EP0151997A2 - Broyeur cylindrique - Google Patents

Broyeur cylindrique Download PDF

Info

Publication number
EP0151997A2
EP0151997A2 EP85100817A EP85100817A EP0151997A2 EP 0151997 A2 EP0151997 A2 EP 0151997A2 EP 85100817 A EP85100817 A EP 85100817A EP 85100817 A EP85100817 A EP 85100817A EP 0151997 A2 EP0151997 A2 EP 0151997A2
Authority
EP
European Patent Office
Prior art keywords
pressure
adjusting
roller
rolling mill
rolls
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.)
Granted
Application number
EP85100817A
Other languages
German (de)
English (en)
Other versions
EP0151997A3 (en
EP0151997B1 (fr
Inventor
Heinz Resch
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.)
Buehler AG
Original Assignee
Buehler 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 Buehler AG filed Critical Buehler AG
Publication of EP0151997A2 publication Critical patent/EP0151997A2/fr
Publication of EP0151997A3 publication Critical patent/EP0151997A3/de
Application granted granted Critical
Publication of EP0151997B1 publication Critical patent/EP0151997B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • B02C4/36—Adjusting, applying pressure to, or controlling the distance between, milling members in mills specially adapted for paste-like materials

Definitions

  • the invention relates to a rolling mill according to the preamble of claim 1.
  • Rolling mills with adjusting devices for interleaving at least one roll have been proposed variously in the literature in order to avoid the need for roll crowning. Examples of such constructions can be found in French Patents 1,028,098 and 1,273,350 and in U.S. Patent 2,762,295. Rolling mills of this type are usually operated at a specific operating pressure which corresponds to a predetermined crowning of the rollers or a predetermined entanglement. Therefore, the known rolling mills were only equipped with a manual adjustment according to the references mentioned, the respective master being able to adjust the size of the adjustment with the aid of a key.
  • the invention is therefore based on the object of finding a practical solution for the automatic adjustment of the entanglement depending on the pressure (or vice versa) in rolling mills in which the pressure exerted on the rollers is several hundred kilos, in particular more than one ton, e.g. is over 4t.
  • This object is achieved by the features of the characterizing part of the main claim.
  • the features of claim 2 are provided for realizing such pressures.
  • the two outer rolls 1, 2 are mounted in bearings 69, 70 on levers 5 and 6, respectively, which can be pivoted about a fixed axis 3 or 4.
  • the two outer rollers 1, 2 are braced by means of fluidic piston-cylinder units 7, 8 against a lever 10 carrying the middle roller 9 via the levers 5, 6.
  • the connection between the Levers 5, 6 and 10 or the units 7, 8 are only shown schematically as a line, but it goes without saying that between the outer levers 5, 6 and the respective piston-cylinder unit 7 and 8, the connection via the respective on the lever 5 or : 6 articulated piston rod 11 or 12, whereas the respective cylinder 13 or 14 is connected to the middle lever 10 by means of a rod 15 or 16 articulated on the lever 10.
  • the piston-cylinder units 7, 8 are supplied with pressure medium, in particular a pressure fluid from a reservoir 17 with the aid of a pump 18, to which a pressure line 19 is connected.
  • the pressure line 19 opens via a branch line 20 into the cylinder 13 of the unit 7 and finally also into the cylinder 14 of the unit 18.
  • the axis 21 of the lever 10 is displaceable in the vertical direction.
  • an additional guide not shown here, for example a straight guide or a slot guide in the roller frame or the like, can be provided be. This will be particularly expedient if the two outer rollers 1, 2 are pressed against the middle roller 9 by the units 7, 8. If, on the other hand, one of the outer rollers, for example roller 2, is mounted in a fixed position, then the arrangement of a guide rocker 68, indicated by dashed lines, is structurally simpler and cheaper.
  • This guide rocker 68 preferably swings about a horizontal plane 73 passing through its pivot bearing 4, since the deviations from a straight line thus remain small.
  • the rocker 68 can also be arranged on the top of the levers 6, 10 if the units 7, 8 engage on the underside, or can be an independent part of the lever 6 or frame part (if the roller 2 is to be stationary) Have camp, but the joint use of the bearing 4 is easier on the one hand, on the other hand, it has proven to be advantageous if the length of the. Swingarm 68 corresponds to the distance to the adjacent roller, that is to say corresponds approximately to the diameter of a roller. An effect is obtained with simpler means, as has already been described in FR-PS 1 273 350.
  • a connecting rod 22 is articulated on the axis 21, which comprises an adjusting eccentric 23 at its lower end.
  • an eccentric the width of which can be selected according to the construction, the pressure is transferred to a relatively large area, so that there are no excessively high surface pressures, as would be the case, for example, with cams.
  • the eccentric 23 is seated on a stationary shaft 24 which runs parallel to the middle roller 9 and at the opposite end carries an eccentric for adjusting the bearing lever provided on this side and corresponding to the lever 10.
  • the arrangement is such that the eccentricity of the two adjustment eccentrics is rotated relative to one another by 180 ° in a known manner, so that when the middle roller 9 is adjusted upwards on one side, the adjustment takes place downwards on the other side and thus an entanglement of the middle roller 9 with respect to the outer rollers 1, 2 is achieved about an axis passing through the middle of their length.
  • an electrical pressure sensor 26 is provided in the pressure line 19, the output signal of which is fed to a control stage 27 which, on the basis of a comparison with an optionally adjustable target value, outputs an adjustment signal. outputs a motor control stage 28.
  • the associated motor 29 can be any motor (in which case a closed control loop for the eccentric adjustment is expedient), but is preferably a stepper motor, so that the adjustment of the eccentric 23 attached to the continuous shaft 24 is dependent on the direction of rotation of the motor 29 and the number of step pulses supplied to it.
  • a closed control loop for the eccentric adjustment is expedient
  • stepper motor so that the adjustment of the eccentric 23 attached to the continuous shaft 24 is dependent on the direction of rotation of the motor 29 and the number of step pulses supplied to it.
  • the rotor of the stepper motor 29 carries a threaded spindle 30, into which a lock nut 31 is screwed.
  • the lock nut 31 is prevented from rotating by stationary axial guides 32 and laterally projecting wings 33.
  • a connecting rod 34 is connected to the lock nut 31 and is connected to the crank pin 36 of the crank 25 via a transverse slot 35. It is understood from the later description that an amplifier 48 to 52 according to FIG. 3 can be provided between stepper motor 29 and crank 25.
  • FIG. 2 the relationship between the crowning height B in ⁇ which is necessary per se and which can be replaced by the entanglement, and the applied pressure in tons (to) is shown in FIG.
  • the adjustment of the middle roller 9 corresponds to one because of its favorable Adjustment eccentric 23 does not favor the ideal of curve 37 (the relationship between crowning and pressure is not linear), but rather the curve 38 drawn in dash-dot lines. If one does not want to accept such a deviation (although this would also be possible), then for compensation for the deviation must be ensured.
  • the shaft 24 can be driven in the manner described with reference to FIG. 1 via a push crank 25, which is arranged opposite the adjusting eccentric 23 in such a way that a linear adjustment movement by the servomotor 29 due to the sinusoidal movement of the crank pin 36 occurs there is an adjustment corresponding to curve 39 in FIG. 2, the bulging of the dash-dotted curve 38 being essentially compensated in this way.
  • the crank 25 (FIG. 1) can be adjustable, for example, in its angular position relative to the eccentrics (see FIG. 23), or a plurality of fastening holes 40 are provided for the crank pin 36.
  • the pressure line 19 can be connected directly to a connecting line 41 in accordance with FIG. 3. which leads to a converter unit 42.
  • a piston 43 is acted upon directly by the pressure and accordingly moves against the pressure of a spring 44. Since the Force of the spring increases, there is a position of the piston 43 where the balance between the spring pressure of the spring 44 and the pressure from the pressure line 19 is established.
  • the spring 44 for example, a suspension formed by a quantity of gas, a magnetic counterforce or the like could also be used.
  • the spring 44 is inexpensive in that it has a linear characteristic and therefore the pressure prevailing in the pressure line 19 is converted into a linear path.
  • a non-linear pressure element is provided precisely for the purpose of the compensation discussed with reference to FIG. 2.
  • the piston 43 is connected to a piston rod 45 which, at its left end (with reference to FIG. 3), is designed as a control element of a servo amplifier known per se, which is connected directly to the pressure pump 18 via a line 46, whereas against the pressure line 19 to a reducing valve 47 is interposed.
  • the piston rod 45 with control edges 48, 49 of widened diameter controls the inflow of the hydraulic medium from the line 46 via channels 50, 51 to one side of a servo piston 52, which in turn adjusts itself relative to the piston rod 45 until it runs out Fig. 3 apparent position is reached, in which both channels 50, 51 are closed off against the line 47.
  • the movement of the servo piston 52 is then transferred to the crank 25 in a similar manner as was shown with reference to FIG. 1.
  • an adjustment possibility is expediently provided within a slot 74.
  • the middle roller 9 is mounted stationary, whereas the levers 5, 6 are adjustable in height by means of adjusting eccentrics 23.
  • an adjustment by a single common eccentric 23, which acts on a carrier that has just been guided, would be possible offers the solution shown the possibility of a separate adjustment of both levers 5, 6 and also saves the complex straight line.
  • the solution shown is particularly suitable for five-roll mills in which two further rolls are connected on both sides of the rolls 1, 2.
  • FIGS. 4 and 5 show a solution in which the push rod 134 corresponding to the rod 34 is designed as a toothed rack and is in engagement with a toothed wheel 53 on the shaft 54 of a drive eccentric 55.
  • the drive eccentric 55 is surrounded by a connecting rod 56 which carries the shaft 24 at its upper end.
  • the shaft 24 receives its drive from a sprocket 57 seated on the shaft 54, which is connected via a chain 58 to a further sprocket 59 wedged onto the shaft 24.
  • a tensioning roller (not shown) for the chain can be provided at 60.
  • servo amplifiers 48 to 52 of the type shown in FIG. 3 can also be used to directly control reciprocating pistons on both sides of the roller 9, it only being necessary to ensure that the movement of these pistons on the two sides of the roller 9 takes place in the opposite direction.
  • Such a solution can then in particular by Be advantageous when, for example, a plurality of rollers to be folded against each other, particularly in a W alz- factory with at least '4 rolls.
  • FIG. 5 Another solution to the adjustment mechanism shown in FIG. 5, in which the support lever 10 for the shaft of the roller 9 (see FIG. F ig. 1, 3) is mounted on a frame 61.
  • This frame 61 is vertically displaceable with the aid of sliding guides 62 and has on one side a toothed rail 63 into which a gearwheel 64 fixed on a fixedly mounted shaft 124 engages.
  • the arrangement on the other side of the roller 9 is essentially the same, but with the difference that there the gear corresponding to the gear 64 is not on the right-hand side (with reference to FIG. 5), but on the left-hand side in a toothed rail provided there engages the frame.
  • the frames 61 accordingly move in different directions on both sides.
  • the drive rod can consist of two interconnected parts 234, 334, of which the rack 334 has thickened portions 65, which can optionally be inserted into different recesses in the rod 234, the two rod parts 234, 334 then being connected by means of fastening screws 67. With this type of adjustment, however, only the height of the desired crowning can be set, the curve profile remaining unaffected for the adjustment characteristic of the entanglement.
  • the adjustment path transferred to the bearing of the roll to be entangled is in a certain ratio to the compensating movement.
  • a depends to a large hat
  • I d 'compensation curve would result.
  • the height adjustment path is too entangling roller not only depends on the contact pressure, but also on the lever length, i.e. on the distance between the center of the roller and the point of application of the bearing lever 10 or 5,6. In practice there is good compensation if the relationship between the height adjustment path of the respective bearing lever 10 (Fig. 1) or 5, 6 (Fig. 3) to the length of the crank 25 is between 1: 3 and 1: 5.
  • the curve shape that can be achieved by entangling does not exactly correspond to the mathematical conditions of crowning, which may also be a reason why the entanglement has so far been used relatively rarely and mostly only for low roller pressures.
  • sicl naturally does not have a crown ground on a roller adapted to different pressures, so that a certain deviation from the ideal shape must always be accepted, especially with large pressure adjustment ranges.
  • a way out of this dilemma can now consist in a rolling mill with at least two rollers and a pressure device for loading at least one roller against the other, and an adjusting device for interlocking the rollers, in that at least one of the rollers 1, 2, 9 which can be interlocked relative to one another additionally has a crowning, which corresponds to a lower range of the operating pressure.
  • a basic crowning is specified, from which an entanglement is made.
  • the basic crowning can be designed in such a way that the mathematical error resulting from entanglement is at least partially (preferably approximately half) compensated.
  • the basic crowning mentioned can be provided on at least one of the rollers 1, 2 and 9, but is preferably present on at least that roller which is adjusted to be entangled, i.e. in the case of FIG. 1 on the roller 9, in the case of FIG. 3 on the rollers 1 and 2, in particular when it is a five-roll mill in the manner described.
  • all the rollers have the basic crowning mentioned, which of course does not have to be the same on all rollers and differs from the crowning of the peripheral rollers, in particular on the central rollers.
  • the adjustment range of the pressure can have a ratio of 1: 6 between minimum and maximum pressure. If one assumes that the minimum pressure is 1, then the basic crowning must be calculated for a pressure of at most 3, the pressure selected for the calculation in practice being significantly lower. For example, the pressure used for the calculation is 1.5 to 2, but can also be selected with 1.
  • FIG. 6 shows that not only a simple control, but also a closed control loop can be used to set the mutual entanglement of the roller 9 with respect to the stationary rollers 1, 2. Parts of the same function have the same reference numerals as in the previously described figures, possibly provided with a 100 number.
  • a carrier 110 that can be displaced in the vertical direction (based on FIG. 6) in the sliding guides 75 is mounted on a piston rod 145 of a hydraulic lifting unit 142.
  • the unit 142 is connected to the pump 18 via a line 146.
  • An electrically controllable solenoid valve 150 which regulates the inflow of hydraulic fluid to the unit 142, is located in the line 146.
  • a position sensor 76 is connected to the carrier 110 of the roller 9, which position can be constructed as desired, but in the arrangement shown has two stationary (for example connected to the unit 142) capacitor plates 77, between which an insulating plate 78 connected to the carrier 110 immersed. Depending on the actual position of the carrier 110, a correspondingly different signal thus results at the output of the position transmitter 76, which output signal can be carried out by a control circuit 79.
  • control loop 79 represents only part of the control system, to which a second controller 179 belongs. It understands It is clear that both control loops 79, 179 can optionally be combined to form one structural unit. Since the control loop 179 is connected to a setpoint input device 81, for example formed by a key device, a connecting line 82 to the control loop 79 is expediently provided in order to transmit a corresponding signal to the control loop 79. If appropriate, this connecting line 82 is designed as a data bus, via which any feedback from the control circuit 79 to the controller 179 can also take place.
  • a control signal for the magnet 80 of the solenoid valve 150 is generated at the output of the control circuit 79, which can also be fed to the magnet 83 of the controllable valve 147 provided in the line 19 via a proportional element P.
  • a simple valve 47 according to FIG. 3 can also be provided here, the setting of which is determined by an input device 181 of any type.
  • the magnet 83 is connected to the controller 179, which on the one hand connects it to a voltage source on the one hand on the basis of the setpoint signal received from the input device 81 or on the other hand on the basis of the signal of a pressure detector 126.
  • adjustment paths for the entanglement of the roller axes can of course be halved in that two adjacent rollers are adjusted in opposite directions.

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  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Crushing And Grinding (AREA)
EP85100817A 1984-02-11 1985-01-26 Broyeur cylindrique Expired EP0151997B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3404932 1984-02-11
DE19843404932 DE3404932A1 (de) 1984-02-11 1984-02-11 Walzwerk

Publications (3)

Publication Number Publication Date
EP0151997A2 true EP0151997A2 (fr) 1985-08-21
EP0151997A3 EP0151997A3 (en) 1986-12-03
EP0151997B1 EP0151997B1 (fr) 1988-12-14

Family

ID=6227468

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85100817A Expired EP0151997B1 (fr) 1984-02-11 1985-01-26 Broyeur cylindrique

Country Status (4)

Country Link
US (1) US4635861A (fr)
EP (1) EP0151997B1 (fr)
JP (1) JPS60183044A (fr)
DE (2) DE3404932A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2641713A1 (fr) * 1989-01-16 1990-07-20 Kloeckner Humboldt Deutz Ag Machine a deux cylindres, notamment broyeur a cylindres
WO2006045206A1 (fr) * 2004-10-26 2006-05-04 Bühler AG Laminoir
WO2007055672A1 (fr) 2005-09-16 2007-05-18 Yukselis Makina Sanayi Ve Ticaret Anonim Sirketi Agencement de positionnement angulaire de rouleaux de broyage
WO2009011667A1 (fr) * 2007-07-16 2009-01-22 Yukselis Makina Sanayi Ve Ticaret Anonim Sirketi Ensemble palier à bras de rotation doté d'un excentrique de réglage de course
CN102441459A (zh) * 2011-12-14 2012-05-09 吴江市冰心文教用品有限公司 一种三辊研磨机

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3702245C3 (de) * 1987-01-27 1993-12-23 Kleinewefers Gmbh Kalander
DE8801758U1 (de) * 1987-08-28 1988-05-05 Sulzer-Escher Wyss AG, Zürich Druckwalze
US5072887A (en) * 1990-01-19 1991-12-17 California Pellet Mill Company Roll mill
DE4226158C2 (de) * 1992-08-07 2003-04-10 Kloeckner Humboldt Wedag Verfahren und Anlage zur Druckbehandlung körnigen Gutes
CA2175879A1 (fr) * 1995-05-17 1996-11-18 Wolfgang Finken Concasseur a cylindres
ITMI980943A1 (it) * 1998-04-30 1999-10-30 Carle & Montanari Spa Procedimento e dispositivo per la premacinazione di materiale dolciario
US6238724B1 (en) * 1998-10-29 2001-05-29 Kraft Foods, Inc. Chocolate refining process
US6920772B1 (en) 2003-02-12 2005-07-26 Morgan Construction Company Pinch roll unit
US7275404B1 (en) 2005-11-22 2007-10-02 Og Technologies, Inc. Method and an apparatus to control the lateral motion of a long metal bar being formed by a mechanical process such as rolling or drawing
US7861567B2 (en) 2005-11-22 2011-01-04 Og Technologies, Inc. Method and apparatus to control the lateral motion of a long metal bar being formed by a mechanical process such as rolling or drawing
US7794346B2 (en) * 2008-02-01 2010-09-14 William Lake Torque transfer device
US20100221081A1 (en) * 2009-02-27 2010-09-02 Leite Paulo Cesar De Andrade System for automation of fluctuation and leveling of top rollers of sugarcane mills
EP2746024B1 (fr) * 2012-12-21 2015-05-27 Reifenhäuser GmbH & Co. KG Maschinenfabrik Siège de cylindre
CN112774781A (zh) * 2020-12-09 2021-05-11 上海铸研重工科技有限公司 摆辊式制砂机

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Publication number Priority date Publication date Assignee Title
DE504851C (de) * 1930-08-08 Heinr Frigge Maschb Parallel-Einstellvorrichtung fuer die Walzen von Quetschwalzenmuehlen
FR804970A (fr) * 1936-04-16 1936-11-06 Repiquet Ets Perfectionnements apportés aux machines à cylindres de pression
FR1028098A (fr) * 1950-10-19 1953-05-19 Repiquet Sa Des Ets Perfectionnements apportés aux broyeuses à cylindres
GB724685A (en) * 1952-03-04 1955-02-23 Miag Muhenbau Und Ind G M B H Improvements in or relating to roller arrangements
US2762295A (en) * 1950-11-01 1956-09-11 Carding Spec Canada Distribution of pressure between a pair of pressure rollers
FR1273350A (fr) * 1959-11-16 1961-10-06 Dispositif oscillant pour la retenue réglable et orientable des rouleaux de calandre et similaires, en particulier pour les machines à cintrer les tôles
US3066876A (en) * 1955-06-28 1962-12-04 Verdier Andre Louis Roller mills, calenders and like roller machines
US3240148A (en) * 1962-10-26 1966-03-15 Carding Spec Canada Pressure rollers
DE2002742A1 (de) * 1970-01-22 1971-07-29 Bauermeister Hermann Maschf Reibwalzwerk
EP0130278A2 (fr) * 1983-06-29 1985-01-09 CARLE & MONTANARI S.p.A. Moulin de raffinage à cylindres, à fonctionnement réglable, pour chocolat

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Publication number Priority date Publication date Assignee Title
GB899532A (en) * 1957-09-17 1962-06-27 British Aluminium Co Ltd Improvements in or relating to the manufacture of metal sheet or strip
US3097591A (en) * 1961-11-24 1963-07-16 Beloit Iron Works Anti-deflection roll
US3138089A (en) * 1963-01-09 1964-06-23 Beloit Corp Anti-deflection roll
FR1376499A (fr) * 1963-03-19 1964-10-31 Perfectionnements au serrage des cylindres de broyeuses et autres machines à cylindres
US3459124A (en) * 1966-10-20 1969-08-05 Black Clawson Co Paper machinery
JPS56146741A (en) * 1980-04-18 1981-11-14 Hitachi Ltd Setting of holding time and system therefor

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE504851C (de) * 1930-08-08 Heinr Frigge Maschb Parallel-Einstellvorrichtung fuer die Walzen von Quetschwalzenmuehlen
FR804970A (fr) * 1936-04-16 1936-11-06 Repiquet Ets Perfectionnements apportés aux machines à cylindres de pression
FR1028098A (fr) * 1950-10-19 1953-05-19 Repiquet Sa Des Ets Perfectionnements apportés aux broyeuses à cylindres
US2762295A (en) * 1950-11-01 1956-09-11 Carding Spec Canada Distribution of pressure between a pair of pressure rollers
GB724685A (en) * 1952-03-04 1955-02-23 Miag Muhenbau Und Ind G M B H Improvements in or relating to roller arrangements
US3066876A (en) * 1955-06-28 1962-12-04 Verdier Andre Louis Roller mills, calenders and like roller machines
FR1273350A (fr) * 1959-11-16 1961-10-06 Dispositif oscillant pour la retenue réglable et orientable des rouleaux de calandre et similaires, en particulier pour les machines à cintrer les tôles
US3240148A (en) * 1962-10-26 1966-03-15 Carding Spec Canada Pressure rollers
DE2002742A1 (de) * 1970-01-22 1971-07-29 Bauermeister Hermann Maschf Reibwalzwerk
EP0130278A2 (fr) * 1983-06-29 1985-01-09 CARLE & MONTANARI S.p.A. Moulin de raffinage à cylindres, à fonctionnement réglable, pour chocolat

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2641713A1 (fr) * 1989-01-16 1990-07-20 Kloeckner Humboldt Deutz Ag Machine a deux cylindres, notamment broyeur a cylindres
WO2006045206A1 (fr) * 2004-10-26 2006-05-04 Bühler AG Laminoir
CN101048231B (zh) * 2004-10-26 2011-08-31 布勒股份公司 辊轧机
WO2007055672A1 (fr) 2005-09-16 2007-05-18 Yukselis Makina Sanayi Ve Ticaret Anonim Sirketi Agencement de positionnement angulaire de rouleaux de broyage
WO2009011667A1 (fr) * 2007-07-16 2009-01-22 Yukselis Makina Sanayi Ve Ticaret Anonim Sirketi Ensemble palier à bras de rotation doté d'un excentrique de réglage de course
CN102441459A (zh) * 2011-12-14 2012-05-09 吴江市冰心文教用品有限公司 一种三辊研磨机

Also Published As

Publication number Publication date
US4635861A (en) 1987-01-13
EP0151997A3 (en) 1986-12-03
EP0151997B1 (fr) 1988-12-14
JPS60183044A (ja) 1985-09-18
DE3404932A1 (de) 1985-08-14
DE3566774D1 (en) 1989-01-19

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