US20080125297A1 - Roll With Rotating Shell - Google Patents

Roll With Rotating Shell Download PDF

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Publication number
US20080125297A1
US20080125297A1 US11/547,723 US54772304A US2008125297A1 US 20080125297 A1 US20080125297 A1 US 20080125297A1 US 54772304 A US54772304 A US 54772304A US 2008125297 A1 US2008125297 A1 US 2008125297A1
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United States
Prior art keywords
pocket
pad
shell
pressure
roll
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Abandoned
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US11/547,723
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English (en)
Inventor
Jean-Paul Faure
Eric Paracuellos
Xiao Wang
Shouqun Chen
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Individual
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Individual
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Publication of US20080125297A1 publication Critical patent/US20080125297A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—Bearings
    • F16C13/022—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle
    • F16C13/024—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle
    • F16C13/026—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle by fluid pressure
    • F16C13/028—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle by fluid pressure with a plurality of supports along the length of the roll mantle, e.g. hydraulic jacks
    • 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
    • B21B27/05—Sleeved rolls with deflectable sleeves
    • B21B27/055—Sleeved rolls with deflectable sleeves with sleeves radially deflectable on a stationary beam by means of hydraulic supports
    • 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
    • D21G1/0206—Controlled deflection rolls
    • D21G1/0213—Controlled deflection rolls with deflection compensation means acting between the roller shell and its supporting member
    • D21G1/022—Controlled deflection rolls with deflection compensation means acting between the roller shell and its supporting member the means using fluid pressure

Definitions

  • the invention relates to a roll with rotating shell of the type consisting of a cylindrical tubular shell rotatably mounted about an elongated support beam and bearing on the said beam via holding means, and applies in particular to a back-up roll in a rolling mill for metal strip, especially steel strip.
  • a rotating shell consisting of a stationary support shaft in the form of an elongated beam, surrounded by a tubular shell rotatably mounted about bearings defining an axis of rotation perpendicular to rolling axis, and bearing on the beam via a plurality of holding means distributed side by side along the length of the beam and centered in an axial bearing plane passing through the roll axis and an external face of the roll, and corresponding to the plane of transmission of the roll force load when the roll is part of a rolling mill.
  • each means of holding the shell consists of a pad essentially centered in the bearing plane, disposed between the shell and the support beam and slideably mounted on the said support beam in a radial direction essentially extending in the roll load plane.
  • Each pad bears on one side of the internal face of the shell, via a cylindrical bearing face, and on the other side on the support beam via an adjustable thrust means generally consisting of at least one hydraulic cylinder arranged between the support beam and the pad. It is thus possible to regulate the thrust of each pad individually in the radial direction, in order to give the tubular shell the desired profile and/or correct the distribution of thrust forces throughout the external bearing face.
  • the tubular shell rotates on the bearing faces of the holding pads, and it is therefore necessary to introduce a lubricant between the bearing face of each pad and the internal face of the shell.
  • each holding pad can be provided, on its bearing face, with at least one hydrostatic pocket consisting of a recess opening towards the outside and fed with a lubricant under a pressure corresponding to the thrust.
  • the lubricant fed in the said pocket under pressure may escape toward the edges of the pocket, forming a lubricating film in the gap between the bearing face of the pad and the shell.
  • the lubricant feeding the hydrostatic pocket is simply taken from the fluid that feeds the thrust cylinder via a channel provided between the cylinder chamber and the hydrostatic pocket.
  • Such a feeding mode could be appropriate when such devices were used, for example, in the paper industry.
  • metal strip rolling in particular steel rolling
  • the thrust loads sustained by the roll are extremely high and it is difficult to control the thrust cylinders if there is a variable leak rate for feeding the hydrostatic pocket.
  • a further advantage of this arrangement is that the lubricant is not fed from the thrust cylinder chamber but through a separate circuit under low pressure. It is thus not necessary, as before, to maintain a leak rate in the high pressure circuit feeding the thrust cylinders.
  • the pressure which is very low at the upstream end of the gap between the pad and the shell, gradually increases due to the oil drag-out, reaches a peak which is angularly shifted downstream with respect to the roll load plane passing through the external bearing face, then very quickly decreases and becomes nil at the downstream end of the gap, at pad exit. This results in a self-centering of the pad by a wedge effect.
  • the bearing face of each pad which, as described above, must cover a large angular sector, has the form of an elongated rectangle of fairly small width compared with its length.
  • the hydrodynamic lift effect created by oil circulation in the gap between the pad and the shell therefore develops in a pressure area comprising, in the lengthwise direction of fluid circulation, an upstream portion for gradually increasing the fluid pressure from pad entry, a hydrodynamic lift central portion and a downstream portion for quick decrease in pressure at pad exit.
  • the central lift part covers an angular sector of the pad subjected to a sufficient pressure to compensate for the global bearing force exerted on the tubular shell by the work roll.
  • transient excess pressures may occur, especially when threading the strip into the rolling stand or when a weld joining two successive strips, which may have different geometric or metallurgical properties, is passing through.
  • the object of the invention is to remedy such disadvantages by a fairly simple arrangement which allows better control of the hydrodynamic film oil feeding and of pressure distribution on the bearing face of each pad, thus more easily maintaining relatively stable operating conditions.
  • the invention therefore relates to a roll with a rotating shell of the type consisting of a tubular shell rotatably mounted about a stationary elongated support beam and bearing on the said beam via a plurality of pads, each provided with a cylindrical bearing face having nearly the same radius as the radius of the internal face of the shell, whereby the position and thrust of each pad can be adjusted through a hydraulic cylinder resting, on one side, on the beam, and on the other side, on the pad, and fed with a pressurized fluid, each pad being, in addition, fitted with an hydrostatic pocket provided in a central part of its bearing face and fed with a pressurized fluid, and besides, associated with means of introducing a lubricating fluid upstream of the gap between the pad bearing face and the internal face of the shell, so as to create a hydrodynamic lift effect in a pressure area which covers a large angular sector and comprises, in the shell rotational direction, an upstream portion for gradually increasing the pressure, a lift central portion and a downstream portion for quick decrease in pressure
  • each pad is fitted with two lateral pockets opening on both sides of the middle pocket, respectively, and fed with a fluid under a pressure sufficient to allow an additional oil flow to be introduced into the dragged out film with a local pressure increase, in order to broaden—in the upstream and downstream direction—the angular sector covered by the central hydrodynamic lift portion of the pad, thus improving the stability of said pad.
  • each pocket of each pad is associated with a means of calibrating the flow rate input through the relevant pocket, whereby the pressure in said pocket is adjusted to a level at least sufficient to cause the calibrated flow to be discharged at the corresponding level of the fluid film, up to a maximum value of the thrust exerted by the pad on the shell.
  • the central lift part of the pressure area consists of a high pressure central pressure stage covering an angular sector nearly corresponding to the middle pocket, and two lateral pressure stages each extending on an angular sector associated with a lateral pocket, an upstream pressure stage having a lower pressure than that of the central pressure stage and a downstream pressure stage having a pressure between that of the central pressure stage and that of the upstream pressure stage.
  • each middle pocket of a pad is individually fed by a pump delivering a calibrated flow and the lateral pockets of all the pads arranged on one side of the middle pocket are supplied in parallel from the same pipe connected to the same pump on which a plurality of individual feed pipes for each pocket, each fitted with a calibrating device for the fluid flow injected through said pocket into the dragged-out film, are connected in parallel.
  • the roll includes at least three units, respectively consisting of the pockets arranged on all pads in the same position with respect to the bearing plane, upstream lateral, central and downstream lateral, respectively, and the pockets of each unit are fed in parallel from a joint piping provided lengthwise on the support beam and on which a plurality of individual feeding pipes for each pocket of said unit respectively, each fitted with an individual flow calibrating device in the corresponding, are connected in parallel.
  • a roll with a rotating shell according to the invention can be used, either in a tandem rolling mill in which the product is always running in the same direction, or in a reversing rolling mill operating in both running directions.
  • the middle pocket of each pad is centered in a radial plane slightly angularly shifted downstream, in the direction of rotation, relative to the bearing plane.
  • the downstream lateral pocket advantageously covers an angular sector which is nearly twice as large as the sector covered by the upstream lateral pocket.
  • the middle pocket is centered in the bearing plane P and the lateral pockets are symmetrical with respect to said bearing plane.
  • the calibrated flow rates in both lateral pockets may be equal and the calibrated flow in the middle pocket is advantageously approx. twice as high as the flow rate in each lateral pocket.
  • FIG. 1 is a cross-sectional schematic view of a roll according to the invention applied to a rolling mill.
  • FIG. 2 is detailed cross-sectional view of a holding pad with associated hydraulic circuits.
  • FIG. 3 is a bottom view of a holding pad.
  • FIG. 4 is a longitudinal cross-sectional view of the roll, on which the oil feeding system is schematically shown.
  • FIG. 5 is a 3-D diagram showing the pressure curve along the bearing face of a pad.
  • FIG. 1 is a schematic cross-sectional view showing, by way of example, a four-high type rolling mill consisting of two work rolls T, T′ between which the rolled product M passes, and supported on the side opposite to the product on two back-up rolls S, S′ respectively, between which a roll force load is applied along a bearing plane P passing virtually through the roll axes.
  • At least one of the back-up rolls e.g. the upper back-up roll S consists of a tubular shell 1 rotatably mounted at its ends, through bearings A, A′ schematically shown in FIG. 4 , on a support beam 11 extending inside the tubular shell 1 , in a direction transverse to the rolling direction, said bearings A, A′ defining the rotational axis x′x of the shell.
  • the tubular shell 1 bears on the beam 11 through a plurality of holding pads 3 distributed throughout its length and intercalated between the internal cylindrical face 13 of the shell and a lower face 12 of the support beam 11 .
  • Each holding pad 3 is provided, on the tubular shell 1 side, with a cylindrical bearing face 31 of a slightly smaller diameter than the diameter of the inner face 13 of the shell, and bears on the lower face 12 of the beam 11 through at least one hydraulic cylinder 2 which, in the depicted example, includes one piston 22 bearing on the beam 11 and entering into a recess 33 machined on the face 32 of the pad 3 turned toward the beam 11 and constituting the chamber of the hydraulic cylinder 2 .
  • Said cylinder is fed with fluid from a hydraulic power station H 1 by a high pressure supply circuit, connected to each pad via a pipe 21 passing through the beam 11 and the piston 22 and opening into the chamber 33 of the associated cylinder.
  • Each pad 3 is thus associated with a cylinder 2 fed by a special circuit 20 , 21 , the flow rate and pressure of which can be controlled by a control system on the basis of data transmitted by devices controlling the thickness and profile or flatness of the rolled product M.
  • a control system on the basis of data transmitted by devices controlling the thickness and profile or flatness of the rolled product M.
  • such a system makes it possible, via a position and pressure control of each cylinder 2 , to adjust the profile of the external bearing face as well as the distribution of thrust forces applied along said external bearing face, in particular to compensate for the deflection of the support beam 11 and to correct gauge or flatness defects detected downstream on the rolled strip M.
  • each pad 3 is normally provided with a hydrostatic pocket substantially centered in the bearing plane P and fed with pressurized oil, said pocket widely opening toward the internal face 13 of the tubular shell in order to form a lubricating film 4 between the internal face 13 of the shell 1 and the bearing face 31 of the pad 3 .
  • the bearing face 31 of the pad 3 covers a circular sector with a very wide angular opening larger than 45°, which may exceed 90° and, preferably being in the order of magnitude of 100 or 110°.
  • an angular sector having a fairly great length allows a hydrodynamic lift effect to be created in the lubricating fluid film 4 .
  • oil can be fed under low pressure by a booster circuit G, at the upstream end of the pad 3 and, through rotation of the shell 1 , is caused to flow into the gap between said shell and the pad 3 , with a gradual increase in pressure through wedge effect.
  • the fact that the pads 3 , distributed across the length of the tubular shell 1 , are provided with a large angular opening ensures excellent centering of said shell relative to the beam 11 , with a transverse stability effect avoiding transverse deformation of the shell between the end bearings when the product is passing through.
  • each pad 3 should have a length L 1 much greater than its width L 2 , as shown in FIG. 3 .
  • the pressure area thus consists of an upstream portion for a gradual increase in pressure, a central part constituting a maximum pressure stage in the region of the central pocket 5 and a downstream portion for quick pressure decrease at pad exit.
  • the hydrodynamic lift effect created by the oil film 4 drag-out permits self-centering of the pad because a closure of the gap on the exit side increases the pressure through a wedge effect and, consequently, tends to re-centre the shell with respect to the pad.
  • the leak rate also tends to increase and is likely to cause a breakage of the oil film, thereby causing the pad to contact the shell.
  • the bearing face 31 of the pad is provided, on each side of the middle pocket 5 , with two downstream 6 and upstream 7 lateral pockets respectively and each pocket 5 , 6 , 7 is associated with a means of calibrating the flow introduced through this pocket under a pressure set to a value at least equal to the hydrodynamic pressure at this level to allow the calibrated flow rate to be discharged into the fluid dragged out by the shell rotation.
  • Oil injected into the three pockets 5 , 6 , 7 spaced apart from each other is thus distributed by forming a continuous film nearly throughout the angular sector covered by the bearing face 31 , as schematically shown in FIG. 5 .
  • each pocket 5 , 6 , 7 is fed at a sufficient pressure to allow the calibrated flow to be discharged and, in the region of each pocket, a local pressure increase occurs, which makes it possible, as explained further, to compensate for the tilting torques sustained by the pad and to ensure stability of said pad in the event of a sudden variation in the applied forces, for example when a weld is passing through the roll gap.
  • FIG. 1 schematically shows an embodiment of the oil feeding system for each pad 3 .
  • the thrust cylinders 2 associated with each pad 3 respectively are fed with pressurized fluid from a hydraulic station H 1 , by a circuit 20 , 21 opening into the chamber 33 of each cylinder 2 .
  • the hydrostatic pockets 5 , 6 , 7 are supplied by pipes 51 , 61 , 71 , respectively, from a second hydraulic power station H 2 . It is thus possible to use oils having different viscosity values depending on the application.
  • the cylinders 2 should be supplied with a low viscosity oil from the hydraulic station H 1 .
  • the hydrostatic pockets 5 , 6 , 7 can be fed with higher viscosity oil from the second hydraulic station H 2 , giving higher hydrostatic lift and less leaks on side edges.
  • FIG. 1 schematically shows a first embodiment of the circuits 8 a , 8 b for pressurized feeding of the pockets 5 , 6 , 7 .
  • the lubricant is fed from tank 80 through a pump 83 with fixed delivery, controlled by flow controller 88 and transferred back to the tank through an overfall system including an adjustable permanent leak system 84 .
  • each pad is fed under pressure, each through a pipe 51 , 61 , 71 respectively, fitted with a flow controller 52 , 62 , 72 which, during operation, enables oil to be introduced into each pocket with a regulated flow rate at a virtually constant value.
  • Pressure values in each feed circuit 51 , 61 , 71 are determined so as to ensure this calibrated oil flow is discharged into each pocket, up to a maximum value of the thrust force likely to be applied on the shell, taking the pocket dimensions into account.
  • the roll is advantageously provided with a collecting device extending throughout the shell length, above the downstream ends of all pads, in order to collect the oil escaping from the pads and transfer it back, through a return circuit 86 , to the hydraulic station H 2 .
  • FIG. 4 a simple schematic axial sectional view, the pads 3 have been shown with a 90° rotation to represent the feeding circuits for the three pockets which, actually, are centered in the same plane in a direction transverse to the centerline.
  • the adjacent pads 3 distributed across the full length of the shell are identical, each consisting of at least three pockets, upstream lateral 7 , middle 5 and downstream lateral 6 , respectively, and arranged in the same position relative to the bearing plane P.
  • said joint pipes can be bored in the support beam 11 , in a direction parallel to the axis of rotation x′x or the may consist of pipes attached to the side of beam 11 .
  • the two pocket units, upstream lateral E 3 and downstream lateral E 2 respectively, can advantageously be supplied under the same pressure from the same pipe 60 .
  • the beam 11 is provided with three axial pipes, respectively 20 for feeding the thrust cylinders 2 , 50 for feeding the middle pockets 5 and 60 for feeding the upstream 7 and downstream 6 lateral pockets.
  • Feed circuits 51 , 61 , 71 associated with each of the pads 3 and which, for reasons of simplification, have been indicated on each side of beam 11 in FIG. 1 , advantageously consist of pipes 51 a , 61 a , 71 a bored crosswise in the support beam 11 and connected in parallel to the feed pipe 50 of the unit E 1 of middle pockets 5 and to the feed pipe 60 of the units E 3 , E 2 of lateral pockets, upstream 7 and downstream 6 .
  • Transverse pipes 51 a , 61 a , 71 a are connected via flexible hoses 51 b , 61 b , 71 b respectively, each to the associated pipe 51 c , 61 c , 71 c bored in the pad 3 and opening, at one end, on one lateral side of the pad 3 and, at the other end, in the corresponding pocket 5 , 6 , 7 , respectively.
  • each individual circuit 51 abc , 61 abc , 71 abc is provided with a calibrating device 52 , 62 , 72 arranged, for example, on the beam 11 , at the outlet of the transverse pipe 51 a , 61 a , 71 a , and allowing control of oil injection into the relevant pocket 5 , 6 , 7 , while keeping the exit flow rate constant.
  • joint pipes 20 , 50 , 60 are bored longitudinally in the support beam 11 but could also be attached to the beam side.
  • Chamber 33 of the thrust cylinder of each pad 3 is supplied with high pressure, low viscosity oil from the first hydraulic station H 1 via a circuit 20 which can advantageously pass through a longitudinal bore in the beam 11 .
  • Said circuit including means of individually adjusting the position and pressure of each pad 3 , is well known and has, therefore, not been described or shown in details on the drawings.
  • joint pipes 50 , 60 are fed, via the hydraulic station H 2 , with higher viscosity oil, preferably through two separate circuits, 8 a , 8 b respectively, that enable the unit E 1 of middle pockets 5 on the one hand, and the two lateral pocket units, upstream E 3 and downstream E 2 respectively, on the other hand, to be supplied at different pressures, said pressures being adjusted to ensure continuous oil discharge throughout the bearing surface of pad 3 , taking into account the distribution of thrust force and hydrodynamic pressure in the lubricating film 4 .
  • the hydraulic station H 2 also comprises a booster pump 87 for low pressure oil feeding at the entry 34 of the pad 3 .
  • the oil introduced through the lateral pockets 6 , 7 is, of course, of the same nature and mixes with the lubricating film 4 dragged out due to the shell rotation.
  • Each pump 83 a , 83 b is associated with a flow controller 88 a , 88 b , with an overfall device 84 a , 84 b .
  • the oil supplied by pumps 83 a , 83 b is returned to the tank.
  • the calibrated flow rate is delivered by the corresponding pocket and mixes with the dragged out fluid in order to compensate for the leaks and to increase the pressure.
  • the rolling mill is designed to operate within a given rolling force range and the feed pressures in joint pipes 50 , 60 as well as the calibrated flow rates introduced into each pocket 5 , 6 , 7 through the individual circuits 51 , 61 , 71 are determined so as to ensure that oil is discharged and a continuous film is formed throughout the adjusting range of the thrust force exerted on each pad by the cylinder 2 , up to a maximum value which depends on the working conditions and on such parameters as—in case of strip rolling—the width and thickness of said strip, material temperature and properties, as well as the reduction in thickness to be obtained.
  • the hydraulic feeding mode shown in FIG. 1 is fairly economical as the hydraulic station H 2 feeding the pockets 5 , 6 , 7 uses only two medium pressure pumps, 83 a for the middle pockets and 83 b for the lateral pockets, respectively.
  • FIG. 4 schematically shows such an embodiment consisting of a pumping unit 9 which comprises as many pumps 91 as there are pads 3 , each pump 91 feeding the middle pocket of a pad at the pressure required for discharging the calibrated flow, taking into account the thrust force applied on the shell 1 in the region of the relevant pad.
  • a pumping unit 9 which comprises as many pumps 91 as there are pads 3 , each pump 91 feeding the middle pocket of a pad at the pressure required for discharging the calibrated flow, taking into account the thrust force applied on the shell 1 in the region of the relevant pad.
  • the two lateral pocket units E 2 , E 3 can be fed through the same pump 83 by a circuit 8 similar to the one that has previously been described with reference to FIG. 1 .
  • this circuit 8 may include, downstream of the pump 83 , a safety block 84 which limits the common pressure to the required level and a device 88 for measuring and controlling the global flow rate in the two units E 2 , E 3 of lateral pockets of the pads 3 .
  • FIG. 5 is a 3D-diagram showing, for a half pad placed on one side of the middle plane Q perpendicular to the axis of rotation, the pressure curve on the ordinate axis, as a function of the angular position along the bearing face 31 of the pad, indicated after development of said bearing face along the horizontal abscissa axis.
  • the upstream lateral pocket 7 covers an angular sector of approx. 10°, having its middle plane P 1 inclined at approx. 25° relative to the bearing plane P on which the middle pocket 5 is centered, and the middle plane P 2 of the downstream pocket 6 , which also covers a sector of approx. 10°, is inclined at approx. 20° relative to said vertical bearing plane P.
  • the middle pocket 5 is centered on the bearing plane P and covers an angular sector of approx. 20°.
  • the pad remains of the type shown in FIG. 2 and, therefore, comprises means of introducing, at the entry 34 of the pad, a lubricating fluid which is dragged out by the rotation of shell 1 and creates a hydrodynamic lift effect.
  • the pressure diagram includes, as usual, an upstream zone A for gradual increase of the fluid pressure, a central zone B of maximum pressure and a downstream zone C for fast pressure decrease at exit of the pad.
  • the two lateral pockets 7 , 6 significantly modify the shape of parts A and C of the diagram by creating therein two pressure stages, upstream 41 and downstream 42 , respectively, on each side of a central pressure stage 40 corresponding to the middle pocket 5 .
  • the width L 2 of the pad is small compared to its length L 1 causes lateral oil leaks and the maximum pressure area tends to tighten in the direction of rotation of the shell.
  • Introducing an additional oil flow through the upstream pocket 7 is a means of compensating for this leakage and, consequently, of longitudinally and transversely widening the central pressure stage 40 , which can thus cover a length and a width fairly close to the dimensions of the middle pocket 5 .
  • the leak rate After exiting said middle pocket 5 , the leak rate further increases and the oil escapes from the gap between pad and shell with a risk of contact with the exit of the pad.
  • the oil introduced through the downstream pocket 6 must be at a fairly high pressure, higher than the pressure of the upstream pocket 7 , and this additional calibrated oil flow permits the part C of the hydrodynamic lift zone to be widened in the downstream direction, thus avoiding any risk of contact with the pad and the shell.
  • pressure in the downstream pocket 6 may be about half the maximum pressure in the middle pocket 5 .
  • the angular sector covered by the hydrodynamic lift zone is thus widened in the upstream and downstream directions.
  • injecting a pressurized fluid into the two lateral pockets 6 , 7 causes, by hydrostatic effect, thrust forces F 1 , F 2 centered on the middle radial planes P 1 , P 2 of both pockets 6 , 7 which are inclined at a minimum angle of 20° relative to the bearing plane P.
  • the hydrodynamic lift zone should, however, cover a large angular sector, approx. one quadrant and, anyway, of at least 45° to 50°.
  • the middle plane P 1 of the downstream pocket 6 be more inclined with respect to the bearing plane P than the middle plane P 2 of the upstream pocket 7 .
  • the middle pocket 5 could be slightly shifted in the downstream direction, in the direction of rotation of the shell 1 , in order to compensate for the deformation of the associated work roll in the reverse direction while the product is passing through. In this case, the middle plane P of the middle pocket 5 would be slightly inclined with respect to the vertical plane.
  • this invention may also advantageously apply to the construction of reversing mills in which the rolls and, consequently the tubular shell 1 , are rotating alternately in one direction and the other.
  • the arrangement would be symmetric, as the middle pocket 5 is centered on the vertical plane passing through the axis and the two lateral pockets 6 and 7 are equal and centered on inclined planes of the same angle relative to the vertical line, on each side thereof.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Geometry (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
US11/547,723 2004-04-16 2004-04-16 Roll With Rotating Shell Abandoned US20080125297A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/FR2004/000954 WO2005110635A1 (fr) 2004-04-16 2004-04-16 Cylindre a enveloppe tournante

Publications (1)

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US20080125297A1 true US20080125297A1 (en) 2008-05-29

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US11/547,723 Abandoned US20080125297A1 (en) 2004-04-16 2004-04-16 Roll With Rotating Shell

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US (1) US20080125297A1 (fr)
EP (1) EP1740326A1 (fr)
CN (1) CN100546733C (fr)
WO (1) WO2005110635A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10677286B2 (en) 2016-05-26 2020-06-09 Flender-Graffenstaden S.A.S. Hydrodynamic bearing with injectors and deflectors

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI123495B (fi) * 2012-04-24 2013-05-31 Metso Paper Inc Järjestely kalanterin telojen värähtelyjen vaimentamiseksi

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4882922A (en) * 1986-06-04 1989-11-28 Clecim S. A. Rolling mill roll with rotating shell
US5967957A (en) * 1995-07-26 1999-10-19 Eduard Kusters Maschinenfabrik Gmbh & Co. Roller assembly with internal supporting elements

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2942002C2 (de) * 1979-10-17 1982-06-16 Kleinewefers Gmbh, 4150 Krefeld Druckbehandlungswalze
DE3700439A1 (de) * 1986-09-05 1988-03-17 Escher Wyss Ag Durchbiegungseinstellwalze
DE4133562A1 (de) * 1991-10-10 1993-04-22 Voith Gmbh J M Walze mit biegungsausgleich

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4882922A (en) * 1986-06-04 1989-11-28 Clecim S. A. Rolling mill roll with rotating shell
US5967957A (en) * 1995-07-26 1999-10-19 Eduard Kusters Maschinenfabrik Gmbh & Co. Roller assembly with internal supporting elements

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10677286B2 (en) 2016-05-26 2020-06-09 Flender-Graffenstaden S.A.S. Hydrodynamic bearing with injectors and deflectors

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Publication number Publication date
WO2005110635A1 (fr) 2005-11-24
EP1740326A1 (fr) 2007-01-10
CN100546733C (zh) 2009-10-07
CN1984728A (zh) 2007-06-20

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