EP1740309B1 - Moulin a cylindres - Google Patents

Moulin a cylindres Download PDF

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Publication number
EP1740309B1
EP1740309B1 EP05740244A EP05740244A EP1740309B1 EP 1740309 B1 EP1740309 B1 EP 1740309B1 EP 05740244 A EP05740244 A EP 05740244A EP 05740244 A EP05740244 A EP 05740244A EP 1740309 B1 EP1740309 B1 EP 1740309B1
Authority
EP
European Patent Office
Prior art keywords
roll
mill according
roll mill
grinding
roller
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
EP05740244A
Other languages
German (de)
English (en)
Other versions
EP1740309A1 (fr
Inventor
Reinhard Rüter
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.)
Reinhard Rueter Maschinenbau
Original Assignee
Reinhard Rueter Maschinenbau
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 DE200420006309 external-priority patent/DE202004006309U1/de
Priority claimed from DE200420006308 external-priority patent/DE202004006308U1/de
Priority claimed from DE200420006307 external-priority patent/DE202004006307U1/de
Application filed by Reinhard Rueter Maschinenbau filed Critical Reinhard Rueter Maschinenbau
Publication of EP1740309A1 publication Critical patent/EP1740309A1/fr
Application granted granted Critical
Publication of EP1740309B1 publication Critical patent/EP1740309B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • B02C4/38—Adjusting, applying pressure to, or controlling the distance between, milling members in grain mills

Definitions

  • the invention relates to a roller mill with two mutually engageable to form a nip roller grinding rollers, which are drivingly coupled together so that they rotate at different peripheral speeds.
  • Roller mills are used in mill operations for grinding cereals and similar products.
  • suitable coupling gears which are today usually formed by toothed belts, the two grinding rollers are coupled together so that their mostly fluted peripheral surfaces move in the same direction at the nip, so that the product is transported through the nip.
  • compressive forces act on the grain grains, but also shearing and frictional forces due to the different circumferential speeds of the rolls, so that the product is not only squeezed but also crushed.
  • the object of the invention is to provide a roller mill with a simplified input and Auslessnessmechanismus.
  • the predetermined amount of the nip in the disengaged position is selected depending on the product to be ground so that the width of the nip is still slightly smaller than the average diameter of the product particles.
  • roller mill since the roller mill is also self-releasing in the case of product shortage, high functional reliability is achieved. Another advantage is that the automatic engagement and disengagement of the rollers no pneumatic or hydraulic power source is needed. This also avoids the risk of contamination of the ground food due to a leak in the hydraulic system.
  • the roller prefferably, it would be conceivable to bias the roller with the larger circumferential speed in the transport direction of the product, so that it is braked by the friction of the product particles and springs back against the transport direction.
  • the movably mounted roller is that which has the smaller peripheral speed, and is biased against the transporting direction and is engaged by the product in the transporting direction.
  • the indented position of the movably mounted roller is preferably limited by a stop having a predetermined breaking point. If Foreign bodies in the nip should jam, it comes to a breakage of the predetermined breaking point, so that the movably mounted roller can swing through in the transport direction and thus greater damage can be avoided.
  • the coupling gear for the two grinding rollers is preferably formed by a crossed, ie 8-shaped belt drive, which has the necessary flexibility for the engagement and disengagement of the rollers.
  • This design of the coupling gear also has the advantage that in the grinding operation, the mechanical stress on the bearings of the grinding rollers is reduced, since the belt drive counteracts a separation of the two rollers.
  • the arrangement can be chosen so that a certain self-regulation of the roller pressure is achieved.
  • round belt drives whose belts each wrap around the associated pulleys several times and intermesh with one another at the intersection points. This makes it possible to transmit high torques and minimize the skew of the drive belt.
  • coupling gears are provided at both axial ends of the two grinding rollers. As a result, can be achieved over the length of the nip uniform roller pressure.
  • each grinding roller and the associated axle or the associated stub axle form an inseparable unit, so that the roller can withstand the high mechanical complaints
  • the grinding roller on a cylindrical roller body which at both ends by releasable centering is completed, each carrying a stub axle. If the grinding rollers must be nachgeriffelt or resharpened, this design makes it possible to pull the two centering axially apart, so that the cylindrical roller body can be removed without the need for this, the bearings and the coupling drives must be removed. As a result, the labor and time required for a roll change is significantly reduced.
  • the invention also relates to a roller mill with two with the formation of a nip against each other engagable grinding rollers, the driving are coupled together so that they rotate at different peripheral speeds, wherein at least one of the grinding rollers has a cylindrical roller body, which is completed at both ends by releasable, each having a stub axle bearing centering.
  • the invention also relates to a roller mill with two mutually engageable to form a nip grinding rollers, which are coupled by a coupling gear together so that they rotate at different peripheral speeds, wherein the coupling gear is a crossed round belt drive, the round belt wraps around such pulleys multiple such, that the intersecting Trumms of the round belt mesh comb-shaped.
  • FIG. 1 shows a roller mill with two grinding rollers, hereinafter referred to as rollers 10, 12, which together form a nip 14.
  • rollers 10, 12 which together form a nip 14.
  • the associated machine frame and drive means and the like are in FIG. 1 omitted for the sake of clarity.
  • the roller 10 is fixedly mounted with stub axles 16 in the machine frame and is driven in a clockwise direction.
  • the roller 12, however, is mounted with its stub axles 18 in a rocker 20, which in turn is pivotable about an axis parallel to the nip 14 and with this approximately at the same level axis 22.
  • the roller 12 is coupled to the roller 10 so that it rotates at a slightly lower peripheral speed than the roller 10 in the counterclockwise direction.
  • the peripheral surfaces of the two grinding rollers move at slightly different speeds in the same direction so that the product fed into the nip is transported down through the nip 14.
  • FIG. 1 shows the rollers 10, 12 in the disengaged position in which the nip 14 has a predetermined width and the rollers do not touch each other.
  • the rocker 20 is biased by a spring 24 up against a stop 26.
  • the stop 26 is arranged so that the width of the nip 14 is slightly smaller than the average particle diameter of the product fed to the nip.
  • the product 28 is fed from above into the nip 14, the individual product particles, such as cereal grains, are slightly squeezed in the nip.
  • the roller 10 which rotates at a higher peripheral speed, tends to accelerate the product downwardly.
  • the product therefore exerts a downward frictional force on the circumference of the roller 12, which rotates at a lower circumferential speed. Since the rotation of the roller 12 can not be accelerated, creates a downward force F, which acts on the swingarm 20 via the stub axles 18 and has a tendency to down to the To pivot axis 22.
  • the position shown leads to a further narrowing of the nip 14 and thus to a further increase in the frictional forces and thus the force F.
  • the rocker 20 and the roller 12 by a self-reinforcing effect against the force of the spring 24 in the in FIG. 2 shown position driven.
  • the nip 14 is narrowed to its working width, so that the product 28 is finely ground.
  • the working width of the nip 14 is finely adjustable, for example by means of an integrated eccentric in the axis 22.
  • FIG. 2 is the rocker 20 to a stop 30, which is designed as a predetermined breaking point and normally prevents penetration of the rocker 20 down. Only in exceptional cases, such as when a foreign body jammed in the nip 14, there is a breakage of the predetermined breaking point, so that the stopper 30 releases the rocker 20 and this can feather down by enlarging the nip.
  • An additional safety measure may optionally be that the stub axle 16 of the roller 10 and / or the axis 22 of the rocker 20 are resiliently mounted in horizontally movable bearing blocks, which are held by strong springs in their operating position.
  • FIG. 3 the roller mill is shown simplified in plan view.
  • the drive of the roller 10 via a motor 38 and a belt drive 40.
  • the side parts 32, 34 also has an eccentric shaft 42 is mounted on which the axis 22 of the rocker 20 is arranged eccentrically. With a lever 44, the eccentric shaft 42 can rotate so that adjusted by appropriate displacement of the axis 22, the working width of the nip 14 precisely can be.
  • the axle stubs 18 of the roller 12 extend freely through openings 46 of the side parts 32, 34 and are mounted with bearing housings 48 in the rocker 20.
  • the stub axles 16, 18 of the rollers 10 and 12 are coupled on both sides by coupling gear 50 with each other.
  • These coupling gear 50 are designed as a round belt drives and each have a round belt 52, the associated pulleys 54, 56 wraps around multiple 8-shaped and is held by the weight of a dancer 58 under tension.
  • the intersecting trims of the round belt 52 engage between the pulleys 54, 56 in a comb-like manner.
  • the round belts 52 preferably have a certain inherent elasticity, so that the slight spacing changes between the pulleys 54 and 56 can be buffered until over the dancer 58 has been compensated.
  • the surface of the round belt 52 preferably has a relatively high coefficient of friction, so that in combination with the multiple wrap of the pulleys results in a good power transmission. The adjusted by the weight of the dancer 58 tension of the round belt 52 may therefore be relatively low.
  • FIG. 4 one of the coupling gear 50 is shown in an end view.
  • idling mode ie, in the position according to FIG. 1
  • the roller 12 is driven by the product in the nip 14 directly through the roller 10, so that the coupling gear 50 acts as a brake.
  • the Trumms 62 are the pulling Trumms.
  • the trims 62 also tend to pivot the rocker 20 back up.
  • the torque exerted by the runners 62 on the rocker 20 is smaller than the torque resulting from the force F at the nip because the force application point of the runners 62 on the pulley 54 is closer to the axis 22 of the rocker than the nip, so that the force F acts through a larger lever arm.
  • the tensile stress of the tufts 62 is outweighed, so that the rolling pressure in the nip is relaxed again. By this effect, the increase of the rolling pressure is limited and an overload of the stopper 30 is avoided.
  • the coupling gears 50 are provided at both ends of the rollers 10, 12, the forces transmitted by the coupling gears to the opposite ends of the roller 12 and the rocker 20 are substantially equal to each other, so that a uniform rolling pressure over the entire length of the nip 14th is reached.
  • the pulley 54 which is associated with the roller 12 and has the larger diameter, has grooves 64 with an approximately semi-cylindrical Profile adapted to the cross section of the round belt 52 and this gives good guidance.
  • the pulley 56 has grooves 66 which are approximately offset to the grooves 64 in gap and have a greater width than this.
  • the bottom of the grooves 66 is also conically tapered outwardly (away from the roller 10).
  • the Trumms 60 can therefore run with relatively little skew on the inside of the respective groove 66 (above in FIG.
  • the runners 62 which are the dragging runners in the grinding operation, ensure that the round belt when circulating around the pulley 56 to the outside (down in FIG. 5 ) is displaced on the conical bottom of the groove 66 and then expires on the outside of the groove 66 and enters into the groove 64 of the pulley 54 without a large change in direction. In this way it is achieved that the round belt 52 in the multiple wrapping of the pulleys 54, 56 each have only a slight skew and only a little mechanical stress.
  • the grinding rolls 10, 12 have, as usual, on their grinding surface, i.e., their outer peripheral surface, a longitudinal, mostly slightly twisted corrugation, by which the grinding effect is improved. These grinding surfaces must be reworked from time to time and resharpened, which requires the removal of the grinding rollers from the roll mill. With reference to Figures 6 and 7, a construction of the grinding rollers will now be described, which allows a particularly simple and time-saving removal of the rollers. As an example, the roller 10 is shown as representative of both grinding rollers.
  • a cylindrical roller body 68 whose outer peripheral surface forms the grinding surface 70, has a planar end face 72 at both ends and an inner cone 74 at the inner peripheral edge.
  • the roller body 68 is at both Ends completed by a centering 76.
  • the centering disk 76 rests with its outer peripheral region on a flat annular surface 78 on the end face 72 of the roller body and has within this annular surface two annular, concentric cutouts 80, 82. These undercuts define an annular, to some extent intrinsic elastic web 84, which forms an outer cone 86 complementary to the inner cone 74.
  • the stub axle 16 is tubular and firmly welded to the centering disc 76.
  • the stub axle 16 carries the pulley 56 shown here only schematically and a rolling bearing 88 which is received axially displaceable in the bearing housing 36.
  • the roller body 68 receives a clamping piece 90, which is held by spokes 92 coaxially in the roller body and has at each end a threaded hole 94.
  • a threaded bolt 96 is inserted from the open end, which is screwed into the threaded bore 94 of the clamping piece 90.
  • the two centering discs 76 are firmly clamped to the roller body 68.
  • roller body 68 can now be removed in the radial direction from the space between the centering discs 76 and replaced by a freshly processed roller body.
  • the latter can then just as easily be reinstalled by reversing the processes described above and clamped with the aid of the threaded bolts 96, whereby it is precisely aligned and centered.

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  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Grinding (AREA)
  • Motorcycle And Bicycle Frame (AREA)

Claims (18)

  1. Moulin à cylindres avec deux cylindres de mouture (10, 12) pouvant être ajustés l'un par rapport à l'autre en formant une fente entre cylindres (14), lesquels sont couplés entre eux en entraînement de manière à tourner à des vitesses périphériques différentes, caractérisé en ce qu'au moins l'un (12) des cylindres de mouture est supporté mobile dans une direction tangentielle à la fente entre cylindres (14) et est précontraint élastiquement, dans cette direction, dans une position dans laquelle la fente entre cylindres est augmentée à une mesure prédéterminée.
  2. Moulin à cylindres selon la revendication 1, caractérisé en ce que le cylindre de mouture (12) monté mobile est le cylindre de mouture avec la vitesse périphérique inférieure et en ce qu'il est précontraint dans la direction qui est opposée au sens de rotation de ce cylindre sur la fente entre cylindres (14).
  3. Moulin à cylindres selon la revendication 1 ou 2, caractérisé en ce que le cylindre de mouture (12) monté mobile est supporté tournant dans une bascule (20) qui peut pivoter autour d'un axe (22) laquelle se situe approximativement dans un plan avec les axes de rotation des deux cylindres de mouture (10, 12).
  4. Moulin à cylindres selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le mouvement du cylindre de mouture (12) monté mobile dans la direction qui est opposée à la direction de précontrainte, est limité par une butée (30).
  5. Moulin à cylindres selon la revendication 4, caractérisé en ce que la butée (30) peut être supprimée par un point destiné à la rupture.
  6. Moulin à cylindres selon l'une quelconque des revendications 1 à 5, caractérisé en ce qu'une transmission d'accouplement (50) pour l'accouplement en entraînement des deux cylindres de mouture (10, 12) est réalisée sous la forme d'une transmission à courroie croisée.
  7. Moulin à cylindres selon la revendication 6, caractérisé en ce que la transmission d'accouplement (50) est une transmission à courroie ronde dont la courroie ronde (52) entoure plusieurs fois des poulies à courroie (54, 56) correspondantes de manière que les brins (60, 62) se croisant de la courroie ronde s'engagent l'un dans l'autre à la manière d'un peigne.
  8. Moulin à cylindres selon la revendication 7, caractérisé en ce que la courroie ronde (52) est maintenue sous tension par un rouleau danseur (58).
  9. Moulin à cylindres selon l'une quelconque des revendications 7 ou 8, caractérisé en ce qu'au moins l'une (56) des poulies à courroie présente des rainures (66) dont la largeur est supérieure à la section transversale de la courroie ronde (52) et dont le fond est rétréci coniquement vers un côté.
  10. Moulin à cylindres selon l'une quelconque des revendications 1 à 9, caractérisé en ce que les cylindres de mouture (10, 2) sont accouplés à chacune des deux extrémités par une transmission d'accouplement (5).
  11. Moulin à cylindres selon l'une quelconque des revendications 1 à 10, caractérisé en ce qu'au moins l'un des cylindres de mouture (10, 12) comporte un corps de cylindre (68) cylindrique qui est fermé aux deux extrémités par des disques de centrage (76) portant chacun un tourillon (16).
  12. Moulin à cylindres selon la revendication 11, caractérisé en ce que les tourillons (16) sont maintenus dans des boîtiers formant palier (36) correspondants, de manière à pouvoir coulisser axialement.
  13. Moulin à cylindres selon les revendications 6 et 12, caractérisé en ce que les poulies à courroie (54, 56) de la transmission d'accouplement (50) sont disposées chacune directement sur les tourillons (16).
  14. Moulin à cylindres selon l'une quelconque des revendications 11 à 13, caractérisé en ce que les disques de centrage (76) s'appliquent chacun par une surface annulaire (78) contre une surface frontale (72) plane du corps de cylindre (68) et présentent, à l'intérieur de la surface annulaire (78), un cône extérieur (86) qui s'engage dans un cône intérieur (74), complémentaire de celui-ci, du corps de cylindre (68).
  15. Moulin à cylindres selon la revendication 14, caractérisé en ce que le cône extérieur (86) est réalisé sur une barrette (84) présentant une élasticité propre.
  16. Moulin à cylindres selon l'une quelconque des revendications 11 à 15, caractérisé en ce que les disques de centrage (76) et le corps de cylindre (68) peuvent être serrés entre eux axialement.
  17. Moulin à cylindres selon la revendication 16, caractérisé en ce que des éléments filetés (96) sont enfoncés coaxialement, à partir d'extrémités opposées, dans les tourillons (16) réalisés en forme de tube et sont serrés entre eux à l'intérieur du corps de cylindre (68) par engagement fileté, pour serrer les disques de centrage (76) et le corps de cylindre (68).
  18. Moulin à cylindres selon la revendication 17, caractérisé en ce que les éléments filetés sont des boulons filetés (96) et en ce que dans le corps de cylindre (68) est maintenue coaxialement une pièce de serrage (90) qui présente à ses deux extrémités des trous taraudés (94) dans lesquels sont vissés les boulons filetés (96).
EP05740244A 2004-04-22 2005-04-18 Moulin a cylindres Not-in-force EP1740309B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE200420006309 DE202004006309U1 (de) 2004-04-22 2004-04-22 Walzenstuhl
DE200420006308 DE202004006308U1 (de) 2004-04-22 2004-04-22 Walzenstuhl
DE200420006307 DE202004006307U1 (de) 2004-04-22 2004-04-22 Walzenstuhl
PCT/EP2005/004112 WO2005102531A1 (fr) 2004-04-22 2005-04-18 Moulin a cylindres

Publications (2)

Publication Number Publication Date
EP1740309A1 EP1740309A1 (fr) 2007-01-10
EP1740309B1 true EP1740309B1 (fr) 2008-10-08

Family

ID=34966846

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05740244A Not-in-force EP1740309B1 (fr) 2004-04-22 2005-04-18 Moulin a cylindres

Country Status (4)

Country Link
EP (1) EP1740309B1 (fr)
AT (1) ATE410231T1 (fr)
DE (1) DE502005005621D1 (fr)
WO (1) WO2005102531A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102921494A (zh) * 2012-11-09 2013-02-13 张春瑜 一种辊式粉碎机
DE102015114992B4 (de) 2015-09-07 2017-07-20 Mbe Coal & Minerals Technology Gmbh Rollenpresse
DE102015114998B4 (de) 2015-09-07 2019-05-09 Mbe Coal & Minerals Technology Gmbh Rollenpresse
DE102015114997A1 (de) 2015-09-07 2017-03-09 Mbe Coal & Minerals Technology Gmbh Verfahren zur Demontage von Rollen einer Rollenpresse
ES2837143T3 (es) 2016-01-27 2021-06-29 Buehler Ag Dispositivo de soporte y procedimiento para la extracción frontal de un cuerpo de rodillo de un molino de rodillos, así como molino de rodillos con un cuerpo de rodillo frontalmente extraíble

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE38102C (de) * R. GAWRON uud J. GAWRON in Grabow bei Stettin Regelung der Walzenstellung durch die Mahlgutwärme
CH664506A5 (de) * 1984-08-03 1988-03-15 Buehler Ag Geb Mahlspaltverstellvorrichtung an einem muellereiwalzenstuhl.
JP3030702B1 (ja) * 1998-10-22 2000-04-10 株式会社オオヤマフーズマシナリー ロ―ラ装置におけるスクレイパ―装置

Also Published As

Publication number Publication date
DE502005005621D1 (de) 2008-11-20
WO2005102531A1 (fr) 2005-11-03
EP1740309A1 (fr) 2007-01-10
ATE410231T1 (de) 2008-10-15

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