EP2471600B1 - Rotor d'un concasseur à marteaux - Google Patents

Rotor d'un concasseur à marteaux Download PDF

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Publication number
EP2471600B1
EP2471600B1 EP11175069.1A EP11175069A EP2471600B1 EP 2471600 B1 EP2471600 B1 EP 2471600B1 EP 11175069 A EP11175069 A EP 11175069A EP 2471600 B1 EP2471600 B1 EP 2471600B1
Authority
EP
European Patent Office
Prior art keywords
rotor
shaft
star
adjacent
cross
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
EP11175069.1A
Other languages
German (de)
English (en)
Other versions
EP2471600A1 (fr
Inventor
Claus Richter
Thomas Woestmann
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.)
Hazemag and EPR GmbH
Original Assignee
Hazemag and EPR 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 Hazemag and EPR GmbH filed Critical Hazemag and EPR GmbH
Priority to EP11175069.1A priority Critical patent/EP2471600B1/fr
Priority to SI201130046T priority patent/SI2471600T1/sl
Priority to PL11175069T priority patent/PL2471600T3/pl
Priority to DK11175069.1T priority patent/DK2471600T3/da
Publication of EP2471600A1 publication Critical patent/EP2471600A1/fr
Priority to CN201210249538.7A priority patent/CN102886289B/zh
Application granted granted Critical
Publication of EP2471600B1 publication Critical patent/EP2471600B1/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
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/02—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft
    • B02C13/04—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft with beaters hinged to the rotor; Hammer mills
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/26—Details

Definitions

  • the invention is directed to a rotor of a hammer crusher with at least two rotor disks, which are arranged rotatably at a distance from each other on a shaft, wherein between two adjacent rotor disks several impact hammers are pivotally mounted at a radial distance from the shaft.
  • a hammer crusher with such a rotor is used for the comminution of various materials and has a high degree of comminution.
  • hammer crushers are performed with one or two rotors as a single or double shaft hammer crusher.
  • a rotor of a hammer crusher is for example from DE 27 13 177 C2 known and comprises a shaft and a certain number of laterally spaced from each other on the shaft mounted circular rotor discs, between which five percussion hammers are arranged rotatably on the circumference.
  • the shaft has a circular cross section, whereby the hammer projection, ie the extension, with which the impact hammers protrude beyond the radius of the rotor disc, turns out very small and also the transmission of torque from the shaft to the rotor disc due to the formed with keyways connection between Wave and the rotor discs is not optimal.
  • a rotor of a hammer crusher of the type mentioned above known is formed by at least one rotor disc mounted on a shaft of the rotor, on which percussion hammers are arranged distributed regularly circumferentially.
  • the impact hammers are freely rotatable within a separated vibration space, with five impact hammers are arranged on each rotor disk.
  • the shaft of the rotor has a pentagonal cross section, wherein the surfaces of the pentagon are respectively facing the vibration chambers.
  • the pentagonal cross-sectional shape of the shaft is not optimum with respect to the transmission of the torque of the shaft to the rotor disks and to the moment of resistance of the shaft. Also, the metrological verification of manufacturing accuracy in a pentagonal shaft is limited or difficult.
  • the invention is therefore based on the object, a rotor of a hammer crusher of the type mentioned in such a way that in a simple and inexpensive way, the transmission of torque between the shaft and rotor disk is improved and that the rotor has consistent good performance characteristics during a long service life. Also to be simplified and improved by the invention, the metrological verification of the manufacturing accuracy of the shaft.
  • this object is achieved in that the shaft of the rotor is formed in cross-section star-shaped with a plurality of tips, wherein a respective tip of two radially outwardly converging side surfaces is defined.
  • the invention provides a safe and durable connection of the rotor disk and the shaft, by means of which a better and higher transmission of the torque compared to the known state of the art is possible.
  • the star-shaped cross-sectional shape of the shaft unlike, for example, a known, in cross-section five- or hexagonal shaft has a higher resistance moment, whereby the star-shaped shaft higher loads, such as higher bending or torsional stresses stand.
  • significantly higher overall performances of a hammer crusher provided with such a rotor can be achieved overall.
  • the adhesion of the drive force transmitting surfaces of the star-shaped in cross-section wave is greater than in known cross-sectional shapes of the shaft, because the forces act more directly on the surfaces.
  • the wear factor in terms of the durability of the shaft-rotor disk connection is a much cheaper, so that the running time of the rotor according to the invention in a hammer crusher is a multiple of the known from the prior art embodiments.
  • a spatially particularly favorable arrangement of percussion hammers with respect to the star-shaped wave is given in development of the invention when extension lines of adjacent peaks limit a swing radius of a corresponding percussion hammer, wherein a respective extension line from the center of the shaft passes through a respective tip of the shaft.
  • These "imaginary" extension lines do not define separate or separated vibration spaces, as known in the art. Rather, it is expressed by the fact that the respective oscillation radii of the impact hammers are arranged spatially efficiently between the tips of the shaft, so that the oscillation radii of the impact hammers can have a minimum possible distance from each other and in addition a large Hammer supernatant is possible, which allows the use of impact hammers with large cross-section.
  • the rotor is inventively provided that six impact hammers are arranged between the at least two rotor disks and that the cross section of the star-shaped shaft of the rotor is a six-star.
  • the cross-sectional shape of a six-star provides a comparison with the prior art improved hammer supernatant with optimum utilization of the resonant circuits.
  • adjacent rotor disks are held at a distance by at least one spacer element arranged between them and mounted on at least one of the rotor disks.
  • the at least one spacer element prevents the impact hammers arranged between two adjacent rotor disks from being trapped by the rotor disks.
  • the rotor discs provided in this invention in contrast to known from the prior art rotor discs have no separate vibrating chambers for the individual impact hammers. Rather, in the rotor according to the invention of a hammer crusher, the side surfaces of the rotor disks, between which the impact hammers are arranged rotatably, constitute a single oscillatory space.
  • the invention provides in a further embodiment that at least on one of the two side surfaces of a rotor disk, the shaft at least partially enveloping and adapted to the cross section of the shaft load-receiving element is attached.
  • the load-bearing member may be fixedly connected to the rotor disk and increases the carrying capacity and load capacity of the shaft. It also serves to protect the shaft and may be formed of a wear-resistant material to counteract the signs of wear that could be caused by material to be crushed, if this material would pass radially inward to the shaft during the crushing process.
  • a load-receiving element can serve as a spacer to keep adjacent rotor disks at a distance.
  • a constructionally particularly suitable measure for holding the impact hammers in a rotatable manner is that each of the at least two adjacent rotor disks has a plurality of through bores corresponding to the number of impact hammers arranged between them, with corresponding through bores of the adjacent rotor disks are aligned with each other, and wherein an axle rod is passed through each of the aligned through holes, on each of which the impact hammers are pivotally mounted.
  • the invention provides in a further embodiment that at least on one of the two side surfaces of a rotor disk, a respective through hole extending extension element is mounted.
  • the extension element can also serve as a spacer to keep adjacent rotor disks at a distance.
  • a respective extension element has the function of improving the bearing stress or better dividing the acting bearing pressure on the existing surfaces.
  • the respective extension elements which have a passage opening aligned with a corresponding through hole, can be welded to a corresponding rotor disk.
  • rotor disks with their further structural features can be produced both as a cast or as a welded construction.
  • a generally designated 1 rotor of a hammer crusher is in FIG. 1 in a perspective view and in FIG. 2 shown in a sectional view.
  • the rotor 1 is part of a single or multi-rotor hammer or impact crusher.
  • the rotor 1 essentially has a plurality of circular rotor discs 2 with a small axial width, wherein for reasons of clarity in the Figures 1 and 2 only three rotor disks 2 are provided with a reference numeral.
  • the rotor 1 according to the invention has at least two rotor disks 2.
  • the rotor disks 2 are mounted rotatably on a shaft 3.
  • a plurality of impact hammers 5 are arranged distributed uniformly over the circumference of the rotor disks 2, which are mounted freely rotatable.
  • a respective rotor disk 2 has a plurality of through holes 6, which are arranged uniformly over the circumference of the rotor disk 2.
  • an extension element 4 is attached to the through holes 6, which has an aligned to the respective through hole 6 passage opening. The extension elements 4 are thus aligned over the through holes 6 of the rotor disk 2.
  • an axle 7 is passed, which extends eccentrically and axially parallel to the shaft 3.
  • a percussion hammer 5 is pivotally mounted between two adjacent rotor disks 2 respectively.
  • the axle rods 7 parallel eccentric to the shaft 3 are rotatably mounted or mounted between adjacent rotor disks 2, wherein the axle rods 7 are secured end side of the rotor 1 against axial movement.
  • the extension element 4 in this case extends the Through hole 6 in the longitudinal direction of the rotor 1 and reduces the acting during operation of the rotor 1 bearing pressure.
  • extension member 4 serves as a spacer to hold the percussion hammers 5 centrally between the rotor disks 2.
  • the extension elements 4 may be fixedly mounted on one of the two side surfaces 17 or on both side surfaces 17 of a respective rotor disk 2, for example by welding.
  • a plurality of spacer elements 14 are mounted on at least one side surface 17 of a respective rotor disk 2, to which an adjacent rotor disk 2 or a spacer element 14 of an adjacent rotor disk 2 is applied, wherein in the FIG. 4 illustrated first embodiment, which will be described below, on the side surface 17 and the back of the rotor disk 2 spacers 14 are mounted.
  • the spacer elements 14 have through openings which are aligned with through holes formed in the rotor disks 2.
  • Through the through holes of the spacer elements 14 and the rotor disks 2 are axially parallel tie rods 18 with respect to the longitudinal axis of the rotor 1 (see FIG. 2 ), with which the rotor disks 2 are clamped together to form a so-called rotor body.
  • the spacer elements 14 of adjacent rotor disks 2 are connected to each other by means of bolts 19, as in FIG. 2 is shown.
  • the shaft 3 is provided in the region of the outer rotor disks or end disks 2 ', each with an annular groove 20, as in FIG. 2 is shown.
  • annular grooves 20 two half-discs 21a and 21b are used, which are connected by screwing or welding together.
  • the half disks 21, 21b inserted into the annular grooves 20 fix the rotor disks 2 clamped together to form a rotor body against axial displacement.
  • FIGS. 3 to 6 a first embodiment of the invention is shown.
  • this has a cross-sectionally star-shaped passage opening 8, which further comprises a in the axial direction of at least one of the two side surfaces 17 of the rotor disk 2 extending from load receiving element 15, which surrounds the shaft 3 in sections substantially.
  • the cross-section of the shaft 3 adapted load-receiving element 15 is fixedly connected to the rotor disk 2 and increases the carrying capacity and load capacity of the shaft 3 and also protects them from this to be shredded material which passes radially inward.
  • the shaft 3 has a corresponding to the passage opening 8 star-shaped cross-section.
  • the star-shaped cross-section of the shaft 3 comprises a plurality of tips 9, each defined by two radially outwardly converging side surfaces 10 and 11, the side surface 11 converging radially inward with a side surface 10 'of an adjacent tip 9', as in FIG FIG. 6 is shown. More specifically, it is in the in the FIGS. 5 and 6 illustrated star-shaped cross-section of the shaft 3 to a five-star with five tips 9, wherein the illustrated rotor disk 2 five impact hammers 5 has. The tips 9 of the shaft 3 are flattened, so that a sharp outer edge is avoided.
  • Further extension lines 12 are shown extending from the center 16 of the star-shaped shaft 3 through a respective tip 9 of the shaft 3 therethrough.
  • extension lines 12 indicate the direction in which the respective tip 9 points. In doing so, two extension lines 12 of adjacent tips 9, 9 'delimit a resonant circuit or oscillation radius 13 of a respective percussion hammer 5 arranged in-between, as in particular FIG. 5 evident.
  • An inventive feature of the star-shaped in cross section shaft 3 is that the respective adjacent tip 9 or 9 'facing away from side surfaces 10 and 11' are formed parallel to each other.
  • the side 9 facing away from the tip 9 'of the tip 9' extends parallel to the side surface 10 of the tip 9 facing away from the tip 9 ' two parallel opposite side surfaces 10 and 11 'offer from a manufacturing point of view, a significant advantage over, for example, a known from the prior art pentagonal shaft, since when machining the shaft geometry always two parallel facing surfaces for clamping ready, whereas the non-clamped surfaces can be edited ,
  • FIGS. 7 and 8 a second embodiment of the invention is shown, which differs from the first embodiment in that the rotor disc 2 now instead of a through hole 8 for a star-shaped shaft 3 in the manner of a five-star now a through hole for a trained in cross section in the form of a six star star-shaped wave. 3 ' having. Furthermore, instead of five, six impact hammers 5 are now rotatably mounted on the rotor disk 2. Regardless of the differences mentioned, which essentially result from the fact that the cross section of the star-shaped shaft 3 'of the rotor 1 is a six-star, remain the same inventive features as in the FIGS. 3 to 6 obtained first embodiment, so that reference is hereby made to avoid repetition.
  • the tip 9 remote from the side surface 11 'of the tip 9' parallel to the tip 9 'facing away from side surface 10 of the tip 9, as seen FIG. 8 is apparent.
  • the respective adjacent tip 9 and 9 'facing away from side surfaces 10 and 11' parallel to each other which offers the advantages mentioned above from a production point of view.
  • the star-shaped shaft 3 ' is a five-star or a six-star
  • the star shape formed shaft 3 or 3 ' is an optimized shaft geometry, which has a higher resistance moment compared to the known from the prior art waves for hammer crusher, whereby the star-shaped shaft higher loads, such as higher bending or torsional stresses holds.
  • extension elements 4 and / or the spacer elements 14 and / or the load-bearing elements 15 may be welded to the rotor disk 2, so that the rotor disk 2 is formed as a welded assembly. But it is also conceivable that the rotor disk 2 is made with extension elements 4 and / or the spacer elements 14 and / or the load-bearing elements 15 as a one-piece casting.

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  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Pulverization Processes (AREA)

Claims (9)

  1. Rotor (1) d'un concasseur à marteaux avec au moins deux disques de rotor (2) qui sont disposés de façon solidaire en rotation à distance l'un de l'autre sur un arbre (3 ; 3'), plusieurs marteaux (5) étant, entre deux disques de rotor (2) voisins, supportés en pivotement à distance radiale de l'arbre (3 ; 3'),
    caractérisé en ce que
    l'arbre (3 ; 3') du rotor (1) est, en section transversale, constitué en étoile avec plusieurs pointes (9 ; 9'), chaque pointe (9 ; 9') étant définie par deux faces latérales (10, 11 ; 10', 11') qui convergent radialement vers l'extérieur.
  2. Rotor (1) selon la revendication 1, caractérisé en ce que des lignes de prolongement (12 ; 12') de pointes (9 ; 9') voisines délimitent un rayon d'oscillation (13) d'un marteau (5) correspondant, une ligne de prolongement (12 ; 12') respective partant du centre (16) de l'arbre (3 ; 3') et traversant une pointe (9 ; 9') respective de l'arbre (3 ; 3').
  3. Rotor (1) selon la revendication 1 ou 2, caractérisé en ce que, par rapport à deux pointes (9 ; 9') voisines de l'arbre (3 ; 3') en étoile, les faces latérales (10; 11'), éloignées de la pointe (9 ; 9') voisine respective, des deux pointes (9 ; 9') s'étendent parallèlement entre elles.
  4. Rotor (1) selon une des revendications précédentes, caractérisé en ce que cinq marteaux (5) sont disposés entre les au moins deux disques de rotor (2), et en ce que la section transversale de l'arbre (3), constitué en étoile, du rotor (1) est une étoile à cinq branches.
  5. Rotor (1) selon une des revendications 1 à 3, caractérisé en ce que six marteaux (5) sont disposés entre les au moins deux disques de rotor (2), et en ce que la section transversale de l'arbre (3'), constitué en étoile, du rotor (1) est une étoile à six branches.
  6. Rotor (1) selon une des revendications précédentes, caractérisé en ce que des disques de rotor (2) voisins sont maintenus à distance par au moins un élément d'espacement (14) disposé entre eux et mis en place sur au moins un des disques de rotor (2).
  7. Rotor (1) selon une des revendications précédentes, caractérisé en ce que, au moins sur une des deux faces latérales (17) d'un disque de rotor (2), il est mis en place un élément de reprise de charge (15) qui enveloppe l'arbre (3 ; 3') au moins par tronçons et qui est adapté à la section transversale de l'arbre (3 ; 3').
  8. Rotor (1) selon une des revendications précédentes, caractérisé en ce que chacun des au moins deux disques de rotor (2) voisins présente plusieurs alésages traversant (6) correspondant au nombre des marteaux (5) qui sont disposés entre eux, des alésages traversant (6), correspondant les uns aux autres, des disques de rotor (2) voisins affleurant les uns avec les autres, et une tige axiale (7) étant introduite à travers chacun des alésages traversant (6) en affleurement, tige sur laquelle les marteaux (5) sont respectivement supportés en pivotement.
  9. Rotor (1) selon la revendication 8, caractérisé en ce que, au moins sur une des deux faces latérales (17) d'un disque de rotor (2), il est mis en place un élément de prolongement (4) qui prolonge un alésage traversant (6) respectif.
EP11175069.1A 2011-07-22 2011-07-22 Rotor d'un concasseur à marteaux Not-in-force EP2471600B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP11175069.1A EP2471600B1 (fr) 2011-07-22 2011-07-22 Rotor d'un concasseur à marteaux
SI201130046T SI2471600T1 (sl) 2011-07-22 2011-07-22 Rotor drobilnega kladiva
PL11175069T PL2471600T3 (pl) 2011-07-22 2011-07-22 Wirnik kruszarki młotkowej
DK11175069.1T DK2471600T3 (da) 2011-07-22 2011-07-22 Rotor til en hammerknuser
CN201210249538.7A CN102886289B (zh) 2011-07-22 2012-07-18 锤式破碎机的转子

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11175069.1A EP2471600B1 (fr) 2011-07-22 2011-07-22 Rotor d'un concasseur à marteaux

Publications (2)

Publication Number Publication Date
EP2471600A1 EP2471600A1 (fr) 2012-07-04
EP2471600B1 true EP2471600B1 (fr) 2013-07-03

Family

ID=44582276

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11175069.1A Not-in-force EP2471600B1 (fr) 2011-07-22 2011-07-22 Rotor d'un concasseur à marteaux

Country Status (5)

Country Link
EP (1) EP2471600B1 (fr)
CN (1) CN102886289B (fr)
DK (1) DK2471600T3 (fr)
PL (1) PL2471600T3 (fr)
SI (1) SI2471600T1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108405074A (zh) * 2018-05-11 2018-08-17 无锡商业职业技术学院 一种新型环锤式破碎机环锤
CN108405075A (zh) * 2018-05-11 2018-08-17 无锡商业职业技术学院 一种三角形环锤
CN108435335A (zh) * 2018-05-11 2018-08-24 无锡商业职业技术学院 一种复合材料环锤式破碎机环锤
CN108686771A (zh) * 2018-04-30 2018-10-23 无锡商业职业技术学院 一种环锤式破碎机圆锤

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CN103831149A (zh) * 2014-02-24 2014-06-04 常熟中材装备重型机械有限公司 锤式破碎机的转子结构
CN103831148A (zh) * 2014-02-24 2014-06-04 常熟中材装备重型机械有限公司 转子机构改进的可逆式无篦子锤式破碎机
CN103831147A (zh) * 2014-02-24 2014-06-04 常熟中材装备重型机械有限公司 可逆式无篦子锤式破碎机
DE102015012588B4 (de) * 2015-09-29 2017-12-28 Khd Humboldt Wedag Gmbh Rotor für eine Zerkleinerungsvorrichtung
CN105498909A (zh) * 2016-01-16 2016-04-20 广西辉煌机械股份有限公司 一种破碎机转子
CN106179608B (zh) * 2016-06-29 2018-10-12 无锡商业职业技术学院 一种新型可逆式锤式破碎机锤头
CN106179607B (zh) * 2016-06-29 2018-06-26 无锡商业职业技术学院 一种新型可逆式锤式破碎机锤头
WO2018006942A1 (fr) * 2016-07-05 2018-01-11 Sandvik Intellectual Property Ab Dispositif de positionnement de rotor
CN109926185B (zh) * 2019-04-16 2023-10-20 太原市欣天力机电技术有限公司 一种用于破碎机的二级破碎辊装置
CN111632685B (zh) * 2020-06-13 2022-03-22 江苏圣耐谱特新材料有限公司 一种天然橡胶加工工艺
CN111604127A (zh) * 2020-06-18 2020-09-01 山东盛奥金万福机械科技有限公司 一种干湿物料粉碎机

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AT218837B (de) 1959-12-11 1961-12-27 Pamag Ges Fuer Patentierte Spe Rotor für Hammermühlen
DE2713177C2 (de) 1977-03-25 1989-06-08 Lindemann Maschinenfabrik GmbH, 4000 Düsseldorf Hammerbrecher
CN85101330B (zh) * 1985-04-01 1987-07-01 麻德克斯株式会社 行星齿轮组件
CN2067775U (zh) * 1990-01-20 1990-12-19 王振东 摩托车自动离合器
DE19848866A1 (de) 1998-10-23 2000-04-27 Krupp Foerdertechnik Gmbh Hammerbrecher
US7823821B2 (en) * 2002-10-24 2010-11-02 Crushing & Mining Equipment Pty Ltd Distributor plate
CA2631999C (fr) * 2005-12-08 2014-02-25 Swissrtec Gmbh Rotor pour broyeur a percussion
CN101934243A (zh) * 2010-08-31 2011-01-05 溧阳中材重型机器有限公司 单段锤式破碎机
CN201807401U (zh) * 2010-09-30 2011-04-27 黄石新兴管业有限公司 单辊破碎机

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108686771A (zh) * 2018-04-30 2018-10-23 无锡商业职业技术学院 一种环锤式破碎机圆锤
CN108405074A (zh) * 2018-05-11 2018-08-17 无锡商业职业技术学院 一种新型环锤式破碎机环锤
CN108405075A (zh) * 2018-05-11 2018-08-17 无锡商业职业技术学院 一种三角形环锤
CN108435335A (zh) * 2018-05-11 2018-08-24 无锡商业职业技术学院 一种复合材料环锤式破碎机环锤

Also Published As

Publication number Publication date
CN102886289B (zh) 2016-08-10
EP2471600A1 (fr) 2012-07-04
PL2471600T3 (pl) 2013-09-30
DK2471600T3 (da) 2013-07-29
SI2471600T1 (sl) 2013-09-30
CN102886289A (zh) 2013-01-23

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