EP1956137A2 - Rouleau compresseur - Google Patents

Rouleau compresseur Download PDF

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Publication number
EP1956137A2
EP1956137A2 EP07150133A EP07150133A EP1956137A2 EP 1956137 A2 EP1956137 A2 EP 1956137A2 EP 07150133 A EP07150133 A EP 07150133A EP 07150133 A EP07150133 A EP 07150133A EP 1956137 A2 EP1956137 A2 EP 1956137A2
Authority
EP
European Patent Office
Prior art keywords
axis
pressing direction
press
frequency
natural 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.)
Withdrawn
Application number
EP07150133A
Other languages
German (de)
English (en)
Other versions
EP1956137A3 (fr
Inventor
Thomas Baumeister
Irmgard Hawix-Bolz
Jochen Autrata
Rolf Dr. 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 EP1956137A2 publication Critical patent/EP1956137A2/fr
Publication of EP1956137A3 publication Critical patent/EP1956137A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • D21F3/0209—Wet presses with extended press nip
    • D21F3/0218—Shoe presses
    • 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
    • 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

Definitions

  • the invention relates to a press roll for treating a paper, cardboard, tissue or other fibrous web in a machine for producing and / or finishing the same, with a, about a fixed, preferably one-piece axis rotatable roll shell, which of a support means of the axis is pressed to form a press nip in the direction (pressing direction) of a counter-pressure element, wherein the frequency of the press nip passes of the roll mantle is below the natural frequency of the axis in the pressing direction.
  • the axes of press rolls in particular of deflection-controlled press rolls, have enormous dimensions and thus also a very high weight because of the high press forces in the press nip and the length of often more than 10 m.
  • the high weight of the axle can easily exceed the capacity of available hoists in the area of the machine.
  • the object of the invention is therefore to reduce the weight of the axle while ensuring a sufficient load capacity and vibration stability.
  • this object is achieved in that the natural frequency of the axis is transverse to the pressing direction below the natural frequency of the axis in the pressing direction and at least one stiffening element is attached to the axis, which increases the rigidity of the axis transverse to the pressing direction.
  • the axis is associated with at least one damping element which dampens vibrations transversely to the pressing direction.
  • a counter-pressure element is particularly suitable a counter roll or a press belt.
  • a cross-section is chosen here whose surface moments in the two main axes of inertia in and across the pressing direction are different, preferably greatly different.
  • the dimensioning of the cross section in the pressing direction is determined by the load, in particular due to the pressing forces in the press nip and the weight and the required natural frequency in the pressing direction.
  • the required natural frequency of the axis also depends on the rotational speed of the roll mantle, i. the machine speed.
  • the load of the axis in the pressing direction is substantially greater than transverse to it, it is often sufficient for the natural frequency of the axis in the pressing direction to be at least 100%, preferably at least 150% higher, than transverse to the pressing direction.
  • the lower natural frequency of the axis transverse to the pressing direction leads to a smaller extension of the axis connected transversely to the pressing direction with a lower weight of the axis. This is also possible because of the lower forces acting on the axle transversely to the pressing direction.
  • the frequency of the press nip passes of the roll mantle during operation should be at least 15%, preferably at least 25% and in particular at least 30% smaller than the natural frequency of the axis in the pressing direction be.
  • the excitation frequency is not or at least only a short time in the range of the natural frequency of the axis.
  • the frequency of the press nip passes of the roll shell should be at least 15%, preferably at least 25% and in particular at least 30% above the natural frequency of the axis transverse to the pressing direction during operation of the machine.
  • the excitation frequency i. the frequency of the press nip passes of the roll shell during operation always between the natural frequency of the axis in and across the pressing direction.
  • the invention thus makes use of the finding that the dimensioning of the axis transversely to the pressing direction has so far mainly been determined by the exciter frequency and much less by the bending stress.
  • this allows the expansion in the pressing direction to be at least 2.5 times, preferably at least 3 times, greater than transverse to the pressing direction.
  • a higher natural frequency in the pressing direction than transverse to the pressing direction can be achieved with advantage by axes with T-profile cross-section.
  • the damping element should be formed by a, preferably on the axis or a stiffening element supporting, hydraulic cylinder, which is pressed transversely to the pressing direction against the inner surface of the roll shell. Vibrations between the axis and the roll shell are damped by the hydraulic pressure chamber.
  • the natural frequency of the axis together with the stiffening element transverse to the pressing direction should be at least 20% above the maximum frequency of the press nip passes of the roll shell during operation.
  • At least one stiffening element should be firmly connected to the axle.
  • At least one stiffening element is connected with play with the axle. In this case, about the game between Stiffener and axle movements allowed to dampen the vibrations.
  • the stiffening element simultaneously acts as a damping element.
  • the axis is made of metal, preferably forged steel.
  • deflection-controlled press roller has a rotatable about a fixed axis 2, cylindrical roll shell 1 made of steel.
  • the roll shell 1 is supported on a hydraulic support device 3 on the axis 2.
  • This supporting device 3 compensates for the deflection of the roll shell 1 and also presses it in the pressing direction 6 to the opposite counter roll 4.
  • the resulting nip the fibrous web 5 can be performed for smoothing alone or together with at least one water-absorbing tape for drainage.
  • the gap between the here convex support surface of the support device 3 and the roll shell 1 can be lubricated hydrostatically and / or hydrodynamically.
  • the excitation frequency corresponds to the frequency of the jacket revolutions and thus depends on the rotational speed of the roll shell 1 and thus the machine speed.
  • the vibrations occur in particular due to imbalances of the roll shell. 1
  • the one-piece axles 2 made of forged steel can well be over 10 m long, it comes alone by the weight to a considerable load on the axis 2.
  • the pressing forces of the support means 3, which as here in upwardly directed support surface axis 2 load together with the weight against the pressing direction 6.
  • the natural frequency is below the natural frequency in the pressing direction, in particular even below the exciter frequency.
  • the weight of the axle 2 can be substantially reduced without compromising the stability, in particular the vibration stability.
  • the natural frequency across the pressing direction 6 is set at 20% below the minimum excitation frequency which results at the minimum operating speed V min of the machine. Also, as in FIG. 2 to see the natural frequency a in the pressing direction 6 20% above the maximum exciter frequency, which is set at maximum operating speed V max of the machine.
  • the Natural frequency of the axis in the pressing direction 6 must be three times higher than transverse to the pressing direction 6.
  • the area moment in the pressing direction 6 must be nine times greater than the area moment transverse to the pressing direction 6.
  • press roller is double-acting, which is why two opposite support means 3 press the roll shell 1 up and down to a counter-roller 4.
  • the axis 2 has a rectangular cross-section with the long sides parallel to the pressing direction 6. This results in a high natural frequency and a high load capacity in the pressing direction 6, but a reduced natural frequency transverse to the pressing direction. 6
  • the load capacity of the axis 2 is transversely to the pressing direction by a plurality of laterally distributed transversely to the pressing direction 6 on the axis 2 and attached thereto stiffening elements 8 in the form of half shells.
  • the half-shell shape reduces the gap to the roll shell 1, which has a positive effect on the lubricating fluid requirement of the press roll.
  • stiffening elements 8 each have a damping element 7 in the form of a hydraulic cylinder resting on the respective stiffening element 8, which is pressed transversely to the pressing direction 6 against the inner surface of the roll shell 1.
  • the natural frequency of the axle 2 with the stiffening elements can be raised above the excitation frequency via the gradient elements 8, without substantially increasing the weight of the axle 2.
  • the natural frequency can be raised by the stiffening elements 8 sufficiently high above the excitation frequency, it can be dispensed with the damping elements 7, as in the case of the embodiments of FIGS. 4 to 10 the case is.
  • FIGS. 4 to 8 are shown differently designed, in particular easy to produce stiffening elements 8, which are fixedly attached to the axis 2. Their design also depends on the cross-sectional shape of the axis 2.
  • axles 2 here I T, double T-beam and cylinder are used.
  • stiffening elements 7 are connected with play with the axis 2. This allows minimal movements between axis 2 and stiffening element 7, which leads to the damping of vibrations.

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  • Paper (AREA)
EP07150133A 2007-02-12 2007-12-19 Rouleau compresseur Withdrawn EP1956137A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200710006743 DE102007006743A1 (de) 2007-02-12 2007-02-12 Presswalze

Publications (2)

Publication Number Publication Date
EP1956137A2 true EP1956137A2 (fr) 2008-08-13
EP1956137A3 EP1956137A3 (fr) 2009-07-22

Family

ID=39364023

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07150133A Withdrawn EP1956137A3 (fr) 2007-02-12 2007-12-19 Rouleau compresseur

Country Status (2)

Country Link
EP (1) EP1956137A3 (fr)
DE (1) DE102007006743A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008000155A1 (de) 2008-01-25 2009-07-30 Voith Patent Gmbh Presswalze
DE102013210496A1 (de) 2013-06-06 2014-12-11 Voith Patent Gmbh Walze und Herstellung einer Walzenachse

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005090802A1 (fr) 2004-03-23 2005-09-29 Metso Paper, Inc. Structure interieure allongee de rouleau de machine a papier/carton ou de machine de finissage

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005090802A1 (fr) 2004-03-23 2005-09-29 Metso Paper, Inc. Structure interieure allongee de rouleau de machine a papier/carton ou de machine de finissage

Also Published As

Publication number Publication date
DE102007006743A1 (de) 2008-08-14
EP1956137A3 (fr) 2009-07-22

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