EP0705786A2 - Transportrolle mit profilierter Oberfläche zum Führen von ultradünnen Bahnen und Vorrichtung mit einer solchen Transportrolle - Google Patents

Transportrolle mit profilierter Oberfläche zum Führen von ultradünnen Bahnen und Vorrichtung mit einer solchen Transportrolle Download PDF

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Publication number
EP0705786A2
EP0705786A2 EP95115687A EP95115687A EP0705786A2 EP 0705786 A2 EP0705786 A2 EP 0705786A2 EP 95115687 A EP95115687 A EP 95115687A EP 95115687 A EP95115687 A EP 95115687A EP 0705786 A2 EP0705786 A2 EP 0705786A2
Authority
EP
European Patent Office
Prior art keywords
web
roller
lands
grooves
width
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP95115687A
Other languages
English (en)
French (fr)
Other versions
EP0705786B1 (de
EP0705786A3 (de
Inventor
Arthur Moore c/o Eastman Kodak Company Stewart
Kevin A. c/o Eastman Kodak Company Cole
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Eastman Kodak Co
Original Assignee
Eastman Kodak Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Eastman Kodak Co filed Critical Eastman Kodak Co
Publication of EP0705786A2 publication Critical patent/EP0705786A2/de
Publication of EP0705786A3 publication Critical patent/EP0705786A3/de
Application granted granted Critical
Publication of EP0705786B1 publication Critical patent/EP0705786B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H27/00—Special constructions, e.g. surface features, of feed or guide rollers for webs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/10—Rollers
    • B65H2404/13—Details of longitudinal profile
    • B65H2404/131—Details of longitudinal profile shape
    • B65H2404/1311—Undulations, wavy shape
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/10—Rollers
    • B65H2404/13—Details of longitudinal profile
    • B65H2404/131—Details of longitudinal profile shape
    • B65H2404/1316—Details of longitudinal profile shape stepped or grooved
    • B65H2404/13161—Regularly spaced grooves

Definitions

  • the invention concerns apparatus for conveying web material such as indeterminate lengths of plastic sheet or paper. More particularly, the invention concerns such apparatus which includes rollers having specially contoured surfaces for conveying at high speeds wide webs of ultrathin or very small thickness, such as less than 0.001 inch (0.0254 mm).
  • FIG. 1 illustrates schematically one example of a wide variety of manufacturing apparatus for conveying and treating web materials.
  • a source 10 such as a stock roll, provides a web 12 of indeterminate length.
  • the web is conveyed through a process zone 14 to a take-up roller 16 by means of a plurality of right circular cylindrical driver and idler rollers 18, only one being illustrated, which typically have widths greater than the width of the web.
  • Rolls 10 and 16 also may be driven.
  • Some rollers 18 may be driven by means such as a motor 20.
  • the relative positions of the rollers and other conventional web guidance features in the apparatus, not illustrated, serve as means to guide the web to wrap onto each roller over a wrap angle ⁇ , which may be in the range of 10 to 300°.
  • Various surface treatments may be performed on the web in the process zone, such as coating, printing, surface texturing and the like, which often require that there be no slippage between the web and the driver or idler rollers. Slippage or loss of traction between a web and a roller is undesirable since it may cause problems for the web such as weaving movement, electrostatic charging, scratching, creasing and the like. Sufficient frictional force is required between the web and each roller to prevent such slippage, this force commonly being known as roller traction.
  • Roller traction can be achieved with smooth-surfaced rollers at low web speeds; however, as web speed increases to as much as 100 feet per minute (30.5 meters per minute), air typically becomes entrained between the web and the roller, as indicated by the arrow in Figure 1.
  • the entrained air causes the web at least partially to lose contact with the roller; so that, slippage can occur.
  • surface patterns of various types have been provided on roller surfaces, thus permitting adequate traction to be maintained at low and high web speeds.
  • Figure 2 illustrates schematically an axial cross section of one such surface pattern and an engaged web, just at the beginning of wrap angle ⁇ .
  • the exterior surface of roller 18 is provided with a plurality of circumferentially extended grooves 24, which may be individual annular grooves or one or more continuous spiral grooves.
  • the grooves are separated by circumferentially extended lands 26 whose outer surfaces are flat or straight when viewed in such an axial section. That is, the lands have a flat profile when viewed in the direction of movement of the web through the apparatus.
  • each groove may be, for example, 6 to 60 such grooves per inch (2.36 to 23.6 grooves per cm), the axial widths of the grooves and lands being about the same and each groove having a depth in the range of 0.002 to 0.010 inch (0.0508 to 0.254 mm).
  • Figure 3 illustrates how, for such relatively thick webs, the coefficient of friction between a 0.0025 inch (0.0635 mm) thick, 54 inch (1372 mm) wide web and a grooved, 2.8 inch (71.1 mm) roller changes only slightly over a range of web speeds up to 1,000 feet per minute (305 meters per minute).
  • a somewhat larger drop in coefficient of friction is observed for web tension of 15 pounds or 0.27 pounds per linear inch across the web (6.8 kg or 0.0048 kg per mm), compared to a tension of 25 pounds or 0.45 pounds per linear inch across the web (11.34 kg or 0.008 kg per mm).
  • rollers of the type shown in Figure 2 fail to provide adequate traction at web speeds above a few hundred feet per minute. Traction no longer remains essentially constant but rather becomes a function of web thickness and web speed. We have discovered that this degradation in performance of such grooved rollers results from a decrease in the bending resistance of the ultrathin web. For the thicker webs, the bending resistance is sufficient to enable the webs to bridge the grooves and engage the lands of known grooved rollers with minimal radial deformation of the web, as shown in Figure 2.
  • Figure 5 illustrates how, for a 0.00025 inch (0.0064 mm) thick, 55 inch (1397 mm) wide, polyethyleneterephthalate web running on a 5.6 inch (142.2 mm) grooved roller, the coefficient of friction between the web and the roller drops rapidly over a range of web speeds up to 800 feet per minute (244 meters per minute).
  • a somewhat larger drop in coefficient of friction is observed for web tension of 10 pounds or 0.18 pounds per linear inch across the web (4.5 kg or 0.0032 kg per mm), compared to a tension of 15 pounds or 0.27 pounds per linear inch across the web (6.8 kg or 0.0048 kg per mm) or to a tension of 25 pounds or 0.45 pounds per linear inch across the web (11.34 kg or 0.008 kg per mm).
  • the primary objective of our invention is to provide an improved roller for conveying ultrathin webs at elevated web speeds, without substantial loss of traction or risk of damage to the web.
  • One embodiment of our apparatus is particularly suited for conveying ultrathin webs having a width.
  • a source of a web to be conveyed such as a stock roll, feeds the web over at least one cylindrical roller having an exterior surface with a length, the length being longer than the width of the web to be conveyed and a portion of the web being wrapped onto the roller over an angle ⁇ .
  • the roller comprises a plurality of circumferentially extending, axially spaced grooves formed in the exterior surface along the length, each groove having an axial width; and a plurality of lands formed in the exterior surface and extended between the grooves, each land having an axial width and a central surface with a convex curvature, the convex curvature having a maximum radius from a centerline of the roller.
  • the lands may be continuous.
  • the convex curvatures of the lands and the axial widths of the grooves and lands are chosen so that, at about a beginning of the wrap angle ⁇ during rotation of the roller, the web undulates along the width of the roller over the lands and into the grooves but is spaced from the convex curvatures of the lands, so that air entrained between the web and the lands can flow into the grooves.
  • Some contact at the apex of the convex curvature is acceptable at this location.
  • a minimum clearance between the web and the exterior surface occurs at the maximum radius of the convex curvature and the clearance between the web and the convex curvature increases with axial distance from the minimum clearance.
  • the wrap angle ⁇ may be in the range of 10 to 300°.
  • Means may be provided for moving the web at a speed in the range of 300 to 1,000 feet per minute (91.4 to 305 meters per minute).
  • the roller may be an idler roller or a driven roller.
  • the convex curvature may have a radius of curvature in the range of 0.020 to 1.2 inch (0.508 to 30.5 mm); the axial width of the grooves may be in the range of 0.020 to 0.105 inch (0.508 to 2.67 mm); and the axial width of the lands may be in the range of 0.020 to 0.105 inch (0.508 to 2.67 mm).
  • the cylindrical roller may have a diameter in the range of 1.5 to 10.0 inch 38.1 to 254 mm).
  • the roller of our invention may include at least one spiral groove formed in the exterior surface along the length, the spiral groove having an axial width; and at least one continuous spiral land formed in the exterior surface and extended between turns of the spiral groove, the spiral land having an axial width and a central surface with a convex curvature, the convex curvature having a maximum radius from a centerline of the roller.
  • the convex curvatures of the spiral land and the axial widths of the spiral groove and spiral land may be chosen so that, at a beginning of the wrap angle ⁇ during rotation of the roller, the web undulates along the width of the roller over the turns of the land and into the turns of the groove but is spaced from the convex curvature of the spiral land, so that air entrained between the web and the spiral land can flow into the spiral groove.
  • the spiral groove and spiral land may be formed by at least one wire wound onto the roller.
  • the apparatus and conveying rollers according to our invention provide various advantages. Ultrathin webs can be conveyed at elevated web speeds with good traction. Web weaving and scratching are minimized due to maintenance of adequate traction.
  • the coefficient of friction between ultrathin webs and rollers of our invention varies only moderately over a wide range of web speeds.
  • the wound wire embodiments of our roller have a high quality surface finish and are simple and economical to manufacture and maintain.
  • Existing apparatus is easily modified for conveying ultrathin webs simply by replacing prior art rollers with those of our invention.
  • Figure 1 illustrates schematically a manufacturing apparatus for conveying and treating web materials, of the general type suitable for use of rollers in accordance with our invention.
  • Figure 2 illustrates a fragmentary, sectional view in the direction of web movement, showing the engagement of a relatively thick web with a prior art grooved roller just as the web enters the wrap angle ⁇ in the apparatus of Figure 1.
  • Figure 3 illustrates how the measured coefficient of friction varies with web speed for a web and roller pair of the type shown in Figure 2.
  • Figure 4 illustrates a fragmentary, sectional view in the direction of web movement, showing the engagement of an ultrathin web with a prior art grooved roller just as the web enters the wrap angle on the roller.
  • Figure 5 illustrates how the coefficient of friction varies with web speed for a web and roller pair of the type shown in Figure 4.
  • Figure 6 illustrates a fragmentary, sectional view in the direction of web movement, showing the engagement of an ultrathin web with one embodiment of a contoured roller in accordance with our invention just as the web enters the wrap angle on the roller.
  • Figure 7 illustrates a schematic, sectional view in the direction of web movement, showing the engagement of an ultrathin web with a further embodiment of a contoured roller in accordance with our invention just as the web enters the wrap angle on the roller.
  • Figure 8 illustrates a calculated radial displacement of an ultrathin web as a function of axial position along a convex land on a contoured roller in accordance with one embodiment of our invention.
  • Figure 9 illustrates a calculated interfacial air pressure between an ultrathin web and a convex land on a contoured roller in accordance with the embodiment of our invention of Figure 8, as a function of axial position along the land.
  • Figure 10 illustrates a schematic, sectional view in the direction of web movement, showing the engagement of an ultrathin web with a still further embodiment of a contoured roller in accordance with our invention just as the web enters the wrap angle on the roller.
  • Figure 11 illustrates a calculated radial displacement of an ultrathin web as a function of axial position along a convex land on a contoured roller in accordance with another embodiment of our invention.
  • Figure 12 illustrates a calculated interfacial air pressure between an ultrathin web and a convex land on a contoured roller in accordance with the embodiment of our invention of Figure 11, as a function of axial position along the land.
  • Figure 13 illustrates how the measured coefficient of friction varies with web speed for an ultrathin web and a 5.2 inch (132.1 mm) diameter roller of the type shown in Figure 10.
  • Figure 14 illustrates how the measured coefficient of friction varies with web speed for a relatively thick web and a 3.7 inch (94 mm) diameter roller of the type shown in Figure 10.
  • Figure 6 illustrates a fragmentary, sectional view in the direction of web movement, showing the engagement of ultrathin web 30 with one embodiment of a contoured roller in accordance with our invention, just as the web enters the wrap angle ⁇ on roller 18.
  • the flat profile grooves and lands of the prior art rollers are replaced with an undulating, contoured surface somewhat geometrically similar to the shape assumed by an ultrathin web when used with a prior art grooved roller, as shown in Figure 4.
  • Our contoured surface may be provided on right cylindrical or concave rollers; however, we have found that concave rollers are preferable for more flimsy webs.
  • the exterior surface of roller 18 is provided with a plurality of circumferentially extended grooves 42, which may be individual annular grooves or one or more continuous spiral grooves.
  • the grooves are separated by circumferentially extended lands 44.
  • At least the central portion of the outer surfaces of lands 44 have convex curvatures when viewed in the illustrated, axial section. That is, lands 44 have an outwardly rounded profile when viewed in the direction of movement of the web through the apparatus.
  • grooves 42 may have a generally concave surface with an axial width w1 in the range of 0.020 to 0.105 inch (0.508 to 2.67 mm).
  • Lands 44 may have a generally convex central portion on surface 46 with an axial width w2 in the range of 0.020 to 0.105 inch (0.508 to 2.67 mm).
  • Surface 46 may have a circular, elliptical, parabolic or similar convex shape with a central location of maximum radius or high point 48. When surface 46 is circular, as illustrated, the radius of curvature may be in the range of 0.020 to 1.2 inch (0.508 to 30.5 mm).
  • grooves 42 and lands 44 are shaped and spaced in this manner, at about the beginning of wrap angle ⁇ and upon rotation of roller 18, web 30 will undulate along the width of the roller over the lands and into the grooves while remaining spaced slightly from the surfaces of the lands and grooves. Because web 30 assumes this undulating configuration at about the beginning of the wrap angle, air entrained between the web and the lands can flow readily into the grooves to permit the web to engage the roller further along in the wrap angle.?
  • FIG. 7 illustrates another embodiment of a roller made in accordance with our invention.
  • roller body 18 is wrapped with a circular cross section wire 50 to provide spiral grooves 42 and lands 44.
  • Wire 50 may have a radius of about 0.020 inch (0.508 mm), for example, and be wrapped tightly onto the roller so that successive turns of the wire abut in the manner illustrated.
  • Roller body 18 may be a circular cylinder having a diameter in the range of 1.5 to 10.0 inch (38.1 to 254 mm).
  • a concave axial profile may be advantageous.
  • a concave profile is suitable whose diameter tapers about 0.2% from its ends to its center.
  • Figure 8 illustrates a calculated radial displacement of an ultrathin web at about the beginning of the wrap angle as a function of axial position along a convex land on a contoured roller in accordance with the embodiment of Figure 7.
  • a web 30 having a thickness of about 0.00025 inch (0.0064 mm) was assumed to be wrapped onto a roller having a diameter of about 2.75 inch (69.85 mm).
  • the clearance between the web and the convex land was calculated to be a minimum at the point of maximum radius of the land, corresponding to high point 48 in Figures 6 and 7.
  • the clearance between the web and the land was calculated to increase, thus indicating that air would be able to escape into the neighboring grooves.
  • Figure 9 illustrates a calculated interfacial air pressure at about the beginning of the wrap angle between web 30 and convex land 44 on a contoured roller in accordance with the embodiment of Figure 7, as a function of axial position along the land. Consistent with Figure 8, this plot indicates that the calculated pressure between the web and the convex land decreases from a maximum at high point 48 to a minimum at the center of the neighboring groove. The convex shape of the curve indicates that the relatively high pressure air at the center of the land can escape readily into the lower pressure area in the grooves.
  • FIG 10 illustrates yet another embodiment of a roller made in accordance with our invention.
  • roller body 18 is wrapped with an essentially rectangular cross section wire 52 to provide spiral grooves 42 and lands 44.
  • Wire 52 may have a convex surface 54 with a radius of curvature in the range of 0.020 to 1.2 inch (0.508 to 30.48 mm), side walls 56 with a radial dimension in the range of 0.035 to 0.045 inch (0.889 to 1.143 mm) and a base wall 58 with an axial dimension in the range of 0.040 to 0.210 inch (1.016 to 5.334 mm), for example.
  • Wire 52 is wrapped tightly onto the roller so that successive turns of the wire abut along side walls 56 in the manner illustrated.
  • Roller body 18 may be a circular cylinder having a diameter in the range of 1.5 to 10.0 inch (38.1 to 254 mm). A concave profile also may be used.
  • Figure 11 illustrates a calculated radial displacement of an ultrathin web at about the beginning of the wrap angle as a function of axial position along a convex land on a contoured roller in accordance with the embodiment of Figure 10.
  • a web 30 having a thickness of about 0.00025 inch (0.0064 mm) was assumed to be wrapped onto a roller having a diameter of about 2.75 inch (69.85 mm).
  • the clearance between the web and the convex land was calculated to be rather uniform across the land, thus indicating that air would be able to escape into the neighboring grooves.
  • Figure 12 illustrates a calculated interfacial air pressure at about the beginning of the wrap angle between web 30 and convex land 44 on a contoured roller in accordance with the embodiment of Figure 10, as a function of axial position along the land. This plot indicates that the calculated pressure between the web and the convex land is relatively constant but decreases to a minimum at the edge of the neighboring groove.
  • Figure 13 illustrates how, for a 0.00025 inch (0.0064 mm) thick, 55 inch (1397 mm) wide polyethyleneterephthalate web running on a 5.2 inch (132.08 mm) diameter contoured roller in accordance with the embodiment of Figure 10, the coefficient of friction between the web and the roller drops very slightly over a range of web speeds up to 1,000 feet per minute (305 meters per minute). A concave profile was used.
  • Figure 14 similar to Figure 3, illustrates how, for a relatively thick 0.0025 inch (0.0635 mm) thick, 54 inch (1372 mm) wide polyethyleneterephthalate web running on a 3.7 inch (93.98 mm) diameter contoured roller of the type shown in Figure 10, the coefficient of friction between the web and the roller changes very little over a range of web speeds up to 1,000 feet per minute (305 meters per minute).

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  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)
  • Rolls And Other Rotary Bodies (AREA)
EP19950115687 1994-10-07 1995-10-05 Vorrichtung zum Führen von ultradünnen Bahnen mit einer Transportrolle mit profilierter Oberfläche Expired - Lifetime EP0705786B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US32007694A 1994-10-07 1994-10-07
US320076 1994-10-07

Publications (3)

Publication Number Publication Date
EP0705786A2 true EP0705786A2 (de) 1996-04-10
EP0705786A3 EP0705786A3 (de) 1996-11-20
EP0705786B1 EP0705786B1 (de) 2001-12-19

Family

ID=23244773

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19950115687 Expired - Lifetime EP0705786B1 (de) 1994-10-07 1995-10-05 Vorrichtung zum Führen von ultradünnen Bahnen mit einer Transportrolle mit profilierter Oberfläche

Country Status (3)

Country Link
EP (1) EP0705786B1 (de)
JP (1) JPH08175727A (de)
DE (1) DE69524705T2 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0820947A1 (de) * 1996-07-26 1998-01-28 Eastman Kodak Company Transportrolle mit profilierter Oberfläche zum Führen von ultradünnen Bahnen und Vorrichtung mit einer solchen Transportrolle
US6436191B1 (en) * 1997-12-01 2002-08-20 Eastman Kodak Company Corona discharge treatment roller and surface finishing process
CN102408035A (zh) * 2011-07-29 2012-04-11 浙江伟博包装印刷品有限公司 一种网带传送装置

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5265161B2 (ja) * 2006-09-27 2013-08-14 富士フイルム株式会社 ウエブ案内ローラ、およびウエブ搬送装置
TWI449655B (zh) * 2006-09-27 2014-08-21 Fujifilm Corp 薄片導引滾輪及薄片輸送設備
JP5094424B2 (ja) * 2008-01-04 2012-12-12 富士フイルム株式会社 製膜方法
JP5317525B2 (ja) * 2008-04-30 2013-10-16 富士フイルム株式会社 溶液製膜方法

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3405855A (en) * 1966-03-11 1968-10-15 Beloit Corp Paper guide and drive roll assemblies
US3630424A (en) * 1970-06-17 1971-12-28 Eastman Kodak Co Drilled nonported vacuum drum
DE2443663C3 (de) * 1974-09-12 1981-01-15 Basf Ag, 6700 Ludwigshafen Walzeneinrichtung zum fortlaufenden Transport von Folienbahnen
US4914796A (en) * 1988-12-12 1990-04-10 Eastman Kodak Company Process for manufacturing nickel coated shot blasted web conveying roller
FR2696166B1 (fr) * 1992-09-28 1994-11-18 Escher Wyss Ag Cylindre de guidage d'une bande.

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0820947A1 (de) * 1996-07-26 1998-01-28 Eastman Kodak Company Transportrolle mit profilierter Oberfläche zum Führen von ultradünnen Bahnen und Vorrichtung mit einer solchen Transportrolle
US6436191B1 (en) * 1997-12-01 2002-08-20 Eastman Kodak Company Corona discharge treatment roller and surface finishing process
CN102408035A (zh) * 2011-07-29 2012-04-11 浙江伟博包装印刷品有限公司 一种网带传送装置

Also Published As

Publication number Publication date
JPH08175727A (ja) 1996-07-09
EP0705786B1 (de) 2001-12-19
DE69524705D1 (de) 2002-01-31
DE69524705T2 (de) 2002-08-14
EP0705786A3 (de) 1996-11-20

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