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EP2125228B1 - Broyeur à rouleaux - Google Patents

Broyeur à rouleaux Download PDF

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Publication number
EP2125228B1
EP2125228B1 EP08717096A EP08717096A EP2125228B1 EP 2125228 B1 EP2125228 B1 EP 2125228B1 EP 08717096 A EP08717096 A EP 08717096A EP 08717096 A EP08717096 A EP 08717096A EP 2125228 B1 EP2125228 B1 EP 2125228B1
Authority
EP
European Patent Office
Prior art keywords
mill
roller
axis
pivot
pivot lever
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
EP08717096A
Other languages
German (de)
English (en)
Other versions
EP2125228A1 (fr
Inventor
Dirk Dilly
Franz-Josef Zurhove
Thomas Rüther
Ludwig KÖNNING
Pedro Guerrero Palma
Bernhard Peterwerth
Thomas Spliethoff
Heiko Fornefeld
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.)
ThyssenKrupp Industrial Solutions AG
Original Assignee
ThyssenKrupp Polysius AG
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Filing date
Publication date
Application filed by ThyssenKrupp Polysius AG filed Critical ThyssenKrupp Polysius AG
Publication of EP2125228A1 publication Critical patent/EP2125228A1/fr
Application granted granted Critical
Publication of EP2125228B1 publication Critical patent/EP2125228B1/fr
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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
    • B02C15/00—Disintegrating by milling members in the form of rollers or balls co-operating with rings or discs
    • B02C15/04—Mills with pressed pendularly-mounted rollers, e.g. spring pressed

Definitions

  • the invention relates to a roller mill with a vertical mill axis.
  • roller or roller mills also referred to as spring force or external power mills
  • spring force or external power mills can be used, for example, for comminuting cement raw materials, cement clinker, coal, ore materials and the like.
  • the ground material fed in generally centrally to the grinding plate or grinding ring is comminuted on the grinding track between the grinding ring and the grinding rollers, whereby pressing elements ensure that a correspondingly large, generally adjustable grinding force is introduced in this area.
  • each grinding roller with its roller axis can be mounted on a corresponding rocker arm, by means of which it is pressed mechanically or hydropneumatically by springs elastically against the grinding material bed formed on the grinding track.
  • the rocker arms are generally located outside of the mill housing and have a rotational axis perpendicular to the roller axis.
  • the grinding force is introduced by a pressure ring, which is under the action of a preloaded compression spring system and presses the grinding rollers against the grinding path or the befmdliche Mahlgutbett.
  • US 2005/0023390 A1 shows a vertical roller mill according to the preamble of claim 1.
  • the roller mill essentially consists of a mill housing, a grinding track rotatably mounted within the mill housing about a mill axis and at least one grinding roller which is rotatable about a grinding roller axis and is in rolling contact with the grinding track.
  • a rocker arm for rotatably supporting the grinding roller is provided, which has a tilting axis, which is arranged parallel to the Mahlrollenachse and which is mounted outside of the mill housing.
  • at least one standing with the rocker arm in operative contact hydropneumatic spring system for adjusting the contact pressure of the grinding roller is provided.
  • a first and a spaced second bearing is provided for the storage of the rocker arm about the tilting axis, wherein the tilting axis is aligned parallel to the grinding roller axis and the ratio of the distance between the grinding roller and the first bearing to the distance between the two bearings 1: 0.5 to 1 : 2 is.
  • a hydropneumatic spring system can be used to produce substantially larger forces than the previously used mechanical spring systems, which enable efficient grinding, in particular in roller mills with high throughputs.
  • the forces of the Anpresssystems and the bearing of the rocker arm on the mill housing were derived, which can lead to higher housing costs and vibration problems of the roller mill when the forces are increased.
  • the hydropneumatic suspension system may, for example, have a pull cylinder with a storage system or a pressure cylinder with a storage system.
  • the hydropneumatic spring system engages below the Mahlrollenachse on the rocker arm.
  • the grinding roller is supported at one end of the rocker arm, while the Anpresssystem comes into operative contact with the rocker arm at the other end and the rocker arm is mounted in a central region.
  • the tilting axis of the oscillating lever can be arranged in the direction of rotation of the grinding path in front of or behind the grinding roller axis. It is also conceivable to move the tilting axis of the rocking lever up to the grinding roller axis upwards or downwards.
  • Roller mill shown essentially consists of a mill housing 1, a grinding track 3 rotatably mounted within the mill housing about a mill axis 2 and at least one grinding roller 4 which is rotatable about a Mahlrollenachse 5 and is in Abrolleingriff with the grinding track 3. Furthermore, at least one rocker arm 6 is provided for rotatably supporting the grinding roller 4, which has a tilting axis 7 which is arranged parallel to the grinding roller axis 5 and which is mounted outside of the mill housing 1.
  • rocker arm is a Anpresssystem for adjusting the contact pressure of the grinding roller 4 in operative contact.
  • This pressure system is formed by a hydropneumatic spring system 8 and the rocker arm 6 is at a distance mounted to the mill housing 1 such that the forces resulting from the Anpresssystem be derived directly or via pylons 9, 10, in the mill foundation 11.
  • a plurality of grinding rollers for example two, four or six grinding rollers, are provided in the roller mill.
  • Each of the grinding rollers would then be equipped with its own rocker arm and associated hydropneumatic spring system 8. It would also be conceivable within the scope of the invention that, for example, two rollers are mounted on a rocker arm.
  • the tilting axis 7 is provided at one end of the rocker arm 6, while the hydropneumatic spring system 8, which has a pull cylinder with storage system, engages the other end of the rocker arm 6.
  • the roller is held in a central region of the rocker arm 6.
  • the Mahlrollenachse 5 is passed through the mill housing 1 to the outside, with a suitable seal is provided.
  • the hydropneumatic spring system 8 can alternatively but at least expediently engage the oscillating lever 6, which is arranged closer to the grinding roller 4.
  • the rocker arm mounting is formed by a first and a second spaced bearings 12a, 12b.
  • the bearings can optionally be designed as a rolling bearing and / or as a sliding bearing.
  • the bearing of the grinding roller 4 can take place via suitable rolling or plain bearings on the non-co-rotating Mahlrollenachse 5. But it is also conceivable that the grinding roller rotatably supported on the Mahlrollenachse 5 and the Mahlrollenachse 5 is rotatably mounted on the rocker arm 6.
  • roller mill according to the embodiment of Fig. 2a and 2 B differs from the first embodiment essentially only in that the hydropneumatic suspension system 8 engages below the Mahlrollenachse 5 on the rocking lever 6. Again, the hydropneumatic suspension system is designed as a pull cylinder. As a result, a direct power line is achieved, since only a small lever for grinding roller is present.
  • the grinding roller 4 is supported at one end of the rocker arm 6, while the hydropneumatic spring system 8 comes into operative contact with the rocker arm at the other end and the rocker arm 6 is mounted in a central region.
  • the hydropneumatic spring system 8 is designed as a pressure cylinder with a storage system. Printing cylinders are cheaper due to the simpler design than pull cylinder.
  • the tilting axis 7 of the rocking lever is arranged in the direction of rotation 13 in front of the grinding roller axis 5.
  • the conditions are reversed accordingly, so that the tilting axis 7 is arranged in the direction of rotation 13 of the grinding track 3 behind the Mahlrollenachse 5.
  • the tilting axis 7 and the grinding roller axis 5 are aligned parallel to each other, the tilting axis 7 in the embodiment according to Fig. 8 opposite the grinding roller axis 5 (slightly) set. In this way, the kinematics of the grinding roller 4 can be improved.
  • Fig. 10 the swinging geometry is shown schematically. By changing the leverage ratios and the different distances, different power ratios can be realized.
  • the rocker arm 6 allows a parallel movement of the grinding roller 4 to the grinding path 3 and therefore does not lead to changed geometry ratios in a wear of the grinding rollers, also with this storage and selection of suitable leverage a force application is possible, which is less than or equal to the force generated at the grinding roller.
  • suitable geometric conditions the forces on the two bearings 12a, 12b may even be smaller than the forces on the grinding roller.
  • this type of Mahlrollenlagerung allows the resulting from the grinding tangential force increases the vertical force on the grinding roller.

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  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Grinding (AREA)
  • Rolls And Other Rotary Bodies (AREA)

Abstract

L'invention concerne un broyeur à rouleaux avec un carter de broyeur, un plateau de broyage monté à rotation autour d'un axe de broyeur dans le carter de broyeur, et au moins un rouleau de broyage qui est rotatif autour d'un axe de rouleau de broyage et qui roule sur le plateau de broyage. Il est en outre prévu un levier oscillant pour le maintien à rotation du rouleau de broyage. Ce levier présente un axe de basculement disposé parallèlement à l'axe du rouleau de broyage, et il est monté à l'extérieur du carter de broyage. Le levier oscillant se trouve en outre en contact fonctionnel avec un système de ressort hydropneumatique, afin de régler la pression de contact du rouleau de broyage. Le levier oscillant est monté à l'extérieur du carter de broyage à distance de ce dernier de telle sorte que les forces produites par le système de ressort hydropneumatique sont déviées directement ou par l'intermédiaire de pylônes dans l'embase du broyeur.

Claims (14)

  1. Broyeur à rouleaux comprenant :
    - un carter de broyeur (1),
    - une sole de broyeur montée en rotation autour d'un axe de broyeur (2), à l'intérieur du carter de broyeur,
    - au moins un rouleau de broyage (4) qui tourne autour d'un axe de rouleau de broyage (5) et est en prise, par roulage, avec la sole de broyeur,
    - au moins un levier oscillant (6) servant à la fixation rotative du rouleau de broyage (4), lequel levier oscillant présente un axe de basculement (7) qui est monté à l'extérieur du carter de broyeur,
    - ainsi qu'au moins un système de compression se trouvant en contact actif avec le levier oscillant et servant au réglage de la force de compression du rouleau de broyage (4), système de compression qui est formé par un système à ressort (8) hydropneumatique,
    caractérisé en ce que
    - le logement du levier oscillant (6) présente un premier et un deuxième paliers (12a, 12b) espacés l'un de l'autre et comportant un axe de basculement commun (7),
    - l'axe de basculement (7) est orienté parallèlement à l'axe (5) du rouleau de broyage,
    - le rapport de la distance (L2) entre le rouleau de broyage (4) et le premier palier (12a), relativement à la distance (L1) entre les deux paliers (12a, 12b), est compris entre 1 : 0,5 et 1 : 2, et
    - le levier oscillant (6) est monté en étant distant du carter de broyeur (1), de manière telle que les forces produites par le système de compression soient déviées, directement ou via des pylônes, dans le socle du broyeur.
  2. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que le système à ressort (8) hydropneumatique présente au moins un vérin de traction comportant un système à accumulateur.
  3. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que le système à ressort (8) hydropneumatique vient s'appliquer sur le levier oscillant (6), au-dessous de l'axe du rouleau de broyage.
  4. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que le système à ressort (8) hydropneumatique présente au moins un vérin de pression comportant un système à accumulateur.
  5. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que le rouleau de broyage (4) est fixé au niveau d'une extrémité du levier oscillant (6), tandis que le système à ressort (8) hydropneumatique vient en contact actif avec le levier oscillant (6), au niveau de l'autre extrémité, et le levier oscillant est monté dans une zone centrale.
  6. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que l'axe de basculement (7) du levier oscillant (6) est disposé, suivant la direction de rotation (13) de la sole de broyeur (3), devant l'axe (5) du rouleau de broyage.
  7. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que l'axe de basculement (7) du levier oscillant (6) est disposé, suivant la direction de rotation (13) de la sole de broyeur (3), derrière l'axe (5) du rouleau de broyage.
  8. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que l'axe de basculement (7) du levier oscillant (6) est disposé en étant décalé vers le haut par rapport à l'axe (5) du rouleau de broyage.
  9. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que l'axe de basculement (7) du levier oscillant (6) est disposé en étant décalé vers le bas par rapport à l'axe (5) du rouleau de broyage.
  10. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que l'axe de basculement (7) du levier oscillant (6) est disposé de façon croisée par rapport à l'axe (5) du rouleau de broyage.
  11. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que l'axe (5) du rouleau de broyage est disposé en étant décalé par rapport à l'axe (2) du broyeur.
  12. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que le palier (12) du levier oscillant (6) présente des paliers à roulement et/ou des paliers lisses.
  13. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que le rapport de la distance (L2) entre le rouleau de broyage (4) et le premier palier (12a), relativement à la distance (L1) entre les deux paliers (12a, 12b), est compris entre 1 : 0,7 et 1 : 1.
  14. Broyeur à rouleaux selon la revendication 1, caractérisé en ce que le rapport de la distance (L3) entre l'axe de basculement (7) et l'axe (5) du rouleau de broyage, relativement à la distance (L4) entre l'axe de basculement (7) et le contact actif du système à ressort (8) hydropneumatique, est compris entre 1 : 0,8 et 1 : 2, de préférence entre 1 : 0,9 et 1 : 1,2.
EP08717096A 2007-02-28 2008-02-25 Broyeur à rouleaux Active EP2125228B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007009723A DE102007009723A1 (de) 2007-02-28 2007-02-28 Rollenmühle
PCT/EP2008/052262 WO2008104521A1 (fr) 2007-02-28 2008-02-25 Broyeur à rouleaux

Publications (2)

Publication Number Publication Date
EP2125228A1 EP2125228A1 (fr) 2009-12-02
EP2125228B1 true EP2125228B1 (fr) 2012-06-20

Family

ID=39473939

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08717096A Active EP2125228B1 (fr) 2007-02-28 2008-02-25 Broyeur à rouleaux

Country Status (7)

Country Link
US (1) US8038084B2 (fr)
EP (1) EP2125228B1 (fr)
JP (1) JP5265579B2 (fr)
CN (1) CN101588870B (fr)
DE (1) DE102007009723A1 (fr)
DK (1) DK2125228T3 (fr)
WO (1) WO2008104521A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008039541B4 (de) * 2008-08-25 2010-05-12 Polysius Ag Rollenmühle
DE102012106554A1 (de) * 2012-07-19 2014-05-15 Thyssenkrupp Resource Technologies Gmbh Verfahren und Anlage zur Zerkleinerung von Mahlgut mit einer Rollenmühle
DE102013110981A1 (de) * 2013-10-02 2015-04-02 Thyssenkrupp Industrial Solutions Ag Verfahren zum Betreiben einer Anlage mit wenigstens einem Aggregat, das eine rotierende Oberfläche aufweist
CN106176234B (zh) * 2016-07-11 2019-05-31 浙江东日药业有限公司 一种药剂科西药研磨器
DK3866979T3 (da) * 2019-04-04 2022-10-24 Loesche Gmbh Vægtstangssystem til kraftoverføring
KR102122923B1 (ko) * 2019-05-01 2020-06-26 오준태 고순도 치아용 치공구 세라믹 분말제조장치
US20230059893A1 (en) 2020-01-14 2023-02-23 Gebr. Pfeiffer Se Roller Mill Having Grinding Rollers Set At An Angle
CN111437934A (zh) * 2020-05-07 2020-07-24 张旭 一种小麦碾压破碎设备
CN112275413A (zh) * 2020-10-11 2021-01-29 绿之韵生物工程集团有限公司 一种冰磨撞击式灵芝孢子粉破壁装置

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1648176A (en) * 1927-11-08 Dry-pan grinding apparatus
DE509212C (de) 1930-10-06 Ernst Curt Loesche Walzenlagerung fuer Feberrollenmuehlen
GB943450A (en) * 1961-01-20 1963-12-04 Ernst Guenter Loesche Ring mill with hydro-pneumatic springing
DE2838782C3 (de) * 1978-09-06 1982-01-14 Loesche GmbH, 4000 Düsseldorf Walzenschüsselmühle mit hydropneumatischer Federung der Mahlwalzen
DE3100341A1 (de) * 1981-01-08 1982-07-22 Loesche GmbH, 4000 Düsseldorf Walzenmuehle, insbesondere fuer die kohlenvermahlung
JPS5836651A (ja) * 1981-08-27 1983-03-03 住友セメント株式会社 竪型粉砕装置
JPS61227855A (ja) * 1985-04-02 1986-10-09 川崎重工業株式会社 竪型ロ−ラミル
JPS62204863A (ja) * 1986-03-05 1987-09-09 川崎重工業株式会社 竪型ミル
JPH0539647U (ja) * 1991-11-05 1993-05-28 石川島播磨重工業株式会社 竪型ミルのローラ圧下装置
DE19603655A1 (de) * 1996-02-01 1997-08-07 Loesche Gmbh Wälzmühle
UA46144C2 (uk) * 1997-04-15 2002-05-15 Фсб Валкова дробарка
JP3524050B2 (ja) * 2000-10-13 2004-04-26 川崎重工業株式会社 セメント原料のための竪型ローラミル
JP2002159875A (ja) * 2000-11-28 2002-06-04 Ishikawajima Harima Heavy Ind Co Ltd 竪型ミル
JP2004160429A (ja) * 2002-11-13 2004-06-10 Abe Kumiko カイテンミル
US7028934B2 (en) 2003-07-31 2006-04-18 F. L. Smidth Inc. Vertical roller mill with improved hydro-pneumatic loading system
DE10338154B4 (de) * 2003-08-20 2010-09-02 Humboldt Wedag Gmbh Rollenmühle
DE102006061328B4 (de) * 2006-12-22 2014-01-16 Gebr. Pfeiffer Ag Wälzmühle

Also Published As

Publication number Publication date
JP2010519036A (ja) 2010-06-03
WO2008104521A1 (fr) 2008-09-04
CN101588870B (zh) 2010-12-01
DE102007009723A1 (de) 2008-09-04
US8038084B2 (en) 2011-10-18
US20100252667A1 (en) 2010-10-07
JP5265579B2 (ja) 2013-08-14
CN101588870A (zh) 2009-11-25
EP2125228A1 (fr) 2009-12-02
DK2125228T3 (da) 2012-10-01

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