USRE32586E - Press roll with adjustable flexion - Google Patents

Press roll with adjustable flexion Download PDF

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Publication number
USRE32586E
USRE32586E US06/830,215 US83021586A USRE32586E US RE32586 E USRE32586 E US RE32586E US 83021586 A US83021586 A US 83021586A US RE32586 E USRE32586 E US RE32586E
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US
United States
Prior art keywords
roll
yoke
shell
press
mating
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US06/830,215
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English (en)
Inventor
Christian Schiel
Robert Wolf
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.)
JM Voith GmbH
Original Assignee
JM Voith GmbH
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Filing date
Publication date
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Priority claimed from DE19803024575 external-priority patent/DE3024575C2/de
Priority claimed from DE19803049080 external-priority patent/DE3049080A1/de
Application filed by JM Voith GmbH filed Critical JM Voith GmbH
Application granted granted Critical
Publication of USRE32586E publication Critical patent/USRE32586E/en
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Classifications

    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H57/022—Adjustment of gear shafts or bearings
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/0006—Driving arrangements
    • 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
    • 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
    • D21G1/0226—Bearings
    • 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
    • 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
    • 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
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02069—Gearboxes for particular applications for industrial applications
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02078—Gearboxes for particular applications for wind turbines

Definitions

  • the invention concerns a press roll with adjustable flexion, preferably intended for use in the paper industry.
  • the press roll has a hollow shell that can rotate around a fixed yoke and, in conjunction with a mating roll, form a .[.web.]. .Iadd.nip.Iaddend., e.g. press nip for a web of paper, to travel through.
  • the axis of rotation of both rolls lie in the same press plane as the press nip.
  • the press roll has the following additional characteristics:
  • a self-aligning bearing keeps each end of the shell at least indirectly away from the yoke.
  • German Auslegeschrift 2 407 510 corresponding to U.S. Pat. No. 3,932,921,
  • German Auslegeschrift 2 826 316 corresponding to U.S. Pat. No. 4,213,232.
  • the shell of the press rolls known from Publications 1 and 2 is approximately as long as that of the mating roll and each end of the shell is mounted directly against the yoke with a self-aligning bearing.
  • the longitudinal distance between the center planes of the self-aligning bearings of the shell, said planes being perpendicular to the axis of rotation of the rolls, is shorter than the distance between the mating-roll bearings.
  • the press roll known from Publication 1 (especially FIG. 1, p. 169) is of the type called a floating roll.
  • the hydraulic support is a semiannular pressurized compartment between the yoke and the shell extending essentially the total length of the shell.
  • the roll known from Publication 2 on the other hand has a certain number of hydrostatic pressure shoes distributed along the press gap over the total length of the shell of the roll.
  • Rolls of this type are used to extract water in the wet sections of papermaking machines or to calender the dry paper, for example.
  • the last function especially, requires an especially precise nip between press roll and mating roll to maintain uniform paper thickness over the total width of the web. This is to ensure that the finished roll of paper will be as cylindrical as possible. If the two rolls do not mate precisely, the rolls of paper will be irregular in shape, making them hard to handle and leading to rejection.
  • FIG. 9 Another type of press roll with an extended shell is known from Publication 5 (FIG. 9).
  • the yoke does not rest immediately on the support caps but through the intervention of additional roller bearings on the inside of the shell. This necessitates a considerable enlargement of the shell bearings, which must now transfer the support forces of not only the shell but also of the yoke to the support caps and the machine frame.
  • the basic purpose of the invention is to provide a press roll with adjustable flexion in order to ensure a perfect mating (or fitting) in the nip when it is pressed against the mating roll without the distance between the supported surfaces of the yoke being significantly greater than that between the mating-roll bearings. It should also be possible if necessary to accommodate devices to apply an additional random flexion to the ends of the press-roll shell without increasing its overall dimensions. Finally it should be possible to employ the press roll in accordance with the invention with a simple type of drive mechanism.
  • the supported surfaces of the yoke and the self-aligning bearings of the shell are "encased" inside each other, although in a different way than that known from Publication 5 and without the drawbacks entailed by that design.
  • self-aligning bearings with dimensions that remain within the ordinary range can be employed for the shell.
  • the greatest advantage of the invention is that the distance between the self-aligning bearings of the shell and that between the bearings of the mating roll can be approximately equal without necessitating an increase in the overall length of the press roll (especially at the yoke). This will ensure a perfect nip between the two rolls, i.e. a uniform mating of the two rolls over their total length.
  • the supported surfaces of the yoke Since the yoke bends when the press roll is in operation, it is preferable for the supported surfaces of the yoke to be spherical, as is in itself known. Otherwise, the design will be carried out in general so that when there is no stress on the press roll the yoke will be coaxial with the shell. In this case, the spherical supported surfaces of the yoke and the self-aligning bearings of the shell of the press roll will share a midpoint at each end. .[.In other words, the two mid-points will be equivalent..]. Deviations are, however, possible. The midpoint of the spherical supported surface can be displaced in relation to that of the self-aligning bearing on the shell, the displacement being radial toward the mating roll. This will permit greater yoke flexion with all other dimensions constant.
  • the drive pinion is also mounted differently. It is mounted rigidly in a drive housing that is separate from the support cap. The drive housing itself is mounted with an additional roller bearing inside the roll shell. The housing will thus accompany, along with the pinion, any inclination of the shell when the latter bends.
  • One drawback of this design is that, in addition to the support cap in which the yoke rests, it requires an extra housing and an additional bearing.
  • the drive also necessitates a longer yoke, and the cap that supports the yoke must be placed farther out than with a roll that has no drive. This results in other drawbacks. In particular, the flexion of the yoke must increase if the dimensions of its cross-section and the load are to remain constant..].
  • the supplemental supports are not activated.
  • the shell bends along the normal line of flexion.
  • the hydraulic pressure in the main support can still be varied to make the press in the nip exactly uniform, heavier in the middle, or heavier at the edges.
  • the supplemental supports act against the direction of press and the hydraulic pressure in the main support is slightly increased. The result is uniform press along a wide middle range and more press at the edges. If the hydraulic pressure in the main support is further increased, a smooth press profile at the edges and a peak pressure in the middle will be obtained.
  • the supplemental supports act in the direction of press and the hydraulic pressure in the main support is slightly reduced. The result is heavy pressing along a wide middle range and reduced pressing at the edges. If the pressure in the main support is reduced even more, a smooth press profile at the edges and reduced pressure in the middle will be obtained.
  • the supplemental supports at both ends of the roll can be adjusted differently if necessary.
  • the main support can also be divided into several individually adjustable sections.
  • the invention permits the roll shell to bend farther than that of a conventional press roll with lower forces. Increasing the distance between the self-aligning bearings on the shell also considerably increases the distance between the self-aligning bearings and the supplemental supports and hence the effective lever arm available to produce the bending moment. This increase also decreases the load on the self-aligning bearings. It is also of course basically possible to employ supplemental hydraulic supports when the distance between the self-aligning bearings is somewhat less than the distance between the bearings on the mating roll (claim .[.17.]. .Iadd.20.Iaddend.). The distance between the supported surfaces of the yoke can then be somewhat greater than distance between the bearings on the mating roll.
  • the hydraulic supports can be designed in various ways.
  • the main support in the middle range can either be a number of hydrostatic pressure shoes or (as with the floating roll discussed in the introduction) a continuous semiannular compartment containing oil under low pressure and bordered by elastic longitudinal and peripheral sealing strips.
  • the advantage of the latter form is that the yoke will not be weakened with holes for hydrostatic shoes, so that its diameter can be shorter, which also decreases the size and weight of the shell and makes it cheaper to manufacture.
  • the supplemental supports can also be either hydrostatic pressure shoes or semiannular pressurized chambers.
  • FIG. 1 shows an embodiment that has no drive and in which the self-aligning bearing of the roll shell is mounted outside it.
  • FIG. 2 shows another embodiment that has no drive and in which the self-aligning bearing of the roll shell is mounted inside it.
  • FIG. 3 shows a development of the embodiment in FIG. 2 that has a drive..].
  • FIG. .[.4.]. .Iadd.3 .Iaddend. shows another modification of the embodiment in FIG. 2.
  • Each roll has a movable bearing on one end, as shown in FIGS. 1 and 2 and a fixed bearing on the other.[., as in FIG. 3. Yoke 57.]..Iadd..
  • the yoke .Iaddend.and roll shell .[.51, 52 and 47.]. are fastened at the fixed-bearing end so as to permit no axial displacement in relation to .Iadd.the .Iaddend.frame .[.60.]., whereas axial displacement of yoke 7; 27 and roll shell 1, 2; 21, 22 with respect to frame 10 is possible at the movable-bearing end. Except for the means that prevent the axial displacement, the mountings at each end do not differ.
  • the rotating roll shell 1 is prolonged by a flanged bearing bushing 2.
  • Self-aligning bearing 3 connects bushing 2 to support cap 4, which also houses the bearing.
  • Cap 4 is sealed with a cover 5 that has a sealing lip 6.
  • Support cap 4 has a tubular collar 4a that extends into bearing bushing 2.
  • Yoke 7 is articulated by means of a spherical liner 8 that has a contact surface 8a to collar 4a of cap 4, on which it rests.
  • a sealing lip 9 seals the gap between yoke 7 and support cap 4.
  • Cap 4 is fastened to a movable bearing lever or to a frame 10.
  • Compartment 11 There is a semiannular pressurized compartment 11 between shell 1 and yoke 7. Compartment 11 is bordered by peripheral seals 12 and by longitudinal sealing strips 13 that lie opposite each other. It can be supplied with compressed oil over a channel 14 to apply a support force to shell 1 to counteract the force of the mating roll. Compartment 11 (the main support) is only slightly shorter than the length of the press area BL. There are supplemental supports in the form of hydrostatic pressure shoes 15 and 16 outside press area BL at each end of shell 1. Their axes lie in the press plane (which coincides with the plane of the drawing). They can be activated with compressed oil supplied from lines 15a and 16a. One shoe 15 works toward mating roll 17, the other in the opposite direction. An additional, calculated flexion can thus be imposed on the ends of roll shell 1 when necessary. A supplemental semiannular pressurized compartment similar to compartment 11 can be used instead of hydrostatic pressure shoes 15 and 16.
  • the center plane m of bearing 20 on the mating roll is perpendicular to the axis of rotation of the press roll.
  • the distance from this center plane to that of the bearing on the other end of the roll is the bearing distance LE.
  • the center planes of bearing 20 and of self-aligning bearing 3 on each end of the roll coincide. This is another way of saying that the bearing distances are equal.
  • the "bearing distance" of support surfaces 8a on yoke 7 is also the same.
  • FIG. 2 also shows a bearing bushing 22 flanged to a rotating roll shell 21 and connected to a support cap 24 with a self-aligning roller bearing 23.
  • bearing 23 is inside bushing 22, whith its inner ring resting on collar 24a of cap 24.
  • a cover 25 with a sealing lip 26 seals off the oil chamber of bearing 23.
  • Yoke 27 is separated, as in FIG. 1, by an intermediate ring 8 from support cap 24.
  • Yoke 27 is provided with hydrostatic pressure shoes 18, also called support pistons, which support shell 21 from inside.
  • the press roll has a row of several such shoes 18 (the main support) along the press plane.
  • Supplemental hydrostatic pressure shoes 15 and/or 16, which are again outside press area BL can be supplied with pressure in such a way as to force a desired flexion of roll shell 21.
  • FIG. 3 shows a powered embodiment with a semiannular pressure compartment 11 (as in FIG. 1) but without supplemental supports, although such could of course be added if necessary.
  • a bearing bushing 52 screws into shell 51 and a crown gear 47 to bushing 52.
  • the shell which is thus extended in length, is again mounted with a self-aligning roller bearing 53 to the collar 54a of the support cap 54.
  • the yoke 57 is again articulated to collar 54a by a spherical liner 58.
  • a sealing lip 59 seals the gap between support cap 54 and a bushing 60 that has been slid onto yoke 57.
  • a spring washer 61 holds spherical liner 58 in place axially over bushing 60 (a fixed bearing).
  • Support cap 54 is attached to a contact-pressure lever, contact-pressure piston, or frame 10.
  • Bearing 53 is prevented from moving axially with respect to support cap 54 by a support ring 62 and a spring washer 63.
  • crown gear 47 is prevented from moving axially with respect to bearing 53 by support ring 64 and spring washer 65 (a fixed bearing).
  • a lug 66 that is fastened to support cap 54 projects into a groove 67 in yoke 57 and prevents it from turning. This device is not shown in FIGS. 1 and 2.
  • a drive shaft 68 with a feather 69 is powered through a cardan drive, not shown.
  • Drive shaft 68 is mounted in a spherical bearing 30 and sealed with a sealing lip 31 in a cover 32.
  • Bearing 30 and cover 32 rest in a bearing bracket 30a that screws onto support cap 54.
  • Shaft 68 powers an angularly adjustable geared coupling 33 that activates a drive pinion 34 that mates with crown gear 47.
  • Bearing 35 is axially stabilized on the one hand by a spring washer 39 in pinion 34 and on the other by a stabilizing ring 40 and spring washer 41 on bolt 36.
  • Support cap 54 also forms a housing for cogwheels 34 and 47. This drive housing is sealed off near bearing bushing 52 with a cover 55 and sealing lip 56.
  • a mating roll and its bearing are positioned as in FIG. 2, although not shown in FIG. 3..].
  • FIG. .[.4.]. .Iadd.3 .Iaddend. that are the same as in FIG. 2 are labeled with the same index numbers.
  • the only essential difference is that collar 24b is extended by distance e inside shell 21, 22 and that the yoke 27' can thus be shorter.
  • .Iadd.A drive for the roll in any of the embodiments may be of a known type, as that shown in U.S. Pat. No. 3,766,620 incorporated herein by reference. .Iaddend.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Paper (AREA)
US06/830,215 1980-06-28 1981-06-26 Press roll with adjustable flexion Expired - Lifetime USRE32586E (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3024575 1980-06-28
DE19803024575 DE3024575C2 (de) 1980-06-28 1980-06-28 Preßwalze, deren Durchbiegung einstellbar ist
DE3049080 1980-12-24
DE19803049080 DE3049080A1 (de) 1980-12-24 1980-12-24 Presswalze, deren durchbiegung einstellbar ist

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
US06/355,571 Reissue US4414890A (en) 1980-06-28 1981-06-26 Press roll with adjustable flexion
US06604867 Continuation 1984-04-30

Publications (1)

Publication Number Publication Date
USRE32586E true USRE32586E (en) 1988-02-02

Family

ID=25786301

Family Applications (2)

Application Number Title Priority Date Filing Date
US06/355,571 Ceased US4414890A (en) 1980-06-28 1981-06-26 Press roll with adjustable flexion
US06/830,215 Expired - Lifetime USRE32586E (en) 1980-06-28 1981-06-26 Press roll with adjustable flexion

Family Applications Before (1)

Application Number Title Priority Date Filing Date
US06/355,571 Ceased US4414890A (en) 1980-06-28 1981-06-26 Press roll with adjustable flexion

Country Status (9)

Country Link
US (2) US4414890A (ja)
EP (2) EP0043119B1 (ja)
JP (1) JPH0229797B2 (ja)
BR (1) BR8108896A (ja)
CS (1) CS231986B2 (ja)
DE (1) DE3165680D1 (ja)
FI (1) FI70988C (ja)
WO (1) WO1982000165A1 (ja)
YU (1) YU158381A (ja)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5081759A (en) * 1986-11-07 1992-01-21 J.M. Voith Gmbh Vibration damping in a roll
US5193258A (en) * 1991-11-15 1993-03-16 Beloit Technologies, Inc. Self-loading controlled deflection roll
US5273626A (en) * 1991-01-07 1993-12-28 Valmet Paper Machinery Inc. Adjustable-crown roll
US20040266596A1 (en) * 2003-06-24 2004-12-30 Walzen Irle Gmbh Roll
US20060005391A1 (en) * 2004-07-12 2006-01-12 Eastman Kodak Company Axially compliant pressure roller utilizing non-newtonian fluid

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DE3138365A1 (de) * 1981-09-21 1983-04-14 Escher Wyss AG, Zürich Durchbiegungseinstellwalze
DE3330204C2 (de) * 1983-08-20 1986-07-31 J.M. Voith Gmbh, 7920 Heidenheim Stirnradgetriebe für den Antrieb eines Walzenmantels
DE3343313A1 (de) * 1983-11-30 1985-06-05 J.M. Voith Gmbh, 7920 Heidenheim Walze zur behandlung von bahnen, vorzugsweise papierbahnen
DE8500950U1 (de) * 1985-01-16 1985-04-18 Walzen Irle GmbH, 5902 Netphen Beheizbare kalanderwalze mit einem einen stroemungsspalt bildenden verdraengerkoerper
DE3519318A1 (de) * 1985-05-30 1986-12-04 Küsters, Eduard, 4150 Krefeld Durchbiegungssteuerbare walze
DE3528588A1 (de) * 1985-08-09 1987-02-19 Voith Gmbh J M Walze zum ausueben einer presskraft auf eine faserstoffbahn
EP0222621B1 (en) * 1985-11-13 1991-05-22 Akechi Yano A roller for stretching or imparting shrinkage to sheeting
CA1270786A (en) * 1986-03-07 1990-06-26 Akechi Yano Roll with an arched shaft
DE3639935A1 (de) * 1986-11-22 1988-06-01 Kuesters Eduard Maschf Walze
ES2021612B3 (es) * 1986-03-13 1991-11-16 Kuesters Eduard Maschf Cilindro.
DE3645034C3 (de) * 1986-03-13 1996-07-04 Kuesters Eduard Maschf Walze
DE3610107A1 (de) * 1986-03-26 1987-10-08 Voith Gmbh J M Stellvorrichtung zum verstellen einer walze
FI74070C (fi) * 1986-04-09 1987-12-10 Valmet Oy Foerfarande foer att kontrollera boejningen av en boejningsreglerad vals samt en vals foer en pappersmaskin foer tillaempning av foerfarandet.
CA1296557C (en) * 1986-04-09 1992-03-03 Josef Pav System of rolls for use in calenders and like machines
DE3623028C3 (de) * 1986-07-09 1992-10-22 Voith Gmbh J M Presswalze mit einstellbarer durchbiegung
FI93389C (fi) * 1987-02-12 1995-03-27 Voith Gmbh J M Lieriöhammaspyörästö telavaipan pyörittämiseksi
DE3804225A1 (de) * 1987-02-12 1988-08-25 Voith Gmbh J M Stirnradgetriebe fuer den antrieb eines walzenmantels
US4891874A (en) * 1987-08-20 1990-01-09 Beloit Corporation Self loading controlled deflection roll
US4837907A (en) * 1987-08-20 1989-06-13 Beloit Corporation Self-loading controlled deflection roll
DE3728389A1 (de) * 1987-08-26 1989-03-16 Voith Gmbh J M Presswalze, deren durchbiegung einstellbar ist
JPH0244098U (ja) * 1988-09-22 1990-03-27
FI100099B (fi) * 1988-11-17 1997-09-30 Valmet Paper Machinery Inc Menetelmä ja laite paperirainan rullauksessa
DE3838852C1 (ja) * 1988-11-17 1990-05-23 J.M. Voith Gmbh, 7920 Heidenheim, De
DE4013772C2 (de) * 1990-04-28 1994-11-24 Kuesters Eduard Maschf Antriebsanordnung für eine Walze
DE4026774A1 (de) * 1990-08-24 1992-03-05 Voith Gmbh J M Mehrwalzen-glaettwerk
DE4033638C1 (ja) * 1990-10-23 1992-02-13 Eduard Kuesters Maschinenfabrik Gmbh & Co Kg, 4150 Krefeld, De
US5461979A (en) * 1992-10-19 1995-10-31 Bruni Ag Grafische Maschinen Multiple blade ink knife
DE786031T1 (de) * 1994-08-16 1998-01-15 Beloit Technologies, Inc., Wilmington, Del. Hydrostatische durchbiegungswalze mit selbsttätiger lastregulierung
DE4440711A1 (de) * 1994-11-15 1996-05-23 Kuesters Eduard Maschf Streichvorrichtung
DE19505379C1 (de) * 1995-02-17 1996-03-28 Voith Sulzer Papiermasch Gmbh Durchbiegungseinstellwalze
US20040154146A1 (en) * 2001-05-17 2004-08-12 Pruitt Paul R. Web spreader roll and methods for spreading webs of material
FI116413B (fi) * 2001-05-31 2005-11-15 Metso Drives Oy Käyttövaihteiston ja telan välinen rakenne
FI117646B (fi) * 2004-10-04 2006-12-29 Metso Paper Inc Tela
DE102005001782A1 (de) * 2005-01-14 2006-07-20 Berstorff Gmbh Vorrichtung zur Kalandrierung von kontinuierlich hergestellten Gegenständen mit mindestens einer Kalanderwalze
DE102006040777B4 (de) * 2006-08-31 2016-02-04 Schaeffler Technologies AG & Co. KG Wälzlagereinheit
DE102010060494A1 (de) * 2010-11-11 2012-05-16 Andritz Küsters Gmbh Walzenanordnung
DE102011052709A1 (de) * 2011-08-15 2013-02-21 Andritz Küsters Gmbh Walzenanordnung für einen Thermobonding-Kalander sowie Betriebsverfahren einer Walze
CN102978990A (zh) * 2012-11-07 2013-03-20 无锡市洪成造纸机械有限公司 一种改进的真空吸移辊
ES2784973T3 (es) * 2016-08-04 2020-10-02 Flender Gmbh Transmisión de turbina eólica
KR102488782B1 (ko) * 2017-08-21 2023-01-16 엘지이노텍 주식회사 기어박스 및 이를 포함하는 액츄에이터

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US5273626A (en) * 1991-01-07 1993-12-28 Valmet Paper Machinery Inc. Adjustable-crown roll
US5495798A (en) * 1991-01-07 1996-03-05 Valmet Paper Machinery, Inc. Adjustable-crown roll
US5193258A (en) * 1991-11-15 1993-03-16 Beloit Technologies, Inc. Self-loading controlled deflection roll
US20040266596A1 (en) * 2003-06-24 2004-12-30 Walzen Irle Gmbh Roll
US7481754B2 (en) * 2003-06-24 2009-01-27 Walzen Irle Gmbh Roll
US20060005391A1 (en) * 2004-07-12 2006-01-12 Eastman Kodak Company Axially compliant pressure roller utilizing non-newtonian fluid
US7465264B2 (en) * 2004-07-12 2008-12-16 Rohm And Haas Denmark Finance A/S Axially compliant pressure roller utilizing non-newtonian fluid

Also Published As

Publication number Publication date
JPH0229797B2 (ja) 1990-07-02
CS489181A2 (en) 1984-01-16
DE3165680D1 (en) 1984-09-27
BR8108896A (pt) 1982-10-26
EP0061456A1 (de) 1982-10-06
FI70988C (fi) 1986-10-27
EP0043119A1 (de) 1982-01-06
YU158381A (en) 1983-09-30
CS231986B2 (en) 1985-01-16
WO1982000165A1 (en) 1982-01-21
EP0043119B1 (de) 1984-08-22
FI70988B (fi) 1986-07-18
FI822393L (fi) 1982-07-06
FI822393A0 (fi) 1982-07-06
US4414890A (en) 1983-11-15
JPS57501037A (ja) 1982-06-10

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