EP0343440B1 - Cylindre de laminoir comportant une bague montée sur un arbre - Google Patents

Cylindre de laminoir comportant une bague montée sur un arbre Download PDF

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Publication number
EP0343440B1
EP0343440B1 EP89108513A EP89108513A EP0343440B1 EP 0343440 B1 EP0343440 B1 EP 0343440B1 EP 89108513 A EP89108513 A EP 89108513A EP 89108513 A EP89108513 A EP 89108513A EP 0343440 B1 EP0343440 B1 EP 0343440B1
Authority
EP
European Patent Office
Prior art keywords
ring
rolling
shaft
retaining
clamping
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.)
Expired - Lifetime
Application number
EP89108513A
Other languages
German (de)
English (en)
Other versions
EP0343440A1 (fr
Inventor
Uwe Kark
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to AT89108513T priority Critical patent/ATE66836T1/de
Publication of EP0343440A1 publication Critical patent/EP0343440A1/fr
Application granted granted Critical
Publication of EP0343440B1 publication Critical patent/EP0343440B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/02—Shape or construction of rolls
    • B21B27/03—Sleeved rolls
    • B21B27/035—Rolls for bars, rods, rounds, tubes, wire or the like
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B2013/006—Multiple strand rolling mills; Mill stands with multiple caliber rolls

Definitions

  • the invention relates to a rolling device with a shaft, a rolling ring arranged on the shaft and an arrangement for securing a constant operating position of the rolling ring on the shaft.
  • a rolling device according to the preamble of claim 1 is already known from US-A-4117705.
  • the rolling ring is partly clamped radially via a conical sleeve and partly axially via a strong ring spring by means of a nut provided on a thread of the shaft.
  • the nut acts on a ring arranged between the conical sleeve and the spring, which can also be preloaded by a hydraulic force tensioning device which sits on the shaft thread on the side of the nut facing away from the rolling ring and whose force is applied to the ring radially outside the nut by means of a sleeve must be transferred.
  • This arrangement is expensive and bulky in the axial direction.
  • it is disadvantageous to use a nut the load-bearing number of thread turns is known to be limited, as an adjustable clamping element.
  • a threaded nut is also used for tensioning the rolling ring.
  • a hydraulic tensioning device is used to generate a hydraulic prestressing force, which has to be installed separately and comprises a tensioning sleeve surrounding the rolling ring.
  • This arrangement has the disadvantage that the hydraulic tensioning device is complex and cumbersome to use.
  • the clamping sleeve covers the outside of the rolling ring and therefore an optical control of the rolling ring is not possible during the clamping process.
  • it can only be used with overhung roller ring assemblies.
  • there are also the problems caused by the use of a threaded nut as a ring stop namely the fact that the load-bearing number of thread turns is limited.
  • the width of the compensation ring must be less than the width of the gap, because otherwise the compensation ring would not be mountable; moreover, compensation rings cannot be used continuously different axial dimensions are kept in stock. Therefore, the achievable axial operating clamping force is always considerably lower than in the case of devices which allow the clamping state achieved by the hydraulic clamping force to be infinitely fixed.
  • the invention relates to the known type of rolling device in which the securing of a constant operating position of the rolling ring on the shaft takes place essentially by means of an axial operating clamping force and in which the arrangement essentially comprises: two retaining rings axially fixed to the shaft on both sides of the rolling ring ; a hydraulic power clamping device for transferring the rolling device from the unclamped state into a preliminary clamping position in which the rolling ring is supported on the end face on one of the two retaining rings; a receiving space for a compensating ring between the other of the two retaining rings and the rolling ring; a compensation ring in the receiving space, which can be brought into the operating position in the provisional clamping position of the arrangement, in which its axial dimension is greater than the axial dimension of the receiving space in the untensioned state, such that the operating clamping force between the two after releasing the hydraulic force clamping device Retaining rings is transferred via the roller ring and the compensation ring in the operating position.
  • the object on which the invention is based is to improve this rolling device with regard to the space requirement, the manufacturing and operating effort and the clamping security.
  • the solution according to the invention is that, starting from a device according to the preamble of claim 1, the compensating ring and a ring adjacent to it can be rotated relative to one another and on their end faces with sawtooth-shaped, distributed over the circumference, complementary inclined surfaces with less in relation to the circumferential direction, far below the slope of the self-locking limit.
  • a rolling ring arrangement which comprises two rolling rings, the spacing of which is adjustable, for rolling H-shaped steel profiles.
  • They On the mutually facing end faces, they have sawtooth-shaped inclined surfaces distributed over the circumference, which interact with complementary inclined surfaces of an adjusting ring arranged between them.
  • This can be rotated by means of a hydraulic motor contained in the arrangement, as a result of which the roller rings are either pushed apart axially or are given the possibility of mutual approximation under the influence of a further hydraulic drive.
  • the slope of the inclined surfaces is relatively large and presumably not below the self-locking limit. This is possible because they are not intended to maintain the operating position of the roller rings.
  • conical sleeves are provided between the clamping rings and the shaft, which are tensioned by a spring in order to ensure the operational connection between the shaft and the rolling rings, and can be released by a hydraulic drive if the rolling rings are to be adjusted relative to one another.
  • This document does not contain the teaching that the operating clamping force for rolling rings can be generated under the very special design requirements of the invention by a ring with inclined faces at the end.
  • the one retaining ring which can be formed by a threaded nut on a shaft thread, is first set against the rolling ring as far as possible and without play, the complementary sawtooth surfaces of the retaining ring and the compensation ring are in deepest engagement.
  • the roll ring arrangement is then put under tension by the hydraulic power tensioning device. This loosens the mutual contact of the rings and creates axial play. Now the compensation ring is turned relative to the retaining ring until the axial play has disappeared. Then the hydraulic tension can be released.
  • the arrangement is extremely simple because the hydraulic power clamping device can be contained on or in the one retaining ring, expediently radially inside the compensating ring, so that it is easily accessible from the outside and without the need for a surrounding force-transmitting sleeve. Since the power clamping device is integrated in the adjustable retaining ring, the axial space requirement is small. In contrast to a nut, which must be relatively large for a given load, the compensating ring can transmit high axial forces even with small dimensions, because the entire contact surface of the complementary inclined surfaces can be regarded as load-bearing.
  • the shaft-fixed designed as a nut retaining ring with a view to the power transmission via the thread on the shaft must have a considerable cross-sectional dimension, not only the hydraulic power clamping device, but also the compensating ring can be accommodated in its cross section, which further reduces the space requirement and the arrangement is simplified.
  • the force clamping device and the compensating ring can then act parallel to one another on one and the same ring adjacent to the retaining ring, preferably even on the same end face of this ring.
  • the device according to the invention allows the transmission of unusually large axial forces, it is particularly suitable for arrangements in which the rolling ring or the Roll rings are predominantly or even axially clamped.
  • the application of the invention can be used both in the case of roll stands mounted on both sides of the roll ring and in the case of overhung use.
  • the invention is also applicable not only to rolling devices, but simply when in a clamping arrangement consisting of a bolt, an abutment connected to the bolt and a retaining ring, any parts located between the abutment and the retaining ring, preferably surrounding the bolt in an axial manner Direction must be set under compressive stress, whereby the bolt is stretched.
  • a tensioning arrangement according to the preamble of claim 4 is known from US-A-4117705.
  • the shaft 1 forms or carries a shaft-fixed collar 2 which, as a retaining ring on one side of the rolling ring, forms an abutment for the rolling ring tension and can be formed in one piece with the shaft, but need not be.
  • the roller rings 3 are mounted on the shaft 1 with intermediate rings 4 and centered either directly on the shaft circumference or by further means, not shown.
  • the shaft is provided with a thread 5 on which a nut 6 sits, which forms the other retaining ring.
  • a thread 5 on which a nut 6 sits, which forms the other retaining ring.
  • roller rings 3 are clamped axially between the retaining rings 2 and 6.
  • the nut 6 contains an annular piston 7, which can be acted upon via lines 8 with hydraulic medium.
  • the nut 6 contains on the outside and on its end facing the rolling ring arrangement 3, 4 a recess 9, which forms the receiving space for the compensating ring 10.
  • Both the hydraulic power tensioning device 7 and the compensating ring are thus accommodated in a space-saving manner in the longitudinal sectional area of the nut 6.
  • the shape of the elements involved, in particular also of the adjacent intermediate ring 4, on which the force clamping device and the compensating ring act, is very simple.
  • the cooperating end faces 11 of the nut 6 and the compensating ring 10 are, as can be seen in the lower half of the figure, sawtooth-shaped with a very low slope.
  • the slope of the flank must be very low, i.e. are very far below the self-locking limit, so that the clamping arrangement cannot be loosened by rotating forces acting on the roller ring. In extreme cases, it may be appropriate to choose the direction of the slope so that the axial tension is increased when the compensating ring 10 is rotated relative to the ring 6 by the drive torque.
  • the compensating ring is first rotated as far as possible so that the sawtooth surfaces 11 are in deepest engagement and the common axial length of the compensating ring 10 and the retaining ring 6 is minimal. Then the nut 6 is screwed on as tightly as possible, so that only a slight axial compression of the rolling ring arrangement 3, 4 is to be expected when the force clamping device is activated. If the annular piston 7 is then acted upon by hydraulic fluid, the rolling ring arrangement 3, 4 is pressed further together and the shaft is stretched. This loosens the arrangement and creates axial play.
  • the compensation ring 10 is rotated so that the Clearance is eliminated, whereby the tension state of the rolling ring arrangement remains fixed and the operating tension force is maintained even after the power tensioning device is released.
  • the proportion of the area in which the sawtooth flanks 11 of the compensating ring 10 and the nut 6 interact is reduced; however, these can easily be dimensioned so that they are still sufficient even after adjusting the compensating ring.
  • the design of these flanks of any size allows the transmission of any large axial forces evenly over the circumference. It goes without saying that the sawtooth surfaces 11 could also be provided between the compensating ring 10 and the intermediate ring 4 instead of between the compensating ring 10 and the retaining ring 6.

Claims (4)

1. Cylindre de laminoir, comportant un arbre (1), au moins un anneau lamineur (3) monté sur l'arbre et un dispositif pour immobiliser l'anneau lamineur (3) dans une position de service invariable sur l'arbre (1) en exerçant essentiellement une force de serrage axiale de service, ce dispositif comprenant: deux anneaux de blocage (2, 6) fixés rigidement à l'arbre (1) en direction axiale des deux côtés de l'anneau lamineur (3); un dispositif de serrage hydraulique (7) pour faire passer le cylindre de laminoir de l'état non contraint à une position de serrage préliminaire, dans laquelle l'anneau lamineur (3) prend appui par sa face frontale sur l'un des deux anneaux de blocage (2); un logement pour un anneau compensateur (10) entre l'autre des deux anneaux de blocage (6) et l'anneau lamineur (3); un anneau compensateur qui est disposé dans le logement et qui, dans la position de serrage préliminaire du cylindre de laminoir, peut être placé dans une position de service dans laquelle sa dimension axiale est plus grande que la dimension axiale du logement à l'état non contraint, de sorte qu'après la désactivation du dispositif de serrage hydraulique, la force de serrage de service soit transmise entre les deux anneaux de blocage (2, 6) par l'anneau lamineur (3) et l'anneau compensateur (10) qui se trouve en position de service, caractérisé en ce que l'anneau compensateur (10) et un anneau (6) adjacent à lui peuvent tourner l'un par rapport à l'autre et coopèrent, au niveau de leurs faces frontales, par des surfaces inclinées complémentaires (11) en forme de dents de scie, réparties sur la circonférence, ayant par rapport à la direction circonférentielle une faible pente, nettement inférieure à la limite d'auto-blocage.
2. Cylindre de laminoir selon la revendication 1, caractérisé en ce que l'anneau de blocage (6) adjacent à l'anneau compensateur contient le dispositif de serrage hydraulique (7) et en ce que le diamètre extérieur du dispositif de serrage hydraulique (7) n'est pas plus grand que le diamètre intérieur de l'anneau compensateur (10).
3. Cylindre de laminoir selon la revendication 2, caractérisé en ce que l'anneau compensateur (10) et le dispositif de serrage hydraulique (7) agissent sur un seul et même anneau (4) adjacent à l'anneau de blocage (6) associé.
4. Structure maintenue par serrage, se composant d'un axe (1), d'un contre-appui (2) solidaire de l'axe, d'un anneau de blocage (6) à l'extrémité de l'axe (1) opposée au contre-appui (2), ainsi que d'éléments (3, 4) qui se trouvent entre le contre-appui (2) et l'anneau de blocage et qui doivent être serrés axialement; la structure comportant un dispositif de serrage hydraulique pour faire passer la structure de l'état non contraint à une position de serrage préliminaire dans laquelle les éléments (3, 4) prennent appui du côté frontal sur le contre-appui (2); un logement pour un anneau compensateur (10) entre l'anneau de blocage (6) et les éléments (3, 4); un anneau compensateur qui est disposé dans le logement et qui, dans la position de serrage préliminaire de la structure, peut être placé dans une position de service dans laquelle sa dimension axiale est plus grande que la dimension axiale du logement à l'état non contraint, de sorte qu'après la désactivation du dispositif de serrage hydraulique, la force de serrage de service soit transmise entre le contre-appui (2) et l'anneau de blocage (6) par les éléments (3, 4) et par l'anneau compensateur (10) qui se trouve en position de service, caractérisé en ce que l'anneau compensateur (10) et un anneau (6) adjacent à lui peuvent tourner l'un par rapport à l'autre et coopèrent, au niveau de leurs faces frontales, par des surfaces inclinées complémentaires (11) en forme de dents de scie, réparties sur la circonférence, ayant par rapport à la direction circonférentielle une faible pente, nettement inférieure à la limite d'auto-blocage.
EP89108513A 1988-05-27 1989-05-11 Cylindre de laminoir comportant une bague montée sur un arbre Expired - Lifetime EP0343440B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89108513T ATE66836T1 (de) 1988-05-27 1989-05-11 Walzvorrichtung mit einem auf einer welle angeordneten walzring.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8806968U DE8806968U1 (fr) 1988-05-27 1988-05-27
DE8806968U 1988-05-27

Publications (2)

Publication Number Publication Date
EP0343440A1 EP0343440A1 (fr) 1989-11-29
EP0343440B1 true EP0343440B1 (fr) 1991-09-04

Family

ID=6824488

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89108513A Expired - Lifetime EP0343440B1 (fr) 1988-05-27 1989-05-11 Cylindre de laminoir comportant une bague montée sur un arbre

Country Status (8)

Country Link
US (2) US4841612A (fr)
EP (1) EP0343440B1 (fr)
JP (1) JPH0235213A (fr)
AT (1) ATE66836T1 (fr)
DD (1) DD286977A5 (fr)
DE (2) DE8806968U1 (fr)
ES (1) ES2026288T3 (fr)
SU (1) SU1715199A3 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5109585A (en) * 1990-10-24 1992-05-05 Uwe Kark Roll for a roll stand having an exchangeable roll ring and a divided roll body
WO2000074869A1 (fr) * 1999-06-07 2000-12-14 Uwe Kark Systeme pour changer l'ecrou maintenant un cylindre de laminage
US7572215B2 (en) 2005-06-17 2009-08-11 Sandvik Intellectual Property Ab Roll
US7582046B2 (en) 2005-06-17 2009-09-01 Sandvik Intellectual Property Ab Roll as well as a spacer ring therefor
DE10302660B4 (de) * 2002-04-24 2011-04-07 Köllges, Ralf Vorrichtung und Verfahren zum Spannen eines Walzrings auf einer Welle eines Walzgerüstes
US8133162B2 (en) 2005-06-17 2012-03-13 Sandvik Intellectual Property Ab Roll, as well as a ring for such a roll
EP3378577A1 (fr) 2017-03-22 2018-09-26 Ralf Köllges Dispositif de serrage hydraulique pour raccordement frictionnelle démontable de deux composants

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DE3834606A1 (de) * 1988-10-11 1990-04-12 Voest Alpine Ind Anlagen Vorrichtung zum befestigen eines walzringes
US5155910A (en) * 1989-07-19 1992-10-20 J. M. Voith Gmbh Process for manufacturing a doctor bar
US5483812A (en) * 1994-02-08 1996-01-16 Asko, Inc. Roll apparatus for reducing work
JP3198877B2 (ja) * 1995-07-24 2001-08-13 三菱マテリアル株式会社 簡易クランプ式圧延ロール
DE60225409T2 (de) * 2001-12-11 2008-11-13 Mario Grimsby Fabris Antriebswelle mit in zwei Stufen arbeitender Spannvorrichtung
DE20212838U1 (de) * 2002-08-21 2002-12-12 Kark Ag Ringhalterung für Walzring
US20050091821A1 (en) * 2003-11-03 2005-05-05 Best Scott D. Method of manufacturing an article having a radio frequency identification (RFID) device
KR100578468B1 (ko) * 2004-05-20 2006-05-10 대한동방 주식회사 단열 롤
SE529027C2 (sv) * 2005-06-17 2007-04-10 Sandvik Intellectual Property Vals samt fjäder för vals med ringformiga ändytor
MX2011000634A (es) * 2010-01-18 2011-11-04 Basf Se Conjunto de guia de hebra y metodo para controlar un flujo de termoplastico fundido.
CN102205347B (zh) * 2011-04-28 2013-03-20 株洲硬质合金集团有限公司 组合式液压预紧锁紧装置及硬质合金复合轧辊
US9334890B2 (en) 2012-01-24 2016-05-10 Kennametal India Limited Hardmetal roll clamping system onto the shaft and the method thereof
DE102014005331B3 (de) 2014-02-11 2015-05-21 Sms Meer Gmbh Werkzeugwechselsystem und -verfahren sowie Reckwalze
KR101595376B1 (ko) * 2016-01-14 2016-02-26 박은수 롤러의 결합 구조
CN107999541B (zh) * 2017-12-11 2024-03-19 株洲硬质合金集团有限公司 一种螺母锁固装置及带有该装置的组合轧辊
CN110340150B (zh) * 2019-07-31 2021-06-25 安徽川岳机械有限公司 一种复合辊环

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Publication number Priority date Publication date Assignee Title
GB877027A (en) * 1958-10-06 1961-09-13 Timken Roller Bearing Co Means for loading bearing members or the like
DE1948424A1 (de) * 1968-10-02 1970-04-09 Okers Styckebruk Ab Verfahren zum Befestigen von Hartmetall-Rollringen auf Stuetzzylindern
DE2439329C3 (de) * 1974-08-16 1982-02-25 Moeller & Neumann Gmbh, 6670 St Ingbert Rollenbefestigung für Rollenrichtmaschinen
US4008598A (en) * 1975-11-13 1977-02-22 Asko, Inc. Work reducing
US4099311A (en) * 1976-02-20 1978-07-11 Uwe Kark Composite roll with roll ring of material which is sensitive to tensile stress
FR2384593A1 (fr) * 1977-03-21 1978-10-20 Sandvik Ab Dispositif pour le montage des bagues de roulement sur un arbre
US4117705A (en) * 1977-08-08 1978-10-03 Asko, Inc. Work reducing and pressure applying
DE3316289A1 (de) * 1983-05-04 1984-11-08 Uwe 2104 Hamburg Kark Verbundwalze mit einem mittels einer konushuelse auf dem walzenkern gehaltenen walzenring
DE3321403A1 (de) * 1983-06-14 1984-12-20 Hermann Dr.-Ing. 7920 Heidenheim Schweickert Einrichtung zur mechanischen vorspannung einer schraubverbindung
JPS60127010A (ja) * 1983-12-15 1985-07-06 Kawasaki Steel Corp 圧延幅可変型ロ−ル
DE3603371A1 (de) * 1986-01-31 1987-08-06 Mannesmann Ag Rollenbefestigung fuer richtrollenmaschinen

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5109585A (en) * 1990-10-24 1992-05-05 Uwe Kark Roll for a roll stand having an exchangeable roll ring and a divided roll body
WO1992007668A1 (fr) * 1990-10-24 1992-05-14 Uwe Kark Cylindre pour cage de laminoir avec couronne et corps cylindrique divise
WO2000074869A1 (fr) * 1999-06-07 2000-12-14 Uwe Kark Systeme pour changer l'ecrou maintenant un cylindre de laminage
EP1066890A1 (fr) * 1999-06-07 2001-01-10 Uwe Kark Dispositif pour changer l'écrou de serrage d'une bague de laminage
US6286394B1 (en) 1999-06-07 2001-09-11 Uwe Kark Arrangement for changing the nut holding a roll ring
DE10302660B4 (de) * 2002-04-24 2011-04-07 Köllges, Ralf Vorrichtung und Verfahren zum Spannen eines Walzrings auf einer Welle eines Walzgerüstes
US7572215B2 (en) 2005-06-17 2009-08-11 Sandvik Intellectual Property Ab Roll
US7582046B2 (en) 2005-06-17 2009-09-01 Sandvik Intellectual Property Ab Roll as well as a spacer ring therefor
US8133162B2 (en) 2005-06-17 2012-03-13 Sandvik Intellectual Property Ab Roll, as well as a ring for such a roll
EP3378577A1 (fr) 2017-03-22 2018-09-26 Ralf Köllges Dispositif de serrage hydraulique pour raccordement frictionnelle démontable de deux composants

Also Published As

Publication number Publication date
US4841612A (en) 1989-06-27
US4932111A (en) 1990-06-12
JPH0235213A (ja) 1990-02-05
SU1715199A3 (ru) 1992-02-23
ES2026288T3 (es) 1992-04-16
ATE66836T1 (de) 1991-09-15
EP0343440A1 (fr) 1989-11-29
JPH0517405B2 (fr) 1993-03-09
DE8806968U1 (fr) 1988-07-28
DE58900255D1 (de) 1991-10-10
DD286977A5 (de) 1991-02-14

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