US3834205A - Selectively insulated mill roll - Google Patents

Selectively insulated mill roll Download PDF

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Publication number
US3834205A
US3834205A US00316809A US31680972A US3834205A US 3834205 A US3834205 A US 3834205A US 00316809 A US00316809 A US 00316809A US 31680972 A US31680972 A US 31680972A US 3834205 A US3834205 A US 3834205A
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US
United States
Prior art keywords
cylinder
coolant
annular
passageways
gaskets
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
US00316809A
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English (en)
Inventor
G Maag
J Callaham
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.)
Procter and Gamble Co
Original Assignee
Procter and Gamble Co
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 Procter and Gamble Co filed Critical Procter and Gamble Co
Priority to US00316809A priority Critical patent/US3834205A/en
Priority to IT54411/73A priority patent/IT1000719B/it
Priority to GB5876373A priority patent/GB1420797A/en
Priority to FR7345543A priority patent/FR2211296B1/fr
Priority to CA188,482A priority patent/CA990550A/en
Priority to DE2363063A priority patent/DE2363063A1/de
Priority to NL7317367A priority patent/NL7317367A/xx
Priority to JP48142905A priority patent/JPS4996157A/ja
Priority to BE139087A priority patent/BE808889A/xx
Application granted granted Critical
Publication of US3834205A publication Critical patent/US3834205A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F5/00—Elements specially adapted for movement
    • F28F5/02—Rotary drums or rollers
    • 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
    • B21B27/06—Lubricating, cooling or heating rolls
    • B21B27/08—Lubricating, cooling or heating rolls internally
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/02—Rolls; Their bearings
    • D21G1/0253—Heating or cooling the rolls; Regulating the temperature
    • D21G1/0266—Heating or cooling the rolls; Regulating the temperature using a heat-transfer fluid

Definitions

  • Proved mill may further comprise rods disposed 5 5 457 5 165/39 9 within its medium-conducting passageways for the purpose of increasing the velocity of medium there- [5 References Cited through for any given rate of medium flow.
  • Such rods UNITED STATES PATENTS may be configured to profile the velocity of medium through the passageways so that areas of the roll subl,382,608 6/l92l Shuman l/89 X jected to the highest head loads are contacted y the l,78l,378 ll/l930 Feeney l65/89 hi best velocit medium and vi Th 2 531 988 11/1950 Price /89 g y Improve 2'849951 9/1958 Heinrich 165/89 x ments reduce the dlsmmo of 0115 whlch would 219121556 11/1959 1161a 165/89 x Otherwise Occur due to thermal gradients- 3,484,227 12/1969 Martin 65/253 x 3,738,423 6/1973 Fleissner 165/89 2 Clams 4 Drawmg Flgul'es SELECTIVELY INSULATED MILL ROLL CROSS-REFERENCE TO RELATED APPLICATIONS This application is related to the commonly assigned and
  • This invention relates generally to providing mill rolls which are internally cooled or heated by having flow-- able heat transfer media circulated through them.
  • This invention specifically relates to means for decreasing temperature gradients in and thermally induced distortion of high mill rolls and means for improving the effectiveness of heat transfer media being circulated therethrough.
  • mill rolls used for rolling sheet or web type products such as paper, metals or dough have true, right circular cylindrical working surfaces so that nips formed between adjacent parallel mill rolls are of uniform height throughout the axial length of the working surfaces of the mill rolls. Unless the rolls are distorted, web type products issuing from such nips are of uniform thickness throughout their entire widths. Such uniform-height nips are ideal also for milling, grinding, or comminuting and the like because of the resulting uniformity of action on materials being milled by the mill rolls throughout the lengths of such nips.
  • Mill roll applications commonly require the working surface of each roll which contacts process stream materials to be maintained isothermally at a predetermined temperature or within a predetermined temperature range because of temperature limitations of the process stream materials. To effect such temperature control, some mill rolls must be heated and others cooled. For simplicity, the present invention is hereinafter described as applied to cooling mill rolls. However, it is not intended to thereby exclude heated mill rolls from the scope of the invention.
  • Circulating coolant provides the zone of lower temperature through the transfer of heat to the coolant from the internal surfaces of the mill roll which the coolant contacts. Heat transfer to such a coolant is directly related to the velocity of the coolant.
  • mill rolls In actual practice, mill rolls generally do not have isothermal working surfaces. Such mill rolls are distorted from their ideal cylindrical shape by thermally induced stresses.
  • Axial thermal gradients on mill rolls commonly result adjacent rolls. For instance. it is not uncommon to confine milling to a centrally disposed working portion of the cylindrical surface of a mill roll, which portion extends axially intermediate non-working portions of the cylindrical surface of the mill roll. Internally cooling such a mill roll by passing coolant through axially extending passageways subjacent its entire cylindrical surface commonly results in overcooling the unheated end portions of the roll intermediate the non-working surfaces and the subjacent passageways. Such overcooling distorts mill rolls which distortion compromises the constant-clearance integrity of nips formed therebetween.
  • mill rolls which are machined to have right circular cylindrical working surfaces and which, when operated, have cool ends tend to be somewhat barrel-shaped with the ends having smaller diameters than their middles.
  • adjacent non-isothermal mill rolls having overcooled ends tend to form hour-glass shaped nips.
  • a major object of the invention is providing an improved, internally cooled mill roll assembly having selectively insulated non-working end portions so that heat flow within the non-working end portions is substantially obviated whereby over-cooling of the end portions is substantially precluded.
  • Another object of the invention is providing an improved, selectively insulated, internally cooled mill roll assembly wherein the efficiency of the circulating coolant, for any given rate of coolant flow, is improved by defining coolant passageways having high ratios of heat transfer surface areas to their cross sectional areas, as compared to tubular passageways having circular cross sections, whereby the coolant is forced to flow faster across the heat transfer surface areas.
  • Yet another object of the present invention is providing an improved, selectively insulated, internally cooled mill roll assembly wherein the relationship between coolant velocity and its heat transfer coefficient is applied, through providing coolant passageways of non-uniform cross sectional areas, to achieve higher heat flux in zones of higher heat load and vice versa so that an asymmetrically heated working surface can be maintained at a substantially isothermal condition.
  • an improved mill roll assembly having axially extending tubular passageways disposed subjacent the cylindrical surface of the mill roll, and which assembly further includes means for conducting coolant into the mill roll assembly, through the passageways, and for conducting the coolant from the mill roll.
  • the improved mill roll assembly includes selectively insulating non-working end portions of the assembly disposed intermediate the outside of the mill roll assembly and the subjacent portions of the coolant passageways so that heat flow within the end portions is substantially obviated.
  • the improved mill roll may further comprise means within the passageways for improving the heat transfer coefficient between the heat transfer medium and the mill roll assembly within the passageways.
  • Such means for improving the heat transfer coefficient includes means for establishing greater velocity of the coolant across the heat transfer surface areas of the passageways for any given rate of coolant flow as compared to simple tubular passageways.
  • the improved mill roll assembly may include coolant passageways of nonuniform cross sectional areas so that zones of high heat load may be cooled by relatively high velocity coolant and vice versa whereby an asymmetrically heated working surface can be maintained at a substantially isothermal condition.
  • FIG. 1 is a fragmentary, partially cut away longitudinal view of a mill roll assembly embodying the instant invention.
  • FIG. 2 is an enlarged scale, fragmentary crosssectional view of the mill roll assembly of FIG. 1 taken along line 2-2 thereof.
  • FIG. 3 is a fragmentary, enlarged scale, crosssectional view of the mill roll assembly of FIGS. 1 and 2 taken along line 33 of FIG. 2.
  • FIG. 4 is a fragmentary longitudinal view of an alternate embodiment cylindrical member which is suitable for transforming tubular coolant passageways into annular conduits of non-uniform cross sectional areas in accordance with the instant invention.
  • FIG. 3 which shows only one of substantially identical ends of mill roll 20
  • the assembly is held together by two rings of circumferentially spaced bolts 35, 36 at each end.
  • Cylinder 21, FIG. 1-3 is substantially solid. Each end of cylinder 21 is provided with a plurality of radially extending holes 40 intermediate manifold 27 and shoulder 41. Cylinder 21 also has a plurality of circumferentially spaced, parallel, axially extending, cylindrical passageways 42 provided subjacent its cylindrical surface 43 and parallel thereto. Each end of cylinder 21, FIG. 3, has an axially extending, toroidal-shape channel 44 formed in it to interconnect adjacent ends of all passageways 42 and to receive bushing 30. The wall 45 of each passageway 42 has a spiral groove 46 (a quasi female thread) formed in it for a purpose to be described hereinafter.
  • Each bushing 30, one of which is shown in FIG. 3, is a toroid having a rectangular cross section.
  • bushings 30 are dimensioned to provide press fits in channels 44.
  • Each bushing 30 is provided with a plurality of axially extending holes 48 which are spaced for concentric registration with passageways 42 when bushing 30 is pressed into channel 44 as shown in FIG. 3.
  • Bushings 30 are fabricated from material having a relatively low coefficient of thermal conductivity so that when they are pressed into channels 44, they insulate the end portions of cylinder 21 from circulating coolant.
  • Each closure collar 22, only one of which is shown in FIG. 3, is configured so that, when bolted to cylinder 21 as shown in FIG. 3, it is thermally isolated from cylinder 21 by gaskets 28, 29.
  • Each closure collar 22 has a counterbore 49 to interconnect, when bolted to cylinder 21, holes 40 with passageways 42 via holes 48 in bushing 30.
  • each closure collar 22 is provided with a plurality of sockets 50 which are concentrically disposed with respect to passageways 42 and holes 48 when mill roll 20 is assembled. Sockets 50 are provided to support rods 31 as shown in FIG. 3.
  • Rods 31 are cylindrical members, one of which is installed in each passageway 42 to transform the passageways 42 into annular conduits 55.
  • mill roll 20 When assembled as indicated in FIG. 3, mill roll 20 comprises a solid core portion 56 which is essentially enveloped by a sheath of coolant in holes 40, counterbores 49, and conduits 55 when coolant is introduced through one journal and removed through the oppositely disposed journal.
  • core portion 46 is a virtually isothermal strongback for the portion of cylinder 21 disposed radially outwardly from the core, which portion is hereby designated the shell portion 57 of cylinder 21.
  • the virtually isothermal solid core resists deformation of the working surface 43 of cylinder 21 which would otherwise be induced by thermal gradients in the shell portion of the cylinder or by mechanical stresses. That is, the strongback resists straining of the shell portion 57 of cylinder 21 which would otherwise be precipitated by thermal or mechanical stresses.
  • a groove 46 is provided in each passageway 42 for the purpose of stimulating and sustaining turbulent flow throughout the length of each passageway so that the heat transfer coefficient between flowing coolant and cylinder 21 is substantially constant.
  • grooves 46 in the preferred embodiment of the present invention are spiral, spiral grooves are but one means of promoting turbulent flow.
  • Rods 31, FIGS. 2, 3, are provided to improve the heat transfer coefficient of circulating coolant. That is, for any given coolant flow rate, coolant must flow faster through conduits 55 than through passageways 42 without rods 31 disposed in them. The relative velocity increase precipitates a commensurate increase in the heat transfer coefficient. Another way of looking at this is that the heat transfer coefficient between coolant and walls 45 is directly related to the ratio ofthe heat transfer area of the wall 45 of a passageway 42 or conduit 55 to the cross sectional area of the coolant flowing therethrough.
  • Each rod 31, FIG. 3, has a uniform diameter D over virtually its entire length so that the velocity of coolant is substantially uniform throughout the length of each conduit 55.
  • rods 31 are provided to stimulate and sustain turbulent flow at relatively high constant velocity through conduits 55.
  • the heat transfer coefficient between the IS coolant and wall 45 of cylinder 21 is relatively high and uniform throughout the length of conduits 55.
  • the edge 60 of web 61 is axially spaced distance L from the end of the cylindrical surface 43 of cylinder 21. This reflects the common practice of using less than the full width of a mill roll as a working surface to effect milling and the like. Frictional heat is generated on the working surface of cylinder 21 subjacent web 61 but not on the non-working end portions of its cylindrical surface. Thus, if heat could flow axially through the end portion of cylinder 21 subjacent its non-working surfaces, axial temperature gradients would develop.
  • bushings 30 and gaskets 29 are composed of insulating material to substantially preclude such heat flow, such axial temperture gradients are substantially obviated.
  • Gaskets 28, also composed of insulating material, further obviate heat paths from the ends of cylinder 21 through closure collars 22. Because heat flow through the ends of the shell portion 57 of cylinder 21 is substantially precluded, the ends will operate at nearly the same temperature as the rest of the shell portion 57 of cylinder 21. By thus virtually eliminating axial thermal gradients, thermal distortion of mill roll is practically eliminated.
  • Rod 31b is yet another means for custom tailoring the heat transfer coefficient between circulating coolant and a mill roll.
  • the cross sectional area of rod 31b is varied to satisfy asymmetrical mill roll heat loads by virtue of the relationship between coolant velocity and the heat transfer coefficient. For instance, were rods 31b to replace rods 31 in mill roll 20, FIG. 3, the coolant velocity would rise from the inlet end of conduit 55 to its middle and then fall from the middle to the outlet end of conduit 55. Such a velocity profile would yield a maximum heat transfer coefficient at the middle of mill roll 20.
  • rods 31b provide means for removing the heat so that a substantially isothermal working surface can be maintained. Within the range that velocity changes can affect the heat transfer coefficient, the profile of rod 31b can be tailored to accommodate the above described and other asymmetrical heat load profiles.
  • a mill roll assembly comprising a substantially solid cylinder, a pair of annular bushings, a pair of closure collars, a plurality of annular gaskets, and means for sealingly securing said collars and gaskets to said cylinder,
  • said cylinder comprising a core portion having a right circular cylindrical surface, and a shoulder of reduced diameter on each end of said cylinder, said cylinder also having an axially extending manifold disposed centrally in each end, a plurality of holes in each end which holes extend substantially radially intermediate each said manifold and the adjacent said shoulder, a longitudinally extending annular channel disposed in each end of said cylinder radially outwardly from said shoulders, and a plu rality of parallel, circumferentially spaced passageways disposed subjacent said cylindrical surface and extending longitudinally of said cylinder intermediate said channels,
  • said cylindrical surface comprising a cylindrical working zone intermediate cylindrical nonworking end zones
  • said cylinder further comprising an annular-shape end portion defined intermediate each said nonworking end zone and the radially outwardly disposed surface of the adjacent said channel,
  • said bushings being configured to be press fit into said channels and provided with a longitudinally extending hole in registration with each said passageway so that coolant cannot flow through said channels except through said holes in said bushmgs,
  • said collars and said gaskets being configured to define annular manifolds for sealingly interconnecting said radial holes with said passageays through said bushings when sealingly secured with said means to said cylinder adjacent said shoulders whereby coolant can be conducted through said assembly via said manifolds, said holes, and said passageways to virtually sheath the core portion of said cylinder disposed radially inwardly of said passageways and to remove heat from the cylinder which heat is generated on said working surface during milling, said collars and said gaskets being sealingly secured to said cylinder by said means with one of said gaskets disposed intermediate each said annular-shape end portion of said cylinder and the adjacent said collar to insulate said end portions from said collars, said bushings and said gaskets being further configured to also insulate said end portions from coolant being circulated through said assembly,
  • said gaskets being composed of material of sufficiently low thermal conductivity to virtually preclude longitudinal heat flow through said annularshape end portions of said cylinder, and
  • said bushings being composed of material of sufficiently low thermal conductivity to substantially preclude radial heat flow from said annular-shape end portions of said cylinder,

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Paper (AREA)
  • Treatment Of Fiber Materials (AREA)
US00316809A 1972-12-20 1972-12-20 Selectively insulated mill roll Expired - Lifetime US3834205A (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
US00316809A US3834205A (en) 1972-12-20 1972-12-20 Selectively insulated mill roll
IT54411/73A IT1000719B (it) 1972-12-20 1973-12-18 Rullo di laminazione perfezionato
FR7345543A FR2211296B1 (sv) 1972-12-20 1973-12-19
CA188,482A CA990550A (en) 1972-12-20 1973-12-19 Selectively insulated mill roll
GB5876373A GB1420797A (en) 1972-12-20 1973-12-19 Mill roll
DE2363063A DE2363063A1 (de) 1972-12-20 1973-12-19 Walze
NL7317367A NL7317367A (sv) 1972-12-20 1973-12-19
JP48142905A JPS4996157A (sv) 1972-12-20 1973-12-20
BE139087A BE808889A (fr) 1972-12-20 1973-12-20 Cylindre de laminoir perfectionne

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US31680772A 1972-12-20 1972-12-20
US00316809A US3834205A (en) 1972-12-20 1972-12-20 Selectively insulated mill roll

Publications (1)

Publication Number Publication Date
US3834205A true US3834205A (en) 1974-09-10

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Application Number Title Priority Date Filing Date
US00316809A Expired - Lifetime US3834205A (en) 1972-12-20 1972-12-20 Selectively insulated mill roll

Country Status (9)

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US (1) US3834205A (sv)
JP (1) JPS4996157A (sv)
BE (1) BE808889A (sv)
CA (1) CA990550A (sv)
DE (1) DE2363063A1 (sv)
FR (1) FR2211296B1 (sv)
GB (1) GB1420797A (sv)
IT (1) IT1000719B (sv)
NL (1) NL7317367A (sv)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4251253A (en) * 1975-08-20 1981-02-17 Hermann Heye Cooling system for molds
US4261112A (en) * 1977-01-10 1981-04-14 Joachim Apitz Heat exchange cylinder
US4506727A (en) * 1982-06-14 1985-03-26 Usm Corporation Converted temperature control roll
US5180002A (en) * 1991-03-22 1993-01-19 Michelin & Cie Cylinder for rubber mixing mill
EP0873805A1 (en) * 1997-04-24 1998-10-28 Kvaerner Technology & Research Limited A casting roll and roll stand
US5983993A (en) * 1996-08-30 1999-11-16 International Paper Company High production chill roll
EP1136621A2 (de) * 2000-03-14 2001-09-26 Walzen Irle GmbH Rotierbare Walze
US20040132596A1 (en) * 2002-08-28 2004-07-08 Heinz-Michael Zaoralek Roller for the thermomechanical treatment of a web-shaped medium
US20040144520A1 (en) * 2001-05-29 2004-07-29 Alfredo Poloni Crystallizer with rollers for a continuous casting machine
RU2629579C2 (ru) * 2015-11-27 2017-08-30 Федеральное государственное бюджетное учреждение науки Институт металлургии и материаловедения им. А.А. Байкова Российской академии наук (ИМЕТ РАН) Листопрокатная клеть
RU2698241C1 (ru) * 2018-10-24 2019-08-23 Федеральное государственное автономное образовательное учреждение высшего образования "Уральский федеральный университет имени первого Президента России Б.Н. Ельцина" Способ прокатки в валках с волнообразным профилем бочки
US20220080695A1 (en) * 2019-01-15 2022-03-17 Src Corporation Corrugating roller having enhanced heat transfer effectiveness

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2844051C3 (de) * 1978-10-10 1982-01-28 Küsters, Eduard, 4150 Krefeld Verfahren zum Kühlen eines Walzenpaars sowie Kalander zur Durchführung des Verfahrens
JPS587056B2 (ja) * 1979-11-02 1983-02-08 東北金属工業株式会社 微細加工方法
DE3009638C2 (de) * 1980-03-13 1982-11-04 Heidelberger Druckmaschinen Ag, 6900 Heidelberg Walzen für Farb- oder Feuchtmitteltransport in Offsetdruckmaschinen
DE4036121C2 (de) * 1990-07-26 1997-06-12 Schwaebische Huettenwerke Gmbh Heizwalze
FR2672523B1 (fr) * 1991-02-13 1995-04-21 Usinor Sacilor Virole de cylindre de coulee continue.
DE10017604A1 (de) * 2000-03-14 2001-10-18 Walzen Irle Gmbh Rotierbare Walze
DE10353288B4 (de) * 2003-11-14 2011-01-05 Shw Casting Technologies Gmbh Temperierbare Walze

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1382608A (en) * 1920-02-18 1921-06-21 Pennsylvania Wire Glass Compan Machinery for rolling glass
US1781378A (en) * 1928-04-23 1930-11-11 Congoleum Nairn Inc Calender roll
US2531988A (en) * 1946-03-13 1950-11-28 Pittsburgh Plate Glass Co Plate glass sizing roll
US2849951A (en) * 1954-11-01 1958-09-02 Harald H Heinrich Printing press with cooled cylinder
US2912556A (en) * 1958-05-02 1959-11-10 Farrel Birmingham Co Inc Electrically heated roll for calenders or the like
US3484227A (en) * 1965-05-13 1969-12-16 Fabricacion De Maquinas Drawing and/or annealing rolls for sheet glass making apparatus
US3738423A (en) * 1970-03-06 1973-06-12 Fleissner Gmbh Godet for drawing units and roller dryers used for treating man-made fibers

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1468066A (fr) * 1965-05-13 1967-02-03 Rouleau pour machines à fabriquer le verre en feuilles

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1382608A (en) * 1920-02-18 1921-06-21 Pennsylvania Wire Glass Compan Machinery for rolling glass
US1781378A (en) * 1928-04-23 1930-11-11 Congoleum Nairn Inc Calender roll
US2531988A (en) * 1946-03-13 1950-11-28 Pittsburgh Plate Glass Co Plate glass sizing roll
US2849951A (en) * 1954-11-01 1958-09-02 Harald H Heinrich Printing press with cooled cylinder
US2912556A (en) * 1958-05-02 1959-11-10 Farrel Birmingham Co Inc Electrically heated roll for calenders or the like
US3484227A (en) * 1965-05-13 1969-12-16 Fabricacion De Maquinas Drawing and/or annealing rolls for sheet glass making apparatus
US3738423A (en) * 1970-03-06 1973-06-12 Fleissner Gmbh Godet for drawing units and roller dryers used for treating man-made fibers

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4251253A (en) * 1975-08-20 1981-02-17 Hermann Heye Cooling system for molds
US4261112A (en) * 1977-01-10 1981-04-14 Joachim Apitz Heat exchange cylinder
US4506727A (en) * 1982-06-14 1985-03-26 Usm Corporation Converted temperature control roll
US5180002A (en) * 1991-03-22 1993-01-19 Michelin & Cie Cylinder for rubber mixing mill
US5983993A (en) * 1996-08-30 1999-11-16 International Paper Company High production chill roll
EP0873805A1 (en) * 1997-04-24 1998-10-28 Kvaerner Technology & Research Limited A casting roll and roll stand
US20030192673A1 (en) * 2000-03-14 2003-10-16 Schweinichen Jaxa Von Rotatable roller
EP1136621A3 (de) * 2000-03-14 2003-08-20 Walzen Irle GmbH Rotierbare Walze
EP1136621A2 (de) * 2000-03-14 2001-09-26 Walzen Irle GmbH Rotierbare Walze
US6793008B2 (en) * 2000-03-14 2004-09-21 Walzen Irle Gmbh Rotatable roller
US20040144520A1 (en) * 2001-05-29 2004-07-29 Alfredo Poloni Crystallizer with rollers for a continuous casting machine
US6883585B2 (en) 2001-05-29 2005-04-26 Danieli & C. Officine Meccaniche Spa Crystallizer with rollers for a continuous casting machine
US20040132596A1 (en) * 2002-08-28 2004-07-08 Heinz-Michael Zaoralek Roller for the thermomechanical treatment of a web-shaped medium
US7097605B2 (en) 2002-08-28 2006-08-29 Shw Casting Technologies Gmbh Roller for the thermomechanical treatment of a web-shaped medium
RU2629579C2 (ru) * 2015-11-27 2017-08-30 Федеральное государственное бюджетное учреждение науки Институт металлургии и материаловедения им. А.А. Байкова Российской академии наук (ИМЕТ РАН) Листопрокатная клеть
RU2698241C1 (ru) * 2018-10-24 2019-08-23 Федеральное государственное автономное образовательное учреждение высшего образования "Уральский федеральный университет имени первого Президента России Б.Н. Ельцина" Способ прокатки в валках с волнообразным профилем бочки
US20220080695A1 (en) * 2019-01-15 2022-03-17 Src Corporation Corrugating roller having enhanced heat transfer effectiveness

Also Published As

Publication number Publication date
GB1420797A (en) 1976-01-14
CA990550A (en) 1976-06-08
JPS4996157A (sv) 1974-09-11
NL7317367A (sv) 1974-06-24
FR2211296A1 (sv) 1974-07-19
IT1000719B (it) 1976-04-10
FR2211296B1 (sv) 1979-06-29
BE808889A (fr) 1974-06-20
DE2363063A1 (de) 1974-07-04

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