EP4581206B1 - Rouleau et appareil de presse - Google Patents

Rouleau et appareil de presse

Info

Publication number
EP4581206B1
EP4581206B1 EP23750609.2A EP23750609A EP4581206B1 EP 4581206 B1 EP4581206 B1 EP 4581206B1 EP 23750609 A EP23750609 A EP 23750609A EP 4581206 B1 EP4581206 B1 EP 4581206B1
Authority
EP
European Patent Office
Prior art keywords
roller
shell
casing
drive flange
gpa
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
EP23750609.2A
Other languages
German (de)
English (en)
Other versions
EP4581206A1 (fr
Inventor
Heiko Linder
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 EP4581206A1 publication Critical patent/EP4581206A1/fr
Application granted granted Critical
Publication of EP4581206B1 publication Critical patent/EP4581206B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • D21F5/00—Dryer section of machines for making continuous webs of paper
    • D21F5/18—Drying webs by hot air
    • D21F5/181—Drying webs by hot air on Yankee cylinder

Definitions

  • the invention relates to a roller for treating a material web according to the preamble of claim 1 and a press device for a material web according to the preamble of claim 13.
  • treatment nips In the production of material webs, such as textile webs, plastic films, metal webs, and especially fibrous webs like paper webs, the material web is frequently guided through so-called treatment nips to smooth, dewater, or compress the webs, for example.
  • treatment nips usually consist of a roller and a counter element – often a counter roller.
  • a flexure compensation roller comprises a rotatable roller shell and internal hydraulic support elements to exert pressure on the roller shell from the inside, thereby influencing the roller profile and consequently the nip profile.
  • Such bending compensation rollers are known in a variety of designs, materials and for various applications, and are described, for example, in the literature. EP1760194 B1 or EP 0 720 698 described.
  • MG machine glazed
  • the systems typically include a treatment nip formed by the Yankee cylinder and a bend compensation roller.
  • the application on the MG cylinder is particularly critical, as its deformation varies significantly depending on the steam temperature.
  • Steel cylinders are typically used, which are hard-coated for corrosion protection. Therefore, re-grinding the contour of the MG cylinder is extremely difficult or even impossible. Compensating for the deformations and thus leveling the treatment nip must therefore be achieved solely via the bending compensation roller.
  • conventional bending compensation rollers with a metallic casing cannot compensate for deformations within this wide range.
  • the power output of a hydraulically supported bending compensation roller is particularly high at high speeds. This power must be transferred to the plastic casing via an external drive. Experience has shown that known transmission methods, such as a bolted connection, do not work during continuous operation of the roller.
  • the purpose of the invention is to further develop the state of the art in such a way that the rollers can be operated in a permanently stable manner.
  • the object of the invention is achieved by a roller according to claim 1 and a pressing device according to claim 13. Further advantageous embodiments of the present invention are found in the dependent claims.
  • the object of the invention is achieved by a roller for treating a web of material, with a rotatable shell, wherein the roller has a plurality of has hydrostatic support elements that can exert a force on the inner circumference of the shell, the support elements being supported on a non-rotating axis passing through the shell.
  • a drive flange is provided on at least one, and in particular both, end faces of the roller to transmit drive power to the shell.
  • the shell is made of plastic material, while the drive flange(s) are made of a metallic material, in particular steel.
  • connection of the casing to the drive flange is realized wholly or partially via an adhesive bond.
  • Such a roller is a bending adjustment roller.
  • roller shells are typically bolted to the drive flange. This is also easily possible with classic bending adjustment rollers made of steel or cast iron. However, the inherent forces of a hydraulically supported bending compensation roller are very high, especially at high speeds. This would mean that a bolted connection between the metal drive flanges and the plastic shell would eventually damage the shell.
  • an adhesive bond is therefore provided to connect the casing to the drive flange.
  • This adhesive bond makes it possible to connect the drive flange to the casing over a flat area, instead of only at the screw points as with screw connections. This results in a more even load distribution on the casing during power transmission, thereby completely or largely preventing damage to the casing.
  • the adhesive surface extends around the entire circumference. This can be in the form of a closed ring or in the form of one or more spirals.
  • the adhesive surface extends at least 30 mm, and in particular at least 40 mm, in the longitudinal direction of the roller. This ensures a particularly durable adhesive bond as well as a particularly even load distribution across the sleeve during power transmission.
  • the drive flange can have a receptacle, for example a slot-shaped receptacle, into which the sleeve is inserted. The adhesive surface(s) can then be located inside this receptacle.
  • connecting elements such as connecting pins or locking pins
  • connecting pins or locking pins are provided to mechanically connect the jacket to the flange.
  • This can be advantageous, for example, to fix the jacket in the correct position while the adhesive dries, or if this is legally required as a safety measure.
  • pins do not cause the damage to the jacket known from screw connections, since the power is still transmitted entirely or predominantly via the adhesive bond.
  • the number of locking pins will usually be small, not exceeding 4, 8, or 12.
  • Suitable materials for the fasteners include, for example, metals, plastics or combinations thereof.
  • the connecting elements are advantageously arranged in the area of an adhesive surface of the adhesive joint.
  • the drive flanges can be connected to a drive, e.g. an electric motor, in a suitable manner, as is known in the usual way.
  • a drive e.g. an electric motor
  • the modulus of elasticity of the shell in the circumferential direction of the roller is larger, preferably twice as high, in particular at least five times as high, as in the longitudinal direction of the roller.
  • the modulus of elasticity of the shell in the longitudinal direction is a maximum of 50 GPa, preferably a maximum of 20 GPa.
  • the modulus of elasticity of the shell in the longitudinal direction is at least 5 GPa, preferably at least 10 GPa.
  • the elastic modulus of the shell is in the longitudinal direction in the range between 10 GPa and 20 GPa.
  • the roller can adapt very well to even significant changes in profile.
  • a correspondingly low modulus of elasticity in the circumferential direction is therefore unnecessary and generally even disadvantageous.
  • the relatively soft plastic sheath is very advantageous for leveling, it can cause problems elsewhere.
  • the underside of the sheath can deform under the load on the support elements and potentially be forced into the spaces between adjacent support elements. Such load breaks can later be visible in the produced material web.
  • the support elements are arranged along a row, with the distance between two adjacent support elements being less than 5 mm, especially between 1 mm and 2 mm. These small distances largely prevent load dips.
  • the width of the support elements in the circumferential direction is less than 100 mm, in particular 80 mm or less, since otherwise the Hydrostatic cracking may be impaired due to the shell deformation, which is significant compared to the metal.
  • the roller shell can be made entirely from or based on a thermosetting plastic, referred to here as thermoset, in which fillers and/or reinforcing particles may also be embedded.
  • thermoset thermosetting plastic
  • Such a thermosetting plastic is particularly suitable for use at relatively high operating temperatures, especially compared to a thermoplastic plastic.
  • the sheath may comprise or consist of a body made of a fiber-reinforced plastic, in particular a glass fiber reinforced plastic (GFRP) or a carbon fiber reinforced plastic (CFRP).
  • GFRP glass fiber reinforced plastic
  • CFRP carbon fiber reinforced plastic
  • the matrix material to be used has a glass transition temperature of >140°C, preferably >170°C, in order to ensure dimensional stability during the production of the roller covering.
  • Such bodies can be composed of several layers, in particular, with the fibers in the different layers being oriented differently.
  • the properties of the body or sheath can be precisely controlled.
  • a further advantage of using such fiber-reinforced plastics is that thermal deformation of the sheath can be largely avoided.
  • the jacket also includes a coating which provides the web-contacting surface of the roller, this coating being made in particular of a polyurethane.
  • the coating can be either hard or soft.
  • the hardness should be in the range of 10-20 P&J.
  • such a (glass) fiber reinforced roller shell acts like an insulator. This means that only a minimal amount of heat can be conducted through the shell from the inside to the outside, nor from the outside to the inside.
  • the body can comprise a fiber material and a matrix material, with heat-conducting elements, in particular aluminum particles, also being incorporated into the matrix material.
  • the heat-conducting elements allow heat to be dissipated through the body into the interior of the roller, where it can be carried away to the outside via internal oil cooling.
  • the jacket unlike, for example, the jacket of a shoe press—possesses inherent stiffness that prevents deflection vibrations perpendicular to the treatment nip and exhibits only minimal deflection when supported in journals. This can be achieved—in addition to a suitable winding structure of GRP and CFRP fibers—by ensuring a certain minimum jacket wall thickness.
  • the jacket should have a thickness of more than 20 mm, preferably more than 30 mm.
  • a pressing device for a material web in particular a paper web
  • the pressing device has a treatment nip
  • the assembly comprises a roller and a counter-roller. It is provided that the roller is designed according to one aspect of the invention.
  • pressing device is defined very generally. It encompasses the aforementioned combination of a (bending-adjusting) roller and a counter roller, which is a heated smoothing cylinder, in particular a Yankee cylinder or MG cylinder.
  • smoothing cylinder MG cylinder, and Yankee cylinder are used synonymously unless explicitly stated otherwise.
  • smoothing cylinders can, for example, have diameters of 3m to 8m.
  • the heated cylinder may have a surface comprising or consisting of a hard metal material, especially a tungsten carbide-cobalt hard metal or a cermet material.
  • the cylinder Due to the size of the Yankee cylinder and its steam filling, the cylinder often bulges. While the surface remains fixed at the end caps, it bulges outwards in the middle section. Furthermore, the Yankee cylinder is subject to thermal deformation, which leads to increased diameters, particularly at the edges. Without bend compensation from the counter roll, this would result in severe edge overloads. Especially with Yankee cylinders featuring a carbide coating, this deformation cannot be regularly corrected by grinding the cylinder when operating parameters change. Therefore, the nip must be compensated for by the bend adjustment roll. This is always the case, for example, when operating parameters, particularly steam pressure, are changed.
  • the bend adjustment roll Since the deformation of the Yankee cylinder can vary considerably depending on the type of paper being produced, the bend adjustment roll must be able to compensate for a wide range of nip disturbances. This can be achieved by means of a roller according to aspects of the invention and represents a This represents a significant customer benefit, as unwanted machine downtime can be avoided.
  • pressing device also encompasses other applications.
  • Calenders which are used to treat paper and textile webs, are one example.
  • the pressing device could be a film press with which a starch film is transferred to one or both sides of the material web.
  • bending adjustment rollers according to aspects of the present invention can be used in the area of so-called 'hard nip sizing'.
  • the bending adjustment roller and/or the counter roller can, in particular, have a hardness of more than 60 Shore D, especially between 80 and 95 Shore D.
  • Figure 1 shows a section of a roller 1 with a shell 2, which is designed to rotate about an axis 4 passing through the shell 2.
  • the axis 4 itself is not rotatable.
  • the rotation of the shell 2 can be effected by means of bearings 11 known per se, for example ball bearings 11 or roller bearings.
  • a plurality of hydraulic support elements 3 are supported on the stationary axis 4. These elements can exert a force on the inner circumference of the shell. This force causes a deformation of the shell 2, allowing the roller profile to be precisely adjusted.
  • the support elements 3 are advantageously arranged in a row, with the distance ⁇ between two adjacent support elements 3 being less than 5 mm, particularly between 1 mm and 2 mm. These small distances ⁇ largely prevent load dips between the support elements 3.
  • the width of the support elements 3 in the circumferential direction is preferably less than 100mm, in particular 80mm or less.
  • the roller 1 further has a drive flange 5.
  • This drive flange 5 accommodates the shell 2 and transmits the power of an external drive (not shown in the figure) to the shell 2.
  • the drive flange(s) 5 are made of a metallic material, in particular steel.
  • the casing 2, on the other hand, is made of a plastic material.
  • the exemplary jacket 2 comprises, for example, a body made of a fiber-reinforced plastic, in particular a glass fiber-reinforced and/or carbon fiber-reinforced plastic.
  • Such fiber-reinforced plastics generally have a fiber material and a matrix material, whereby particles such as heat-conducting elements, in particular aluminum particles, may also be incorporated into the matrix material.
  • this jacket 2 includes a coating 12, which provides the web-contacting surface of the roller 1, and which may in particular be made of polyurethane.
  • connection between the casing 2 and the drive flange 5 is achieved here via an adhesive bond.
  • An adhesive is applied to an adhesive surface 6.
  • the adhesive bond makes it possible to connect the drive flange 5 to the casing 3 over its entire surface, instead of only at the screw points as with screw connections. This results in a more even load distribution on the casing 2 during power transmission, thus preventing or largely preventing damage to the casing 2.
  • the drive flange 5 can, for example, be configured as shown in Figure 1
  • the figure shown has a receptacle, preferably a slot-shaped receptacle, into which the sheath 2 is inserted.
  • the adhesive surface 6 or adhesive surfaces 6, 6a can then be located inside this receptacle.
  • the adhesive surface 6 of the adhesive joint is relatively large and evenly distributed over the circumference of the jacket 2 or the drive flange 5.
  • the adhesive surface 6 extends around the entire circumference. This can be realized in the form of a closed ring or in the form of one or more spirals.
  • the adhesive surface 6 extends in the longitudinal direction L of the roller 1 over at least 30 mm, in particular at least 40 mm. This allows for a particularly durable adhesive bond as well as a particularly uniform load distribution on the casing 2 during power transmission.
  • roller 1 on the opposite driver or drive side can be designed analogously, in particular with regard to the mounting of the jacket 2 in the corresponding drive flange 5.
  • FIGS. 2a and 2b The figures show alternative realizations of the connection between drive flange 5 and casing 2 and correspond approximately to the region within the dashed circle.
  • Figure 1 During the execution of the Figure 2a
  • an additional locking pin 7 is provided. This is inserted into a bore through the drive flange 5 and the casing 2.
  • the locking pin 7 is located in the area of the adhesive surface 6.
  • the locking pin 7 can also be bonded to ensure a secure fit in the bore.
  • Figure 2b Figure 1 shows an embodiment in which a second adhesive surface 6a is provided. This second adhesive surface 6a can be used as shown in Figure 2.
  • Figure 2b in combination with a locking pin 7, or alternatively thereto.
  • Figure 3 shows a press device 10 according to a further aspect of the invention.
  • the press device comprises a roller 1 according to another aspect of the invention.
  • a Yankee cylinder 8 is shown here as the counter roller 8.
  • Roller 1 and Yankee cylinder 8 form the treatment nip 9 for the material web 9, in particular a paper web 9.
  • the Yankee cylinder 8 is a cylinder heated—usually with steam—for example, a steel cylinder, the cylinder having a surface that often comprises or consists of a hard metal material, in particular a tungsten carbide-cobalt hard metal or a cermet material.
  • the cylinder 8 Due to the size of the Yankee cylinder 8, which can have a diameter of 3m to 8m, and the filling with steam, the cylinder 8 experiences an inflation effect. While the surface remains fixed at the end caps, it bulges outwards in the middle section. This is in the Figure 3 - greatly exaggerated - indicated. Furthermore (not shown here), the Yankee cylinder 8 is subject to thermal deformation, which leads to increased diameters, particularly in the edge regions. Without bending compensation by the counter roller, this would result in severe edge overloads. Especially with Yankee cylinders 8 with a hard metal coating, this deformation cannot be regularly corrected by grinding the Yankee cylinder 8 when operating parameters change. Therefore, the treatment nip 20 must be compensated for by the bending adjustment roller 1.

Landscapes

  • Rolls And Other Rotary Bodies (AREA)

Claims (15)

  1. Rouleau (1) pour le traitement d'une bande de matériau (9), avec une enveloppe rotative (2), le rouleau (1) présentant une pluralité d'éléments d'appui hydrostatiques (3), qui peuvent exercer une force sur la périphérie intérieure de l'enveloppe (2),
    les éléments d'appui (3) s'appuyant sur un axe (4) non rotatif traversant l'enveloppe (2),
    et une bride d'entraînement (5) étant respectivement prévue sur au moins une, en particulier sur les deux faces frontales du rouleau (1), afin de transmettre une puissance d'entraînement à l'enveloppe (2),
    et l'enveloppe (2) étant constituée d'un matériau plastique, tandis que la ou les brides d'entraînement (5) sont constituées d'un matériau métallique, en particulier d'un acier,
    caractérisé en ce que
    la liaison de l'enveloppe (2) avec la bride d'entraînement (5) est réalisée entièrement ou partiellement par une liaison adhésive.
  2. Rouleau (1) selon la revendication 1, caractérisé en ce que la surface adhésive (6) de l'assemblage par collage s'étend sur toute la circonférence de l'enveloppe (2) ou de la bride d'entraînement (5) et/ou en ce que la surface adhésive (6) s'étend dans la direction longitudinale du rouleau (1) sur au moins 30 mm, en particulier au moins 40 mm.
  3. Rouleau (1) selon l'une des revendications précédentes, caractérisé en ce que le module d'élasticité de l'enveloppe (2) dans la direction longitudinale (L) est au maximum de 50 GPa, de préférence au maximum de 20 GPa, et/ou au moins de 5 GPa, de préférence au moins de 10 GPa.
  4. Rouleau (1) selon l'une des revendications précédentes, caractérisé en ce que l'enveloppe (2) comprend ou est constituée d'un corps qui est construit à partir d'une matière plastique renforcée par des fibres, en particulier une matière plastique renforcée par des fibres de verre et/ou une matière plastique renforcée par des fibres de carbone.
  5. Rouleau (1) selon la revendication 4, caractérisé en ce que le corps comprend un matériau fibreux et un matériau de matrice, des éléments conducteurs de chaleur, en particulier des particules d'aluminium, étant en outre intégrés dans le matériau de matrice.
  6. Rouleau (1) selon l'une des revendications 4 ou 5, caractérisé en ce que l'on utilise un matériau de matrice qui présente une température de transition vitreuse >140°C, en particulier >170°C.
  7. Rouleau (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le module d'élasticité de l'enveloppe (2) dans la direction circonférentielle du rouleau (1) est plus grand, de préférence deux fois plus grand, en particulier au moins cinq fois plus grand, que dans la direction longitudinale (L) du rouleau (1).
  8. Rouleau (1) selon l'une des revendications précédentes, caractérisé en ce que les éléments de support (3) sont disposés le long d'une rangée, la distance (Δ) entre deux éléments de support (3) adjacents étant inférieure à 5mm, notamment comprise entre 1mm et 2mm.
  9. Rouleau (1) selon l'une des revendications précédentes, caractérisé en ce que la largeur des éléments de support (3) dans la direction circonférentielle est inférieure à 100mm, en particulier 80mm ou moins.
  10. Rouleau (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que l'enveloppe (2) comprend en outre un revêtement (12) qui fournit la surface de contact avec la bande du rouleau (1), ce revêtement (12) étant notamment constitué d'un polyuréthane.
  11. Rouleau (1) selon l'une des revendications précédentes, caractérisé en ce que l'enveloppe (2) présente une épaisseur supérieure à 20 mm, de préférence supérieure à 30 mm.
  12. Rouleau (1) selon l'une des revendications précédentes, caractérisé en ce qu'il est prévu, en plus de la liaison par collage, d'autres moyens de liaison (7), notamment des broches de liaison (7), qui relient mécaniquement l'enveloppe (2) à la bride d'entraînement (5).
  13. Dispositif de pressage (10) pour une bande de matériau (9), en particulier une bande de papier (9), le dispositif de pressage (10) comprenant une pince de traitement (20) formée par un rouleau (1) et un contre-rouleau (8), caractérisé en ce que le rouleau (1) est réalisé selon l'une des revendications précédentes.
  14. Dispositif de pressage (10) selon la revendication 12, caractérisé en ce que le contre-rouleau (8) est un cylindre chauffé (8), notamment un cylindre de lissage (8).
  15. Dispositif de pressage (10) selon la revendication 13, caractérisé en ce que le cylindre chauffé (8) présente une surface qui comprend ou est constituée d'un matériau en métal dur, en particulier un métal dur en carbure de tungstène-cobalt ou un matériau en cermet.
EP23750609.2A 2022-08-31 2023-07-28 Rouleau et appareil de presse Active EP4581206B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022121998.4A DE102022121998A1 (de) 2022-08-31 2022-08-31 Walze und Pressvorrichtung
PCT/EP2023/071030 WO2024046673A1 (fr) 2022-08-31 2023-07-28 Rouleau et appareil de presse

Publications (2)

Publication Number Publication Date
EP4581206A1 EP4581206A1 (fr) 2025-07-09
EP4581206B1 true EP4581206B1 (fr) 2025-10-29

Family

ID=87555156

Family Applications (1)

Application Number Title Priority Date Filing Date
EP23750609.2A Active EP4581206B1 (fr) 2022-08-31 2023-07-28 Rouleau et appareil de presse

Country Status (4)

Country Link
EP (1) EP4581206B1 (fr)
DE (1) DE102022121998A1 (fr)
FI (1) FI4581206T3 (fr)
WO (1) WO2024046673A1 (fr)

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI50364C (fi) * 1971-01-19 1976-02-10 Tampella Oy Ab Puristustela
DE9314568U1 (de) 1993-09-27 1995-02-02 Eduard Küsters Maschinenfabrik GmbH & Co KG, 47805 Krefeld Walze
DE4340724A1 (de) * 1993-11-30 1995-06-01 Sigri Great Lakes Carbon Gmbh Mit Fasern verstärkte Kunststoffwalze mit Rautierung
DE102005040868A1 (de) 2005-08-29 2007-03-08 Voith Patent Gmbh Biegeeinstellwalze
JP4721896B2 (ja) * 2005-12-27 2011-07-13 東芝機械株式会社 シート・フィルム成形ロールおよびシート・フィルム成形ロールのクラウニング制御方法およびシート・フィルム成形装置
DE102007018475A1 (de) * 2007-04-19 2008-10-23 Voith Patent Gmbh Walze für Papiermaschine
DE102015212399A1 (de) * 2015-07-02 2017-01-05 Voith Patent Gmbh Bauteil für eine Maschine zur Herstellung und/oder Behandlung einer Faserstoffbahn
CN113167027B (zh) * 2018-12-04 2023-08-29 安德里茨库斯特斯有限责任公司 辊子及辊子的制造方法
DE102020125395A1 (de) 2020-09-29 2022-03-31 Voith Patent Gmbh Maschine und Verfahren zur Herstellung einer Faserstoffbahn

Also Published As

Publication number Publication date
WO2024046673A1 (fr) 2024-03-07
FI4581206T3 (fi) 2026-01-30
EP4581206A1 (fr) 2025-07-09
DE102022121998A1 (de) 2024-02-29

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