FI123283B - Adjustable sheath roll, hardware and method - Google Patents

Description

WEATHER THROUGH THE CUTTING DRIVE, THE APPARATUS AND THE METHOD VALS MED JUSTERBAR MANTEL, ANORDNING OCH FÖRFARANDE

FIELD OF THE INVENTION

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The invention relates to an adjustable sheath roll and belt wrapping apparatus used in fiber web machines. In particular, but not exclusively, the invention relates to a deflection compensated roll suitable for use in a press and dryer section of a papermaking machine for transferring heat to a metal belt and / or paper, and a method of using a deflection compensated roll.

BACKGROUND OF THE INVENTION

In a deflection compensated floating roll, a jacket is arranged to rotate over the fixed shaft of the roll, which is loaded by introducing pressure oil into the pressure chamber between the shaft and the jacket to correct the deflection of the roll jacket. Oil used for pressurizing the roll has been used to heat the floating roll. Deflection compensated floating rollers have been manufactured under the brands SymRoll, EcoNip and S-Roll, for example. US 5,244,448 discloses a 20 deflection compensated floating roll. Typically floating rollers have been used on narrow and slow paper machines up to 1300 m / min.

Oil-loaded floating rollers have been limited in some applications by a limited rotation speed. As the rotation speed increases, e.g. to bathe

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o The oil-based friction of the 25 oil-loaded rollers increases and the roller requires a large amount of power.

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x As paper yields increase, paper production will continue

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wider and faster paper machines, whereby the speed of rotation of the floating deflection rolls used in the press section and the drying section of the O) ra 30, for example, is not desired to limit the process in the high speed range over 130000 meters per minute.

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US 5,725,465 discloses an air-loaded deflection compensated floating roll.

WO 03064762 discloses a metal belt calender. A deflection compensated roll is used as the outer roll of the metal belt loop 5 and / or the inner roll of the belt ring pressed against the outer roll. Particularly in a wide metal belt calender, it has proved challenging to compensate for the difference in tension and speed between the edge and the center of the metal belt and to control the metal belt. Metal belt calendars are manufactured under the brand VaIZone.

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Instead of the traditional thermal roller, a more cost-effective way of heating the metal belt provided on the press section is desired.

The rollers of the drying cylinder are large in size and take up a lot of space. 15 It has been suggested to use a metal belt for the drying section as a way of transferring heat. The use of a drying cylinder as a heat transfer medium for a metal belt has not been found to be widespread.

With peripheral drilled thermal coils, the cost is high and 20 peripheral drilled thermal coils are difficult to manufacture.

SUMMARY

According to a first aspect of the invention there is provided a roll which comprises

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o 25 longitudinal seals and end seals disposed between the shaft and the shaft to form a first pressure chamber and a second pressure chamber, the roll being x pressure medium for the first pressure chamber and / or the second pressure chamber

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by conducting the load to control the diaphragm deflection, and the amount and direction of the total load exerted internally on the diaphragm by o § 30 to determine the pressure in the first pressure chamber and in the second

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the difference in the loads caused by the pressure in the pressure chamber, and the pressure medium is superheated steam which must be heated by passing at least one of said 3 pressure chambers.

In another aspect of the invention, an apparatus is provided comprising a deflection compensated roll according to any aspect or embodiment of the invention.

The roll axis may be a hollow, preferably a tubular axis.

The roll shell thickness may be 15 to 50 mm, preferably 30 mm.

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Preferably, the at least one longitudinal seal comprises a bypass arrangement for steam.

The apparatus may comprise an endless metal belt against which is provided a roll deflection adjustable sheath to compensate for the difference in width tension 15 of the metal belt.

Preferably, in the apparatus, the roll jacket is disposed against the metal belt or fiber web to transfer heat to the metal belt and / or fiber web.

The apparatus may comprise an endless metal belt and at least one deflection compensated roll as a belt guide roll which may be heated.

The apparatus may be part of a dryer section of a fiber web machine in which at least one roller may be replaced with at least one drying cylinder, respectively, wherein the roller diameter

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o 25 be substantially smaller than the diameter of the replaced drying cylinder.

According to a third aspect of the invention, there is provided a fiber web machine

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x a press member comprising any aspect of the invention or

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a roll or apparatus according to an embodiment.

According to a fourth aspect of the invention, there is provided a fiber web machine

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a drying member comprising a roll or apparatus according to any aspect or embodiment of the invention.

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According to a fifth aspect of the invention, there is provided a method of operating a roll comprising a hollow shaft rotatably mounted on a fixed shaft and a longitudinal seal 5 and end seals disposed between the shaft and the shell to form a first pressure chamber and a second pressure chamber. introducing a second pressure chamber for adjusting the diaphragm deflection, and the method determining the amount and direction of the total load exerted by the pressure medium internally by the difference between the pressures in the first pressure chamber and the pressure in the second pressure chamber;

Preferably, the method comprises fitting the roll sheath against an endless metal belt to guide the metal belt and adjusting the deflection of the roll shell to compensate for the endless tension differences of the endless metal belt.

A pressure difference of 8 bar can be provided between the first pressure chamber of the roll and the second pressure chamber, whereby a linear load of 350 kN / m can be achieved on the roll. A pressure difference of 2 bar can be provided between the first pressure chamber of the roll and the second pressure chamber, whereby a line load of 100 kN / m can be achieved.

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o 25 The roller and / or equipment may be used in different parts of a fiber web machine such as a paper machine, a paperboard machine, and a pulp machine. The roll and / or hardware can be used in i cvj deflection compensation solutions. The roll can be used in particular with a metal belt x. The roll is well suited as a deflection compensation solution for use with a metal belt, so that, for example, the difference in tension and velocity o caused by the bending of the rolls, particularly between the wide metal belt edge and the center of § 30, can be compensated and guided appropriately. The roller can

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in addition, achieve a good and economical heat transfer to the metal belt or paper web. The roll can be manufactured more cost-effectively than 5 peripherally drilled rolls. The roll and / or the apparatus may be used in a press and dryer section, and preferably in low calorie calenders. The roller can also be used instead of a drying cylinder. With the help of deflection compensation, the diameter of the roll casing may be substantially smaller than the current diameter of the drying cylinders 5. In some cases, the roller may be operated at higher speeds than current deflection compensated rollers. Thus, there is no speed limit due to the deflection compensated roll in the fiber web manufacturing process. Other advantages will be apparent from the following description and claims.

Various embodiments of the present invention will be described or described only in connection with one or more aspects of the invention. One skilled in the art will appreciate that any embodiment of an aspect of the invention may be applied to the same and other aspects of the invention, alone or in combination with other embodiments.

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BRIEF PRESENTATION OF THE PATTERNS

The invention will now be described, by way of example, with reference to the accompanying drawings, in which: Figure 1 shows a deflection compensated roll which can be heated by steam; Fig. 2 is a cross-sectional view of the roll of the type of Fig. 1 in the end region of the roll; Fig. 3 shows a roll of the type of Fig. 1 disposed outside the metal belt cycle as a deflection compensated roll; Figures 4 to 7 show some cross-sectional views of the roll of type 1 roll of B-B in the central region of roll 0 25; and ό Figs. 8 and 9 show a roll of the type of Fig. 1 as a belt guide roll for a metal belt cycle i cm.

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DETAILED EXPLANATION

O) CO 30 m § In the following description, like reference numerals refer to the same

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like parts. It is to be noted that the figures shown are not to scale in their entirety and that they serve primarily the purpose of illustrating embodiments 6 of the invention.

Fig. 1 is a partially sectional side view of a floating deflection adjustable roll 1 comprising a stationary shaft 2 and a rotatable sleeve 3. The shaft 2 is supported 5 at its ends 2.1 on the outer structure of the roll 1 to allow bending 5 of the shaft 2 and the sleeve 3. The jacket 3 is fitted at its end ends 3.1 to the end bearings 4 which are fitted to the shaft ends 2.1. The sheath 3 comprises a sheath surface 3.2 that can be adjusted to the desired curvature. By means of the sheath surface 3.2, the deflection compensation movement 3 'of the roll 1 can be transferred to another processing element of the fibrous web 10 such as nip roll 12 or the metal belt 11. The sheath 3 deflects under load from the roll, belt or fibrous web;

15 The deflection adjustable roller 1 can be loaded and heated with superheated steam. The use of roller 1 makes it possible to increase the speed of rotation of the heated floating roll, since, when applied with steam, the internal friction of the heating and pressure medium does not increase significantly as the speed of rotation increases. Roller 1 is competitive in energy consumption compared to fluid-loaded heated floating rollers 20.

The shaft 2 and the housing 3 are sealed to one another by means of the longitudinal seals 8 so that between the outer surface 2.2 of the shaft 2 and the inner surface 3.3 of the shell 3, the longitudinal seals 8 define the first pressure chamber 6 and the second pressure chamber 7.

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The 25 is secured to the shaft 2 by means of grooves edullisesti arranged on opposite sides of the shaft 2. The longitudinal seals 8 allow the rotational movement of the diaper 3 and the bending movement i cvj to suitably keep the pressure chambers 6, 7 tight.

x The first 6 and the second 7 pressure chambers are shown in oblique lines.

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The first and / or second pressure chambers may be subdivided into subchambers which each form a series of chambers (not shown).

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In the end region 3.1 of the sheath 3, the roll 1 comprises end seals by means of which the pressure chambers 6 and 7 are sealed in a manner allowing rotation and bending of the sheath 3. In the example of Figure 1, the end sealing of the first pressure chamber 6 is accomplished at both ends of the housing 3 by first end seals 9 fitted to the center faces of the shaft 2, and the second pressure chamber 7 comprises similar second seals 10 as the first 5 seals 9 of forming a single end seal. The end seals 9 and 10 are pressurized to the longitudinal seals 8. The end seals 9, 10 rotate the shaft ends fixed to the center of the shaft 2. Sealing flanges 11 are attached to the end areas 3.1 of the shell 3 on the inside of the bearings 4, against which the end seals 9, 10 of the first and second 10 are pressurized. The sealing flange 11 has a central hole through which the shaft end 2.1 is arranged to travel in a manner allowing for a change in the distance between the shaft 2 and the shell 3.

In some embodiments, the longitudinal seals 8 are arranged to leak 15 intentionally. For example, if the roller 1 is not heating critical, then the minimum flow of pressure vapor fed into one pressure chamber into the other pressure chamber can be implemented as a controlled seal leakage, i.e., bypass flow of the seal. Thereby, at least one longitudinal seal 8 comprises a bypass arrangement for steam. The seal leak may be realized from the first pressure chamber 6 to the second pressure chamber 7 or from the second pressure chamber 7 to the first pressure chamber 6.

The leakage of the end seals 9,10 is preferably prevented to prevent condensation and steam from entering the oil lubrication of the bearings 4.

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o 25 Condensation condensing from steam acts as a lubricant for seals 8, 9, 10 when rotating the diaphragm 3 ό.

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C \ l x The main types of seals 8, 9, 10 of the present floating deflection roller 1

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possible structures include abrasive molds and membrane seals.

O) co 30 Optionally, a fixed sealing strip 8 or 9 or 10 fitted to the roller 1 is preferably provided with a load to ensure sealing. optionally

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the fixed sealing strip 8 or 9 or 10 fitted to the roller 1 is preferably provided with an adjustment to ensure sealing. Optionally, the fixed 8 projection sealing strip 8 or 9 or 10 fitted to the roll 1 may be sufficiently flexible to assist in sealing the seal, as well as the diaphragm seal structure optionally fitted to the roll 1, assisted by a differential pressure.

The longitudinal seals 8 and the end seals 9, 10 preferably comprise a water-resistant material to maintain good seal properties despite the high temperature and the presence of water, and to avoid harmful water absorption into the seals. Water absorption into the seals can result in boiling water in the seal and breaking the seal structure.

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In some embodiments, the longitudinal seal between the first pressure chamber 6 and the second pressure chamber 7 may comprise at least one longitudinal seal 8, for example two parallel seals. In some embodiments, one longitudinal seal 8 is provided between the first pressure chamber 6 and the second pressure chamber 7, which may comprise sealing shapes directed towards the inner surface 3.3 of the diaper 3, for example sealing lips, in the direction of each pressure chamber 6, 7.

The pressure difference 20 between the first pressure chamber 6 and the second pressure chamber 7 defines the direction in which the deflection of the diaper 3 is controlled by the pressure of the pressure medium. If the pressure of the steam supplied to the first pressure chamber 6 is adjusted sufficiently higher than the pressure of the steam in the second pressure chamber 7, the distance of the sheath 3 from the shaft 2 increases in the middle region of the roll 1, i.e. Pressure chambers 6

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The pressure difference between 0 25 and 7 suitably influences the ό frictional forces between the counter force diaper 3 and the seals 8, the movable mass of the diaper 3 and any forces exerted by the roll and / or fibrous web and / or belt on the diaper 3.

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The roller 1 may be supplied with steam, for example, through a first shaft end, and the steam 30 may be discharged, for example, through a second shaft end. The roller 1 is provided with means for circulating the steam acting as a heated pressure medium into the roller

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1 in and 1 out of roll. When steam is supplied to the pressure chamber 6 inside the shell 3 of the roll 1; 7, the steam forms condensate when it releases heat to the jacket 9 3. Liquid condensate water can be collected from the inner walls 3.3 of the jacket 3, from which the longitudinal seals 8 scrape the condensate. The condensate may be removed from the inside of the pressure chamber in any known manner. For example, the condensate may be sucked in or blown off by pressure on the roller 1. The condensate may be introduced outside the roll 1 by the same or different paths as the steam flowing out of the roll pressure chamber.

The internal pressure of the first pressure chamber 6 and the second pressure chamber 7 of the roller 1 is preferably not more than 10 bar, which corresponds to the usual maximum pressure of an industrial pneumatic network. In some cases, the pressure of the pressurized steam may be replaced by the air pressure of the compressed air network, for example, in a pressure chamber test.

In some cases, the pressure difference between the first pressure chamber 6 and the second pressure chamber 7 is 8 bar, whereby a line load of, for example, 350 kN / m can be achieved on the roller 1. In some design cases, a pressure difference of 2 bar between the first pressure chamber 6 and the second pressure chamber 7 can achieve a line load of 100 kN / m, which corresponds to the line load achieved with some soft calenders. The roller 1 can be applied particularly advantageously in a bending compensation solution for metal belt rotation. As an example, a metal belt calender has a belt tension of about 100 kN / m.

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Fig. 2 shows an end direction roll 1, in particular a cross sectional view AA of Fig. 1, showing end seal 9, 10 of pressure chambers 6 and 7 located in the end region of roll 3 of roll 1. 2.3 boundaries

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δ 25 hollow state. The tubular construction can save the material costs of the shaft 2 and

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ό The weight of the shaft 2 can be low. It is also possible to utilize the hollow interior space 2.3 of the tube 2 in the steam inlet and outlet arrangements.

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The sheath 3 may be formed of steel such as stainless or O) § 30 corrosion resistant material. The sheath 3 may be made of Duplexes material or Duplex LDX material.

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The sheath 3 may be designed to be particularly thin, e.g. about 30 mm thick, such that the sheath 3 can withstand vapor pressure loads and applications such as nip or belt twisting. Floating deflection adjustable rolls have traditionally had a shell thickness of 50-100 mm, which is not intended to be limited by the invention, but the shell 3 may have a much smaller thickness, for example 15-50 mm, preferably 5 30 mm.

Fig. 3 shows a deflection compensated and heated roll 1 of the type of Fig. 1 disposed outside the first metal belt assembly 30. The metal belt assembly 30 comprises an endless metal belt 11 which is arranged to be rotated through the belt guide rollers 13, in a simple case, outside the belt guide rollers 13. The metal belt 11 may be arranged to travel inside and out of the belt guide rollers 13. The deflection compensated roll 1 is arranged to form a heat treatment nipple N1 on the fibrous web W which is introduced into the metal belt assembly 30 on the surface of the metal belt 11 15 passing through the belt guide roll 13 before the deflection compensated roll 1 The nip roll 12 shown by a dotted dash line may be arranged to provide a line load against the roll 1 at the long nip area N1 inside the metal belt 11.

The curvature of the diaper 3 of the deflection compensated roll 1 can be adjusted as desired. By adjusting the curvature of the sheath 3, it is possible to compensate for the difference in tension and speed between the edge and the center of the metal belt and to guide the metal belt in a suitable manner. By adjusting the curvature of the sheath 3, it is possible to compensate for the unevenness of the line load due to the deflection of the rolls 1, 12 and to adjust the deflection line to the desired shape.

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δ 25 Furthermore, a good and economical heat transfer can be achieved with roller 1

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ό fiber web. The roll can be manufactured more cost-effectively than an i cvj peripheral drilled roll. The roll can be used with a press and dryer section, and preferably with low heat calendars.

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Fig. 4-7 show some cross-sections B-B of deflection compensated rollers 1

o from the center of roll 1, o

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Fig. 4 shows a roll 1 with a metal belt 11 11 fitted on the outer surface 3.2 of the sheath 3. The roll 1 and the metal belt 11 form part of an apparatus 20 for handling the fibrous web W. The roller 1 can achieve a good and economical heat transfer to the metal belt 11 and / or the fibrous web web W guided to the processing nip formed between the shell 3 and the metal belt 11. Roll 1 can be fabricated 5 more cost-effectively than peripheral drilled rolls for heat transfer applications. The roller 1 can be used with a press and dryer section, and preferably with low heat calendars. The roller 1 can also be used instead of a drying cylinder. With the help of deflection compensation, the diameter of the shell 3 of the roll 1 may be substantially smaller than the current diameter of the drying cylinders. The deflection of the drying cylinders 10 is prevented by the large diameter of the drying cylinder. The deflection compensation can be used to adjust the shell 3 of the roll 1 to be straight or to the desired curvature. In Figure 4, the shaft 2 is formed of a solid material, for example by casting and machining steam flow channels (not shown) and attachment points for seals 8.

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Fig. 5 shows a roll 1 having a fiber web web W, such as a paper web, arranged on the outer surface 3.2 of the jacket 3. The roller 1 forms part of the apparatus 20 for handling the fibrous web W. The roll 1 can achieve a good and economical heat transfer to the fibrous web web W guided to run on the outer surface 3.2 of the rotating jacket 3. In addition, a belt may be provided on the fiber web web W to enhance heat transfer (not shown), which belt may be a metal belt or a belt of other material. Roll 1 can be manufactured more cost-effectively than peripheral drilled rolls for heat transfer applications. The roller 1 can be used with a press and dryer section, and preferably with low heat calendars. Roller 1 can be used

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0 25 also in place of drying cylinder. Due to the deflection compensation, the diameter 3 of the roll 1 of the roll 1 may be substantially smaller than the current diameter of the drying cylinders.

In Fig. 5, axis 2 is formed in a manner similar to Fig. 2.

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Figures 6 and 7 illustrate the directions of operation of a deflection compensated roller 10). In some cases, the roller 1 may also be used in angular positions that deviate from the directions of the figures o, for example at constant load.

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The load to be understood as a standard load on the roller 1 may be, for example, as a belt guide roller for the belt passage 11. In Fig. 6, the diaper 3 of roll 1 is loaded vertically upwardly by a differential pressure 12 between the first 6 and the second pressure chamber 7 so that the pressure prevailing in the first pressure chamber 6 is greater than in the second pressure chamber 7. by a differential pressure 5 vertically downwards so that the pressure in the second pressure chamber 7 is higher than in the first pressure chamber 6 when the tension of the metal belt 11 which presses the fibrous web W against the jacket 3 is 100 kN / m.

Fig. 8 illustrates an embodiment of a roll adjustable and heated roll 10 1 of the type of Fig. 1, wherein the rolls 1 are disposed inside belt second roller assembly 31 as belt guide rollers 1. The metal belt assembly 31 comprises an endless metal belt 11 The metal belt 11 may be arranged to pass 15 inside and out of said belt guide rolls 13.1. The deflection compensated rolls 1 may be arranged in an appropriate amount to compensate for the difference in tension and speed between the edge and center of the metal belt 11 and to control and heat the metal belt 11. The deflection compensated rollers 1 may be arranged as every other belt guide roll The metal belt assembly 31 comprises a nip roll 32 which forms with the metal belt 11 a heat treatment and / or nip N1 on the fibrous web W. The fibrous web W is introduced into the metal belt assembly 31 by a

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0 25 from metal belts 11 at guide roll 13 after nip N1. The deflection adjustable and heated roll 1 shown by the dotted dash line ό may be arranged against the nip roll i cm 32 at the long nip area N1 inside the metal belt 11.

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Fig. 9 illustrates an embodiment of a deflection compensated and heated roller 10 0) of the type of Fig. 8, wherein the rolls 1 are disposed inside the third metal belt assembly 33o as belt guide rollers 1. The deflection compensated rollers 1 are arranged

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in the metal belt cycle 11 as nip rolls 32 upstream of the nip roll 32 as deflection compensated and heated belt guide rolls 1. The dotted roll nip roll 12 may be arranged to provide line loading against nip roll 32 at the long nip area N1 inside the metal belt 11. The nip roll 32 shown in Figures 8 and 9 may be a thermal roll.

The foregoing description provides non-limiting examples of some embodiments of the invention. However, it will be apparent to one skilled in the art that the invention is not limited to the details set forth, but that the invention may be practiced in other equivalent ways.

Some features of the embodiments shown may be utilized without the use of other features. The foregoing description is to be construed as merely describing the principles of the invention and not limiting the invention. Thus, the scope of the invention is limited only by the appended claims.

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Claims (12)

1. Vais (1) comprising a fixed shaft (2) and a hollow sheath (3) rotatably arranged on the shaft, and longitudinal seals (8) and end seals (9, 10) are arranged between the shaft and the manifold to provide a first pressure chamber (6) and a second pressure chamber (7), and the roller (1) can be loaded by passing a pressure medium to the first pressure chamber (6) and / or the second pressure chamber (7) to adjust the deflection of the sheath (3), characterized by that the degree and direction of the total load caused by the interior of the manifold (3) with the pressure medium is determined by the difference between the pressure caused by the pressure in the first pressure chamber (6) and the pressure in the second pressure chamber (7), and the pressure medium is superheated meadow, the roller (1) can be heated by passing it to at least one of said pressure chambers (6, 7). Roll according to claim 1, characterized in that the shaft (2) is hollow, preferably a tube shaft. Roll according to claim 1 or 2, characterized in that the thickness of the sheath (3) is 15 - 50 mm, preferably 30 mm. 20 Roll according to any of claims 1 to 3, characterized in that at least one of the length seals (8) comprises a bypass arrangement for the meadow. An installation (20,30,31,33) comprising a deflection-compensated roller (1) CM and 25 according to any of claims 1-4 in o cm An installation according to claim 5, characterized in that the installation x (20,30,31,33) comprises an endless metal band (11) against which the deflection adjustable sheath (3) of the roller (1) is arranged to compensate for 0) co. In the width direction of the metal strip (11). CD o o CNJ Installation according to claim 5 or 6, characterized in that the sheath (3) of the roller (1) in the installation (20,30,31,33) is arranged against the metal strip (11) or a fiber web (W) for transferring heat to the metal strip. (11) and / or the fiber web (W). Installation according to any of claims 5-7, characterized in that the installation (31, 33) comprises an endless metal strip (11) and at least one deflection-compensated drum (1) as a strip control drum which is heated. Plant according to any of claims 5-8, characterized in that the plant (20) belongs to the drying portion of a fiber web machine, where at least one roller (1) in the corresponding manner replaces at least one drying cylinder and the diameter of the roller (1) is substantially smaller than the diameter of the drying cylinder. A fiber web press section comprising a roller (1) according to any one of claims 1-4 or a plant (20, 30) according to any of claims 5-9. 15 The fiber web machine dryer portion, comprising a roller (1) according to any of claims 1-4 or a plant (20, 30) according to any of claims 5-9. Method for using a roller (1), said roller (1) comprising a fixed shaft 20 (2) and a hollow sheath (3) rotatably arranged on the shaft, and longitudinal seals (8) and end seals are provided between the shaft and the manifold. (9, 10) to provide a first pressure chamber (6) and a second pressure chamber (7), and the roller (1) can be loaded by passing a pressure medium to the first pressure chamber (6) and / or the second pressure chamber (7). for adjusting the deflection CVJ and (3) deflection, characterized in that on the basis of the difference between the stresses caused by the pressure ό in the first pressure chamber (6) and the pressure in the second pressure chamber (7) in cvj, the degree and the direction of the total load x to be caused internally in the manifold with the pressure medium, and conducted superheated meadow CL as the pressure medium into at least one of said pressure chambers (6, 7) and 0) co. CD o o CVJ