EP1876293A1 - Atténuation de vibrations - Google Patents

Atténuation de vibrations Download PDF

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Publication number
EP1876293A1
EP1876293A1 EP07107621A EP07107621A EP1876293A1 EP 1876293 A1 EP1876293 A1 EP 1876293A1 EP 07107621 A EP07107621 A EP 07107621A EP 07107621 A EP07107621 A EP 07107621A EP 1876293 A1 EP1876293 A1 EP 1876293A1
Authority
EP
European Patent Office
Prior art keywords
smoothing
correction
roll
frequency
vibrations
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
EP07107621A
Other languages
German (de)
English (en)
Other versions
EP1876293B1 (fr
Inventor
Jochen Dr. Niemann
Rolf Dr. Van Haag
Volker Schölzke
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 EP1876293A1 publication Critical patent/EP1876293A1/fr
Application granted granted Critical
Publication of EP1876293B1 publication Critical patent/EP1876293B1/fr
Not-in-force 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
    • D21G1/0073—Accessories for calenders
    • D21G1/008—Vibration-preventing or -eliminating devices

Definitions

  • the invention relates to a method for damping vibrations in a smoothing arrangement with a plurality of smoothing rollers for smoothing a paper, cardboard or other fibrous web in a machine for producing and / or finishing the same, in which the fibrous web by at least one of two pressed against each other smoothing rollers formed smoothing gap is performed, wherein at least one smoothing roller of the smoothing arrangement is driven and at least one smoothing roll has an elastic roll cover or elastic roll shell.
  • the invention also relates to a device for damping vibrations in a smoothing arrangement with several smoothing rollers for smoothing a paper, cardboard or other fibrous web in a machine for producing and / or finishing the same, in which the fibrous web by at least one, of two against each other pressed Glättwalzen formed smoothing gap is performed, wherein at least one smoothing roller of the smoothing arrangement is connected to a drive and at least one smoothing roller has an elastic roll cover or elastic roll shell.
  • resonance phenomena In connection with the formation of axial stripes in the paper (thickness, gloss, smoothing stripes) of multi-roll calenders, vibrations often occur which are referred to as resonance phenomena.
  • the resonance phenomenon develops within a few minutes under considerable noise (> 100 dBA) and at the same time produces stripes in the paper.
  • These resonance phenomena depend on the line force, the calendering speed and the type of paper produced. A higher line force tends to reduce the influence of the resonance, while a higher speed and / or a higher basis weight increase the undesired influence of the resonance.
  • the stripes form in response to a vibrational excitation, as opposed to the phenomenon otherwise called barring, directly on the paper.
  • the vibrations do not create a polygon pattern on the plastic coating of flexure compensation and Center rollers, since this is not an integer multiple of the rotational frequency of a roller in the multi-roll calender.
  • the object of the invention is therefore to damp these vibrations.
  • the object with regard to the method has been solved by measuring the vibrations in at least one smoothing roll and by a correction drive at least one smoothing roll correction torques are introduced at a frequency that corresponds to the frequency or a multiple of the frequency of the measured vibrations, or at least be initiated with a frequency that leads to a reduction of the vibrations.
  • the frequency of the correction torques should be controlled so that there is a minimum in the vibrations.
  • the oscillations in resonance phenomena are thus characterized by a combination of oscillations in the nip direction and transverse to the nip direction in a relatively narrow frequency band of a few hearts in the range of 200 to over 1000 Hz.
  • the amplitude of the correction torques should be increased so far, until a minimum in the vibrations sets or the oscillations even disappear completely.
  • the frequency of the correction torques should also be between 200 and 1000 Hz.
  • correction drive is selected so strong drive that it can be used at the same time for the drive of the corresponding smoothing roller.
  • At least one smoothing roll is assigned a vibration meter for detecting vibrations of the smoothing roller and at least one smoothing roller a correction drive for the introduction of high-frequency correction torques, wherein the vibration meter and the correction drive are connected to a control unit ,
  • a correction drive is particularly suitable a synchronous motor, which is preferably controlled by a frequency converter.
  • the correction drive should be driven directly, i. be connected without an intermediate gear with the pin or the axis of the smoothing roll.
  • This special electric motor should be equipped with a very fast working frequency converter, which also works in the frequency range of the resonance phenomenon of about 200 to more than 1000Hz.
  • a high-frequency torque pulsating with the resonance frequency is now introduced into the roll neck or the roll axis and thus into the smoothing roll arrangement.
  • the introduction of a high-frequency torque with the inverse amplitude of the same frequency of the smoothing roller arrangement can also be advantageous.
  • the amplitude and phase of the introduced high-frequency correction torque should be controlled, for which purpose a measurement of the roller vibration is preferably carried out at least two smoothing rollers.
  • the measurement of the oscillations of the smoothing roll can be done directly with eddy current, laser technology or accelerometers.
  • An indirect vibration measurement is possible via a measurement of the motor current of the drive of the smoothing roller.
  • a frequency converter is used to control the direct drive.
  • this high resolution motor current measurement is detected directly with an integrated diagnostic tool in the frequency converter and stored as a reference value over a certain period of time (e.g., 1 minute).
  • a diagnostic tool integrated in the frequency converter is more accurate and faster than an external measuring device.
  • the amplitudes thus determined are then used in inverse form for vibration prevention.
  • the fast-acting correction drive must not be designed in terms of its performance on the drive power of the smoothing roller, but this is also possible. In the latter case, the correction drive also acts as a normal drive of the smoothing roller at the same time.
  • smoothing arrangements which are formed by more than two smoothing rollers, wherein the smoothing rollers are preferably arranged one above the other in a stacking plane.
  • the correction drive should be connected to a smoothing roll, which forms a smoothing gap with two smoothing rollers, i. a center roll of the roll stack.
  • correction drives can also be provided on several smoothing rollers.
  • the figure shows a schematic cross section through a calender arrangement, which serves to smooth the fibrous web 1 and is located at the end of a production machine.
  • the calender is formed by a stack of 8 superposed smoothing rollers 2,3,4, which are held by a stand of the calender.
  • the fibrous web 1 passes through the smoothing column from top to bottom, wherein the fibrous web 1 is guided between the smoothing columns on guide rollers, not shown here. After the calender, the fibrous web 1 is guided to a winding device 9 immediately following in the web running direction.
  • the stack is limited by an upper and a lower end smoothing roll 2.
  • These end smoothing rollers 2 are designed as deflection adjustment rollers with a roll jacket supported on a support held in a rotationally fixed manner by means of a deflection adjustment device.
  • the deflection adjustment is in each case formed by a plurality of axially juxtaposed and hydraulically compressible support piston, the Press the rotatable roll shell in the stacking and pressing plane to the opposite end smoothing roll 2.
  • the smoothing rollers 3 with elastic reference, each forming with the end smoothing rollers 2 the first or last calendering slit of the calender, each associated with a drive 5.
  • all smoothing rolls 2, 3, 4 have a drive 5, which allows the insertion of the fibrous web 1 through the open smoothing nip and the subsequent closing of the smoothing nips.
  • the three upper smoothing rolls 2,3,4 are associated with vibration meter 7 for detecting the vibrations occurring in and across the pressing direction in the nip.
  • vibration meter 7 for detecting the vibrations occurring in and across the pressing direction in the nip.
  • the measured values of the vibration meters 7 are transmitted to the control unit 8 and evaluated there.
  • a correction drive 6 is present in each case on the three upper smoothing rollers 2, 3, 4.
  • These correction drives 6 are designed as electric synchronous motors and connected directly to the roll neck of these smoothing rolls 2, 3, 4.
  • the synchronous motors have very fast operating frequency, which are controlled by the control unit 8.
  • correction torques are introduced into the smoothing rollers 4 for damping the vibrations via the correction drives.
  • the frequency of the correction torques corresponds approximately to the frequency or a multiple of the frequency measured by the vibration meters 7.
  • the correction drives 6 must be designed only for the application of the correction torques.
  • the drive of the calender could also be effected via these and / or correction torques could be introduced via the drives 5 of the smoothing rollers 2, 3, 4.
  • the axial stripes in the fibrous web 1 can be prevented or at least reduced so effectively and simply.

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  • Paper (AREA)
  • Golf Clubs (AREA)
EP07107621A 2006-07-05 2007-05-07 Atténuation de vibrations Not-in-force EP1876293B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006031022A DE102006031022A1 (de) 2006-07-05 2006-07-05 Schwingungsdämpfung

Publications (2)

Publication Number Publication Date
EP1876293A1 true EP1876293A1 (fr) 2008-01-09
EP1876293B1 EP1876293B1 (fr) 2011-01-19

Family

ID=38461953

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07107621A Not-in-force EP1876293B1 (fr) 2006-07-05 2007-05-07 Atténuation de vibrations

Country Status (3)

Country Link
EP (1) EP1876293B1 (fr)
AT (1) ATE496171T1 (fr)
DE (2) DE102006031022A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008138692A1 (fr) * 2007-05-09 2008-11-20 Voith Patent Gmbh Procédé et dispositif de compensation des fluctuations périodiques d'un couple
EP2034092A3 (fr) * 2007-09-04 2011-09-21 Voith Patent GmbH Agencement de cylindres

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999004181A2 (fr) * 1997-07-15 1999-01-28 Lord Corporation Procede et appareil anti-vibrations pour cylindres de calandre et analogue
EP0949378A1 (fr) * 1998-04-06 1999-10-13 Voith Sulzer Papiertechnik Patent GmbH Machine à rouleaux et son procédé de fonctionnement
EP1333122A2 (fr) * 2002-02-05 2003-08-06 Eduard Küsters Maschinenfabrik GmbH & Co. KG Méthode d'amortissement actif de vibrations
EP1516955A1 (fr) * 2003-09-19 2005-03-23 Eduard Küsters Maschinenfabrik GmbH & Co. KG Calandre
EP1746204A2 (fr) * 2005-05-18 2007-01-24 Voith Patent GmbH Procédé pour réduire les vibrations dans les machines à papier

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999004181A2 (fr) * 1997-07-15 1999-01-28 Lord Corporation Procede et appareil anti-vibrations pour cylindres de calandre et analogue
EP0949378A1 (fr) * 1998-04-06 1999-10-13 Voith Sulzer Papiertechnik Patent GmbH Machine à rouleaux et son procédé de fonctionnement
EP1333122A2 (fr) * 2002-02-05 2003-08-06 Eduard Küsters Maschinenfabrik GmbH & Co. KG Méthode d'amortissement actif de vibrations
EP1516955A1 (fr) * 2003-09-19 2005-03-23 Eduard Küsters Maschinenfabrik GmbH & Co. KG Calandre
EP1746204A2 (fr) * 2005-05-18 2007-01-24 Voith Patent GmbH Procédé pour réduire les vibrations dans les machines à papier

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008138692A1 (fr) * 2007-05-09 2008-11-20 Voith Patent Gmbh Procédé et dispositif de compensation des fluctuations périodiques d'un couple
EP2034092A3 (fr) * 2007-09-04 2011-09-21 Voith Patent GmbH Agencement de cylindres

Also Published As

Publication number Publication date
ATE496171T1 (de) 2011-02-15
DE502007006286D1 (de) 2011-03-03
DE102006031022A1 (de) 2008-01-10
EP1876293B1 (fr) 2011-01-19

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