EP1956138B1 - Rouleau compresseur - Google Patents

Rouleau compresseur Download PDF

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Publication number
EP1956138B1
EP1956138B1 EP07150303A EP07150303A EP1956138B1 EP 1956138 B1 EP1956138 B1 EP 1956138B1 EP 07150303 A EP07150303 A EP 07150303A EP 07150303 A EP07150303 A EP 07150303A EP 1956138 B1 EP1956138 B1 EP 1956138B1
Authority
EP
European Patent Office
Prior art keywords
pressing direction
shaft
frequency
natural frequency
machine according
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.)
Not-in-force
Application number
EP07150303A
Other languages
German (de)
English (en)
Other versions
EP1956138A3 (fr
EP1956138A2 (fr
Inventor
Thomas Baumeister
Jochen Autrata
Rolf Dr. Van Haag
Irmgard Hawix-Bolz
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 EP1956138A2 publication Critical patent/EP1956138A2/fr
Publication of EP1956138A3 publication Critical patent/EP1956138A3/fr
Application granted granted Critical
Publication of EP1956138B1 publication Critical patent/EP1956138B1/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
    • 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 machine for producing and / or refining a paper, board, tissue or another fibrous web with a press roll having a roll shell which is rotatable about a fixed, preferably one-piece axis and which is supported by a support means of the axis to form a press nip is pressed in the direction (pressing direction) of a counter-pressure element, the frequency of the press nip passes of the roll shell during operation between minimum and maximum operating speed (V max ) below the natural frequency of the axis in the pressing direction, the natural frequency of the axis transverse to the pressing direction below the natural frequency of the axis lies in the pressing direction and the axis is associated with at least one damping element which dampens vibrations transversely to the pressing direction.
  • V max minimum and maximum operating speed
  • 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 sufficient load capacity and vibration stability.
  • the object has been achieved in that the frequency of the press nip passes of the roll shell during operation is between the minimum (v min ) and maximum operating speed (v max ) over the natural frequency of the axis transverse to the pressing direction. It is advantageous if at least one stiffening element is attached to the axle, which increases the rigidity 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 between minimum and maximum operating speed (V max ) should be at least 15%, preferably at least 25% and in particular be at least 30% smaller than the natural frequency of the axis in the pressing direction.
  • 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 25% and in particular at least 30% above the natural frequency of the axis transverse to the pressing direction during operation between minimum and maximum operating speed (V max ) of the machine.
  • the excitation frequency ie the frequency of the press nip passes of the roll shell during operation between minimum and maximum operating speed (V max ) is 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.
  • 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.
  • Half shells, square profiles or the like are particularly suitable as stiffening elements.
  • the natural frequency of the axis together with the stiffening element should be at least 20% greater than the transverse direction to the pressing direction maximum frequency of the press nip passes of the roll shell during operation are.
  • 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, movements are allowed by the play between the stiffening element and the axis, dampening 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-roller 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 area moments of inertia of the axis 2 in and across the pressing direction 6 must be designed accordingly. Since the design of the axles 2 at high machine speeds of more than 1500 m / min and lengths of more than 6 m is already characterized by the natural frequency and not by the compressive and gravitational forces, the axis 2 transverse to the pressing direction 6 due to the lower natural frequency also much narrower than in the pressing direction 6.
  • 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 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 excitation frequency, which sets 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.
  • 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 8 are connected with play with the axis 2. This allows minimal movements between axis 2 and stiffening element 8, which leads to the damping of vibrations.

Landscapes

  • Paper (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Press Drives And Press Lines (AREA)

Claims (14)

  1. Machine pour la fabrication et/ou le traitement d'une bande de papier, de carton, de papier tissu ou d'une autre matière fibreuse (5) avec un rouleau compresseur comportant une enveloppe de rouleau (1) apte à tourner autour d'un axe stationnaire (2), de préférence en une seule pièce, laquelle est pressée par un dispositif d'appui (3) de l'axe (2) en direction d'un élément de contre-pression (direction de pressage 6) pour former une fente de pressage, dans laquelle la fréquence des passages de l'enveloppe de rouleau (1) à travers la fente de pressage pendant le fonctionnement entre une vitesse de fonctionnement minimale (vmin) et une vitesse de fonctionnement maximale (vmax) se situe en dessous de la fréquence propre de l'axe (2) dans la direction de pressage (6), la fréquence propre de l'axe (2) transversalement à la direction de pressage (6) se situe en dessous de la fréquence propre de l'axe (2) dans la direction de pressage (6), et au moins un élément d'amortissement (7), qui amortit les vibrations transversalement à la direction de pressage (6), est associé à l'axe (2), caractérisée en ce que la fréquence des passages de l'enveloppe de rouleau (1) à travers la fente de pressage pendant le fonctionnement entre une vitesse de fonctionnement minimale (vmin) et une vitesse de fonctionnement maximale (vmax) se situe au-dessus de la fréquence propre de l'axe (2) transversalement à la direction de pressage (6).
  2. Machine selon la revendication 1, caractérisée en ce que la fréquence des passages de l'enveloppe de rouleau (1) à travers la fente de pressage pendant le fonctionnement entre une vitesse de fonctionnement minimale (vmin) et une vitesse de fonctionnement maximale (vmax) est inférieure d'au moins 15% à la fréquence propre de l'axe (2) dans la direction de pressage (6).
  3. Machine selon la revendication 1 ou 2, caractérisée en ce que la fréquence des passages de l'enveloppe de rouleau (1) à travers la fente de pressage pendant le fonctionnement entre une vitesse de fonctionnement minimale (vmin) et une vitesse de fonctionnement maximale (vmax) est inférieure d'au moins 25 %, de préférence d'au moins 30 %, à la fréquence propre de l'axe (2) dans la direction de pressage (6).
  4. Machine selon l'une quelconque des revendications précédentes, caractérisée en ce que la fréquence des passages de l'enveloppe de rouleau (1) à travers la fente de pressage pendant le fonctionnement entre une vitesse de fonctionnement minimale (vmin) et une vitesse de fonctionnement maximale (vmax) se situe au moins 15 % au-dessus de la fréquence propre de l'axe (2) transversalement à la direction de pressage (6).
  5. Machine selon l'une quelconque des revendications précédentes, caractérisée en ce que la fréquence des passages de l'enveloppe de rouleau (1) à travers la fente de pressage pendant le fonctionnement entre une vitesse de fonctionnement minimale (vmin) et une vitesse de fonctionnement maximale (vmax) se situe au moins 25 %, de préférence au moins 30 %, au-dessus de la fréquence propre de l'axe (2) transversalement à la direction de pressage (6).
  6. Machine selon l'une quelconque des revendications précédentes, caractérisée en ce que l'axe (2) présente une section transversale sensiblement rectangulaire, dans laquelle l'extension dans la direction de pressage (6) est au moins 2,5 fois, de préférence au moins 3 fois plus grande que transversalement à la direction de pressage (6).
  7. Machine selon l'une quelconque des revendications 1 à 5, caractérisée en ce que l'axe (2) présente un profil en double T.
  8. Machine selon l'une quelconque des revendications précédentes, caractérisée en ce que l'axe (2) est constitué de métal, de préférence d'acier.
  9. Machine selon l'une quelconque des revendications précédentes, caractérisée en ce qu'il se trouve au moins un élément de raidissement fixé sur l'axe, qui augmente la rigidité transversalement à la direction de pressage et en ce que les éléments de raidissement (8) sont réalisés sous la forme de demi-coquilles ou de profilés carrés.
  10. Machine selon l'une quelconque des revendications précédentes, caractérisée en ce que la fréquence propre de l'axe (2) muni de l'élément de raidissement (8) transversalement à la direction de pressage (6) se situe au moins 20 % au-dessus de la fréquence maximale des passages de l'enveloppe de rouleau (1) à travers la fente de pressage pendant le fonctionnement.
  11. Machine selon l'une quelconque des revendications précédentes, caractérisée en ce qu'au moins un élément de raidissement (8) est assemblé fixement à l'axe (2).
  12. Machine selon l'une quelconque des revendications précédentes, caractérisée en ce qu'au moins un élément de raidissement (8) est assemblé avec du jeu à l'axe (2).
  13. Machine selon l'une quelconque des revendications précédentes, caractérisée en ce qu'au moins un élément d'amortissement (7) est formé par un vérin hydraulique prenant appui de préférence sur l'axe (2) ou un élément de raidissement (8), et qui est pressé contre la surface intérieure de l'enveloppe de rouleau (1) transversalement à la direction de pressage (6).
  14. Application de la machine avec un rouleau compresseur selon l'une quelconque des revendications précédentes, caractérisée en ce que la bande de matière fibreuse (5) est guidée à travers la fente de pressage pour le satinage ou l'essorage.
EP07150303A 2007-02-12 2007-12-21 Rouleau compresseur Not-in-force EP1956138B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007006742A DE102007006742A1 (de) 2007-02-12 2007-02-12 Presswalze

Publications (3)

Publication Number Publication Date
EP1956138A2 EP1956138A2 (fr) 2008-08-13
EP1956138A3 EP1956138A3 (fr) 2009-07-29
EP1956138B1 true EP1956138B1 (fr) 2012-04-18

Family

ID=39364020

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07150303A Not-in-force EP1956138B1 (fr) 2007-02-12 2007-12-21 Rouleau compresseur

Country Status (3)

Country Link
EP (1) EP1956138B1 (fr)
AT (1) ATE554221T1 (fr)
DE (1) DE102007006742A1 (fr)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10122648A1 (de) * 2001-05-10 2002-11-28 Voith Paper Patent Gmbh Biegeausgleichswalze
FI119446B (fi) * 2004-03-23 2008-11-14 Metso Paper Inc Paperi-/kartonkikoneen tai jälkikäsittelykoneen telan sisäpuolinen pitkänomainen rakenne
DE102006062284A1 (de) * 2006-12-22 2008-06-26 Andritz Küsters GmbH & Co. KG Walze mit Schwingungsdämpfer sowie Verfahren zur Dämpfung von Schwingungen einer Walze

Also Published As

Publication number Publication date
ATE554221T1 (de) 2012-05-15
EP1956138A3 (fr) 2009-07-29
EP1956138A2 (fr) 2008-08-13
DE102007006742A1 (de) 2008-08-14

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