EP2582457B1 - Rollenpresse mit momentenwaage - Google Patents

Rollenpresse mit momentenwaage Download PDF

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Publication number
EP2582457B1
EP2582457B1 EP11719234.4A EP11719234A EP2582457B1 EP 2582457 B1 EP2582457 B1 EP 2582457B1 EP 11719234 A EP11719234 A EP 11719234A EP 2582457 B1 EP2582457 B1 EP 2582457B1
Authority
EP
European Patent Office
Prior art keywords
roller press
bearing housings
rolls
machine frame
torque balance
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.)
Not-in-force
Application number
EP11719234.4A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2582457A1 (de
Inventor
Meinhard Frangenberg
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.)
KHD Humboldt Wedag AG
Original Assignee
KHD Humboldt Wedag 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
Application filed by KHD Humboldt Wedag AG filed Critical KHD Humboldt Wedag AG
Publication of EP2582457A1 publication Critical patent/EP2582457A1/de
Application granted granted Critical
Publication of EP2582457B1 publication Critical patent/EP2582457B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B3/00—Presses characterised by the use of rotary pressing members, e.g. rollers, rings, discs
    • B30B3/04—Presses characterised by the use of rotary pressing members, e.g. rollers, rings, discs co-operating with one another, e.g. with co-operating cones
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C4/00—Crushing or disintegrating by roller mills
    • B02C4/28—Details
    • B02C4/32—Adjusting, applying pressure to, or controlling the distance between, milling members
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides

Definitions

  • the invention relates to a roller press for pressure treatment or compaction granular Guts having at least two each rotatably mounted on a shaft in a machine frame and driven in opposite directions and separated by a nip, designed as Loswalzen rollers, the waves of the rollers received in the machine frame movably arranged bearing housings and wherein in each case two bearing housings of different rollers arranged on one side of the rollers are connected to one another via at least one pressure cylinder and a method for centering a roller gap of a roller press.
  • a first roller is fixedly mounted as a fixed roller in the machine frame in bearings in the simplest case, which in turn are secured by bearing housings in a machine frame to consoles.
  • a second roller is stored as a Loswalze in camps, the arranged in between two consoles of the machine frame movably arranged bearing housings.
  • the hydraulic drives for relative positioning of the floating roller relative to the hard roller and to maintain the pressure in the nip exert high forces on the machine frame as an abutment, for which it is necessary to design the machine frame accordingly stable.
  • roller presses with rollers with a weight of up to 50 t a correspondingly large dimensions of the machine frame is necessary so that the logistics of the machine frame and its handling in a necessary and regular change of the rollers is complicated and only with correspondingly large-sized cranes and removal aids possible ,
  • this roller press is in the DE102007059072 proposed to use a hydraulic double cylinder, which is fixed to the machine frame.
  • this hydraulic double cylinder two adjacent hydraulic chambers work and are supported against each other.
  • the force of the hydraulic cylinder acting on the nip is not transmitted to the machine frame.
  • the object of the invention is therefore to develop the roller presses so that while maintaining the self-contained and largely separate from the machine frame power system, the centering is made easier and less expensive to manufacture.
  • connection of the bearing housing in each case has at least one torque balance.
  • Further advantageous embodiments of the invention are specified in the subclaims.
  • the process object of the invention is achieved by the use of the moment scale according to claim 10.
  • a torque balance is understood to mean a rocker-like or pendulum-like suspension, on which pairs counteracting, first and second hydraulic cylinders engage opposite arms of the torque balance. These counteracting hydraulic cylinders in each case alone cause the tilting of the torque balance in the direction of the related hydraulic cylinder.
  • This change in position of the torque balance on the opposite side of the first hydraulic cylinder has the effect that there is more stress on the opposite second hydraulic cylinder and therefore the control circuit of the now more heavily loaded second hydraulic cylinder builds up a higher pressure and counteracts the first hydraulic cylinder until the torque scale back in is positioned in its equilibrium position.
  • the first and the second hydraulic cylinder have in the roller press according to the invention a rotatably configured clutch, so that the first and the second hydraulic cylinder can also attack at an angle to the arms of the torque balance.
  • a rotatably configured clutch By this rotatable coupling, it is possible that the rollers of the roller press can not assume mutually parallel positions, which is always the case when a larger grain outside the center of the nip passes through the nip or when the nip is loaded unevenly with ground material .
  • the effect of the torque balance is that a rolling centering is forced via a simple, movably mounted, mechanical element, provided that the hydraulic cylinders operating to generate the pressure in the nip work against each other.
  • the torque scale can be constructed asymmetrically or symmetrically.
  • the symmetry of the torque balance especially the unequal length of the boom, reflects the Torque scale the different size and rated load capacity of the opposite hydraulic cylinder again.
  • a symmetrical configuration of the torque balance which is arranged approximately centrally between the bearing housings, is preferred. In this case, two identical hydraulic cylinders or at least two hydraulic cylinders with the same nominal load capacity and the same characteristic curve are used on the same length cantilevers of the torque balance.
  • the torque balance is preferably rotatably mounted about a vertical axis of rotation which lies in a plane which is spanned by the center line of the nip and the vertical. Due to the vertical axis of rotation, the torque scale rotates in a horizontal plane and thus allows a skewing of the rollers to each other, the torque balance on this misalignment has a balancing effect, so that the rollers experience a misalignment of a force that causes after return of the roller press in equilibrium position, the rollers of the roller press are again parallel to each other.
  • the torque balance on a rocker with two arms via which the two bearing housing of the roller press are connected to each other, and the torque scale has a rotatably mounted pendulum, via which the rocker is pivotally mounted with the two arms about the axis of rotation , Due to the pendulum, the rocker of the torque balance with the two arms rotates about a pivot point outside the line of force between the two hydraulic cylinders, which pull on the opposite arms of the torque scale.
  • the hydraulic cylinders are loaded in the roller press according to the invention only to train.
  • the torque balance has the effect that the distance between the hydraulic cylinders is minimized to each other and thus aligns the torque balance. This causes the centering effect on the nip.
  • two bearings of two different rollers are formed on one side of the roller press as a fixed bearing and two bearings on the opposite side of the roller press are designed as a floating bearing.
  • the floating bearings allow axial movement of the shaft in the bearing, so that the change in length of the roller is compensated by temperature and also the distance of the bearing to each other in an inclined position of the rollers.
  • the bearing housings all bearings mounted on a slide in the machine frame.
  • the bearings can move in a direction perpendicular to the center line of the nip and the floating bearings provide a degree of freedom in the axial direction, ie parallel to the center line of the nip available.
  • FIG. 1 a roller press 100 according to the invention is shown in a view from above (parts of a machine frame are hidden for better representation of the items).
  • a first roller 110 is rotatably supported in the roller press 100 by means of the shafts 111 and 112.
  • a second, adjacent roller 120 which in turn is rotatably mounted in the roller press via shafts 121 and 122, is arranged in the roller press 100.
  • the two rollers 110 and 120 are driven in opposite directions, so that the material to be ground fed onto the nip 115 is pulled into the nip 115.
  • the bearings of the rollers 110 and 120 in the roller press 100 is done via fixed bearings, which are arranged in the fixed bearing housings 130 and 140 and via floating bearings, which are arranged in the floating bearing housings 150 and 160, in the roller press 100 the bearing housings 130 and 140 in the axial Direction of the rollers 110 and 120 are opposite.
  • These bearing housings 130, 140, 150 and 160 are in turn arranged on slide rails 170 and 180, on which the bearing housings 130, 140, 150 and 160 together with the bearings received therein and in turn received waves 111, 112, 121 and 122 in the machine frame 171st , which is here only interrupted and partially illustrated, horizontal compensating movements perpendicular to the axis of the rollers 110 and 120 can perform.
  • the bearing housings 130, 140, 150 and 160 can also perform rotational movements about a vertical axis of the bearing housings 130, 140, 150 and 160.
  • each upper torque scale 250 respectively torque scale 260, not visible in this view
  • the respective upper torque scales 250 and 260 and the lower torque balances 250 ', 260' which are not visible in this view, are fastened in a rotationally movable manner via rotary hangers 310 and 320 on the machine frame 171.
  • roller press 100 During operation of the roller press 100, it happens that the rollers 110 and / or 120 must perform compensatory movements for the passage of particles which may not be comminuted, for example metal pieces which have undesirably entered the material to be ground or for the passage of regrind unevenly distributed over the length of the nip 115. During this balancing movement, the roller press is temporarily in an imbalance condition. This condition is shown in the following figure, FIG. 2 represented.
  • FIG. 2 shows the roller press 100 in an instant of an exaggerated illustrated compensation movement.
  • Both roller 110 and roller 120 have performed a slight rotational movement about a vertical axis, whereby the nip 115 has a trapezoidal profile, with a in FIG. 2 on the lower side larger opening of the nip 115.
  • This compensation movement is only possible if the bearing housings 130, 140, 150 and 160 can dodge on the slide rail 170 and 180 in the horizontal direction and if the floating bearings in the floating bearing housings 150 and 160 an axial movement allow the waves 112 and 122.
  • the roller press 100 In this state, the roller press 100, the distance between the paired bearing housings 130 and 140 and / or bearing housings 150 and 160 is greater than in the equilibrium state in FIG. 1 is shown.
  • the roller press 100 By the pulling force of the two hydraulic cylinders 210 and 220 and / or the hydraulic cylinders 230 and 240, the roller press 100 is inclined to return to the equilibrium state, which in FIG. 1 is shown, wherein the in FIG. 2 Trapezoidal nip shown again assumes a rectangular profile and is aligned in the machine frame 171 centered.
  • the rotary hangers 310 and 320 do not have to accommodate the forces of the train loaded hydraulic cylinders 210, 220, 230 and 240 for centering the nip 115, however, causes the rotatable suspension of the torque scale 250 and / or 260, that an aligned, equilibrium position of the rollers 110 and 120 is possible only in a horizontal position, whereby the nip 115 is centered.
  • An advantage of the use of the torque balance is a simplification of the hydraulic control, which can take place in each case in an extreme case without compensation with each other, because the torque balance is able to compensate for minor deviations of the control characteristic of the hydraulic systems with each other. Furthermore, can be dispensed with the use of multi-chamber hydraulic cylinders.
  • the roller press 100 presented here is robust, offers automatic centering and can be equipped with a lightweight machine frame thanks to the closed power system.
  • FIG. 3 a perspective view of a roller press 100 according to the invention is shown, in which selected elements are hidden to illustrate the invention.
  • the perspective is clear To take a view that a roller 120 is received via a shaft 122 in a floating bearing housing 160. At this point, the shaft 122 protrudes from the floating bearing housing 160 and there is the drive side of the shaft 122.
  • This floating bearing housing 160 is like the floating bearing housing 150 of the second, here hidden roller 110 housed within a frame of several elements, in this embodiment of Roller press 100 of four loaded on train hydraulic cylinders 230, 230 ', 240 and 240', from which the floating bearing housing 150 and 160 encompassing blocks 155 and 165 and the torque scales 260 and 260 ', said frame forms a closed force system, which for receiving the force resulting from the pressure in the nip 115 is designed.
  • the movable bearing housings shown here 150 and 160 are on a slide rail 180, which is not part of the above-described frame of a plurality of elements, but part of a non-witnessed here machine frame 171.
  • the slide rail 180 thus takes only the weight of the rollers 110 and 120 along with their shafts 111, 112, 121 and 122 and the floating bearing housing 150, 160 on.
  • This pin is fixedly mounted on a part of the machine frame 171 and takes on compared to the tensile force of the hydraulic cylinders 230, 230 ', 240 and 240' slightly dimensioned forces.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Food Science & Technology (AREA)
  • Press Drives And Press Lines (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Road Paving Machines (AREA)
  • Glanulating (AREA)
EP11719234.4A 2010-06-18 2011-05-06 Rollenpresse mit momentenwaage Not-in-force EP2582457B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010024231 DE102010024231B4 (de) 2010-06-18 2010-06-18 Rollenpresse mit Momentenwaage
PCT/EP2011/057305 WO2011157483A1 (de) 2010-06-18 2011-05-06 Rollenpresse mit momentenwaage

Publications (2)

Publication Number Publication Date
EP2582457A1 EP2582457A1 (de) 2013-04-24
EP2582457B1 true EP2582457B1 (de) 2014-10-29

Family

ID=44626336

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11719234.4A Not-in-force EP2582457B1 (de) 2010-06-18 2011-05-06 Rollenpresse mit momentenwaage

Country Status (9)

Country Link
US (1) US9108377B2 (zh)
EP (1) EP2582457B1 (zh)
CN (1) CN102947003B (zh)
AU (1) AU2011267295B2 (zh)
BR (1) BR112012030316A2 (zh)
DE (1) DE102010024231B4 (zh)
DK (1) DK2582457T3 (zh)
RU (1) RU2560561C2 (zh)
WO (1) WO2011157483A1 (zh)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014223524A1 (de) 2014-11-18 2016-05-19 Takraf Gmbh Maschinenrahmen für eine Rollenpresse
DE102015110033A1 (de) * 2015-06-23 2016-12-29 Gebr. Pfeiffer Se Gutbett-Walzenmühle
ES2755484T3 (es) * 2017-05-09 2020-04-22 Buehler Ag Molino de rodillos para piensos y alimentos con un engranaje
CA3139936A1 (en) * 2019-05-09 2020-11-12 Metso Outotec USA Inc. Crushing device
US11000887B2 (en) * 2019-05-24 2021-05-11 The Boeing Company Apparatuses and methods for applying pressure to edge surfaces
US11001024B2 (en) * 2019-05-24 2021-05-11 The Boeing Company Apparatuses and methods for applying pressure to edge surfaces
US11007741B2 (en) * 2019-05-24 2021-05-18 The Boeing Company Apparatuses and methods for applying pressure to edge surfaces
US11007740B2 (en) * 2019-05-24 2021-05-18 The Boeing Company Apparatuses and methods for applying pressure to edge surfaces
US11014320B2 (en) * 2019-05-24 2021-05-25 The Boeing Company Apparatuses and methods for applying pressure to edge surfaces
CA3160767A1 (en) * 2020-02-14 2021-08-19 Pedro Guerrero Palma Roller mill with a synchronizing device
BE1028057B1 (de) * 2020-02-14 2021-09-13 Thyssenkrupp Ag Walzenmühle mit einer Gleichlaufeinrichtung
EP4056280A1 (en) * 2021-03-11 2022-09-14 Sandvik SRP AB A drive train assembly for a roll crusher

Family Cites Families (17)

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Publication number Priority date Publication date Assignee Title
GB959186A (en) * 1959-08-19 1964-05-27 Nat Res Dev Improvements in or relating to infinitely variable change speed gears
GB1040398A (en) * 1962-12-24 1966-08-24 Schloemann Ag Improvements in rolling mills, with cooling means, for the treatment of pulverulent and granular materials, particularly metals
US4212504A (en) * 1979-02-26 1980-07-15 Bakanov Anatoly I Backing device for a working roll of a roll stand
DE3109536C3 (de) * 1981-03-13 1994-04-14 Escher Wyss Ag Regelanordnung für ein Quarto-Metallwalzwerk
DE3723605A1 (de) * 1987-07-17 1989-01-26 Kloeckner Humboldt Deutz Ag Zweiwalzenmaschine, wie z. b. walzenpresse
DE4234481A1 (de) 1992-10-13 1994-04-14 Krupp Polysius Ag Walzenmühle
DE4404634A1 (de) * 1994-02-14 1995-08-17 Krupp Polysius Ag Walzenmühle
GB2293990A (en) * 1994-10-11 1996-04-17 Satake Uk Ltd A cereal milling machine
JP3688178B2 (ja) * 2000-03-10 2005-08-24 光洋精工株式会社 トロイダル型無段変速機
RU2169045C1 (ru) * 2000-05-26 2001-06-20 ООО "Мировые технологии" Секционный двухвальцовый станок для размола зерновых культур
EP1184094A3 (en) * 2000-08-29 2004-12-22 Hitachi, Ltd. Rolling mill and rolling method
DE102005006090A1 (de) 2005-02-10 2006-08-24 Khd Humboldt Wedag Gmbh Zweiwalzenmaschine insbesondere zur Gutbettzerkleinerung
CN2776541Y (zh) * 2005-03-04 2006-05-03 张立建 一种带同步支撑装置的辊式破碎机
US7325489B2 (en) * 2006-06-13 2008-02-05 The Procter & Gamble Company Process for controlling torque in a calendering system
DE102007059072A1 (de) 2007-12-07 2009-06-10 Khd Humboldt Wedag Gmbh Rollenpresse mit zwei Losrollen
DE102007059073A1 (de) * 2007-12-07 2009-06-10 Khd Humboldt Wedag Gmbh Rollenpresse mit symmetrischer Walzenzentrierung
SE532690C2 (sv) * 2008-06-30 2010-03-16 Metso Brasil Ind E Com Ltda Lagerarrangemang

Also Published As

Publication number Publication date
DE102010024231B4 (de) 2015-02-12
US20130087054A1 (en) 2013-04-11
WO2011157483A1 (de) 2011-12-22
EP2582457A1 (de) 2013-04-24
DE102010024231A1 (de) 2011-12-22
RU2013102117A (ru) 2014-07-27
RU2560561C2 (ru) 2015-08-20
CN102947003A (zh) 2013-02-27
BR112012030316A2 (pt) 2016-08-09
CN102947003B (zh) 2015-01-07
DK2582457T3 (en) 2015-01-26
AU2011267295A1 (en) 2012-12-13
US9108377B2 (en) 2015-08-18
AU2011267295B2 (en) 2016-02-25

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