FI120594B - Telastosovitelma - Google Patents

Description

Track assembly - En valsstapel

The present invention relates to the treatment of a fibrous web, such as paper, board, pulp, tissue or the like, in a fiber web machine. More particularly, the present invention relates to a track assembly in which the web material is passed through a nip or nip formed by opposing rolls of a track comprising at least two rolls, the nip or nip forming a vertical nip plane or an inclined nip plane or a sloping nip plane.

In the context of the present invention, the term roll means a pair of rolls formed by two rolls or a stack of several rolls. By the attribute nipple is meant the contact area of the two rolls which are in contact with each other, which may be a linear nip or an extended nip. When the nip is extended, the shell of at least one of the contact rolls is deformable under surface pressure. Such a roll is, for example, a soft surface roll and / or a zone adjustable roll. The original nip plane attribute refers to the plane passing through the nip formed by the rolls in contact with the two roller tracks and the central axes of the rolls and the plane passing through the nipples in contact with the multiple rollers 20. The original nip plane may thus be a plane parallel to the vertical line of gravity and transverse to the machine direction, i.e. MD direction, or a plane inclined or angled plane.

From FI96334 C (VALMET PAPER MACHINERY INC.) There is known a method and a calender applying it for calendering paper or similar web material. According to the publication, the web material is passed through the nip formed by deflection compensated upper roller and lower roller and two or more intermediate rollers arranged between the upper roller and lower roller. The rolls are arranged in substantially vertical 30 rolls. Intermediate rolls are those which have a substantially similar shape to the natural deflection line caused by its own weight. The nip load caused by the masses of the intermediate rollers and associated auxiliary devices is substantially reduced 2 completely by means of an effective loading cylinder mounted on a roll bearing housing or a support lever, whereby and / or external loading on the upper roller or lower roller.

From the weaknesses and / or problems associated with the prior art, it may be mentioned that the roll is bound to a single fixed orientation, whereby to adjust the nip load, the rolls 10 can only be moved while maintaining said orientation. Because the nip plane is typically solid, it is always difficult to adjust the nip load more accurately due to gravity caused by the roll masses and compensation of the gravity effect. In addition, there is the problem that irreversible deformations occur in the soft intermediate roller of the roller as a result of heat and wear, resulting in 15 vibrations in the roller and a groove and / or wavy surface of the roller intermediate roller, i.e. developing a barring effect.

One object of the present invention is to provide an improved fiber web machine track design that can improve nip load or nip line load control 20 and reduce the development of track vibrations. It is an object of the present invention to provide an improved roller assembly, particularly to reduce the barring problem, when the surface of a soft-surfaced roller is wavy by an excitatory mechanism or by irreversible deformation or wear. Yet another object of the present invention is, according to another aspect of the present invention, to improve the track suspension of a track assembly that can reduce track vibrations of the track. One object of the invention is to provide an improved power cylinder for a fiber web machine roller assembly which can eliminate or at least substantially reduce variations in the roller due to changes in the nip load associated with nip load control.

The objects of the present invention can be solved, for example, by at least one roll of the roll being movable along a linear guide relative to the original nip plane. In this case, the roll 30 can be even completely removed from its nip contact with the counter roll or counter rolls.

According to one aspect of the solution of the present invention, each roll 5 of the track is movable relative to and / or out of the original nip plane independently of the other rolls of the track. In this case, it is possible that only the intermediate rolls between the top roller and the lower roller of the track can be displaced relative to the original nip plane and / or out of the nip plane.

According to the present invention, the roll / intermediate roll can be moved with or without an actuator in a direction different from the original nip plane. Such a deviation from the nip plane may be parallel to the machine direction, i.e. the MD direction or this direction may form an angle of <90 ° in the direction of web travel or in the opposite direction of the web direction.

15

The actuator acting on the roller bearing bracket and preferably belonging to the movable roll support means and / or loading means and providing an external load for moving the roll along the linear guide may be adjustable in length, e.g. the actuator may be 20 - power cylinder, preferably hydraulic and / or pneumatic telescopic means for adjusting the length, such as a wedge means, a power cylinder or the like, an adjusting rocker lever or a lever arm, - a manual power means such as a knife, a mechanical counterweight means or other means for adjusting the actuator.

The actuator acting on the roller bearing bracket and preferably belonging to the movable roll support means and / or the loading means and providing an external load for moving the roll along the linear guide may include, for example: - a power cylinder, preferably a hydraulic and / or pneumatic power cylinder; or lever arm, 4 - eccentric axis of rocker arm or lever arm joint, - power driven screw or spindle nut or toothed rack, - linear guide with servo-hydraulics and linear motor, or other such power unit to provide an external load and thereby move the roll in linear guides.

The actuator for moving the roll along the linear guide associated with the roll bearing bracket may comprise a tiltable linear guide, wherein the linear guide is preferably provided with a power unit based on a suitable positioning technique to deflect or pivot the linear guide from its original, preferably upwardly inclined position. A suitable power unit may be, for example, a 15 - power cylinder, which is preferably a hydraulic and / or pneumatic power cylinder, - a rocker or lever arm driven by a power cylinder or the like, or 20 - a manual force means such as a knife, a mechanical counterweight means or the like, with which the linear guide can be tilted and thereby move the roll in the linear guides ..

With such actuators, the movable roll can be moved in a direction substantially different from the initial nip plane by the movement provided by the lower cylinder and / or the upper cylinder. For example, the actuator may be arranged to improve nip load for fine tuning.

According to the invention, the individual nip for adjusting the nip load or closing, i.e. moving the roll, may be based on the wedge force caused by the wedge rolls. Hereby, at least one roller mounted on a linear guide, such as in a calender, can be displaced on a linear guide whose travel can be dimensioned such as, for example, short so that the nip is opened and closed.

To control the nip load by controlling the wedges of the rolls, it may also be helpful to adjust the angle of the wedge rollers relative to the gravity line. In this case, a high line load is achieved at a low angle when the wedge strengthens the gravity and there is no need for transverse loading cylinders with respect to the gravity line. The track can be tilted 45 °. The nip load can then be increased above the tilted track and allow sufficient nip load only by wedging the track.

As with adjusting the nip load of the nip or nip, the opening and closing of the nip or nip can also be accomplished by the tilt angle and gravity of the track. Hereby the opening / closing of the nip or the adjustment of the nip load can be effected by changing the angle of the plane passing through the central axes of the rollers 15 in relation to the gravity line or nip plane. A high line load, i.e. high nip load, is achieved at a low angle with respect to the horizontal plane, when the rolls pressed against each other reinforce gravity and do not necessarily require any transverse loading cylinders. In a tilted track, the nip load can be increased above the 20 tilted track and lowered below the tilted track. In addition, it is even possible to quickly open the nip by releasing the roll support upwards, i.e. simply dropping the roll from the original nip plane.

In one exemplary embodiment of the invention, the nipples are open when the nip plane is inclined with respect to the vertical gravity line, and in the nip loading state, the nip plane is parallel or only slightly inclined with respect to the vertical gravity line. As the nip load is increased or the nip is closed, the linear guide provided with the linear guide of the roll and the bearing housing thereof are rotated or twisted relative to the vertical line of gravity so that the roll slides in the linear guide and nip 30 closes by gravity and angle. The actuator for such a pivoting or rotating motion may be, for example, an electric motor or a hydraulic motor. Because gravity is used to control the nip load or to close the nip, no high turning force or twisting force is required and the required torque arm, i.e. the length of the linear guide, may be small. A further advantage is that different adjustable nip loads can be used on the nipples, the magnitude of which can be determined by the formula Fy = M x G x sin (A), where 5 M - mass of the roll G = gravity constant (9.81 m / s2) A = loading angle of the roll

Another object of the invention may be solved, for example, by changing the nip dynamics of the track 10 to prevent the onset of a developing oscillation problem by changing the position of the problem roll that generates the oscillation relative to the nip plane, i.e. generating roll overlap. Such a change in the position of the problem roll can be accomplished by making the joint of the intermediate roller rocker or support lever eccentric and turning this eccentric, for example, while driving, whereby the intermediate roll 15 is displaceable in the machine direction, i.e. MD direction. According to another embodiment of the second embodiment of the invention, when the roll is formed of at least three rolls, and when the nip plane is wavering, the distance between the rolls fixedly in the nip plane is smaller than the diameter of the roll . Thus, the nip load can thus be adjusted or the nip closed or opened by moving the movable roll relative to the fixed and / or other rolls. Such an arrangement is particularly effective for the barring type of a multinip calender, in which the polymer-coated roll shell is wavy by an excitation mechanism.

25

The third object of the invention can be solved, for example, by the fact that the bearing housing of the roll, slidably mounted on the neck of the intermediate roll, is fixed to the body of the roll by means of a guide means. To form a force greater than the force exerted by the nip load, matching means are provided between the bearing housings which hit each other when the roller or nipples are closed by a lower cylinder. In the force ring thus formed, the forces pass from the lower cylinder through the bearing housings and counter members to the upper part of the track body, and due to the force ring formed, the track does not have the elasticity caused by the roll diapers. Thus, in accordance with one embodiment of the invention, the counter members can be attached to the bearing housings, whereby the counter members can be modified to correspond to the milled diameter of the roll.

According to one aspect of the solution of the third problem, the line loading of the nipples can be created by means of a diaphragm loaded upper roller and a lower roller, and the intermediate roller relief can be accomplished by sliding bearings with vertical impact. In addition, the plain bearings can be fitted in MD-direction guides along which the intermediate roll is movable in the MD direction.

10

The problem with hydraulic cylinders in particular is that the seals used in the hydraulic cylinders have a large difference between rest friction and motion friction. This causes problems with the large difference between resting friction and motion friction when adjusting the nip load, especially when small adjustment and small adjustment movements are required. In practice, the added pressure 15 is unable to overcome the rest friction, with the force cylinder not moving at all or the high rest friction causing the cylinder to build up pressure, which ultimately causes a jerk in the cylinder movement which in most cases exceeds the desired adjustment. Aging of seals also causes faster seal wear, which further increases the likelihood of jolts.

20

The fourth object of the invention can be solved by a force cylinder for the roller assembly of the fiber web machine, for example by selecting the material of the seal used in the hydraulic cylinder so that the material has a resting friction and movement friction as close as possible.

25

The material group meeting the criteria is, for example, carbon-based materials, and in particular graphite-rich carbon-based materials, because graphite has a self-lubricating property and is good in terms of wear resistance and sufficient surface pressure. If abrasion resistance is considered as the primary criterion, suitable materials are fiber reinforced graphite composites having substantially similar friction properties. Thus, the material of the gasket may be selected from the group consisting of 8 preferably fiber-reinforced graphite composites and carbon based materials, more preferably graphite-rich carbon based materials.

Generally, therefore, the present invention relates to a track assembly of a fiber web machine in which web material is passed through a nip formed by opposing rolls in the track. The advantages of the present invention may be mentioned, the invention can improve the adjustability of nip loads, reduce roll vibrations and change the position of the problem roll or problem rolls. Still other advantages of the present invention may be noted as follows. Each individual nipple on the track can be opened and closed independently of the other 10 tracks on the track. The nip load on each individual nip is adjustable independently of the other nipples on the track. In a track system, a soft-surface intermediate roll, such as an intermediate polymer roll, which has worn or otherwise undergone irreversible deformation, can be displaced by the invention, thus reducing the effects of wear corrugation and the barring effect. It is also an advantage that, due to the independent movability of the intermediate roll, the adverse effects of roll vibrations caused by soft surface intermediate roll and other deformations can be reduced by moving the problem roll sideways and / or out of the nip contact.

The invention will now be described with reference to a preferred field of application of a fibrous web machine, that is, a paper machine calender with a plurality of rollers. It is thus a multi-roll calendar consisting of a multi roll roll system. In the future, such a multi-roll calender will be referred to as a calender for simplicity.

25

A web, such as a paper web, passes through several successive nipples in the calendar. The nips may be web calendering nipples, such as a nip between a hard surface thermal roller and its soft surface counter roll, or non-calendering nipples, such as a pivot nip between two soft surface rolls.

It is not essential to the present invention for the structure or arrangement of the roller rolls, but for the means provided by the invention for more precise and individual adjustment of nip loads, - opening or closing the nip independently of other nipples if necessary, - to continue processing the web by removing damaged roll nip contacts; .

5

patent drawing:

FIGS. 1a, FIG.lb, FIG.lc, FIG.ld and FIG.le schematically show some preferred examples of roller track orientations in which the roller roller roller (s) movement according to the present invention is applicable, FIG. 2 shows an advantageous embodiment of the invention. Figure 3 shows another preferred embodiment of the invention for changing the position of the roller rollers, Figure 3. Fig. 4 shows a fourth preferred embodiment of the invention for changing the position of the roller rollers, Fig. 5 shows a fourth preferred embodiment of the invention for changing the position of the roller rollers, Fig. 6 shows a fifth preferred embodiment of the invention for changing the position of roller rollers FIG. 7 illustrates a sixth preferred embodiment of the invention for changing the relative position of the roller rollers, FIGS. 8a, FIG, 8b and FIG. 9 show a seventh preferred embodiment of the invention for moving the roller roller, and FIG. 10 shows an eighth preferred embodiment of the present invention for hanging track rollers on a track frame.

In the figures of the drawings, the calender is generally designated by reference numeral 1. In the exemplary embodiments shown in the drawings, the web passes through nipples from top to bottom through a roller which is a lower roll 11, a first roll and a second roll 15 arranged on top thereof. and so on..

10

FIGS. 1a to FIG. Schematically show some preferred roller orientations of the calender roller 1 to which the roller roll (s) movement according to the present invention is applicable.

5. 1a and FIG. Examples 1b each show a five-roller roller which comprises a lower roller and four rollers 12 to 15 arranged on top thereof. The rollers of FIGS. 1 and FIG. 1b are vertical, i.e. parallel to the weight of the power line. In this case, the shape of the nip plane, where each roll of the track in a nip contact with at least one other track of the track, is a straight nip plane in the form of a gravity line.

10

The example of FIG. 1a differs from the example of FIG. 11b in that the example of FIG. 11a only comprises intermediate rolls 12,13 and 14, which between the lower roller 11 and the upper roller 15 can be moved away from the original nipple plane NLS according to the invention. The lower roller may generally be loaded upwards by the lower cylinder 34 (cf. Figs. 2 to 5), and the upper roller 15 15 may be loaded downward by the upper cylinder 35 (cf. Figs. 2 and 5). FIG. In Example Ib, all the rolls above the lower roll 11, i.e. the intermediate rolls 12,13,14, and the upper roll 15 are movable away from the original nip plane NLS according to the invention.

FIG. The example illustrates a five-roll roller comprising a lower roller and four rollers 12 ... 15 arranged on top thereof. FIG. le track is straight but inclined relative to the vertical weight of the power line. Thus, the shape of the nip plane where each roll of the track in a nip contact with at least one other track of the track is a nip plane NLK inclined with respect to the gravity line.

FIG. Example 1d shows a five-roll roller which comprises a lower roller and four rollers 12 ... 15 arranged on it. FIG. Id roller tracks are overlapping with respect to each other, so the so-called roller bearings are implemented. overlap. In this case, the nip plane, with each roll of the track in a nip contact with at least one other track of the track, follows a line passing through the nipples of the center points of the rolls, the nip plane shape being a meandering nip plane.

11

The example of FIG. 1 shows an eight-axis roller comprising a lower roller Ila and seven rollers 12 ... 18 arranged on it. The track is divided at the pivot nip formed by the soft-surface intermediate rolls 14 and 15, which is a non-calendered nip, into a lower track comprising lower rolls 11 ... 14 and an upper track comprising 5 upper rolls 15 ... 18. FIG. 1e tracks are both tilted but have opposite tilt directions. In this case, the shape of the nip plane, where each roll of the track in a nip contact with at least one other track of the other track, is a nip plane NLM in the shape of a single-angle broken line.

10 It should be emphasized that the order and / or the number of different types of rollers 1 are not essential. In a conventional multi-roll roll, for example, an octagonal calender has superimposed: - a lower roll 11, which is loaded and can be deflection compensated and / or zone adjustable thermo roll or only hard surface thermo roll, 15 - soft surface, e.g. , for example, polymeric surface 14, then - soft surface roll, for example polymeric surface 15, then - hard surface thermal roll 16, then 20 - soft surface roll, for example polymer surface 17, and top - upper roll 18 which may be deflection compensated and / or zone adjustable thermo roll .

- In a track, the order of the tracks may also be as follows. The lower roll is a soft surface roll, for example a polymer surface, on which are arranged 25 hard surface thermo rolls, and at the top again is a soft surface roll, for example polymer surface.

Thus, the nip formed between each of the opposing hard-surface and soft-surface rolls may be a web calendering nip and the nip formed between each of the two soft surface rolls 30 may be a non-web calendering nip. A typical non-web calendering nip is, for example, a non-web calendering nip. When the calender has both web calendering nips and a web calendering twist nip 12, it is common for one side of the web to be calendered before the turn nip and the other side to be calendered after the turn nip.

In order to generate nip load, the lower roll 11 of the track 1 can be loaded from below 5, for example by a lower cylinder 34, and / or the upper roll 15; 18 may be loaded in the same manner as the lower roll but from above, for example the upper cylinder 35, and in addition each intermediate roll 12 ... 14 between the upper roll and the lower roll; 12 ... 17 loads the intermediate roll by means of a loading arm acting on the bearing bracket, such as a power cylinder 51, 92, or a rocker arm 61 or a rocker arm 71 or a lever arm 81 or similar roller actuator 5, 6, 7, 8, 9. Adjustable spacing roller loading can also compensate for, or at least reduce, the problems caused by the ground's pulling force to maintain a steady nip load in the calender.

Typically, such, for example, the aforementioned octagonal racks are 15 vertical. In FIG. Fig. 1e shows an eighth roller deviating from the usual one with the lower roller underneath the swivel nip being tilted anticlockwise and the upper roller above the swivel nip tilted clockwise.

The main objectives of the present invention are: 20 - to provide an improved fiber web machine roll assembly to improve nip load or nip line load control and to reduce roll vibrations, to provide an improved roll assembly embodiment to reduce , or web thickness variations, improves the roller assembly roller suspension to reduce roller vibration, provide an improved power cylinder for a fiber web machine roller assembly to reduce jerks caused by nipple load changes associated with nip load adjustment.

In general, these objects can be achieved in accordance with the invention so that at least one roller 11 ... 18 of the track 1 is movable within the track nipple NLS, NLK, NLK, NLM

30 13, in which nip plane each roll of the track is in nip contact with at least one other track of the track.

Referring to FIGS. 2 to .FIG.8, there are various equivalent alternative examples of actuators for adjusting nip load or moving the roll relative to the original nip plane with the rolls facing each other away. The original nip plane is not essential to the operation of the invention. Thus, the original nip plane may be in relation to the gravity line - vertical or near-vertical nip plane NLS, 10-inclined or strongly inclined nip plane NLK, or - kneeling nip plane NLP.

Also, the number of rolls that can be moved by the track is not critical to the invention. Thus, all of the tracks on the track, or just one of the tracks on the track, may be displaceable with respect to the 15 original nip levels.

In one embodiment of the invention shown in Fig. 2, the actuator 5 for moving the roll 12,13, 14 includes a length adjustable power cylinder 51 which acts on the bearing bracket of the movable roll 12,13,14. By adjusting the length of the power cylinder, the bearing brackets of the 20 rollers and the rolls are moved along the linear guides 40.

In another embodiment of the invention shown in Figure 3, the actuator 6 for moving the roll 12,13,14, 15 includes a swivel lever 61 pivotable about its pivot point by means of an adjustable force cylinder 62 which acts on the bearing of the movable roll. By rotating the rocker lever, the roller bearing brackets and the roller bearing brackets and the roller are moved in linear guides 40.

In a third embodiment of the invention shown in Fig. 4, the actuator 8 for moving the roll 12, 13, 14 includes a lever arm 81 which is pivotable about its pivot point by means of an adjustable force cylinder 30 which acts on the bearing bracket of the movable roll 12, 13. By turning the lever arm, the roller bearing brackets and the roller bearing brackets and the roller are moved in linear guides 40.

14

In a fourth embodiment of the invention shown in FIG. 5, the actuator 7 for moving the roll 12,13,14,15 includes a length adjustable lever 71 which is pivotable by means of a wedge cylinder 62 which is adjustable in length by its pivot point 5 and acts on the roller bearing. Either by adjusting the length of the rocker arm or by adjusting both the length of the rocker arm and the rocker arm, the roller bearing brackets and the roller are moved in linear guides 40.

In a fifth embodiment of the invention shown in FIG. 6, the actuator 9 for moving the roll 12,13,14 includes a linear guide 40 which is pivotable about its pivot point 95 by means of an adjustable force cylinder 92 by tilting the linear guides in the roll bearing brackets.

15

In a sixth embodiment of the invention shown in FIG. 7, the actuator for displacing the roll 12, 14 relative to the original nip plane may itself be any of the actuators described above. It is essential to the sixth embodiment that the wedges of the rollers are utilized to adjust the nip loads and to close / open the nipples 20. The operation of this embodiment is characterized in that the distance between each other roll 11 and 13 and / or 13,15 is smaller than the diameter 14 of the roll 12 to be displaced with respect to this distance.

In a seventh embodiment of the invention shown in FIG. 8, the actuator 9 for moving the roll relative to the original nip plane includes an eccentric bearing that makes the swivel arms of the roller rollers 12,13,14 eccentric, i.e., the rocker arm 61, acting on the roller bearing which acts on the roller bearing bracket, the hinge 85 uses an eccentric shaft 101,102. By turning the eccentric 30 shafts, the joint and the roller bearing brackets move, and the roller moves along the linear guides 40 with them.

15

Referring to FIG. 2, there is shown a calendar having roller 1 comprising five rolls 11,12,13, 14,15. The calender garden roller 11 is loaded upwardly by a lower cylinder 34. The upper roller is supported by a downwardly supported support 35, which may include an upper cylinder 35 for loading down the track.

To individually load the intermediate rolls 12,13,14, a support assembly 5 is provided on the rack 1 which is movable along the vertical portion 32 of the rack body. According to the basic idea of the invention, the support assembly can individually load the roll against another roll and thereby affect nip loading. For moving the roll relative to the nip plane, the support assembly includes a power adjustable length actuator 10, which is an adjustable length power cylinder 51, which may be a hydraulic and / or pneumatic cylinder and / or an electric screw.

Thus, the actuator 5 for moving the roll can individually adjust each nip load and, if necessary, the individual roll 12,13,14 can be removed from the 15 nip contacts. The ability to open the nip and move the roll out of the nip contact enables, for example, a problem roll damaged from its diaper surface, which not only causes damage to the web to cause vibration vibrations, can now simply move the web into a nipple unprocessed roll and continue processing without interrupting the paper machine.

20

In the embodiment of FIG. 2, to change the relative position of rolls 11, 12, 13, 14, 15 of roller 1, the roller actuator and roll support assembly 5 includes a vertical roller body 32 of movable relative to its vertical portion and adjustable in length. A power cylinder, preferably a hydraulic force cylinder, one end of which is attached to a roller bearing bracket 41 and the other end of which is slidably movable along the frame portion, wherein the force cylinder 52 for vertical positioning of the roller is movable vertically relative to the fixed support which is fixed to the vertical calender body 30 32. The bearing bracket 41 is movably fitted, for example, slidingly by means of a bracket projection 42, to the linear guide 40. The load on the power cylinder 51 then changes the length of the power cylinder and slides 40 n bearing brackets allow the roll to move away from the 16 original straight nipples in the NLS or vice versa. Depending on the magnitude of the movements generated, the new nip plane of the track 1 may be a kneeling nip plane NLS or an inclined nip plane NLK. The nip plane is a broken line nip plane NLM, the roll is loose from its nip contact or nip contacts.

5

It should be noted that other equivalent solutions for actuator 5 may be used. Suitable actuators include, for example: a rocker lever or lever arm loaded with a power cylinder; a rocker lever adjustable in length by means of a wedge means or the like; tiltable linear guide; an eccentric axis of a rocking lever joint or 10 linkage joints; a power-driven screw or spindle nut or toothed rack (not shown); linear guide line equipped with power-position controlled servohydraulics and linear motor; power toothed rack; or a device or arrangement based on another suitable positioning technique for deflecting or positioning the pivotable linear guide 40 away from its original inclined position with the rolls facing each other.

Referring to FIG. 3, there is shown a calender having roller 1 comprising five rolls 11,12,13,14,15. The lower roller 11 of the calender is loaded upwardly by the lower cylinder 34. To support the upper roller 15 and the intermediate rolls 12 ... 14, a support assembly 6 is provided in the roller.

20 The support assembly may support or load the roll individually against another roll. In this way, the support assembly can both influence the nip load and move the roll relative to the nip plane, thereby individually adjusting each nip load and, if necessary, moving the individual roll off the nip contact.

The ability to open the nip and move the roll out of the nip contact enables, for example, a problem roll damaged from its diaper surface that not only causes damage to the web to cause vibration vibrations, but can simply simply move the web into a nip into a unprocessed roll.

In the embodiment of FIG. 3, to change the relative position of the rolls 11,12,13,14,15 of the roller 1, the roller support assembly 6 includes a support arm 61 hinged to a vertical frame 17 body 32 of the roller, such as a swinging lever bearing bracket 41 and one end of which is loaded by a power cylinder 62 disposed between one end of the support arm and a power cylinder support projection 63 attached to a vertical frame portion of the track. The bearing bracket 5 is movably adapted to the linear guide 40, for example by means of a bracket projection 42. In this case, by applying a force cylinder, the rocker arm pivots about its rocking joint 65 and the bearing bracket arranged to move on the slider 40 moves along the linear guide. Depending on the magnitude of the movements generated, the new nip plane of the track 1 may be 10 - straight or nearly straight nip plane NLS, - inclined nip plane NLK, - kneeling nip plane NLP, or - fracture shaped nip plane NLM.

The movement of the rolls along the linear guides is illustrated in the figure by a double-headed arrow 15.

In the embodiment of Figure 3, the positions of the swing joint shafts in the vertical frame member 32 are differentiated. The differentiation can be accomplished, as shown in FIG. 3, by positioning the rocker joints 65 so that the rocker arms 61 are at different angles relative to the axis line RL passing through the axes of the rocker joints. When the force cylinders 62 produce the same deflection movement at the ends of the support arms, the movements of the rolls 11,12,13, 14,15 in the linear supports 40 are different with respect to each other.

To provide different lengths of roller movement along the linear conductors, the rocker arms 61 may also be pivotally mounted on the bearing brackets 41 such that the rocker arm anchoring points in the bearing brackets differ from each other so that the rocker arm movement around its rocker arms 65 causes corresponding displacements from the origin.

The displacement of the rolls 11,12,13,14,15 away from the original nip plane can also be achieved by moving the entire roller 1 by means of the rocking levers 61 having different mounting positions of the rocking joints 65 on the roll body 32 or bearing brackets with respect to the pivot points.

It should be noted that other equivalent solutions for providing the rocker lever 61 may be used. Suitable actuators for moving the roll include, for example: a rocker lever loaded by a power cylinder; a rocking lever adjustable in length by means of a wedge means or the like (compare FIG. 5); tiltable linear guide; eccentric rocker joint shaft; power-driven screw or spindle nut or gear rack; a linear guide 40 provided with power-position controlled servo hydraulics 10 and a linear motor; power toothed rack; or a device or arrangement based on another suitable positioning technique for deflecting or positioning the pivotable linear guide 40 away from its original inclined position with the rolls facing each other.

Reference is made to FIG. 4, which shows a calender having a roll 1 having five rolls 11, 12, 13, 14, 15. The lower calender 11 of the calender is loaded upward by a lower cylinder 34. The upper roll is supported by a lower support 35, .

Independently of the loading of the intermediate rolls 12,13,14, i.e. independent of the loading of the other rolls, a support assembly 8 is provided on the rack 1 for each intermediate roll. Each individual intermediate roll support assembly is pivotally attached to the rack body by a vertical member 32. affects nipple loading. To move the roll relative to the nip plane, the support assembly 25 includes a lever arm 81 which is pivoted about its pivot point 85 by an adjustable-length power unit 82, such as a length-adjustable power cylinder, for example a hydraulic and / or pneumatic power cylinder.

Thus, the support assembly 8, which acts as an actuator for moving the roll, can individually adjust each nipple load and, if necessary, move a single intermediate roll 12,13, 14 out of its nip contacts. The ability to open the nip and move the roll out of its nip contacts enables, for example, a problem roll 19 damaged from its diaper surface, which not only causes damage to the web to cause vibration vibrations, but can simply simply move the web into a nipple unprocessed roll and paper processing without interruption.

5, for changing the relative position of the rolls 11,12,13,14,15 of the roller 1, the support assembly 8 of each roll thus comprises a lever arm 81 with one end pivotally engaged in the vertical body and the other end pivotally attached to the roller. in the bearing bracket 41. The lever arm is loaded by a length adjustable power cylinder 82 having one end attached to the lever arm as shown in Figure 4, or 10 in a roller bearing bracket 41 and the other end pivotally engaging in a vertical frame member 32. The lever arm and one side thus the diameter of the whole triangle is adjustable.

The bearing bracket is movably mounted, e.g. slidingly, by a liner 42 on the linear guide 40. By loading the force cylinder, the lever arm pivots about its pivot point 85 and the slides 40 by the sliding bearing brackets move from the original straight nipple plane NLS or vice versa. Depending on the magnitude of the movements generated, the new nip plane of the track 1 may be a kneeling nip plane NLS or an inclined nip plane NLK. The nip plane is a broken line 20 nip plane NLM, the roll is loose from the nip contact or its nip contacts.

It should be noted that other equivalent solutions, i.e. length adjustable, for moving the lever arm can be used. Suitable actuators include, for example: tiltable linear guides; eccentric lever arm pivot; a screw or spindle nut or toothed bar driven by a power train 25; linear guide line equipped with power-position controlled servohydraulics and linear motor; power toothed rack; or a device or arrangement based on any other suitable positioning technique, capable of deflecting or positioning the pivotable linear guide away from its original inclined position which holds the rollers against each other.

Reference is made to FIG. 5, which shows a calender with roller 1 comprising five rolls 11,12,13,14,15. The lower roller 11 of the calendar is loaded upwards by the lower cylinder 34. To support the upper roller 15 30 20 and the intermediate rollers 12 ... 14, a support assembly 7 is provided on the roller. whereby each nipple load 5 can be individually adjusted and, if necessary, the individual roll removed from the nip contact.

The ability to open the nip and move the roll out of the nip contact allows, for example, a problem roll damaged from its diaper surface, which not only causes damage to the web to cause vibration vibrations, can now simply be moved to nipple 10 into a unprocessed roll.

In the embodiment of Figure 5, to change the relative position of the rolls 11,12,13,14,15 of the roller 1, the roller support assembly 7 includes a support arm 71 hinged to a vertical frame body 32 of the roller, such as a swinging lever with one end pivotally attached 41, the other end being loaded by a force cylinder 62. The support cylinder is disposed between one end of the support arm and the support cylinder projection 63 of the force cylinder attached to the vertical frame portion of the track. The roller bearing bracket is movably adapted, for example, by the bracket projection 42 to the linear guide 40. Then, by loading the power cylinder, the bracket pivots about its rocking joint 75 and the bearing bracket arranged to move by the bracket almost vertical nip plane NLS. Depending on the magnitude of the motion generated, the new nip plane of the track 25 1 may be a straight nip plane NLS or an inclined nip plane NLK or a meandering nip plane NLP or a molded nip plane NLM. The movement of the rolls along the linear wires is illustrated by a double-headed arrow.

The support assembly shown in FIG. 5 differs from another preferred embodiment of the invention described in connection with FIG. 3, in that in the embodiment of FIG. 5 the length of the rocker lever 71 is adjustable such that the movable roll 12,13,14 is movable relative to the original nip plane. 71 by means of a load force cylinder 62. The rocker lever is a telescopically elongated rocker lever. In the embodiment of FIG. 5, the force exerted on the actuator to adjust the length of the rocker lever comprises a wedge device assembly 7 whose axial movement in the transverse direction of the rocker lever lengthens and / or 5 restores the length of the rocker lever.

Another difference between the embodiment of Figure 3 and the embodiment of Figure 5 is that in the embodiment of Figure 5 the pivot points of the rocker arms 71 are not differentiated. However, a similar effect can be achieved if the individual rocker arms 10 use different settings for the wedge device adaptations.

In the wedge device assembly 7, movement of the wedge device 72 may be provided by a power unit 73, for example a hydraulic power unit or the like. It should be noted that other equivalent devices or arrangements 15 based on suitable positioning techniques can naturally be used.

It should be noted that instead of the rocker lever, the track support means and / or load means may also be a lever arm, and other equivalent actuator solutions for adjusting the rocker arm 61 or lever length can be used. Suitable alternatives to the keyway assembly 20 include, for example: - a telescopic rocker lever or lever arm acting on a roll bearing housing with a power cylinder, wherein turning the rocker lever or lever arm upward about its pivot point extends the rocker arm or lever lever; linear guide with servohydraulics; a power-driven screw or spindle nut or gear rack or the like; a propulsion system based on other suitable positioning techniques which can adjust the length of the rocker arm or lever; or a manual force means, such as a lever, a mechanical counterweight means or the like, for adjusting the length of the actuator.

30 22

The advantage of wedge adjustment is that wedge adjustment enables precise nip control by means of a force transducer, and that low wedge force provides high nip load, i.e. high line load on the nip.

Reference is made to FIG. 6, which shows a fifth preferred embodiment of the present invention for moving the rollers 12, 14 of the track 1 to change and then position the track rollers, adjusting the nip load and / or opening or closing the nip by a combination of angle and gravity.

In the embodiment of Fig. 6, a calender is shown schematically with roller 1 comprising five rolls 11,12,13,14,15. The calender lower roll 11 is loaded upwards by the lower cylinder 34 and the calender upper roll 15 is loaded down by the upper cylinder 35. The middle intermediate roll is stationary and, from below, the second roll and the fourth roll are nip-displaceable rolls. The original nip plane, with all the rollers of the roller 1 15 in a nip contact, is a nip plane NLP that bends vertically in relation to the power line.

The magnitude of the loading of the nipes between the rolls 11 ... 15 is based in this embodiment on the magnitude of the wedge forces 20 between the rolls wedging against each other. In this case, the rolls are wedged by moving the roll (s) in a linear direction along the rotating linear guides 40 of the pivot points 95. A high line load is obtained by changing the angle of the linear guide sharply upwards, whereby a strong wedge effect enhances gravity. Correspondingly, the quick opening of the nip is achieved by changing the angle of the linear conductor with respect to the horizontal plane downwards strongly. 25

In the embodiment of FIG. 6, the bearing brackets 41 of the intermediate rollers 12,13,15 of the calender roller 1 are fitted to the linear guides 40, for example by means of a bracket 42 of a bearing bracket forming the pivot point 95 of the linear guide 40. The lengths of the linear guides 30 can be dimensioned such that the length of the guide rail of the linear guide allows the nip to be opened and closed.

23

Although in the embodiment of FIG. 6 the original nip plane where the nipples are loaded is bending in the nip plane NLP, the nip plane may also be a straight, preferably vertical or near-vertical nip plane NLS or an inclined nip plane NLK.

When all rollers 11,15 of the calender 1 are in nip contact, i.e. the nipples are loaded, the linear guide is pivoted away from the horizontal transverse weight of the power line to an angle where the roll bearing and thus the movable roll 12 mounted thereon; The 14 rolls are forced to slide against their counter roll or counter rolls.

Generally, the nip load can be calculated by the formula Fy = M x G x sin (Ar), where M = roll number r mass, G = gravity constant 9.81 m / s, and Ar = roll loading angle.

15

To close the nip or increase the nip load, the linear guide 40 secured to the bearing housing 41 of the pivotally movable roll 12,14 is pivoted upwardly so that the movable roll slides in the linear guide against its counter rollers and the nip closes or increases nip load. It should be noted that the exact directions of the linear guides naturally depend on the direction of the individual linear guides selected. When the linear guide is rotated about its pivot point 95 in the opposite direction, i. in the embodiment of FIG. 6, the roll in the linear guide slides downwardly away from the original nip plane NLP where the rolls are facing each other. In this case, the rolls moving away from the 25 original nip planes open the nipples or the nip load is reduced by gravity and angle. It should be noted that the exact directions and tilt angles of the linear guides will naturally depend on the orientation of the individual linear guides.

In the embodiment of FIG. 6, the linear guide 40 is pivoted about the pivot point 95 30 by means of an adjustable length cylinder 92. The force cylinder may be, for example, a hydraulic and / or pneumatic force cylinder. Other actuators for rotating the linear guide are also equivalent alternatives. As other examples of 24 actuators for moving the roll and thereby opening or closing the nip or adjusting the nip load by means of a linear guide pivoting about its pivot point 95, mm may be mentioned: , 81 articulated shaft 101, 102, - power driven screw or spindle nut or toothed rack (not shown), for example, linear guide 40 provided with power-position controlled 10 servo-hydraulics and linear motor (not shown), - powered toothed rack, or.

another device or arrangement based on another suitable positioning technique for deflecting or positioning the pivotable linear guide 40 away from its original inclined position with the rolls facing each other.

15

The adjustment and / or opening of the nip load can also be performed manually by means of, for example, a hand lever (not shown in the figures). In the embodiment of Figure 6, both the loading of the nip and the closing and opening of the nip are by gravity, i.e. no great force is required since the torque arms, i.e. the length of the linear conductors, can be kept short.

The embodiment of FIG. 6 also makes it possible to use its own adjustable angle and thus individual nip load on the various nipples. It is also advantageous that the quick release of the nipples is simple only by turning the angle motor 25 which rotates the linear guide 40 in the opposite direction to when closing the nip or increasing the load on the nip.

If the nip line load of the rolls alone of the rolls 11 ... 15 is insufficient for calendering, small additional cylinders (not shown in the figures 30) are added to the linear guides of the rolls 40 to provide additional force.

25

A preferred embodiment of the embodiment of FIG. 6 is a nip plane that is inclined at an angle of 45 °. NLP. Sufficient nip force is achieved by pure gravity by allowing the wedge rollers 12,14 to move downward. The movable rolls then become wedged between the fixed rollers 11,13,15. The nipple load relief 5 can be implemented at relief pressures from below, which requires an actuator.

For angled track rollers, the quick release can be accomplished by dropping the movable roll (s) downwards.

Referring to FIG. 7, a sixth preferred embodiment of the present invention is shown for changing the relative positions of the rollers 11 ... 15 of the track 1 and adjusting the nip load. In the embodiment of Fig. 7, the actuator 5, 6,7, 8 transfers the wedge rollers 11 to 15, whereby the nip load and the nip load control are based on the wedge force of the rolls.

15

In order for the rolls 11 to 15 to be wedged against each other as they are moved, it is essential according to the invention that the spacing of the rolls which remain vertically fixed, preferably every other roll, is slightly smaller than the diameter of the rolls which are horizontally displaceable.

20

Generally, the nip load can be calculated by the formula Fy = M x G x sin (Ar), where M = roll number r mass, G = gravity constant 9.81 m / s2, and 25 Ar = roll loading angle.

In the embodiment of FIG. 7, every other roll in the calendar roller 1 is slightly different nip plane and movable horizontally, i.e. horizontally, preferably with actuator 5,6, 7, 8, away from the original nip plane, which is the nip plane NLP in FIG.

The actuator for opening the nip, i.e. moving the roll relative to the original nip plane 26, or towards the counter roll (s) can be selected quite freely. Suitable actuators include various length adjustable power units and pivotally swinging levers / levers. Examples of suitable actuators include: 5 - horizontal support arm and power cylinder mounted thereto, - rocker arm and lever arm, rocker arm or lever pivot shaft, - power driven screw or spindle nut or toothed rack, - linear guide fitted with power-position controlled servohydraulics and linear motor, or .

The operating principle of the embodiment of FIG. 7 is based on pushing horizontally movable rolls 11,13,15 vertically in order to load the nipples, so that in the final loading condition of the nipples, the nip plane is a bending nip plane NLP. The advantage of nip loading based on wedging is that a small horizontal force results in a large nip line load. There is also the advantage of being able to precisely adjust the nip load with a force sensor when the force sensor does not have to be dimensioned according to gravity 25

Referring to Figs. 8a, 8b and 9, a seventh preferred embodiment of the present invention is shown for changing the position of the rollers and eliminating the barring effect. A seventh embodiment is based on the fact that the hinge arm of the intermediate roll 12,13,14, for example a rocking lever 61, is pivoted on the roll body 32 or the roll bearing bracket 41 to move the roll.

27

In the past, attempts have been made to prevent the Barring phenomenon by changing the processing speed of the web and / or the loading of the nipples of the calender roller 1. In addition, various vibration dampers are known to eliminate the problem. However, it is not practically possible to change sufficient speed on on-line machines. Modifying the load on the nipples 5 is somewhat effective in addressing the problem, but the resulting variation in paper quality may prevent full utilization and will require the use of a large number of debris. The effectiveness of the vibration dampers is questionable, because in practice bearing-box-dampers are required.

A seventh embodiment is based on changing the dynamics of the track nipples such that stopping the onset of the oscillation problem by changing the position of the problem roll 12 relative to the original nip plane. According to a seventh embodiment, displacement of the problem roll in a problem situation can be accomplished by making the joints of the support arms of the roller rollers 12,13, 14 eccentric, i.e. by using the 15 eccentric axes of the support arm linkage 101,102. The joint may be located on the roll body 32 or roll bearing bracket 41 to effect displacement. When the joint is eccentric, the problem roll 12 may be displaced in the machine or MD direction during travel, as schematically illustrated in Figure 8b.

The arrangement of the seventh embodiment is effective on a barring type in which a soft-surface, such as polymer-coated, roll shell is wavy by an excitatory mechanism that can result from irreversible deformation or wear. Barring not only reduces the available web quality, it also causes significant losses.

25

Figure 9 shows a typical vibration shape of roll 12 associated with the barring problem. In the example case, the frequency is 289 Hz and 31 waves are deformed on the polymer surface of the roll.

According to the invention, the development of the phenomenon is stopped by changing the excitation produced by the waviness of the coating of the roll 12 from an "odd-wave excitation" to an "even-wave excitation". Of course, the same can be done the other way around. After the roller 28 has been moved, the roller set 1 can no longer receive additional vibration energy to the shape that caused the original problem. Because the problem roll is an intermediate roll, the roll has a roll above and below the problem roll that are in the same phase. As the roller causing the problem is moved, the corrugation 5 of the coating tends to force the rolls above and below to run in opposite directions. Thus, a change in the form of vibration is obtained.

When roller 12 is deflected away from its original nip plane, it is likely that roller 1 will no longer vibrate in a new form at the "characteristic frequency" or at least at the same 10 frequencies. The problem can be removed and the roll re-circulated if timely action is taken.

The onset problem at odd wave number is illustrated by a solid line in Figure 9 when the nip plane is a vertical nip plane NLP. The roll 12 is moved approx.

15 a quarter of a wavelength, whereby the new nip plane is represented by a straight line drawn in the image.

In order to apply the seventh embodiment, it is necessary to know or guess with some accuracy the wave number which tends to develop on the surface of the roll 12. In the example of Figure 9, wave numbers 21, 31, and 41 are shown. Within this range of wave numbers, the invention can still be effectively applied using only the "roll overlap" and "roll over off" modes.

If there are even more different wave numbers at the same roll position, the amount of roll overlap must also be varied to achieve an "even - odd" effect. Of course, changing the dynamics per se (without controlling the excitation phasing of the upper and lower nip) also has a deadly effect on the barring phenomenon.

In a seventh embodiment, the oscillation measurement (e.g., SENSIDEC + STA) identifies an incoming 30 barring, - identifies the problem roll (and wave number if variable interleaving is used), and modifies the interleaving.

29 The vibration now continues as a forced vibration for some time. Tracks 1 no longer oscillates at its "characteristic frequency" because the changed form of oscillation is not at least a characteristic of the type. excitation frequency. In this case, the vibration dampens as the smooth surface 5 of the roll 12 is leveled.

The oscillation may begin to evolve again, now to an even wave number, e.g., the original 31-wave excitation vibration will evolve into a 32-wave excitation. The vibration would then be the same as the original. The problem is solved by moving the roll 12 to its original position because the vibrations of the "odd" waveform excitation and the even wave excitation are different.

Referring to Fig. 10, which illustrates an eighth preferred embodiment of the present invention for hanging rolls 11, ..., 15 of the track 1 on the track frame 31, 15 32, 33. To move the rolls away from the original nip plane, the roller bearing housings are fitted with linear guides. In this case, the relative position of the rolls is adjustable.

Current bearing and suspension solutions for rollers 11, ..., 15 have a force ring in which nip forces are transmitted from the lower part of the frame through the roller shells to the upper part of the track body. In this case, the roll shell acts as a resilient element and flattens under the effect of loading. Such a combination of track and chassis is naturally susceptible to harmful excitations of the track, such as large roll vibrations due to thermal roll deformation, poor rolls or vibrations due to soft coating deformation. Such a combination also delivers the vibrations of the track to the frame and foundation of the 25 calendars.

In contrast to the prior art, in addition to the horizontally displaceable rolls 11 ... 15 of the eighth embodiment of the invention, a matching member 10a, 1b is provided in the roller between the bearing housings of the rolls 11 ... 15. Here, a roller 30 is provided with a force ring extending from the lower part of the track body 31,32, 33, for example from the lower cylinder 34, between the bearing housings 41 of the rolls through the opposing counter members 10a, 10b to the upper part of the track 1 body 32,33, 30 or a fixed track load counterpart 36. The force is greater than the nip load.

The embodiment of FIG. 10 includes a bearing housing which is bearing, preferably 5 sliding bearing, on the neck of the roller 11, ..., 15, in the preferred embodiment of the roller 12, 13, 14, and secured to the roller body by linear guide 40. The sliding bearing housings 10b.

When closing the track, for example with the lower cylinder 34, the counter members 10a, 10b meet and a force circle is formed which is greater than the nip load caused by the line load. In the force ring, the forces pass from the lower cylinder 34 through the bearing housings and counter members 10a, 10b to the top of the frame.33. The force circle thus formed does not have a resilient element caused by the shell of the rollers 11, ..., 15.

The counter members 10a, 10b may be attached to the bearing housings 41 and thus be adjustable to correspond to the milled diameter of the roll 11 ... 15. When the track 1 closes, there is no line load between the tracks. The line load is created by diaphragm loaded roller rollers 11, 13. Lightening of the intermediate rollers 12,13,14 is accomplished by means of a plain bearing with a vertical impact. In the quick release, the nipples are opened by the lower roller 20 11 and the load on the intermediate roller and the roller suspensions is transferred to the appropriate auxiliary cylinders.

With the embodiment of FIG. 10, the calender body 31,32, 33 and the track 1 can be made rigid and the body and track set integrated into a vibration damping unit. In addition, the invention allows the reduction of the intermediate roll 12, 13, 14 to be effected with less friction and thus to improve the line load control of the nip. The invention further enables the roll to be supported more rigidly and the calender speed increased.

By means of the invention, the frame and the track can be converted into a system for better vibration damping. Slide bearings provide vibration damping fluid damping and higher roller speeds. The force circle provided by the invention reduces the number of machine members involved in the elasticity of the track to support the machine structure. Due to its good damping properties, the invention limits the vibrations caused by the roll more to the internal phenomenon of the roll, thus less stress on the frame and foundations.

5 Seals currently used in power cylinders, such as hydraulic cylinders, for example in reels, presses and calendars, have a large difference between rest friction and motion friction. If the adjustment required is small, or if the adjustment requires only small changes in the required force, the difference between rest friction and motion friction will cause significant problems. In practice, either the pressure applied to the cylinder 10 is unable to overcome the friction at rest and the cylinder does not move at all, or the high friction causes the pressure to build up in the cylinder which causes a delay and eventually the pressure builds up to jerk the cylinder. . The problem is aggravated by the fact that as the gasket ages, the phenomenon becomes stronger and gasket wear becomes faster.

15

It is an object of the invention to reduce this problem and provide fine-tuning of the seals used in the cylinders in demanding applications, such as those requiring adjustment of the nip load on the track, so that their resting and motion friction are as close as possible to each other.

20

If the material friction between movement and resting friction are close to each other, the cylinder can be operated substantially without any visible adjustment.

The largest group of materials that meet the criteria are carbon materials. In this case, especially graphite-rich materials which, due to the self-lubricating properties of graphite, have very low friction and very little difference between rest friction and motion friction are preferred. With regard to cylinders, such materials are sufficiently resistant to surface pressure and also have good wear resistance.

However, if wear is considered to be a problem, fiber reinforced graphite composites can be introduced. These wear are significantly reduced compared to both graphite materials not reinforced with current sealing materials. Furthermore, the friction properties of the reinforced graphite composites 32 are very similar to those of non-reinforced graphite materials. The most significant drawback is that the reinforced graphite composite is non-elastic, which in practice results in the gasket having to be redesigned using at least a two-piece gasket or by applying 5 labyrinth sealing solutions for dynamic shaft seals.

The biggest benefits of better or essentially jerk-free process control are.

Adjustment accuracy improves; the typical torque produced by hydraulic cylinders is 10 orders of magnitude 5-10 kN / m while the internal torque loss of the cylinders used for adjustment is 2-3 kN / m - thus, it is very difficult for current cylinders to adjust for example a 5% increase in nip line pressure. With the cylinder according to the invention, where the seals have substantially smaller resting friction and movement friction close to each other, the internal torque loss is reduced, so that a 5% increase in the nip line pressure, for example, can be achieved more easily.

- Line pressure adjustment accelerates. The line pressure monitoring is facilitated because by using the seals according to the invention, there is no longer a great difference between rest friction and motion friction, so that when the pressure is increased, energy is no longer stored and the desired loading pressure is immediately applied to the calender / press.

20 - The aging of the seals slows down. Existing seals are aging rapidly and, for example, the friction and wear properties are markedly reduced.

- The carbon materials of the invention are not known to exhibit aging effects. It is also not known that the wear properties of carbon materials change over time. Thus, the life of the gasket is increased due to the absence of the aging phenomenon on the carbon materials.

- Carbon materials allow the use of water hydraulics in the cylinders, which allows replacing the more expensive and more environmentally friendly oil with water.

The invention has been described above by way of embodiments only by way of example. As will be apparent to those skilled in the art, the invention is not limited to the embodiments described but many and functionally alternative and equivalent solutions 33 and various combinations and alternatives of individual partial solution solutions are possible within the scope of the inventive concept defined in the appended claims.

In particular, it should be emphasized that the present invention is limited in scope to industrial usability only in fiber web machines, since the present invention can also be applied in other fields of technology where opposed loading rolls are used in material processing. The present invention is applicable to both the wet end and the dry end of fiber web machines, particularly with respect to any pair of rollers in which 10 rolls loaded against each other and thus forming a nip are used. Specific applications in fiber web machines include various types of press sections, drying section, coating section, machine calender and other calenders.

*

Claims (23)

A track assembly, wherein the web material is passed through a nip or nip formed by opposing rolls of at least two rolls (11,12; 12,13; 5 13,14; 14,15), wherein the nip or nipples form a vertical weight. vertical nip plane (NLS) or tilted nip plane (NLK) or kneeling nip plane (NLP) or broken line nip plane (NLM) with respect to the power line, characterized in that at least one roll of the track (1) is displaceable along 10 linear guides (40) NLS, NLK, NLP, NLM). A track assembly according to claim 1, characterized in that the movable roll (11, 12, 13, 14, 15) is movable to completely open the nip from its nip contact with the counter roll (s). 15 A track assembly according to claim 1 and / or 2, characterized in that each roll (11, 12, 13, 14, 15) of the track (1) is movable with respect to and / or out of the original nip plane (NLS, NLK, NLP, NLM). from the original nip plane independently of the other tracks on the track. 20 A track assembly according to claim 3, characterized in that the intermediate rolls (12, 13, 14) at least between the top roll (15) and the lower roll (11) of the track (1) are movable relative to the original nip plane (NLS, NLK, NLP, NLM). and / or off the nip plane. 25 5 G = gravity constant (9.81 m / s), A = roll loading angle. A track assembly according to claim 3, characterized in that the soft surface intermediate rolls (12, 14) in the track (1) at least between the top track (15) and the lower track (11) are displaceable relative to the original nip plane (NLS, NLK, NLP, NLM) and / or off the nip plane. 30 A track assembly according to any one of claims 1 to 5, characterized in that in the track (1) having a nip plane which is a meandering nip plane (NLP), the distance between each other roll (11,13; 13,15) is smaller than that of the roll ( 12; 14) diameter measurement. A track assembly according to any one of claims 1 to 6, characterized in that the 5 movable rolls are movable with or without an actuator (5, 6, 7, 8, 9) in a direction different from the original nip plane (NLS, NLK, NLP, NLM). A track assembly according to claim 7, characterized in that the direction deviating from the original nip plane (NLS, NLK, NLP, NLM) may be parallel to the machine direction, i.e. MD direction, or may form an angle in the web direction or in the opposite direction of the web direction. 90. A rig assembly according to any one of claims 1 to 8, characterized in that the actuator acting on the bearing bracket (41) of the movable roll (11 ... 15) with a linear guide 15 is preferably included in the movable roll support means and / or loading means (5). , 6, 7, 8, 9), and which actuator exerts an external load to move the roll along the linear guides (40) and is adjustable in length. A track assembly according to claim 9, characterized in that the actuator is selected from the group consisting of: • a power cylinder (51), which is preferably a hydraulic and / or pneumatic power cylinder; an adjustable rocker lever (61, 71) or a lever arm (81) or the like, such as a lever, a mechanical counterweight means, or 30. other means adjustable actuator length. A rack assembly according to any one of claims 1 to 8, characterized in that the actuator acting on the bearing bracket (41) of the movable roll (11, ... 15) with the linear guide (40) is preferably included in the movable roll support means and / or to the loading means (5, 6, 7, 8, 9) and providing 5 external loading for moving the roll along the linear guide (40) is selected from the group consisting of: • a power cylinder, preferably a hydraulic and / or pneumatic power cylinder • a power cylinder or the like loadable rocker arm or lever arm, 10. eccentric axis of rocker arm or lever arm joint, power unit to apply an external load acting on the bearing bracket or, thus, to move the roll in the linear guides. A rack assembly according to any one of claims 1 to 8, characterized in that the actuator 20 for moving the roll (11 ... 15) comprises an eccentric axis of the rocker arm (61, 71) or the pivoting arm (81) acting on the roll bearing. A track assembly according to claim 12, characterized in that the eccentric shaft is disposed on a pivot joint which is connected to the roll bearing bracket or by means of which the pivoting support of the rocker arm (61, 71) or the lever arm (81) is arranged on the track body (32). A track assembly according to any one of claims 1 to 8, characterized in that the actuator for moving the roll (11 ... 15) along the linear guide (40) associated with the roll bearing bracket (41) comprises a tiltable linear guide. A track assembly according to claim 14, characterized in that the tiltable linear guide (40) is provided with a power unit based on a suitable positioning technique, whereby the linear guide can be deflected or pivoted away from its original, preferably upwardly inclined position. A track assembly according to claim 15, characterized in that the power unit is selected from the group consisting of: • a power cylinder, which is preferably a hydraulic and / or pneumatic power cylinder 10, • a rocking lever or lever nut driven by a power cylinder or the like; A linear motor equipped with servo-hydraulics, or a corresponding power unit based on other suitable positioning techniques, or 15. a manual force means such as a lever, a mechanical counterweight means or another power means for tilting the linear guide (40) associated with the roller bearing bracket (41); A rig assembly according to any one of claims 1 to 8, characterized in that adjusting the nip load or closing or opening the nip is based on gravity and wedges of the rolls (11-15) of the tilted rack (1) with the original nip plane relative to the vertical tilted kneeling nipple (NLP). A track assembly according to claim 17, characterized in that the roll (1) is inclined preferably 45 °, whereby the nip load can be increased above the tilted track and allow sufficient nip loading only by wedging the track. A rack assembly according to any one of claims 1 to 18, characterized in that the ramp is inclined with respect to a vertical gravitational line having an original nip plane either a straight nip plane (NLS) or a tilted nip plane (NLP) or a fractured nip plane , the magnitude of the nip flutter can be determined by the formula Fy = M x G x sin (A), where M = mass of the roll, 'j A track assembly according to any one of claims 1 to 19, characterized in that the bearing housing (41) of the roll (11 ... 15), mounted on the roll neck, is secured to the body of the track 10 (1) by means of guide means (40). greater than the force exerted by the nip load, means (10a, 10b) are provided for forming between the bearing housings of the superimposed rollers, which hit each other when the track nipples are closed, the forces being transmitted from the lower part (31) of the track body and the track members to the upper part of the body (33) such that the roller has no elasticity caused by the roller casings. A track assembly according to claim 20, characterized in that the counter members (10a, 10b) are attached to the bearing housings (41), wherein the counter members can be modified 20 to correspond to the milled diameter of the roll. A track assembly according to any one of claims 1 to 21, characterized in that the material of the seal used in the force cylinder (51, 52, 62, 82, 92) is selected such that the material has a substantially equal or close frictional friction. A track assembly according to claim 20, characterized in that the material of the gasket is a carbon-based material, preferably a graphite-rich carbon-based material, more preferably a fiber-reinforced graphite composite.