WO2008003820A2 - Procédé et dispositif pour amortir une vibration de roulis - Google Patents

Procédé et dispositif pour amortir une vibration de roulis Download PDF

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Publication number
WO2008003820A2
WO2008003820A2 PCT/FI2007/000188 FI2007000188W WO2008003820A2 WO 2008003820 A2 WO2008003820 A2 WO 2008003820A2 FI 2007000188 W FI2007000188 W FI 2007000188W WO 2008003820 A2 WO2008003820 A2 WO 2008003820A2
Authority
WO
WIPO (PCT)
Prior art keywords
vibration
vibrator
primary system
frequency
damper
Prior art date
Application number
PCT/FI2007/000188
Other languages
English (en)
Other versions
WO2008003820A3 (fr
Inventor
Marko Jorkama
Timo Virtanen
Original Assignee
Metso Paper, Inc.
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 Metso Paper, Inc. filed Critical Metso Paper, Inc.
Priority to ATA9299/2007A priority Critical patent/AT506025B1/de
Priority to DE112007001589T priority patent/DE112007001589T5/de
Publication of WO2008003820A2 publication Critical patent/WO2008003820A2/fr
Publication of WO2008003820A3 publication Critical patent/WO2008003820A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H20/00—Advancing webs
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21F—PAPER-MAKING MACHINES; METHODS OF PRODUCING PAPER THEREON
    • D21F3/00—Press section of machines for making continuous webs of paper
    • D21F3/02—Wet presses
    • D21F3/08—Pressure rolls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/1005—Vibration-dampers; Shock-absorbers using inertia effect characterised by active control of the mass
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2701/00—Handled material; Storage means
    • B65H2701/10—Handled articles or webs
    • B65H2701/17—Nature of material
    • B65H2701/177—Fibrous or compressible material

Definitions

  • the invention concerns a method for damping roll vibration, as well as a roll vibration damper and a fibrous web machine or device fitted with a roll vibration damper.
  • Vibration of nip forming rolls causes intermittent markings on the web as it passes through the nip.
  • the web markings which correspond with the vibration of the rolls, are typically manifested as an undesirable fluctuation in, e.g., thickness, gloss, smoothness or density that weakens the quality of the web.
  • the vibrational stimulus typically corresponds to a multiple of the rotation frequency of either roll.
  • the vibration is also time-dependent, particularly if the nip counter roll is soft-surfaced, as the roll cover polymer undergoes deformation during operation which is not restored during rotation.
  • the roll surface deformation acts as an additional stimulus, amplifying the commencing vibration.
  • This example phenomenon can be reduced by suitably altering the operating conditions or control parameters, such as drive speed, nip load or roll torque distribution.
  • control parameters such as drive speed, nip load or roll torque distribution.
  • the aim of paper machines and paper finishing machines is to produce a grade that is as homogeneous as possible throughout the entire batch, so any changes in control parameters for the purpose of minimising vibration would also require additional controls compared to operating situations where vibration can be kept under control by other means.
  • On-line machines a sufficiently rapid change in driving speed, in particular, is usually not possible due, e.g., to the number of controls and their slowness.
  • the grade produced cannot be kept uniform during the change, so the end result deviates from the desired quality.
  • a vibration damper for the rolls of web handling equipment is presented in patent publication EP 1333123A1.
  • the damper is implemented with an active actuator so that the bending moment is set on the roll shaft relative to the vibration in an out-of-phase manner; in practice, in the opposite phase.
  • the actuator presented in the publication comprises an electric, electromagnetic, magnetostrictive, piezoelectric, hydraulic or pneumatic operating device.
  • Patent publication DE 19605416 B4 shows a method for vibration damping which includes a damping primary system and a linear active vibration damper, in which the linear active vibration damper consists of a) a passive vibration damper, which is fastened to the damping primary system, b) a passive vibration damper fitted with additional components which produce a load in the lateral system and a torque between the damping primary system frame and the passive vibration damper, c) the load or moment is derived from the absolute or relative position of both frames or the position relative to each other, or using these together with one selectable linear filter and transfer function, d) the difference signal is derived from the absolute or relative ratio between the frames, whereupon the difference signal is entered as the linear filter input signal and the output signal is the load or torque.
  • the linear active vibration damper consists of a) a passive vibration damper, which is fastened to the damping primary system, b) a passive vibration damper fitted with additional components which produce a load in the lateral system and a torque between the damping primary
  • roll vibration damper and/or simply damper can be used to designate the device as a whole in reference to only a structural component or other feature of a structural component for which at least one of the properties describing its function is the damping factor cXX (XX index can vary numerically).
  • the aim of the invention is to further improve these known vibration damping methods and achieve an efficient and as versatile as possible roll vibration damper.
  • the objective is to prevent weakening of the quality of the fibrous web produced due to barring, and to carry this out without the need to change the fibrous web production parameters for the prevention or elimination of barring.
  • One of the objectives is to devise a method with which vibrations can be damped efficiently and sufficiently from a wide band of frequencies without solely limiting the surrounding structural natural undamped frequency.
  • the objective is to also be able to separately control the damping and the characteristic frequency of the roll vibration damper, as well as to perform, if necessary, this change and tuning of the damping frequency range when the fibrous web machine is operating.
  • the objective is to also place a separate device at the position of the problem vibration; the device must be easy to connect, commission and calibrate, as well as specially accurate and suitably simple.
  • a procedure for damping roll vibration has been created according to claim 1.
  • a roll vibration damper for a fibrous web machine has been created according to claim 12.
  • a fibrous web machine has been created according to claim 22.
  • a vibrating device has been configured to vibrate the primary system at the desired vibration frequency to be damped, such as the frequency corresponding to the barring frequency, so that the vibrations in question can be controlled with delayed resonator-based control circuits for damping roll vibration of a fibrous web machine.
  • the roll vibration can be damped significantly in the primary system of a fibrous web machine.
  • the roll vibration reduction can be automatic or self-adjusting, and so manual control is not necessarily required.
  • proportionally accurate roll vibration reduction is possible, i.e., the so-called frequency of the counter vibrator accurately compensates the actual harmful vibration of the primary vibrator.
  • the invention allows adjustment of the damper and the characteristic frequency of the mass damper simultaneously and independently. This prevents instability and sensitivity problems that are associated with current systems. Furthermore, the invention allows the use of a load-producing actuator without it changing the dynamics or rigidity of the damper. The invention also eliminates the effect of non-linearities and other, for example, time dependencies of the load actuator for the operation of the damper.
  • the load element's own dynamics can be easily eliminated from the system with the invention-based load control circuits presented, in which case the damper can operate in its own resonance frequency environment. Therefore, the delayed resonator -based control circuit in several applications, e.g. two nested cascaded delayed resonator principle -based control circuits, enables more accurate and efficient vibration damping in a fibrous web machine.
  • the invention-based method also enables compensation for potential non-linearities of the load elements.
  • the vibrations to be damped occur in fibrous web machines in a very wide frequency range, approximately between 5 to 1000 Hz. In different structural groups this range can also be narrower. Typical frequency ranges are, for example, in the press section 50 to 150 Hz, in size press coating machines 40 to 100 Hz, in calenders 250 to 500 Hz, in winders 15 to 35 Hz, etc. For example, the roll rotation speeds and the various multiples of these, the natural frequencies of frame structures and other corresponding structural items affect such typical frequency ranges.
  • Figure 1 shows the delayed resonator in a fibrous web machine according to several applications of the invention.
  • Figure 2 describes in more detail the delayed resonator of Figure 1 in a fibrous web machine.
  • Figure 3 shows one example of roll vibration damping according to several applications of the invention.
  • Figure 4 shows the delayed resonator control based on the cascade control principle according to several additional applications of the invention.
  • Figure 5 shows amplitude curves of the damper at the frequency level with different parameter values according to several applications of the invention.
  • Figure 6 shows the effect of the roll vibration damper tuning parameters on the frequency response.
  • Figure 1 shows a delayed resonator according to several applications of the invention in a fibrous web machine.
  • Figure 2 shows a magnification according to several applications of the invention of the principle of a delayed resonator in a fibrous web machine of Figure 1.
  • Figure 2 (and also 1 ) shows the system to be damped, such as a roll, i.e. the primary system 120, the mass of which is m12.
  • the primary system 120 is fastened to the base 100, i.e. to another structure with a force of F dist 123, the joint of which between the fastening/other structure and primary system 120 can be simplified using a spring 121 with a spring constant k12, as well as a damper 122 with a damping constant c12.
  • the base can be, for example, the frame structure, another roll, the nip between the rolls through which the fibrous web is run, or a corresponding structure.
  • the primary system 120 is connected to a vibrator 110, the mass of which is m11.
  • a spring 111 with a spring constant of k11 and a damper 112 with a damping constant c11 are part of this connection.
  • An actuator 113 which can be electric, electromagnetic, piezoelectric, magnetostrictive, hydraulic, pneumatic or equivalent based on its operating principle, is also part of the connection.
  • the actuator is connected between the vibrator 110 and the primary system 120.
  • the control circuit also comprises a controller 140, which includes a delay 141 and amplifier 142.
  • the controller 140 received is an input control signal from sensor 115, e.g. from a speed sensor or a so-called vibration sensor.
  • the output control voltage from controller 140 is fed into the actuator 113 via amplifier 116.
  • FIG. 3 shows an example of a control circuit presented in the principle circuit according to several additional applications of the invention.
  • the figure shows a system to be damped, such as a roll, i.e. the primary system 220, the mass of which is m22.
  • the primary system 220 is fastened to the base 200, i.e. to another structure with a force of F dist 223, the joint of which between the fastening/other structure and primary system 220 can be simplified using a spring 221 with a spring constant k22, as well as a damper 222 with a damping constant c22.
  • the primary system 220 is connected to a vibrator 210, the mass of which is m21.
  • a spring 211 with a spring constant of k21 and a damper 212 with a damping constant c21 are connected to this.
  • the actuator is connected to the vibrator 210 so that the load sensor 214 is located between the actuator and vibrator 210.
  • the control circuit also includes a controller 240, which has a delay 241 , e.g., resistance, an amplifier 242, a PID controller 243 and an operator 244.
  • the controller receives its input control signal from the load sensor 214 and speed sensor 215, while the output control voltage is fed into actuator 213 via amplifier 216.
  • Control circuits 140, 141 , 142, 166, 133, 155, 240, 241 , 242, 243, 244, 213, 214, 215, 216 in several application possibilities of the invention have been devised for making a cascade connection.
  • a second control circuit can be suitably mounted inside the first control circuit so that two nested circuits are connected for control on the basis of the delayed resonator principle.
  • Figure 4 shows delayed resonator control based on the cascade control principle according to several additional applications of the invention where the outermost is speed control circuit 301 and the innermost is load control circuit 302.
  • Several applications of the invention also include a type of control with which problems related to the actuator producing the load are avoided.
  • the speed is measured with speed sensor 215, which along with control circuit 240 forms speed control circuit 301 , the so-called outermost control circuit.
  • load measurement 214 is added between the actuator Fv producing the mass and load. With this load measurement a second innermost control circuit 320, or so-called load control circuit, is implemented.
  • the delayed and amplified speed signal is not fed directly to the actuator Fv producing the load, but is fed as a standard value to the innermost load control circuit 302.
  • Such a double nested control circuit, 301 , 302 is called cascade control. It gives the following benefits: • Problems can be eliminated with the innermost control circuit 302 so these do not impair the operation of the outermost control circuit 301.
  • a loss of rigidity in the actuator occurs, for example, when the amplification (gain) of outer circuit 301 is set to zero, the load control of the inner load control circuit 302 becomes zero.
  • inner control circuit 302 maintains the zero load between the mass and actuator so that the damper operates as though there was no actuator.
  • the delay and gain of the delayed resonator can be calculated so that the damper and the characteristic frequency of the damper can be controlled separately.
  • the obtained delay and gain values thus place the poles of the system on the imaginary axis.
  • Tc _ - atan(&0n n 6 2 - k n + m u a 2 ) /(c u b 2 + _ m u a 3 + c u a 2 + ak n + am u b 2 )) + n ⁇
  • the relative damping is 5%, so that
  • Figure 5 shows the amplitude curves of the clamper at the frequency level with different parameter values (passive damper (no control) - 401, adjusted damper resonance frequency 125 Hz and 1% damping - 402, adjusted damper resonance frequency 125 Hz and 5% damping - 403, adjusted damper resonance frequency 125 Hz and 10% damping - 404).
  • Curve 401 shows the amplitude of the damper as a function of frequency without control. The maximum amplitude is obtained at the characteristic frequency of 120 Hz.
  • the damper has been adjusted to the 125 Hz frequency with three different damping points.
  • Curves 402, 403 and 404 present these received responses with three different dampings. This shows that the damping can also be controlled without affecting the characteristic frequency.
  • Figures 6A to 6D show the frequency response function of the structure to be damped from the primary system, e.g. from the bearing housing of the roll in the nip direction.
  • the horizontal axis is the frequency and the vertical axis is displacement/load.
  • Resonance without a clamper is represented by a dashed line and the solid line represents the resonance with a damper.
  • Figures 6A and 6B show the effect of the mass.
  • Figure 6A has a large damper mass, with widely spaced peaks
  • Figure 6B has a small mass, with the peaks close to each other.
  • the damper must be tuned so that the barring frequency is in the troughs between the peaks, i.e. where the response is small. With a small mass, small tuning deviations considerably increase the response.
  • Figures 6C and 6D show the effect of the mass.
  • the damper's own damping is large, in which the trough between two peaks is flat and the bottom of the trough is not so deep.
  • the damping in Figure 6D is small and the trough's bottom is deep.
  • the damper mass be as small as possible.
  • the tuning accuracy must be as good as possible and the damping as small as possible so that the wave trough shown in Figures 6A to 6D is as deep as possible, i.e. the roll vibration damper operates as efficiently as possible.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Paper (AREA)
  • Vibration Prevention Devices (AREA)
  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)

Abstract

L'invention concerne un dispositif de vibration configurée pour vibrer à une fréquence correspondant à une fréquence de vibration souhaitée devant être amortie du système primaire (120, 220), tel qu'une fréquence de blocage, de telle sorte que les vibrations en question peuvent être contrôlées par des circuits de commande basés sur un résonateur retardé pour amortir une vibration de roulis d'une machine à bande fibreuse. Une vibration de roulis peut ainsi être significativement amortie dans le système primaire d'une machine à bande fibreuse. La réduction de vibrations de roulis peut être automatique ou à autoajustement, et ainsi une commande manuelle n'est pas nécessairement requise. En outre, une réduction de vibrations de roulis relativement précise est possible, c'est-à-dire que la fréquence de ce que l'on appelle un contre-vibreur compense de façon précise la vibration nuisible du vibreur principal réel.
PCT/FI2007/000188 2006-07-05 2007-07-05 Procédé et dispositif pour amortir une vibration de roulis WO2008003820A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
ATA9299/2007A AT506025B1 (de) 2006-07-05 2007-07-05 Verfahren und vorrichtung zur dämpfung von walzenschwingungen
DE112007001589T DE112007001589T5 (de) 2006-07-05 2007-07-05 Verfahren und Vorrichtung zur Dämpfung von Walzenschwingungen

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20060653A FI118741B (fi) 2006-07-05 2006-07-05 Menetelmä telavärähtelyn vaimentamiseksi ja terävärähtelyn vaimennin
FI20060653 2006-07-05

Publications (2)

Publication Number Publication Date
WO2008003820A2 true WO2008003820A2 (fr) 2008-01-10
WO2008003820A3 WO2008003820A3 (fr) 2008-02-28

Family

ID=36758261

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/FI2007/000188 WO2008003820A2 (fr) 2006-07-05 2007-07-05 Procédé et dispositif pour amortir une vibration de roulis

Country Status (4)

Country Link
AT (1) AT506025B1 (fr)
DE (1) DE112007001589T5 (fr)
FI (1) FI118741B (fr)
WO (1) WO2008003820A2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8372245B2 (en) 2009-03-18 2013-02-12 Metso Paper, Inc. Roll assembly for a fiber-web machine and method of attenuating vibration of a fiber-web machine roll
EP2754750A1 (fr) * 2013-01-11 2014-07-16 Valmet Technologies, Inc. Agencement pour commander les vibrations dans une machine à bande fibreuse et amplificateur de mouvement linéaire

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102494071B (zh) * 2011-11-15 2013-12-11 江苏大学 一种被动天棚和地棚阻尼隔振系统

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5431261A (en) * 1994-05-12 1995-07-11 University Of Connecticut Delayed resonators as active dynamic absorbers
EP1015685A1 (fr) * 1997-01-07 2000-07-05 Ecopump Oy Procede servant a regler la consistance d'une pate a papier

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19605416B4 (de) 1996-02-14 2004-05-13 Schröder, Dierk, Prof. Dr.-Ing. Dr.-Ing. h.c. Linearer Aktiver Resonator (LAR)
FI101320B1 (fi) * 1997-04-30 1998-05-29 Valmet Corp Menetelmä ja laitteisto värähtelyn vaimentamiseksi paperikoneessa tai paperin jälkikäsittelylaitteessa
EP1013203B1 (fr) 1998-12-18 2002-02-27 Unilever Plc Système pour préparer des boissons
DE10204763A1 (de) 2002-02-05 2003-08-14 Kuesters Eduard Maschf Verfahren zur aktiven Dämpfung von Schwingungen in einer Vorrichtung zum Bearbeiten einer laufenden Bahn, zum Durchführen dieses Verfahrens geeignete Vorrichtung sowie zum Einsatz in dieser Vorrichtung geeignete Walze

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5431261A (en) * 1994-05-12 1995-07-11 University Of Connecticut Delayed resonators as active dynamic absorbers
EP1015685A1 (fr) * 1997-01-07 2000-07-05 Ecopump Oy Procede servant a regler la consistance d'une pate a papier

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8372245B2 (en) 2009-03-18 2013-02-12 Metso Paper, Inc. Roll assembly for a fiber-web machine and method of attenuating vibration of a fiber-web machine roll
EP2754750A1 (fr) * 2013-01-11 2014-07-16 Valmet Technologies, Inc. Agencement pour commander les vibrations dans une machine à bande fibreuse et amplificateur de mouvement linéaire

Also Published As

Publication number Publication date
WO2008003820A3 (fr) 2008-02-28
FI118741B (fi) 2008-02-29
FI20060653A (fi) 2008-01-06
AT506025B1 (de) 2013-04-15
DE112007001589T5 (de) 2009-05-20
AT506025A3 (de) 2013-02-15
AT506025A2 (de) 2009-05-15
FI20060653A0 (fi) 2006-07-05

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