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US3318131A - Multiple-roll rolling mill for exchangeable work rolls of substantially varying diameter - Google Patents

Multiple-roll rolling mill for exchangeable work rolls of substantially varying diameter Download PDF

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Publication number
US3318131A
US3318131A US408427A US40842764A US3318131A US 3318131 A US3318131 A US 3318131A US 408427 A US408427 A US 408427A US 40842764 A US40842764 A US 40842764A US 3318131 A US3318131 A US 3318131A
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US
United States
Prior art keywords
rolls
roll
intermediate rolls
backing
rolling mill
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
US408427A
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English (en)
Inventor
Karl J Neumann
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.)
Moeller and Neumann Verwaltungsgesellschaft Offene GmbH
Moeller and Neuman GmbH
Original Assignee
Moeller and Neuman GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Moeller and Neuman GmbH filed Critical Moeller and Neuman GmbH
Application granted granted Critical
Publication of US3318131A publication Critical patent/US3318131A/en
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
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • B21B13/147—Cluster mills, e.g. Sendzimir mills, Rohn mills, i.e. each work roll being supported by two rolls only arranged symmetrically with respect to the plane passing through the working rolls
    • 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
    • B21B13/001—Convertible or tiltable stands, e.g. from duo to universal stands, from horizontal to vertical stands

Definitions

  • the invention relates to a cold rolling mill having more than four rolls, especially to a so-called multiple-roll rolling mill for rolling thin sheets or strips. It is known that the thinnest strip thickness which may be rolled on a cold rolling mill determines the diameter of the working rolls.
  • Thick working rolls of a four-high rolling mill allow substantial pass reductions but roll only down to a strip thickness at which the roller flattening, due to the solidification of the strip, becomes greater so that even with an increased rolling pressure no further noticeable reductions can be obtained.
  • the strip is to be rolled even thinner, or in the case where a hard material is worked, one must use a multiple-roll rolling mill having small diameter working rolls.
  • thick working rolls are to be under: stood those which have a diameter comparable to the usual Working roll diameters employed in four-high rolling mills.
  • the objects of the invention are to be accomplished with the smallest possible number of rolls.
  • the best known multiple-roll rolling mill presently has twenty rolls.
  • the rolling mill according to the invention should comprise not more than ten rolls.
  • the invention is based on a multiple-roll rolling mill having on both sides of the rolling gap roll sets comprising each an equal amount of rolls, and each set consisting of a working roll, two driven intermediate rolls and two backing rolls for absorbing the forces received by the intermediate rolls, wherein the intermediate rolls are mounted in chocks which are guided radially of the axial center lines of the backing rolls.
  • the guides for the chocks of the driven intermediate rolls consist of pivot elements which are movable around the axis center lines of these backing rolls both symmetrically in that the horizontal distance of the intermediate rolls from each other is adjustable by means of a displacing device which engages directly or indirectly at the pivot elements in the same pivot direction to set the axial center lines of the intermediate rolls unsymmetrically out of alignment with the connection lines between the working roll and the axial center of the backing rolls.
  • each backing roll may be displaced individually or in pairs of superimposed backing rolls together.
  • one is able to adjust the pivot elements of a pair of intermediate rolls which drive a work roll unsymmetrically to the vertical plane running through the axis center lines of the work rolls in order to produce in the intermediate roll chocks a force component resulting from rolling pressure directed against the bearing pressure in the intermediate roll chocks, which equals the resulting bearing pressure derived from the driving rotation moment and the strip tension which engages at the two driven intermediate rolls in the same horizontal direction.
  • This is obtained by the individual displacement of the axis center lines of the intermediate rolls laterally of and out of alignment with the mentioned inclined connection line between the working roll center and the backing roll center, called hereafter articulated position.
  • the pivot elements are adjustable relative to each other symmetrically to the vertical plane which runs through the center lines of the Working rolls so that rotating moments are constantly effective at the pivot elements whereby the adjusting parts remain loaded.
  • the intermediate roll axis center lines laterally away from the connection lines between the working roll and backing roll axis center lines for setting the articulated position, whereby the forces arising from the rolling pressure at the intermediate rolls are directed against the forces resulting from the driving rotation moment and the strip tension
  • the invention provides that the pivot elements are also pivotable in a displacement in the same direction of rotation.
  • the invention purposes that the pivot elements may be switched over with each reversing pass in the same pivot direction, namely between two predetermined pivot positions which are symmetrical to the inclined connection line of the axis center lines of the associated backing rolls and working rolls.
  • FIGURE 1 shows the lower roll set of a ten-roll rolling mill with an adjusting device for the pivot elements, the roll set in side view and the displaying device in crosssection.
  • FIGURE 2 a cross-section along line II-II in FIG- URE 1 showing parts of the roll assembly with a pivot element and FIGURE 3, a roll asembly including the composition of forces.
  • the roll set consists of a working roll 1, two intermediate rolls 2, 3 engaging the working roll, and of two large backing rolls 4 and 5.
  • the intermediate rolls 2, 3 are driven by suitable means (not shown).
  • For setting the position of the intermediate rolls 2, 3 they are mounted in chocks 6, 7 which are guided by bolts 8, 9 in cross bores 10, 11 of the backing roll shaft 4a, a radially to the axis center line 4b, 5b of the backing rolls, so that the intermediate rolls bear always against the backing rolls even after some wear.
  • the pivot elements 12, 13 are secured on the backing roll shafts 4a, 5a at both ends, for example by a shrunk-fit, and these pivot elements extend the guide bores 10, 11 for the bolts 8, 9.
  • the horizontal distance between the intermediate rolls may be varied in opposite direction to each other with respect to the vertical center plane 14 by a symmetrical pivoting of the pivot elements 12, 13.
  • This displacement is carried out when instead of the thin work roll 1, which in the embodiment shown, has a diameter of 80 mm., a thick working roll 15 shown in dot-and-dash lines and having a diameter of 250 mm. is to be inserted.
  • the intermediate rolls are then moved into the positions 2a, 3a, shown in dot-and-dash lines, in which positions the axis center lines of the intermediate rolls are located on the inclined connection lines 16, 17 between the axis center lines of the working roll 15 and on the axis center lines 4b, 5b of the backing rolls 4, 5.
  • This position of the intermediate rolls in alignment with the axis center lines of the adjacent rolls Will be called hereafter the neutral position.
  • the roll sets of the rolling mill are to be separated from each other a corresponding amount by a screw-down device (not shown).
  • a screw-down device not shown.
  • the screw-down distance is to be so measured that instead of thick working rolls 51 for rolling down a strip thin working rolls 1 of less than half the diameter of the thickest working rolls 15 may be inserted.
  • the backing rolls 4 and 5 consist of stationary shafts 4a, 5a with individual roller bearing rings "19 mounted in spaced relationship.
  • the shafts 4a, 5a are mounted on both sides of the bearing rings 19 in common frames 18.
  • each roll set displacement devices which comprise displacement elements which may be driven in opposite directions or in the same directions and which may be fixed in position.
  • the drawing shows a displacement device which has the advantage of not requiring any linkage parts and which may be so tensioned that during the rolling operation no play can be effective in the displacement parts.
  • a setting cylinder 21, 22 respectively is provided which may be displaced in the axial direction, these setting cylinders being guided in the embodiment illustrated in a common guide cylinder 20.
  • the setting cylinders 21, 22 each receive a pair of pistons having pistons 23, 24, and 25, 26 which may be moved back and forth hydraulically in pairs in the same direction. These piston sets engage on each side a lever arm 12a or 13a of the pivot elements 12 and 13.
  • This axial play makes it possible to displace by alternate admission of pressure against the one or the other piston 23 or 24 through conduits 28, 29 the lever arm 12a of the pivot element 12 and thus also the intermediate roll 2 toward the one or the other side from the neutral position.
  • the same hydraulic displacement in the same direction is also provided by the pistons 25, 26, which are displaceable over hydraulic conduits 30, 31 through the axial play s relative to their stationary cylinder 22.
  • the setting 0 the intermediate rolls In FIGURE 1 the intermediate rolls 2, 3 for the bearing of the very thin working roll 1 are set to a minimum distance from each other.
  • the pivot elements 12, 13 Before inserting a thicker working roll 15 it is necessary to swing the pivot elements 12, 13 in opposite directions outwardly to such an extent that the intermediate rolls 2, 3 move into the position 2a, 3a shown in dot-and-dash lines, in which symmetrical position their axis center lines lie on the connection lines 16 and 17 between the axis center lines of the Working roll 15 and the backing rolls 4 and 5.
  • the axis center lines of the intermediate rolls move on arcs 40 and 41 during this displacement.
  • the setting position is released in that first the counter hand wheels 33, 39 are loosened and the cylinders 21, 22 are brought closer to each other 5 by threading in the stop spindles 34, 35. During this operation the pressure in the chamber 33 must be let off temporarily. It is to be understood that instead of the manual operation also a motor drive may be provided for the stop spindles 34, 35.
  • the correct adjustment of the cylinders 21, 22 corresponds to the diameter of the new working roll 15 and may be determined from a dial (not shown).
  • This articulated position of the driven intermediate rolls 2, 3 reduces the forces which are produced from the driving rotating movement and the strip tension and which act as rotating moment on the pivot elements 12, 13.
  • the displacement of the axis center lines of the intermediate rolls 2, 3 is switched over beyond the neutral position opposite to the new rolling direction with respect to the changing direction of the forces which occurs during the reversing before each reversing and before each pass reduction by the screwdown device.
  • the new position of the intermediate rolls is shown in FIG. 3 in dash-and-dot lines. For this position the pressure conduits 29, 30 are simply connected to the pressure source and the pressure conduits 28, 31 are switched to reversing.
  • the intermediate rolls 2, 3 are displaced for the rolling direction from left to right opposite to the rolling direction relative to the connection line 16, 17 of the neutral position.
  • the rolling force P is divided into the unequal components P and P which are directed to the axis center lines of the intermediate rolls 2, 3 and into two components which are directed perpendicularly thereto, which are not of interest in this connection.
  • the components P and P may again be divided into forces P or P directed to the axis center lines 4b, 5b of the backing rolls and into forces P or P which are perpendicular thereto. It is these forces which exert-' over the checks 6, 7 of the intermediate rolls 2, 3 as hearing pressure a rotation moment on the pivot elements 12, 13 where no equal oppositely directed forces oppose them.
  • the opposiing forces are derived from the peripheral forces which engage at the driven intermediate rolls, namely the forces P and P resulting from the driving rotation moment and the strip tension as well as the forces P and P resulting from the roll friction moments between the intermediate rolls and the backing rolls as well as from their roller bearings.
  • buckling forces result by subtraction of the smaller P -forces from the always larger P -forces counterforces P and P which are directed opposite to the buckling forces P and P
  • the conditions are assumed to be such that the buckling force P for the intermediate rolls 3 is equal to the counterforce P Therefore no rotation moment which would have to be taken up by the displacement device is exerted on the pivot element 13.
  • the counterforce P is equal to P but the buckling force P is smaller due to the outwardly directed articulated position (P smaller than P A remaining force is effective at the intermediate roll 2 which tends to drive the intermediate roll 2 inwardly. This remaining force is absorbed over the piston 23 by the pressure means when the pressure conduit 28 is closed.
  • Multiple-roll rolling mill including two sets of rolls on both sides of the rolling gap; each roll set comprising a work roll of small diameter, two driven, horizontally spaced intermediate rolls engaging said work roll and two horizontally spaced backing rolls arranged at a fixed distance from one another for engaging each one of said two intermediate rolls; said intermediate rolls being supported in checks carried on guide means mounted for adjustment radially of the axial center lines of said backing rolls, said guide means including pivot elements movable about the axial center lines of said backing rolls; a diplacement device for moving said pivot elements both symmetrically to change the horizontal distance of said intermediate rolls from each other for adapting said distance to the actual working roll diameter, and in the same pivot direction to set the axial center lines of said intermediate rolls unsymmetrically and out of alignment with the connection lines between the axial center of the working roll and the backing rolls. to absorb the components force resulting from the rolling pressure, the driving rotation moment and the strip tension, taken up by said pivot elements.
  • said displacing device for one pivot element consists of a setting cylinder movable in an axial direction containing two pistons hydraulically reciprocable in the same direction, said pistons engaging in pairs a lever arm of said one pivot element on opposite sides.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Metal Rolling (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Straightening Metal Sheet-Like Bodies (AREA)
US408427A 1963-10-31 1964-11-02 Multiple-roll rolling mill for exchangeable work rolls of substantially varying diameter Expired - Lifetime US3318131A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DEV24787A DE1279587B (de) 1963-10-31 1963-10-31 Reversierbares Vielrollen-Walzwerk

Publications (1)

Publication Number Publication Date
US3318131A true US3318131A (en) 1967-05-09

Family

ID=7581440

Family Applications (1)

Application Number Title Priority Date Filing Date
US408427A Expired - Lifetime US3318131A (en) 1963-10-31 1964-11-02 Multiple-roll rolling mill for exchangeable work rolls of substantially varying diameter

Country Status (4)

Country Link
US (1) US3318131A (de)
DE (1) DE1279587B (de)
FR (1) FR1412934A (de)
GB (1) GB1040536A (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3490120A (en) * 1967-05-15 1970-01-20 Ashtabula Bow Socket Co Method and apparatus for constructing convertible top linkages
DE19914475C2 (de) * 1998-03-30 2003-12-18 Hitachi Ltd Vielwalzen-Walzgerüst

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE418004C (de) * 1925-08-24 Anton Schoepf Dipl Ing Kaltwalzwerk
GB523777A (en) * 1938-12-14 1940-07-23 Robert Bass Rolling-mills
US2677978A (en) * 1950-03-22 1954-05-11 Frank P Dahlstrom Rolling mill
DE1084221B (de) * 1959-04-11 1960-06-30 Moeller & Neumann Gmbh Mehrrollen-Walzwerk
US3049949A (en) * 1958-08-12 1962-08-21 Schloemann Ag Rolling mill

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE521610C (de) * 1931-03-25 Georg Reimer Anordnung der Stuetzwalzen bei Umkehrwalzwerken mit vier oder sechs Walzen
LU35252A1 (de) * 1956-06-29
DE1028959B (de) * 1957-01-04 1958-04-30 Moeller & Neumann Gmbh Mehrrollen-Walzwerk
AT203445B (de) * 1957-01-04 1959-05-11 Moeller & Neumann Gmbh Mehrrollen-Walzwerk
GB870777A (en) * 1958-08-25 1961-06-21 United Eng Foundry Co Method of and apparatus for rolling strip material

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE418004C (de) * 1925-08-24 Anton Schoepf Dipl Ing Kaltwalzwerk
GB523777A (en) * 1938-12-14 1940-07-23 Robert Bass Rolling-mills
US2677978A (en) * 1950-03-22 1954-05-11 Frank P Dahlstrom Rolling mill
US3049949A (en) * 1958-08-12 1962-08-21 Schloemann Ag Rolling mill
DE1084221B (de) * 1959-04-11 1960-06-30 Moeller & Neumann Gmbh Mehrrollen-Walzwerk

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3490120A (en) * 1967-05-15 1970-01-20 Ashtabula Bow Socket Co Method and apparatus for constructing convertible top linkages
DE19914475C2 (de) * 1998-03-30 2003-12-18 Hitachi Ltd Vielwalzen-Walzgerüst

Also Published As

Publication number Publication date
GB1040536A (en) 1966-08-24
DE1279587B (de) 1968-10-10
FR1412934A (fr) 1965-10-01

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