WO1991005913A1 - Calandre - Google Patents

Calandre Download PDF

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Publication number
WO1991005913A1
WO1991005913A1 PCT/EP1990/001713 EP9001713W WO9105913A1 WO 1991005913 A1 WO1991005913 A1 WO 1991005913A1 EP 9001713 W EP9001713 W EP 9001713W WO 9105913 A1 WO9105913 A1 WO 9105913A1
Authority
WO
WIPO (PCT)
Prior art keywords
roller
force
roll
press
bar
Prior art date
Application number
PCT/EP1990/001713
Other languages
German (de)
English (en)
Inventor
Hans Dahl
Andreas Meschenmoser
Wolf-Gunter Stotz
Karl Volz
Original Assignee
Sulzer-Escher Wyss 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 Sulzer-Escher Wyss Gmbh filed Critical Sulzer-Escher Wyss Gmbh
Publication of WO1991005913A1 publication Critical patent/WO1991005913A1/fr

Links

Classifications

    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/006—Calenders; Smoothing apparatus with extended nips
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/002—Opening or closing mechanisms; Regulating the pressure

Definitions

  • the invention relates to a roller press with at least two adjacent rollers, which can also be part of a calender.
  • this press can also be used in other contexts, especially in paper manufacture.
  • rollers does not only include those rollers which have a circular cylindrical shape.
  • the rollers can also be flexible rollers, which do not always assume a precisely circular cylindrical shape.
  • roller presses are e.g. known from DE 34 08 118 AI or DE 34 08 119 AI.
  • rollers form a nip through which a web of material passes and is treated by pressure.
  • forces have to be applied to the rollers in order to generate the required pressing force in the nip, it being generally desirable to influence the pressing force occurring in the nip depending on the respective conditions in the device, either with regard to one over the length of the Roll nip constant pressing force, or with regard to the creation of a specially desired pressing force profile, which is not uniform over the length of the nip, ie over the width of the material web.
  • a plurality of force elements actuated by pressure medium are usually used, which have to be fed with the pressure medium.
  • valves and other control elements for the pressure medium such as air or hydraulic oil, have been used for this purpose.
  • the strip of the pressing device provided with force elements has a width which covers a U section of the roll - or counter-roll - which in turn forms the press nip (EP-A1-0 254 819).
  • the cross profile of this bar is flattened or concave on the side facing the press nip.
  • the pressure device has an impermeable, flexible band which is guided continuously through the press nip and prevents contact between the pressure medium fed into the pressure pockets and the material to be guided through the press nip during operation.
  • the bar is sufficiently flexible in the pressing direction of the roller press to enable it to be adapted to the shape of the counter roller during operation.
  • the individual pressure pockets are limited by bars.
  • the flexible bar can be bent, particularly in the area of the outermost pressure pockets. This bend increases on both sides at the end of the area of the pressure pockets, at the outermost edge of the last pressure pocket where the contact pressure gradually drops to zero at the end of the bar.
  • These adverse consequences of the bend can be counteracted by grouping the force elements in groups into zones, each of which can be controlled in terms of force independently of one another. This makes it possible, for example in the edge zones of the region of the pressure pockets, to achieve a uniform pressure over the length of the pressure gap by means of a higher contact pressure.
  • the disadvantage of bending the bar at its ends cannot be compensated for, apart from the effort involved in this measure, which also requires complex safety precautions in the system.
  • roller press in the previously defined sense, which is less complex in terms of its structure and in which damage to the rollers and in particular the flexible roller shell can be largely eliminated by overstressing.
  • a roller press which consists of at least two adjacent rollers forming a nip through which a web of material passes, at least one roller for the creation a wide nip is designed as a flexible roll shell having a hollow roll, a pressing plane being defined by the center lines of the adjacent rolls. At least one roller is such a roller, which is fixed or supported in the two end regions at least in one direction of the press plane. Both rolls are pressurized to one another over the length of the roll gap by force elements actuated by flow medium. The force elements in opposing support zones are connected to a common control element with their pressure medium lines, in which no control elements are required.
  • This solution ensures that only one common control valve can be used for the pressing force generation in the nip for both rollers with a significant advantage.
  • This advantage results from the fact that in the event of a control element failure in the communicating zones of the two adjacent rollers, the pressure drops to the same extent, with the result that no excessive pressure difference can occur, which can lead to partial or complete destruction of the flexible roller jacket. This also applies if the common fluid line breaks. Apart from the fact that this destruction is disadvantageous for economic reasons, such a destruction in the case of the rotating rollers and the forces that arise represents a considerable risk to the people staying in the area of the roller press. The simplification claimed also leads to a reduction in the production costs.
  • One of the rollers can nestle against the sag of the other roller in the concave as well as in the convex region of one roller. This essentially depends on the structure, size and weight of the respective roller.
  • the two adjacent rolls can be designed as hollow rolls having a roll casing, the force elements preferably being arranged within the roll casing.
  • the non-rotating yoke, on which the force elements are supported, can be located within the roll shell.
  • the two adjacent rollers can be fixed radially in particular in both end regions in the pressing plane, the roller shell being rotatably mounted on the yoke in the case of the hollow roller.
  • Two so-called K-rolls can be combined.
  • a roller of the adjacent rollers and, in the case of a hollow roller, the roller shell thereof in the two end regions can be fixed radially in both directions of the pressing plane and the other roller or its roller shell in the two end regions can only be fixed radially in one direction of the pressing plane.
  • This can then be a combination of a roll cover fixed on the end faces with a roll cover that is not radially fixed on the end faces, the latter being normally limitedly movable over its entire length in the pressing plane and being driven on one side to the stop at the appropriate point and thereby fulfills the function of a fixed roller shell.
  • the roll shell can also be designed to be flexible in order to allow the roll shell to conform to the sag of the other roll.
  • This flexible roll shell also allows a flat roll gap, so that no linear force, but a surface force occurs in the gap.
  • the flexible roll jacket can rest on at least one support bar extending in the longitudinal direction of the roll gap.
  • This support bar also referred to as a shoe, is flexible, in particular with regard to a less forceful fit to the sagging roller or the sagging roller shell, although there is also the possibility, in this sense, of letting the roller shell rest directly on the force elements, which in the case of a flexible roll shell allows a better fit to the sagging roll or the sagging roll shell.
  • all the force elements along the roller gap are expediently subjected to the same force.
  • the force elements for forming several press zones along the roller gap in the different support zones can be subjected to different forces. This not only enables a more flexible adjustment of the line or surface force in the gap, but also enables a better fitting of the support strip or the roll shell to the sagging roll or the sagging roll shell, since the deformation forces occurring over the length of the roll gap are not the same.
  • the active surfaces of the force elements which generate force in the pressing direction are expediently dimensioned such that the forces generated by them cause the roller guided on the end face in the pressing plane to be brought against an end stop on the end face.
  • the opposing rollers can also each have only one support zone. It is advantageous if the communicating support zones have the same length. However, it is also possible for only one support zone of both rolls to extend essentially over the entire effective press length.
  • all the force elements of a support zone of a roller have the same force-generating irk surfaces.
  • the force elements of the communicating support zones of both rollers can each have different force-generating active surfaces.
  • Another object of the invention is to provide a strip with the associated force elements for the roller press of the type described above, which has a satisfactory pressing function in the specified roller press without the need for complex zone control of the force elements and while maintaining a pressing force that is as uniform as possible in the press nip. guaranteed over its length.
  • a lengthened press nip between a roller and a pressing device which has a strip arranged in the area of the press nip with hydrostatic pressure pockets open towards the press nip to an impermeable circumferential band, which means by means of below a region of the pressure pockets the bar of arranged force elements can be pressed to the press nip, in which arrangement the area of the pressure pockets as well as an equivalent press area limited by the rectangular profile equivalent to the real pressure profile and a cylindrical area of the roller are symmetrical to one another, whereby - viewed axially - the equivalent press area is shorter than the cylindrical one Area, but longer than the area of the pressure pockets, and wherein the bar is at least as long as the cylindrical area of the roller, the relation of the distance between the end of the equivalent pressing area hs and the jex »?
  • an extended press nip between a roller and a pressing device which has a bar arranged in the area of the press nip with hydrostatic pressure pockets opened in the direction of the press nip towards an impermeable circumferential band, which means below a region of the pressure pockets the bar of arranged force elements can be pressed to the press nip, in which arrangement the area of the pressure pockets as well as an equivalent press area limited by the rectangular profile equivalent to the real pressure profile and a cylindrical area of the roller are symmetrical to one another, whereby - viewed axially - the equivalent press area is shorter than the cylindrical one Area, but longer than the area of the pressure pockets, and wherein the bar is at least as long as the cylindrical area of the roller, the arrangement of the force elements along the bar being matched to the relation of the Distance between the end of the equivalent pressing area and the outermost edge of the piston at the extreme force elernent to the distance between this force element and the force element adjacent in the row, namely in
  • hydrostatic force elements with hydrostatic pressure pockets is particularly advantageous.
  • 1 is a longitudinal sectional view of two adjacent deflection compensation rollers, without free stroke of the jackets in the press plane,
  • Deflection compensation rollers the jackets of which have a free stroke in the press plane, the upper of which runs against a stop in the press plane during operation, and for this purpose is provided on the jacket with support bearings,
  • Fig. 3 is a longitudinal sectional view similar to FIG. 1 with the combination of a
  • FIG. 5 shows a representation similar to FIG. 4, but with the use of two flexible roller shells
  • Fig. 9 shows a part of a further roller press in cross section
  • Fig. 10 is a press nip section of the roller press in cross section.
  • two deflection compensation rollers 26 and 27 are shown in section. This is on both ends Compensating roller via bearings 28 in a frame 29 supported in a stroke-movable manner in the pressing direction, a corresponding pressing force being able to be applied by pressing cylinder 30.
  • Both rollers are so-called deflection compensation rollers with a roller jacket 26a or 27a, which is supported on both end areas by a bearing 31 on a yoke 26b or 27b.
  • Force elements 26c and 27c are located between the yoke and the roll shell in groups of two or three (other support zone distributions are also possible).
  • the rollers form a roller gap WS in the area of the force elements.
  • the force elements 26c and 27c can be pressurized with a fluid in which support pistons move in cylindrical recesses in the yoke.
  • the individual force elements are supplied by pressure lines 26d and 27d, the pressure lines of opposite force elements being connected to one another either as a whole or in each case by a common hydraulic or pneumatic control element 32 such that the opposite force elements of a respective support zone are acted upon with the same pressure and thus at the same pressure Formation of the force elements in opposite directions in the area of a press plane generate an equal force.
  • a common hydraulic or pneumatic control element 32 such that the opposite force elements of a respective support zone are acted upon with the same pressure and thus at the same pressure Formation of the force elements in opposite directions in the area of a press plane generate an equal force.
  • four support zones are provided, each with three and two force elements. Of course, only a single support zone can also be provided.
  • Fig. 2a shows a representation similar to Fig. 1 with two deflection compensation rollers 36 and 37, the jackets of which have a free stroke in the press plane, in which the jacket 37a is supported on the piston of the force elements 37c, and not on the yoke 37b, opposite to that the coat is arranged radially movable.
  • the upper roller 36 acts in such a way that the jacket 36a is supported here from above, via support bearings on the front side on the yoke 36b, since the force elements 36c press the jacket downward in the direction of the roller gap WS and the weights of both jackets 36a and 37a do not can be compensated for by the difference in force between the force elements 36c and 37c.
  • the pressure is applied via the pressure lines 36d and 37d.
  • the yokes 36b and 37b are immovably supported in the frame 29. An air gap remains between the yoke and the support bearing on the underside of the yoke 36b.
  • FIG. 2b shows a constellation similar to FIG. 2a, but in which the lower one
  • Deflection compensation roller is a K roller and the upper roller is an F roller, which is not supported on one side with its jacket on a yoke.
  • a combination of a solid roller 46 arranged at the top and a deflection compensation roller 47 at the bottom is provided, the roller jacket 47a of which is supported on the yoke 47b via bearings 31.
  • there are force elements 37c within the roll shell which force the roll shell 47a in the direction of the roll gap WS. On the full rolls also act in the press plane against the force elements 37c force elements 46c.
  • FIGS. 2 and 3 show cross sections of two design variants, specifically in the area of the force elements.
  • an upper roller 56 is combined with a rigid roller jacket 56a with a lower roller 57, which has a flexible roller jacket 57a.
  • the roller jackets are each supported on a force element 56e or 57e, which are supported with webs 56f or 57f in such a way that a pressurizable space 56g or 57g is provided between the force element and the respective roller jacket.
  • the force element 56e or 57e forms a piston 56h or 57h which can be pressurized within a cylinder.
  • Pressure medium lines 56i and 57i are provided in the force element and in the yoke.
  • the center lines of the rolls define a press plane which passes through the nip WS and lies at the level on which the pressure medium line 56i, 57i or 66i or 67i is drawn in FIGS. 4 and 5.
  • an extended press nip 1 is left between a roller 2 as a counter roller and a pressure device 3.
  • the pressing device 3 has a bar 4, which over the entire length of the roller 2 is sufficient. It is provided with hydrostatic pressure pockets 5, which are distributed on the side facing the press nip 1 according to, for example, a regular pattern.
  • the strip 4 for forming the extended press nip 1 has a length, with which it covers part of the circular circumference of the jacket 8 of the roller 2. In the transverse profile, the bar 4 is concave according to the diameter of the roller 2.
  • the bar is elastic in the longitudinal direction and can be pressed into the press nip by means of force elements 7.
  • the force elements 7 are arranged along the bar 4 at, for example, regular intervals 13, 13 'to one another, so that they each act on an equally large longitudinal section of the bar 4 provided with the pressure pockets 5.
  • roller 2 and the bar 4 can be seen across the width of the roller press:
  • a region 6 of the printing pockets 5 extends from the left edge of the outermost printing pocket on the left to the right edge of the outermost printing pocket on the right on the bar 4.
  • a cylindrical region 9 of the roller 2 extends from the bevel on the left to the bevel on the right on the jacket 8 of the roller 2
  • An equivalent pressing area 10 is determined as follows: Between the curves that describe the pressure curve actually occurring in the zones adjoining the area 6 to the outside and the zero line of the ambient pressure, a surface is spanned which is characterized by an equally large area the area 6 adjoining rectangular area can be replaced, the outer boundaries of which also form the boundaries of the equivalent pressing area 10. The real pressure curve is generated by applied forces and weight forces.
  • the equivalent press area 10 is shorter than the cylindrical area 9 of the roller 2, but longer than the area 6 of the pressure pockets. Said three areas 6, 9 and 10 are generally symmetrical to one another, since the entire configuration with the press nip, the roller and the bar with the pressure pockets and force elements is mostly symmetrical and is mirror image of an imaginary vertical center line.
  • the pressure pockets 5 and the force elements 7 assigned to them are arranged along the bar 4 in such a way that the distance 11 between the end of the equivalent pressing region 10 and the respective outermost force element 71 is essentially the same size as half 12 of one on both sides of the roller press Distance 13 and 13 'between this force element 71 and the force element 7 closest to this 71 in the series of force elements 7.
  • the distances 13, 13 'between the individual force elements 7, measured on the inner wall (outermost edge), are generally the same size along the bar 4. If a special controlling effect on the pressure profile is desired, unequal distances are also conceivable. All force elements 7 on the bar 4 can be loaded with a pressure of the same size, as a result of which they generally all act with the same force on the bar 4 in an area of the bar 4 of the same size.
  • the force element has a cylindrical part 22 which is attached to the bar 4 below the pressure pocket 5. This is associated with a piston-like part 23, which is supported on a beam-like yoke 16.
  • a pressure chamber 24 is provided between the cylinder 22 and the piston 23, in which a pressure medium, for example oil or water, is to be passed under pressure through a channel 25.
  • a channel 26 leads from the pressure chamber 24 into the pressure pocket 5, where a pressure is built up which acts on the impermeable band 20.
  • All force elements 7 can be acted upon via a composite line 14 with the pressure medium from a single pressure source 15, each with a pressure of the same size in each case. Since all of the systems have the same performance, that is to say power generation, they act on the strip 4 in the same area with the same force.
  • the roller 2 is a conventional roller, which undergoes deflection during operation under the action of the forces on the side of the bar 4, so that the press nip runs along an arcuate line.
  • the strip 4 is bent with corresponding contact forces, so that a desired, as uniform as possible line force in the press nip 1 is achieved in the equivalent pressing region 10.
  • roller 2 Any suitable, arbitrary roller - also one of the known deflection compensation rollers - can be used as roller 2.
  • Any suitable, arbitrary roller - also one of the known deflection compensation rollers - can be used as roller 2.
  • the roller 2 has a jacket 8 which is rotatable about a yoke 16 which is mounted in a rotationally fixed manner and which is supported on the yoke 16 in the pressing direction of the roller press by means of hydrostatic force elements 18.
  • the jacket 8 is guided and stored concentrically to the yoke 16 on its sides, left and right. Essentially, the axis of the jacket 8 remains unchanged relative to the yoke 16 during operation.
  • the force elements 18 are designed in terms of power, ie in terms of force generation, to be equivalent to the force elements 7 on the bar 4 and are basically divided along the jacket 8 of the roller according to the same pattern as the force elements 7 along the bar 4.
  • the two systems, the one in the roller 2 , such as that on the bar 4, can act against one another in the press plane of the roller press under the same conditions with equally large forces.
  • the line forces in the press nip are thus uniform and uniform.
  • the control of this roller press is relatively simple. All force elements 18 are connected to a composite line 14, which on the other hand is connected to a pressure source 15, from which the force elements 7 can be acted upon by the pressure medium via the composite line 14.
  • Deflection compensation roller can be used. Like the previously mentioned, this also has a jacket 8 which can be rotated about a yoke 16 which is mounted in a rotationally fixed manner and which is supported on the yoke 16 in the pressing plane of the roller press by means of hydrostatic force elements 18. However, in this deflection compensating roller, the jacket 8 is guided and supported on its sides in the pressing direction. For lifting the jacket 8 against the pressing direction of the roller press away from the press nip 1 or from the bar 4 of the pressing device 3, force elements 19 are provided which are effective against the pressing direction.
  • the force sources 18 of the deflection compensation roller are powerful, i.e. In terms of power generation, in the sense explained above, it is equivalent to the force elements 7 on the bar 4 of the pressing device.
  • each of the zones can be acted upon independently of one another in terms of pressure.
  • the force elements 19 for lifting the jacket 8, one of which is provided on each side of the jacket 8, can also be controlled independently of one another.

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  • Paper (AREA)
  • Rolls And Other Rotary Bodies (AREA)

Abstract

Une calandre comporte au moins deux cylindres adjacents (26, 27) qui forment un écartement (WS) à travers lequel passe une bande. Au moins un cylindre se présente sous la forme d'un cylindre creux avec une chemise de cylindre (26a, 27a), et un plan de pressage est défini par l'axe médian des cylindres adjacents. Au moins un cylindre se présente de telle manière qu'au moins une direction du plan de pressage est fixée dans les deux régions frontales. Les deux cylindres sont pressés l'un contre l'autre sur la longueur de l'écartement par des organes de force à commande hydrodynamique (26c; 27c). Ces organes de force sont reliés, dans des régions de support opposées, à un organe de commande commun (32) via leurs canalisations hydrauliques (26d; 27d) dans lesquelles il n'y a aucun élément de commande.
PCT/EP1990/001713 1989-10-11 1990-10-11 Calandre WO1991005913A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DEP3933941.6 1989-10-11
DE3933941 1989-10-11
DE19904017433 DE4017433A1 (de) 1989-10-11 1990-05-30 Walzenpresse
DEP4017433.6 1990-05-30

Publications (1)

Publication Number Publication Date
WO1991005913A1 true WO1991005913A1 (fr) 1991-05-02

Family

ID=25886011

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1990/001713 WO1991005913A1 (fr) 1989-10-11 1990-10-11 Calandre

Country Status (2)

Country Link
DE (1) DE4017433A1 (fr)
WO (1) WO1991005913A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0674043B1 (fr) * 1994-03-18 1997-05-07 Voith Sulzer Papiermaschinen GmbH Dispositif pour le traitement d'une bande fibreuse
EP0839952A1 (fr) * 1996-10-31 1998-05-06 Voith Sulzer Papiermaschinen GmbH Patin de pressage
EP2087984A1 (fr) * 2008-02-05 2009-08-12 Texmag GmbH Vertriebsgesellschaft Cylindre destiné à exercer une pression de contact sur des bandes de matériau

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19522761C2 (de) * 1995-06-27 2000-11-16 Voith Sulzer Papiermasch Gmbh Schuh-Preßeinrichtung
DE19616800C2 (de) * 1996-04-26 2001-03-22 Voith Sulzer Papiermasch Gmbh Anpreßvorrichtung für eine Walze
AT412218B (de) * 2002-10-17 2004-11-25 Andritz Ag Maschf Presswalze

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2057027A (en) * 1979-08-27 1981-03-25 Beloit Corp Extended nip press
DE3126492A1 (de) * 1981-06-30 1983-01-20 Escher Wyss AG, Zürich "presswalze"
DE3138365A1 (de) * 1981-09-21 1983-04-14 Escher Wyss AG, Zürich Durchbiegungseinstellwalze
EP0107607A2 (fr) * 1982-09-30 1984-05-02 Beloit Corporation Presse à pinçage prolongé
DE3239954A1 (de) * 1982-10-28 1984-05-03 J.M. Voith Gmbh, 7920 Heidenheim Walzenpresse, insbesondere fuer papierbahnen
EP0151447A2 (fr) * 1984-02-06 1985-08-14 Sulzer-Escher Wyss Gmbh Presse humide pour la déshydratation d'une matière en bande
EP0155465A1 (fr) * 1984-02-06 1985-09-25 Sulzer-Escher Wyss Gmbh Presse humide pour la déshydratation d'une matière en bande
DE3426235A1 (de) * 1984-07-17 1986-01-23 J.M. Voith Gmbh, 7920 Heidenheim Walzenpresse fuer bahnen aus papier, textilien o.dgl.
EP0254819A1 (fr) * 1986-06-20 1988-02-03 Sulzer-Escher Wyss Gmbh Elément de support hydraulique pour presse

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH610374A5 (fr) * 1975-10-24 1979-04-12 Fred H Freuler

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2057027A (en) * 1979-08-27 1981-03-25 Beloit Corp Extended nip press
DE3126492A1 (de) * 1981-06-30 1983-01-20 Escher Wyss AG, Zürich "presswalze"
DE3138365A1 (de) * 1981-09-21 1983-04-14 Escher Wyss AG, Zürich Durchbiegungseinstellwalze
EP0107607A2 (fr) * 1982-09-30 1984-05-02 Beloit Corporation Presse à pinçage prolongé
DE3239954A1 (de) * 1982-10-28 1984-05-03 J.M. Voith Gmbh, 7920 Heidenheim Walzenpresse, insbesondere fuer papierbahnen
EP0151447A2 (fr) * 1984-02-06 1985-08-14 Sulzer-Escher Wyss Gmbh Presse humide pour la déshydratation d'une matière en bande
EP0155465A1 (fr) * 1984-02-06 1985-09-25 Sulzer-Escher Wyss Gmbh Presse humide pour la déshydratation d'une matière en bande
DE3426235A1 (de) * 1984-07-17 1986-01-23 J.M. Voith Gmbh, 7920 Heidenheim Walzenpresse fuer bahnen aus papier, textilien o.dgl.
EP0254819A1 (fr) * 1986-06-20 1988-02-03 Sulzer-Escher Wyss Gmbh Elément de support hydraulique pour presse

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0674043B1 (fr) * 1994-03-18 1997-05-07 Voith Sulzer Papiermaschinen GmbH Dispositif pour le traitement d'une bande fibreuse
EP0839952A1 (fr) * 1996-10-31 1998-05-06 Voith Sulzer Papiermaschinen GmbH Patin de pressage
EP2087984A1 (fr) * 2008-02-05 2009-08-12 Texmag GmbH Vertriebsgesellschaft Cylindre destiné à exercer une pression de contact sur des bandes de matériau

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