FI120797B - Apparatus for a fiber web machine and a fiber web machine - Google Patents

Description

EQUIPMENT FOR FIBER MACHINE MACHINE AND ANORDNING FÖR EN FIBERBANAMASKIN FIBER MACHINE OCH EN FIBERBANAMASKIN

FIELD OF THE INVENTION

The invention relates to fiber web machines such as paper and board machines. In particular, but not exclusively, the invention relates to displacement of the centerline of a fiber web-pressing roll.

BACKGROUND OF THE INVENTION

Calendering generally aims to improve the properties such as smoothness and glossiness of a web material such as paper or board. In the calender, nipples are generally formed between a smooth-faced press roll, such as a metal roll, and a roll coated with a flexible coating, such as a polymer roll. In calendering, the web is guided to a nip formed between rolls to be pressed against each other, i.e. a calendering nip, in which the web is deformed by the action of temperature, humidity and nip pressure. The flexible surface roll conforms to the surface contours of the web and press the web uniformly against the opposing flat surface 20 of the press roll.

··· • · · · · · *

In multi-roll calendars, i.e. calendars in which the roll rolls are formed with at least one roll, usually a roll stack, the calendering nips are formed between two adjacent rolls, usually a thermal roll and a polymer roll. The multi-roll calenders • · · **!; * 25 thus comprise one or more rolls, whereby one roll is formed by at least • * ***** two roll rolls. Most commonly in multi-roll calendars, track systems,. is formed such that the S * * iS line passing through the center lines of the end roll axes is straight. The track position can vary from vertical to 0 ° to 90 °.

In this context, calender rolls refer to calendering nip forming rolls, the top roll being the top roll of the roll, the lower roll being the roll *; * ': the bottom roll, the top nipple top calender nip, bottom nipper means the lowest calender nip of a roller set between the lower roller and the calender roller adjacent to the lower roller 2. Intermediate nipples mean the calendering nip formed between the top and the bottom of the calender by means of calender rolls. Intermediate rolls refer to calender rolls in the track between the upper and lower rollers. The nip rolls herein refer to rolls intended to compress the fibrous web in the nip formed between the nip rolls 5.

Line loading generally increases in multi-nip calendars from the top nip to the bottom nip due to the earth's attraction. In order to eliminate this downward pressure on the line, to control the roll deflection as well as to quickly open the roll, the current multi-nip calendars use roller-compensating roll relief provided by a cylinder and a lever mechanism. One such roller lightening system is found in OptiLoad ™ and Twinline ™ calendars.

15 The OptiLoad ™ Multi Roll Calender is suitable for almost all types of paper. It is particularly well suited for calendering glossy and smooth paper grades. OptiLoad has 4-12 rolls. It can be placed in connection with a fiber web machine as an online calender or it can be a separate unit.

··· v · 20 One problem that may occur with fiber web-pressing nipples in a fiber web machine, particularly calenders such as multi-calendars, is barring · V. · or nip vibration, which causes the web surfaces to wear on rollers and • · * · * · . As one solution to * * * *; [· *, barring rolls have been proposed, ♦ · ***** 25 one or more of the rolls in the stack have been moved at a distance from the others in the stack. , a line passing through the center axles of the rollers. Typically, this overlap is in the order of a few tens of millimeters.

»* • · * ·· • · · · ·

One arrangement for overlapping calender rolls is disclosed in patent application EP

• ♦ '· * 30 1275777. An overlapping structure of calender rolls is disclosed, for example, in application Fl • 20055407.

• · 3

SUMMARY

According to a first aspect of the invention, there is provided an apparatus for a fiber web machine comprising a body and an apparatus 5 comprising a support and loading arm mounted on the frame for rotatably supporting the first nip roll and and the apparatus comprising means for deflecting the axis of rotation of the first nip roll from a line passing through the axes of rotation of the first and second nip rolls. The apparatus comprises a support and loading arm provided with at least one linear movement mechanism in the form of an overlapping movement, such as a linear guide, and the apparatus comprises a slide (s) arranged on said at least one linear movement mechanism, and the apparatus comprises an axis to the frame for pivoting the support and load arms to the frame.

According to a particularly advantageous embodiment of the invention, the shaft comprises at least one eccentric surface, and a means (1) of transmission (s) configured to move said at least one eccentric surface is provided for coupling said at least one eccentric surface and 20 support and loading arms. • »· movement parallel to the eccentric surface overlapping movement with at least one of the linear 1 · *: V mechanisms of the support and load arm • · / * · /.

Preferably, said transmission means comprises at least one counter member which is. . and the transmission means further comprises at least one · · · one interleaving portion defining an eccentric surface of the bearing bore eccentric • · * ·] and at least one transmission portion for receiving said at least one counter element.

• * • · »a · • ·; *** Preferably the counter member comprises a pin or at least one sliding surface, and preferably the transmission member comprises guides or fork-like slides.

4

Preferably, the apparatus comprises an actuator for rotating said at least one eccentric surface, preferably at the drive end of the shaft.

Preferably, the actuator is a rotary motion actuator such as an electric motor and further comprises a gear such as a helical or planetary gear or the actuator is a linear motion actuator such as a cylinder actuator such as a hydraulic actuator or a screw jack.

Preferably, the apparatus comprises a transmission means for engaging said at least one eccentric surface and a bearing and loading arm further configured to prevent said at least one eccentric surface from transverse movement into a movement of the bearing and loading arm.

Preferably, the support and loading arm comprises at least one mounting surface provided therein for mounting the bearing housing of the first nip roll.

Preferably, the size of the reciprocating interleaving motion is 10-50 mm, more preferably 30-40 mm.

According to another aspect of the invention, there is provided a fiber web machine comprising an apparatus according to any one of claims 1-9. Preferably, the fiber web machine • ♦ · / Y comprises at least three nip rolls. Preferably, the fiber web machine comprises a calender or a 'Γ.1 press or a coating machine. Particularly preferably, the fiber web machine is a calender, and the first 25 nip rolls are offset.

* • «* · 1

Roll overlapping can occur in a straightforward manner when the roller bearings • · «. ·· 1. is fixed on its own, either directly or by means of intermediate parts, to move the support arms and the load arms and the support arms and the load arms are linearly moved by means of the 30 ainak • 11 11 linear movements between the fiber body and the support arms and load arms. mechanisms such as linear guides.

• · • ♦ • 1 · «*

Preferably, the driving force is arranged to be transmitted to a deflectionable support and load arm by a rotatable eccentric surface, preferably arranged on the same axis on which the support and load arm is mounted on the body of the fiber web machine. The arrangement can provide an overlapping device of very compact construction.

The combination of the bearing and load arm and the bearing housing 5 can be moved linearly without any transverse movement component relative to the overlapping movement. By performing an overlapping motion in such a straightforward manner, it is possible to make the nip slots of the track remain almost constant regardless of the amount of overlap. The overlapping mechanism shown allows for fast movements, preferably with continuous control. By using the illustrated 10 interleaver in conjunction with a press nip, it is possible to achieve lower levels of vibration in the fiber web machine.

The disclosed method and solution can be used to reduce and eliminate barring problems in fiber web machines such as presses, coating equipment and calenders, such as multi-roll calenders.

Various embodiments of the present invention will be described or described only in connection with some or some 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.

* • * · • * · · «·

0 ': BRIEF PRESENTATION OF THE PATTERNS

The invention will now be described, by way of example, with reference to the accompanying drawings, in which: Fig. 1 shows a roll of a multi-roll calender with an overlap of a roll of a roll, Figure 2 shows an overlapping apparatus, and m · * ': ** Figure 3 shows the overlapping apparatus of Figure 2 divided into components.

• · · V: 30 «··

DETAILED EXPLANATION

In the following description, like reference numerals will be understood to refer to like parts. It should be noted that the figures shown are not in their entirety on the 6 scale, and are for the purpose of illustrating embodiments of the invention only.

In the following description, the multi-roll calender will be used as an example of a fiber web machine 5 wherein the fiber web is compressed in a nip between two press rolls. In multi-roll calenders, press nipples are called calender roll nips or calender nips formed between adjacent calender rolls, whereby a stack of rolls formed by adjacent calender rolls, i.e., the roll, can be placed in a vertical position or 10 vertical inclined positions. The calenderable fibrous web, such as paper or cardboard, traverses through the above-mentioned nipples so that it is introduced into the track, e.g., from the beginning of the track and leaves the track at the end.

Figure 1 schematically illustrates a fiber web machine having eight nip rolls 11 -15 18 and seven nip N1-N7. The multi-roll calender 10 of FIG. through rollers 11-18 arranged as a track and I ·· V * 'intermediate rollers 12-17 are supported relative to the calender body F by hydraulic relief cylinders 29 and support and load arms 30 caused by the masses of the bearing housings and associated auxiliary rollers of the intermediate rollers. :; 4! to reduce the nip load, the roll preferably comprising one or more thermal rollers T, 12, 15, 17 as a hard surface intermediate roll and one or more preferably polymeric rolls as a soft and flexible surface roller. , calendering roll 13, 14, 16.

In the example schematically shown in Fig. 1, in the roller system of the multi-roll calender 10, the fiber web W is calendered in all the nipples between the calender rolls ···! with track output from top to bottom. The web W may not necessarily be calendered in all nipples in all t · · driving situations, but in some driving situations it may be advantageous to pass the web through the open nip without calendering and in some 7 driving situations it may be advantageous to partially track the web. Thus, the web may be arranged to completely rotate one or more nipples, for example by means of take-out rollers. In Figure 1, the web W is guided through an output roller 21 to the top nipple N1 and further 5 through the other nipples N2-N6 and finally out of the bottom nip N7. At nipples N1 through N7, the web W is removed from the surface of the calender rolls by the take-up rolls 22, 23, 24, 25, 26 and 27.

In the multi-roll calender 10, the retaining roll support means for either the roll bearing housings 10 or the calender body F are not shown for clarity. After the track, the fiber web W can be further guided as needed, for example by roll 28.

The body F of a fiber web machine is shown by a dashed line, the joints and arms are shown only 15 schematically with one intermediate roll. The multi-roll calender 10 shown in Figure 1 has a vertical track, but the fiber web machine track or part of the track may equally well be a non-vertical track.

As a solution for barring prevention, T: roll offset RO (roll offset, shown by a bidirectional arrow) described by FIGS. 1-3 is illustrated, so that one or more of the pressing rolls can be deflected v.J from the center axis of other roll rolls. Preferably, the size of such an overlapping motion is in the range of 10-50mm, more preferably 30-40mm · 25mm.

«M • * • · • • f

Figures 2 and 3 illustrate in Fig. 1 the top position from the top • · ·· '·' calculating the lateral displacement of the flexible calendering roll 13, the *, * ··· * third calender roll, i.e. the overlap shown by the bidirectional arrow in the compression plane . Figure 2 shows the assembly

«M

mode, an inexpensive structure of an interleaving apparatus 100 for real-time fiber web machine lateral displacement and roll · * · .. interleaving.

• · 8

The interleaving apparatus 100 is compact in design and size. Preferably, the interleaving apparatus 100 is adaptable to a plurality of positions in the fiber web machine, particularly when lateral displacement of the axis of the loaded nip roll relative to the axis of the other nip roll is required. Preferably, each bearing housing of the interleaved roll is supported by a single interleaving assembly 100 on a fiber web machine such as a calender body F. FIG. 3 illustrates the structure of FIG. 2 in more detail, divided into components.

The overlapping apparatus 100 comprises a bearing and loading arm 30, a first slide 10 40 and a second slide 40 ', an eccentric shaft 50, a first overlap portion 60 and a second overlap portion 60', an actuator 70 and preferably a gear actuator gear 71.

The support and loading arm 30 comprises a first lever end 31 having an attachment point 15 such as a first hole 31 'for a loading and lightening cylinder 29 supported on the calender body F. The support and loading arm 30 comprises a second end 32 associated with the first end 31, at least one mounting surface 34 and fastening means 35 such as threads for securing the non-shown bearing housing of the calender roll 13 are provided. The second end 32 of the support arm 20 and the load arm 30 is bipartite according to the embodiment * ··· VJ in Figures 2 and 3, whereby it comprises a distance * · *.: * To the other end 32 rigidly connected to the other. end 32 • · \ V by means of intermediate part 38. Preferably, said at least one mounting surface 34 and • · i: fixing means 35 for the roll bearing housing are arranged in the region of the supporting end 32 'and the intermediate part »· 25 38. Preferably, the mounting surface 34 is arranged rigidly and immobile * ··· 'on the support and loading arm 30.

* · • · ·

An important feature of the overlapping apparatus 100 shown in Figs. 2 and 3 is that the bearing housing of the interleaved roller is fixedly mounted directly on the bearing and V * 30 load arms 30, so that the bearing housing mounting surfaces 34 are not moved relative to • · ·

* ··· * support and loading arm 30. Roll overlap occurs in calender body F

and a combination of an eccentric shaft between the support and load arm 30 and a guide for carrying a straight line movement, which moves the combination of the support and load arm 30 and the bearing housing in a straight line 9 without a vertical motion component. It should be noted that the interleaving motion RO is performed in a straightforward manner. In this case, the nip gaps in the track remain almost constant regardless of the amount of overlap.

The bearing and loading arm 30 comprises a first attachment and guide region 33, between the first end 31 and the second end 32, respectively, a first slip region 33. Accordingly, the bearing and loading arm 30 comprises a second attachment and conducting region 33 'in the region of the support 32'. cooperates with the first slide region 33 of the second end 32 to provide support and bearing for the support and loading arm 30 to the calender body F. Preferably, the support and loading arm 30 comprises a plate-shaped first end 31, a second end 32 and a support end 32 '. Preferably, the first and second slide regions 33, 33 'comprise openings in the plate structure of the bearing and loading arm 30.

15

The first slide area 33 comprises a first linear guide 33a, preferably the slide, by means of which RO direction of the arrow, ie in the direction of the desired limitysliikkeen is arranged to be movable first slider 40, and the second gate region 33 'comprises a second linear guide 33a', preferably the slide, which allows the direction of arrow RO or 20 of the desired limitysliikkeen direction is arranged to be moved by another slide 40 '.

• M

V! The clearance of the first and second slides 40, 40 'with linear guides 33a, 33a' in the direction of overlap allows for an overlap movement of about 10-50 mm, more preferably about 30-40 mm.

• ·

v .: The first and second slides 40, 40 'can only move in the sliding regions overlapping RO

in the suunn · ϊ i direction, since the support of the slides 40, 40 'in the first and second slides 33, 33', respectively, do not allow other directions of movement relative to the supporting and • * * ··· * load arms 30.

The first slide 40 comprises a first bearing bore 41 for an eccentric shaft 50 to receive the first bearing surface 51. The first bearing bore 41 ··· V: 30 preferably comprises a first sliding surface 42 for forming a sliding bearing with a first bearing surface 51 of the eccentric shaft 50. The second slide 40 'comprises • * ·· a second bearing bore 41' for receiving the second bearing surface 51 'of the eccentric shaft 50. The second bearing bore 41 'preferably comprises a second sliding surface 10 42' for forming a sliding bearing with a second bearing surface 51 'of the eccentric shaft 50.

The eccentric shaft 50 comprises a first bearing surface 51, a second bearing surface 51 'and an actuating end 53 which are concentric. The first and second support surfaces 51, 51 'are preferably spaced from one another with the other end 32 and support end 32' of the bearing and loading arm 30 and preferably with the sliding surfaces 42, 42 'of the first and second slides 40, 40'. Preferably, the eccentric shaft 50 is formed by a plurality of pieces to facilitate assembly of the interleaving device 100 10.

Preferably, the first and second bearing surfaces 51, 51 'of the eccentric shaft 50 and the first bearing hole 41 and the second bearing hole 41' of the second slide 40 'respectively have different diameters for ease of assembly.

The calender body F, shown in the examples of Figures 2 and 3 comprising an H-profile, preferably comprises bearing holes (not shown) in the H-profile flanges for receiving the first and second support surfaces 51, 51 'of the eccentric shaft 50.

The support and load arm 30 of the interleaver assembly 100 is supported and supported by a first linear guide 33a, a first slide 40, a first bearing hole 41, a first sliding surface 42, and an eccentric shaft 50. the first * · * · * 25 pivotably through the support surface 51 to the first bearing hole • · * ··· * in the calender body F. Similarly, the support and loading arm 30 is supported and supported by a second linear guide 33a ', a second slide 40', a second bearing bore ♦ ♦ · 41 ', a second sliding surface 42' and a second support surface 51 'of the eccentric shaft 50. to another bearing hole.

The eccentric axis 50 further comprises a first eccentric surface 52 and a second eccentric surface 52 ', the eccentricity of which is preferably half of the desired ***** overlapping motion R0. Eccentricity in this context preferably refers to the distance between the center axis of the circular eccentric surface 52, 52 'and the axis of rotation defined by the first bearing surface 51, the second bearing surface 51' and the drive end 53. The eccentric surfaces 52, 52 'are preferably circular for insertion into a circular bearing bore to move the movement component in the direction of the eccentric surface overlapping motion RO by a linear movement mechanism 33a, 33a for the carrier and load arm 30.

To effect the transmission connection of the eccentric shaft 50 and the bearing and loading arm 30, the first 10 of the overlapping portion 60 and the second overlapping portion 60 'is to transfer the overlapping movement defined by the offset of the eccentric surfaces 52, 52' into the desired overlapping motion RO. The transmission takes place by turning the angular position of the eccentric shaft 50, i.e. by rotating the eccentric shaft 50, preferably by rotating back and forth.

The first overlap portion 60 comprises a third bearing bore 61 for receiving a first eccentric surface 52 of the eccentric shaft 50. The third bearing bore 61 preferably comprises a third sliding surface 62 for forming a sliding bearing with the first eccentric surface 52 of the eccentric shaft 50.

The first interleaving section 60 further comprises a first transmission section 66,: T: which preferably blocks the movement of the first interleaving section 60 in the t-** direction of the interleaving movement RO relative to the bearing and loading arm 30, but * · *. RO to transverse • · · direction 67. Preferably, the first transmission portion 66 comprises conductors such as • · \ v 25 fork-like slides, opposite to the center axis of the third bearing bore 61

«M

sides.

To form a transmission connection between the support and load arm 30 and the eccentric shaft 50 and the first overlap portion 60, the support and v * 30 load arm 30 comprises a first counter member 36 (preferably m »9

mounted immovably on the supporting and loading arm 30) for the first transmission part 66. Preferably, the first counter member 36 comprises pin *: ** or sliding surfaces on opposite sides of first skid region 33 overlapping RO

transversely 67 viewed. Preferably, the first counter member 36 is located in the middle of the range of motion of the first 12 linear guides 33a viewed in the direction of the overlap RO.

The first transmission portion 66 is adapted to move (preferably slide) 5 relative to the first counter member 36 in the transverse direction 67 of the overlap, and the connection between the first transmission member 66 and the first counter member 36 is preferably disengaged in the RO direction.

The second overlap portion 60 'comprises a fourth bearing hole 61' for receiving a second eccentric surface 52 'of the eccentric shaft 50'. The fourth bearing bore 61 'preferably comprises a fourth sliding surface 62' for forming a sliding bearing with a second eccentric surface 52 'of the eccentric shaft 50.

Preferably, the second overlapping portion 60 'is similar in function and direction of movement to the first overlapping portion 60. The second overlapping portion 60' comprises a second transmission portion 66 'which preferably formally blocks the motion of the second overlapping portion 60' in the direction of overlapping motion R0 with respect to and to the support end 32 ', 20 of the load arm 30, but allowing the movement of the second overlap portion 60' to overlap in the RO direction transverse ···: 67. Preferably, the second transmission portion 66 'comprises fork-like guides such as slides on opposite sides of / 'f.

The support and load arm 30 comprises a second counter member * * "* 36 '(preferably fixedly fixed to the support and load arm. 30) in the region of the support head 32'. Repeat the transmission. for the part 66 '. The second counter member 36' preferably comprises • · · '• «·

the pin or sliding surfaces on opposite sides of the second slider region 33 '

• «] ·] viewed in cross direction 67. Preferably, the second counter member 36 'is located in the middle of the motion range of the second linear guide 33a' viewed in the direction of the overlap RO.

The second transmission portion 66 'is adapted to move (preferably slide) relative to the second' * counter member 36 'in the transverse direction 67 of the overlap RO, and the second transmission member 66' and the second counter member The joint 36 'is preferably arranged to be free of play in the RO direction of the overlap.

13

The apparatus 100 comprises an actuator 70, and preferably a gear 71 associated with the actuator, to provide the rotational movement required by the overlapping motion RO of the calender roll 13. The actuator 70 preferably comprises an electric motor and the gear unit 71 preferably comprises a worm gear or planetary gear whose gear ratio is selected to be high enough to provide sufficient torque to the eccentric shaft 50. Preferably, the actuator 70 is driven back and forth such that the eccentric surfaces 52, 52 'of the eccentric shaft 50 rotate back and forth by up to 180 °. Preferably, if one wishes to continuously perform the largest reciprocating motion, the eccentric shaft 50 may be rotated unidirectionally. Alternative actuators for rotating the eccentric shaft 50 could be a cylinder drive such as a hydraulic drive, or a screw jack.

15

Generally, the length and frequency of the linear overlapping motion RO can be adjusted as desired. Preferably, the angular position of the eccentric shaft 50 may be rotated at a desired frequency and at a desired angular position to provide a suitable barrier or damping effect on the barring.

20 ··· v J The actuator 70 comprises a support 72 to prevent rotation of the actuator 70 relative to the support and load arm 30. Preferably, the support 72 comprises means for rotationally engaging the support • ·, e.g., a groove • #: 77, which cooperates with the support arm. and with the shape of the load arm 30, such as the pin 37. The actuator 70, preferably the actuator gear 71, is ··· * ··· * coupled to rotate the eccentric shaft 50 at its actuator end 53.

• ♦ • · ·

Naturally, it is also possible to implement the overlapping apparatus 100 by means of an eccentric shaft 50 having only one eccentric surface 52. Thus, the eccentric surface ·· v: 30 is, for example, formed sufficiently wide to support the bearing and ***** loading arm 30. support relative to the body of the fiber web machine F would be sufficient! ** ·· stable.

• · 14

In one aspect, it is proposed to implement a fiber web machine comprising apparatus 100 in accordance with a preferred embodiment. Preferably, the fiber web machine comprises at least three nip rolls 11-18. According to a preferred embodiment, the fiber web machine comprises a calender or a press or a coating machine 5, According to a very preferred embodiment, the fiber web machine is a calender and the first nip roll 13 is an intermediate roll.

The invention can be applied to new structures as well as rebuild structures, whereby existing structures are supplemented or repaired. The invention is applicable to fiber web machines or parts of fiber web machines such as calenders, presses and coating machines.

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.

• 1 1 • • • • • • • • • • • • • • • 1 · · · 1 * · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · ● tomed · service ····· · · · · · · · · · · · · · · «• • • • • • • • • • • 1 1 * • • * 1 • 1 · ·

Claims (13)

Device (100) for a fiber web machine (10), said fiber web machine (10) comprising a frame (F) and said device (100) comprising a support and load arm (30) fixed to the frame (F) for rotatably supporting up a first nip roll (13) at a bearing housing and to load it against a second rotatably supported nip roll (12) to form a nip (N2), through which said nip (N2) can be passed a fiber web (W), and which device (100) comprises means for deflecting the axis of rotation of the first nip roller (13) from a line which likes to rotate through the axis of rotation of the first and second nip roller 10 (12,13), characterized in that the device (100) comprises - a bar and load arm (30) provided with at least one mechanism (33a, 33'a), such as a linear guide, which performs a rectilinear movement parallel to the overlap movement (RO) - a slide / slider (40, 40 ') provided for said at least one mechanism (33a, 33'a) performing a rectilinear motion, and - an ax electrical (50) which can be connected to at least one slide (40, 40 ') and the fiber web machine frame (F) for storing the load and load arm (30) in the frame (F) rotatably. Device according to claim 1, characterized in that the shaft (50) comprises at least one eccentric surface (52, 52 '), and for coupling said at least one eccentric surface (52, 52') with the support and load arm. (30) is provided with a power transmission means (s) (60, 66, 36) which / which means are provided. are configured to transmit a parallel movement to said carrier at least one eccentric (52, 52 ') overlap (RO) motion to the carrier and load arm's movement with said eating at least one mechanism (33a, 33'a). performs a rectilinear motion. • · · • t • · · «·, v. Device according to claim 2, characterized in that • · ·, ·· *. The power transmission means comprises at least one motor member (36, 36 ') located on the support and load arm (30), and the power transmission means further comprises at least one overlap member (60, 60') having a bearing heel (61 , 61 ') for receiving the eccentric surface (52, 52') of the eccentric shaft (50) and at least one power transmission portion (66, 66 ') for receiving said at least one motor member (36, 36'). Device according to claim 3, characterized in that the motor means (36, 36 ') comprises a pin and at least one sliding surface and the power transmission part (66, 66') comprises guiding or fork-like sliding guides. Device according to any of claims 1-4, characterized in that the device comprises a drive device (70, 71) for rotating said at least one eccentric surface (52,52 '), preferably from the drive end (53) of the shaft (50). . Device according to claim 5, characterized in that the drive device (70) is a drive device which produces rotary motion, such as an electric motor, and further comprising a gear (71), such as a worm or planetary gear, or the drive device (70) is a a drive which produces linear motion, such as a cylinder drive, for example a hydraulic drive, or a screwdriver. Device according to any of claims 2-6, characterized in that the device comprises a power transmission means (60, 66, 36) for coupling said at least one eccentric surface (52, 52 ') and the support and load arms ( 30), which power transmission means is additionally configured to prevent transmission of a * * .v. relative to said at least one eccentric surface (52, 52 '). overlapping movement (RO) transverse movement of the and the support and load arms * · ♦ ·. ·. *. (30) movement. * ·. "*. 25 • · • · · Apparatus according to any of claims 1-7, characterized in that the support and: T: load arm (30) comprises at least one mounting surface (34) which is arranged rigid and immovable thereon for attaching the bearing housing of the first nip roll (13). * • · • * * • · * • ». ·· *. 30 Device according to any one of claims 1-8, characterized in that • · * 1. the size of the overlap movement (RO) back and forth is 10-50 mm, • preferably 30-40 mm. • ♦ · · · · · A fiber web machine comprising a device according to any of claims 1-9. Fiber web machine according to claim 10, characterized in that the fiber web machine comprises at least three nip rolls (11-18). Fiber web machine according to claim 10 or 11, characterized in that the fiber web machine (10) comprises a calender or press or coating machine. Fiber web machine according to claim 10, characterized in that the fiber web machine is a calender and that the first nip roll (13) is an intermediate roll. · • · 1 φ ♦ ♦ ♦ ♦ 1 1 1 1 1 1 1 1 1 1 1 1 1 • Φ • · • · ♦ ♦ ♦ ♦ ♦ ♦ ♦ ♦ ♦ ♦ ♦ ♦ ♦ «« «« # # # «• I · • · ♦ ·« ·· · • · · • «· • ·