EP2502860A2 - Dispositif d'enroulement d'une bande de matériau - Google Patents

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

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Publication number
EP2502860A2
EP2502860A2 EP12159567A EP12159567A EP2502860A2 EP 2502860 A2 EP2502860 A2 EP 2502860A2 EP 12159567 A EP12159567 A EP 12159567A EP 12159567 A EP12159567 A EP 12159567A EP 2502860 A2 EP2502860 A2 EP 2502860A2
Authority
EP
European Patent Office
Prior art keywords
bearing
winding
throttle
roller
roll
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
EP12159567A
Other languages
German (de)
English (en)
Other versions
EP2502860B1 (fr
EP2502860A3 (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
Application filed by Voith Patent GmbH filed Critical Voith Patent GmbH
Publication of EP2502860A2 publication Critical patent/EP2502860A2/fr
Publication of EP2502860A3 publication Critical patent/EP2502860A3/fr
Application granted granted Critical
Publication of EP2502860B1 publication Critical patent/EP2502860B1/fr
Active 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
    • 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
    • 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 web of material to a winding roll with at least one roller on which the winding roller bears during winding and which rotates during winding, wherein the roller is mounted in a bearing device with a bearing at each end of the roll.
  • Devices for winding 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.
  • the invention has for its object to be able to wind even vibration-critical material webs with as few problems.
  • the bearing is a hydrostatic Support with at least a first bearing pocket, which is fed with hydraulic fluid.
  • roller In a hydrostatic support, the roller rests on hydraulic fluid, which flows continuously through an "oil gap", which results at the boundary of the bearing pocket. Regardless of the load, the same oil gap always appears on average 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.
  • the bearing pocket is fed with a constant volume flow of hydraulic fluid.
  • the oil gap decreases slightly and the throttle resistance for the hydraulic fluid flowing out through the oil gap increases. This increases the pressure in the bearing pocket, which counteracts the increased load. This results in a static position control, so to speak.
  • a constant volume flow can be provided relatively easily, for example by a constant-flow pump or a pump with a constant-flow regulator.
  • the storage bag can be connected via a throttle with a constant form.
  • the constant admission pressure depends on the expected load and should be much greater than a counterpressure generated by this load. Also in this case results in an automatic static position control.
  • the throttle resistance increases in the Oil gap. Accordingly, less hydraulic fluid can flow out of the bearing pocket and the pressure drop across the throttle between the constant admission pressure and the bearing pocket becomes correspondingly smaller, so that the pressure in the bearing pocket rises again. This increasing pressure counteracts the increased 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 supplied with a constant volume flow of hydraulic fluid or via a throttle of a constant pressure, 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 bearing device has a stiffness that varies with the exciter frequency. So you have a static stiffness that is effective against loads whose frequencies theoretically go to zero. In practice, loads are usually considered static, whose frequencies are less than 0.1 Hz. In contrast, the dynamic stiffness is effective against loads whose frequencies are higher than 0.1 Hz. Thus, when a roller rotates, the static stiffness remains substantially effective against the effective weight of the roller, while the dynamic stiffness must be effective against the higher frequency loads that then occur.
  • 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 relatively stiff for very small excitation frequencies (f ⁇ 0.1 Hz), so that even when larger forces, such as the weight of a finished winding roll, no change in location of the roll is 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 at the reduced rotational frequency has a dynamic stiffness 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 device when the maximum winding speed has been reached, the device can be moved overcritically, i. the rotational frequency of the roller may be 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 device can also be driven under critical.
  • the first natural frequency may even be 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 of 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 applies to the desired feed speed of the material web and thus for the maximum rotational frequency of the roller, which it reaches when at the beginning of a winding process, the material web on the desired feed rate has been accelerated.
  • 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 roller 5 has reached its maximum diameter, the winding roller 5 rotates at 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 on the supply line 13th incoming hydraulic fluid can therefore only escape via the gap 15 and be discharged via a drain 16.
  • the bearing pocket 12 is fed with a higher pressure and the hydraulic fluid is supplied 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 12 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 conditions, limited oil flow, storage volume, etc., the hydrostatic bearing in conjunction with the pressure accumulator does not provide the desired combination of dynamic stiffness and damping behavior.
  • 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 roller 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 of the support rollers 2, 3 is greater than the natural frequency f01A of the roller assembly, which is formed in each case from a 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 it was 1.3 times the maximum rotation 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)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
EP12159567.2A 2011-03-25 2012-03-15 Dispositif d'enroulement d'une bande de matériau Active EP2502860B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011006158A DE102011006158A1 (de) 2011-03-25 2011-03-25 Vorrichtung zum Aufwickeln einer Materialbahn

Publications (3)

Publication Number Publication Date
EP2502860A2 true EP2502860A2 (fr) 2012-09-26
EP2502860A3 EP2502860A3 (fr) 2013-08-07
EP2502860B1 EP2502860B1 (fr) 2016-06-29

Family

ID=45887971

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12159567.2A Active EP2502860B1 (fr) 2011-03-25 2012-03-15 Dispositif d'enroulement d'une bande de matériau

Country Status (3)

Country Link
EP (1) EP2502860B1 (fr)
CN (1) CN102745532B (fr)
DE (1) DE102011006158A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103171920A (zh) * 2013-04-12 2013-06-26 江苏金呢工程织物股份有限公司 造纸成形网验网用卷网机
DE102018119740A1 (de) 2018-08-14 2020-02-20 Voith Patent Gmbh Aufwickelvorrichtung

Family Cites Families (10)

* 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
US4782919A (en) * 1987-12-21 1988-11-08 United Technologies Corporation Supply system for oil dampers
US4867655A (en) * 1988-03-14 1989-09-19 United Technologies Corporation Variable stiffness oil film damper
JPH08261231A (ja) * 1995-03-20 1996-10-08 Ishikawajima Harima Heavy Ind Co Ltd スクイーズフィルムダンパ軸受
DE10122648A1 (de) * 2001-05-10 2002-11-28 Voith Paper Patent Gmbh Biegeausgleichswalze
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
DE102006058940B4 (de) * 2006-12-12 2008-10-02 Voith Patent Gmbh Verfahren und Vorrichtung zur Dämpfung von Schwingungen
DE102008000096A1 (de) * 2008-01-18 2009-07-23 Voith Patent Gmbh Rollenwickelvorrichtung und Verfahren zum Aufwickeln einer Materialbahn zu einer Wickelrolle

Non-Patent Citations (1)

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

Also Published As

Publication number Publication date
EP2502860B1 (fr) 2016-06-29
CN102745532B (zh) 2016-12-07
CN102745532A (zh) 2012-10-24
DE102011006158A1 (de) 2012-09-27
EP2502860A3 (fr) 2013-08-07

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