EP0667186A1 - Broyeur à rouleaux - Google Patents

Broyeur à rouleaux Download PDF

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Publication number
EP0667186A1
EP0667186A1 EP94119972A EP94119972A EP0667186A1 EP 0667186 A1 EP0667186 A1 EP 0667186A1 EP 94119972 A EP94119972 A EP 94119972A EP 94119972 A EP94119972 A EP 94119972A EP 0667186 A1 EP0667186 A1 EP 0667186A1
Authority
EP
European Patent Office
Prior art keywords
gear
machine frame
coupling
roller
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.)
Granted
Application number
EP94119972A
Other languages
German (de)
English (en)
Other versions
EP0667186B1 (fr
Inventor
Jörg Dipl.-Ing. Bettenworth
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
Krupp Polysius 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 Krupp Polysius AG filed Critical Krupp Polysius AG
Publication of EP0667186A1 publication Critical patent/EP0667186A1/fr
Application granted granted Critical
Publication of EP0667186B1 publication Critical patent/EP0667186B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • B02C4/42—Driving mechanisms; Roller speed control
    • B02C4/426—Torque counterbalancing mechanisms
    • 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

Definitions

  • the invention relates to a roller mill, in particular a material bed roller mill, according to the preamble of claim 1.
  • Roller mills of this type which are also referred to as two-roller mills, are sufficiently known from practice.
  • the torques of the gears or gearbox housings placed on the shafts of the two rollers must be supported in a corresponding manner against a mill foundation or machine frame in which the rollers are rotatably supported by their shafts.
  • the invention is therefore based on the object of providing a roller mill, in particular a material bed roller mill, of the type required in the preamble of claim 1, by means of which an extremely reliable and essentially lateral force-free torque support is provided, even under relatively high stress forces and with relatively large wear-induced displacement paths of the idler roller with respect to the associated roller shaft is guaranteed.
  • each gear housing is supported with respect to the machine frame by a separate torque support device (independent of the other gear housing).
  • the torque support device for the transmission is designed on the idler roller, for example in the form of a coupling transmission.
  • This coupling gear contains two double-armed levers, each of which is pivotally mounted on the machine frame on a fixed axis of rotation and, on the one hand, via its one, outer first lever arms with mutually opposing upper and lower articulation points of the gear housing (for the associated roller) and, on the other hand, via their roughly opposing ones inner, second lever arms are each articulated with a rigid coupling member.
  • each gearbox or gearbox housing can be supported by itself on the machine frame in relation to the torque that occurs, the two rollers being able to influence one another only via the ground material crushed between them.
  • a particular advantage of such a coupling gear can be seen in the fact that the rigidity of the torque support device formed thereby remains largely unaffected even with relatively large wear paths on the part of the idler roller. All of the force application points in this coupling gear lie approximately in one plane, which is particularly advantageous for the power flow in this coupling gear.
  • Each of the rollers' housing, which is connected to the machine frame by such a coupling gear can be supported with virtually no shear force with respect to the associated roller shaft.
  • each coupling gear rigidly connects the two inner second lever arms of the two levers
  • this coupling member is loaded on the torque support by the corresponding rotary movements of the levers, whereby a further rotary movement of the levers ver prevents and thus the torque to be supported is introduced into the machine frame via the fixed axes of rotation.
  • the torque support device for the gear housing of the fixed roller in the form of a second coupling gear, which is arranged in the same way between this gear housing and the machine frame as the first coupling gear for the idler roller, but is supported independently of this first coupling gear .
  • the torque support device for the gear housing of the fixed roller essentially by means of a lever arm-like attachment on this gear housing, which is supported directly on the machine frame, preferably in an articulated manner.
  • the torque support device for the fixed roller or its gear is also formed by a coupling gear, then a completely lateral force-free support is ensured because this support system can adjust itself to it.
  • the support forces in the support arms or support lugs can be unequal, as a result of which lateral forces are to be expected.
  • This material bed roller mill 1 contains in the usual way a machine frame 2 with longitudinally extending upper chords 3 and lower chords 4.
  • two rollers 5, 6, which can be driven in opposite directions and are pressed against one another at relatively high pressure, are arranged, likewise in a manner known per se one is designed as a fixed roller 6 and the other as a loose roller 5 which can be displaced in the machine frame 2 in the direction of the fixed roller 6.
  • the fixed roller 6 is mounted on both sides in the machine frame 2 in fixed bearing blocks 7 via its shaft 6a and the loose roller 5 is supported on both sides in the machine frame 2 in floating bearing blocks 8 via its shaft 5a.
  • the roller mill 1 On one outer longitudinal side of the machine frame 2 (in FIG. 1 on the outer longitudinal side facing the viewer), the roller mill 1 contains two gears 9 and 10, respectively, which are mounted on the shafts 5a, 6a of the two rollers 5, 6, in the present case directly flanged on which can be seen above all the associated housing 9a and 10a.
  • a separate torque support device 11 or 12 is assigned to each gear housing 9a, 10a in order to be able to absorb the torque occurring between the associated gear housing 9a or 10a and the machine frame 2 and to support it with respect to the machine frame 2.
  • At least the torque support device 11 for the gear housing 9a of the idler roller 5, but in the exemplary embodiment illustrated, preferably both torque support devices 11 and 12 for the gear housing 9a, 10a on the idler roller 5 and on the fixed roller 6, are designed approximately in the form of a coupling gear.
  • Each coupling gear 11, 12 provided according to the invention has two double-armed levers 13, 14 or 13 ', 14', which are pivotally mounted on the machine frame 2 on fixed axes of rotation 15, 16 or 15 ', 16'.
  • the second coupling gear 12 for the gear housing 10a of the fixed roller 6 is in principle designed and arranged in the same way as the first coupling gear 11 for the idler roller 5, only the first coupling gear 11 for the gear housing 9a of the idler roller 5 is below for the sake of simplicity and clarity in its structure and function explained somewhat in more detail (the same applies accordingly and in an adapted manner for the second coupling gear 12).
  • This first coupling gear 11 or each coupling gear contains, in addition to the two double-armed levers 13, 14, an essentially rigid coupling member 17 and two essentially rigid connecting rods 18, 19.
  • the two double-armed levers 13, 14 of the coupling gear 11 are now on the one hand via their one, first lever arms 13a and 14a and via the associated upper and lower connecting rods 18 and 19 with mutually opposing upper and lower articulation points 20, 21 of the transmission housing 9a and, on the other hand, articulated with their rigid coupling member 17 via their approximately mutually opposing second lever arms 13b, 14b connected.
  • Each transmission housing 9a, 10a which is connected to a coupling gear 11, 12, expediently has a fixed attachment, first lever 9b pointing upward like a lever arm, and a fixed attachment, second projection 9c pointing downward like a lever arm.
  • first lever 9b pointing upward like a lever arm
  • second projection 9c pointing downward like a lever arm.
  • the two articulation points 20 and 21 of the gear housing, here the gear housing 9a incorporated, preferably in such a way that the upper and lower articulation points 20, 21 are diametrically opposed to each other.
  • the upper first connecting rod 18 of the first coupling gear 11 in question runs in the region of an upper chord 3 of the machine frame 2 and is articulated at one end with the associated upper articulation point 20 and at the other end articulated with the free end of the first lever arm pointing upward 13a in connection
  • the lower second connecting rod 19 runs in the region of a lower flange 4 of the machine frame 2 and is articulated on the one hand to the downwardly pointing first lever arm 14a of the lower second lever 14 and on the other hand to the lower second articulation point 21 of the associated transmission 9a.
  • the first and second lugs 9b and 9c of the gear housing 9a are directed substantially radially and vertically upwards and downwards and accordingly the upper and lower articulation points 20 and / or If they are diametrically opposed to each other on an approximately vertical line - as indicated by the dot-dash line in FIG. 2 - then even with certain deflecting movements of the shoulders 9b, 9c in the circumferential direction they will not extend into the area above and below the adjacent gear housing (eg 10a) .
  • the minimum distance between the two rollers 5, 6 is only determined by the size or diameter of the gear housing, i.e. there is a particularly space-saving design and arrangement for each coupling gear, so that it can be arranged particularly cheaply on the outer longitudinal side of the machine frame 2, on which the gear 9, 10 for driving the rollers are located.
  • levers 13, 14 and 13 ', 14' will generally depend on the size of the roller mill and thereby on the size of the machine frame 2 and the rollers or the gears driving them. Accordingly, the double-armed levers 13, 14 or 13 ', 14' can be designed quite generally as levers with lever arms of equal length or with non-armed lever arms, in accordance with the most expedient design and arrangement of the coupling gears on the machine frame.
  • each coupling gear 11, 12 are designed as non-uniform levers, the levers of which, pointing upwards and downwards, with the connecting rods 18, 19 connected first lever arms 13a, 14a are shorter than their opposing second lever arms 13b, 14b connected by the coupling member 17, 17 '.
  • each coupling gear 11, 12 it is now also expedient to determine the length and arrangement of the second lever arms, e.g. to select the two lever arms 13b and 14b of the two levers 13, 14 of the first coupling gear 11, and the length of the associated coupling element 17 or 17 'in such a way that the coupling element 17, 17' is predominantly subjected to horizontal tensile forces, so that vertical forces are as low as possible can be kept possible.
  • This is particularly important in the case of the first coupling gear 11, which is assigned to the gear 9 or the associated gear housing 9a of the idler roller 5, in that the said operating state (with regard to the tensile forces) also in the various wear-related displacement positions of the idler roller 5 and associated gear 9 is to be largely maintained.
  • the fixed axes of rotation 15, 16 and 15 ', 16' of both coupling gears 11, 12 - viewed in plan, but also recognizable in FIG. 2 - are arranged on the machine frame 2 with such a horizontal distance HA, that the opposing second lever arms, e.g. 13b, 14b, both levers 13, 14 and 13 ', 14' of the two coupling gears 11, 12 with their articulated connections, e.g. 17a, 17b, overlap the associated coupling element 17 or 17 'at least in their vertical or in their approximately vertical position, as is dot-dashed in FIG. 2 on the coupling gear 11 and indicated in solid lines on the coupling gear 12.
  • Each coupling member 17, 17 ' can be designed in a particularly simple design, for example in the form of a rigid flat connecting strap.
  • all articulated connections can be made extremely simply, for example in the form of claw-like link joints with slide bearings.
  • the cross member 24 is fastened for the axis of rotation 15 'of the upper first lever 13' and the cross member 25 for the axis of rotation 16 'of the lower second lever 14' in the region of the lower belt 4 of the machine frame 2.
  • the crossbeams can preferably be attached to the upper and lower chords 3, 4 by means of bolts. As a result, only tensile or compressive forces and no bending moments are introduced into the straps of the machine frame.
  • first coupling gear 11 If, for example, in the side view according to FIG. 2, the force flow on the left, first coupling gear 11 is assumed, assuming that a left-turning torque is to be supported with respect to the machine frame 2, then the directions of force indicated by arrows result in the various articulation points or connecting joints. Accordingly, the upper connecting rod 18 guides compressive forces into the upwardly directed first lever arm 13a of the upper first lever 13, which tends to turn this lever 13 - in FIG. 2 - to the left. At the same time, tensile forces are introduced on the part of the lower connecting rod 19 into the downwardly pointing first lever arm 14a of the lower second lever 14, as a result of which there is a tendency to likewise rotate this lower second lever 14 to the left, as shown in FIG.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Grinding (AREA)
EP94119972A 1994-02-14 1994-12-16 Broyeur à rouleaux Expired - Lifetime EP0667186B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4404634 1994-02-14
DE4404634A DE4404634A1 (de) 1994-02-14 1994-02-14 Walzenmühle

Publications (2)

Publication Number Publication Date
EP0667186A1 true EP0667186A1 (fr) 1995-08-16
EP0667186B1 EP0667186B1 (fr) 1998-07-01

Family

ID=6510199

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94119972A Expired - Lifetime EP0667186B1 (fr) 1994-02-14 1994-12-16 Broyeur à rouleaux

Country Status (4)

Country Link
US (1) US5553796A (fr)
EP (1) EP0667186B1 (fr)
DE (2) DE4404634A1 (fr)
ES (1) ES2117754T3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005006090A1 (de) * 2005-02-10 2006-08-24 Khd Humboldt Wedag Gmbh Zweiwalzenmaschine insbesondere zur Gutbettzerkleinerung
CN102947003A (zh) * 2010-06-18 2013-02-27 Khd洪保德韦达克有限公司 带有力矩平衡器的辊压机
CN103721783A (zh) * 2014-01-10 2014-04-16 中信重工机械股份有限公司 一种无壳体式对辊挤压机
CN105689049A (zh) * 2016-04-15 2016-06-22 高洪福 肥料结块松散机
CN113649112A (zh) * 2021-08-12 2021-11-16 龙泉市金宏瓷业有限公司 一种陶瓷生产用原料破碎装置及其使用方法

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19805137A1 (de) * 1998-02-09 1999-08-12 Krupp Polysius Ag Walzenmühle
US8695907B2 (en) 2012-04-20 2014-04-15 Metso Minerals Industries, Inc. Roller crusher with cheek plates
US8708265B2 (en) 2012-04-20 2014-04-29 Metso Minerals Industries, Inc. Roller crusher with balancing cylinders
WO2014189919A1 (fr) * 2013-05-20 2014-11-27 Flsmidth A/S Presse à rouleau et bâti associé
WO2016048814A1 (fr) * 2014-09-25 2016-03-31 Flsmidth A/S Dispositif de fixation mobile pour presses à rouleaux et procédé pour retirer certaines parties de celui-ci
DE102015205713A1 (de) * 2015-03-30 2016-10-06 Takraf Gmbh Radialrahmen zur Aufnahme von radialen Mahlkräften
CA3014904A1 (fr) * 2015-11-24 2017-06-01 Flsmidth A/S Systeme et procede d'enlevement d'un entrainement de presse a rouleaux
DE102015223694A1 (de) * 2015-11-30 2017-06-01 Takraf Gmbh Getriebehalter für eine Rollenpresse und Verfahren zum Ausbau des Getriebes einer Rollenpresse
GB2545224B (en) * 2015-12-09 2018-08-01 Terex Gb Ltd Material processing apparatus with rotor control system
EP3536404B1 (fr) * 2018-03-08 2020-08-05 Flender GmbH Dispositif support pour un couple cinématique et application industrielle
DE102020103823B3 (de) * 2020-02-13 2021-01-21 Matthews International GmbH Drehmomentstütze zum Abfangen von Antriebsmomenten und Walzenanordnung mit einer Drehmomentstütze

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE887443C (de) * 1943-10-14 1953-08-24 Asea Ab Anordnung von Antriebsaggregaten, die auf der Welle der angetriebenen Maschine aufgehaengt sind
EP0280897A2 (fr) * 1987-03-05 1988-09-07 Krupp Polysius Ag Broyeur à cylindres
EP0469376A1 (fr) * 1990-07-30 1992-02-05 Klöckner-Humboldt-Deutz Aktiengesellschaft Machine à deux rouleaux, en particulier presse à rouleaux
DE9217285U1 (de) * 1992-12-17 1993-03-25 A. Friedr. Flender AG, 4290 Bocholt Drehmomentstütze

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3901060A1 (de) * 1989-01-16 1990-07-19 Kloeckner Humboldt Deutz Ag Zweiwalzenmaschine, insbesondere walzenbrecher
DE4019363C1 (en) * 1990-06-18 1991-08-14 A. Friedr. Flender Ag, 4290 Bocholt, De Roller drive for press - has torque supports connected directly on defined load lines
US5060874A (en) * 1990-08-16 1991-10-29 Mclanahan Corporation Crusher

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE887443C (de) * 1943-10-14 1953-08-24 Asea Ab Anordnung von Antriebsaggregaten, die auf der Welle der angetriebenen Maschine aufgehaengt sind
EP0280897A2 (fr) * 1987-03-05 1988-09-07 Krupp Polysius Ag Broyeur à cylindres
EP0469376A1 (fr) * 1990-07-30 1992-02-05 Klöckner-Humboldt-Deutz Aktiengesellschaft Machine à deux rouleaux, en particulier presse à rouleaux
DE9217285U1 (de) * 1992-12-17 1993-03-25 A. Friedr. Flender AG, 4290 Bocholt Drehmomentstütze

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005006090A1 (de) * 2005-02-10 2006-08-24 Khd Humboldt Wedag Gmbh Zweiwalzenmaschine insbesondere zur Gutbettzerkleinerung
CN102947003A (zh) * 2010-06-18 2013-02-27 Khd洪保德韦达克有限公司 带有力矩平衡器的辊压机
CN102947003B (zh) * 2010-06-18 2015-01-07 Khd洪保德韦达克有限公司 带有力矩平衡器的辊压机
CN103721783A (zh) * 2014-01-10 2014-04-16 中信重工机械股份有限公司 一种无壳体式对辊挤压机
CN103721783B (zh) * 2014-01-10 2016-03-23 中信重工机械股份有限公司 一种无壳体式对辊挤压机
CN105689049A (zh) * 2016-04-15 2016-06-22 高洪福 肥料结块松散机
CN105689049B (zh) * 2016-04-15 2017-12-12 高洪福 肥料结块松散机
CN113649112A (zh) * 2021-08-12 2021-11-16 龙泉市金宏瓷业有限公司 一种陶瓷生产用原料破碎装置及其使用方法

Also Published As

Publication number Publication date
ES2117754T3 (es) 1998-08-16
US5553796A (en) 1996-09-10
EP0667186B1 (fr) 1998-07-01
DE4404634A1 (de) 1995-08-17
DE59406370D1 (de) 1998-08-06

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