WO2006108555A1 - Procede de raffinage de fibres de papier ou de cellulose en suspension aqueuse et dispositif de raffinage permettant de mettre en oeuvre ledit procede - Google Patents

Procede de raffinage de fibres de papier ou de cellulose en suspension aqueuse et dispositif de raffinage permettant de mettre en oeuvre ledit procede Download PDF

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Publication number
WO2006108555A1
WO2006108555A1 PCT/EP2006/003142 EP2006003142W WO2006108555A1 WO 2006108555 A1 WO2006108555 A1 WO 2006108555A1 EP 2006003142 W EP2006003142 W EP 2006003142W WO 2006108555 A1 WO2006108555 A1 WO 2006108555A1
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WO
WIPO (PCT)
Prior art keywords
grinding
drum
rollers
grinding drum
grinding device
Prior art date
Application number
PCT/EP2006/003142
Other languages
German (de)
English (en)
Inventor
Harald Hess
Michael Kramer
Wolf Gunter Stotz
Original Assignee
Voith Patent Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Voith Patent Gmbh filed Critical Voith Patent Gmbh
Publication of WO2006108555A1 publication Critical patent/WO2006108555A1/fr

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Classifications

    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21D—TREATMENT OF THE MATERIALS BEFORE PASSING TO THE PAPER-MAKING MACHINE
    • D21D1/00—Methods of beating or refining; Beaters of the Hollander type
    • D21D1/20—Methods of refining
    • D21D1/34—Other mills or refiners
    • D21D1/38—Other mills or refiners with horizontal shaft

Definitions

  • the invention relates to a method according to the preamble of claim 1.
  • pulp fibers are ground in a knife refiner, their drainage resistance increases with increasing milling.
  • a common measure of the drainage resistance is the degree of grinding according to Schopper-Riegler.
  • the increase in the freeness has an unfavorable effect on sheet formation on the paper machine, but is tolerated, since the already mentioned quality characteristics of the pulp play a paramount role for its applicability.
  • the grinding parameters are selected so that the degree of freeness which has occurred in order to achieve the required fiber quality is as low as possible. This influence is very limited. In addition, the grinding can be economically unfavorable.
  • the fiber length is much better preserved. 2.
  • the fiber surface is not or significantly less fibrillated.
  • This milling process is also called compression milling.
  • DE 894 499 shows a grinding apparatus which has a circulating grinding drum, on the inner wall of which several grinding rollers are pressed in order to grind pulp.
  • the grinding rollers are provided with special circumferential grooves in order to achieve a certain desired grinding action can.
  • the grinding device is not equipped for continuous driving.
  • the webs delimiting the grooves or grooves are provided with teeth on the outside.
  • teeth are apparently intended to effect or improve the cleaning of the grinding tools.
  • the invention is based on the object to provide a continuous process, with which it is possible to mill pulp or paper fibers so that the advantages of compression grinding can be used.
  • the process should be suitable for use on an industrial scale in the production of paper.
  • Claim 37 specifies a grinding device for carrying out the method according to the invention.
  • the features of the invention make it possible in a special way, even larger amounts of paper fibers, such as those incurred in paper production in a paper mill, to mill in a particularly economical manner.
  • the hitherto known possibilities for loading the substance (generation of grinding forces) in the grinding zones work with technical devices for generating force, whose forces are transmitted to the rotating grinding rollers, for example via bearings mounted on both sides. This means a considerable effort with a variety of highly loaded bearings and possibly drives. Furthermore, it is inevitable, as a result of the deflection of the grinding rollers over the axial extent uneven formation of grinding forces to obtain.
  • the grinding force is an essential parameter determining the grinding success, so that uneven or uncontrollable grinding forces can lead to a significantly poorer grinding result. The disadvantages are avoided by the invention.
  • the grinding rollers can be guided by means of laterally mounted bearings in a correspondingly moving support structure.
  • This support structure can . be provided with sliding seats for the bearings of the grinding rollers, for example, is ensured by the limited radial mobility of the grinding rollers.
  • a certain relative speed between the grinding rollers and the inner wall of the grinding drum may be desired, which is at least possible if in the grinding zone no kinematics of the roller movement determining toothing is used.
  • Figure 1 An example for carrying out the method according to the invention with
  • Figure 2 The grinding device of Figure 1 in a sectional side view, greatly simplified.
  • FIG. 3 shows another grinding device for carrying out the method
  • FIG. 5 an example of a modular grinding device
  • FIG. 6 a grinding device according to the invention without a central body
  • FIG. 8 A similar grinding device as shown in Figure 7 in another view.
  • FIG. 9 a longitudinally grooved grinding roller
  • FIG. 10 c Various transversely grooved grinding rolls
  • FIG. 11 a drilled grinding roller
  • FIG. 12 a grinding device with integrated pre-drainage
  • FIG. 13 Another grinding device according to the invention.
  • the grinding apparatus shown in Fig. 1 has a lying grinding drum 1, in which a number of evenly arranged over the circumference
  • Grinding roller 2 and grinding drum 1 each have a grinding zone, at the point at which the inner wall of the grinding drum 1 and the outer wall of the
  • Grinding rollers 2 are closest. In order to produce the necessary grinding force, the grinding rollers 2 are pressed by means of centrifugal forces 7 radially against the inner wall of the grinding drum 1. Preferably, this is the only measure for
  • a central body 3 is used, which is arranged concentrically with the grinding drum 1 and generates a particularly advantageous rotational movement.
  • the grinding rollers 2 and the central body 3 with an external toothing 5 and 6 and the grinding drum 1 is provided with an internal toothing 4. These teeth are engaged, so that when driving e.g. the central body 3 both a rotational movement of the grinding rollers 2 takes place about their own axes, as well as a rotational movement of the rollers themselves around the center of the central body 3. So superimposed on the rotational movement of the grinding rollers 2 about its center line with a rotational movement of the center lines around the center of the Central body 3.
  • the centrifugal force 7 depends on the weight of the grinding roller 2 and its rotational movement about the center of the central body 3. Due to the fact that central body 3 and grinding roller 2 can be driven separately, both rotational movement of the grinding rollers to their own center, as well as to the center the central body 3 can be adjusted freely. This has the advantage that the kinetic grinding conditions and the grinding forces can be optimized independently of each other. If, for example, the rotational speed of the grinding rollers is specified for reasons of grinding technology, the centrifugal forces 7 increase when the grinding drum 1 and the central body 3 are driven in the same direction (dashed arrow). By opposing drive they can be greatly reduced, or it can be transmitted at the same centrifugal forces significantly more pressure pulses for grinding the fibers.
  • the throughput can also be controlled by such variations.
  • the grinding drum 1 or the central body 3 can be fixed in the circumferential direction. Then, however, eliminates a degree of freedom in the choice of operating settings.
  • the grinding rollers 2 do not require their own drive, whereby the grinding device used is much easier.
  • a storage of the grinding rollers 2 is not required here.
  • Di.e teeth 4 and 5 or 6 must be chosen so that the grinding rollers 2 are movable with a radial clearance so that they follow the centrifugal force 7 and can transmit them as a grinding force.
  • the pulp suspension due to the centrifugal forces as a pulp view of light 18, of which only a part is drawn here create on the inner wall of the grinding drum 1.
  • FIG. 2 is roughly schematically the grinding device of Fig. 1 in a side view in section.
  • the central body 3 with the grinding rollers 2 peripherally surrounding it and the radially outer end of the grinding drum 1 can be seen.
  • the central body 3 is driven via a left drive shaft 9 and the grinding drum 1 via a right drive shaft 10.
  • the fiber suspension S can be centrally introduced through a material line 11, which is located in the left drive shaft 9 of the central body 3 and pass through corresponding bores radially outward into the grinding drum 1.
  • the fiber suspension S is distributed on the inner wall of the grinding drum 1 due to the centrifugal forces. It then flows in the axial direction through the grinding zones, until it is removed again on the axial opposite side as a ground fiber suspension S ' .
  • a circumferential locking ring 14 is provided which serves as a weir. In order to allow the emptying of the grinding drum 1 when parking, the locking ring 14 may be interrupted.
  • a similar function is in the in Fig. 3 The grinding device shown achieved by the fact that the outlet 13 'radially further inward than the refining zones.
  • FIG. 1 The kinematic design of the grinding device described in connection with FIG. 1 is a relatively simple technical realization. But it may also be useful not to use the actual grinding surfaces to drive the grinding rollers, but at least one end face of the grinding rollers 2, the external teeth 5 ' and also to make the milling drum 1 and central body 3 accordingly.
  • FIGS. 3 and 4. Such a variant is shown in FIGS. 3 and 4.
  • Fig. 3 shows a sectional side view of the varied grinding rollers 2 ' and the varied central body 3 ' .
  • teeth 4 ' , 5' and 6 ' On both sides of the grinding rollers 2 ' and on the central body 3 ' are teeth 4 ' , 5' and 6 ', the similar, as already described, interlock and determine the kinematic processes in the grinding device.
  • the grinding surface itself that is, the surfaces of the grinding rollers 2 ' and the inner surface of the grinding drum 1 ' can be made as desired by the grinding technology.
  • a groove profile is conceivable, but may have a deviating from a standard toothing shape.
  • Such grooves may, for example, extend axially or circumferentially or obliquely or helically. This orientation also influences the axial conveyance of the suspension in the milling zones.
  • support members 23 such as slip rings.
  • Fig. 3 an alternative (which is also conceivable in other embodiments).
  • the suspension S to be ground is added here by the drive shaft of the grinding drum 1 ' and discharged on the opposite side, ie where the drive shaft of the central body 3' is located.
  • Fig. 4 the relationships in the area of the toothing are shown in somewhat greater detail, without this being a construction drawing.
  • the toothing can be seen, which serves to move the grinding rollers 2 in the desired manner and in which there is basically a toothing on the grinding surfaces (example in Fig.
  • the grinding rollers 2 are next to the grinding surfaces (example in Fig. 3) can. If the toothing lies on the grinding surfaces, then the grinding zone 24 is located mainly in the part of the toothing wetted by the fibrous material layer 18. To give the grinding rollers 2 the opportunity to follow the centrifugal forces to the outside, a certain radial play is present in the teeth. In the operating state shown here, ie in rotating grinding rollers, they press into the internal teeth 4 of the grinding drum 1. As a result, the distance in the other teeth (5 with 6) is correspondingly larger, without there the engagement of the teeth is lost.
  • the grinding roller 2 is here drawn as a hollow cylinder, but it is also conceivable to perform them fully or with a core of another material, eg to give it the highest possible weight and thus to produce correspondingly large centrifugal forces 7.
  • a modular construction as indicated in Fig. 5 may be very useful.
  • a total of three grinding sections are shown here in the axial direction, in such a way that the teeth 4 ' and 5 ' and 6 'are provided at certain axial distances from each other.
  • the grinding rollers 2 ' can be assembled as modules. Since an axial transport of the fiber suspension to be ground is generally conducted through the grinding device, it may also be useful to provide different grinding surfaces in different modules, since the material is changed on its axial path through the device and possibly different grinding technology requirements result.
  • Fig. 6 shows the possibility of spatially positioning the grinding rollers 2 by means of laterally mounted bearings 17. This means that here measures have been taken to move the axes or center lines of these grinding rollers 2 by means of engaging these bearings holding or moving elements.
  • These holding or moving elements would, for example, be supported in one or two holding devices 19 mounted laterally of the grinding drum 1, wherein this holding device 19 must be set in rotation in order to be able to move the center lines of the grinding rollers 2 around the center of the grinding drum 1 on a circular path 8.
  • the grinding drum 1 can stand still, but in general, these will also be rotated so that a suspension layer can form on its inner wall.
  • the lateral bearings can be held by parallel guides 20 or pivot lever guides 21 or cantilevered torsion springs 22.
  • FIG. 6 to simplify the drawings, several possibilities are indicated in a single grinding apparatus, the combination of these possibilities being rather uncharacteristic in a single machine.
  • the embodiment shown in FIG. 6 on the basis of the grinding roller 2 shown as the uppermost one is shown somewhat more accurately in FIG.
  • the grinder shown here has a total of eight grinding rollers 2 ' , of which only seven are shown. These are spatially positioned by means of laterally mounted bearings 17 and are guided by parallel guides 20 in at least one, usually two holding devices 19 ' . Grinding drum 1 ' and holding device 19 ' can be moved in opposite directions (arrows 37 and 38) or in the same direction (arrows 37 and 39).
  • the holding device 19 ' may be substantially disc-shaped with parallel guides 20 open towards the outer periphery. As a result of this arrangement, the grinding rollers 2' may be light be mounted and adjust radially during operation.
  • the holding device is provided with spokes or slots 26 in order to improve the axial flow of the suspension flow in the grinding device.
  • the holding device 19 ' is driven by the concentric with the grinding drum 1 ' mounted shaft 25.
  • the grinding drum 1 ' no teeth on to drive the grinding rollers 2 ' . Therefore, in the grinding zone 24, a certain relative movement of the grinding surfaces to each other possible, which may be in certain circumstances of grinding technology advantage.
  • the grinding drum here has a smooth inner wall (grinding surface), so it is not grooved. The interaction of smooth drum wall and grooved grinding rollers is often particularly advantageous.
  • a similar device as shown in FIG. 7 is drawn in a side sectional view.
  • the fiber suspension S is introduced radially outward into the grinding drum 1 ' , so that it engages with rotating grinding drum on the inner wall. Since a continuous axial transport of the fiber suspension S takes place during continuous operation of the grinding device, it can be discharged on the opposite end face of the grinding drum through one or more outlets 13 into the annular channel 28. It may be advantageous that within the annular channel 28 at least one blade 29 is located, which also rotates, for example, to the grinding drum 1 'is attached.
  • Such a blade 29 can prevent the settling of pulp in the annular channel 28. This is then removed as a ground fiber suspension S ' from the underlying fabric outlet 30. It can also be seen from this illustration that both the drive of the holding devices 19 ' and the drive 27 of the grinding drum 1 ' can be arranged on the same side, namely in the bearing block 16. In such a case, the bearing block 15 of the other side can be relatively easily built because it contains no drives. Such a design facilitates the opening of the grinding drum 1, for example, after separation from the end plate 31st
  • the grinding rollers can be provided with different grinding surfaces. Thus, the grinding roller shown in Fig. 9 includes a larger number of longitudinal grooves.
  • Such an embodiment leads in the milling zone to a high number of pressure pulses on the fibrous suspension to be ground, which is desirable in many cases.
  • the grooves 32 and webs 33 may be on a flat helix, since by the slope of such a helix of the axial transport of the suspension on the inner wall of the grinding drum can be influenced, so supported or braked.
  • the grooves 32 have a groove width A, which is advantageously between 3 and 8 mm, with the smaller values tend to be more favorable in the grinding of short fiber.
  • the width B of the webs 33 is conveniently between 2 and 5 mm.
  • the ratio A to B is generally to be chosen so that the number of webs 33 and the available grinding surface on its circumference are as large as possible.
  • a value below 2 even better 1 or smaller.
  • the depth C of the grooves 32 may be between 5 and 30 mm.
  • the grinding rollers may be composed of discs. By selecting the discs, grooves and bars can be slightly varied. Even the replacement of worn discs is easily possible.
  • the discs either sit on a continuous roller shaft or are connected directly (without shaft). In order to change the weight of the grinding rollers, they can be filled with liquid or have exchangeable weights.
  • a plurality of holes 34 are incorporated in the periphery.
  • Such holes can favor the local dewatering of the pulp suspension and therefore lead to a higher consistency in the milling zone.
  • the water which collects in these bores can be spun off after leaving the grinding zone or be discharged inwards through corresponding channels.
  • Their diameter is best between 0.5 mm and 3 mm.
  • Hard surfaces, such as steel, can work together or soft surfaces, such as plastics or hard rubber. Special possibilities result from the combination of hard and soft materials.
  • the grinding drum can be provided with a soft layer against which hard grinding rollers are pressed. The reverse driving is conceivable.
  • the grinding surfaces with a porous surface, e.g. with a corresponding coating of sintered metal, which favors the local dewatering of the pulp.
  • the method can be further improved, at least for certain applications, by increasing the consistency of the fiber suspension S to be ground before being fed to the grinding zone 24.
  • a predewatering zone 35 may be provided in the grinding device, which is arranged on the end face of the grinding drum, to which the fiber suspension S is supplied.
  • a part of the grinding drum 1 upstream of the grinding zone 24, a part of the grinding drum 1 "can be provided with a sieve 36 which separates the pulp from the water W.
  • Fig. 13 the measures that serve the Axialtransport to be ground or ground pulp suspension, shown in more detail, without this is already a construction drawing.
  • an outlet ring 46 is mounted, which thus closes the grinding drum on this side and rotates at the same speed as this.
  • the pulp suspension located inside the grinding drum 1 ' can be conveyed out through an outlet 13, more preferably through a plurality of outlets 13, into an outlet chamber 48. This is delimited by the outlet ring 46 and one axially thereto beabstand 'eten annular disk 47.
  • the outlet chamber 48 is at least partially open at its outer diameter to a peripheral thereto arranged fixed annular channel 28th In this case, this annular channel 28 is sealed against the rotating parts.
  • the fabric outlet 30 At the lower end of the annular channel is the fabric outlet 30 for the discharge of the ground fiber suspension S ' .
  • the bearing 40 of the grinding drum 1 ' is supported on the shaft 25 via this outlet ring 46.
  • the bearing 40 serves to accommodate the relative movements of shaft 25 and grinding drum 1 ' . It is also expedient to transmit the drive of the grinding drum Y via this outlet ring 46, to which purpose the drives 27 can only serve.
  • an inlet sleeve 44 is rigidly connected to the shaft 25 on the inlet-side end face, so that the bearings 41 and 42 can be provided on the outer circumference of this inlet sleeve 44.
  • the bearing 41 takes the relative speed between the grinding drum 1 ' and shaft 25 and the bearing 42, the relative speed of the shaft 25 relative to the fixed bearing block 15.
  • the inlet sleeve 44 can be kept relatively large to the largest possible free flow cross-section for the supplied fiber suspension S. to obtain.
  • a core 51 and a number of spokes 45 are provided.
  • the non-rotating inlet 49 can be sealed with advantage over a sliding coupling 43 with respect to the interior of the inlet sleeve 44.
  • the measures taken in connection with FIG. 13 are particularly suitable for solving the long-standing problem of constructing a grinding device with which it is possible to achieve the grinding technology required for compression grinding, even with larger quantities of material, such as those needed for paper production to achieve.

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Abstract

La présente invention concerne un procédé de raffinage de fibres de papier ou de cellulose basé sur le fait qu'il n'existe aucune ou seulement une faible vitesse relative entre les éléments de raffinage travaillant conjointement, mesurée dans le sens de déplacement des éléments de raffinage, contrairement au cas d'un raffineur à lame par exemple. Dans un tambour de raffinage (1), un ou plusieurs cylindres de raffinage (2) se déplacent en tournant sur eux-mêmes et sont guidés sur une trajectoire circulaire (8) dont le centre coïncide avec celui du tambour de raffinage (1). En raison du déplacement susmentionné, les cylindres de raffinage (2) sont comprimés depuis l'intérieur contre le tambour de raffinage (1), sous l'effet de forces centrifuges (7). A l'aide des entraînements du tambour de raffinage (1) et des cylindres de raffinage (2), il est possible de commander la cinématique du dispositif de raffinage utilisé. Les cylindres de raffinage (2) sont guidés de manière à conserver une certaine mobilité en direction radiale, afin de pouvoir laisser agir les forces centrifuges comme des forces de raffinage.
PCT/EP2006/003142 2005-04-09 2006-04-06 Procede de raffinage de fibres de papier ou de cellulose en suspension aqueuse et dispositif de raffinage permettant de mettre en oeuvre ledit procede WO2006108555A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005016318.1 2005-04-09
DE200510016318 DE102005016318A1 (de) 2005-04-09 2005-04-09 Verfahren zur Mahlung von wässrig suspendierten Papier- oder Zellstoffasern sowie Mahlvorrichtung zu seiner Durchführung

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WO2006108555A1 true WO2006108555A1 (fr) 2006-10-19

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PCT/EP2006/003142 WO2006108555A1 (fr) 2005-04-09 2006-04-06 Procede de raffinage de fibres de papier ou de cellulose en suspension aqueuse et dispositif de raffinage permettant de mettre en oeuvre ledit procede

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WO (1) WO2006108555A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202019101661U1 (de) 2018-03-26 2019-07-12 Pasi Ahonen Vorrichtung zur Faserbearbeitung für die Herstellung einer Faserbahn

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008056978A1 (fr) * 2006-11-06 2008-05-15 Agrotechnology And Food Innovations B.V. Appareil de traitement d'une matière de pâte fibreuse
DE102007003964A1 (de) * 2007-01-26 2008-01-24 Voith Patent Gmbh Verfahren zur Erzeugung von Holzstoff

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2289013A (en) * 1938-06-04 1942-07-07 Haug Anton Joseph Machine for working paper stock and similar materials
DE894499C (de) * 1940-02-16 1953-10-26 Belgique Papeteries Vorrichtung zum Behandeln von Fasergut, insbesondere Papierstoff
WO1986006427A1 (fr) * 1985-04-29 1986-11-06 Beloit Corporation Procede et appareil de traitement de pulpe
DE10236962A1 (de) * 2002-08-13 2004-02-26 Institut für Papier-, Zellstoff- und Fasertechnik der Technischen Universität Graz Verfahren zur Faserstoffbehandlung
WO2005019528A1 (fr) * 2003-08-18 2005-03-03 Voith Paper Patent Gmbh Procede de raffinage de fibres de papier ou de cellulose en suspension aqueuse

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2289013A (en) * 1938-06-04 1942-07-07 Haug Anton Joseph Machine for working paper stock and similar materials
DE894499C (de) * 1940-02-16 1953-10-26 Belgique Papeteries Vorrichtung zum Behandeln von Fasergut, insbesondere Papierstoff
WO1986006427A1 (fr) * 1985-04-29 1986-11-06 Beloit Corporation Procede et appareil de traitement de pulpe
DE10236962A1 (de) * 2002-08-13 2004-02-26 Institut für Papier-, Zellstoff- und Fasertechnik der Technischen Universität Graz Verfahren zur Faserstoffbehandlung
WO2005019528A1 (fr) * 2003-08-18 2005-03-03 Voith Paper Patent Gmbh Procede de raffinage de fibres de papier ou de cellulose en suspension aqueuse

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202019101661U1 (de) 2018-03-26 2019-07-12 Pasi Ahonen Vorrichtung zur Faserbearbeitung für die Herstellung einer Faserbahn

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