WO2006017010A1

WO2006017010A1 - Compliant pressure roller with shell supported on titabl hydrodynamic bearing shoes lubricated by a non-newtonian fluid

Info

Publication number: WO2006017010A1
Application number: PCT/US2005/022927
Authority: WO
Inventors: Richard Bomba
Original assignee: Eastman Kodak Company
Priority date: 2004-07-12
Filing date: 2005-06-27
Publication date: 2006-02-16
Also published as: US20060005391A1; US7465264B2; TW200611819A; CN1985098A; CN100497972C; JP2008506085A

Abstract

A compliant pressure roller (10) for creating uniform pressure at a nip comprises a stationary inner core (12). A plurality of shoes (14) is pivotall' mounted to the stationary inner core. Dividers (16) create a plurality of annular chambers (18) wherein each of the shoes occupies one of the chambers. non-Newtonian fluid (70) fills each of the chambers. A plurality of actuators(66) is connected to at least one of the shoes. A thin, rotatable shell (24) surrounds the plurality of chambers, shoes, and stationary inner core.

Description

COMPLIANT PRESSURE ROLLER WITH SHELL SUPPORTED ON TILTABL HYDRODYNAMIC BEARING SHOES LUBRICATED BY A NON-NEWTONIAN FLUID

FIELD OF THE INVENTION

The present invention relates in general to pressure rollers, and in 5 particular, to a compliant pressure roller which adjusts to deformation in a thin outer shell.

BACKGROUND OF THE INVENTION

In preparing certain substrates it is important that at least one surface have a smooth finish. Often this smooth finish requires very high 10 tolerances. Prior art solutions to the problem of creating a smooth finish have not been completely satisfactory. One prior art solution has been to use elastomeric rollers. Elastomeric rollers, however, cannot be ground to the same high tolerance as metallic rollers.

Another prior art solution has used carrier webs having a smooth 15 surface finish as a backing material for the substrate as it passes through the nip.

A problem with this solution is that the carrier web usually must be discarded or recycled adding to the cost of the manufacturing process. Another problem is that the carrier web often wrinkles.

Using a roller having a metal sleeve with a smooth surface finish 20 over an elastomeric backing is a possibility. This solution, however, also has drawbacks. The thin metal sleeve is subject to cracking after repeated use, especially along the margins.

One prior art solution is discussed in U.S. Patent No. 5,146,664

(Biondetti). The solution proposed is a series of hydraulic pistons. These 25 hydraulic pistons, however, operate on a thick outer shell to correct for beam deflections in the roller. An apparatus as disclosed would be expensive and not suitable for all applications.

For a patterned roller, a rapid pressure rise at a nip is important to force material into the pattern. Metallic shells of small diameter inherently will 30 create a small nip footprint, for a given nip load, which results in a higher pressure. In the formation of extrusion cast web materials the nip action improves the replication of the polished or patterned roller surfaces. In an ideal situation, rollers would be perfectly cylindrical and the molten resin would be uniformly distributed. In practice, neither condition is achieved. An ability to locally adjust roller shape is desirable to improve cross width nip loading. Consequently the web material will have more consistent thickness and surface uniformity. Self adjusting rollers are utilized in paper manufacturing or web calendaring operations which require high nip loads, but they have minimal heat transfer capabilities.

It is desirable to have a roller capable of creating a smooth finish, with a small nip footprint, having an improved heat transfer capability, and capable of adjustment.

SUMMARY OF THE INVENTION Briefly, according to one aspect of the present invention a compliant pressure roller for creating uniform pressure at a nip comprises a stationary inner core. A plurality of shoes is pivotally mounted to the stationary inner core. Dividers create a plurality of annular chambers wherein each of the shoes occupies one of the chambers. A non-Newtonian fluid fills each of the chambers. A plurality of actuators is connected to at least one of the shoes. A thin, rotatable shell surrounds the plurality of chambers, shoes, and stationary inner core. A compliant pressure roller for creating uniform pressure at a nip comprises a stationary inner core. A plurality of shoes is pivotally mounted to the stationary inner core. Dividers create a plurality of annular chambers wherein the shoes occupy one of the chambers and a non-Newtonian fluid fills each of the chambers. A plurality of gap adjusting devices changes a relationship of each shoe with respect to the inner surface of the outer shell to change the shape of the converging region (gap) in each of the chambers. A thin, rotatable shell surrounds the plurality of chambers, shoes, and stationary inner core.

Localized pressure variations are created through adjustment of the gap between the outer shell and the curved surface of the shoe. The average shear rate in this gap is proportional to the surface velocity of the shell divided by the gap height. External manipulation of the gap combined with a fluid of desirable shear sensitive properties provides a means of creating localized pressure differences within each chamber which in turn provides a means of locally deforming the thin outer shell. Non-Newtonian fluids exhibit a logarithmic relationship between viscosity and shear rate for a given rotational speed of the outer shell. A given gap and an apparent viscosity within this region create a pressure profile in this converging region. Reducing the gap will increase shear rate causing reducing fluid viscosity and reducing hydrodynamic force. A limited number of shear thickening non-Newtonian fluids are available and can be utilized as well but with this type fluid increased shear rate from gap reduction would result in increased viscosity and increased local pressure. The invention and its objects and advantages will become more apparent in the detailed description of the preferred embodiment presented below.

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is an isometric representation of an axially compliant pressure roller according to the present invention with a partial cross section taken through the outer shell to expose internal components.

Figure 2 A is a cross section of the axially compliant pressure roller shown in Figure 1 taken at the center of one of the internal flow chambers.

Figure 2B is an enlarged view of the interface of the shoe and the outer shell as noted in Figure 2A. Figure 3 is a graph of radial deformation (UX) of the outer shell normal to the nip point for various internal pressure conditions.

Figure 4 is a cross section of a nip formed between two rollers. Figure 5 is a cross section of the axially compliant pressure roller with a bi-metallic gap adjusting mechanism. Figure 6A is a cross section of a the axially compliant pressure roller with a motor driven gap adjusting mechanism.

Figure 6B is an enlarged view of the interface of the shoe and outer shell with non-Newtonian fluid region.

DETAILED DESCRIPTION OF THE INVENTION The present invention will be directed in particular to elements forming part of, or in cooperation more directly with the apparatus in accordance with the present invention. It is to be understood that elements not specifically shown or described may take various forms well known to those skilled in the art. Referring now to Figure 1 a compliant pressure roller is referred to in general by numeral 10. Compliant pressure roller 10 is comprised in general of a stationary inner core 12 and a plurality of shoes 14 which are pivotally mounted to the stationary inner core 12. A series of non-magnetic dividers 16 create a plurality of annular chambers 18 and each of the shoes 14 occupies one of the annular chambers 18.

Referring to Figures I₅ 2A₅ and 2B, shoe 14, which is eccentrically mounted, is shown. One surface of shoe 14 is curved. A pivot point 15 and spring loading assembly 17 are attached to shoe 14. A non-magnetic, metallic material is used in the construction of the shoe 14, but the present invention is not limited to this embodiment. The curvature of the face of the shoe 14 is slightly smaller than the curvature of the inner surface of the thin walled outer shell 24. This creates a converging cross section at the interface between these components. The compliant pressure roller 10 comprises of a non-rotating inner core 12, which is the main support structure for the compliant pressure roller 10. A non-magnetic, metallic material is used in the construction of the inner core, but the present invention is not limited to this embodiment. The inner core 12 has a cylindrical form in which axial holes 19 have been provided. At least one of these holes is used to house the magnetic field generator 13. In the preferred embodiment one magnetic field generator 13 is associated with each of the plurality of shoes 14. This allows for local adjustments to the thin walled outer shell 24. hi an alternate embodiment a magnetic field generator 13 maybe located in each of the plurality of shoes 14 as shown in Figure 2B.

Axial holes 19 are used for the circulation of heat transfer media within the core. A series of pockets 26 are created in a radial direction to serve as supports for the shoes 14. Seats on the inner core 12 enable mounting of bearings 20 and fluid seals 22. In operation, the hydrodynamic effect of a viscous fluid subject to the shear stress created by the relative velocity of the thin walled shell with respect to the shoe, develops a pressure profile within the converging section 11. This pressure acts on the thin walled shell curved surface 25 and the curved surface 27 of the shoe. The pressure acting on the shoe results in a force normal to the curvature at the center of pressure. This force is resisted by the spring preloading force acting on the shoe 14. The pressure acting on the rotating thin walled outer shell 24 creates an internal force on the shell. The net difference in force acting on the shell from the internal hydrodynamic action and the external nip force will result in a localized deformation of the thin walled shell in this region.

A thin walled shell of small shell diameter is possible with this embodiment because the structural design of the shell is not dictated by beam bending criteria or shell crushing criteria. The wall thickness of the shell can be significantly thinner because the surface of the shell subjected to the external nip force is directly supported internally by the pressure created by the interaction of the magneto-rheological fluid 28 and the shoe 14. The thin walled outer shell 24 is constrained with bearings 20 to rotate about the inner core 12. The rotation of the shell can be imparted by the friction force at the nip point 42, shown in Figure 4, or with an external drive mechanism. Along the curved surface 25 of the thin walled shell, for a given convergent interface, relative velocity, and fluid viscosity create a uniform pressure. The annular chambers 18 in conjunction with the shoes 14, magneto- rheological fluid 28, and axially variable magnetic field generator 13 can be subjected to variable hydrodynamic pressure forces by changing the viscosity of the fluid. The ability to exert axially variable pressure along the thin walled shell results in localized deformation changes of small magnitude and at a much higher frequency than possible by other prior art.

Figure 3 shows the results of finite element calculations used to model the effect of the variable internal pressure capability of this apparatus on the radial profile of the roller surface in the nip point. The dimensions of the shell can be represented in terms of the following quantities; a flexural rigidity of approximately 1800 lb-in and a shell thickness to diameter ratio of 0.025. The flexural rigidity is defined as the quantity of the product of the material elastic modulus and the shell thickness cubed divided by the quantity of the product of a constant value 12 and the quantity of the difference of 1 and Poisson's ratio squared. An average nip pressure of 250 psi, placed on the thin walled outer shell 24 along a localized region parallel to the axis of rotation, has been used in this calculation. The variable (UX) is the radial displacement in the x-direction, which is also normal to the applied nip pressure region.

Curve 30 with circle shaped markers represents the expected shell deformation under nip load but without internal support. Curve 32 with triangular shaped markers represents the effect of applying a localized pressure, on an area equivalent to the curved surface of the shoe 14 acting at the center of the shell with an average pressure of 50 psi. Curve 34 with square shaped markers represents the positive effect on the radial deformation obtained by applying a gradient pressure profile along the inner surface of the shell ranging from 15 psi to 20 psi. Utilizing basic fluid dynamic principles it has been calculated that a pressure of approximately 30 psi can be developed in this region given a fluid of viscosity of approximately 10 Pa-s sheared between the outer shell and the curved surface of the shoe with an average shear rate of 250 1/s.

Figure 4 shows a cross sectional view of a typical two roller nip utilized in the extrusion cast web formation. A compliant pressure roller 10 is loaded radially into the interface of the molten resin 52 and a second roller 40. Utilizing a non-contacting deformation detector 50 such as a laser triangulation gage or an eddy current device, the resulting shell surface deformation can be measured. This measurement data can be utilized to control internal loading conditions along the axis of the roller by sending a deformation signal 54 to microprocessor 56, which alters the strength of one or more of the magnetic field generators 13. hi addition to the magneto-rheological fluid described previously, this apparatus can accommodate other fluids without magneto-rheological properties but which exhibit non-Newtonian characteristics (viscosity of fluid is dependent on shear rate imposed). Localized pressure variations can be created through adjustment of the gap between the outer shell and the curved surface of the shoe. The average shear rate in this gap is proportional to the surface velocity of the shell divided by the gap height. Non-Newtonian fluids exhibit a logarithmic relationship between viscosity and shear rate. External manipulation of the gap combined with a fluid with desirable shear sensitive properties provides an additional means of creating localized pressure differences within each chamber. A bimetallic actuator 58 along with heating element 60 and coarse adjustment screw 62 are shown in Figure 5. This configuration provides a means of adjusting the gap between the shoe 14 and the thin walled outer shell 24. The heating element 60 changes the temperature of the bimetallic actuator 58. The change in temperature results in predictable length change. The coarse adjustment screw 62 is used to initially set the gap and preload the components. The access chamber 64 provides a conduit for wiring and space for manual adjustment. External manipulation of the gap is realized through heater power level or temperature control via a microprocessor controller 56.

Figure 6A shows another possible configuration to adjust the gap between the shoe 14 and the thin walled outer shell 24. The action of the linear actuator 66 as adjusted by the motor 68 through the connection at the shoe 14 changes the position of the shoe and accordingly the gap. The linear actuator 66 can take the form of a screw type mechanism, a cam mechanism or a solenoid with locking provision. Alternate gap adjustment mechanisms are possible and not limited to the methods described.

Figure 6B shows an enlarged view of the shoe 14, thin walled shell 24 and the interface filled with non-Newtonian fluid 70. The position of the shoe 14 with respect to the inner surface of the thin walled outer shell 24 creates a converging region. The non-Newtonian fluid 70 within this region experiences shear resulting from the rotation of the thin walled outer shell 24. Manipulation of the gap changes the shear rate imposed on the fluid. An increase in shear rate (through reduction in gap) will reduce fluid viscosity for a shear thinning non- Newtonian fluid. The region of the outer shell exposed to this action will experience a decrease in hydrodynamic pressure. Depending on the net pressure difference in the nip region, the shell will locally deform. Conversely, an increase in the gap will result in a increase of hydrodynamic pressure. If a shear thickening non-Newtonian fluid is utilized the response to gap changes will be reversed. Specifically, a decrease in gap will increase fluid viscosity and increase hydrodynamic pressure.

PARTS LIST compliant pressure roller converging section inner core magnetic field generator shoe pivot point non-metallic dividers spring loading assembly annular chambers axial holes bearings seals thin walled outer shell curved surface, shell pockets curved surface, shoe magneto-rheological fluid curve curve curve second roller nip deformation detector molten resin signal microprocessor bimetallic actuator heating element coarse gap adjustment screw access chamber linear actuator motor non-Newtonian fluid

Claims

CLAIMS:

1. A compliant pressure roller for creating uniform pressure at a nip comprising: a stationary inner core; a plurality of shoes pivotally mounted to said stationary inner core; dividers creating a plurality of annular chambers wherein each of said shoes occupies one of said chambers; a non-Newtonian fluid filling each of said chambers; a plurality of actuators each of which is connected to at least one of said shoes; and a thin, rotatable shell surrounding said plurality of chambers, shoes, and stationary inner core.

2. A compliant pressure roller as in claim 1 wherein each of said actuators comprises a bimetallic device.

3. A compliant pressure roller as in claim 1 wherein each of said actuators comprises a cam.

4. A compliant pressure roller as in claim 1 wherein each of said actuators comprises an electric motor.

5. A compliant pressure roller as in claim 1 wherein each of said actuators comprises a solenoid.

6. A compliant pressure roller as in claim 1 wherein each of said actuators comprises a stepper motor and lead screw.

7. A compliant pressure roller as in claim 1 wherein each of said actuator is individually adjustable to compensate for deformation in said thin, rotatable shell.

8. A compliant pressure roller as in claim 1 wherein each of said actuators are individually adjustable to compensate for variations in thickness of a web.

9. A compliant pressure roller as in claim 1 wherein a force on said non-Newtonian fluid created by rotation of said thin, rotatable shell compensates for deformation in said shell.

10. A compliant pressure roller as in claim 1 wherein a deformation detector is located in each of said shoes.

11. A compliant pressure roller as in claim 1 wherein an eddy current detector detects deformation in said thin, rotatable shell and provides a deformation signal to a microprocessor which adjusts at least one of said actuators.

12. A compliant pressure roller as in claim 1 wherein a laser detector detects deformation in said thin, rotatable shell and provides a deformation signal to a microprocessor which adjusts at least one of said actuators.

13. A compliant pressure roller as in claim 1 wherein a face of a each of said pluralities of shoes creates a converging zone with an inner surface of said thin, rotatable shell.

14. A compliant pressure roller as in claim 1 wherein a curvature of a face of each of said pluralities of shoes is greater than a curvature of an inner surface of said thin, rotatable shell in order to create a converging zone.

15. A compliant pressure roller as in claim 1 wherein said plurality of shoes are eccentrically mounted.

16. A compliant pressure roller for creating uniform pressure at a nip comprising: a stationary inner core; a plurality of shoes pivotally mounted to said stationary inner core; dividers creating a plurality of annular chambers wherein each of said shoes occupies one of said chambers; a non-Newtonian fluid filling each of said chambers; a plurality of actuators for moving said shoes; a thin, metal, rotatable shell surrounding said plurality of chambers, shoes, and stationary inner core; wherein each of said actuators are individually adjustable to compensate for deformation in said rotatable shell; and wherein a hydrodynamic force on said fluid created by rotation of said shell compensates for deformation in said shell.

17. A compliant pressure roller as in claim 16 wherein each of said actuators moves at least one of said shoes.

18. A compliant pressure roller as in claim 16 wherein said fluid is a heat transfer agent.

19. A compliant pressure roller as in claim 1 wherein said shoes are mounted on said stationary inner core.

20. A compliant pressure roller as in claim 1 wherein a deformation detector detects deformation in said shell and adjusts at least one of said actuators to compensate for said deformation.

21. A compliant pressure roller as in claim 20 wherein an eddy current detector detects deformation in said shell and provides a deformation signal to a microprocessor which adjusts at least one of said actuators.

22. A compliant pressure roller as in claim 20 wherein a laser detector detects deformation in said thin, rotatable shell and provides a deformation signal to a microprocessor which adjusts at least one of said actuators.

23. A method for creating uniform pressure at a nip comprising: providing a stationary inner core; pivotally mounting a plurality of shoes to said stationary inner core; attaching a plurality of actuators wherein each of said shoes is connected to an actuator; creating a plurality of annular chambers wherein each of said shoes occupies one of said chambers; filling each of said chambers with a non-Newtonian fluid; surrounding said plurality of chambers, shoes, actuators, and stationary inner core with a thin, rotatable shell; detecting a deformation in said shell; and changing a displacement of at least one of said actuators to change a position of at least one of said shoes to correct said deformation.

24. A method as in claim 23 wherein a hydrodynamic force on said fluid created by rotation of said shell compensates for deformation in said shell.

25. A method as in claim 23 wherein said fluid has non- Newtonian viscosity characteristics.

26. A method as in claim 23 wherein an eddy current detector detects deformation in said shell.

27. A method as in claim 23 wherein a laser detector detects deformation in said thin, rotatable shell.

28. A compliant pressure roller for creating uniform pressure comprising: a stationary inner core; a plurality of shoes mounted on said stationary inner core; dividers creating a plurality of annular chambers wherein each of said shoes occupies one of said chambers; a non-Newtonian fluid filling each of said chambers; a plurality of actuators for changing a position of each of said shoes; a thin, rotatable shell surrounding said plurality of chambers, shoes, actuators, and stationary inner core; at least one detector for detecting deformation in said thin, rotatable shell; a microprocessor for processing information on shell deformation; and adjusting a position of at least one of said actuators to compensate for shell deformation.