EP4361345A1 - Presse à patin - Google Patents

Presse à patin Download PDF

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Publication number
EP4361345A1
EP4361345A1 EP23205353.8A EP23205353A EP4361345A1 EP 4361345 A1 EP4361345 A1 EP 4361345A1 EP 23205353 A EP23205353 A EP 23205353A EP 4361345 A1 EP4361345 A1 EP 4361345A1
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EP
European Patent Office
Prior art keywords
support
shoe press
presser
shoe
upper block
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.)
Pending
Application number
EP23205353.8A
Other languages
German (de)
English (en)
Inventor
Francesco Simoncini
Michael Angerilli
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.)
Toscotec SpA
Original Assignee
Toscotec SpA
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 Toscotec SpA filed Critical Toscotec SpA
Publication of EP4361345A1 publication Critical patent/EP4361345A1/fr
Pending 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

Definitions

  • the present invention relates to a shoe press.
  • a shoe press in accordance with the present invention can be used for the production of systems for the treatment of web-like materials in which the formation of an extended pressure nip or "extended nip" is required.
  • Such systems are generally used for the dehydration, by compression, of the fibrous material from which paper is obtained, in particular tissue paper.
  • a shoe press generally comprises a pressing element, known as “shoe”, oriented transversally to the direction of the fibrous material being treated (so-called “Machine Direction” or “MD”) and intended to compress the web itself in cooperation with a counter-presser.
  • the latter is typically constituted by a roller also oriented transversely to said direction.
  • the counter-presser can also be a heated cylinder, generally known as “Yankee”.
  • the shoe has a transversal profile adapted to define, in cooperation with the counter-presser, a compression nip extended along the MD and also suitable for determining a predefined pressure distribution, so that a prolonged compression of the fibrous material that passes through this nip is achieved, with pressure values generally varying along the MD.
  • such shoes are made of metal structures or deformable structures made of elastic materials, such as polyurethane, with pressurizable internal chambers.
  • Metal shoes have greater rigidity and offer greater resistance to deformation of the counter-presser, in particular when the latter is a Yankee, in correspondence with the nip.
  • the typical rigidity of a metal shoe does not guarantee that there is always a uniform pressure distribution within the nip in the prevailing direction of development of the shoe (so-called "Cross Direction" or "CD"). This can lead to negative effects on the moisture profile of the fibrous material along the CD.
  • the fibrous material is generally supported by a felt while it passes through the pressure nip, the non-uniformity of the pressure profile along the CD causes a non-uniform compression of the felt itself, which further amplifies the non-uniformity of the pressure profile on the fibrous material along the CD.
  • a further drawback due to the use of entirely metal shoes lies in the fact that the pressure profile along the MD can be adjusted only in part and only by using at least two lines of actuators or systems that simultaneously allow to apply a load in a radial direction and a torque around the longitudinal axis of the shoe itself.
  • the pressure ratio between the inlet actuator line and the outlet actuator line so-called "tilt"
  • this system is used to modify the output pressure peak from time to time, in order to increase the compression and therefore the escape of water from the fibrous material, or vice versa to increase the width of the load footprint to safeguard the bulk and thickness of the product.
  • shoes made in the form of a block of elastic material such as for example the shoe described in EP2013412 , guarantee greater adaptability of the shoes themselves to the deformed profile of the counter-presser, in particular when the counter-presser is a Yankee.
  • the greater elasticity of shoes made of elastic material compared to entirely metallic shoes also produces a greater extension of the compression nip along the MD, thus increasing the compression time of the fibrous material. Therefore, for the same pressure peaks, shoes made of elastic material allow higher levels of dryness.
  • EP16805044 discloses a shoe press in which the pressing element, i.e. the shoe, is made up of a block of elastic material inserted into a more rigid body in which a containment chamber is formed which surrounds the elastic block on all sides except the upper side which is defined as the work surface.
  • the elastic block can move parallel to itself inside said containment chamber and can be made up of several layers of materials with different degrees of elasticity or hardness.
  • the shoe press disclosed in EP16805044 has an actuation system consisting of a hydraulic chamber formed below the elastic block or by hydraulic cylinders arranged below the containment chamber or by a combination of such actuation elements.
  • the shape and the rigidity of the containment chamber of the elastic block limit the ability of the latter to correctly adapt to the deformed profile of the counter-presser in the CD direction so that the load cannot be correctly transmitted along the entire area of contact with the counter-presser.
  • DE3030233 discloses a shoe press in which the shoe is made up of a block of elastic material mounted on an underlying metal support that, in turn, is mounted on a hydraulic chamber constituting the actuation element.
  • the hydraulic chamber is made up of flexible membranes anchored to a fixed beam. Even in this case the load cannot be correctly transmitted since every increase in pressure in the hydraulic chamber also causes a non-predeterminable lateral expansion of the same.
  • WO2022/122327 discloses a shoe press comprising an upper element and a support intended to form a rigid, non-flexible base for the upper element.
  • US6951824 discloses a shoe press intended to interact with a solid counter-presser, and therefore practically non-deformable under load, in which the shoe press has a concave surface with an invariable shape, compatible with the radius of the counter-presser, on which a yielding membrane is applied.
  • the shoe press has a rigid core so that the nip defined by the shoe press/counter-presser interaction is of invariable shape.
  • WO2005/038130 describes a shoe press comprising an elastic upper side and an underlying rigid support.
  • the latter in particular, is made up of a beam of invariable shape which has a channel and two ends closing the channel itself. Said beam is structured in such a way that its shape remains stable.
  • the main aim of the present invention is to overcome the aforementioned drawbacks.
  • Another object of the present invention is to propose a shoe press made according to construction criteria alternative to the known criteria.
  • the present invention it is possible to ensure a very precise adaptation of the shoe to the deformed profile of the counter-presser in all operating conditions thanks to the flexibility of the shoe along the CD. Furthermore, it is possible to use elastic materials, such as polyurethane (PU) with a high degree of hardness in order to exploit its substantial incompressibility under the expected load conditions and the ability to maintain the shape of the upper profile of the shoe in order to obtain a sudden drop of pressure at the exit of the nip to avoid re-wetting of the sheet, which would otherwise tend to reabsorb part of the water previously expelled, and guarantee a high degree of dryness of the sheet at the exit from the nip.
  • PU polyurethane
  • the elastic modulus of the shoe is, for example, 3-4 orders of magnitude lower than the elastic modulus of the metals used for the production of entirely metallic shoes, the flexibility of the shoe along the CD direction is favored without however provoking appreciable variations in the uniformity of the linear pressure applied along the CD.
  • a shoe press (1) in accordance with the present invention can be used to create a pressure nip (EN) which extends by a pre-established value (VN) along a direction (MD) traversed by a web-like material that passes through the same pressure nip to be subjected to compression, in particular to be dehydrated.
  • the shoe press (1) can be used to dehydrate, by compression, a sheet of wet fibrous material in a papermaking machine.
  • the shoe press (1) is combined with a counter-presser consisting of a Yankee cylinder (2): the sheet of wet fibrous material (S) passes through the pressure nip (EN) formed in cooperation by the shoe press (1) and the Yankee (2); after passing through the pressure nip (EN), the sheet (S) moves along the external surface of the Yankee, from which it receives heat, and, after its detachment by a suitable doctor blade (T), it is wrapped in form of a reel (RS) downstream of the Yankee.
  • the Yankee (2) and the shoe press (1) are oriented along a direction (CD) orthogonal to the direction (MD) followed by the sheet (S) as it passes through the pressure nip (EN).
  • the shoe press (1) can assume a rest position, as schematically represented in Fig.4 , and an operative position, as schematically represented in Fig. 2 , Fig.5 and Fig.6 . In the operative position the shoe is pushed towards the Yankee in such a way that the compression to which is subjected the wet fibrous sheet (S) passing through the pressure nip causes the expulsion of water from the sheet itself.
  • the Yankee (2) has a hollow central part which houses inside it a system (not shown in the drawings) for the distribution of steam, through which is produced the heating of the external cylindrical surface (20), on which the sheet (S) runs downstream of the pressure nip (EN).
  • Two side heads (21) close said central part at the sides and are provided with pins (22) for its insertion on a support structure (not shown in the drawings) and the connection to a motor member (not shown in the drawings) that controls its rotation around a central axis (A2) oriented along the machine direction (MD).
  • a support structure not shown in the drawings
  • A2 central axis
  • Such a structure determines, when a pressure is applied along the direction (CD) on the external cylindrical surface (20) of the Yankee, the formation of a deformed profile (P2) in the pressure application area, i.e.
  • the presence of the side heads (21) determines a greater rigidity of the Yankee on its sides compared to the central part delimited by the cylindrical shell (20).
  • the formation of the deformed profile generally implies a non-uniform transmission of the load along the CD by the presser.
  • a shoe press in accordance with the present invention comprises a presser (10) consisting of a block (11) of elastic material mounted on an underlying more rigid support (12) which, in turn, is slaved to an actuation system allowing to push it towards the counter-presser (2).
  • Said block (11) constitutes the upper part of the presser (10).
  • the presser (10) will also be called “shoe” in the continuation of this description.
  • the material of which the block (11) is made has a lower modulus of elasticity than the material of which the support (12) is made. For this reason, the block (11) is also called “elastic block” in this description.
  • the elastic block (11) is a single block of material (for example polyurethane) having a modulus of elasticity 2-4 orders of magnitude lower than the material of the support (12), i.e. from 100 to 10000 times lower.
  • the support (12) can be made of aluminum, bronze or stainless steel, having elastic modules comprised between 60000MPa and 200000MPa.
  • the material of which the block (11) is made has a hardness. comprised between 80 Shore A and 100 Shore A, preferably a hardness comprised between 92 and 96 Shore A and even more preferably a hardness of 95 Shore A and the modulus of elasticity normally is comprised between 10 and 100MPa.
  • the support (12) is a flat metal body (width and length prevailing with respect to the thickness).
  • the support (12) can be made of aluminum, bronze or stainless steel, with a thickness comprised between 5 mm and 20 mm, preferably with a thickness comprised between 7 mm and 15 mm.
  • the elastic block (11) is joined to the support (12) so that these elements (11, 12) form a unitary body.
  • the joining between the elastic block (11) and the support (12) can be achieved by forming an anchor between the lower side of the elastic block (11) and the upper side of the support (12) which extends along the entire contact area between the block of elastic material and the underlying support.
  • the elastic block (11) is free to deform elastically along the CD direction because the anchoring between the elastic block (11) itself and the support (12) is free of constraints acting on the heads of the block (11).
  • the lower side (110) of the elastic block (11) can have a width (measured in the MD direction) equal to or less than the width (even measured in the MD direction) of the upper side (120) of the support (12), as schematically represented in Figs.7A-7C .
  • the width of the elastic block (11) measured in the MD direction is comprised between 50 mm and 300 mm, preferably between 70 mm and mm.
  • the thickness (S11) of the elastic block (11) above the support (12) is comprised between 3 mm and 50 mm, preferably between 5 mm and 25 mm.
  • the block (11) of elastic material can be joined to the support (12) by gluing.
  • the aforementioned anchoring can be achieved by directly vulcanizing the block (11) onto the support (12); in this case, preferably the upper side of the support (12) is preliminarily subjected to sandblasting and degreasing to facilitate the adhesion of the elastic block (11).
  • the upper side (120) of the support (12) can be provided with depressions (121) into which the material of the block (11) can be poured which, when solidifying, will give rise to the formation of corresponding appendages (111) inserted in the same depressions (121).
  • the latter can be, for example, grooves longitudinally formed on the upper side (120) of the support (12).
  • said grooves are dovetail-shaped.
  • the block (11) of elastic material can also be already preformed with the appendages (111) to be inserted into the depressions (120) of the support (12). In the latter case the joining can be achieved by gluing the two parts.
  • An intermediate anchoring layer can also be positioned between the block of elastic material (11) and the support (12), also made of elastic material (for example polyurethane of lower hardness than that used to create the block 11) whose function is that to facilitate the different expansions between the rigid layer and the elastic layer.
  • the material of the intermediate anchoring layer has a hardness of 60 Shore A while the material of the block (11) has a hardness of 95 Shore A.
  • This layer of anchoring material can have a very limited uniform thickness (0.5-5mm, preferably 1-2mm).
  • the elastic block (11) and the more rigid support (12) have respective flat surfaces (110, 120) which, in the assembled shoe (10) configuration, are counter-faced and adhered to each other.
  • the upper face (120) of the rigid support (12) does not exhibits depressions or irregularities causing non-uniformity in the rigidity of the support itself.
  • the block (11) preferably has a cross section made to obtain a pressure profile in the MD direction which determines a gradual increase in pressure in an entry zone of the sheet (S) in the pressure nip (EN) and, at the exit, a pressure peak.
  • the block (11) preferably has an entry zone (A) defined by a relatively large radius curvature (radius of curvature between 30 mm and 100 mm, preferably between 35 mm and 55 mm), followed by a intermediate zone (B) which is flat or slightly convex towards the outside (radius of curvature between 1000 mm and 5000 mm) and an exit zone (C) defined by a connection of a relatively small radius with the intermediate zone (between 2 mm and 30 mm, preferably between 5 mm and 25 mm) and by an inclination greater than 10° (preferably greater than 13°) with respect to the underlying support (12).
  • A entry zone
  • B which is flat or slightly convex towards the outside
  • C exit zone
  • C defined by a connection of a relatively small radius with the intermediate zone (between 2 mm and 30 mm, preferably between 5 mm and 25 mm) and by an inclination greater than 10° (preferably greater than 13°) with respect to the underlying support (12).
  • the presser (10) is slaved to an actuation system (3) comprising a series of hydraulic cylinders (30) arranged below the presser and acting on the lower side (122) of the support (12).
  • the actuation system (3) is supported by an underlying fixed beam (T3).
  • the actuation system (30) is of the type described in EP2994569 , i.e. of the type comprising a plurality of hydraulic pistons (30) arranged in two parallel rows along the CD direction inside a block (31) in which pressurization are formed chambers (32) supplied with a hydraulic fluid through corresponding supply lines formed in a lower part (33) of the block (31).
  • the actuation system (3) is fixed on the underlying fixed beam (34) through the lower part (33) of the block (31) and has suitable surfaces (35) for lateral guide and containment of the pistons (30).
  • FIG.8 represents, in a thicker line, a qualitative trend of a possible pressure profile (PP) along the MD for a given tilt.
  • PP possible pressure profile
  • PR axis of the ordinates
  • PK peak pressure
  • the actuation system (3) allows the compression load to be applied to the sheet (S) through the shoe (10) in a direct and controllable way, both in terms of the value of the overall applied load and in terms of the tilt.
  • the group formed by the presser (10) and the respective actuation system is inside a tubular polyurethane sock (4), known per se, rotating around an axis parallel to the CD.
  • a tubular polyurethane sock (4) known per se, rotating around an axis parallel to the CD.
  • more nozzles can be positioned (not visible in the drawings and which are known per se), to spray lubricating oil downstream of the presser (10).
  • the lubricating oil dragged by the rotating sock (4), forms a hydraulic meatus which supports the sock itself and allows the nip pressure to be applied without an actual contact between the presser and the sock, so as to avoid abnormal wear of both the sock and the presser.
  • the shape of the inlet side (A) of the presser (10) favors the interposition of the lubricating oil between the presser and the sock.
  • the shoe made according to the invention can be pushed directly against the rotating polyurethane sock which isolates the external side of the press from the external environment, or a layer (5) of material with a low friction coefficient can be provided between the shoe itself and the polyurethane sock.
  • This second solution consists in appropriately mounting, for example through a jaw system or through the interposition of the low friction coefficient layer between two metal surfaces (50, 51) placed against each other and tightened with a plurality of screws (52).
  • the layer in question in addition to guaranteeing a low friction coefficient, has a high resistance to wear.
  • the layer (5) is intended to avoid any possible contact between the rotating polyurethane sock and the elastic material which constitutes the upper part (11) of the shoe (10), even in the worst conceivable operating conditions.
  • the layer (5) can be made of a technopolymer with a reduced friction coefficient and high resistance to contact with synthetic lubricating oils.
  • Thordon ® is often used in the production of plain bearings and is also available in very thin thicknesses.
  • the cushion layer (6) can be placed under the rigid support (12) which can contribute to further standardize the distribution of the thrust provided by the actuation system.
  • the cushion layer (6) can be a layer of polyurethane with a thickness between 5 mm and 20 mm.
  • this additional layer is due not only to the ability to further distribute the thrust over a larger surface, but also to the fact that, by avoiding a direct contact between the metal surfaces of the support (12) and the heads of the pistons, which are not mutually locked, it is avoided that, following even minimal relative movements between these components, caused for example by possible angular movements spontaneous movements of the shoe, the point of force transmission shifts.
  • the use of the more rigid support (12) also allows the tilt to be adjusted more effectively, allowing, in fact, the use of two rows of pistons to exert a differentiated load at the entry and respectively the exit of the pressure nip.
  • the elastic block (11) made integral with the underlying more rigid support (12) so as to form a single body and the actuation system (3) which transmits the load to the rigid support (12) in a direct and controllable way cooperate synergistically with each other to overcome the previously mentioned drawbacks.
  • the different nature of the elastic material of the block (11) compared to the metallic material of the support (12) also determines a different value of thermal expansion.
  • vulcanization is carried out at a temperature higher than the normal operating temperature of the shoe or, in any case, of the rom temperature (vulcanization normally occurs at temperatures above 150°C, while the peak temperatures of a shoe press in operating conditions hardly exceed 70°-80°C). Therefore, following cooling, the layer of elastic material tends to shrink more than the underlying metal layer to which the elastic material is joined.
  • the elastic block (11) can assume a tensile load state that, due to the high flexibility of the underlying metal layer due to its limited thickness, can determine a concave deformity of the shoe with the concavity facing the counter-presser as schematically represented in Fig.9 .
  • this deformation of the shoe in rest conditions can also be reduced or canceled (in case it creates problems of interference with the sock or with other parts of the shoe press, when in rest configuration) by providing a curvature of the rigid support (12) in the opposite direction to the concavity resulting from the vulcanization of the elastic block. Since the stiffness of the metal support (12) is much greater than that of the elastic block (11), a limited pre-deformation is sufficient, as schematically represented in Fig.
  • a shoe press in accordance with the present invention offers numerous technical advantages.
  • the overall flexibility of the shoe is significantly increased compared to the typical flexibility of a shoe made entirely of metallic material or of a shoe made up of an elastic element mounted on a substantially non-deformable support.
  • This provides the advantage of a greater ability of the shoe to "copy" the deformed profile of the Yankee in correspondence with the pressure zone.
  • the shoe adapting itself to the profile of the Yankee and, consequently, deforming, reacts elastically, exerting a reaction which disturbs the uniformity of the ideal pressure profile; but this reaction, although present, is much smaller compared to the linear pressure exerted against the Yankee.
  • halving the thickness of the metal support layer compared to the thickness of an original metal shoe (whose thickness cannot be reduced beyond certain limits, to allow maintaining the material necessary for the creation of the pressure profile) thanks to the possibility of creating the desired geometric profile (112) on the elastic material allows the overall elastic reaction exerted by the shoe following a deformation to be reduced by 8 times (neglecting the contribution of block 11 whose modulus of elasticity is 2-4 orders of magnitude lower than that of the metal substrate 12).
  • the presence of a metal substrate allows the loads necessary for the operation of the shoe press to be applied by means of hydraulic actuators applied against the metal substrate directly or through a possible further layer of elastic material, not rigidly connected to the shoe, whose function is to compensate for the differences in instantaneous positioning of the piston heads in the transient phases (loading or unloading) and to increase the width of the so-called load distribution cone on the shoe by increasing the distance between the point of application of the load by the pistons and the upper profile of the block 11 (this is to avoid the presence of areas of pressure concentration due to a eventuale lack of distribution of the load applied by the single cylinder).
  • hydraulic actuators much more robust components than pressurized air chambers made of elastic materials, increases the reliability of the system and avoids frequent breakages with consequent long repair times and machine downtime.
  • the shoe made with the layer of elastic material on its upper part allows to take advantage of the greater adaptability of the shoe profile in the advancement direction of the paper (machine direction). In this way it is possible to increase the pressure footprint (area of the nip actually affected by the contact between the presser and the counter-presser), consequently increasing the time during which the paper remains in the pressure nip.
  • This is particularly useful for producing paper with high bulk values (a measurement equal to the inverse of the density and representative of the thickness of the paper produced, indicative, in turn, of the drying characteristics of the sheet), renouncing to concentrate the pressure profile in the machine direction over a less extensive area (useful for increasing water removal at the expense of the bulk), but distributing the pressure more correctly along the entire pressure footprint in the machine direction .

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  • Paper (AREA)
EP23205353.8A 2022-10-27 2023-10-23 Presse à patin Pending EP4361345A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT202200022131 2022-10-27

Publications (1)

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EP4361345A1 true EP4361345A1 (fr) 2024-05-01

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EP23205353.8A Pending EP4361345A1 (fr) 2022-10-27 2023-10-23 Presse à patin

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3030233A1 (de) 1980-08-09 1982-02-18 J.M. Voith Gmbh, 7920 Heidenheim Nasspresse zum entwaessern von faserbahnen
US5951824A (en) * 1997-06-19 1999-09-14 Beloit Technologies, Inc. Compliant hydrodynamic/hydrostatic shoe for papermaking press
WO2005038130A1 (fr) 2003-10-21 2005-04-28 Metso Paper Karlstad Ab Corps d'appui, dispositif de support pour celui-ci, appareil equipe d'un tel corps pour traitement d'une bande, procedes permettant de former une ligne de pincement prolongee dans l'appareil et de reguler la charge dans la surface de pincement
US6951824B2 (en) 2000-02-10 2005-10-04 Robert Bosch Gmbh Method for manufacturing a micromechanical component and a component that is manufactured in accordance with the method
EP2013412A1 (fr) 2006-04-21 2009-01-14 Metso Paper Karlstad AB Corps de support destine a un appareil pourvu d'une ligne de contact etendue servant au cours du traitement d'une bande de fibres
EP2994569A1 (fr) 2013-05-09 2016-03-16 Toscotec S.p.A. Presse à patin
WO2022122327A1 (fr) 2020-12-07 2022-06-16 Valmet Ab Corps de support et machine à papier comprenant un tel corps de support

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3030233A1 (de) 1980-08-09 1982-02-18 J.M. Voith Gmbh, 7920 Heidenheim Nasspresse zum entwaessern von faserbahnen
US5951824A (en) * 1997-06-19 1999-09-14 Beloit Technologies, Inc. Compliant hydrodynamic/hydrostatic shoe for papermaking press
US6951824B2 (en) 2000-02-10 2005-10-04 Robert Bosch Gmbh Method for manufacturing a micromechanical component and a component that is manufactured in accordance with the method
WO2005038130A1 (fr) 2003-10-21 2005-04-28 Metso Paper Karlstad Ab Corps d'appui, dispositif de support pour celui-ci, appareil equipe d'un tel corps pour traitement d'une bande, procedes permettant de former une ligne de pincement prolongee dans l'appareil et de reguler la charge dans la surface de pincement
EP2013412A1 (fr) 2006-04-21 2009-01-14 Metso Paper Karlstad AB Corps de support destine a un appareil pourvu d'une ligne de contact etendue servant au cours du traitement d'une bande de fibres
EP2994569A1 (fr) 2013-05-09 2016-03-16 Toscotec S.p.A. Presse à patin
EP2994569B1 (fr) * 2013-05-09 2020-08-12 Toscotec S.p.A. Presse à patin
WO2022122327A1 (fr) 2020-12-07 2022-06-16 Valmet Ab Corps de support et machine à papier comprenant un tel corps de support

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