US3119324A - Controlled deflection roll - Google Patents

Controlled deflection roll Download PDF

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US3119324A
US3119324A US52456A US5245660A US3119324A US 3119324 A US3119324 A US 3119324A US 52456 A US52456 A US 52456A US 5245660 A US5245660 A US 5245660A US 3119324 A US3119324 A US 3119324A
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roll
pressure
roll shell
nip
support
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US52456A
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Edgar J Justus
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Beloit Iron Works Inc
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Beloit Iron Works Inc
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02Bearings
    • F16C13/022Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle
    • F16C13/024Bearings 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
    • F16C13/026Bearings 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
    • F16C13/028Bearings 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
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B65CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65HHANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H27/00Special constructions of feed or guide rollers and surfaces thereof
    • DTEXTILES; PAPER
    • D21PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21FPAPER-MAKING MACHINES; METHODS OF PRODUCING PAPER THEREON
    • D21F3/00Press section of machines for making continuous webs of paper
    • D21F3/02Wet presses
    • D21F3/08Pressure rolls
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00Sliding-contact bearings for exclusively rotary movement
    • F16C17/02Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B65CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65HHANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00Parts for transporting or guiding the handled material
    • B65H2404/10Rollers
    • B65H2404/13Details of longitudinal profile
    • B65H2404/137Means for varying longitudinal profiles
    • B65H2404/1372Means for varying longitudinal profiles anti-deflection

Description

Jan. 28, 1964 E. J. Jus-rus 3,119,324

CONTROLLED DEFLECTION ROLL Filed Aug. ze. 1960 2 sheets-sheet a INVENTOR. 04am d, das/a5 MM nu ,L wrrulcx'lfs United States Patent O 3,119,324 CONTRLLED DEFLECTION ROLL Edgar J. Justus, Beloit, Wis., assigner to Beloit Iron Works, Beloit, Wis., a corporation of Wisconsin Filed Aug. 29, 1960, Ser. No. 52,456 9 Claims. (Cl. 10G-170) The present invention relates to improvements in supported rolls and mechanisms for controlling the deflection of the rolls.

In various uses of press rolls and in support or drive rolls deflection of the roll exists. Mechanisms employ rolls positioned to form a pressure nip for rolling materials between them which will cause a deflection of the rolls due to forces at the nip. Other mechanisms employ rolls subject to deflection forces such as those carrying a travelling belt or web. In paper making machinery, for example, drive rolls mounted to engage the loop of the forming wire in a Fourdrinier type paper making machine engage the surface of the wire and the weight of the roll coupled with an applied load arising from the resistance of the wire to being driven produce a force component which tends to deflect the drive roll in a direction downwardly and toward the oncoming forming wire. The deflection of the roll tends to cause the off-running portion of the forming wire to be compacted or squeezed materially increasing the wear on the wire. As well, in press roll couples and other roll arrangements wherein at least a pair of rolls are in nip defining relationship the algebraic summation of the weight, the nip forces, the bending movements produced by the journal loading, and torque (if any) tends to produce in each of such rolls a curvature of its centroidal axis, in accordance with well-known laws of flexure of materials. It is common to attempt to counter this effect by crowningj i.e. by grinding the rolls slightly barrel shape in an amount and curvature calculated to offset the curvature under operating conditions. In certain environments this causes undesirable effects and the difference in the surface speed of the roll between the central and end portions of the roll is often disadvantageous to the product being rolled. Various stages in the course of paper manufacturing employ such roll structures. Efforts have heretofore been made to avoid the undesirable effects of deflection or eliminate the deflection such as by constructing the rolls with a crowned shape, as referred to above, or by externally supporting mid-portions of the roll.

A feature of the present invention is to provide a roll and a support therefor wherein the deflection of the roll can be controlled to eliminate deflection or to obtain a controlled amount of desirable deflection.

The mechanism contemplates providing either a single roll, or a pair of rolls in nip defining relationship. Where a pair of rolls are used, the mechanism includes a first roll having support bearings at its ends and a second tubular shaped roll with a plurality of support members engaging the inner surface opposite the pressure nip between the rolls. A first fluid pressure means is provided for supporting the bearings and a second fluid pressure means is provided for supporting the support members. A selectively controlled pressure source is connected to the pressure means through a ratio control so that a constant ratio is maintained between the pressure applied to thc 3,119,324 Patented Jan. 28, 1964 ICC bearings and to the support members. The support members in a preferred form for a single roll or for the second roll of a pair of rolls are pivotally carried arcuately shaped shoes which form a film of fluid between the shoe surfaces and the inner surface of the second roll from fluid carried within the roll.

Accordingly, an object of the present invention is to provide an improved ioll assembly of the above nature in which the deflection of a single roll is controlled or in which deflection of opposed rolls is controlled in an improved manner to obtain a desirable pressure along the pressure nip.

A further object of the invention is to provide an improved roll assembly wherein the roll pressures may be selectively changed to obtain desirable variations in pressure conditions along the pressure nip or to obtain uniform pressure along the nip.

A further object of the invention is `to provide a support for a pressure roll which does not have to engage the outer surface of the roll and which supports the inner surface of a tubular roll with `a minimum frictional drag and is capable of a long wearing life.

A still further object of the invention is to provide an improved pressure roll assembly of simplified construction well suited to use in the paper industry.

Other objects and advantages of the invention will become more apparent with the teaching of the principles thereof in connection with the disclosure of the preferred embodiments in the specification, claims and drawings, in which:

FIGURE l is a schematic elevational view, with portions in section, of pressure rolls embodying the principles of the present invention;

FIGURE 2 is a vertical sectional view taken substantially along line II-II of `FIGURE l; and

FIGURE 3 is a fragmentary sectional view of a portion of the lower pressure roll illustrating `a modified form of the invention.

As shown on the drawings:

FIGURES 1 and 2 show a first upper roll l0 forming a pressure nip with a second lower roll 11. The lower roll is tubular in construction. The first roll 10 has a first fluid pressure means or support members 12 at the ends supporting it and holding it in pressure engagement with the second roll 11. A second fluid pressure operated means or support members 13 within the tubular second roll urges the roll upwardly providing a support at the inner surface of the tubular roll holding it in pressure engagement with the first roll. A fluid pressure source 14 shown in the form of a pump supplies fluid such as air under pressure to operate the pressure means 12 and 13 and a fluid pressure ratio control box 15 is positioned between the pump 14 and the first and second pressure means 12 and 13 maintaining a predetermined ratio of the pressure of air delivered to the pressure means 12 and 13.

In greater detail, the upper roll 10 has ya supporting shaft 16 carried on bearings 17 and 18 at the ends of the roll. Fluid pressure members 19 and 20 shown in the form of fixedly supported chambers with flexible diaphragrns apply a downward force to the bearings and the diaphragrns are connected to the bearings by rods 21 and 22. The various elements described are illustrated schematically and as will be appreciated by those skilled in the art may take various other forms. The pressure members 19 and 20 for example may take the form of pistons slidably mounted in xed cylinders. The rods 21 and 22 are connected to the ends ot lever arms such as illustrated at 23 in FIGURE 2, with the other end of the lever arms mounted on a fixed pivot Z4 and secured at a midpoint to the bearings 17 and 18. Accordingly, the downward force applied to the upper roll will be dependent on the air pressure delivered to the pressure members 19 and 20 and air is delivered through a line 25 connected to `the ratio box 15.

As will be understood by those skilled in the art, the ratio box is a uid pressure control mechanism or valve assembly which controls the outlet pressure in output lines maintaining the pressures at a predetermined ratio with the pressures varying as the input pressure but main taining said ratio. These valves are commercially available and need not be described in detail.

The pressure to the ratio box may be selectively varied such as by a pressure control valve 41 connected to the supply for the ratio box. This may of course be incorporated into the valve of the ratio box.

The second or lower tubular roll 11 is carried on a beam member 26 conveniently in the form of a hollow tube. The beam member 26 is mounted at its ends on fixed end supports 27 and 28. The support for the deliection control pressure applied to the lower roll 11 and for the weight of the roll assembly is provided by the fixed supports 27 and 28.

The lower roll 11 is rotatably positioned by being rotatably mounted on the beam 26 on bearings 29 and 30 at its ends. The load carried by the bearings 29 and 30 will vary dependent upon the upwardly acting forces applied to the inside of the roll 11 by the support members 13 and the primary support for the roll 11 and the force at the nip N is provided by the support members 13.

The support members 13 are positioned at axially spaced locations within the lower roll 11 and engage the inner surface of the lower roll at positions opposite the pressure nip N between the rolls 10 and 11.

Each support member 13 includes a shoe 31 having an arcuate outer face 31a facing the inner surface 11u, FIG- URE 2, of the roll 11. Each shoe is pivotally mounted at 32 on a piston rod 33 supported in a bearing sleeve 37 in the tube shaped beam 26.

The shoes 31 `slide along on the inner surface 11a of the roll 11 and a'supporting film or cushion of lubricant is formed between the outer surface 31a of the shoe and the inner surface 11a of the roll 11 from lubricant within the roll. Lubricant may be conveniently supplied to the interior of the roll through a supply tube 38, FIGURE 2. The lubricant may be a suitable fluid such as oil which maintains the frictional drag between the shoes 31 and the roll 11 at a very low amount and also functions to dissipate heat.

These shoes 31 are urged upwardly to provide a backing support for the lower roll 11 by pistons 34, FIGURE l, connected to the lower ends of the piston rods 33 and slidably mounted in supported cylinders 35, mounted on supports 39 within the tubular beam 26. Air pressure is delivered to a lower end of the cylinders 35 through ports 36 connected to lines 40 to the ratio box 15.

FIGURE 3 illustrates another form somewhat dif ferent in construction than the foregoing preferred form, wherein a lower roll 11' is supported on a plurality of rollers 44 carried on pivotal arms 42 mounted on fixed pivots 43 within the roll 11'. Each of the rollers 44 is forced upwardly on a piston rod 37' connected to a piston within a cylinder similar to the construction shown in FIGURES l and 2.

In the aforedescribed arrangements the forces on each of the shoes 31 or rollers 44 are preferably equal inasmuch as this provides the most practical and versatile structure. It is contemplated however that the forces applied by different shoes can be diiierent such as, for example, having the shoes at the center of the roll apply a larger force. This could be accomplished by pressure regulators in the lines 4t) and delivering a higher pressure to certain of the cylinders. lt also could be accomplished by providing the pistons 34 and cylinders 35 for diiierent shoes of different sizes, or it could be accomplished by decreasing or increasing the spacing between certain support members.

The support members 13 may be employed to achieve various nip loading ei'Iects such as uniform loading across the nip or unequal loading. The effect of unequal loading across the nip is useful in paper making machinery wherein a paper web passing between the rolls may tend to crush at the outer edges and may have a less tendency to crush at the center of the nip. For this operation a nip load is used wherein a greater load is applied at the center of the rolls than at the edges and this is accomplished by bowing the lower roll 11 upwardly at the center to obtain a greater force at the center of the nip.

By way of an example of structure wherein a greater loading at the center of the nip can be accomplished, a roll assembly is used wherein the total area of the diaphragms of the fluid pressure means 19 and 20 for the top roll are equal to the total areas of the pistons 34 for the lower roll 1l. A ratio box is used wherein the fluid pressure delivered to the cylinders 3S is double that of the pressure delivered to the pressure members 19 and 20. A pressure of l0() pounds per square inch in the line 25 and a pressure of 200 pounds per square inch in the lower lines 40 will cause the bottom roll to bow up thereby creating a greater pressure at the center of the nip than at the edges. If the pressures in both of the lines 25 and 40 are dropped, which can be accomplished by reducing the output pressures of the ratio box such as by reducing the delivery pressure through the control valve shown schematically at 41, the bowing of the lower roll 11 will decrease thus decreasing the difference between the pressure at the center of the nip and the edges. At some lesser fluid pressure the pressure along the nip N will become uniform. Further reduction in pressure will result in a greater pressure at the edges of the rolls. However. the structure for a particular use will normally be designed for the nip pressure relationship that is to be used during normal running operation and the pressure in the nip is also dependent on factors as the weight of the roll and their strength or resistance to deection. Thus it will be seen that various effects can be accomplished both by design and by pressure control.

It is also contemplated that the lower tubular roll `11 be used without an upper roll such as for applying a rolling pressure to a surface or for carrying a travelling belt or wire.

As to the ratio box referred to above, various commercial structures for automatically providing an output pressure as a function of a variable input pressure may be employed as will be fully recognized by those versed in the art. For example, a device available commercially known as a Kendall biasing regulator could be used with a separate regulator for each of the cylinders to obtain the fluid pressure desired for each cylinder with a change in supply pressure.

In paper making machinery, the lower roll may be used to carry a travelling wire as in the Fourdrinier section of the machine. The roll may also be used as a drive roll for the Wire. The upper roll 10 is of course omitted and a drive mechanism is attached to the lower roll 1l. In carrying a Fourdrinier wire deflection of the roll due to the weight of the wire and due to driving forces on the roll will cause deflection of the roll to tend to cause the oit-running portion of the forming wire to be compacted or squeezed laterally which substantially increases `the wear on the wire. This deflection of the roll and the ultimate undesirable effects on the wire can be avoided by the roll of the instant invention wherein the support members 13 are placed at an appropriate location and apply a support force to prevent deflection.

By this it will be seen that l have provided an improved roll assembly which meets the objectives and advantages above set forth. The mechanism is susceptible of uses in many fields and provides a reliable structure capable of long operating life and wherein controlled deflection of the roll is accomplished without undesirable effects and without excessive frictional drag.

The drawings and specification present a detailed disclosure of the preferred embodiments of the invention, and it is to be understood that the invention is not limited to the specific forms disclosed, but covers all modifications, changes and alternative constructions and methods falling within the scope of the principles taught by the invention.

I claim as my invention:

l. In a roll assembly subject to deflection, an elongated tubular cylindrical roll shell adapted to receive lubricating fluid on the inner surface thereof, a rigid support within said roll shell, bearing means at each end of the roll shell positioning the ends of said roll shell relative to the support, a shoe inside of said roll shell having an arcuate stationary convex surface supportingly engaging only a portion of the inner circumference of the roll shell, said stationary convex surface being formed to build up a supporting film of fluid during relative rotation of the roll shell from the fluid within the roll shell, and means positioned between the shoe and support for applying a predetermined radial force to said shoe thereby urging said shoe radially outwardly against the inside of the roll shell for controlling deflection of the roll shell.

2. In a roll assembly subject to deflection, an elongated tubular cylindrical roll shell adapted to receive lubricating fluid on the inner surface thereof, a rigid support within said roll shell, bearing means at each end of the roll shell positioning the ends of said roll shell relative to the support, a plurality of shoes axially spaced inside of said roll shell each having an arcuate stationary convex surface supportingly engaging only a portion of the inner circumference of the roll shell, said stationary convex surface being formed to build up a supporting film of fluid during relative rotation of the roll shell from the fluid within the roll shell, and means positioned between each of the shoes and the support for applying predetermined radial forces to said shoes thereby urging said shoes radially outwardly against the inside of the roll shell for controlling deflection of the roll shell.

3. In a roll assembly subject to deflection, an elongated tubular cylindrical roll shell adapted to receive lubricating fluid on the inner surface thereof, a rigid support within said roll shell, bearing means at each end of the roll shell positioning the ends of said roll shell relative to the support, a plurality of shoes axially spaced inside of said roll shell each having an arcuate stationary convex surface supportingly engaging only a portion of the inner circumference of the roll shell, said stationary convex surface being formed to build up a supporting film of fluid during relative rotation of the roll shell from t'ne fluid within the roll shell, means pivotally supporting each of said shoes about an axis parallel to the roll shell axis, and means positioned between each of said pivotal supporting means for the shoes and said support for applying predetermined radial forces to said shoes thereby urging said shoes radially outwardly against the inside of the roll shell for controlling deflection of the roll shell.

4. In a roll assembly subject to deflection, an elongated tubular cylindrical roll shell adapted to receive lubricating fluid on the inner surface thereof, a rigid support within said roll shell, bearing means at each end of the roll shell positioning the ends of said roll shell relative to the support, a shoe inside of said roll shell having an arcuate stationary convex surface supportingly engaging only a portion of the inner circumference of the roll shell, said stationary convex surface being formed to build up a supporting fllm of fluid during relative rotation of the roll shell from the fluid within the roll shell, and a fluid motor positioned between the shoe and support for applying a predetermined radial force to said shoe thereby urging said shoe radially outwardly against the inside of the roll shell for controlling the deflection of the roll shell.

5. In a roll assembly subject to deflection, an elongated tubular cylindrical roll shell adapted to receive lubricating fluid on the inner surface thereof, a rigid support Within said roll shell, bearing means at each end of the roll shell positioning the ends of said roll shell relative to the support, a plurality of shoes axially spaced inside of said roll shell each having an arcuate stationary convex surface supportingly engaging only a portion of the inner circumference of the roll shell, said stationary convex surface being formed to build up a supporting film of fluid during relative rotation of the roll shell from the fluid within the roll shell, a force applying means positioned between each of the shoes and the support, and means for individually operating each of the force applying means so that independent forces may be applied to each of the shoes urging the shoes radially outwardly against the inside of the roll shell for controlling deflection of the roll shell.

6. A pressure rolling mechanism comprising a first rotatable roll, a second rotatable roll shell, a first variable pressure means providing a support for the first roll holding it in pressure engagement with said second roll shell forming a pressure nip therebetween, a plurality of support elements in engagement with the inner surface of said second roll shell opposite the pressure nip, second pressure means having individual members connected to said support elements providing a support for the second roll shell and controlling deflection thereof for obtaining a predetermined nip load, said members being individually controllable for applying pressures to obtain a predetermined nip load characteristic along the nip, nip loading means connected to said first and said second pressure means for changing the nip load, and ratio control means connected to said nip loading means and to said fluid pressure members controlling said individual memhers to retain said predetermined characteristic with change in nip load.

7. A pressure rolling mechanism in accordance with claim 6 wherein said ratio control means provides a uniform nip pressure along the length of the nip at different operating nip loads.

8. A pressure rolling mechanism comprising a rst rotatable roll, a tubular second rotatable roll shell, a first Variable fluid pressure means providing a support for the first roll holding it in pressure engagement with said second roll shell forming a pressure nip therebetween, a plurality of support elements in engagement with the inner surface of the second roll shell opposite the pressure nip, second variable fluid pressure means having individual members connected to said support elements providing a support for the second roll shell and controlling deflection thereof, said members being individually controllable for applying pressures to obtain a predetermined nip load characteristic along the nip, a fluid pressure supply means connected to said first and second pressure means for changing the pressure of the supply fluid and changing the nip load, and ratio control means connected to said fluid pressure members controlling said individual members to retain said predetermined characteristic with change in nip load.

9. A pressure rolling mechanism comprising a first rotatable roll, a tubular second rotatable roll shell, a support for the first roll holding it in pressure engagement with said second roll forming a pressure nip therebetween, a plurality of support elements in engagement with the inner surface of the second roll shell opposite the pressure nip, variable fluid pressure means having individual members connected to said support elements providing a support for the second roll shell and controlling deflection thereof and nip pressure, said members being individu ally controllable for applying pressures to obtain n uniform nip load characteristic along the nip, nip loading means connected to said variable pressure means forchanging the total nip load, and ratio control means connected to said nip loading means and said uid pressure members controlling said individual members to retain said uniform characteristic along the nip with change of said nip loading means.

References Cited in the file of this patent UNITED STATES PATENTS Schurmnnn May 24, Stacom Jan. 21, Specht Mar. 15, Hornbostel Aug. 11, Appcnzelier Oct. 20, Keyser Aug. 30, Kuster Mar. 6,

Claims (1)

1. IN A ROLL ASSEMBLY SUBJECT TO DEFLECTION, AN ELONGATED TUBULAR CYLINDRICAL ROLL SHELL ADAPTED TO RECEIVE LUBRICATING FLUID ON THE INNER SURFACE THEREOF, A RIGID SUPPORT WITHIN SAID ROLL SHELL, BEARING MEANS AT EACH END OF THE ROLL SHELL POSITIONING THE ENDS OF SAID ROLL SHELL RELATIVE TO THE SUPPORT, A SHOE INSIDE OF SAID ROLL SHELL HAVING AN ARCUATE STATIONARY CONVEX SURFACE SUPPORTINGLY ENGAGING ONLY A PORTION OF THE INNER CIRCUMFERENCE OF THE ROLL SHELL, SAID STATIONARY CONVEX SURFACE BEING FORMED TO BUILD UP A SUPPORTING FILM OF FLUID DURING RELATIVE ROTATION OF THE ROLL SHELL FROM THE FLUID WITHIN THE ROLL SHELL, AND MEANS POSITIONED BETWEEN THE SHOE AND SUPPORT FOR APPLYING A PREDETERMINED RADIAL FORCE TO SAID SHOE THEREBY URGING SAID SHOE RADIALLY OUTWARDLY AGAINST THE INSIDE OF THE ROLL SHELL FOR CONTROLLING DEFLECTION OF THE ROLL SHELL.
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DE3024575A1 (en) * 1980-06-28 1982-01-28 Voith Gmbh J M Paper making pressure roller - has swivel bearings at ends to allow bend adjustment
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US4357743A (en) * 1980-02-05 1982-11-09 Escher Wyss Limited Controlled deflection roll
EP0087729A1 (en) * 1982-03-03 1983-09-07 Componenti Grafici S.r.l. Impression cylinder with a variable shape axle
US4414890A (en) * 1980-06-28 1983-11-15 J. M. Voith Gmbh Press roll with adjustable flexion
DE3407485A1 (en) * 1983-12-22 1985-07-04 Escher Wyss Ag Rolling device
DE3533210A1 (en) * 1985-09-18 1987-03-26 Kuesters Eduard Method for controlling the linear-pressure distribution in roller arrangements and corresponding control device
US4850088A (en) * 1987-08-08 1989-07-25 Beloit Corporation Self-loading controlled deflection roll
DE3900294A1 (en) * 1989-01-07 1990-07-12 Kuesters Eduard Maschf Print calendar
AT399175B (en) * 1989-10-30 1995-03-27 Escher Wyss Gmbh Calendar for surface processing of materials
US5507916A (en) * 1993-06-11 1996-04-16 J.M. Voith Gmbh Method of treating the edges of a fiber web
DE29503126U1 (en) * 1995-02-24 1996-06-20 Kuesters Eduard Maschf Roller
EP0741253A2 (en) * 1995-05-05 1996-11-06 De Pretto-Escher Wyss s.r.l. Press roll and machine with a press roll
DE19521860A1 (en) * 1995-06-16 1996-12-19 Kuesters Eduard Maschf Deflection-controllable roller
DE19521859A1 (en) * 1995-06-16 1996-12-19 Kuesters Eduard Maschf Deflection-controllable roller
EP0854227A2 (en) * 1996-12-23 1998-07-22 Voith Sulzer Papiermaschinen GmbH Roll for a machine for the manufacturing of a fibrous web
US5813959A (en) * 1993-09-27 1998-09-29 Eduard Kusters Maschinenfabrik Gmbh & Co. Kg Roller
EP1043119A2 (en) * 1999-04-03 2000-10-11 Küsters Beloit GmbH & Co. KG Method and apparatus for external grinding of thin-walled tube
US6299571B1 (en) 1999-10-22 2001-10-09 Morrison Berkshire, Inc. System and method for controlling deflection of a dynamic surface
US6309333B2 (en) 1999-10-22 2001-10-30 Morrison Berkshire, Inc. System and method for controlling vibration of a dynamic surface
US6860030B1 (en) * 2000-11-15 2005-03-01 Voith Paper, Inc. Control system for gap measuring
US20060005391A1 (en) * 2004-07-12 2006-01-12 Eastman Kodak Company Axially compliant pressure roller utilizing non-newtonian fluid

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US3703862A (en) * 1963-06-25 1972-11-28 Edward Kusters Mas Fab Work pressure rolling assembly
US3250211A (en) * 1963-12-17 1966-05-10 Artama Arvi Apparatus for making laminated glass panes
US3276102A (en) * 1964-01-24 1966-10-04 Beloit Corp Adjustable crown roll
US3411333A (en) * 1965-11-22 1968-11-19 Frankel Sydney Rolling mill device
US3362055A (en) * 1965-12-06 1968-01-09 Dominion Eng Works Ltd Hydraulic anti-deflection roll
US3418703A (en) * 1966-05-31 1968-12-31 Leon F. Thiry Antideflection roll with non-rotating beam and lever supports
US3416435A (en) * 1966-06-13 1968-12-17 Beloit Corp Roller press
US3430319A (en) * 1966-08-15 1969-03-04 Beloit Corp Nondeflection support for web carrying roll
US3516135A (en) * 1968-04-16 1970-06-23 Mount Hope Machinery Ltd Roll with vibration damping means
US3512475A (en) * 1968-09-21 1970-05-19 Beloit Corp Self-damped calender roll
US3619359A (en) * 1969-03-10 1971-11-09 Beloit Corp Gross machine moisture control system for the net end of a paper machine
US3638292A (en) * 1969-10-29 1972-02-01 Vlaanderen Machine Co Van Roll for applying uniform pressure
US3679115A (en) * 1970-12-04 1972-07-25 Fmc Corp Uniform pressure draw rolls
US3747181A (en) * 1971-01-19 1973-07-24 Tampella Oy Ab Press roll
US3736869A (en) * 1971-03-16 1973-06-05 Motter J Printing Press Co Pressure roller device for a rotogravure printing press
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US3802044A (en) * 1971-06-28 1974-04-09 Escher Wyss Ltd Controlled deflection roll
US3921514A (en) * 1973-02-08 1975-11-25 Escher Wyss Ltd Rolling mill
US3879827A (en) * 1973-06-15 1975-04-29 Escher Wyss Ltd Roll for a rolling mill
US3932921A (en) * 1974-02-12 1976-01-20 Escher-Wyss Limited Controlled deflection roll
DE2510410A1 (en) * 1975-03-04 1976-09-16 Escher Wyss A Zuerich Schweiz Control apparatus for a controlled deflection roll
US4023480A (en) * 1975-03-04 1977-05-17 Escher Wyss Limited Apparatus for controlling a deflection compensating press roll of a rolling mill
US4058877A (en) * 1975-04-15 1977-11-22 Escher Wyss Limited Deflection-controlled roll for the pressure treatment of materials in web form
US4069569A (en) * 1975-05-15 1978-01-24 Continental Gummi-Werke A. G. Deflection-controlled roll for the pressure treatment of materials in web form
US4030177A (en) * 1975-06-04 1977-06-21 Usm Corporation Controlled deflection roll
US4047273A (en) * 1975-11-05 1977-09-13 Escher Wyss Limited Deflection compensating roll
US4074624A (en) * 1975-12-08 1978-02-21 Escher Wyss Limited Method of adjusting the contact pressure of a rolling mill and apparatus for the performance thereof
US4007522A (en) * 1976-05-26 1977-02-15 Usm Corporation Controlled deflection roll assembly
US4154160A (en) * 1976-05-26 1979-05-15 Edward Kusters Pressure control device for a processing machine with rolls
US4089094A (en) * 1976-06-11 1978-05-16 Valmet Oy Press roll with controllable deflection
FR2368631A1 (en) * 1976-10-19 1978-05-19 Escher Wyss Sa deflection compensating device
US4090282A (en) * 1976-10-19 1978-05-23 Escher Wyss Limited Deflection control device
US4188874A (en) * 1976-12-16 1980-02-19 Escher Wyss Limited Press with two pressure rollers
DE2905542A1 (en) * 1979-02-14 1980-08-28 Kuesters Eduard Roller for the pressure treatment of tracks
DE3003395A1 (en) * 1980-01-31 1981-09-03 Kuesters Eduard Method for controlling the line pressure distribution of a roller and corresponding roller
US4357743A (en) * 1980-02-05 1982-11-09 Escher Wyss Limited Controlled deflection roll
DE3020669A1 (en) * 1980-05-30 1981-12-10 Kuesters Eduard Method for controlling the line pressure distribution in a rolling device and corresponding rolling device
US4414890A (en) * 1980-06-28 1983-11-15 J. M. Voith Gmbh Press roll with adjustable flexion
DE3024575A1 (en) * 1980-06-28 1982-01-28 Voith Gmbh J M Paper making pressure roller - has swivel bearings at ends to allow bend adjustment
USRE32586E (en) * 1980-06-28 1988-02-02 J. M. Voith Gmbh Press roll with adjustable flexion
FR2501542A1 (en) * 1981-03-13 1982-09-17 Escher Wyss Sa Device for regulating a quarto laminator for rolling metals
EP0087729A1 (en) * 1982-03-03 1983-09-07 Componenti Grafici S.r.l. Impression cylinder with a variable shape axle
DE3407485A1 (en) * 1983-12-22 1985-07-04 Escher Wyss Ag Rolling device
EP0149108A2 (en) * 1983-12-22 1985-07-24 Sulzer-Escher Wyss AG Roller assembly
EP0149108A3 (en) * 1983-12-22 1985-10-09 Sulzer-Escher Wyss Ag Roller assembly
DE3533210A1 (en) * 1985-09-18 1987-03-26 Kuesters Eduard Method for controlling the linear-pressure distribution in roller arrangements and corresponding control device
US4850088A (en) * 1987-08-08 1989-07-25 Beloit Corporation Self-loading controlled deflection roll
DE3900294A1 (en) * 1989-01-07 1990-07-12 Kuesters Eduard Maschf Print calendar
AT399175B (en) * 1989-10-30 1995-03-27 Escher Wyss Gmbh Calendar for surface processing of materials
US5507916A (en) * 1993-06-11 1996-04-16 J.M. Voith Gmbh Method of treating the edges of a fiber web
US5813959A (en) * 1993-09-27 1998-09-29 Eduard Kusters Maschinenfabrik Gmbh & Co. Kg Roller
DE29503126U1 (en) * 1995-02-24 1996-06-20 Kuesters Eduard Maschf Roller
EP0741253A2 (en) * 1995-05-05 1996-11-06 De Pretto-Escher Wyss s.r.l. Press roll and machine with a press roll
EP0741253A3 (en) * 1995-05-05 1997-06-25 Pretto De Escher Wyss Srl Press roll and machine with a press roll
DE19521860C3 (en) * 1995-06-16 2002-02-28 Kuesters Eduard Maschf Deflection-controllable roller
DE19521860A1 (en) * 1995-06-16 1996-12-19 Kuesters Eduard Maschf Deflection-controllable roller
DE19521859A1 (en) * 1995-06-16 1996-12-19 Kuesters Eduard Maschf Deflection-controllable roller
US5904642A (en) * 1995-06-16 1999-05-18 Eduard Kusters Maschinenfabrik Gmbh & Co. Kg. Roller with controllable sag
DE19521859C2 (en) * 1995-06-16 1999-06-24 Kuesters Eduard Maschf Deflection-controllable roller
US5919121A (en) * 1995-06-16 1999-07-06 Eduard Kusters Maschinenfabrik Gmbh & Co. Kg Roller with controllable deflection
EP0854227A3 (en) * 1996-12-23 1999-06-02 Voith Sulzer Papiermaschinen GmbH Roll for a machine for the manufacturing of a fibrous web
EP0854227A2 (en) * 1996-12-23 1998-07-22 Voith Sulzer Papiermaschinen GmbH Roll for a machine for the manufacturing of a fibrous web
EP1043119A3 (en) * 1999-04-03 2003-10-01 Küsters Beloit GmbH & Co. KG Method and apparatus for external grinding of thin-walled tube
EP1043119A2 (en) * 1999-04-03 2000-10-11 Küsters Beloit GmbH & Co. KG Method and apparatus for external grinding of thin-walled tube
US6309333B2 (en) 1999-10-22 2001-10-30 Morrison Berkshire, Inc. System and method for controlling vibration of a dynamic surface
US6361483B1 (en) 1999-10-22 2002-03-26 Morrison Berkshire, Inc. System for controlling vibration of a dynamic surface
US6299571B1 (en) 1999-10-22 2001-10-09 Morrison Berkshire, Inc. System and method for controlling deflection of a dynamic surface
US6860030B1 (en) * 2000-11-15 2005-03-01 Voith Paper, Inc. Control system for gap measuring
US7465264B2 (en) 2004-07-12 2008-12-16 Rohm And Haas Denmark Finance A/S Axially compliant pressure roller utilizing non-newtonian fluid
US20060005391A1 (en) * 2004-07-12 2006-01-12 Eastman Kodak Company Axially compliant pressure roller utilizing non-newtonian fluid
WO2006017010A1 (en) * 2004-07-12 2006-02-16 Eastman Kodak Company Compliant pressure roller with shell supported on titabl hydrodynamic bearing shoes lubricated by a non-newtonian fluid

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