EP3037250A2 - Cadre de machine pour une presse a rouleaux - Google Patents

Cadre de machine pour une presse a rouleaux Download PDF

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Publication number
EP3037250A2
EP3037250A2 EP15194199.4A EP15194199A EP3037250A2 EP 3037250 A2 EP3037250 A2 EP 3037250A2 EP 15194199 A EP15194199 A EP 15194199A EP 3037250 A2 EP3037250 A2 EP 3037250A2
Authority
EP
European Patent Office
Prior art keywords
frame
radial
machine frame
axial
rollers
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
EP15194199.4A
Other languages
German (de)
English (en)
Other versions
EP3037250B1 (fr
EP3037250A3 (fr
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.)
Takraf GmbH
Original Assignee
MAN Takraf Fordertechnik GmbH
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 MAN Takraf Fordertechnik GmbH filed Critical MAN Takraf Fordertechnik GmbH
Publication of EP3037250A2 publication Critical patent/EP3037250A2/fr
Publication of EP3037250A3 publication Critical patent/EP3037250A3/fr
Application granted granted Critical
Publication of EP3037250B1 publication Critical patent/EP3037250B1/fr
Active 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
    • 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
    • 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 machine frame for a roller press.
  • Roller presses are machines for comminution with mostly two rollers, also referred to as rollers, which are arranged in a machine frame. For the comminution grinding, the particles are drawn into a roller gap, pressed together by the high pressure exerted by the rollers and crush each other. Of the roles is usually designed as a fixed and a loose role. Roller presses are also referred to as roller mills or presses and are used in cement production and mining.
  • the machine frame must absorb the high radial forces as well as the occurring axial forces. In this case, torsions in the machine frame are to be avoided, since these lead to a misalignment of the rollers and thus to an inhomogeneous pressure distribution with concomitant deterioration of the crushing result.
  • the rollers are guided with their bearings and held in position in the axial direction, while allowing a misalignment and the possibility of horizontal movement of the rollers or their storage in the frame.
  • the Losrolle has a much greater freedom of movement than the fixed role due to a support by hydraulic cylinders.
  • a roller press which has a cuboid, closed frame, consisting of a top and bottom chord.
  • the radial forces are absorbed by the straps as tensile forces.
  • the axial forces are guided in laterally attached to the straps and the rollers axially limiting carrier.
  • the belts are also loaded with a proportion of the weight of the rollers.
  • a disadvantage of this machine frame for a roller press is the high weight and the high cost of disassembly for repair purposes.
  • a roller press comprising a machine frame consisting of a plurality of welded elements, which are interconnected with a shear bolt screw connection.
  • the rollers with bearings once as a loose roller with hydraulic support and once as a fixed roller, are guided in a friction-smooth sliding manner.
  • the closed frame takes over the pressing forces in the radial and axial direction and is therefore designed to be correspondingly stiff.
  • the frame On the fixed roller side, the frame is easy and quick to open so that the rollers with storage can be removed and installed horizontally quickly.
  • the disadvantage of this frame is material-consuming and therefore costly to produce. A repair of the frame is expensive.
  • the object of the present invention is to propose a simply constructed machine frame for a roller press, which is easy to manufacture and quick to assemble, and which can accommodate the radial and axial forces occurring torsion-free.
  • the task is solved by a subdivision of the machine frame according to the forces acting in intersecting frame parts.
  • the machine frame according to the invention for a roller press has an axial frame and at least two radial frames.
  • the terms axial frame and radial frame mean that the axial frame, the axial forces of the rollers, in particular the weight and forces that occur when misalignment of the idler roller, and the radial frame, the radial forces of the rollers, in particular the contact forces absorb. Consequently, the radial frame is aligned transversely to the axes of rotation of the rollers.
  • the radial frame are rectangular, so each form a flat structure with four carrier-like frame elements.
  • the means for receiving the radial forces are not rigid, but elastically mounted in the machine frame.
  • the radial forces are not transmitted to the Axialrahmen.
  • the axial frame has an axial frame upper part and an axial frame lower part.
  • the Axialrahmenoberteil is formed by two U-shaped assemblies, which are aligned parallel to the axes of rotation of the rollers.
  • the two U-shaped modules are interconnected by structural elements.
  • the Axialrahmenunterteil is a rectangular structure that forms the base plate of the Axialrahmens.
  • Axialrahmenoberteil and -untererteil means for sliding movement of the rollers with storage, preferably slideways on.
  • the Axialrahmenunterteil so takes on the weight of the rollers in addition to the axially acting operating forces.
  • a horizontal, low-friction sliding of the hydraulically supported idler roller in the frame is preferably achieved by the sliding pair Teflon / polished chromium plate.
  • polished chrome plates are arranged on Axialrahmenoberteil and -unterteil; Chambered slide plates made of Teflon are used as a sliding counter surface on the bearing housing.
  • the individual elements of this sliding pair are preferably screwed and thus advantageous to replace a wear part in a simple manner.
  • the sliding plate made of Teflon is arranged in a depression in a carrier plate, so that the depression holds the sliding plate made of Teflon, and the edges of the opening in the carrier plate absorb the thrust forces.
  • the screwing and / or bonding of the sliding plate must thereby only perform the fixation of the sliding plate in the carrier plate.
  • Axialrahmenoberteil and -unterteil outside, parallel to the radial frame, supporting plates with slide rails.
  • sliding and guide elements are arranged, via which the rollers are slidably guided on the support plates with slide rails, so that both in the roller press operation necessary freedom of movement of the idler roller is guaranteed, as well as the installation and removal of the rollers is possible.
  • This slide and guide system also includes external guides, are introduced via the axial forces occurring in the axial frame.
  • the radial frames have longitudinal sides and short sides, wherein the longitudinal sides are arranged horizontally in the assembled state and the short sides vertically.
  • the longitudinal sides each comprise a belt system which, referred to the installation location, has upper or lower belts (in the installed state near the ground).
  • the short sides of the radial frames are referred to as vertical spars.
  • the storage of belts in the belt system is carried out in elastic damping elements.
  • the introduction of the radial operating force via the vertical bars in the straps. Between the straps and the vertical beams there is a positive connection.
  • the machine frame according to the invention has no shear bolt screw connection between the straps and the force receiving points (belt contact surfaces for the vertical struts).
  • the belts are stressed by the radial operating forces to train in the direction of elongation.
  • the straps are made of sheet steel or wide flattened steel.
  • the radial frame is constructed as follows.
  • the vertical beams consist of two parallel, vertically arranged, spar-like side parts, which are interconnected at the upper end by the axis of rotation of a rotary joint (vertical pair of hollows).
  • the swivel joint is preferably fastened by means of an axis of rotation with slide bearing and locknuts.
  • the axis of rotation carries a suspension joint between the two spar-like side parts.
  • the suspension joint has a lower link.
  • the lower link has a lower link hook.
  • the upper end of the vertical bars is fastened to the axial frame by means of the lower link catch hook of the rotary joint.
  • the lower end of the vertical frame end pieces is inserted into cavities formed of the lower axial frame, a closure member and the lower straps.
  • the side parts at its lower end preferably on the side facing away from the pivot side, preferably insertion surfaces.
  • These plug-in surfaces facilitate the insertion of the side parts in the cavities. They are preferably conically shaped. Particularly preferably, the insertion surfaces on sliding coatings (eg. Teflon).
  • Upper and lower straps are preferably designed as two parallel superimposed straps, which are referred to as double straps.
  • a belt system can also each have a single belt with welded, forged headboard.
  • the double straps are connected at their head ends with special hammer head-like welded constructions - the head connections.
  • the straps run between the two parallel side panels of the vertical struts.
  • the vertical bars are supported in the direction of the radial force on the head parts or head connections of the straps.
  • the straps At the ends directed away from the vertical bars, the straps have an elastic damping element.
  • the damping element of the straps is biased by the amount (path) resulting from the elongation resulting from the operating force.
  • the biased by a defined path elastic support of the straps in operation at nominal force is almost relieved, i. relaxed.
  • the elaborate shear bolt screw connection between the straps and the load-bearing points is replaced in this frame version by a welded or forged connection and belongs to the belt system.
  • the mechanical combination of vertical spar and belt can be significantly stabilized and the torque transmission can be improved.
  • the recording of the radial forces and the absorption of the axial forces are largely separated by the inventive structure of the machine frame, a mutual influence was largely excluded.
  • the damping element also causes the shocks occurring during operation mitigated.
  • the machine frame is simple and individual parts of the frame are easy to swap.
  • the weight-optimized belt systems are held parallel by the axial frame, auxiliary supports are advantageously not required.
  • the belt systems take no weight forces from the rollers with bearings and thus have no sliding elements for the Losrollenzi on.
  • the straps are thus purely zugbelastetet by the radial forces and obtain a component symmetrical expansion. Due to the absence of the sliding elements, the belt systems do not need to be machine-optimized over their length to be machined and cost-effective to manufacture.
  • At least one of the vertical beam pairs of the radial frame is detachable.
  • the vertical bars can be quickly removed to remove the rollers.
  • the bearing housings of both rollers are supported in the radial frame in the horizontal direction.
  • one of the two Vertikalholmpaare a radial frame on a system for the storage of a loose roll and the other a system for the storage of a fixed role.
  • the support on the fixed roller side via a rubber thrust bearing and on the Losrollenseite via a rubber thrust bearing and hydraulic cylinder.
  • a foundation frame is located under the machine frame.
  • This foundation frame can form the ground-level support of the single frame.
  • the foundation frame is preferably made by means of welded joints.
  • axial and radial frame parts can be fastened to the foundation frame by means of screw connections.
  • the separate, easy-to-align foundation frame advantageously provides a platform that allows easy and fast construction of the drive and frame parts of a roller press.
  • axial frames and radial frames are each screwed together via the belt system of the radial frame.
  • a belt system box-shaped Frame elements These preferably have parallel longitudinal support elements, between which run the straps.
  • the longitudinal support members are bolted to Axialrahmenober- and -unterteil, wherein the radial operating forces according to the invention are not passed through the screw to the Axialrahmenimplantation by the elastic mounting of the straps in the box-shaped frame members.
  • the box-shaped frame members of a belt system and the axial frame are connected by a vertical pin as a centering connector. Due to the screw connections, the machine frame is easy to assemble and disassemble, and also repair work is easier than in a multi-part welded together of horizontal and vertical frame members frame.
  • the radial frames are smaller than the axial frames, so that in the assembled state, the radial frames are within the Axialrahmens. This means, as it were, that the rollers fit in a direction orthogonal to their axis of rotation through the axial frame.
  • the removal of the rollers is further simplified because the axial frame does not have to be removed.
  • the so-called cross frame enables the clear separation of the forces into the frame components provided therefor, ie. the axial frame absorbs the axial forces and the radial frames absorb the radial forces.
  • the radial frames no longer have to take up any weight forces of the rollers, so that no bending moments are effective, but only tensile forces acting as far as possible on the radial frames.
  • the rollers Due to the two large axial frames through which the rollers can be passed, the rollers are also very simple and can be removed in the direction of the fixed roller. Further preferably, an expansion is also possible in the direction of the idler.
  • the structure of the frame as a modular system is very advantageous because different frame components can be used for roller presses of various sizes.
  • FIG. 1 shows the structure of a machine frame 1 according to the invention for a roller press.
  • This machine frame 1 has an axial frame 2 with a Axialrahmenoberteil 21 and a Axialrahmenunterteil 22. Perpendicular thereto and within the Axialrahmens 2 two radial frame 3 are arranged. Near the ground is located under the Axialrahmenunterteil 22 a foundation frame 4.
  • the radial frame each have an upper belt system 32 designed as a double belt upper flange 321 and a lower belt system 31 with designed as a double belt lower flange 311. Upper and lower belt system are identical.
  • the short sides of the radial frame 3 form vertical spars, which are each arranged as a vertical pair of hollows 33.
  • Axialrahmenunterteil 22 Parallel to the belt systems 31, 32 supporting plates with slide rails 23 on the Axialrahmenoberteil 21 and the Axialrahmenunterteil 22 are mounted.
  • the rigid components of the outer guides 24 are also attached to the Axialrahmenoberteil 21 and the Axialrahmenunterteil 22.
  • Indicated on Axialrahmenunterteil 22 is the housing 6 of the rollers, which prevents comminuted material in operation from the roller gap penetrates to the outside.
  • the upper belt system 32 is connected to the Axialrahmenoberteil 21 and the lower belt system 31 with the Axialrahmenunterteil 22 via screw (mounting holes are indicated) and each a centering 81 (on the radial frame, concealed below) with counter-hole 82 (on the axial frame, top concealed).
  • FIG. 2 Shown are a respective half of the axial frame 2 with Axialrahmenoberteil 21 and the Axialrahmenunterteil 22 and a radial frame 3, consisting of the lower belt system 31 with lower flange 311, the upper belt system 32 with Obergurt 321 and two vertical pair of hollows 33.
  • a belt system 31, 32 consists of, here as running parallel double straps, straps 311, 321 and box-frame-shaped brackets, the longitudinal beam members 37 have. In the distances between the straps 311, 321 and the longitudinal support members 37 each engage the individual struts of a Vertikalholmcrus 33 a.
  • the straps 311, 321 have special welded constructions or forged head connections 38 at the respective ends.
  • the straps are mounted in elastic damping elements 36 in the belt system.
  • Fixed and Losrolle a roller press usually each have a fixed bearing and a movable bearing. Shown is the fixed bearing side view of the machine frame with the fixed bearing of the idler roller 51 and the fixed bearing of the fixed roller 52, each with bearing housings. Both roles are supported horizontally in the radial frame 3. You can see the system for the Losrollenlager 51 in the form of a rubber pressure bearing with hydraulic cylinder 34 which is attached to the vertical pair of fins 33.
  • the fixed roller-side system in the form of a rubber thrust bearing is covered in the figure.
  • the hydraulic elements on the idler side set the gap between the idler and the idler during operation (operating gap).
  • sliding guides 25 are mounted, which guide the weight of a roller to the belt systems 31, 32 around in the Axialrahmenunterteil 22.
  • sliding guides 25 are arranged at the top and bottom sliding plates 251, preferably made of Teflon, arranged (see FIG. 4 ).
  • Gleit Vietnamese construction 22 are on the Axialrahmenoberteil 21 and the Axialrahmenunterteil with support plates Slide rails 23, preferably made of polished chromium plates, attached.
  • the outer guide 24 has both rigid, attached to the Axialrahmenoberteil 21 or -unterteil 22, elements 241 and movable, attached to the sliding guides 25 elements 242 (see FIG.
  • the outer guides 24 hold the rollers axially in position and direct the axial forces in the Axialrahmen 2.
  • the outer guides 24 are also preferably equipped with the sliding pair Teflon / polished chrome plate.
  • FIG. 3 shows a detailed view of the lower belt system 31 of a machine frame 1 according to the invention, comprising the connected by means of the welded construction 38 (head connection), designed as a parallel double straps lower straps 311 and the longitudinal support members 37 as a holder of the straps 311.
  • the longitudinal support members 37 via screw (fastening holes 39) and a centering pin 81 with counter-hole 82 (see FIG. 1 ) is connected to the Axialrahmenunterteil 22.
  • the two individual spars of the vertical spar pair 33 are inserted between the straps 311 and the longitudinal support elements 37.
  • the vertical hinge pair 33 absorbs the radial operating forces and forwards them to the straps 311 on.
  • the belt heads with the force bearing surfaces 331 for introducing the radial forces from the vertical beams 33 in the straps 311 have no screw or bolt connections.
  • the straps 311 are elastically mounted via a damping element 36 in the belt system 31. As a result, the radial operating forces are not transmitted to the side members 37 and thus not to the Axialrahmenunterteil 22.
  • FIG. 4 shows a side view of the fixed bearing side of a machine frame 1 according to the invention, to illustrate the structure of the roller bearing in the machine frame 1, are introduced by the axial forces only in the axial frame 2 in an advantageous manner.
  • sliding guides 25 are mounted, which have at its upper and lower end chambered sliding plates 251, preferably made of Teflon.
  • the outside lying sliding plates 251 which are wearing parts can be removed in an advantageous manner without having to remove the rollers with storage from the frame.
  • As a sliding counterpart on the Axialrahmenoberteil 21 and -unterteil 22 support plates with slide rails 23, preferably polished chrome plates, attached, preferably with tack welds and / or screws.
  • the rigid components 241 of the outer guides 24 are attached to the Axialrahmenoberteil 21 and -unterteil 22.
  • the movable members 242 of the outer guides 24 are attached to the slide guides 25.
  • the sliding guides 25 serve, connected to a cross member, not shown, also as a stop means for the transport and lifting of the rollers.
EP15194199.4A 2014-11-18 2015-11-12 Cadre de machine pour une presse à rouleaux Active EP3037250B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014223524.3A DE102014223524A1 (de) 2014-11-18 2014-11-18 Maschinenrahmen für eine Rollenpresse

Publications (3)

Publication Number Publication Date
EP3037250A2 true EP3037250A2 (fr) 2016-06-29
EP3037250A3 EP3037250A3 (fr) 2016-08-17
EP3037250B1 EP3037250B1 (fr) 2020-02-19

Family

ID=54601619

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15194199.4A Active EP3037250B1 (fr) 2014-11-18 2015-11-12 Cadre de machine pour une presse à rouleaux

Country Status (8)

Country Link
US (1) US10065192B2 (fr)
EP (1) EP3037250B1 (fr)
AU (1) AU2015258205B2 (fr)
CA (1) CA2912492C (fr)
CL (1) CL2015003380A1 (fr)
DE (1) DE102014223524A1 (fr)
MX (1) MX364404B (fr)
PE (1) PE20160342A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015205713A1 (de) * 2015-03-30 2016-10-06 Takraf Gmbh Radialrahmen zur Aufnahme von radialen Mahlkräften
US10933422B2 (en) * 2018-06-19 2021-03-02 Ecomill, Llc Roller grain mill
DE102019119070B4 (de) * 2019-07-15 2023-05-25 Takraf Gmbh Maschinenrahmen für walzenpresse
GB2607620B (en) * 2021-06-09 2023-06-07 Weir Minerals Netherlands Bv High pressure grinding roll module

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DE102005045273A1 (de) 2005-09-22 2007-03-29 Khd Humboldt Wedag Gmbh Zweiwalzenmaschine insbesondere zur Gutbettzerkleinerung
DE102005061085A1 (de) 2005-12-21 2007-06-28 Khd Humboldt Wedag Gmbh Zweiwalzenmaschine insbesondere zur Gutbettzerkleinerung
DE102010015374A1 (de) 2010-04-20 2011-10-20 Khd Humboldt Wedag Gmbh Maschinenrahmen für eine Walzenpresse

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CN1114918A (zh) * 1994-07-11 1996-01-17 贵州省建筑材料科学研究设计院 对辊辊压破碎机
EP1374999B1 (fr) * 2002-04-26 2011-08-17 Rieter-Werke GmbH Broyeur à rouleaux
DE102005006090A1 (de) * 2005-02-10 2006-08-24 Khd Humboldt Wedag Gmbh Zweiwalzenmaschine insbesondere zur Gutbettzerkleinerung
DE102007031879B4 (de) * 2007-07-09 2009-07-02 Polysius Ag Walzenpresse mit verschiebbaren Kopfstücken
DE102010024231B4 (de) 2010-06-18 2015-02-12 Khd Humboldt Wedag Gmbh Rollenpresse mit Momentenwaage
AU2012253238A1 (en) * 2011-05-12 2013-11-28 Mclanahan Corporation Pty Ltd Crushing apparatus and method
DE102012000423B4 (de) 2012-01-12 2017-05-24 Khd Humboldt Wedag Gmbh Maschinenrahmen einer Hochdruckrollenpresse
CN202683265U (zh) 2012-07-02 2013-01-23 广西靖西县一洲锰业有限公司 对辊破碎机
DE102012112102B3 (de) 2012-12-11 2013-12-24 Maschinenfabrik Köppern GmbH & Co KG Walzenpresse
DE102013104097A1 (de) 2013-04-23 2014-10-23 Thyssenkrupp Industrial Solutions Ag Walzenmühle
CN104088959B (zh) 2013-12-31 2019-04-26 飞翼股份有限公司 一种辊压机减振装置及辊压机

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DE102005045273A1 (de) 2005-09-22 2007-03-29 Khd Humboldt Wedag Gmbh Zweiwalzenmaschine insbesondere zur Gutbettzerkleinerung
DE102005061085A1 (de) 2005-12-21 2007-06-28 Khd Humboldt Wedag Gmbh Zweiwalzenmaschine insbesondere zur Gutbettzerkleinerung
DE102010015374A1 (de) 2010-04-20 2011-10-20 Khd Humboldt Wedag Gmbh Maschinenrahmen für eine Walzenpresse

Also Published As

Publication number Publication date
CL2015003380A1 (es) 2016-09-30
MX364404B (es) 2019-04-24
EP3037250B1 (fr) 2020-02-19
AU2015258205A1 (en) 2016-06-02
CA2912492C (fr) 2017-09-05
AU2015258205B2 (en) 2016-09-15
EP3037250A3 (fr) 2016-08-17
PE20160342A1 (es) 2016-04-30
DE102014223524A1 (de) 2016-05-19
US20160136649A1 (en) 2016-05-19
US10065192B2 (en) 2018-09-04
MX2015015780A (es) 2016-06-07
CA2912492A1 (fr) 2016-05-18

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