EP1793037B1 - Presswalze mit flexiblem Mantel für eine Schuhpresse - Google Patents

Presswalze mit flexiblem Mantel für eine Schuhpresse Download PDF

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Publication number
EP1793037B1
EP1793037B1 EP05111682A EP05111682A EP1793037B1 EP 1793037 B1 EP1793037 B1 EP 1793037B1 EP 05111682 A EP05111682 A EP 05111682A EP 05111682 A EP05111682 A EP 05111682A EP 1793037 B1 EP1793037 B1 EP 1793037B1
Authority
EP
European Patent Office
Prior art keywords
sleeve
attachment
segments
flange
translation
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
EP05111682A
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English (en)
French (fr)
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EP1793037A1 (de
Inventor
Francis Boffano
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.)
ALLIMAND
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ALLIMAND
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Filing date
Publication date
Application filed by ALLIMAND filed Critical ALLIMAND
Priority to PL05111682T priority Critical patent/PL1793037T3/pl
Priority to AT05111682T priority patent/ATE403030T1/de
Priority to EP05111682A priority patent/EP1793037B1/de
Priority to ES05111682T priority patent/ES2311936T3/es
Priority to DE602005008623T priority patent/DE602005008623D1/de
Publication of EP1793037A1 publication Critical patent/EP1793037A1/de
Application granted granted Critical
Publication of EP1793037B1 publication Critical patent/EP1793037B1/de
Active 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
    • D21F3/0227—Belts or sleeves therefor
    • D21F3/0245—Means for fixing the sleeve to the roller end

Definitions

  • the present invention relates to the technical field of shoe presses used, particularly in the field of papermaking or paperboard, without it being necessary to consider that this is an exclusive application.
  • a shoe press comprises a pressure roller with a flexible sleeve, inside which is disposed a shoe that comes to apply the flexible sleeve to the surface of a rigid counter-cylinder, to define an extended zone for pressurizing a tablecloth flexible, such as a sheet of paper or cardboard being developed, to express the moisture.
  • a tablecloth flexible such as a sheet of paper or cardboard being developed
  • the invention relates to the embodiment of the pressure roller with flexible sleeve.
  • such a pressure roll comprises a flexible tubular sleeve, a carrier shaft and two flanges for holding and guiding the flexible sleeve in rotation, along an axis ⁇ , which are fitted on the carrier shaft and each comprise a control system. fixing the corresponding end of the sleeve.
  • the invention relates, more particularly, to the embodiment of the fastening systems of the flexible sleeve on the flanges.
  • this fastening system is relatively important, insofar as it is necessary to be able to regularly change the sleeve, because of the wear that it is likely to know.
  • this change operation must be performed as quickly as possible, to reduce, as much as possible, the shutdown time of the installation in which the shoe press is integrated.
  • a patent EP 0 442 257a proposed to come to pinch the extreme edges of the sleeve by means of a system of fixed and movable jaws, the movable jaws having a frustoconical bearing operating with a ramp of complementary shape, so that an axial translation of the movable jaws induces a pinch of the flexible sleeve, between said movable jaw and the fixed jaw.
  • each fastening system comprises, on the one hand, a fixed inner jaw of frustoconical shape with which is associated an outer jaw also having a frustoconical bearing surface for gripping, with the complementary bearing of the inner jaw, the sleeve.
  • the outer jaw has, in addition, a series of slots provided with pins for the attachment of the sleeve.
  • the fastening system according to the patent US 4,878,281 has the disadvantage of inducing, during the power of the sleeve, a series of folds near each flange. These folds do not disappear until a certain distance from the end of the sleeve and it is then necessary to increase the length of the sleeve and the pressure roller relative to the effective length of the press corresponding to the pressure zone. .
  • the use of the segments which are mobile at least in radial translation, makes it possible to reduce the diameter of the cylindrical bearing surface for said sleeve during mounting of the sleeve, so that its positioning is easy and it is not necessary to exert a major force of traction on the sleeve to pass it at the range defined by the snap segments.
  • the reduction of the diameter by placing in the retracted position of the gripping segments, facilitates, by giving slack to the sleeve, the establishment of the eyelets of the fastening tabs on the corresponding fastening studs.
  • This implementation can then be performed without the use of a particular tool and without effort on the part of the operator.
  • the use of the sleeve smoothing band makes it possible to eliminate the appearance of folds during the tensioning of said sleeve, so that it is not necessary to increase the dimensions to remove the sleeve. active part of the sleeve of the attachment zone of the latter, as would be the case in the absence of the smoothing band.
  • the smoothing band does not intervene to ensure clamping of the sleeve by pinching but only for the purpose of removing the folds.
  • the radial distance between the bearing surface of the band fixed on the flange and the segments of hooking in the working position is greater than or equal to the thickness of the constituent material of the sleeve at rest.
  • the smoothing ring has, at its bearing surface, an annular sealing gasket intended to cooperate with the outer surface of the sleeve.
  • the attachment segments are movable relative to the corresponding flanges, according to a combined movement of axial and radial translations.
  • the displacement in axial translation of the annular carriage can then be achieved in different ways and, for example, be carried out by the implementation of a set of double acting hydraulic cylinders, arranged at the periphery of the flange and having each a direction parallel to the axis of rotation of the cylinder.
  • each fastening system comprises at least two gripping segments.
  • the fastening system comprises at least three gripping segments.
  • the number of snap rings can be chosen according to the diameter of the sleeve.
  • each end of the sleeve comprises at least twelve fastening tabs and at most twenty-eight fastening tongues.
  • the number of tabs Fixing will also be optimized according to the size of the sleeve in order to give the latter the best possible geometry in working conditions.
  • At least one of the flanges comprises removable means for supporting the corresponding smoothing band in an unobstructed position relative to the segments of the sleeve. hooking.
  • the invention also relates to a shoe press comprising a sleeve press cylinder, as mentioned above, and a counterpressure cylinder placed opposite the sleeve press cylinder to cooperate with the latter and define a treatment or treatment zone. pressurizing a wet fibrous web.
  • the Fig. 1 is a schematic section of a shoe press using a flexible sleeve cylinder according to the invention.
  • the Fig. 2 is a partial section along line II-II of the Fig. 1 .
  • Fig. 3 and 4 are detailed views, in axial cross-section of zone A of the Fig. 1 , showing a part of the sleeve fixing system, respectively in the retracted position and in the working position.
  • a shoe press as illustrated in Fig. 1 comprises a carrier structure S , schematically in dash, on which is fitted a flexible sleeve press cylinder, generally designated by the reference 1 and a counterpressure cylinder C.
  • the general design of such a shoe press is not within the scope of this patent and is widely known to those skilled in the art, including machinery for the manufacture and processing of paper or cardboard.
  • the pressure roller with flexible sleeve 1 comprises, in addition to a sleeve 2, a carrier shaft 3 equipped with two flanges 4 for holding and guiding the sleeve in rotation along an axis ⁇ .
  • the carrier shaft 3 is fixed and the flanges 4 are adapted to the shaft 3, by means of bearings 5, so as to be rotatable about the axis ⁇ .
  • the shaft 3 is furthermore equipped with a shoe 6 intended to press the sleeve 2 against the cylinder C.
  • the flanges 4 are adapted to the shaft so as to be movable in axial translation with respect to the shaft 3 which is, in addition, equipped with hydraulic cylinders 7 which make it possible to apply an axial tension to the sleeve 2.
  • the invention relates, more particularly, to the method of fixing the sleeve to the flanges 4.
  • the flexible tubular sleeve 2 has, at each of its ends 10, a series of flexible tongues 12 , a portion of which is visible at Fig. 2 .
  • each end 10 preferably has at least twenty tabs being understood that the case of small diameters of sleeves it could fewer tabs are required, the number of tabs preferably being greater than twelve.
  • the sleeve comprises twenty four fastening tongues 12 of which only six tongues visible to the Fig. 2 .
  • the number of tongues 12 could also be greater than twenty four, preferably less than twenty-eight, depending, in particular, on the dimensions of the sleeve and the stresses to which it is subjected.
  • each of these tongues 12 is furthermore provided with at least one and, according to the illustrated example, exactly one attachment eyelet 13 , the function of which will be more particularly described below.
  • each flange 4 comprises a fastening system 15 of the corresponding end 10 of the sleeve 2.
  • each fastening system of the sleeve 2 comprises at least two and, according to the illustrated example, six gripping segments 16 integral with the corresponding flange 4 being distributed at the periphery thereof.
  • the segments 16 are movable in a combined movement of axial and radial translation between a retracted position, as illustrated in FIG. Fig. 3 , and a working position, as illustrated in Fig. 4 .
  • each fastening system 15 comprises, as operating means, an annular carriage 17 which is fitted on the corresponding flange 4, so as to be movable in translation. axial and on which are fixed the segments 16, so as to be movable relative to the annular carriage 17 in radial translation.
  • Each attachment segment 16 then comprises an internal ramp 18 in the form of a cone portion, which bears on an outer annular ramp 19 provided by the corresponding flange 4.
  • the annular ramp 19 of the flange 4 then has the shape of a truncated cone axis ⁇ which converges towards the inside of the pressure roller 1.
  • the annular ramp 19 and the ramps 18 of the attachment segments 16 have a complementary shape.
  • any axial translation of the annular carriage 17 corresponds to a combined movement of axial and radial translations of the segments 16.
  • each attachment system 15 comprises, as translation drive means of the carriage 17, at least one helical thread 20 arranged, according to the illustrated example, on the outer periphery of the annular carriage.
  • the translational means of the annular carriage also comprises a ring 21 which is fitted on the flange 4 corresponding to be movable in rotation axis ⁇ .
  • the ring 21 then has at least one helical thread 22 intended to cooperate with the thread 20 of the annular carriage 17, so that a rotation of the ring 21 causes the carriage 17 to be translated .
  • Each fastening system 15 further comprises, as means for rotating the crown 21, a pinion 23 which meshes with a toothed sector 24 connected to the crown and which is actuated by a shaft 25 having, on the outside face corresponding flange 4 , a receiving head 26, either for a crank, or for an electrical or pneumatic actuator.
  • each segment 16 comprises, according to the illustrated example, four pins 27 , as shown in FIG. Fig. 2 .
  • the number of pins 27, equipping each segment 16 is a function, on the one hand, of the total number of eyelets 13 and therefore of tongues and, on the other hand, of the total number of segments 16.
  • the pins 27 are disposed on the face of each segment 16 perpendicular to the axis ⁇ and oriented towards the outside of the sleeve 2 .
  • Each system 15 for fixing one end of the sleeve 2, as described above, is implemented in the following manner.
  • the segments 16 are placed in the retracted position R , as illustrated in FIG. Fig. 3 , so that they define, by their outer surface 30, a cylindrical seat having a diameter smaller than the nominal working diameter of the sleeve and less than the internal diameter of the sleeve.
  • each end 10 of the sleeve 2 is at the level of the corresponding flange 4 and each eyelet 13 can be engaged on a pin 27.
  • This operation is particularly facilitated by the slack of the sleeve 2 given, in particular, by the difference between the inside diameter of the sleeve and the outside diameter of the span defined by the segments 16 in the retracted position R.
  • each fastening system 15 is rotated from the head 26 , so as to rotate around the axis ⁇ , the ring 21 , so that the annular carriage 17 is moved in translation in the direction of the arrow F 1 and that the segments 16 experience a combined axial and radial translation movement which brings them to the working position T , as illustrated in FIG. Fig. 4 .
  • the outer surface of the segments 16 then defines a cylindrical bearing surface for holding the sleeve 2 to a nominal working diameter greater than or equal to the inside diameter of the sleeve at rest.
  • a smoothing band 35 is set up. of the sleeve 2.
  • the purpose of this hoop 35 is not pinching the sleeve against the segments 16, but rather to smooth folds may arise during the application of axial tension to the sleeve 2.
  • the The band 35 is made in such a way that the radial distance d between, on the one hand, the surface 30 of the segments 16 in working position and, on the other hand, the bearing surface 36 of the band 35 is greater than or equal to to the thickness e of the constituent material of the sleeve 2 when it is subjected to the maximum axial stretching stress which it is likely to undergo during use of the cylinder 2.
  • the distance d will preferably be chosen for be greater than or equal to the thickness e of the constituent material of the sleeve at rest, as shown in FIG. Fig. 4 .
  • each band 35 further comprises a groove 37 in which is disposed a seal 38 which is applied on the outer surface of the sleeve 2 , so as to provide a static sealing. It will be noticed that each band 35 is fixed on an annular flange 39 of the corresponding flange 4 . The outer diameter of the flange 39 is then less than or equal to the diameter of the span defined for the outer surfaces 30 of the segments in the retracted position R and this so as not to hinder the introduction of the sleeve 2.
  • the annular carriage 17 abuts in the working position T against the ramp 19, so that the working position corresponds to the maximum radial extension position of the segments 16.
  • the combined axial and radial translation movement of the segments 16 allows, at the same time, a reduction in the diameter of the flange 4 to facilitate the passage of the flexible sleeve 2, but also a reduction of the distance between the fastening segments of the two fastening systems 15 of the two flanges 4 in the retracted position relative to the working position, so that it further facilitates the positioning of the sleeve by giving the extra slack for the introduction of the sleeve, soft which is then caught automatically when moving to the working position.

Landscapes

  • Paper (AREA)
  • Press Drives And Press Lines (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Mutual Connection Of Rods And Tubes (AREA)

Claims (11)

  1. Druckzylinder mit flexibler Muffe für eine Backenpresse, umfassend:
    - eine flexible röhrenförmige Muffe (2), die im Bereich jedes ihrer beiden Enden eine Reihe von flexiblen Befestigungslaschen (12) aufweist, wobei jede Lasche (12) mit mindestens einer Befestigungsöse (13) versehen ist,
    - eine Tragwelle (3),
    - zwei Flansche (4), die die Muffe (2) um eine Achse Δ drehbar halten und führen und die an die Tragwelle (3) angepaßt sind und jeweils ein System (15) zur Befestigung des entsprechenden Endes (10) der Muffe (2) umfassen, wobei jedes Befestigungssystem (15) auf einer im wesentlichen zur Drehachse des Zylinders senkrechten Seite eine Reihe von Stücken (27) zur Befestigung der Ösen (13) der Laschen (12) zur Befestigung des entsprechenden Endes der Muffe umfaßt,
    dadurch gekennzeichnet, daß jedes Befestigungssystem der Muffe umfaßt:
    - mindestens zwei Befestigungssegmente (16), die mit dem entsprechenden Flansch (4) verbunden und in Bezug zu dem Flansch (4) zumindest in radialer Translation beweglich sind zwischen:
    - einer sogenannten Arbeitsposition (T), in der die Segmente (16) in der äußersten radialen Dehnungsposition sind und eine zylindrische Fläche zum Halten der Muffe (2) auf einem Nominalarbeitsdurchmesser definieren,
    - einer sogenannten Einzugsposition (R), in der die Segmente (16) in eingezogener Position sind und eine zylindrische Fläche definieren, die einen Durchmesser aufweist, der kleiner ist als der Nominalarbeitsdurchmesser, wobei jedes Segment (16) einen Teil der Befestigungsstücke (27) für die Muffe (2) trägt,
    - Mittel zum Verschieben der Befestigungssegmente (16) zwischen ihrer Arbeitsposition (T) und ihrer Einzugsposition (R) und
    - einen Glättring (35) der Muffe (2), der abnehmbar auf dem entsprechenden Flansch (4) befestigt ist und eine innere zylindrische Fläche (36) zur Abstützung auf der Außenfläche der Muffe im Bereich der Auflagefläche, die durch die Befestigungssegmente (16) in Arbeitsposition (T) definiert ist, aufweist, wobei der Radialabstand zwischen der Auflagefläche (36) des Rings (35), der auf dem Flansch (4) befestigt ist, und den Befestigungssegmenten (16) in Arbeitsposition (T) größer oder gleich der Dicke (e) des die Muffe (2) bildenden Materials ist, wenn sie der maximalen axialen Dehnungskraft ausgesetzt ist, der die Muffe (2) während der Verwendung des Zylinders standhalten kann.
  2. Druckzylinder nach Anspruch 1, dadurch gekennzeichnet, daß der Radialabstand (d) zwischen der Auflagefläche (36) und dem Ring (35), der auf dem Flansch (4) befestigt ist, und den Befestigungssegmenten (16) in Arbeitsposition (T) größer oder gleich der Dicke (e) des die Muffe (2) bildenden Materials in Ruheposition ist.
  3. Druckzylinder nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Glättring (35) im Bereich seiner Auflagefläche eine Ringdichtung (38) aufweist, die dazu bestimmt ist, mit der Außenfläche der Muffe (2) zusammenzuwirken.
  4. Druckzylinder nach Anspruch 3, dadurch gekennzeichnet, daß der Glättring im Bereich seiner Auflagefläche eine Rille (37) für die Aufnahme der Dichtung (38) aufweist.
  5. Druckzylinder nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Befestigungssegmente (16) in Bezug zum Flansch (4) in einer kombinierten axialen und radialen Translationsbewegung beweglich sind.
  6. Druckzylinder nach Anspruch 5, dadurch gekennzeichnet, daß:
    - der Flansch (4) eine ringförmige kegelstumpfartige zum Inneren des Zylinders konvergierende Rampe (19) der Achse Δ umfaßt,
    - jedes Befestigungssegment (16) eine Rampe (18) umfaßt, die dazu bestimmt ist, mit der ringförmigen Rampe (19) des Flansches (4) zusammenzuwirken,
    - die Mittel zum Verschieben der Befestigungssegmente (16) umfassen:
    - einen ringförmigen Wagen (17), der an den Flansch (4) angepaßt ist, um in Bezug zum Flansch (4) in axialer Translation zwischen zwei Positionen, einer sogenannten Arbeitsposition und einer sogenannten Einzugsposition, beweglich zu sein, der in axialer Translation mit jedem der Befestigungssegmente (16) verbunden ist, so daß eine Translation des Wagens (17) zu einer kombinierten axialen und radialen Translationsbewegung jedes der Befestigungssegmente (16) führt, wobei die Segmente in äußerster radialer Dehnungsposition oder Arbeitsposition (T) sind, wenn der Wagen (17) in Arbeitsposition ist,
    - und Mittel für den Translationsantrieb des Wagens (17).
  7. Druckzylinder nach Anspruch 6, dadurch gekennzeichnet, daß die Mittel für den Translationsantrieb des Wagens umfassen:
    - mindestens ein spiralförmiges Netz (20), das auf dem ringförmigen Wagen (17) angeordnet ist,
    - eine Krone (21), die an den Flansch (4) angepaßt ist, um in Drehung um die Achse Δ beweglich zu sein, und die ein spiralförmiges Netz (22) aufweist, das dazu bestimmt ist, mit jenem des ringförmigen Wagens (17) zusammenzuwirken, so daß eine Drehung der Krone (21) zu einer Translation des Wagens (17) führt,
    - und Mittel zur Betätigung der Krone in Drehung, umfassend ein Ritzel (23), das in einen Zahnsektor (24), der mit der Krone (21) verbunden ist, eingreift.
  8. Druckzylinder nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß er mindestens drei Befestigungssegmente (16) umfaßt.
  9. Druckzylinder nach Anspruch 8, dadurch gekennzeichnet, daß jedes Ende der flexiblen Muffe (2) mindestens zwölf Befestigungslaschen (12) und höchstens achtundzwanzig Befestigungslaschen (12) umfaßt.
  10. Druckzylinder nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß mindestens einer der Flansche (4) abnehmbare Mittel (40) zur Unterstützung des entsprechenden Glättringes (35) in einer in Bezug zu den Befestigungssegmenten (16) freien Position umfaßt.
  11. Backenpresse, umfassend einen Druckzylinder mit flexibler Muffe nach einem der Ansprüche 1 bis 9 und einen Gegenzylinder (C), der gegenüber dem Druckzylinder (1) mit Muffe angeordnet ist, um mit diesem letztgenannten zusammenzuwirken und eine Behandlungszone einer feuchten Faserschicht zu definieren.
EP05111682A 2005-12-05 2005-12-05 Presswalze mit flexiblem Mantel für eine Schuhpresse Active EP1793037B1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PL05111682T PL1793037T3 (pl) 2005-12-05 2005-12-05 Cylinder dociskowy z giętkim manszonem do prasy ślizgowej
AT05111682T ATE403030T1 (de) 2005-12-05 2005-12-05 Presswalze mit flexiblem mantel für eine schuhpresse
EP05111682A EP1793037B1 (de) 2005-12-05 2005-12-05 Presswalze mit flexiblem Mantel für eine Schuhpresse
ES05111682T ES2311936T3 (es) 2005-12-05 2005-12-05 Cilindro de presion de manguito flexible para prensa de mordaza.
DE602005008623T DE602005008623D1 (de) 2005-12-05 2005-12-05 Presswalze mit flexiblem Mantel für eine Schuhpresse

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05111682A EP1793037B1 (de) 2005-12-05 2005-12-05 Presswalze mit flexiblem Mantel für eine Schuhpresse

Publications (2)

Publication Number Publication Date
EP1793037A1 EP1793037A1 (de) 2007-06-06
EP1793037B1 true EP1793037B1 (de) 2008-07-30

Family

ID=35517138

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05111682A Active EP1793037B1 (de) 2005-12-05 2005-12-05 Presswalze mit flexiblem Mantel für eine Schuhpresse

Country Status (5)

Country Link
EP (1) EP1793037B1 (de)
AT (1) ATE403030T1 (de)
DE (1) DE602005008623D1 (de)
ES (1) ES2311936T3 (de)
PL (1) PL1793037T3 (de)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3805350A1 (de) * 1988-02-20 1989-08-31 Voith Gmbh J M Presswalze zum behandeln bahnfoermigen gutes
JPH10158987A (ja) * 1996-09-24 1998-06-16 Mitsubishi Heavy Ind Ltd 抄紙機用プレス装置
US5700357A (en) * 1996-10-16 1997-12-23 Beloit Technologies, Inc. Mechanical blanket clamp in rotating head assembly
DE19643910A1 (de) * 1996-10-30 1998-05-07 Voith Sulzer Papiermasch Gmbh Preßwalze zum Behandeln bahnförmigen Gutes und Schuhpresse mit einer solchen Preßwalze
JP2003013383A (ja) * 2001-07-02 2003-01-15 Mitsubishi Heavy Ind Ltd プレスロール

Also Published As

Publication number Publication date
ATE403030T1 (de) 2008-08-15
PL1793037T3 (pl) 2009-04-30
ES2311936T3 (es) 2009-02-16
DE602005008623D1 (de) 2008-09-11
EP1793037A1 (de) 2007-06-06

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