EP0311911B1 - Cylindre de laminoir à plusieurs parties consistant en un arbre porteur actionnable et une bague de laminage démontable - Google Patents

Cylindre de laminoir à plusieurs parties consistant en un arbre porteur actionnable et une bague de laminage démontable Download PDF

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Publication number
EP0311911B1
EP0311911B1 EP88116560A EP88116560A EP0311911B1 EP 0311911 B1 EP0311911 B1 EP 0311911B1 EP 88116560 A EP88116560 A EP 88116560A EP 88116560 A EP88116560 A EP 88116560A EP 0311911 B1 EP0311911 B1 EP 0311911B1
Authority
EP
European Patent Office
Prior art keywords
ring
roller
end faces
annular
roll
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
EP88116560A
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German (de)
English (en)
Other versions
EP0311911A3 (en
EP0311911A2 (fr
Inventor
Hans-Jürgen Reismann
Alexander Svagr
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.)
SMS Siemag AG
Original Assignee
SMS Schloemann Siemag AG
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 SMS Schloemann Siemag AG filed Critical SMS Schloemann Siemag AG
Priority to AT88116560T priority Critical patent/ATE80568T1/de
Publication of EP0311911A2 publication Critical patent/EP0311911A2/fr
Publication of EP0311911A3 publication Critical patent/EP0311911A3/de
Application granted granted Critical
Publication of EP0311911B1 publication Critical patent/EP0311911B1/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

Definitions

  • the invention relates to a multi-part, drivable support shaft and on this roll ring existing rolling mill, in which the support shaft consists of two coaxial and facing end faces each on one of the two end faces of the rolling ring ring collar pieces, and one connectable to the one ring collar piece and guided in the center with radial play through the other ring collar and which is present on the axial tensioning device acting on the end face facing away from the rolling ring, and the end faces of the ring collar pieces facing the rolling ring have a plurality of support ring surfaces which can be placed on corresponding counter faces of the end faces of the rolling ring, the end faces of the ring collar pieces from the center axis to the outer edge have two or more support ring surfaces with different inclinations to the radial axis of the center axis.
  • the tensioning device consists of a tie rod which axially displaceably connects the two ring collar pieces and a tie rod arranged thereon against the ring collar pieces supportable clamping device in the form of a hydraulic nut.
  • the tie rod is inserted into one ring collar, screwed tightly to it and passed through a center hole in the other ring collar.
  • the hydraulic nut is placed on the free end of this tie rod.
  • multi-part rolls can be used, for example, for roll stands with support shaft pairs mounted in two parallel roll stands and which can be coupled on one side with drive elements, as such a support shaft which carries the roll ring.
  • the drive-side collar and the roller ring have interlocking shoulders or recesses of a spur gear coupling on their facing end faces with axial play as driving elements for the torque transmission from the collar to the roller ring.
  • the centering of the rolling ring on the center axis of the rolling mill roll formed in this way is achieved by cylindrical edge projections provided on the outer ring edges of the ring collar pieces and comprising corresponding ring coils arranged on both end faces of the rolling ring.
  • the centering of the rolling ring is effected with the aid of support ring surfaces which are inclined in the end faces of the ring collar pieces and are inclined to an axial radial of the center axis and which are inclined accordingly Support ring surfaces can be placed on both end faces of the rolling ring.
  • the respective inclination points either inwards or outwards at different degrees.
  • the axial pressure applied to the rolling ring can increase the fatigue strength of the roll material, in addition to increasing the rolling pressure permissible for the roll, the object of the invention to improve these known multi-part rolling mill roll designs so that the fatigue strength of the rolling ring is increased considerably by targeted application of the axial pressure to certain areas of the rolling ring body and in adaptation to the different shapes of the respective rolling ring and the material used for this.
  • This object is achieved in that the number and the inclination of the support ring surfaces, their distance from the center axis and the size of the contact pressure exerted by the tensioning device on this are measured so that the expected during operation of the roller on the respective roller design taking into account their dimensions, calibres or materials, in particular in the outer circumferential area occurring bending-tension stresses are significantly reduced by this pressure.
  • the support ring surfaces in the outer circumferential area of the rolling ring are expediently guided up to the outer ring edge of the ring collar pieces and advantageously also have a slightly inwardly inclined angle.
  • the additionally arranged support ring surfaces with a larger angle of inclination facilitate the exact centering of the rolling ring in the manner known per se and, after releasing the compressive stress, have the effect that the ring collar pieces can be easily detached from the rolling ring.
  • the rolling ring of which is not replaced or only replaced at large time intervals support ring surfaces close to the axis with inclination angles of approximately 0 °, i.e. with approximately axially concentric bearing ring surfaces, in which case the ring collar pieces are then difficult to detach from the rolling ring.
  • the angle of inclination of the support ring surfaces which extend up to the outer ring edge of the ring collar pieces and the axial thickness of this outer ring edge of both ring collar pieces are dimensioned according to the invention so that the ring edges of the ring collar pieces can be pressed so far away from one another in the elastic range when the end faces of the rolling ring are acted on that the clamping process takes place the ring contact surfaces each lie in a plane with a rotational axis or in a plane slightly inclined to this, not only can this result in a particularly favorable targeted transmission of the clamping pressure to the outer peripheral region of the rolling ring body, but a further advantage is also achieved, namely the avoidance of the gaping of the bearing ring surfaces lying on top of each other with a more or less large deflection of the rolling ring.
  • the greater angle of inclination of support ring surfaces close to the axis can be dimensioned according to the invention in such a way that they come to rest on the correspondingly inclined end sections of the rolling ring in the region of the axial displacement path of the ring collar pieces, in which the bearing ring surfaces of the ring collar pieces are pressed outward in the elastic region.
  • the multi-part rolling mill roll is also to be provided with a driver coupling between the ring collar and the rolling ring for constructional and operational reasons, as is evident from the training already mentioned at the beginning according to DE-B-11 40 535 and 11 46 467 and EP-A-214 521 is known, then in the inventive design of the multi-part rolling mill, the driving elements of the coupling can be expediently arranged on the mutually facing end faces of the ring collar pieces outside the contact ring surfaces and counter surfaces of the ring collar piece and the rolling ring, advantageously in a region between the center axis and the inner ring boundary surface of the rolling ring.
  • a driving sleeve can be inserted between the mutually facing end faces of the ring collar pieces and pushed onto the tie rod, which carries out the function of the torque coupling only transmitting the torque between the two ring collar pieces.
  • the elements of the driver coupling formed in this way are expediently arranged on the mutually facing end faces of the ring collar pieces and on the ring end faces of the driving sleeve facing them, so that the driver coupling connection is disassembled during disassembly, i.e. automatically detaches when pulling off the roller ring.
  • Pressure sleeves can also be inserted between the respective outwardly facing end face of one or both ring collar pieces and the respective adjacent screw nut, which allow the axial distance between the facing end faces of the ring collar pieces to be adapted to the axial thickness of the rolling ring used in each case.
  • the elements of the driver clutches there is of course the possibility of arranging the elements of the driver clutches on the mutually facing end faces of the ring collar pieces.
  • This design of the driver clutches also has the particular advantage that the two ring collar pieces remain rotatably coupled to one another even if the torque transmission from the rolling ring and ring collar pieces is impaired and relative movements between them as a result of insufficiently strong contact pressure or, for example, oily or graphite-containing contact surfaces between the rolling ring and ring collar pieces occur on the contact surfaces, which may lead to the destruction of the roller.
  • the pressurization of the contact surfaces unlike when using the known driver clutches described at the beginning, is always symmetrical.
  • intermediate rings are arranged on both sides of the rolling ring between its end face and the facing end faces of the ring collar pieces, which can be placed on the end face on the one hand on the rolling ring and on the other hand on the respective ring collar piece.
  • the cross section of the ring collar pieces on the end faces of such intermediate rings can be the same as the cross section of the intermediate ring on the end faces of the rolling ring.
  • the diameter of the ring pins can be dimensioned such that the diameter enlargement of the ring pins caused by the tensioning of the elements forming the rolling mill roller axially fixes the bearing rings causes; this is advantageous because the bearings in this rolling mill roll formation must be connected to the supporting shafts in a rotationally fixed manner during the rolling process.
  • the thread of the tie rod receiving the screw nuts is a conical thread, to increase the tensile strength of the thread so that a better load distribution is achieved.
  • the rolling mill roll training requires a high preload, which is often loaded and unloaded.
  • a tie rod 7 with a thread 7a is screwed into the annular collar piece 2.
  • the tie rod is guided through a through hole 1b in the collar 1 and screw-connected at its free end 7b via a further thread 7c to a nut 14a.
  • a sleeve 8 is placed on the pin end 1k. This sleeve serves as a drive transmission element in a manner not shown the roll of a roll stand set up in a parallel rolling line.
  • a drive sleeve 9 is placed on the pin end 2b of the ring collar piece 2.
  • the rolling ring 10 which here has a profile groove 10a, is inserted; it rests with bearing ring surfaces 10b and 10c running in planes of rotation axis on correspondingly running bearing ring surfaces 1e and 2e of the ring collar pieces 1 and 2, respectively.
  • axially telescopic driving claws 12 of the two ring collar pieces 1 and 2 are provided on the mutually facing end faces 1d, 2d.
  • the rolling mill roller formed via the nut 14a, the tie rod 7 and the two ring collar pieces 1, 2 and the rolling ring 10 clamped between them can be used in operation as a one-piece roller.
  • the basic design of the rolling mill roll according to FIG. 2 corresponds to that shown in FIG. 1 with the difference that the annular collar piece 112 on the end face 112d facing the annular collar piece 111d has a sleeve-like extension projection 112e in the center, which allows it, as shown below the center axis line, a very wide rolling ring 110, for example for the machining of flange supports or, as shown above the center axis line, to insert two intermediate rings 30 and 31 between the facing side surfaces 111c and 112d of the ring collar pieces 111 and 112, which in turn act on the outer sides of a narrow rolling ring 110 '.
  • the respective contact cross sections of the annular collar pieces 11 and 12 on the intermediate rings 30 and 31 is the same as that of these intermediate rings 30, 31 on the rolling ring 110 '.
  • the tie rod 7 carries at its end 7b on the thread 7c a screw nut 14 which is against the outwardly facing end face 112f of the ring collar piece 112 is supported.
  • the screw nut 14 is covered by a cover pot 18 screwed onto this end face 112f by means of screws.
  • the rolling mill roll designed in this way makes it possible to use rolling rings 110, 110 'of different thicknesses with the shape of the basic elements unchanged.
  • the configuration of the rolling mill roller according to FIG. 3 corresponds in part to the configuration of the rolling mill roller according to FIG. 1 and in part to the configuration according to FIG. 2.
  • the center axis line between the outwardly facing end face 212f of the annular collar piece 212, which here as well as that 1 has no sleeve shoulder 112e, as in the embodiment according to FIG.
  • the screw nut 14 has a pressure sleeve 20 pushed onto the tie rod 7, against which one ring end face 20b the pressure nut 14 bears and the other ring end face 20a the outwardly facing side surface 212f of the ring collar 212 creates and thus allows the clamping of the rolling ring 210 'between the mutually facing end faces 212d and 211c of the ring collar 212 and 211.
  • the torque is transmitted as in the embodiment according to FIG. 1 with the aid of the driving claws 12.
  • a driving sleeve 22 is inserted between the inwardly facing end faces 211c and 212d of the ring collar pieces 211, 212, through which the tie rod 7 is passed.
  • This driver sleeve 22 has driver claws 12 on both end faces, its length is dimensioned such that it does not receive any axial stress when the roller ring 210 is clamped between the two ring collar pieces 211 and 212.
  • the two ring collar pieces 311, 312 and the rolling ring 310 are tensioned by means of a tie rod 307 which carries screw nuts 314 on both ends.
  • a tie rod 307 which carries screw nuts 314 on both ends.
  • the rolling ring 410 clamped between the annular collar pieces 511 and 512 by means of the tie rod 507 has a plurality of profiled troughs 410a;
  • Such a multi-part rolling mill roll like those described above, can be handled and used in the same way as corresponding one-piece rolls.
  • annular collar piece 1 shows that the side surfaces can have bearing ring surfaces 1g lying in axially radial planes as well as inclined bearing surfaces 1f, and instead there are (see FIG. 1) bearing ring surfaces 1e with an inclination angle of 90 ° possible. With these contact ring surfaces, however, it is necessary to shrink the ring collar pieces on each.
  • Fig. 7 shows an up to the outer ring edge 1h of the collar 1 1 bearing ring surfaces 1g ', the inclination to the axis-radial plane E corresponds to the angle ⁇ a slight inclination inwards.
  • This inclination angle ⁇ and the axial thickness S of the ring edge 1h of the collar 1 are dimensioned such that when the multi-part rolling mill roll (not shown here) is tightened, this ring edge 1h through the respective end face (also not shown) of the rolling ring in the elastic range can be pressed outwards into the dash-dotted position that the bearing ring surface 1g 'is in the operating state of the rolling mill roller in the axis-radial plane E or at a certain angle to this.

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  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Rolls And Other Rotary Bodies (AREA)

Claims (7)

  1. Cylindre de laminoir composite qui est constitué par un arbre de support pouvant être entraîné et par un anneau de laminage (10, 110, 210, 310, 410) pouvant être monté sur cet arbre et dont l'arbre de support comprend deux bourrelets annulaires (1, 2; 111, 112; 211, 212; 311, 312; 411, 412) disposés coaxialement et pouvant s'appliquer, au niveau de chacune de leurs faces frontales tournées l'une vers l'autre, contre l'une des deux faces frontales de l'anneau de laminage et un dispositif de serrage axial qui peut être relié à l'un des bourrelets annulaires, traverse en son milieu, avec un certain jeu radial, l'autre bourrelet annulaire et agit sur celui-ci au niveau de la face frontale située à l'opposé de l'anneau de laminage et dans lequel les faces frontales des bourrelets annulaires qui sont tournées vers l'anneau de liminage comportent des surfaces annulaires de contact qui peuvent s'appliquer contre des contre-faces correspondantes des faces frontales de l'anneau de laminage, les faces frontales des bourrelets annulaires comportant, depuis l'axe médian jusqu'au bord extérieur, deux ou plus de deux surfaces annulaires de contact présentant différentes inclinaisons par rapport aux directions radiales de l'axe médian, caractérisé en ce que le nombre et l'inclinaison des surfaces de contact (1f, 1g), leur distance par rapport à l'axe médian et la grandeur de la pression de contact exercée sur cet axe par le dispositif de serrage (14a) sont calculés de telle manière que cette pression ait pour effet de réduire d'une manière considérable les contraintes de flexion et de traction qui doivent normalement se developper dans le cylindre pendant sa marche, notamment dans ses zones périphériques, compte tenu de ses dimensions, de ses cannelures et des matériaux qui le constituent.
  2. Cylindre de laminoir composite selon la revendication 1, caractérisé en ce que la surface de contact (1g') va jusqu'au bord extérieur (1) des bourrelets annulaires.
  3. Cylindre de laminoir composite selon la revendication 2, caractérisé en ce que l'angle d'inclinaison (α) des surfaces de contact (1g') correspond à une légère inclinaison vers l'intérieur.
  4. Cylindre de laminoir composite selon la revendication 3, caractérisé on ce que l'angle d'inclinaison (α) de la surface de contact (1g') et l'épaisseur (S) dans le sens axial du bord annulaire extérieur (1h) des deux bourrelets annulaires (1, 2) sont calculés de telle manière que, lors du serrage, les bords annulaires (1h) des bourrelets annulaires (1, 2) peuvent, au moment de l'action exercée sur les faces frontales du bourrelet (10) dans le domaine élastique, être écartée assez loin l'un de l'autre vers l'extérieur pour que les surfaces de contact (1g') se trouvent dans un plan (E) orienté dans le sens radial par rapport à l'axe de rotation ou dans un plan légèrement incliné par rapport au plan en question.
  5. Cylindre de laminoir selon les revendications 2 à 4, caractérisé en ce que le plus grand angle d'inclinaison de surfaces de contact (1f) voisines de l'axe est calculé de telle manière que ces surfaces s'appliquent sur les parties d'inclinaison correspondantes des faces frontales de l'anneau de laminage (10) dans la zone du trajet de déplacement axial des bourrelets annulaires (1, 2), dans laquelle les surfaces de contact (1g') des bourrelets annulaires (1, 2) sont, dans le domaine élastique, poussés vers l'extérieur.
  6. Cylindre de laminoir composite selon une ou plusieurs des revendication 1 à 5, qui comporte un accouplement d'entraînement qui, par un déplacement axial, peut être amené dans et sorti d'une position d'accouplement et comporte des élements d'entraînement au niveau des faces frontales des bourrelets annulaires qui sont tournées l'une vers l'autre, caractérisé en ce que les éléments d'entraînement se trouvent en dehors des surfaces de contact et des contre-surfaces du bourrelet annulaire (1, 2) et de l'anneau de laminage (10).
  7. Cylindre de laminoir composite selon la revendication 6, caractérisé en ce que les éléments d'entraînement de l'accouplement d'entraînement (12) se trouvent dans une zone comprise entre l'axe médian du cylindre et la surface intérieure de l'anneau de laminage (10).
EP88116560A 1987-10-16 1988-10-06 Cylindre de laminoir à plusieurs parties consistant en un arbre porteur actionnable et une bague de laminage démontable Expired - Lifetime EP0311911B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88116560T ATE80568T1 (de) 1987-10-16 1988-10-06 Mehrteilige aus antreibbarer tragwelle und auf diese aufsetzbarem walzring bestehende walzwerkswalze.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3735098 1987-10-16
DE19873735098 DE3735098A1 (de) 1987-10-16 1987-10-16 Mehrteilige aus antreibbarer tragwelle und auf diese aufsetzbarem walzring bestehende walzwerkswalze

Publications (3)

Publication Number Publication Date
EP0311911A2 EP0311911A2 (fr) 1989-04-19
EP0311911A3 EP0311911A3 (en) 1989-10-04
EP0311911B1 true EP0311911B1 (fr) 1992-09-16

Family

ID=6338486

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88116560A Expired - Lifetime EP0311911B1 (fr) 1987-10-16 1988-10-06 Cylindre de laminoir à plusieurs parties consistant en un arbre porteur actionnable et une bague de laminage démontable

Country Status (5)

Country Link
EP (1) EP0311911B1 (fr)
JP (1) JPH01133604A (fr)
AT (1) ATE80568T1 (fr)
DE (2) DE3735098A1 (fr)
ES (1) ES2035206T3 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2743523B1 (fr) * 1996-01-15 1998-03-06 Komori Chambon Cylindre massif pour machine de faconnage rotative
CN107672271A (zh) * 2017-11-08 2018-02-09 张家港市华申工业橡塑制品有限公司 抗压防脱落橡胶辊

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1441980A (fr) * 1965-07-26 1966-06-10 Demag Ag Cylindre de laminoir
DE1602086A1 (de) * 1967-11-29 1970-04-16 Hoestemberghe & Kluetsch Gmbh Walzenanordnung mit auswechselbaren Walzenkoerpern,insbesondere fuer Walzgerueste
AT313839B (de) * 1971-05-21 1974-03-11 Plansee Metallwerk Walzanordnung zur Herstellung von Profildrähten, insbesondere für Baustahlgewebe, mit Hartmetall-Walzringen
DD132726A1 (de) * 1977-09-09 1978-10-25 Vnii Pk I Metall Maschino Walze
DE3019921C2 (de) * 1980-05-24 1984-11-22 Schmolz & Bickenbach, 4000 Düsseldorf Walze
DE3531843A1 (de) * 1985-09-06 1987-03-19 Schloemann Siemag Ag Walzgeruest mit in zwei parallelen walzenstaendern gelagerten und an einer seite mit antriebselementen kuppelbaren tragwellenpaaren

Also Published As

Publication number Publication date
ATE80568T1 (de) 1992-10-15
ES2035206T3 (es) 1993-04-16
EP0311911A3 (en) 1989-10-04
JPH01133604A (ja) 1989-05-25
EP0311911A2 (fr) 1989-04-19
DE3735098A1 (de) 1989-04-27
DE3874666D1 (de) 1992-10-22

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