EP3106228B1 - Dispositif et outil de broyage de materiaux de chargement - Google Patents

Dispositif et outil de broyage de materiaux de chargement Download PDF

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Publication number
EP3106228B1
EP3106228B1 EP16174479.2A EP16174479A EP3106228B1 EP 3106228 B1 EP3106228 B1 EP 3106228B1 EP 16174479 A EP16174479 A EP 16174479A EP 3106228 B1 EP3106228 B1 EP 3106228B1
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EP
European Patent Office
Prior art keywords
rotor
comminution
tools
axial length
grinding
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
EP16174479.2A
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German (de)
English (en)
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EP3106228A1 (fr
Inventor
Hartmut Pallmann
Berthold Alles
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Pallmann Maschinenfabrik GmbH and Co KG
Original Assignee
Pallmann Maschinenfabrik GmbH and Co KG
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Priority to PL16174479T priority Critical patent/PL3106228T3/pl
Publication of EP3106228A1 publication Critical patent/EP3106228A1/fr
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    • 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
    • B02C13/14—Disintegrating by mills having rotary beater elements ; Hammer mills with vertical rotor shaft, e.g. combined with sifting devices
    • 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
    • B02C13/14—Disintegrating by mills having rotary beater elements ; Hammer mills with vertical rotor shaft, e.g. combined with sifting devices
    • B02C13/18—Disintegrating by mills having rotary beater elements ; Hammer mills with vertical rotor shaft, e.g. combined with sifting devices with beaters rigidly connected to the rotor
    • 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
    • B02C13/28—Shape or construction of beater elements
    • 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
    • B02C13/28—Shape or construction of beater elements
    • B02C13/2804—Shape or construction of beater elements the beater elements being rigidly connected to the rotor
    • 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
    • B02C13/282—Shape or inner surface of mill-housings
    • 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
    • B02C13/288—Ventilating, or influencing air circulation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C23/00—Auxiliary methods or auxiliary devices or accessories specially adapted for crushing or disintegrating not provided for in preceding groups or not specially adapted to apparatus covered by a single preceding group
    • B02C23/18—Adding fluid, other than for crushing or disintegrating by fluid energy
    • B02C23/24—Passing gas through crushing or disintegrating zone
    • B02C23/28—Passing gas through crushing or disintegrating zone gas moving means being integral with, or attached to, crushing or disintegrating element
    • 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
    • B02C13/14—Disintegrating by mills having rotary beater elements ; Hammer mills with vertical rotor shaft, e.g. combined with sifting devices
    • B02C2013/145—Disintegrating by mills having rotary beater elements ; Hammer mills with vertical rotor shaft, e.g. combined with sifting devices with fast rotating vanes generating vortexes effecting material on material impact
    • 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
    • B02C13/28—Shape or construction of beater elements
    • B02C2013/2808—Shape or construction of beater elements the beater elements are attached to disks mounted on a shaft

Definitions

  • the invention relates to a device for comminuting feed material according to the preamble of patent claim 1.
  • Such devices are known, inter alia, as eddy-current mills for the fine and ultra-fine grinding of pourable feed material and in particular for the grinding of heat-sensitive feed material.
  • the DE 35 43 370 A1 discloses such a mill with a cylindrical stator and a rotor rotating therein. While the stator extends over the entire axial length of the rotor, the rotor is divided into several mill stages by arranging axially spaced circular disks. Each grinding stage is assigned a large number of grinding plates which are detachably attached to the outer circumference of the circular disks. When the rotor is rotating, the grinding plates with their axially running edges create a vortex field in which the good particles are constantly accelerated and redirected. The size of the feed material is reduced by acceleration, impact and friction forces to which the material particles are exposed in the swirl field.
  • An improved mill is in the DE 197 23 705 C1 described.
  • the grinding zone is divided into an inlet-side area, where the feed material is first shredded by mechanical action of the grinding bars before it reaches the outlet-side area of the grinding zone, where autogenous shredding takes place in the vortex field of the rotor.
  • the mill can be adapted to the specific peculiarities of the feed material and the comminution process both in the inlet-side and outlet-side mill area, thereby increasing the effectiveness of the mill.
  • an eddy current mill known, with a housing and a turbine rotatably mounted therein.
  • the inner circumference of the housing is designed as a stator, with which grinding tools arranged along the outer circumference of the turbine interact. Due to the high peripheral speed of the grinding tools, a vortex field is generated in which the good particles are exposed to high impact and shear forces, which cause the feed material to be minced very finely.
  • the object of the invention is to further develop known devices with a view to an economical shredding operation and a consistently high quality of the end product.
  • a basic idea of the invention is to modify the shape of the effective edges of the grinding tools of a rotor in such a way that there are additional effects which improve the size reduction effect.
  • the invention is based on the fact that an edge moving in a gaseous medium produces vortices whose vortical axis is aligned parallel to the edge. In the area of influence of the vortices, the individual good particles are exposed to enormous acceleration forces and changes of direction, as well as impact and friction forces, which perform the shredding work.
  • the invention now aims to change the vortex field in the peripheral region of the rotor, for which purpose the axially extending effective edges of the grinding tools are set back in one or more sections in the direction of the rotor axis. It arise in first sections L 1 axially extending effective edges with a first radial distance R 1 to the rotational axis and arranged between the first sections L 1 second sections L 2 axially extending active edges with a differing therefrom, a second radial distance R 2 to the rotation axis, wherein the first radial distance R 1 is greater than the second radial distance R 2 .
  • the second subsections L 2 include all subsections with a smaller radial distance compared to the first subsections L 1 , which means that the second subsections L 2 can also have different radial distances R 2 from one another as long as they are smaller than the radial distance R 1 of the first sections L 1 to the axis of rotation.
  • This constructive measure creates radially running effective edges that not only lengthen the length of an effective edge of a grinding tool, but also generate additional vortices with a radially oriented vortex axis.
  • radial Effective edge is understood not only as a right angle between axially and radially extending edges, but generally also as an arrangement of the radial edges transverse to the axially extending edges. Because of the course of the active edge according to the invention, each grinding tool therefore creates two types of vortices, whose vortical axes are transverse, preferably perpendicular, to one another and whose intensity varies temporally and spatially due to mutual influence.
  • the superimposition of the differently oriented vortices causes extremely complex turbulent flow conditions in the spaces between two adjacent grinding tools.
  • the efficiency of the comminution process is increased considerably, which is initially noticeable in an unexpectedly high increase in performance of a device according to the invention.
  • the relatively short dwell time of the feed material in the grinding area minimizes the heat input into the feed material, so that such a device is also suitable for comminuting heat-sensitive feed material.
  • a device according to the invention is thus also distinguished from known devices by a higher degree of comminution.
  • a grinding tool generally extends over the entire axial length of the grinding zone, all the effective edges can be exchanged by changing a relatively small number of grinding tools.
  • the tool change times when the grinding tools are replaced due to wear or when the device is switched to another feed material can be reduced to a minimum in this way, which leads to an extremely economical overall operation of a device according to the invention.
  • the intended for an advantageous adjustment and optimization Measures include, among other things, the selection of a suitable number and / or relative length of the first and second subsections L 1 , L 2 of the axially running effective edges in relation to the total length L of the grinding tools or the selection of a suitable length ratio between the first subsections L 1 and second Sections L 2 .
  • the sum of the lengths of all first sections L 1 is 50% to 90% of the total axial length L of a grinding tool, most preferably 60% to 80% and / or the sum of all lengths of the first sections L 1 and / or the sum of all lengths of the second sections L 2 are in a ratio of 5: 1 to 1: 1.
  • This means that at least half the length of an effective edge of a grinding tool according to the invention is available due to the smaller radial distance from the stator tools for intensive interaction with the stator tools, where a large part of the shredding work is carried out.
  • the axial length of a single second section L 2 of an effective edge of a grinding tool of a device according to the invention can be 10% to 50% of the total axial length L of the grinding tool, preferably 20% to 40%. This measure limits the axial length of the second subsection L 2 with respect to the total length of the grinding tool and thus enables targeted control of the material flow within the rotor.
  • a grinding tool has at most eight second sub-sections L 2 over its length, preferably two to four second sub-sections L 2 .
  • the number of second subsections L 2 can influence the intensity and thus the efficiency of the comminution, a vortex field with a largely uniform comminution effect being generated in the peripheral region of the rotor.
  • the number and thus the effect of the vertebrae with the radially oriented vertebrae axis can be set by a suitable length of the radially effective edges.
  • the radially effective edge has a maximum length which corresponds to the axial length of the adjacent second section L 2 and which is preferably 30% to 60% of the axial length of the adjacent second section L 2 .
  • this will also have an influence on the course of the material flow in the rotor, since the material to be fed flows in a concentrated manner from one chamber to an adjacent chamber between the grinding tools in the regions of the second subsections L 2 due to the greater radial distance from the stator tools.
  • the length of the radially effective edges of a preferred grinding tool is, for example, at least 5 mm, at least 8 mm, at least 10 mm, at least 15 mm or at least 20 mm.
  • the set back second sections L 2 of the axially effective edges thus lead to a material flow within a device according to the invention, in which larger particles in the area of these second sections L 2 flow from a chamber formed between two adjacent grinding tools in the rotor into a subsequent chamber in order to continue there to be crushed.
  • already sufficiently fine particles of good are entrained by the air flow in the leading vortex chamber and removed from the device.
  • this type of processing has the additional advantage that the comminuted good is very uniform within narrow limits with regard to the shape and size of the individual commodity particles, so that high demands on the quality of the end product are also met.
  • the effective edges of the second section L 2 or the second section L 2 of two grinding tools adjacent in the rotor can have the same radial distance R 2 to the axis of rotation or else a different radial distance. If, for example, the radial distance R 2 of the section L 2 leading in the direction of rotation is smaller than that of the subsequent section L 2 , a larger proportion of the feed material will strike the subsequent grinding tool and be comminuted there. In this way, the material flow and the intensity of the shredding can be controlled become.
  • This effect is controlled according to the invention by the fact that the second sections L 2 of a grinding tool have an axial offset V with respect to the second sections L 2 of a grinding tool adjacent in the rotor.
  • the material flow is thereby controlled by a device according to the invention in such a way that the feed material flows successively through a plurality of chambers formed in the rotor between the grinding tools on its way from the inlet side to the outlet side of the rotor.
  • the chambers each form a processing stage through which the feed material passes in succession.
  • the axial offset V can be selected to be smaller.
  • a grinding tool it is possible for a grinding tool to have a plurality of second sections L 2 over its axial length and for the feed material to pass through a larger number of chambers.
  • the offset V of two second sections L 2 adjacent in the direction of rotation can be, for example, at least the sum of half the axial length of the second section L 2 of the leading milling tool and half the axial length of the second section L 2 of the subsequent milling tool , most preferably at least the sum of the axial length of the second section L 2 of the leading milling tool and the axial length of the second section L 2 of the subsequent milling tool.
  • the second portions L 2 lie on a number of parallel helical lines about the rotor axis, the pitch of the helical lines determines the degree of axial displacement.
  • the helical lines preferably run at an angle ⁇ between 10 degrees and 50 degrees to the surface lines of the rotor, most preferably at an angle ⁇ between 20 degrees and 35 degrees.
  • an advantageous embodiment of the invention provides that the effective edges of the grinding tools run at an angle ⁇ to the surface lines of the rotor. If the effective edge of the grinding tool on the outlet side is inclined in the direction of rotation (- ⁇ ), there is a restrained effect with longer dwell times of the feed material in the area of the grinding tools, while with an opposite inclination (+ ⁇ ) the flow of material accelerates and the duration of the stay is shortened .
  • Preferred angles ⁇ for this purpose are -5 degrees to +5 degrees with respect to a surface line of the rotor, preferably -3 degrees to +3 degrees.
  • the effective edge at the inlet and / or outlet end of a grinding tool is formed by a third section L 3 with a third radial distance R 3 from the axis of rotation, the first radial distance R 1 of the first section L 1 is greater than the third radial distance R 3 .
  • the third radial distance R 3 of two grinding tools adjacent in the rotor is of different sizes. If a grinding tool leading in the direction of rotation has a third section L 3 with a smaller radial distance R 3 compared to the radial distance R 3 of a third section L 3 of a subsequent grinding tool, a larger proportion of the feed material will strike the subsequent grinding tool and be comminuted there. In this way, the flow of material and the intensity of the comminution can be controlled.
  • the 1 to 3 show a first embodiment of a device 1 according to the invention in the form of an eddy current mill, which is used without limitation for fine and very fine grinding of plastics such as thermosets, thermoplastics and elastomers or for grinding crystalline substances or agglomerates.
  • the device 1 comprises a platform-like machine substructure 2, which ends at the top with a horizontal mounting plate 3, on which a rotary drive 4 and a support frame 5 are mounted next to one another.
  • a cylindrical housing 6 is fixedly connected to the supporting frame 5, the housing axis of which is oriented perpendicular to the mounting plate 3 and bears the reference number 7.
  • the housing 6 is subdivided in the axial direction into an entry-side housing section 8, a central cylindrical housing section 9 and a discharge-side housing section 10.
  • a rotor 11 with a drive shaft 12 coaxial with the axis 7 is arranged within the housing.
  • the drive shaft 12 is rotatably supported with its lower end section in a lower bearing 13 and with its opposite end section in an upper bearing 14.
  • the end of the drive shaft 12 which extends through the mounting plate 3 carries a multi-grooved pulley 15 which is coupled to the multi-grooved pulley 17 of the rotary drive 4 via drive belts 16.
  • an upper support disk 18 is seated perpendicular to the drive shaft 12 and, at an axial distance from it, a plane-parallel lower support disk 19 which rotate with the drive shaft 12.
  • the support disks 18 and 19 have position slots for receiving axially parallel plate-shaped grinding tools 20, which are distributed in this way in a ring-like manner over the circumference of the rotor 11 and, for example, at a circumferential speed of approximately between 100 m / sec and Can move 180 m / sec depending on the product.
  • the angular spacing of the grinding tools 20 over the circumference of the rotor 11 is uniform and is three degrees in the present exemplary embodiment, but can also be four degrees, five degrees, six degrees or more be.
  • the inlet-side housing section 8 forms the end of the housing end at the bottom and, in the region of the axis 7, has a concentric inlet opening 21 for the feed material, which surrounds the drive shaft 12 at a slight radial distance. Via the axial thickness of the housing section 8 on the entry side, the inlet opening 21 develops into a flat-conical widening, which in this way forms a distributor space 22 with the lower vertical support disk 19, which tapers radially outward and thus accelerates the feed material in this area worries.
  • the outlet-side housing section 10 forms the upper end-side housing closure and houses there an annular channel 23 which is concentric with the axis 7 and which merges into a material outlet 24 which tangentially emerges from the housing section 10.
  • the central cylindrical housing section 9 houses a stator, for which purpose stator tools 35 are arranged on the inner circumference of the housing, which form an impact path in their entirety and which include a grinding gap 36 with the axially running effective edges of the plate-shaped grinding tools 20 of the rotor 11 ( Fig. 3 ).
  • the device 1 is fed with feed material 37 on the inlet side via an inlet channel 38, through which the feed material 37 enters the interior of the housing as a gas-solid mixture via the inlet opening 21 and is accelerated there in the distributor space 22 after deflection in the radial direction towards the grinding gap 36 .
  • the feed 37 flows helically around the axis 7 upwards while it is being comminuted.
  • the sufficiently fine material finally arrives in the annular channel 23, from where it is drawn off from the device according to the invention via the product outlet 24.
  • each grinding tool 20 has an effective edge 25 which runs parallel to the axis 7 and which is opposite the stator tools 35 while maintaining a radial grinding gap 36.
  • Active edge 25 is subdivided into three first sections L 1 , each with a first radial distance R 1 from the axis 7 and two second sections L 2 , each with a second radial distance R 2 from the axis 7.
  • the second radial distance R 2 is smaller than the first radial distance R 1 , there is a radial offset of the effective edge 25 ′′ in the area of the second partial sections L 2 compared to the active edge 25 ′ in the area of the first partial sections L 1 in the direction of the axis 7.
  • the first are Sub-sections L 1 and second sub-sections L 2 are connected to each other via radially effective edges 26.
  • the geometrical relationships are selected such that the sum of the lengths of all axially extending partial sections L 1 makes up approximately 75% of the total axial length L of a grinding tool 20.
  • the ratio of the total lengths of the first sections L 1 to the total lengths of the second sections L 2 is approximately 3: 1.
  • the axial length of a single second section L 2 corresponds to approximately 15% of the total axial length L of a grinding tool 20.
  • the radial length of the edge 26 which is effective in the radial direction is at most half as long as the axial length of the subsequent second section L 2 .
  • the 4a to c show different types of grinding tools 20.1, 20.2, 20.3, which are adjacent in the rotor 11, as they are basically under Fig. 3 are described.
  • the arrangement of these different grinding tools 20.1, 20.2, 20.3 in a rotor 11 with a predetermined recurring sequence is finally in Fig. 4d shown.
  • the grinding tool 20.1 is the leading grinding tool and the grinding tool 20.2 is the subsequent grinding tool.
  • the grinding tools 20.1, 20.2 and 20.3 according to the 4a to 4d it is common that their axially effective edge 25 begins in the inlet-side region with a third section L 3 .
  • the grinding tool 20.2 ends as the only one with a third section L 3 .
  • the axial length of the inlet-side third section L 3 is all Grinding tools 20.1, 20.2 and 20.3 of the same size.
  • the radially effective edge 26.1, 26.2 and 26.3 of the different tool types adjoining this section L 3 has different lengths.
  • the radially effective edge 26.1 of the grinding tool 20.1 has the greatest length and the radially effective edge 26.3 of the grinding tool 20.3 has the smallest length, while the radially effective edge 26.2 has an intermediate length.
  • the radial distance R 3 between the axially extending effective edge 25 ′′ in the third subsection L 3 to the axis of rotation 7 increases in each case from the grinding tool 20.1 or 20.2 to the grinding tool 20.2 or 20.3.
  • the grinding tools 20.1, 20.2 and 20.3 have an axial distance from the inlet-side third section L 3 ( Fig. 4a ) or two ( 4b and 4c ) second sections L 2 , with a second section L 2 of the grinding tool 20.1 or grinding tool 20.2 having an axial offset V with respect to a second section L 2 of the adjacent grinding tool 20.2 or grinding tool 20.3.
  • the radially effective edges 26 of all grinding tools 20.1, 20.2 and 20.3 adjoining the second subsections L 2 all have a uniform length.
  • the further embodiment according to the 5a to 5d differs from that among the 4a to 4d described only by the higher number of second subsections L 2 . This also increases the number and density of the radially active edges 26, so that such a grinding tool 20.1, 20.2, 20.3 is able to grind the feed material more intensively. To avoid repetitions, this applies to the 4a to 4d According to meaning.
  • Fig. 6 represents a settlement of the in Fig. 4d shown circumferential section of the rotor 11. Again one sees a recurring sequence of the grinding tools 20.1, 20.2 and 20.3 in the circumferential direction. Two adjacent grinding tools 20.1, 20.2, 20.3 each form an axially flow-through chamber in which the feed material arrives from the inlet side to the outlet side. The effective edge of all grinding tools is divided from the inlet side to the outlet side into an inlet side third section L 3 , a first section L 1 , a second section L 2 and a first section L 1 .
  • the grinding tools 20.2 also end on the outlet side with a further third section L 3 , the effective edge 25 ′ ′′ of which is aligned with the effective edge 25 ′′, and the grinding tools 20.3 with a further sequence of a second section L 2 and subsequent first section L 1 .
  • the second subsections L 2 of two adjacent grinding elements 20.1, 20.2, 20.3 have a uniform axial offset V in the direction of the outlet side, which results in their arrangement on lines 39 extending helically around the rotor circumference.
  • the lines 39 enclose an angle ⁇ with a surface line 40 of the rotor circumference, which in the present exemplary embodiment is approximately 45 degrees.
  • Fig. 7 is finally an embodiment of a device according to the invention, in which the grinding tools 20 for controlling the residence time of the feed material in the area of the grinding tools 20 are arranged with their effective edge at an angle ⁇ to a surface line 40 of the rotor circumference. If the outlet-side end of the grinding tool 20 is inclined in the direction of rotation R (- ⁇ ), the material particles receive an impulse against the general material flow 41 on impact with the grinding tool 20, which has a restrained effect on the material flow 41. With an opposite inclination (+ ⁇ ), however, the good particles are accelerated in the direction of the good flow 41 upon impact with the grinding tools 20.

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  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Pulverization Processes (AREA)
  • Crushing And Grinding (AREA)
  • Polishing Bodies And Polishing Tools (AREA)

Claims (14)

  1. Dispositif pour le broyage de matériau d'alimentation avec un carter (6) s'étendant le long d'un axe de rotation (7) et dans lequel un rotor (11) est entrainé en rotation autour de l'axe de rotation (7) et présente sur son pourtour une pluralité d'outils de broyage (20; 20.1, 20.2, 20.3) parallèles à l'axe, lesquels sont entourés par un stator équipé d'outils de stator (35), les bords efficaces des outils de broyage (20; 20.1, 20.2, 20.3) étant disposés à un écart radial par rapport aux outils de stator (35) en formant une fente de broyage (36) et s'étendant sur la longueur axiale de la fente de broyage (36), le matériau d'alimentation (37) étant chargé sur le coté entrée de la fente de broyage (36) et déchargé sur le coté sortie de la fente de broyage (36), les bord efficaces (25) des outils de broyage (20; 20.1, 20.2, 20.3) s'étendant axialement étant respectivement subdivisés en direction axiale en au moins deux premières sections partielles L1 avec respectivement un premier écart radial R1 par rapport à l'axe de rotation (7) et en au moins une deuxième section partielle L2 avec un deuxième écart radial R2 par rapport à l'axe de rotation (7), la deuxième section partielle L2 avec un deuxième écart radial R2 par rapport à l'axe de rotation (7), la deuxième section partielle L2 étant située entre les au moins deux premières sections partielles L1 et le premier écart radial R1 étant plus grand que le deuxième écart radial R2 et les bords efficaces (25') s'étendant axialement d'au moins les deux premières sections partielles L1 et le bord efficace (25") s'étendant axialement d'au moins une deuxième section partielle L2 sont reliées entre elles par des bords (26) s'étendant en travers ou essentiellement radialement, caractérisé en ce que les deuxièmes sections partielles L2 d'un outil de broyage (20.1, 20.2, 20.3) présentent un décalage axial V par rapport aux deuxièmes sections partielles L2 d'un outil de broyage (20.1, 20.2, 20.3) adjacent dans le rotor (11).
  2. Dispositif selon la revendication 1, caractérisé en ce que la somme des longueurs de toutes les premières sections partielles L1 correspond à 50 % à 90 % de la longueur axiale totale L d'un outil de broyage (20; 20.1, 20.2, 20.3), de préférence à 60 % à 80 %.
  3. Dispositif selon la revendication 1 ou 2, caractérisé en ce que la somme de toutes les longueurs des premières sections partielles L1 et la somme de toutes les longueurs des deuxièmes sections partielles L2 ont un rapport de 5:1 à 1:1.
  4. Dispositif selon l'une des revendications 1 à 3, caractérisé en ce que la longueur axiale d'une seule deuxième section partielle L2 est de 10 % à 50 % de la longueur axiale totale L d'un outil de broyage (20; 20.1, 20.2, 20.3), de préférence de 20 % à 40 %.
  5. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce que la longueur radiale du bord efficace (26) s'étendant en direction radiale est au maximum aussi grande que la longueur axiale de la deuxième section partielle L2 adjacente, de préférence de 30% à 60% de la longueur axiale de la deuxième section partielle L2 adjacente.
  6. Dispositif selon l'une des revendications 1 à 5, caractérisé en ce que la longueur radiale du bord efficace (26) s'étendant en direction radiale est d'au moins 5 mm, de préférence d'au moins 8 mm, d'au moins 10 mm, d'au moins 15 mm ou d'au moins 20 mm.
  7. Dispositif selon l'une des revendications 1 à 6, caractérisé en ce que la longueur axiale L2 d'une deuxième section partielle L2 de deux outils de broyage (20.1, 20.2, 20.3) (11) adjacents dans le rotor (11) décroît ou croît.
  8. Dispositif selon l'une des revendications 1 à 7, caractérisé en ce que le deuxième écart radial R2 entre deux outils de broyage (20.1, 20.2, 20.3) adjacents dans le rotor (11) décroît ou croît.
  9. Dispositif selon l'une des revendications 1 à 8, caractérisé en ce qu'un outil de broyage (20; 20.1, 20.2, 20.3) ne présente sur sa longueur qu'au plus huit deuxièmes sections partielles L2, de préférence deux à quatre deuxièmes sections partielles L2.
  10. Dispositif selon l'une des revendications 1 à 9, caractérisé en ce que le bord efficace (25) présente sur l'extrémité coté entrée et/ou coté sortie d'un outil de broyage (20) une troisième section partielle L3 avec un troisième écart radial R3 par rapport à l'axe de rotation (7), le premier écart radial R1 étant plus grand que le troisième écart radial R3.
  11. Dispositif selon la revendication 10, caractérisé en ce que le troisième écart radial R3 de deux outils de broyage (20.1, 20.2, 20.3) adjacents en direction de rotation dans le rotor (11) décroît ou croît.
  12. Dispositif selon l'une des revendications 1 à 11, caractérisé en ce que décalage axial V correspond au moins à la somme de 50% de la longueur axiale de la deuxième section partielle L2 d'un outil de broyage (20; 20.1, 20.2, 20.3) précédant en direction de rotation et de 50 % de la longueur axiale de la deuxième section partielle L2 d'un outil de broyage (20; 20.1, 20.2, 20.3) succédant, de préférence à la somme de la longueur axiale de la deuxième section partielle L2 de l'outil de broyage (20; 20.1, 20.2, 20.3) précédant et de la longueur axiale de la deuxième section partielle L2 de l'outil de broyage (20; 20.1, 20.2, 20.3) succédant.
  13. Dispositif selon l'une des revendications 1 à 12, caractérisé en ce que par le décalage V des sections partielles L2 de deux outils de broyage (20; 20.1, 20.2, 20.3) adjacents dans le rotor (11) une voie de forme hélicoïdale est définie qui forme avec la génératrice du rotor un angle ε, l'angle ε étant de préférence de 10 degrés à 50 degrés, de préférence ultime de 20 degrés à 35 degrés.
  14. Dispositif selon l'une des revendications 1 à 13, caractérisé en ce que les bords efficaces des outils de broyage forment avec la génitrice du rotor un angle β, l'angle β étant de préférence de +5 degrés à-5 degrés, de préférence ultime de +3 degrés à -3 degrés.
EP16174479.2A 2015-06-15 2016-06-14 Dispositif et outil de broyage de materiaux de chargement Active EP3106228B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL16174479T PL3106228T3 (pl) 2015-06-15 2016-06-14 Urządzenie i narzędzie mielące do rozdrabniania materiału wsadowego

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015007435.0A DE102015007435A1 (de) 2015-06-15 2015-06-15 Vorrichtung und Mahlwerkzeug zum Zerkleinern von Aufgabegut

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EP3106228B1 true EP3106228B1 (fr) 2020-07-22

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US (1) US10625267B2 (fr)
EP (1) EP3106228B1 (fr)
CN (1) CN106238145B (fr)
CA (1) CA2933068C (fr)
DE (1) DE102015007435A1 (fr)
ES (1) ES2826773T3 (fr)
PL (1) PL3106228T3 (fr)
TW (1) TW201703860A (fr)

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CN107930772B (zh) * 2017-11-17 2019-10-18 乐山新天源太阳能科技有限公司 硅料打散回收系统

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US3556420A (en) * 1967-05-08 1971-01-19 New Life Foundation Apparatus for comminuting compost
DE3543370A1 (de) 1985-12-07 1987-06-11 Jackering Altenburger Masch Muehle mit mehreren mahlstufen
US5110059A (en) * 1989-11-30 1992-05-05 Titmas James A Solid waste shredder
DE4419510B4 (de) * 1994-06-03 2008-07-03 Hosokawa Alpine Ag Schläger für Prallmühlen
JP3060398B2 (ja) * 1994-08-08 2000-07-10 ホソカワミクロン株式会社 微粉砕装置
DE19723705C1 (de) 1997-06-06 1999-01-28 Pallmann Kg Maschf Mühle zum schonenden Feinstvermahlen von Produkten unterschiedlicher Herkunft
US6431477B1 (en) * 1998-10-20 2002-08-13 Pallmann Maschinenfabrik Gmbh & Co. Kg Gas flow-type chipping machine
AU2003271483A1 (en) * 2002-10-15 2004-05-04 Medic Tools Ag Disposable mixer and homogeniser
WO2005089948A1 (fr) * 2004-03-23 2005-09-29 Fumao Yang Broyeur a turbulence elevee et sa turbine a pression bi-negative
CN104549647A (zh) * 2013-10-28 2015-04-29 杨松科 一种双转子立轴式破碎机

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US10625267B2 (en) 2020-04-21
CA2933068C (fr) 2018-07-31
ES2826773T3 (es) 2021-05-19
CN106238145A (zh) 2016-12-21
EP3106228A1 (fr) 2016-12-21
DE102015007435A1 (de) 2016-12-15
CN106238145B (zh) 2019-06-14
PL3106228T3 (pl) 2021-04-06
TW201703860A (zh) 2017-02-01
US20160367996A1 (en) 2016-12-22
CA2933068A1 (fr) 2016-12-15

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