EP2502861B1 - Dispositif et procédé d'enroulement d'une bande de matériau - Google Patents

Dispositif et procédé d'enroulement d'une bande de matériau Download PDF

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Publication number
EP2502861B1
EP2502861B1 EP12159574.8A EP12159574A EP2502861B1 EP 2502861 B1 EP2502861 B1 EP 2502861B1 EP 12159574 A EP12159574 A EP 12159574A EP 2502861 B1 EP2502861 B1 EP 2502861B1
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EP
European Patent Office
Prior art keywords
bearing
roll
winding
stiffness
frequency
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.)
Active
Application number
EP12159574.8A
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German (de)
English (en)
Other versions
EP2502861A3 (fr
EP2502861A2 (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
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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
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Publication of EP2502861A2 publication Critical patent/EP2502861A2/fr
Publication of EP2502861A3 publication Critical patent/EP2502861A3/fr
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Publication of EP2502861B1 publication Critical patent/EP2502861B1/fr
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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
    • B65H2402/00—Constructional details of the handling apparatus
    • B65H2402/50—Machine elements
    • B65H2402/52—Bearings, e.g. magnetic or hydrostatic bearings
    • 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
    • B65H2515/50—Vibrations; Oscillations
    • 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
    • B65H2515/81—Rigidity; Stiffness; Elasticity
    • 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

Definitions

  • the invention relates to a device for winding a material web to a winding roll with at least one roller against which the winding roll during winding and which rotates during winding with a maximum rotational frequency, wherein the roller is mounted in a bearing device with a bearing at each end of the roll and the Roller including their storage device having a first natural frequency.
  • the invention relates to a method for winding a material web to a winding roll, wherein the winding roll rests against at least one roller which rotates during winding with a maximum rotational frequency.
  • the invention will be described below with reference to a paper web as an example of a material web. But it is also applicable to other webs where similar problems occur.
  • Devices for winding of paper webs reach high working widths of more than 10 m.
  • the winding rolls produced on them can achieve a final diameter of 1.6 m and more in the case of longitudinally divided webs. In the case of undivided webs, the final diameters may be 3.5 m and more.
  • vibration-critical papers Especially when winding up papers with a high coefficient of friction, there are strong unwanted oscillatory phenomena. These papers are generally referred to as vibration-critical papers. These are present when the static friction coefficient of the paper layers is greater than 0.5, in particular reaches the value 0.7 and more.
  • document EP 1 748 011 shows a device for winding a material web wherein the speed of the web roll is reduced when a vibration exceeds a predetermined strength.
  • the invention has for its object to be able to wind even vibration-critical material webs with as few problems.
  • This object is achieved in a device of the type mentioned above in that the first natural frequency is smaller than the maximum rotational frequency of the roller.
  • the device is in any case when the maximum winding speed is reached, driven supercritical, ie, the rotational frequency of the roller is greater than the natural frequencies of the system of roller and bearing device.
  • the rotational frequency of the roller is greater than the natural frequencies of the system of roller and bearing device.
  • This makes it possible to produce a phase shift of approximately 180 ° between the path excitation of the (non-round) winding roll and the system response of the oscillating roll with the winding roll resting thereon. Even if this phase shift is not completely achieved, there is nevertheless a very positive effect in that the vibrations are damped or are not excited as much as before.
  • the winding roller rotates upon reaching its maximum diameter with a reduced rotational frequency and the first natural frequency is smaller than the reduced rotational frequency of the winding roll.
  • the web is wound many times at a constant speed. This causes the speed of the winding roll decreases with increasing diameter of the winding roll.
  • the natural frequency of the system Roller and bearing device is then chosen even smaller, namely smaller than the reduced rotational frequency of the winding roll at its maximum diameter.
  • the maximum diameter is usually predetermined by the winding device. The same also applies to the desired feed rate of the material web and thus to the maximum rotational frequency of the roller which it achieves when the material web has been accelerated to the desired feed rate at the beginning of a winding process, and usually remains substantially constant during the main winding phase.
  • the bearing device has a stiffness that varies with the exciter frequency.
  • one has a static stiffness (when the exciter frequency of the roller is zero) which differs from a dynamic stiffness which is given when the roller is energized at a higher excitation frequency.
  • the rigidity here is the sum stiffness of both bearings of a roller.
  • the bearing device has a static stiffness which is greater than the rigidity of the roller.
  • the bearing device is thus for low-frequency (f ⁇ 0, or f ⁇ 0.1 Hz) loads, that is relatively stiff with respect to long-term loads, so that even with the occurrence of larger forces, such as the weight of a finished winding roll, no change in location of the roller can be observed.
  • the static stiffness is at least 2 times the rigidity of the roll.
  • the static stiffness can therefore be chosen relatively large.
  • the bearing device has a dynamic rigidity which is smaller than the rigidity of the roller. With increasing excitation frequency, the rigidity of the bearing device is thus reset, so that the bearing device opposes the vibration movement of the roller less resistance. In the range of the vibration amplitude, the bearing device can thus yield within certain limits.
  • the roller is always in the winding process by several influences, so superimposed excited. The arousal changes continuously, as it mainly emanates from the winding roll. The actual out of the current rotational frequency of the roller itself excitation is far better predictable in many areas and therefore plays a sideline role in achieving critical winding conditions.
  • the dynamic stiffness is at most 50% of the rigidity of the roller. Thus, there is a significant difference between the dynamic stiffness and the static stiffness of the bearing device.
  • the bearing has a hydrostatic support with at least a first bearing pocket, which is supplied with hydraulic fluid.
  • the supply of the storage bag can be done in two ways: with a constant volume flow or with a constant admission pressure via a throttle, whereby the admission pressure is substantially larger than the pressure in the storage bag. Both cases cause a static Position control.
  • a static Position control Depending on the load, in any case, on average, essentially always the same oil gap is established at the boundary of the bearing pocket. However, short-term or fast movements, such as those of a swinging movement, can be recorded.
  • An example electronic control of the roller position is not required because the gap changes are very small as a function of the static load.
  • the bearing pocket is connected via a throttle with a pressure accumulator in connection.
  • the accumulator takes on a vibration movement of the roller for a short time on the liquid that can not flow through the gap at the edge of the bearing pocket, and returns it in the opposite movement of the roller again.
  • the liquid must flow through the throttle, which causes a damping. With the help of the throttle so energy is taken out of the oscillating system.
  • the combination of hydrostatic support and pressure accumulator with throttle thus causes a clear separation of the dynamic and the static properties of the bearing, so that can be achieved in a simple manner different stiffnesses for the static state and for the dynamic state.
  • the throttle has an adjustable throttle resistance. This allows you to adjust the damping. It is easy to influence the dynamic stiffness of the bearing so that the dynamic stiffness can be adjusted to give as few vibrations as possible.
  • the throttle is connected to an externally operable actuator. Accordingly, one can change the dynamic stiffness even when the throttle is installed inside the bearing. This makes it possible to effect adaptive damping, i. You can adjust the dynamic stiffness and damping depending on the situation.
  • the hydrostatic support is connected in series with a spring arrangement.
  • the spring arrangement can produce, for example, a bias in the direction of the bearing pocket. It can also be used to make the bearing harder overall.
  • At least one further hydrostatic support is provided with at least one second bearing pocket, which is fed with a constant volume flow of hydraulic fluid, wherein the second bearing pocket has a different effective direction than the first bearing pocket.
  • the second bearing pocket has a different effective direction than the first bearing pocket.
  • At least one storage pocket is divided into two sub-pockets, each of which is fed via a supply throttle.
  • the object is achieved in a method of the type mentioned above by driving the roller supercritical.
  • the winding device when the maximum winding speed is reached, the winding device is driven supercritical, i. the rotational frequency of the roller is greater than the natural frequency of the system of roller and its bearing means, i. the bearings at the two ends of the roller.
  • the rotational frequency of the roller is greater than the natural frequency of the system of roller and its bearing means, i. the bearings at the two ends of the roller.
  • Fig. 1 shows very schematically a winding device 1 in the form of a Doppeltragwalzenwicklers.
  • the winding device 1 has two support rollers 2, 3, which form between them a winding bed 4, in which a winding roll 5 shown schematically is, on which a material web, not shown, is wound up.
  • the formation of such a Doppeltragwalzenwicklers itself is known.
  • each support roller 2, 3 is mounted in a machine frame 6.
  • each support roller 2, 3 has a bearing device with a bearing 7, 8 at each end of the support rollers 2, 3. Only one camp 7, 8 is in Fig. 1 each visible.
  • Such a winding device can be operated at a maximum feed rate.
  • This feed rate is, for example, 2,500 m / min or 3,000 m / min.
  • the winding device is designed.
  • the speed of the winding roller 5 is at the beginning of a winding process largest, because the winding roller 5 here has its smallest diameter. At the end of the winding process, when the winding roll 5 its maximum Has reached diameter, the winding roller 5 rotates with a reduced rotational frequency.
  • Each support roller 2, 3 has (including its bearing means with the bearings 7 and 8) to a first natural frequency.
  • the first natural frequency is the lowest natural frequency. In simple terms, this is a natural bending frequency.
  • the first natural frequency of the carrier roll 2, 3 with bearings 7, 8 is now selected so that it is smaller than the maximum rotational frequency of the carrier roll 2, 3.
  • the device 1 can be operated supercritically, with the result that it is possible to generate a phase shift of approximately 180 ° between the excitation of the winding roller 5 and the system response of the oscillation system from a carrier roll with the overlying deformable winding roller 5.
  • the support rollers 2, 3 must be dynamically tuned very soft.
  • the system must be relatively hard statically, for example, to accommodate the mass of the finished winding roll 5 can.
  • Fig. 2 shows the bearing 7 enlarged and in a highly schematic form.
  • the bearing 7 has a bearing housing 9, in which a roll neck 10 of the support roller 2 is rotatably mounted.
  • the roll neck 10 may well be stored in the bearing housing 9 with rolling bearings or the like.
  • the bearing housing 9 is arranged in a machine housing 11, which is connected to the machine frame 6 or forms part of the machine frame 6.
  • the machine housing 11 has a first bearing pocket 12 of a hydrostatic support in the direction of gravity below the bearing housing 9.
  • the first bearing pocket 12 is connected to a feed channel 13 for hydraulic fluid.
  • the supply channel 13 is supplied via a supply device not shown with a constant current Vp to hydraulic fluid. The necessary pump and control device is known and therefore not shown.
  • the first bearing pocket 12 is surrounded by a ring-like oil web 14.
  • the oil bar 14 forms with the bearing housing 9 a gap 15 which is also formed circumferentially around the bearing pocket 12. The hydraulic fluid flowing in via the supply line 13 can thus escape only via the gap 15 and be discharged via an outlet 16.
  • the storage bag is fed 12 with a higher pressure and supplies the hydraulic fluid via a throttle (not shown). Also in this case, the described effect results.
  • the first storage pocket 12 is connected to a pressure accumulator 17 in connection via a throttle 18.
  • the pressure accumulator 17 is formed here as a gas pressure accumulator with a membrane 19 which separates a liquid portion 20 from a pressurized gas region 21.
  • the support roller 2 vibrates, and the bearing housing 9 is placed in corresponding vibrations. As a result, while the gap 15 is maintained on average with its height ho. However, the thickness of the gap 15 varies with the same frequency with which the support roller 7 oscillates.
  • the bearing 7 has a high rigidity against static loads and a relatively low rigidity against dynamic loads. Based on the rigidity of the support roller 2, the static stiffness of the bearing 7, for example, at least twice as large and the dynamic stiffness of the bearing 7 is, for example, at most half as large.
  • the throttle 18 may have a variable throttle resistance. This is schematically represented by an arrow 22. You can use an externally operable adjusting device for adjusting the throttle resistance, such as an electric motor or the like. Accordingly, it is possible to adjust the throttle resistance of the throttle 18 even when the throttle 18, as shown, installed in the bearing 7 and thus is not accessible.
  • the bearing housing 9 has a cross section in the form of a rectangle in the present embodiment.
  • the first bearing pocket 12 acts on one side of this rectangle.
  • two second bearing pockets 23, 24 are provided, which act on sides of the rectangle, which are arranged perpendicular to the side on which the first bearing pocket 12th acts.
  • the second bearing pockets 23, 24 are connected to feed channels 25, 26, which are supplied with a constant volume flow Vp.
  • the second bearing pockets 23, 24 are surrounded by oil lands 27, 28, which form an oil gap 29, 30 with the bearing housing 9, so that the bearing housing 9 with respect to the machine housing 11 in other directions has a hydrostatic support.
  • These second bearing pockets 23, 24 can then also be connected to a pressure accumulator, not shown.
  • Fig. 3 shows a modified embodiment of the bearing 7, in which the same and functionally identical elements are provided with the same reference numerals.
  • the second bearing pockets 23, 24 are omitted.
  • the bearing housing 9 is supported here relative to the machine housing 11 by spring assemblies 31, 32.
  • These spring assemblies 31, 32 are relatively soft parallel to the effective direction of the first bearing pocket 12, but perpendicular to it relatively hard. The effect of the spring assemblies 31, 32 is therefore added to the effect of the pressure of the hydraulic fluid in the first bearing pocket 12, so that the hydraulic support formed by means of the bearing pocket 12 and the spring assembly formed by the spring packs 31, 32 are connected in series.
  • the spring assemblies 31, 32 may be formed for example by bending spring packages. This combination can be useful if due to the boundary conditions, such as space, limited oil flow, storage volume, etc., the hydrostatic bearing in conjunction with the accumulator not the desired Combination of dynamic stiffness and damping behavior delivers.
  • Fig. 4 shows a further embodiment of the bearing 7, which is essentially the of Fig. 2 equivalent.
  • the same and corresponding components are therefore provided with the same reference numerals.
  • a compression spring 33 acts on the bearing housing 9.
  • the compression spring 33 is biased by a lid 34 connected to the machine housing 11, so that the bearing housing 9 is biased in the direction of the first bearing pocket 12.
  • Fig. 5 shows a further embodiment of the bearing 7, wherein the same and functionally identical elements are denoted by the same reference numerals as in the previous embodiments.
  • Right second bearing pocket 24 is here divided into two partial pockets 24a, 24b.
  • Each partial pocket 24a, 24b is supplied with hydraulic fluid from the supply line 26 via a supply throttle 35a, 35b.
  • the volume flow Vp fed into the supply line 26 is again constant.
  • the subdivision of the bearing pocket 24 into two or more partial pockets 24a, 24b has the advantage that it is possible to counteract a tilting of the bearing housing 9 relative to the machine housing 11.
  • Fig. 6 schematically shows different frequency characteristics that occur in the winding device.
  • a diameter d of the winding roll 5 is applied horizontally to the right and vertically upwards the respective frequencies f.
  • the representation is to be understood qualitatively.
  • the rotational frequency of the support rollers 2, 3 is designated by fr.
  • the rotational frequency of the winding roller 5 is denoted by fw. It can be seen that the rotational frequency of the support rollers 2, 3 remains constant after a run-up phase. The rotational frequency of the winding roll, however, decreases after reaching a maximum rotational frequency, because the material web is wound at a constant speed, while the diameter of the winding roll 5 grows.
  • a natural frequency of the support rollers 2, 3 is shown with f01A. It can be seen that the rotational frequency fr the support rollers 2, 3 is greater than the natural frequency f01A of the roller assembly, which is formed from a respective support roller 2, 3 and their bearings 7, 8 at the two ends.
  • a frequency f0R is drawn, as it has been used as the natural frequency of the support roller 2, 3.
  • the natural frequency was usually chosen to be 1.3 times the maximum rotational frequency fR.
  • the natural frequency f01A is selected to be 10 to 20% lower than the maximum rotational frequency fR, or even lower, when referring to the reduced rotational frequency.

Landscapes

  • Winding Of Webs (AREA)
  • Support Of The Bearing (AREA)

Claims (16)

  1. Ensemble d'enroulement d'une nappe de matière en un rouleau (5), l'ensemble présentant au moins un cylindre (2, 3) contre lequel le rouleau (5) repose lors de l'enroulement et qui tourne lors de l'enroulement avec une fréquence de rotation maximale, le cylindre (2, 3) étant monté dans un dispositif de palier qui présente un palier (7, 8) à chaque extrémité du cylindre et le cylindre (2, 3), conjointement avec son dispositif de palier, présentant une première fréquence propre,
    caractérisé en ce que
    la première fréquence propre est inférieure à la fréquence de rotation maximale du cylindre (2, 3).
  2. Ensemble selon la revendication 1, caractérisé en ce que le rouleau (5), une fois son diamètre maximal atteint, tourne avec une fréquence de rotation réduite et la première fréquence propre est inférieure à la fréquence de rotation réduite du rouleau (5).
  3. Ensemble selon la revendication 1 ou 2,
    caractérisé en ce que le dispositif de palier présente une rigidité qui varie avec la fréquence d'excitation.
  4. Ensemble selon la revendication 3, caractérisé en ce que le dispositif de palier présente une rigidité statique supérieure à la rigidité du cylindre (2, 3).
  5. Ensemble selon la revendication 4, caractérisé en ce que la rigidité statique vaut au moins le double de la rigidité du cylindre (2, 3).
  6. Ensemble selon les revendications 4 ou 5,
    caractérisé en ce que le dispositif de palier présente une rigidité dynamique inférieure à la rigidité du cylindre (2, 3).
  7. Ensemble selon la revendication 6, caractérisé en ce que la rigidité dynamique vaut au plus 50 % de la rigidité du cylindre (2, 3).
  8. Ensemble selon l'une des revendications 1 à 7,
    caractérisé en ce que le palier (7, 8) présente un soutien hydrostatique doté d'au moins une première poche (12) de palier alimentée en liquide hydraulique.
  9. Ensemble selon la revendication 8, caractérisé en ce que la poche (12) de palier est reliée par un étranglement (18) à une réserve (17) sous pression.
  10. Ensemble selon la revendication 9, caractérisé en ce que la réserve (17) sous pression est configurée comme réserve sous pression de gaz.
  11. Ensemble selon la revendication 9 ou 10,
    caractérisé en ce que l'étranglement (18) présente une résistance d'étranglement (22) ajustable.
  12. Ensemble selon la revendication 11, caractérisé en ce que l'étranglement (18) est relié à un dispositif de réglage apte à être actionné de l'extérieur.
  13. Ensemble selon l'une des revendications 8 à 12,
    caractérisé en ce que le soutien hydrostatique est raccordé en série à un système élastique (31, 32 ; 33).
  14. Ensemble selon l'une des revendications 8 à 13, caractérisé en ce qu'au moins un autre soutien hydrostatique doté d'au moins une deuxième poche (23, 24) de palier qui est alimentée par un écoulement volumique (Vp) constant de liquide hydraulique est prévu, le sens d'action de la deuxième poche (23, 24) de palier étant différent de celui de la première poche de palier.
  15. Ensemble selon la revendication 14, caractérisé en ce qu'au moins une poche (24) de palier est divisée en deux poches partielles (24a, 24b) dont chacune est alimentée par un étranglement d'amenée (35a, 35b).
  16. Procédé pour enrouler une nappe de matière en un rouleau (5), dans lequel le rouleau (5) repose contre au moins un cylindre (2, 3) qui tourne lors de l'enroulement avec une fréquence de rotation maximale, caractérisé en ce que le cylindre (2, 3) fonctionne de manière supercritique.
EP12159574.8A 2011-03-25 2012-03-15 Dispositif et procédé d'enroulement d'une bande de matériau Active EP2502861B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011006161A DE102011006161A1 (de) 2011-03-25 2011-03-25 Vorrichtung und Verfahren zum Aufwickeln einer Materialbahn

Publications (3)

Publication Number Publication Date
EP2502861A2 EP2502861A2 (fr) 2012-09-26
EP2502861A3 EP2502861A3 (fr) 2014-12-03
EP2502861B1 true EP2502861B1 (fr) 2019-08-07

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Application Number Title Priority Date Filing Date
EP12159574.8A Active EP2502861B1 (fr) 2011-03-25 2012-03-15 Dispositif et procédé d'enroulement d'une bande de matériau

Country Status (3)

Country Link
EP (1) EP2502861B1 (fr)
CN (1) CN102756938B (fr)
DE (1) DE102011006161A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018119740A1 (de) * 2018-08-14 2020-02-20 Voith Patent Gmbh Aufwickelvorrichtung

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5240636A (en) * 1975-09-25 1977-03-29 Mitsubishi Heavy Ind Ltd Support method and apparatus for high speed winder bobbin holder axis
CH647213A5 (de) * 1979-08-31 1985-01-15 Barmag Barmer Maschf Spindel fuer hohe drehzahlen.
DE19548142A1 (de) * 1995-12-22 1997-06-26 Barmag Barmer Maschf Aufspulvorrichtung
CH691856A5 (de) * 1997-02-18 2001-11-15 Rieter Ag Maschf Spulendorn.
DE102004062890A1 (de) * 2004-01-06 2005-10-13 Eras Gmbh Rollenwickeleinrichtung
DE102005024266A1 (de) * 2005-05-27 2006-11-30 Voith Patent Gmbh Rollenwickeleinrichtung
DE102005035619A1 (de) * 2005-07-29 2007-02-08 Voith Patent Gmbh Verfahren zum Aufwickeln einer Materialbahn und Wickelvorrichtung
DE102009055353A1 (de) * 2009-12-29 2011-06-30 Voith Patent GmbH, 89522 Rollenwickelvorrichtung und Verfahren zum Aufwickeln einer Materialbahn

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
CN102756938B (zh) 2017-03-01
EP2502861A3 (fr) 2014-12-03
EP2502861A2 (fr) 2012-09-26
DE102011006161A1 (de) 2012-09-27
CN102756938A (zh) 2012-10-31

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