arrange a spring 26 in series with a damper 27.
  • this second highest contact frequency refers to a predetermined winding diameter, which is for example in the range of 80 to 100% of the final diameter of the winding roll 5. This results in certain inaccuracies with smaller diameters. However, this is not critical, because the vibration damper 14, 15 too in adjacent frequencies still develop a sufficient damping effect.
  • the vibration damper has a natural frequency which is above the first free bending natural frequency of the support roller.
  • the "free bending natural frequency” is by definition the natural frequency of the support roller without the influence of an overlying winding mass, such as the winding roll.
  • the vibration absorber may preferably have a natural frequency which is more than 10%, preferably more than 15% above the first free bending natural frequency of the carrier roll.
  • the vibration absorber can thus have a natural frequency, which is preferably between the second highest and highest contact natural frequency.
  • absorber masses 16, 17 have a significant share of the mass of the support rollers 2, 3 and are strongly attenuated.
  • 5 to 10% of the carrier roll mass is sufficient as absorber mass 16, 17 in order to greatly reduce the formation of waviness on the winding roll 2.
  • the support roller 2 has a roll shell 22, in which a damping mass 16 is arranged as a roll insertion.
  • the absorber mass 16 is connected via springs 24 with the inside of the roll shell 22.
  • a viscous oil is arranged, the viscosity of which influences the damping properties. By choosing a suitable viscosity, therefore, the damping properties can also be changed.
  • the springs 24 may be formed, for example, as disc springs.
  • Fig. 4 shows a section of the support roller 3, wherein it can be seen that the Tilgermasse 17 is connected via the spring-damper assembly 19 with the roll shell 23.
  • the spring-damper assembly 19 has a spring 26 which is formed as a spring assembly of disc springs.
  • the spring is in series with a damper 27 having a piston 29 which is reciprocable in a cylinder 30.
  • the piston 29 has a throttle bore 31 through which liquid must flow during the movement of the piston 29.
  • an annular gap 32 is provided, which basically performs the same task as the throttle bore 31.
  • a modified embodiment of the support roller 2 in which the absorber mass 16 is connected to the roll shell 22 via a viscoelastic intermediate layer 33, for example of a rubber material or a plastic.
  • the intermediate layer 33 then fulfills both the task of the spring 24 and the task of the damper 25.
  • Fig. 6 shows a modified embodiment of the support roller 2 is shown, in which the absorber mass is connected via a plurality of rubber spring packages 34 with the roll shell 22.
  • the individual rubber spring packages 34 are spaced apart both in the axial direction and in the circumferential direction, as shown in FIGS. 6a and 6b.
  • Such an embodiment also has the advantage that it is possible to divide the vibration absorber into a plurality of individual modules 14a, 14b,..., 14n, which in the present embodiment still have the absorber mass 16 in common. However, one can make the natural frequencies of the individual absorber modules 14a-14n in the axial direction of the support roller 2 different. This then offers the possibility that the vibration absorber can respond to asymmetries that may occur in practice. For example, you can take into account in very wide machines, that the Kunststoffigenfrequenzen due to drive elements, such as the coupled mass of a propeller shaft, not exactly the same on both sides of the reel winder 1 form.
  • a support roller 2 is provided in a schematic longitudinal section, in which a plurality of absorber masses 16a-16c are shrunk into the roll shell 22, including an intermediate layer 33a-33c, between the intermediate layer 33a-33c and the roll shell 22 piezoceramic film modules 35a -35c are arranged. These piezoceramic film modules do not extend over the entire circumference. On the contrary, four or more such film modules 35a-35c can be provided distributed over the inner periphery of the roll shell 22. In connection with a non-illustrated, but within the support roller 2 arranged passive electrical network can be realized with the piezoceramic foil modules, a passive electro-mechanically acting vibration damper.
  • the piezoceramic film modules 35a-35c are glued in their direction of action to the inner periphery of the roll shell 22, that their effective direction corresponds to the direction of greatest elongation of the roll.
  • the axial rolling expansions occurring during a vibration generate an electrical voltage in the foil modules 35a-35c.
  • the electrical oscillation circuits connected to the film modules 35a-35c are tuned in their resonance frequency to the problem frequency of the mechanical structure. If the mechanical structure oscillates in this frequency, then the electromechanical coupling also operates the electrical network in its resonance. Due to the feedback of the oscillating electrical currents, a damping expansion component is introduced into the roll shell 22 via the expansion of the piezoceramic foil modules 35a-35c, which causes the same damping effects as the purely mechanically acting absorber modules.
  • piezoceramic film modules 35a-35c by using piezoceramic film modules 35a-35c, one can realize an active damping system.
  • a control loop is necessary with which the film modules 35a-35c are controlled in terms of voltage.
  • the detected oscillatory motion according to amplitude and phase angle of the respective support roller 2, 3 are detected.
  • an active system has the advantage of being able to react very flexibly to changing problem frequencies. However, it is associated with an increased cost because you have to perform, for example, in the rotating support roller electrical energy.
  • the vibration absorbers 14, 15 and the absorber modules 14a-14n are adjustable in a limited frequency range. This can be achieved for example by changing a bias of a non-linear acting spring absorber mass storage.

Landscapes

  • Vibration Prevention Devices (AREA)
  • Winding Of Webs (AREA)
  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)
  • Replacement Of Web Rolls (AREA)
EP06123332A 2005-11-29 2006-11-02 Enrouleuse Expired - Fee Related EP1790600B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200510056748 DE102005056748A1 (de) 2005-11-29 2005-11-29 Rollenwickeleinrichtung
DE200610023831 DE102006023831A1 (de) 2006-05-20 2006-05-20 Rollenwickeleinrichtung

Publications (3)

Publication Number Publication Date
EP1790600A2 true EP1790600A2 (fr) 2007-05-30
EP1790600A3 EP1790600A3 (fr) 2008-09-17
EP1790600B1 EP1790600B1 (fr) 2012-03-07

Family

ID=37745221

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06123332A Expired - Fee Related EP1790600B1 (fr) 2005-11-29 2006-11-02 Enrouleuse

Country Status (2)

Country Link
EP (1) EP1790600B1 (fr)
AT (1) ATE548308T1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010018305A1 (fr) * 2008-08-14 2010-02-18 Metso Paper, Inc. Procédé d’utilisation d’une coupeuse-bobineuse
EP2341021A3 (fr) * 2009-12-29 2012-01-25 Voith Patent GmbH Dispositif d'enroulement de rouleaux
EP2341020A3 (fr) * 2009-12-29 2012-01-25 Voith Patent GmbH Procédé d'enroulement d'une bande de matériau

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004062890A1 (de) 2004-01-06 2005-10-13 Eras Gmbh Rollenwickeleinrichtung

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7305837U (de) * 1973-02-16 1974-10-10 Voith J Gmbh Trageinrichtung fuer aus bahnen aufgewickelte rollen
DE4318035C2 (de) * 1993-05-29 1997-02-20 Voith Gmbh J M Walze mit Schwingungsdämpfer
DE10125192A1 (de) * 2001-05-23 2002-11-28 Voith Paper Patent Gmbh Verfahren und Vorrichtung zur aktiven Schwingungsdämpfung bei Wickelmaschinen

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004062890A1 (de) 2004-01-06 2005-10-13 Eras Gmbh Rollenwickeleinrichtung

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010018305A1 (fr) * 2008-08-14 2010-02-18 Metso Paper, Inc. Procédé d’utilisation d’une coupeuse-bobineuse
EP2341021A3 (fr) * 2009-12-29 2012-01-25 Voith Patent GmbH Dispositif d'enroulement de rouleaux
EP2341020A3 (fr) * 2009-12-29 2012-01-25 Voith Patent GmbH Procédé d'enroulement d'une bande de matériau

Also Published As

Publication number Publication date
EP1790600B1 (fr) 2012-03-07
ATE548308T1 (de) 2012-03-15
EP1790600A3 (fr) 2008-09-17

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