WO1998004844A1 - Walze für die druckbehandlung einer bahn - Google Patents
Walze für die druckbehandlung einer bahn Download PDFInfo
- Publication number
- WO1998004844A1 WO1998004844A1 PCT/DE1997/001388 DE9701388W WO9804844A1 WO 1998004844 A1 WO1998004844 A1 WO 1998004844A1 DE 9701388 W DE9701388 W DE 9701388W WO 9804844 A1 WO9804844 A1 WO 9804844A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- roller
- longitudinal direction
- support element
- sealing strip
- support
- Prior art date
Links
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
- 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
Definitions
- the invention relates to a roller of the type corresponding to the preamble of claim 1.
- Such a roller is known from DE-GM 93 14 568.
- the support elements rest on the inner circumference of the hollow roller with the edges of storage pockets formed on them themselves.
- Support elements adjacent to one another in the longitudinal direction of the roller follow one another directly.
- the bearing pockets extend on the mutually adjacent sides in the longitudinal direction of the roller of successive support elements as far as directly to the edge of the support element, so that there is the minimum possible distance between successive bearing pockets.
- the hollow rollers made of fiber-reinforced plastic with a wall thickness of 15 to 20 mm can be deformed such that the transition points from a support element to the support element following in the longitudinal direction of the roller become apparent in the line pressure curve.
- the hydraulic pressure in the storage pockets drops transversely to the edge from the value prevailing in the storage pocket to zero and rises again at the edge of the next storage pocket from zero to the pressure in the storage pocket there.
- This pressure drop on the inner circumference of the hollow roller is still noticeable on the outer circumference because of the flexibility of the hollow roller.
- the invention has for its object to design a generic roller so that the pressure drops at the transitions in the longitudinal direction of the roller of successive support elements are avoided. This object is achieved by the invention reproduced in claim 1.
- bearing pockets are no longer formed on each individual support element itself, but on a continuous "sealing strip" which is arranged in the longitudinal direction of the roller and carries a number of bearing pockets corresponding to the number of support elements , which are provided at the locations of the support elements and extend over their longitudinal extent.
- the invention is already realized when a continuous sealing strip with a plurality of bearing pockets extends over a plurality of support elements which follow one another in the longitudinal direction of the roller; In the preferred embodiment, however, it is provided that the sealing strip runs over the entire length of the roller.
- the pressure at the front edge of the respective storage pocket fell to zero or at least a small value because the edge freely bordered on the space between the crosshead and the inner circumference of the hollow roller.
- the arrangement in the longitudinal direction of the roller of successive bearing pockets on the sealing strip makes it possible to give the bearing pockets adjacent to one another in the longitudinal direction of the roller a common border.
- the pressure of the storage pockets and thus also against the inner circumference of the hollow roller applied pressure essentially the same, because the ⁇ pressure of the bearing pockets is applied from both sides and there is no pressure drop. If the pressure in the storage pockets is equal to one another in the longitudinal direction of the roller of adjacent storage pockets, this applies strictly.
- the form stability of the sealing strip at the transitions between the individual support elements also contributes purely mechanically to compensate for the line pressure curve.
- the sealing strip also avoids excessive surface pressures on the edges of adjacent support elements which are subjected to different pressures.
- the sealing strip must not be too stiff, because otherwise it hinders the sensitive pressure by the independent control in the longitudinal direction of the roller of successive support elements.
- a continuous sealing strip with a storage pocket over the length of the roller is known per se from DE 25 02 161 AI.
- This sealing strip is not supported by individual separately controllable support elements, but by a rod-shaped piston which extends over the length of the roller and by means of which only a pressing force which is uniform over the length can be exerted.
- the bearing pocket also runs through the length of the roller, so that only a uniform hydrostatic pressure can act against the inner circumference of the hollow roller.
- DE 35 28 333 C2 also has a continuous sealing strip which can even be supported by individual support elements, which, however, do not follow one another directly in the longitudinal direction of the roller.
- the bearing pocket formed on the sealing strip is designed to be continuous over the entire length of the roller, so that the possibility sought in the invention of exerting separate pressures along the roller is not given.
- the sealing strip can be held on the top of the support elements in the manner shown in claim 4.
- the support elements can have a rectangular plan in the planes perpendicular to their direction of action and the bearing pockets can be narrower in the circumferential direction than the support element bodies.
- the narrower design of the bearing pockets in the U direction is intended to prevent the hollow roller from being pressed into the circumferentially spanned region of the bearing pocket under the effect of the line force, which could lead to increased pressures and wear on the edges of the edges.
- the support pocket according to claim 6 should result in an at least partial hydraulic relief of the sealing strip.
- the sealing strip When the hydraulic relief is complete, i.e. the sealing strip "floats" on the pressure fluid in the support pockets, the sealing strip can nestle particularly perfectly against the course of the inner circumference of the hollow roller.
- the support elements should be controllable in smaller groups of several support elements each, or preferably individually. Such a control can be carried out relatively easily in the manner set out in claim 10.
- the force exerted by the individual support element is determined by the hydrostatic pressure in the cylinder chambers of the individual support elements which are closed except for the feed line. To change this pressure, only very small volumes are required, which can be brought in by feed lines of very small cross-section. If the storage pockets are connected to a single supply line, only this larger amount of pressure fluid needs to be able to carry.
- stabilization pockets of claim 11 each of which has only a much smaller basic cross-section than the storage pocket itself and thus does not consume a lot of pressure fluid, so that the pressure control of the cylinder chamber from which the stabilization pockets derive their pressure fluid relate, is not significantly influenced.
- the invention is primarily for using rollers Hollow rollers are provided which are relatively easily deformable. Although they should keep their tube shape during operation and not “flutter”, they should nevertheless be so deformable that they can "let through” a non-constant pressure profile of the support elements and can easily nestle against a counter roller.
- the material of the hollow roller should have an elastic modulus that is at most half the elastic modulus of steel.
- a design according to claim 13 comes into consideration.
- the “hollow roll which is noticeably deformable under the line forces in the roll gap” is made of a fiber-reinforced plastic (claim 14).
- the modulus of elasticity is different in the longitudinal direction and circumferential direction of the hollow roller, which can be achieved in the manner set out in claim 16.
- a roller with a hollow roller made of rubber-elastic material with reinforcing inserts emerges from DE-PS 25 22 657.
- the inserts are not arranged in three layers in the manner according to the invention, which has the purpose here of avoiding any stiffening sandwich effect with regard to bending in a plane passing through the axis.
- Fiber-reinforced plastics often do not always offer optimal sliding conditions on their outer surface. For this reason, it is advisable to provide a low-friction layer on the inner circumference of the hollow roller, which at the same time prevents the hydraulic Liquid is present directly against the resin material of the hollow roller and may therefore undergo chemical reactions in the long term.
- a coating made of an elastomeric material can be provided on the outside of the hollow roller in a manner known per se.
- FIG. 1 shows a schematic view of a roller according to the invention, partly in section
- Fig. 2 shows a cross section through the roller of Figure 1 along the line II-II.
- FIG. 3 shows an enlarged representation of the upper part of Fig. 2
- Fig. 4 shows a view of the upper part of the roller of Fig. 1, partly in section along the line IV-IV in Fig. 3;
- FIG. 5 shows a view according to FIG. 4 from above;
- FIG. 6 shows a top view of the sealing strip recognizable in FIG. 5 taken on its own;
- Fig. 7 shows a cross section along the line VII-VII on an enlarged scale
- FIG. 8 shows a section along the line VIII-VIII in Fig. 6; 9a), b) and c) and 10a), b) and c) show a comparison of the pressure conditions at the joints between successive support elements in a roller of the prior art and in a roller according to the invention on an enlarged scale.
- the roller designated 100 in FIG. 1 as a whole comprises a hollow roller 1, which is penetrated lengthwise by an non-rotatable crosshead 2, which leaves all around distance from the inner circumference 3 of the hollow roller 1 and at the projecting ends 2 'in a manner not shown in is supported on a roll stand or in the wings of a calender.
- the hollow roller 1 is rotatably supported at its ends on bearings 4 on the crosshead 2.
- you Outer circumference 5 forms the working roller circumference, which cooperates in a roll nip 7 located at the top in the exemplary embodiment with a counter-roller 8, which is only indicated, in order to subject a paper web or the like (not shown) to a smoothing or similar treatment.
- the hollow roller 1 can optionally also have a cover 9 made of elastomeric material, for example a suitable plastic, as indicated at the bottom right in FIG. 1, the outer circumference 6 of which then forms the working roller circumference.
- the hollow roller 1 itself consists of a fiber-reinforced plastic tube which, with the usual roller diameter of 40 to 60 cm, has a wall thickness of 15 to 20 mm and has a smooth, low-friction pressure-fluid-tight coating on the inner circumference 3.
- Each support element 10 consists of an annular piston 12 and a support element body 20.
- the annular pistons 12 have a cylindrical outer circumferential surface 13 and a cylindrical inner surface 14 coaxial with their axis A. They are on the flattened upper side 2 "of the crosshead 2 with axis A perpendicular to this arranged in a row running in the longitudinal direction of the roller 100.
- the support element body 20 has on its side Transverse head 2 facing underside a cylinder bore 15 which cooperates with the cylindrical outer circumference 13 of the annular piston 12 via seals 16 (FIG. 4).
- a cylindrical shoulder 17 coaxial with the axis A extends down to the lower edge of the support element body 20, which cooperates with the cylindrical inner circumference 14 of the annular piston 12 via a seal 18.
- the support element body 20 can thus be displaced relative to the ring piston 12 in the direction of the axis A, a cylinder chamber 21 being formed below the cylindrical projection 17 and a cylindrical ring chamber 22 being formed above the ring piston 12.
- the expansion of the support element bodies 20, to which zones in the longitudinal direction of constant force application correspond in the configuration shown, is limited.
- the support element bodies 20 are therefore generally no longer than 20 cm and can have a shorter length of up to approximately 10 cm, with roller lengths of the order of 4 to 10 m. These support element bodies 20 follow one another as closely as possible and thus form a finely divided row of separately controllable force application points.
- Two types of supply lines for pressure fluid are provided in the crosshead 2, each of which comprises a supply line 23 for each support element 10 for supplying the storage pockets to be described and a supply line 24 which opens into the cylinder chamber 21.
- the feed line 23 is connected via a non-throttling channel 25 in the annular piston 12 to the annular chamber 22, of which in the exemplary embodiment two non-throttling channels 26, which lie one behind the other in the longitudinal direction of the roller 100, run on the upper side 20 'of the support element body 20 .
- the feed lines 23 can be connected to a common feed channel of larger cross section in the crosshead 2.
- the entirety of these lines forms the supply system 11 shown in simplified form in FIG. 2.
- a channel 27 is also provided in the cylindrical extension 17, which opens into the cylinder chamber 21 and is closed at the upper end except for branch lines 28, in which throttling points 29 are arranged (FIG. 3).
- the top 20 ′ of the support element body 20 facing the inner periphery 3 of the hollow roller 1 is curved with a somewhat smaller radius than the inner periphery 3 of the hollow roller 1, so that it maintains a uniform distance of a few millimeters from the inner periphery 3.
- circular stabilization pockets 50 are provided, into which the branch lines 28 lead and which are surrounded by a circular edge 51, the top of which is shaped corresponding to the inner circumference 3 of the hollow roller 1 and bears there in a sealing manner.
- the support element bodies 20 furthermore have rectangular grooves 31 of a width 32 which are aligned with one another in the longitudinal direction of the roller 100 and which receive a sealing strip 30 which in the exemplary embodiment is integral with all of the support elements 10 present.
- a bearing pocket 33 in the form of a flat rectangular depression is provided above each support element 10, which is delimited by longitudinal edges 34 on the longitudinal edges of the sealing strip 30 and by transverse edges 35 which are arranged at the level of the joints St between the support element bodies 20 of successive support elements 10.
- the top of the edges 34, 35 is shaped in accordance with the inner circumference 3 of the hollow roller 1, so that the edges 34, 35 can rest against the inner urafang 3 of the hollow roller 1.
- the sealing strip 30 has non-throttling perforations 19 on each support element 10, which pass from the respective storage pocket 33 to the underside 30 ′′ of the sealing strip 30 and with the channels 26 in the top 20 ′ of the respective support element body 20 are aligned.
- the transition area is sealed by an O-ring 19 'surrounding it, so that the pressure fluid cannot escape between the upper side 20' of the support element 20 and the lower side 30 "of the sealing strip 30.
- the stabilization pockets 50 are supplied with the throttle point 29 via the branch lines 28.
- the pressure fluid supplied to the inside of the stabilization pockets 50 flows outwards via the edge 51. If the distance is increased, the outflow cross section is increased and the pressure drops because of the throttle point 29.
- the stabilization pocket 50 in question then approaches the inner circumference 3 of the hollow roller 1 again, as a result of which the outflow cross-section drops and the pressure increases. In this way, an equilibrium is established, the edge 51 automatically being kept at a certain small distance from the inner circumference 3 of the hollow roller 1 and remaining separated from the inner circumference 3 by a supporting liquid film.
- This function is performed by all four stabilization pockets 50 which can be seen in FIG. 5, so that the support element body 20, which is held a little wobble on the seals 16, 18 and can adjust its position relative to the inner circumference 3 of the hollow roller 1, always in one defined position relative to the inner circumference 3 is held.
- the upper sides of the edges 51 and 34, 35 are designed so that they are all located on a common cylinder surface, which corresponds to the inner circumference 3 of the hollow roller 1.
- the pressure fluid supplied to the bearing pockets 33 flows outward in the circumferential direction via the longitudinal edges 34, because a gradient between the pressure in the bearing pockets 33 and the pressure prevailing on the outer edge of each longitudinal edge 34 in the space Z between the Inner circumference 3 of the hollow roller 1 and the crosshead 2.
- Fig. 3 and on the right-hand sides of Figs. 4 and 5 a modification is indicated, the flat support chamber 40 of a few worked out in a under the respective storage pocket 33 in the bottom of the groove 31 on the top 20 'of the respective support element body 20 Millimeter depth.
- the support chamber 40 has an essentially rectangular plan and an active surface which corresponds at least to the active surface of the associated storage pocket 33 and is rather a little higher.
- a storage pocket 33 and a support pocket 40 arranged underneath each other are therefore assigned to one another one above the other.
- the O-rings 19 ' are omitted at the transition points of the channels 26 and the perforations 19, and instead a closed seal 40' runs all around the respective support pocket 40.
- the channels 26 thus open into the support pocket 40 and the perforations 19 also proceed from the support pocket 40. In this way, the support pocket 40 fills with pressure fluid under the same pressure as the bearing pockets 33.
- the sealing strip 30 “floats” on the pressure fluid in the support pocket 40 and can be particularly easily positioned in the inner circumference 3 of the hollow roller 1 adjust.
- the seal 40 ' is a cord seal or a lip seal, which remains tight with the slight possible displacements of the sealing strip 30 relative to the respective support element body 20.
- Each bearing pocket 33 has the two perforations 19 on the bottom, which open out into the bearing pocket 33 with a step-like extension 19 ′′ and are aligned with the channels 26 in the support element body 20.
- each bearing pocket 33 has its own longitudinal edges 34, the transverse edges 35 jointly have successive bearing pockets 33, 33 in the longitudinal direction of the roller. sam and are formed by a single closed web, as can be seen from Fig. 8.
- the support element bodies 20 are pressed against the inner circumference 3 of the hollow roller 1 under the force of the pressure fluid present in the cylinder chamber 21, the support element bodies 20 not abutting the inner circumference 3 directly but via the sealing strip 30.
- transverse groove 36 which is introduced from the underside 30 ′′ of the sealing strip 30 and which extends to about half the thickness of the sealing strip 30 (FIG. 8). Above the transverse groove 36, however, the transverse edge 35 bridges the abutment St between the individual support elements 10.
- the transverse grooves 36 are not shown in FIG. 5.
- 9 shows the prior art, in which support elements 110 and 110 'follow one another in the longitudinal direction of the roller.
- the support elements 110, 110 'each have bearing pockets 33, which are delimited by longitudinally running edges and transverse edges 135, 135'.
- Each bearing pocket 33 thus has its own transverse edges 135 and 135 ', which are directly adjacent to one another at the joint St, but leave a gap 136 between them which is connected to the intermediate space Z.
- FIG. 9b shows the course of the pressure in the pressure fluid. It has the value P 33 in the area of the bearing pockets 33, which in the exemplary embodiment is the same in the two successive bearing pockets 33.
- the pressure fluid flows out of the respective storage pocket 33 out over the transverse edges 135 or 135 ′ into the gap 136.
- the pressure of the intermediate space Z prevails in the gap 136, ie the pressure is zero or in any case a lower pressure than in the bearing pockets 33 Transverse edges 135, 135 'therefore the pressure drops in the longitudinal direction of the roller in accordance with curves P 135 and P 135 . to the value P 136 .
- a pressure drop corresponding to FIG. 9b thus results at the joint St.
- FIG. 10 shows the embodiment according to the invention modified by the sealing strip 30.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Rolls And Other Rotary Bodies (AREA)
- Treatment Of Fiber Materials (AREA)
- Food Preservation Except Freezing, Refrigeration, And Drying (AREA)
- Treatments Of Macromolecular Shaped Articles (AREA)
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP97932720A EP0912836B2 (de) | 1996-07-25 | 1997-07-02 | Walze für die druckbehandlung einer bahn |
US09/230,402 US6045492A (en) | 1996-07-25 | 1997-07-02 | Web pressing roller |
JP50836598A JP3263087B2 (ja) | 1996-07-25 | 1997-07-02 | ウェブの圧力処理用のロール |
DE59701274T DE59701274D1 (de) | 1996-07-25 | 1997-07-02 | Walze für die druckbehandlung einer bahn |
CA002261983A CA2261983C (en) | 1996-07-25 | 1997-07-02 | Web pressing roller |
AT97932720T ATE190701T1 (de) | 1996-07-25 | 1997-07-02 | Walze für die druckbehandlung einer bahn |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19629967.5 | 1996-07-25 | ||
DE19629967A DE19629967C2 (de) | 1996-07-25 | 1996-07-25 | Walze für die Druckbehandlung einer Bahn |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1998004844A1 true WO1998004844A1 (de) | 1998-02-05 |
Family
ID=7800762
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE1997/001388 WO1998004844A1 (de) | 1996-07-25 | 1997-07-02 | Walze für die druckbehandlung einer bahn |
Country Status (7)
Country | Link |
---|---|
US (1) | US6045492A (de) |
EP (1) | EP0912836B2 (de) |
JP (1) | JP3263087B2 (de) |
AT (1) | ATE190701T1 (de) |
CA (1) | CA2261983C (de) |
DE (2) | DE19629967C2 (de) |
WO (1) | WO1998004844A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002048559A1 (en) * | 2000-12-14 | 2002-06-20 | Metso Paper, Inc. | Deflection-comprensated roll |
US7482757B2 (en) | 2001-03-23 | 2009-01-27 | Tokyo Electron Limited | Inductively coupled high-density plasma source |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1162045B1 (de) * | 2000-05-30 | 2007-03-14 | Andritz Küsters GmbH & Co. KG | Walzenvorrichtung |
DE10239097A1 (de) * | 2002-08-26 | 2004-03-11 | Voith Paper Patent Gmbh | Biegeausgleichswalze |
FI119521B (fi) * | 2006-08-28 | 2008-12-15 | Metso Paper Inc | Kuiturainakoneen tela |
ITTO20110444A1 (it) * | 2011-05-19 | 2012-11-20 | Tecnau Srl | "equipaggiamento per perforazioni trasversali di lunghezze variabili su moduli continui in movimento" |
DK3577361T3 (da) * | 2017-03-16 | 2021-01-25 | Siemens Gamesa Renewable Energy As | Glidelejepudestøtte |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2502161A1 (de) * | 1975-01-21 | 1976-07-29 | Voith Gmbh J M | Presswalze fuer papiermaschinen zur erzeugung eines liniendruckes |
DE2522657A1 (de) * | 1975-05-22 | 1976-11-25 | Continental Gummi Werke Ag | Walze zur druckbehandlung von bahnfoermigen materialien |
DE3528333A1 (de) * | 1985-08-07 | 1987-02-19 | Kuesters Eduard | Walze |
DE9205796U1 (de) * | 1992-04-30 | 1993-08-26 | Eduard Küsters Maschinenfabrik GmbH & Co KG, 47805 Krefeld | Walze mit Stützleiste |
DE9314568U1 (de) * | 1993-09-27 | 1995-02-02 | Eduard Küsters Maschinenfabrik GmbH & Co KG, 47805 Krefeld | Walze |
DE19527225A1 (de) * | 1995-07-26 | 1997-01-30 | Kuesters Eduard Maschf | Walze oder Stützelement für eine Walze |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AT360831B (de) * | 1977-12-20 | 1981-02-10 | Escher Wyss Ag | Hydraulisches stuetzelement |
DE3820974C3 (de) † | 1988-06-22 | 1996-03-21 | Kuesters Eduard Maschf | Dichtungsglied bzw. Walze |
DE3909911C1 (de) * | 1989-03-25 | 1990-06-07 | Kleinewefers Gmbh, 4150 Krefeld, De | |
DE3925019A1 (de) * | 1989-07-28 | 1991-02-07 | Voith Gmbh J M | Durchbiegungs-ausgleichswalze fuer walzenpressen |
DE4012439C1 (de) * | 1990-04-19 | 1991-10-17 | Eduard Kuesters Maschinenfabrik Gmbh & Co Kg, 4150 Krefeld, De | |
EP0537315B1 (de) * | 1991-05-03 | 1996-09-25 | Voith Sulzer Papiermaschinen GmbH | Durchbiegungseinstellwalze und deren verwendung |
DE4239411C1 (de) * | 1992-09-04 | 1993-09-02 | Sulzer-Escher Wyss Ag, Zuerich, Ch | |
FI97565C (fi) * | 1995-02-22 | 1997-01-10 | Valmet Paper Machinery Inc | Menetelmä paperikonetta tai vastaavaa varten tarkoitetun putkimaisen telan telavaipan liukulaakeroimiseksi ja menetelmää soveltava putkimainen tela |
FI98320C (fi) * | 1994-03-09 | 1997-05-26 | Valmet Paper Machinery Inc | Menetelmä paperikonetta tai vastaavaa varten tarkoitetun putkimaisen telan telavaipan liukulaakeroimiseksi ja menetelmää soveltava putkimainen tela |
DE4429499C1 (de) * | 1994-08-19 | 1995-11-16 | Kleinewefers Gmbh | Durchbiegungssteuerbare Walze für einen Kalander o. dgl. |
DE4430268C1 (de) * | 1994-08-26 | 1995-11-02 | Kleinewefers Gmbh | Durchbiegungssteuerbare Walze für einen Kalander o. dgl. |
DE4444892C2 (de) * | 1994-12-16 | 1997-04-24 | Voith Sulzer Papiermasch Gmbh | Preßwalze |
-
1996
- 1996-07-25 DE DE19629967A patent/DE19629967C2/de not_active Expired - Fee Related
-
1997
- 1997-07-02 EP EP97932720A patent/EP0912836B2/de not_active Expired - Lifetime
- 1997-07-02 WO PCT/DE1997/001388 patent/WO1998004844A1/de active IP Right Grant
- 1997-07-02 CA CA002261983A patent/CA2261983C/en not_active Expired - Fee Related
- 1997-07-02 US US09/230,402 patent/US6045492A/en not_active Expired - Fee Related
- 1997-07-02 JP JP50836598A patent/JP3263087B2/ja not_active Expired - Fee Related
- 1997-07-02 DE DE59701274T patent/DE59701274D1/de not_active Expired - Lifetime
- 1997-07-02 AT AT97932720T patent/ATE190701T1/de not_active IP Right Cessation
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2502161A1 (de) * | 1975-01-21 | 1976-07-29 | Voith Gmbh J M | Presswalze fuer papiermaschinen zur erzeugung eines liniendruckes |
DE2522657A1 (de) * | 1975-05-22 | 1976-11-25 | Continental Gummi Werke Ag | Walze zur druckbehandlung von bahnfoermigen materialien |
DE2522657C3 (de) * | 1975-05-22 | 1979-03-01 | Continental Gummi-Werke Ag, 3000 Hannover | Walze zur Druckbehandlung von bahnförmigen Materialien |
DE3528333A1 (de) * | 1985-08-07 | 1987-02-19 | Kuesters Eduard | Walze |
DE3528333C2 (de) * | 1985-08-07 | 1989-01-19 | Kuesters, Eduard, 4150 Krefeld, De | |
DE9205796U1 (de) * | 1992-04-30 | 1993-08-26 | Eduard Küsters Maschinenfabrik GmbH & Co KG, 47805 Krefeld | Walze mit Stützleiste |
DE9314568U1 (de) * | 1993-09-27 | 1995-02-02 | Eduard Küsters Maschinenfabrik GmbH & Co KG, 47805 Krefeld | Walze |
DE19527225A1 (de) * | 1995-07-26 | 1997-01-30 | Kuesters Eduard Maschf | Walze oder Stützelement für eine Walze |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002048559A1 (en) * | 2000-12-14 | 2002-06-20 | Metso Paper, Inc. | Deflection-comprensated roll |
US7482757B2 (en) | 2001-03-23 | 2009-01-27 | Tokyo Electron Limited | Inductively coupled high-density plasma source |
Also Published As
Publication number | Publication date |
---|---|
JP2000503751A (ja) | 2000-03-28 |
DE19629967C2 (de) | 2002-04-11 |
CA2261983C (en) | 2005-09-13 |
DE59701274D1 (de) | 2000-04-20 |
CA2261983A1 (en) | 1998-02-05 |
EP0912836B1 (de) | 2000-03-15 |
EP0912836A1 (de) | 1999-05-06 |
US6045492A (en) | 2000-04-04 |
JP3263087B2 (ja) | 2002-03-04 |
EP0912836B2 (de) | 2004-09-08 |
DE19629967A1 (de) | 1998-03-05 |
ATE190701T1 (de) | 2000-04-15 |
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