EP0482318A1 - Durchbiegungssteuerbare Walze - Google Patents

Durchbiegungssteuerbare Walze Download PDF

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Publication number
EP0482318A1
EP0482318A1 EP91114596A EP91114596A EP0482318A1 EP 0482318 A1 EP0482318 A1 EP 0482318A1 EP 91114596 A EP91114596 A EP 91114596A EP 91114596 A EP91114596 A EP 91114596A EP 0482318 A1 EP0482318 A1 EP 0482318A1
Authority
EP
European Patent Office
Prior art keywords
bearing
hollow roller
roller
crosshead
hollow
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.)
Withdrawn
Application number
EP91114596A
Other languages
German (de)
English (en)
French (fr)
Inventor
Karl-Heinz Küsters
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.)
Eduard Kuesters Maschinenfabrik GmbH and Co KG
Original Assignee
Eduard Kuesters Maschinenfabrik GmbH and Co KG
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 Eduard Kuesters Maschinenfabrik GmbH and Co KG filed Critical Eduard Kuesters Maschinenfabrik GmbH and Co KG
Publication of EP0482318A1 publication Critical patent/EP0482318A1/de
Withdrawn legal-status Critical Current

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Classifications

    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/0006—Driving arrangements

Definitions

  • Deflection-controllable rollers are mainly used for the pressure and temperature treatment of webs made of paper, nonwoven, plastic film and textile, although their suitability is by no means limited to this. They consist of a non-rotatable crosshead and a hollow roller rotating around it, which is supported from the inside by a suitable hydraulic device against the crosshead, which can bend inside the hollow roller. The counterforce to the line load caused by the line force in the roll gap is created in normal solid rolls by a corresponding deflection of this roll. In the deflection-controllable rollers, this deflection is transmitted to the crosshead, so that the hollow roller remains independent of it and can assume a desired deflection course, in particular can remain straight.
  • the hollow roller In a number of applications, it is necessary to drive the hollow roller.
  • the drive poses considerable design problems because, in certain cases, the hollow roller is displaced in the radial direction and can also have misalignments due to deflection with respect to an axis fixed to the housing.
  • the area of attack of the drive on the hollow roller therefore has no defined position, neither with respect to the machine frame nor in particular with respect to the crosshead, which bends under any load.
  • the drives in particular in the case of the rolls in the paper industry, which can have a length of up to ten meters and a diameter of one meter, have to transmit considerable power at equally considerable peripheral speeds in the order of magnitude of one thousand meters per minute and above. An unclean gear meshing will take revenge very soon due to excessive wear.
  • the mounting of the gear housing is not particularly advantageous because the support length is limited to the width of the double roller bearing and considerable forces are exerted on this bearing when the gear housing is tilted relative to the hollow roller.
  • Deflection-controllable rollers are known from DE-PSen 25 o7 677 and 36 23 o28, in which the hollow rollers are not supported at the ends on the crosshead, but as a whole can radially shift relative to the crosshead on corresponding guides.
  • the total displacement of the ends of the hollow roll, on which the drives act, is therefore even greater because, in addition to the mere change in angle, they also include translation components.
  • a drive housing with pinion is mounted on both sides of the same on the outside of an extension of the hollow roller.
  • a constructively modified embodiment of this type is also the subject of DE-PS 36 23 o28, the special feature being that the drive pin, which carries the pinion, is designed as a hollow pin, which has an internal serration inside, in which a corresponding serration at the end of one Drive shaft engages.
  • the displacements of the drive housing were compensated for by a drive via a double-jointed source; in the latter embodiment, the drive shaft with the curved teeth accomplishes this.
  • the drive housing is mounted exclusively on the neck of the hollow roller and the hollow roller is guided within it and is guided on the crosshead by bearings or degree guides.
  • the invention has for its object to provide a pinion drive with a closed housing for a roller of the type corresponding to DE-PS 36 45 o34.
  • the inventive design of the generic roller overcomes the difficulty that the outside of the approach, on which the gear housing is mounted in the known constructions and on which the pinion engages, in the embodiment according to DE-PS 36 45 o34 by the bearing bell covered and is therefore no longer accessible from the outside.
  • An arrangement of the overall drive between the bearing bell and the end of the hollow roller would be possible in principle, but would lead to an unacceptable increase in the overall length of the roller.
  • the support length of the crosshead is already increased anyway by the arrangement of the main bearing axially outside the hollow roller. For reasons of the limitation of the deflection or the maintenance of the transferable line force and also for reasons of space, a further extension of the roller is forbidden.
  • the invention has made it possible to integrate a drive with a drive housing and pinion with a minimal axial space requirement, it being essential that the drive housing is supported on the end of the roller facing the outside of the bearing bell, so that for the storage there no additional axial space is required of the drive housing.
  • the drive housing is therefore optimal, that is to say on both sides of the drive pinion, mounted, the space for the bearing facing the adjacent end of the roller being saved by the attack from the outside.
  • a useful way of providing the external toothing is the subject of claim 2.
  • the training as a separate gear to be attached to the shoulder means a simplification in terms of production and also allows the use of a compared to the outer diameter of the approach, which must be as small as possible because of the bearing , enlarged pitch circle diameter.
  • the bearing of the drive housing facing the hollow roller can be supported on the separate gear, which facilitates an axial pulling of the entire drive unit from the shoulder.
  • the support on the gearwheel can be implemented in the manner set out in claim 4.
  • Claim 5 reflects an embodiment that is important from the aspect of an axially compact design.
  • the toothing of the gear wheel must have a certain width because of the large powers to be transmitted in order to avoid excessive flank pressures.
  • a corresponding width or thickness is not necessary in the case of the inner gear wheel disk, which is only used to transmit the torque.
  • the bearing of the gear housing can be to a certain extent nested in the gear, so that a gain in overall length that makes up at least part of the bearing width is made possible.
  • FIG. 1 An embodiment of the invention is shown.
  • the single figure shows a longitudinal section through the drive end of a deflection-controllable roller.
  • the roller designated 100 in the drawing as a whole comprises a rotating hollow roller 1, which forms the working roller circumference 2 and has a cylindrical inner circumference 4.
  • the hollow roller 1 is penetrated lengthways by an non-rotatable crosshead 3, which projects with its end 3 ′ from the hollow roller 1 and is mounted in a roller stand 6 via a self-aligning bearing 5.
  • the crosshead 3 leaves all around distance from the inner circumference 4 of the hollow roller 1 and can thus bend within the hollow roller 1 without coming into contact with the inner circumference 4.
  • the axis 7 of the crosshead 3 is displaced approximately along the line 7 'during the deflection, the deviation in the drawing 2 being exaggerated, but significant deflection amounts do occur: With very long rolls As they occur in the paper industry, the radial deviation of the crosshead 3 in the middle from the unloaded position can be up to 30 mm.
  • a hydraulic support device (not shown) is provided, which is supported by a row of support pistons acting against the inner circumference 4 of the hollow roller 1, by a hydraulic chamber which is open all round and sealed against the inner circumference 4 by a can be formed along the hollow roller 1 web piston or in a similar manner.
  • the support device allows a hydraulic force to be exerted against the inner circumference 4 or supports the hollow roller 1 in the opposite way against the line force in the Roll gap from the inside of the crosshead 3 which bends under the action of these forces.
  • an axial shoulder 20 which is fastened directly to the end face of the hollow roller 1 by means of screws 8.
  • the crosshead 3 tapers in the area of the end of the hollow roller 1 in its diameter.
  • the approach 2o makes this reduction in diameter and accordingly consists of a radial part 2 0 'fastened to the end face of the hollow roller 1 and a part 2o "which surrounds the slimmer outer part 3" of the crosshead 3 at a short distance and which is opposite the hollow roller 1 essential, in the exemplary embodiment reduced to about half the outer diameter.
  • a spherical roller bearing 9 is arranged on the outer circumference near the axial outer end of the bush-like part 2 0 ", which is supported on the outside on the inner circumference of a larger-diameter part 3o 'of a bearing bell designated as a whole by 3o a part 3 0 "of reduced diameter, on the outer circumference of which the bearing 5 is arranged, the inner diameter of which corresponds to the outer diameter of the projecting end 3 'of the crosshead 3, and which is arranged without play on a larger support length 1 on this end.
  • a mechanical seal designated as a whole is provided, which prevents hydraulic fluid from passing from the space 12 between the crosshead 3 and the inner circumference 4 of the hollow roller 1 into the region of the bearing 9.
  • the bearing 9 is lubricated separately. In this way, the lubricating fluid can be kept separate from the hydraulic fluid.
  • the part 3o 'of the bearing bell 3o is formed as a separate part which is firmly connected to the rest of the bearing bell 3o, which consists of bearing bronze and has a spherical surface 13 on the outside, the center of which lies on the axis 7 at the level of the axial central plane of the bearing 9 .
  • the batch 2o or its Part 2 0 'of smaller diameter externally surrounding multi-part drive casing 25 has an axial projection 14 which is divided in a direction perpendicular to axis 7 plane, and the inner circumference 15 corresponds to the spherical surface 13 and is mounted thereon.
  • a gearwheel 18 is arranged on the part 2 0 "close to the end of the part 3o 'facing the hollow roller 1 and is connected in a rotationally fixed manner by means of a wedge 19 which bears a spur toothing 16.
  • the spur toothing 16 has a drive pinion 17 on a drive pin 21 engages which can be connected to a drive motor or a transmission at its end 22 via a double universal joint shaft.
  • the drive pin 21 is mounted on both sides of the drive pinion 17 via bearings 23, 24 in an external part of the transmission housing 25.
  • the gear housing 25 is pulled on the hub 14 with respect to the gear 18 opposite side in front of the perpendicular to the axis part 2 0 'of the lug 2o radially inwardly.
  • the wall part local 25 'of the gear housing 25 has a circular opening 26 in which a roller bearing 27 is disposed, which with its inner ring 27' of the gear 18 is supported on the cylindrical outer peripheral surface 28 of the part 2 0 "adjacent axial approach 29th
  • the inner part 25 'surrounding the opening 26' of the wall of the drive housing 25 facing the hollow roller 1 jumps axially outwards in relation to the part 25 "of the inner boundary of the wall of the drive housing 25 which is perpendicular to the axis and engages in a circumferential, annular groove-like Indentation 31 of the side surface of the gear wheel 18 facing the hollow roller 1.
  • the axially close boundary of the indentation 31 is formed by the cylindrical outer peripheral surface 28 of the projection 29.
  • the drive housing 25 is supported with a sufficient length on both sides of the drive pinion 17, with no additional overall length being required for the attachment of the bearings holding the drive housing 25 on the left side in the drawing, because the drive housing 25 is permanently connected to the drive housing 25 Approach 14 engages from the outside over the already necessary further part 3o 'of the bearing bell 3o and only a slight axial length is required on the side facing the hollow roller 1 because the bearing 27 is partially seated in the axial extent of the gearwheel.
  • the support is "mixed", namely on one side on the shoulder 2o connected to the hollow roller 1 and on the other side on the bearing bell 3 0 connected to the crosshead 3.
  • the angular displacements of the hollow roller 1 and Crosshead 3 are caught by the spherical design of the bearing surfaces 13, 15 on the neck 14, which can slide on each other.

Landscapes

  • Rolls And Other Rotary Bodies (AREA)
  • General Details Of Gearings (AREA)
  • Nonwoven Fabrics (AREA)
  • Paper (AREA)
  • Extrusion Moulding Of Plastics Or The Like (AREA)
EP91114596A 1990-10-23 1991-08-30 Durchbiegungssteuerbare Walze Withdrawn EP0482318A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4033638A DE4033638C1 (fi) 1990-10-23 1990-10-23
DE4033638 1990-10-23

Publications (1)

Publication Number Publication Date
EP0482318A1 true EP0482318A1 (de) 1992-04-29

Family

ID=6416856

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91114596A Withdrawn EP0482318A1 (de) 1990-10-23 1991-08-30 Durchbiegungssteuerbare Walze

Country Status (6)

Country Link
US (1) US5174002A (fi)
EP (1) EP0482318A1 (fi)
JP (1) JPH04272293A (fi)
CA (1) CA2054002A1 (fi)
DE (1) DE4033638C1 (fi)
FI (1) FI914960A (fi)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0790350A1 (de) * 1996-02-19 1997-08-20 Andritz-Patentverwaltungs-Gesellschaft m.b.H. Saugwalze
DE10024851A1 (de) * 2000-05-19 2002-01-31 Netzsch Erich Holding Walze mit Durchbiegungsausgleich

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4227643C2 (de) * 1992-08-21 1996-01-11 Roland Man Druckmasch Lagerung für Zylinder und Trommeln in Druckmaschinen
WO1996005367A2 (en) * 1994-08-16 1996-02-22 Beloit Technologies, Inc. Hydrostatic self-loading controlled deflection roll
FI100350B (fi) * 1995-06-02 1997-11-14 Raahen Tevo Oy Levitystelan käytön kytkentä
DE19705638A1 (de) * 1997-02-14 1998-09-03 Kuesters Eduard Maschf Walzvorrichtung für die Druckbehandlung von Warenbahnen
US6843762B2 (en) 2000-12-18 2005-01-18 Spencer Johnston Company Spreader roll
FI116413B (fi) * 2001-05-31 2005-11-15 Metso Drives Oy Käyttövaihteiston ja telan välinen rakenne
US6482141B1 (en) 2001-07-25 2002-11-19 Spencer Johnston Company Flexible end supporting arrangement for direct drive adjustable spreader rolls
JP2003048006A (ja) * 2001-08-02 2003-02-18 Mitsubishi Heavy Ind Ltd 流体圧シリンダ及び圧延機
FI117646B (fi) * 2004-10-04 2006-12-29 Metso Paper Inc Tela
WO2009131594A1 (en) * 2008-04-21 2009-10-29 Lubrication Systems Company Of Texas, Llc Self aligning bearing and seal assembly
DE102010060494A1 (de) * 2010-11-11 2012-05-16 Andritz Küsters Gmbh Walzenanordnung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3766620A (en) * 1972-08-08 1973-10-23 Beloit Corp Controlled deflection roll drive
GB2046869A (en) * 1979-03-29 1980-11-19 Valmet Oy Roll drive eg in a paper machine
EP0043119A1 (de) * 1980-06-28 1982-01-06 J.M. Voith GmbH Presswalze, deren Durchbiegung einstellbar ist
DE3623028C2 (fi) * 1986-07-09 1990-02-01 J.M. Voith Gmbh, 7920 Heidenheim, De
DE3645034C2 (en) * 1986-03-13 1990-04-05 Eduard Kuesters, Maschinenfabrik, Gmbh & Co Kg, 4150 Krefeld, De Roller with hollow peripheral working section

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3855681A (en) * 1972-02-18 1974-12-24 Usm Corp Drive for shell-type rolls
CH588308A5 (fi) * 1975-02-18 1977-05-31 Escher Wyss Ag
FI800386A (fi) * 1980-02-07 1981-03-19 Valmet Oy Mekanisk drivanordning foer en pao en fast axel lagrad roterbar mantel
DE3330204C2 (de) * 1983-08-20 1986-07-31 J.M. Voith Gmbh, 7920 Heidenheim Stirnradgetriebe für den Antrieb eines Walzenmantels
ES2021612B3 (es) * 1986-03-13 1991-11-16 Kuesters Eduard Maschf Cilindro.
US4837907A (en) * 1987-08-20 1989-06-13 Beloit Corporation Self-loading controlled deflection roll

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3766620A (en) * 1972-08-08 1973-10-23 Beloit Corp Controlled deflection roll drive
GB2046869A (en) * 1979-03-29 1980-11-19 Valmet Oy Roll drive eg in a paper machine
EP0043119A1 (de) * 1980-06-28 1982-01-06 J.M. Voith GmbH Presswalze, deren Durchbiegung einstellbar ist
DE3645034C2 (en) * 1986-03-13 1990-04-05 Eduard Kuesters, Maschinenfabrik, Gmbh & Co Kg, 4150 Krefeld, De Roller with hollow peripheral working section
DE3623028C2 (fi) * 1986-07-09 1990-02-01 J.M. Voith Gmbh, 7920 Heidenheim, De

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0790350A1 (de) * 1996-02-19 1997-08-20 Andritz-Patentverwaltungs-Gesellschaft m.b.H. Saugwalze
DE10024851A1 (de) * 2000-05-19 2002-01-31 Netzsch Erich Holding Walze mit Durchbiegungsausgleich
DE10024851B4 (de) * 2000-05-19 2005-06-16 Erich Netzsch Gmbh & Co Holding Kg Walze mit Durchbiegungsausgleich
DE10024851C5 (de) * 2000-05-19 2010-12-16 Erich Netzsch Gmbh & Co Holding Kg Walze mit Durchbiegungsausgleich

Also Published As

Publication number Publication date
DE4033638C1 (fi) 1992-02-13
CA2054002A1 (en) 1992-04-24
FI914960A (fi) 1992-04-24
JPH04272293A (ja) 1992-09-29
FI914960A0 (fi) 1991-10-22
US5174002A (en) 1992-12-29

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