EP2808445B1 - Biegeeinstellwalze - Google Patents

Biegeeinstellwalze Download PDF

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Publication number
EP2808445B1
EP2808445B1 EP13169860.7A EP13169860A EP2808445B1 EP 2808445 B1 EP2808445 B1 EP 2808445B1 EP 13169860 A EP13169860 A EP 13169860A EP 2808445 B1 EP2808445 B1 EP 2808445B1
Authority
EP
European Patent Office
Prior art keywords
roll
loading
damping
tolerance
loading element
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
EP13169860.7A
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English (en)
French (fr)
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EP2808445A1 (de
Inventor
Jani Hakola
Mika Viljanmaa
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.)
Valmet Technologies Oy
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Valmet Technologies Oy
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 Valmet Technologies Oy filed Critical Valmet Technologies Oy
Priority to EP13169860.7A priority Critical patent/EP2808445B1/de
Priority to CN201420282184.0U priority patent/CN204059089U/zh
Publication of EP2808445A1 publication Critical patent/EP2808445A1/de
Application granted granted Critical
Publication of EP2808445B1 publication Critical patent/EP2808445B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/02—Rolls; Their bearings
    • D21G1/0206—Controlled deflection rolls
    • D21G1/0213—Controlled deflection rolls with deflection compensation means acting between the roller shell and its supporting member
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/0073—Accessories for calenders
    • D21G1/008—Vibration-preventing or -eliminating devices
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/02—Rolls; Their bearings
    • D21G1/0226—Bearings

Definitions

  • the invention relates to a deflection compensated roll according to the preamble of claim 1.
  • the deflection compensated roll is a nip roll for a calender of the fiber web machine.
  • a typical production and treatment line comprises a head box, a wire section and a press section as well as a subsequent drying section and a reel-up.
  • the production and treatment line can further comprise other devices and sections for finishing the fiber web, for example, a sizer, a calender, a coating section.
  • the production and treatment line also comprises at least one winder for forming customer rolls as well as a roll packaging apparatus.
  • fiber webs are meant for example a paper, board, tissue webs. In each section and device vibrations may occur in several different components.
  • vibrations may occur in a nip, which is formed in between two elements, typically between two rolls but also the nip can be formed with a roll, a belt, a shoe or corresponding element and a counter-element of corresponding or different kind, often at least one of the nip forming elements is a roll.
  • the roll can be a deflection compensated roll, which are used in nips of the press section and of the calenders of the fiber web machine.
  • water is removed from the fiber web and in the calender nips the fiber web is treated for example to achieve certain surface properties such as gloss.
  • the fiber web is passed through the nip freely or supported by a belt, a felt, a wire or a corresponding fabric.
  • the fiber web is pressed in order to remove water from the web or to effect to the properties of the web and by the deflection compensated roll the nip pressure is controlled in cross-direction or the fiber web i.e. in the longitudinal direction of the roll.
  • one vibration form is barring which is caused by resonance of a roll pair, in which the calender vibrates such that nip load varies.
  • the variations in nip load gradually form the soft cover of the calender such that the cross section of the roll will be angular.
  • the resonance of roll pairs of calenders is unavoidable and only size of rolls and frames have influence on the frequencies on which the resonance occurs.
  • the amplitude of vibration is limited only by damping in the mechanical system i.e. the heat energy created by the vibration of elements of the system. Damping is observed for example as internal hysteresis of materials (very little effect), in connections with friction, as friction losses on glide-surfaces.
  • the largest damping occurs in connection with movements of pistons of loading elements of the deflection compensated roll. It should be noted that the movement must be long enough in order not to remain only as elastic deformation of seals of the loading elements.
  • a deflection compensated roll comprises a shell around the loading shaft with loading zones in which loading shoes with a piston are arranged.
  • the loading zones are connected to the shell of the roll rigidly, since thicknesses of lubricating oil between the loading shoes and the shell are thin.
  • the loading shoes are supported on the loading shaft by means of a pressure medium volume, typically an oil volume and also this medium volume is significantly rigid, since as the piston moves the moving medium area is large and flow channels are very narrow.
  • DE-A-102005049524 is disclosed a a deflection-compensated roll in a paper machine which the roll has a shell and is supported on it by supporting elements pressed against the inside of the sleeve with the aid of a hydraulic pressure medium, where each element comprises a radially-moveable shoe pressing against the inside of the roll and a radially-moveable piston. Also the roll includes elements between the shoe and the piston by means of which vibration transmitted from the nip is transferred from the shoe to the piston.
  • EP 1411254 B1 is disclosed a middle roll of a calender with a damper assembly having an inertial mass.
  • the roll has a roll shell that surrounds an internal space, in which there is arranged a damper assembly having at least one passive oscillation damper that has a damper frequency which lies below a natural frequency of the roll, or a roll system containing the rolls, that is critical for the formation of barring.
  • a damper assembly having at least one passive oscillation damper that has a damper frequency which lies below a natural frequency of the roll, or a roll system containing the rolls, that is critical for the formation of barring.
  • the middle roll at least in a region between the oscillation damper and the roll shell, the internal space is filled with liquid, the viscosity of which exceeds a predetermined minimum amount.
  • the damper will be set to a certain frequency for damping.
  • the roll disclosed is a tube roll not a deflection compensated roll.
  • An object of the invention is to create a deflection compensated roll and in which the disadvantages and problems of prior art are eliminated or at least minimized.
  • an object of the invention is to provide a deflection compensated roll for a calender of a fiber web machine.
  • the deflection compensated roll according to the invention is characterized by the features of the characterizing clause of claim 1.
  • a new way of controlling vibrations in a deflection compensated for example a zone controlled roll for a calender is created, in which the vibrations are controlled with the help of loading means of the deflection compensated roll and/ or with the help of support means of the deflection compensated roll.
  • the support means may be the bearing support to the frame of the calender for the shaft ends of the roll or the loading cylinder support of the calender.
  • optimum design of at least one roll is provided by vibration modeling simultaneously combining limitations of static loading and providing optimal amplitude of movement in the loading elements of the at least one roll in the / in those natural frequency / frequencies that cause nip pressure or nip load variation in the nip formed by the deflection compensated roll with another roll.
  • the deflection compensated roll is designed and damping means are designed for the at least one loading element and advantageously for the support of the roll. It should be noted that prior art design methods of calender rolls do not take into account any parameters relating to vibration or its damping and when vibration occurs in use of the calender rolls solutions are sought to dampen the vibration i.e. action is taken only after the problems occur.
  • the hydraulic piston of a loading element of the deflection compensated roll is separated from the loading element by resilient connection, i.e.
  • the loading element is located in the pressure pocket of the shaft such that there is a significant tolerance between the loading element and the pressure pocket.
  • the tolerance is 0,5 -2,5 mm, advantageously 1,0 - 2,0 mm.
  • this tolerance is advantageously not sealed and the loading element floats in the medium, advantageously in oil.
  • the loading element When the loading element is under vibration it moves the medium in the volume between the piston and the loading element, which medium is pressurized and forced to flow in the tolerance of the pressure pocket of the loading element. In the tolerance the medium flow creates pressure loss that is in direct relationship with movement velocity of the loading element and thus functions as a viscous damper.
  • the deflection compensated roll comprises a resilient element, which is a disc spring which is located between the piston of the at least one loading element of the roll and support of the at least one loading element is provided freely movable in the loading direction of the at least one loading element.
  • the hydraulic piston of the loading element may also be loaded by a high pressure gas volume, which will be significantly more compressible than oil.
  • a separate oil feed line is arranged for the lubrication of the loading element.
  • Leakage free air loaded zones of the roll also make it possible to use simple and compact solenoid valves for pressure control of the loading zones.
  • Complicated servo/proportional valves are not needed, but instead pressure is controlled by adjusting the opening and closing times of the solenoid valves. Such control is known as digital pressure control.
  • the shell of the deflection compensated roll vibrates, at least one loading element moves with the shell as only thin foil of medium is between the shell and the loading element.
  • the loading element moves towards the shaft of the roll, it causes a medium flow into the tolerance with high flow speed due to the narrowness of the tolerance and a flow loss is caused.
  • the flow loss is dependent on viscosity of the medium, dimensions of the tolerance and thus at a certain movement speed a pressure loss is created which is dependent on the cross-sectional flow area of the tolerance and by this the damping force is created.
  • the optimum damping design can be calculated such that the vibration damping by loading elements will provide its maximum under different vibrations.
  • the vibration damping can further be influenced during operating the calender, as damping is dependent from the viscosity of the medium and adjustment of viscosity of the medium is provided by adjusting the temperature of the medium and thus also adaptive vibration damping can be achieved.
  • the stiffness of the loading elements is in the range of 1 x 10 5 N/m - 1 x 10 7 N/m and damping is the range of 1 x 10 5 Ns/m - 1 x 10 6 Ns/m.
  • the roll support stiffness is advantageously 1 x 10 7 N/m -5 x 10 8 N/m.
  • the roll support damping is advantageously 5 x 10 5 Ns/m -5 x 10 7 Ns/m.
  • the desired damping properties are designed to the roll.
  • the deflection compensated roll is designed for a roll nip of a calender such that total damping is maximized by taking into account all resonances in the roll causing pressure variations in the nip area.
  • the deflection compensated roll is supported by its shaft ends to the frame of the by resilient support and by a bearing.
  • a vibration damping support of the roll is provided by liquid film damping, i.e. squeeze film damping.
  • the shaft of the roll moves oil in a tolerance of a bearing housing
  • the oil film in the tolerance is squeezed between hard surfaces and forced to flow in the narrow gap volume. Pressure loss in the flow creates an opposite force and damping is achieved. Damping force is dependent on viscosity of the liquid, height of the tolerance and width of the shaft and the liquid film sector dimensions.
  • support of the deflection compensated roll is provided by construction the bearings of the roll on support of a separate bushing which is supported in the loading direction to the respective bearing house by pressure pockets.
  • the pressure pockets are filled for supporting the load pressurized gas, for example air, which has high compressibility.
  • the area and volume of the pressure pocket is designed to provide desired compliance of the support.
  • liquid pockets that are filled with oil or other liquid. The tolerance between the liquid pockets and the bushing and the sector covered by the liquid pockets and the area of the liquid pockets give the different factors to design the liquid volume such that desired viscous damping is provided.
  • the support arrangement can also be fitted in the fixing points of calender loading cylinders.
  • the damping is provided such that when the bushing moves in loading direction at the other end of the liquid volume the tolerance decreases and at the other end the tolerance increases. As the liquid flows in the narrow tolerance according to the replacement volume pressure loss is created in the flow and thus an opposing force to the movement is provided.
  • the stiffness and damping properties of the support of the deflection compensated roll are designed.
  • the deflection compensated roll is loaded in the calender by loading cylinders provided with resilient support.
  • vibrations damping support is provided by liquid film damping, i.e. squeeze film damping, in which in loading direction the force is carried by a high pressurized gas pocket and the shaft of the loading cylinder is "floating" on a small tolerance defined by discharge amount and throttling of the inlet side.
  • figure 1 is shown schematically an example of the invention.
  • figure 2A is shown schematically an example of an advantageous loading element according to the invention.
  • figure 2B is shown schematically another example of a loading element which example does not fall under the scope of the claims.
  • figure 3 is shown schematically an example of an advantageous bearing arrangement according to an advantageous feature of invention.
  • figure 4 is shown schematically in further detail the liquid flow in liquid pockets of the example of figure 3 .
  • figure 5 is shown schematically another example of an advantageous bearing arrangement according to an advantageous feature of invention.
  • FIGS 6 and 7 are schematically shown an example of schematic example a swimming roll.
  • FIG. 8A - 8B is shown schematically an example the loading cylinder support of the calender.
  • a nip N for example a calender nip, is formed between a deflection compensated roll 10 and its counter roll 11.
  • the counter roll 11 is supported by its shaft ends 13 by a vibration damping element 15 and by a spring element 17 to the frame structure of the device, for example the calender.
  • the deflection compensated roll 10 is supported by its shaft ends 12 by a vibration damping element 14 and by a spring element 16 to the frame structure of the device for example the calender.
  • On the shaft 12A of the deflection compensated roll 10 are supported loading elements 20 of which only one is marked by reference numeral for clarity reasons.
  • the loading elements 20 load the shell 10A of the roll in the nip direction, as shown in the figure, i.e. towards the counter roll 11 of the deflection compensated roll 10.
  • Each loading element 20 is also provided with a damping element 24 and a spring element 26.
  • the optimum damping design can be calculated such that in vibration modes the vibration damping by loading elements is maximized.
  • the vibration damping can further be influenced during operating the calender, as damping is dependent from the viscosity of the medium and adjustment of viscosity of the medium is provided by adjusting the temperature of the medium and thus also adaptive vibration damping can be achieved.
  • FIG 2A is the example of the loading element 20 loads the shell 10A and it is located in a pressure pocket of the shaft 12A of the deflection compensated roll10.
  • the loading element 20 comprises a loading shoe 23, which has oil pockets 25 for lubricating medium, for example oil.
  • the lubricating medium is passed to the oil pockets 25 via channels 27.
  • the hydraulic piston 21 is separated from the loading element 20 by the resilient spring element 26, by a disc spring and seals 35 seal the loading pressure pocket 33 of the piston 21.
  • the loading element 20 is located in the pressure pocket 33 of the shaft 12A such that there is a significant tolerance 31 between the loading element 20 and the pressure pocket.
  • the tolerance is 0,5 - 2,5 mm, advantageously 1,0 - 2,0 mm.
  • the loading element 20 floats in the medium, advantageously in oil.
  • the cross section of the element deviates from circular form, for example it may have grooves for providing cross-sectional flow area (not shown).
  • Below the spring element 26 is the piston 21 that provides the loading force for the loading element 20, as shown by arrows.
  • the piston 21 is sealed in the pressure pocket 33 by seals 35.
  • the hydraulic piston 21 of the loading element 20 may also be loaded by a high pressure gas volume in loading pocket 33 sealed by seals 35 as shown in figure 2B .
  • the loading element 20 comprises a loading shoe 23, which has oil pockets 25 for lubricating medium, for example oil.
  • a separate oil feed line 38 is arranged for the lubrication of the loading element 20.
  • the piston 21 of the loading element 20 of is separated from the loading element 20 by the gas space 39 sealed by seals 35, 36.
  • the loading element 20 is located in the pressure pocket 33 of the shaft 12A such that there is a significant tolerance 31 between the loading element 20 and the pressure pocket.
  • the tolerance is 0,5 - 2,5 mm, advantageously 1,0 - 2,0 mm.
  • a deflection compensated roll 10 comprises a shell 10A around the loading shaft 12A with loading zones provides by the loading elements 20 pistons 21.
  • the loading zones are connected to the shell 10A of the roll 10 rigidly, since thicknesses of lubricating oil between the loading elements 20 and the shell 10A are thin.
  • the loading elements 20 are supported on the loading shaft 12A by means of a pressure medium volume.
  • the loading and vibration damping is provided such that when the shell 10A of the deflection compensated roll 10 vibrates the at least one loading element 20 moves with the shell 10A as only thin foil of medium is between the shell 10A and the loading shoe 23 of the loading element 20.
  • FIG 3 is shown a schematic example of the shaft end 12 bearing house 41, in which around bearing 43 an oil film is provided in tolerance i.e. liquid pocket 45 between the bearing 43 and the bearing house 41.
  • the loading direction is marked by arrow LD.
  • Pressure pockets 47 are provided in the loading direction LD.
  • Seals 49 are located between the pressure pockets 47 and liquid pockets 45.
  • the support of the shaft ends 12 of the roll 10 has a separate bushing 50 which is supported in the loading direction LD to the respective bearing house 41 by pressure pockets 47.
  • the pressure pockets 47 are filled with pressurized gas, for example air, which high compressibility.
  • the area and volume of the pressure pocket 47 is designed to provide desired compliance of the support.
  • Perpendicular to the loading direction LD is additionally provided liquid pockets 45 that are filled with oil or other liquid. The tolerance between the liquid pockets 45 and the bushing 50 and sector covered by the liquid pockets 45 and area of the liquid pockets 45 give the different factors to design the liquid volume such that desired viscous damping is provided.
  • the damping is provided such that when the bushing 50 moves in loading direction LD at the other end of the liquid volume the tolerance decreases and at the other end the tolerance increases. As the liquid flows in the narrow tolerance according to the replacement volume pressure loss is created in the flow and thus an opposing force to the movement is provided.
  • a swimming roll 60 is provided by a spring (not shown) in the loading element 62, which loading element is similar to figure 2 .
  • the spring follows the shell 65 and thus compensates the movement and vibration damping is provided.
  • FIGS 8A - 8B is shown schematically an example the loading cylinder support 70 of the calender, with resilient support.
  • vibrations damping support is provided by liquid film damping, i.e. squeeze film damping, in which in loading direction the force is carried by a high pressurized gas pocket 71, which corresponds to pressure pocket 47 of figures 3 and 5 and the shaft of the loading cylinder is "floating" on a small tolerance defined by discharge amount and throttling of the inlet side.
  • a cone structure 72 provides the positioning of the shaft of the loading cylinder and functional tolerances are provided by axial tightening means 73.
  • Hydraulic pockets 74 In direction perpendicular to the loading the shaft positions by hydraulic pockets 74, in which oil is fed into middle of the pockets and discharged from edge grooves of the pockets and operation of which corresponds to that of liquid pockets 45 of figures 3 - 5 . Hydraulic pockets 74 also provide viscous dampening by squeeze film effect.

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  • Paper (AREA)
  • Rolls And Other Rotary Bodies (AREA)

Claims (2)

  1. Biegungskompensierte Walze für eine Faserbahnmaschine, insbesondere für einen Kalander, wobei die Walze (10) eine Welle (12A) und Wellenenden (12), einen Mantel (10A) und wenigstens ein Belastungselement (20), das den Mantel (10A) belastet und in Drucktaschen (33) der Welle (12A) angeordnet ist, aufweist, wobei die Walze (10) eine Nipwalze ist, wobei die biegungskompensierte Walze (10) Dämpfungseinrichtungen (24, 26) für das wenigstens eine Belastungselement (20) der biegungskompensierten Walze (10) zum Dämpfen von Vibrationen des Mantels (10A) der Walze aufweist, wobei die Dämpfungseinrichtungen ein Federelement (26) und ein Dämpfungselement (24) aufweisen, wobei das wenigstens eine Belastungselement (20) in der Belastungsrichtung frei beweglich ist, wobei das Belastungselement (20) und ein Kolben (21) zum Bewegen des Belastungselements (21) in der Drucktasche (33) angeordnet sind und das Federelement eine in der Drucktasche (33) zwischen dem Belastungselement (20) und dem Kolben (21) angeordnete Tellerfeder ist und die Drucktasche (33) ein Medium aufweist, in dem das Belastungselement (20) schwimmt, und wobei das Dämpfungselement als ein viskoser Dämpfer durch einen Freiraum (31) zwischen dem Belastungselement (20) und der Drucktasche (33) ausgebildet ist,
    dadurch gekennzeichnet, dass
    der Freiraum (31) 0,5 bis 2,5 mm, vorzugsweise 1,0 bis 2,0 mm, beträgt und das Medium aufweist, und wenn das Belastungselement (20) aufgrund der Vibration des Walzenmantels (10A) vibriert, sich das Medium in der Drucktasche (33) in Richtung des Freiraums (31) bewegt und in dem Freiraum (31) der Strom des Mediums einen Druckverlust erzeugt, der in direkter Beziehung zu der Bewegungsgeschwindigkeit des Belastungselements (20) steht.
  2. Biegungskompensierte Walze nach Anspruch 1,
    dadurch gekennzeichnet, dass
    der Freiraum (31) offen ist.
EP13169860.7A 2013-05-30 2013-05-30 Biegeeinstellwalze Active EP2808445B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP13169860.7A EP2808445B1 (de) 2013-05-30 2013-05-30 Biegeeinstellwalze
CN201420282184.0U CN204059089U (zh) 2013-05-30 2014-05-29 纤维幅材机的偏移补偿辊

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13169860.7A EP2808445B1 (de) 2013-05-30 2013-05-30 Biegeeinstellwalze

Publications (2)

Publication Number Publication Date
EP2808445A1 EP2808445A1 (de) 2014-12-03
EP2808445B1 true EP2808445B1 (de) 2017-03-15

Family

ID=48520801

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13169860.7A Active EP2808445B1 (de) 2013-05-30 2013-05-30 Biegeeinstellwalze

Country Status (2)

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EP (1) EP2808445B1 (de)
CN (1) CN204059089U (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI127119B (en) 2015-10-27 2017-11-30 Valmet Technologies Oy System for damping vibrations in a nip in a fiber web machine
CN106946079B (zh) * 2017-05-05 2018-06-22 东莞市鑫盛手袋工艺有限公司 一种具有自动校正机构的布料输送切割机构
CN106904476B (zh) * 2017-05-05 2018-06-29 郑端金 一种布料输送用自动校正机构
CN106904474B (zh) * 2017-05-05 2018-05-25 佛山市南海区金龙恒家具有限公司 一种具有自动提升式布料输送用自动校正机构
EP3617403B1 (de) * 2018-08-30 2021-09-01 Valmet Technologies Oy Verfahren zur behandlung eines faservlieses und behandlungssystem zur behandlung eines faservlieses
CN113862927B (zh) * 2021-09-06 2023-11-03 海宁忆丹纺织股份有限公司 装饰面料后整理装置

Family Cites Families (7)

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Publication number Priority date Publication date Assignee Title
DE10248519B4 (de) 2002-10-17 2006-11-02 Voith Patent Gmbh Mittelwalze eines Kalanders und Kalander
FI118056B (fi) * 2004-11-11 2007-06-15 Metso Paper Inc Järjestely taipumakompensoidun telan värähtelyiden vaimentamiseksi
FI118812B (fi) * 2006-02-01 2008-03-31 Metso Paper Inc Menetelmä kalanterin välitelan värähtelyn ominaistaajuuden hallitsemiseksi ja värähtelyn vaimennin
US20080000363A1 (en) * 2006-06-29 2008-01-03 Metso Paper, Inc. Adjustable Anti-Barring Device for Calender Rolls
FI121752B (fi) * 2009-07-07 2011-03-31 Metso Paper Inc Laitteisto ja menetelmä kuiturainan käsittelynipin ajettavuuden hallitsemiseksi
DE102010002503A1 (de) * 2010-03-02 2011-09-08 Voith Patent Gmbh Walze für eine Papier- oder Kartonmaschine und Verfahren zum Dämpfen von Schwingungen einer Walze
DE102010039795A1 (de) * 2010-08-26 2012-03-01 Voith Patent Gmbh Vorrichtung und Verfahren zur Reduzierung von Schwingungen an einer Biegeeinstellwalze

Non-Patent Citations (1)

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CN204059089U (zh) 2014-12-31
EP2808445A1 (de) 2014-12-03

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