EP4127310B1 - Vorrichtung zur mahlung einer faserstoffsuspension - Google Patents

Vorrichtung zur mahlung einer faserstoffsuspension Download PDF

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Publication number
EP4127310B1
EP4127310B1 EP21712970.9A EP21712970A EP4127310B1 EP 4127310 B1 EP4127310 B1 EP 4127310B1 EP 21712970 A EP21712970 A EP 21712970A EP 4127310 B1 EP4127310 B1 EP 4127310B1
Authority
EP
European Patent Office
Prior art keywords
shaft
fluid
bearing
shaft bearing
refiner
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP21712970.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP4127310A1 (de
EP4127310C0 (de
Inventor
Thomas Reisinger
Peter Ortner
Daniel HOGUE
Christian HARPIN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Andritz AG
Original Assignee
Andritz AG
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
Priority claimed from ATA50275/2020A external-priority patent/AT523590B1/de
Application filed by Andritz AG filed Critical Andritz AG
Publication of EP4127310A1 publication Critical patent/EP4127310A1/de
Application granted granted Critical
Publication of EP4127310C0 publication Critical patent/EP4127310C0/de
Publication of EP4127310B1 publication Critical patent/EP4127310B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • D21D1/30—Disc mills
    • D21D1/303—Double disc mills
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C7/00—Crushing or disintegrating by disc mills
    • B02C7/11—Details
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C7/00—Crushing or disintegrating by disc mills
    • B02C7/02—Crushing or disintegrating by disc mills with coaxial discs
    • B02C7/08—Crushing or disintegrating by disc mills with coaxial discs with vertical axis
    • 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
    • D21D1/30—Disc mills
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C7/00—Crushing or disintegrating by disc mills
    • B02C7/11—Details
    • B02C7/14—Adjusting, applying pressure to, or controlling distance between, discs

Definitions

  • the invention relates to a refiner for beating fibrous materials in a fibrous stock suspension, comprising a shaft, a rotor disk firmly connected to the shaft and a shaft bearing, the rotor disk being arranged between two stator disks to form a grinding chamber between the rotor disk and the stator disks, the shaft being movable in an axial direction, at least one stator disk being displaceable in the axial direction, the size of the grinding chamber being adjustable via the distance between the stator disks and the rotor disk between the stator disks being adjustable via a movement of the shaft in the axial direction is movable.
  • Refiners - or the described double disc refiners - are known in different designs.
  • a rotor disk typically rotates between two stationary stator disks, with the rotor disk or the stator disks being equipped with grinding plates.
  • the fibrous material in suspension is ground in the grinding space between the rotor disk and the stator disks.
  • a uniform distribution of the grinding pressure in the grinding chamber and thus in the area between the rotor disk and the first stator disk and in the area between the rotor disk and the second stator disk is essential. To do this, the rotor must be able to move axially.
  • Various solutions are known in the prior art.
  • the aim of the invention is a refiner with reduced wear of the rotor disks and stator disks and in particular the refining plates on these disks.
  • the shaft bearing is hydraulically connected to the grinding chamber.
  • “hydraulically connected” means that a fluid—preferably water—can be transferred between the shaft bearing and the grinding chamber is.
  • a fluid preferably water
  • continuous stream threads of the fluid between the shaft bearing and the grinding chamber can be represented or given.
  • the smooth-running axial mobility of the shaft and thus of the rotor disk, which is firmly connected to the shaft, is an essential prerequisite for the fibrous material present in a suspension in the grinding chamber, i.e. in the area between the rotor disk and the first stator disk and in the area between the rotor disk and the second stator disk, to be ground evenly, since the grinding pressure is distributed evenly in the grinding chamber.
  • the even distribution of the grinding pressure results from the independent and smooth positioning of the rotor disc between the stator discs. Any resistance to positioning, e.g.
  • the fixed connection of the rotor disk to the shaft means that there is no axial displaceability between the shaft and the rotor disk and therefore no relative movement in the axial direction between the shaft and the rotor disk.
  • the connection between the rotor disk and the shaft can be detachable, which can be important for service and installation.
  • a favorable embodiment of the refiner is characterized in that the rotor disk is firmly connected to the shaft inside or outside the shaft bearing.
  • the shaft is thus mounted on both sides of the rotor disc or cantilevered. Bearing the shaft of a refiner on both sides of the rotor disk allows for an even and distributed bearing load, but not a very compact design, since the shaft bearing is designed on both sides of the rotor disk.
  • the rotor disk is firmly connected to the shaft at a first end of the shaft and the rotor disk lies outside of the shaft bearing.
  • the shaft is connected to a motor via a coupling, the coupling being outside of the shaft bearing.
  • the overhung storage of the rotor disk together with the hydraulically connected shaft bearing according to the invention a very compact design.
  • An advantageous embodiment of the refiner is characterized in that the shaft is mounted exclusively on fluid-lubricated slide bearings. This allows the shaft to move particularly easily in the axial direction of the shaft.
  • the shaft is mounted on both sides of the rotor disk, only fluid-lubricated plain bearings are arranged on both sides of the rotor disk. If the shaft is cantilevered, the rotor disk is firmly connected to the shaft at a first end of the shaft and the shaft is mounted exclusively via fluid-lubricated plain bearings, with the shaft bearing being arranged between the rotor disk and a second end of the shaft.
  • a further advantageous refinement of the refiner is characterized in that the shaft bearing is designed as a fluid-lubricated slide bearing, with a fluid, preferably water, being able to be fed to the grinding chamber via the shaft bearing.
  • a fluid preferably water
  • the design as a water-lubricated plain bearing is particularly advantageous.
  • water can be supplied to the grinding chamber via the water-lubricated plain bearing.
  • the use of water as a fluid means the possibility of realizing an oil-free shaft bearing, which means that contamination of the fibrous suspension by oil or hydraulic oil is ruled out. It is particularly advantageous to provide forced guidance to ensure a flow direction of the fluid—preferably water—through the fluid-lubricated slide bearing into the grinding chamber.
  • the fluid in the shaft bearing has a higher pressure than the fibrous suspension in the grinding chamber in the area where the fluid is fed into the grinding chamber. Due to the higher pressure of the fluid in the shaft bearing, the fluid flows in the direction of the grinding chamber, which advantageously effectively prevents contamination of the shaft bearing or the water-lubricated plain bearing.
  • the water-lubricated slide bearing is always flushed in the direction of the grinding chamber and the smooth movement of the shaft is maintained over the operating time.
  • a further favorable refinement of the refiner is characterized in that a seal is arranged between the grinding chamber and the shaft bearing.
  • the shaft bearing is designed as a fluid-lubricated plain bearing, with a fluid, preferably water, being able to be fed to the grinding chamber through the shaft bearing via the seal.
  • An advantageous embodiment of the seal includes a shaft sealing ring or a throttle ring.
  • the seal is arranged, for example, between the shaft and the bearing housing, inserted into a recess in the bearing housing and fixed in the bearing housing via a fixing ring.
  • the shaft is guided through the seal, with the seal being in contact with the shaft in the case of a shaft seal, or with a gap between the shaft and the seal in the case of a throttle ring.
  • Seals advantageously have at least one sealing lip.
  • seal has a sealing effect that is dependent on the direction of flow of the fluid.
  • seals include oil seals or throttle rings.
  • the sealing effect dependent on the direction of flow can be realized in that, for example, when the fluid flows in a direction from the shaft bearing to the grinding chamber, the fluid or the fluid pressure lifts the seal from the sealing surface and/or the seal releases a larger flow cross section for the fluid.
  • the seal is designed with a sealing lip, the sealing lip being designed in the shape of a truncated cone in order to form a sealing effect depending on the direction of flow.
  • a seal with a frustoconical sealing lip can be arranged in such a way that the shaft is guided inside the seal, with the axial direction of the shaft and the axis of the frustoconical sealing lip coinciding.
  • the seal is clamped in the bearing housing and the truncated cone-shaped sealing lip is guided against the shaft.
  • a flow of the fluid from the base to the imaginary cone tip of the truncated cone-shaped sealing lip then leads to the sealing lip widening, to the seal being lifted off the shaft or at least to a Reduction of the contact pressure of the seal against the sliding surface or shaft, which is decisive for the seal and the sliding friction. If the direction of flow is reversed in this first example - ie a flow of the fluid from the imaginary apex of the cone to the base of the frustoconical sealing lip - the fluid would press the sealing lip against the shaft and lead to an increase in the contact pressure of the sealing lip.
  • the seal is clamped to the shaft, for example, and the truncated cone-shaped sealing lip is oriented towards the bearing housing.
  • a flow of the fluid from the base to the imaginary cone tip of the frustoconical sealing lip then leads to an expansion of the base area and thus to increased contact pressure of the sealing lip and an improved sealing effect against the bearing housing.
  • Seals that have a sealing effect that is dependent on the direction of flow of the fluid are advantageous, since when the fluid flows in accordance with the desired direction of flow, very little or no friction losses of the seal can be realized. With a reversal of the direction of flow, however, the best possible seal can be implemented and a flow of the fluid counter to the desired direction of flow can be reduced or avoided.
  • An equally advantageous embodiment of the refiner is characterized in that when the fluid flows through the shaft bearing into the grinding chamber, the seal has a sealing effect that is less than when the fluid flows out of the grinding chamber into the shaft bearing.
  • Seals that have a sealing effect that is dependent on the flow direction of the fluid are advantageous because they allow very little or no friction losses in the seal when the fluid flows in the desired flow direction from the shaft bearing into the grinding chamber.
  • this behavior is advantageously reversed, since the best possible seal is required when the fluid flows from the grinding chamber into the shaft bearing, in particular to prevent the fibrous suspension from flowing from the grinding chamber into the shaft bearing and thus avoiding contamination of the shaft bearing by the fibrous materials.
  • a further advantageous refinement of the refiner is characterized in that a damping element is assigned to the shaft bearing, with the damping element being preferably between the rotor disk and a motor between the rotor disc and a clutch, the clutch being arranged between the rotor disc and the engine.
  • the bearing according to the invention allows the shaft to move so easily in the axial direction that, surprisingly, jerky movements of the shaft can occur during operation, which should be avoided.
  • the clutch can provide a small amount of damping, for example due to friction effects in the clutch.
  • this is not sufficient, which is why the arrangement of a damping element is advantageous in order to ensure uniform movements of the shaft in the axial direction.
  • the damping element is hydraulically connected to the shaft bearing.
  • the damping element includes, for example, a damping area and a throttle element.
  • the throttle element can, for example, be designed as a throttle ring, with the throttle ring being arranged between the shaft and the bearing housing and largely covering the gap between the shaft and the bearing housing.
  • the damping area is formed, for example, by an area between the shaft, bearing housing and throttle element, with the damping area being arranged between the shaft bearing and the clutch.
  • the damping element is hydraulically connected to the shaft bearing, i.e.
  • the fluid - preferably water - which can be fed to the shaft bearing is also fed to the damping element, with continuous streams of fluid between the shaft bearing, ie the fluid feed to the shaft bearing and the damping element being able to be represented.
  • the volume of the damping area changes, with an increase in the volume causing fluid to flow into the damping area via the throttle element and a reduction in the volume causing fluid to flow out of the damping area via the throttle element.
  • a damping effect results in accordance with the viscous losses of the fluid as it passes through the throttle element.
  • the arrangement of the damping element between storage and clutch is advantageous because it is so there is no hydraulic influence on the seal, since the bearing is arranged between the seal and the damping element.
  • An equally advantageous embodiment of the refiner is characterized in that the pulp suspension can be fed to the grinding chamber via an inlet area or through the shaft.
  • This advantageous bearing allows shaft diameters to be realized that allow the fibrous suspension to be fed through the shaft to the grinding chamber, and in contrast to the use of conventional roller bearings, larger shaft diameters can also be realized in a technically sensible manner.
  • a further advantageous embodiment of the refiner is characterized in that the rotor disk is designed with openings, with the openings providing a uniform distribution of the fibrous suspension that can be fed via the inlet area or via the shaft in the grinding chamber.
  • the fibrous stock suspension is fed to the refiner on one side of the rotor disk, with the fibrous stock suspension being able to be fed directly into a first gap between a first stator disk and the rotor disk.
  • the fibrous suspension can also be fed to the second side of the rotor disk through the openings in the rotor disk, with the fibrous suspension being able to be guided into a second gap between a second stator disk and the rotor disk.
  • An advantageous embodiment of the refiner is characterized in that the shaft is connected to a motor via a coupling, the movement of the shaft in the axial direction being able to be absorbed by the coupling. Since the motor is arranged immovably and the shaft is advantageously movable in the axial direction, a relative movement in the axial direction between the shaft and the motor can be accommodated via the coupling.
  • a particularly advantageous embodiment of the refiner is characterized in that the coupling is designed as a curved tooth coupling and the shaft can move radially and/or axially in the curved tooth coupling.
  • the shaft is designed with external teeth in the area of the coupling and is connected to the motor via a coupling spacer that has internal teeth. In the case of maintenance, there is very good accessibility to the refiner by dismantling the adapter.
  • curved tooth couplings In addition to the movement of the shaft in the axial direction, curved tooth couplings also allow a movement in the radial direction. Curved-tooth couplings also allow the external gearing of the shaft and the internal gearing of the coupling spacer to perform a wobbling movement when the shaft rotates, with permanent sliding friction occurring between the gearings.
  • Curved-tooth couplings also allow the external gearing of the shaft and the internal gearing of the coupling spacer to perform a wobbling movement when the shaft rotates, with permanent sliding friction occurring between the gearings.
  • a rotor disk 2 is arranged on a shaft 1 in a housing 19 , the rotor disk 2 being movable in the axial direction 7 relative to the shaft 1 .
  • the pulp suspension is fed to the refiner 17 via an inlet area 12 and is distributed through openings 13 (not shown) in the rotor disc 2 in the grinding chamber 6.
  • the pulp suspension is ground in a first grinding gap between the rotor disc 2 and the first stator disc 4 and in a second grinding gap between the rotor disc 2 and the second stator disc 5 and leaves the refiner 17 via the outlet area 18.
  • At the rotor disc 2 or the St ator discs replaceable grinding plates are arranged.
  • the second stator disk 5 can be moved in the axial direction 7 via an adjusting device 20 and the distance between the stator disks 4.5 or between the rotor disk 2 and the stator disks 4.5 can be adjusted.
  • the axial mobility of the rotor disk 2 on the shaft 1 allows the rotor disk 2 to be centered independently between the stator disks 4.5, with comparable grinding gaps being established.
  • This embodiment of the refiner 17 provides no mobility of the shaft 1 in the axial direction 7, the shaft bearing 3 as Rolling bearing is running. Shaft bearing 3 and grinding chamber 6 are clearly separated.
  • the roller bearings are oil-lubricated.
  • a seal 8 seals the grinding chamber 6 or the inlet area 12 against the shaft 1. The introduction of oil into the grinding chamber 6 is to be prevented by design, and no fibrous material suspension may get into the oil circuit of the roller bearing.
  • a rotor disk 2 is arranged on a shaft 1 in a housing 19 , the rotor disk 2 being fixedly connected to the shaft 1 and the shaft 1 being movable in the axial direction 7 .
  • the pulp suspension is fed to the refiner 17 via an inlet area 12 and is distributed through openings 13 (not shown) in the rotor disc 2 in the grinding chamber 6.
  • the pulp suspension is ground in a first grinding gap between the rotor disc 2 and the first stator disc 4 and in a second grinding gap between the rotor disc 2 and the second stator disc 5 and leaves the refiner 17 via the outlet area 18.
  • At the rotor disc 2 or the St ator discs replaceable grinding plates are arranged.
  • the second stator disk 5 can be moved in the axial direction 7 via an adjusting device 20 and the distance between the stator disks 4.5 or between the rotor disk 2 and the stator disks 4.5 can be adjusted.
  • the axial mobility of the shaft 1 and thus of the rotor disk 2, which is firmly connected to the shaft 1, allows the rotor disk 2 to be centered independently between the stator disks 4.5, with comparable grinding gaps being established.
  • the shaft 1 is connected to a motor 10 (not shown) via a coupling 11 , the coupling 11 being able to absorb the movement of the shaft 1 in the axial direction 7 .
  • the shaft 1 is cantilevered via a shaft bearing 3 , the rotor disk 2 being arranged outside of the shaft bearing 3 .
  • the shaft bearing 3 is hydraulically connected to the grinding chamber 6 .
  • the shaft bearing 3 is designed as a fluid-lubricated slide bearing 23, with a fluid—preferably water—serving as a lubricating medium in the shaft bearing 3 and being at least partially feedable to the grinding chamber 6 via the shaft bearing 3.
  • the seal 8 arranged between the shaft bearing 3 and the grinding chamber 6 limits the amount of fluid that flows between the shaft bearing 3 and the grinding chamber 6 in accordance with the pressure conditions. The fluid is advantageously guided in a targeted manner from the shaft bearing 3 in the direction of the grinding chamber 6 .
  • a seal 8 with a sealing effect that is dependent on the direction of flow of the fluid.
  • a seal 8 is particularly advantageous which, when the fluid flows through the shaft bearing 3 into the grinding chamber 6, has a sealing effect which is less than when the fluid flows from the grinding chamber 6 into the shaft bearing 3. In this way, with a higher pressure in the grinding chamber 6 and a lower pressure in the shaft bearing 3, a flow of fibrous suspension from the grinding chamber 6 into the shaft bearing 3 can be minimized or prevented.
  • the refiner 17 also includes a damping element 9 which is assigned to the shaft bearing 3 .
  • the damping element 9 is arranged between the rotor disk 2 and the motor 10 (not shown) and preferably between the rotor disk 2 and the clutch 11.
  • the damping element 9 can be hydraulically connected to the shaft bearing 3, with the damping element 9 comprising a damping area 15 and a throttle element 16.
  • the fluid supplied to the shaft bearing 3 flows through the shaft bearing 3 and also fills the damping area 15.
  • the volume of the damping area 15 can be changed by a movement of the shaft 1 in the axial direction 7, with an increase in volume of the damping area 15 fluid flowing to the damping element 9 and a reduction in volume of the damping area 15 fluid flowing out of the damping element 9, the fluid flowing through the throttle element 16 to the damping area 15. or drains off.
  • the fluid is fed to the shaft bearing 3 via a fluid inlet 21 and flows through the fluid-lubricated plain bearing 23 or fills the damping area 15.
  • the seal 8 is arranged between the shaft bearing 3 and the grinding chamber 6 and limits the amount of fluid that flows according to the pressure conditions between the shaft bearing 3 and the grinding chamber 6, with the majority of the fluid being discharged from the shaft bearing 3 via the fluid return 22.
  • the fluid is advantageously guided in a targeted manner in the direction of the grinding chamber 6 by a greater pressure of the fluid in the shaft bearing 3 compared to the pressure in the grinding chamber 6 .
  • the damping element 9 is hydraulically connected to the shaft bearing 3, and includes the damping area 15 and the throttle element 16.
  • the throttle element 16 is in 3 connected to the shaft 1, the damping area 15 being delimited by the shaft 1, the bearing housing 14 and the throttle element 16.
  • the volume of the damping area 15 can be changed by moving the shaft 1 in the axial direction 7, with fluid flowing into the damping element 9 when the volume of the damping area 15 increases, and fluid flowing out of the damping element 9 when the volume of the damping area 15 decreases, the fluid flowing in and out of the damping area 15 in each case via the throttle element 16.
  • Figure 4a and Figure 4b each show an advantageous seal 8 of the shaft bearing 3, which allows a sealing effect dependent on the direction of flow of the fluid.
  • the seal 8 is fixed in the bearing housing 14 via a fastening element 24 , sealing lips 25 being guided against the shaft 1 .
  • the direction of flow is reversed, i.e.
  • a seal 8 with two free-standing sealing lips 25 is shown.
  • a seal 8 with two sealing lips 25 is shown, with a free-standing sealing lip 25 being arranged closer to the shaft bearing 3 and the sealing lip 25, which is arranged closer to the grinding chamber 6, does without a cavity 26 oriented towards the grinding chamber 6, which advantageously prevents fibrous material from being stored and possibly hardening in the cavity 26 oriented toward the grinding chamber 6.
  • the present invention thus offers numerous advantages. Particularly advantageous is the low wear of the rotor discs and stator discs - and in particular the grinding plates on these discs, which is achieved by the very easy positioning of the rotor disc, which is also maintained in continuous operation.
  • the solution according to the invention makes it possible to avoid contamination by fibrous material in the sealing area and bearing area.
  • the storage according to the invention avoids the risk of oil contamination of the fibrous suspension, since the storage can be operated oil-free and the risk of contamination of the storage by the fibrous material is eliminated or is minimal.
  • the storage according to the invention also allows a more compact design of the refiner and, above all, a shorter overall length.

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  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Paper (AREA)
EP21712970.9A 2020-04-01 2021-03-12 Vorrichtung zur mahlung einer faserstoffsuspension Active EP4127310B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA50275/2020A AT523590B1 (de) 2020-04-01 2020-04-01 Vorrichtung zur mahlung einer faserstoffsuspension
PCT/EP2021/056317 WO2021197805A1 (de) 2020-04-01 2021-03-12 Vorrichtung zur mahlung einer faserstoffsuspension

Publications (3)

Publication Number Publication Date
EP4127310A1 EP4127310A1 (de) 2023-02-08
EP4127310C0 EP4127310C0 (de) 2023-07-26
EP4127310B1 true EP4127310B1 (de) 2023-07-26

Family

ID=76876009

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21712970.9A Active EP4127310B1 (de) 2020-04-01 2021-03-12 Vorrichtung zur mahlung einer faserstoffsuspension

Country Status (4)

Country Link
US (1) US20230047528A1 (pt)
EP (1) EP4127310B1 (pt)
CN (1) CN113164967B (pt)
BR (1) BR112022013920A2 (pt)

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB745987A (en) * 1954-02-17 1956-03-07 E D Jones & Sons Company A refining apparatus, attrition mill or the like
CH410612A (de) * 1962-01-15 1966-03-31 Sprout Waldron & Co Inc Schleifmühle
NO128777B (pt) * 1962-08-08 1974-01-07 K Thomas
US3323731A (en) * 1963-07-01 1967-06-06 Defibrator Ab Grinding apparatus primarily for lignocellulose containing material
IT964369B (it) * 1971-09-17 1974-01-21 Escher Wyss Gmbh Dispositivo di macinatura in par ticolare per l industria carta ria
SE380848B (sv) * 1974-03-27 1975-11-17 Sca Development Ab Anordning for raffinering av fibermaterial
US4036443A (en) * 1974-10-03 1977-07-19 Beloit Corporation Refiner head assembly and refining disk therefor
SE419659B (sv) * 1976-03-19 1981-08-17 Rolf Bertil Reinhall Sett och anordning for framstellning av fibermassa av fiberformigt lignocellulosahaltigt material
US4081147A (en) * 1976-05-27 1978-03-28 The Black Clawson Company Reversible disk refiner plates
US4083503A (en) * 1976-10-08 1978-04-11 Beloit Corporation Paper stock rotor axial position controlling and locking device
SE422224B (sv) * 1978-08-07 1982-02-22 Berggren Torsten L Malmaskin for behandling av fiberuppslamningar, sasom pappersmassa, samt styckeformigt malgods, sasom treflis och span
CA1246374A (en) * 1983-10-24 1988-12-13 Steve Rowland Two stage high consistency refiner
US5011091A (en) * 1989-08-10 1991-04-30 Haybuster Manufacturing Inc. Cellulose fiberization apparatus
SE467343B (sv) * 1990-10-03 1992-07-06 Sunds Defibrator Ind Ab Lagersystem i en raffineringsapparat foer framstaellning av massa
SE9201448L (sv) * 1992-05-08 1993-11-01 Sunds Defibrator Ind Ab Anordning för raffinering av fibermaterial innefattande två motstående malskivor av vilka åtminstone den ena uppbäres av en roterbar axel lagrad i ett stativ
US5445328A (en) * 1993-08-25 1995-08-29 Andritz Sprout-Bauer, Inc. Dual zone refiner with separated discharge flow control
US5564634A (en) * 1994-03-31 1996-10-15 Rouse; Michael W. Rubber comminuting apparatus
JP2950780B2 (ja) * 1996-09-24 1999-09-20 相川鉄工株式会社 ダブルディスクリファイナ−
JP4245272B2 (ja) * 1997-10-09 2009-03-25 サーモ・ブラック・クローソン・インコーポレーテッド 製紙用パルプ精製機制御装置および方法
US6673211B2 (en) * 2001-07-11 2004-01-06 Voith Paper Patent Gmbh Apparatus for loading fibers in a fiber suspension with calcium carbonate
DE202006002999U1 (de) * 2006-02-24 2007-06-28 Voith Paper Patent Gmbh Scheibenrefiner zum Mahlen von Faserstoffmaterial

Also Published As

Publication number Publication date
BR112022013920A2 (pt) 2022-10-11
US20230047528A1 (en) 2023-02-16
EP4127310A1 (de) 2023-02-08
CN113164967A (zh) 2021-07-23
EP4127310C0 (de) 2023-07-26
CN113164967B (zh) 2022-02-25

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