EP2926907B1 - Rotor - Google Patents

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Publication number
EP2926907B1
EP2926907B1 EP14192208.8A EP14192208A EP2926907B1 EP 2926907 B1 EP2926907 B1 EP 2926907B1 EP 14192208 A EP14192208 A EP 14192208A EP 2926907 B1 EP2926907 B1 EP 2926907B1
Authority
EP
European Patent Office
Prior art keywords
rotor
blow
protective cap
shell
elements
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
EP14192208.8A
Other languages
German (de)
English (en)
Other versions
EP2926907A1 (fr
EP2926907C0 (fr
Inventor
Erich Schönenberg
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.)
Craco GmbH
Original Assignee
Craco 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
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Publication of EP2926907A1 publication Critical patent/EP2926907A1/fr
Application granted granted Critical
Publication of EP2926907C0 publication Critical patent/EP2926907C0/fr
Publication of EP2926907B1 publication Critical patent/EP2926907B1/fr
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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
    • B02C13/26—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
    • B02C13/02—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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C2210/00—Codes relating to different types of disintegrating devices
    • B02C2210/02—Features for generally used wear parts on beaters, knives, rollers, anvils, linings and the like

Definitions

  • the invention relates to a rotor for a shredding machine, the rotor being formed from a rotor shaft with support disks arranged at a distance in the axial direction of the rotor shaft, impact tools mounted so as to be rotatable between support disks of the rotor, and protective caps, with the protective caps being fastened on or between support disks, with a a plurality of protective caps arranged radially or between the support disks, a cylindrical casing of the rotor is formed with openings for the striking tools, the casing forming striking edges, the protective cap having a striking edge, the striking edge being formed by at least one striking bar, the protective cap having a striking bar receptacle forms, wherein the blow bar is attached to the blow bar receptacle in a form-fitting and interchangeable manner.
  • Shredding machines are known from the prior art which, among other things, have a rotor consisting of discs. Such crushing machines are also referred to as so-called hammer crushers, since between the disks or support disks are rotatable Impact tools or hammers are stored, by means of which a crushing of, for example, metal scrap, plastic waste, wood waste or similar fractions can be done. Since the outer surfaces of the discs can suffer considerable damage or wear as a result of the impact of material during comminution, it is known to provide the discs with a protective agent. The protective means can extend over a length of the rotor and thus form a wear-resistant, cylindrical shell for the disks of the rotor.
  • the protective means are regularly designed as so-called protective caps and, like the hammers of the rotor, are subject to wear, although they are not actively involved in the comminution process.
  • the protective caps are therefore also referred to as inactive wearing parts.
  • the protective caps are fastened together with the hammers, which are also referred to as active wearing parts, on an axis which is guided through the disks or support disks, so that the hammers can swing freely and the protective caps essentially completely cover the spaces between the hammers fill out.
  • the protective caps and the hammers can be exchanged or exchanged in the event of advanced wear.
  • the basic structure of such a rotor of a crushing machine is, for example, from DE 2 605 751 A1 known.
  • Protective caps which are not designed in one piece as cast protective caps, but in several parts.
  • a partial lateral surface of these protective caps is formed from a bent and hardened steel sheet, to which a connecting plate made of construction steel is welded on the inside and in which a hub for attachment to an axle is formed.
  • a comparatively hard surface of the protective cap that is protected against wear and a comparatively tough and soft suspension of the same can also be formed.
  • a disadvantage of such protective caps is that the sheet steel used can exhibit segregation caused by a manufacturing process of the sheet steel. Bending the steel sheet results in tensile and compressive stresses within the steel sheet, which can cause flexural cracks. As has also been shown in practice, cracks on the protective caps also tend to occur in the area of segregation of the steel sheet, in particular under the influence of tensile and compressive stresses during bending. These cracks then cause premature failure or wear of the protective caps.
  • a rotor of a comminution machine which has support disks with hammers mounted so as to be rotatable between the support disks. Furthermore, protective caps are arranged on the support disks, which form a jacket of the rotor and also have impact edges. In particular, the beating edges serve to convey feed material away from the shell of the rotor in the direction of the hammers.
  • the FR 2 635 022 A1 describes a rotor formed from a rotor shaft with support disks and between the support disks rotatably mounted hammers or striking tools.
  • a casing of the rotor is formed from protective caps, the protective caps being fastened via screws to a spacer element arranged between the support disks.
  • a blow bar is arranged on a front edge of the protective caps in the direction of rotation of the rotor and protrudes a little beyond the casing of the rotor in the radial direction. This blow bar is attached to the protective cap with two screws and nuts.
  • the present invention is therefore based on the object of proposing a rotor for a comminution machine which has a long service life.
  • the rotor for a crusher according to the invention, consists of a rotor shaft with the rotor shaft in the axial direction spaced-apart support disks, between the support disks of the rotor rotatably mounted striking tools and protective caps, with the protective caps being fastened on or between the supporting disks, with a plurality of protective caps arranged radially on or between the supporting disks forming a cylindrical shell of the rotor with openings for the striking tools is, the casing forming impact edges, the casing forming impact edges, the protective cap having an impact edge, the impact edge being formed by at least one blow bar, the protective cap forming a blow bar receptacle, the blow bar being fastened to the blow bar receptacle in a form-fitting and interchangeable manner, the blow bar receptacle being formed from two profile elements which are arranged between wear elements, the profile elements forming a receiving groove for the blow bar.
  • the feed material can firstly be coarsely crushed by means of the impact tools or hammers of the rotor, with the coarsely crushed feed material being able to be crushed more finely at the same time by means of the beating edges.
  • the finer comminution results on the one hand from a beating effect of the beating edges on the feed material and on the other hand from an impact effect of the beating edges.
  • the feed material is thus conveyed away from the shell of the rotor into a crushing chamber. In contrast to an exclusively circular shell, the feed material cannot slide along the shell and cause abrasive wear when the rotor rotates. A concentration of feed material directly on the shell is therefore prevented.
  • a rotor of this type can be used more universally, since coarse-sized feed material that has not been pre-comminuted can also be comparatively finely comminuted with the rotor.
  • the impact edge is formed by at least one impact bar.
  • the blow bar can then be a strip-shaped component or element. It is basically irrelevant whether the blow bar runs as one element over the entire casing of the rotor or just over a protective cap.
  • a plurality of protective caps can each have blow bars. A blow bar can protrude beyond the casing or a protective cap in a comminution space, so that the blow bar can come into direct contact with the feed material when the rotor rotates.
  • the protective cap forms a blow bar receptacle, the blow bar being fastened to the blow bar receptacle in a form-fitting and exchangeable manner. Since the blow bar is exposed to particularly high stress due to its exposed position on the shell, the blow bar can then also be easily replaced in accordance with wear and tear of the blow bar. Depending on the design of the form-fitting attachment of the blow bar to the protective cap, it may not even be necessary to disassemble the protective cap from the rotor, but the respective worn blow bars can be dismantled from the rotor on their own.
  • the blow bar receptacle is formed from two profile elements, with the profile elements being arranged between or on the wear elements, with the profile elements forming a receiving groove for the blow bar.
  • the design of the receiving groove is particularly advantageous since the blow bar can then be at least partially inserted into the receiving groove and fastened in it.
  • the receiving groove is easy to produce, for example, by arranging the profile elements parallel to one another at a distance from one another. If the profile elements are arranged between the wear elements, the profile elements can also form a surface section of the jacket. Furthermore, a particularly stable fastening of the profile elements can result from the arrangement between the wear elements result. For example, the profile elements can be welded to the wear elements.
  • blow bars can be distributed over the jacket at regular, radial intervals. This ensures that the rotor runs evenly.
  • the blow bars can be designed to run over the casing in the axial direction.
  • the blow bars can run continuously over the jacket axis-parallel to an axis of rotation of the rotor or can also be interrupted in sections by impact tools.
  • the blow bars can be arranged offset relative to one another in the radial and axial direction on the jacket or can also run helically over the jacket.
  • the blow bars can advantageously form a V-shaped pattern on the shell, so that the feed material can be concentrated in a central area of the shell.
  • the blow bars can be designed in such a way that an averaged outer diameter of the casing can project radially beyond the blow bars.
  • the protective caps forming the jacket consequently protrude beyond the average outer diameter of the jacket with their impact strips. In this way it can be ensured that no feed material can concentrate directly on the shell during operation of a rotor, since the feed material constantly bounces off the blow bars and is conveyed in the direction of, for example, hammers.
  • the blow bar can consist of a cast material, fine-grain construction steel or a ceramic insert, with the blow bar having a hardness of 350 to 550 Brinell (HB).
  • the impact bar can also have a hardness of 430 to 550 Brinell.
  • the hardness of the blow bar or the material can be selected so that the blow bar is adapted to the respective feed material.
  • the protective cap can be formed from a plurality of elements joined together.
  • the elements can preferably be joined by welding, although other suitable joining techniques can also be provided. It is then also possible to form the elements from materials that are most suitable for determining the elements.
  • the protective caps can form an essentially closed jacket, which is broken through by the openings for the impact tools or hammers.
  • the protective caps can be distributed over the jacket in the axial and also in the radial direction in relation to the rotor and can form this by means of partial jacket surfaces in the form of segments.
  • the segment-shaped partial lateral surfaces can be of different size or shape.
  • Impact tools also do not necessarily have to be arranged between all the support disks of the rotor. It is essential, however, that the partial lateral surface of the protective cap or the respective protective caps of the rotor can be formed from at least two flat surface sections.
  • the protective cap can then also be produced in a particularly cost-effective manner, since the time-consuming bending of a comparatively thick steel sheet, which involves the use of a machine, can be completely dispensed with. In this way it is also possible to achieve considerable cost savings in the production of the protective cap and to extend the service life of the protective cap.
  • the protective cap can also form more than two flat surface sections. It is essential that the entire lateral surface area of the protective cap can be composed almost completely or predominantly of flat surface sections.
  • the surface sections are each formed from a plate-shaped or straight-shaped wearing element.
  • the plate-shaped wearing element can be produced particularly easily from a steel sheet by cutting.
  • the plate-shaped wearing element can also be subjected to a temperature treatment, such as annealing, hardening and/or tempering. A possible deformation of the plate-shaped wearing elements as a result of the temperature treatment is not important here, in contrast to curved wearing elements.
  • the surface sections can preferably be arranged in such a way that surface normals of the surface sections run at an angle ⁇ relative to one another.
  • the angle ⁇ can be an acute angle deviating from 0°. It is then also possible to form a rotor from a plurality of protective caps, which rotor forms a comparatively round cross section.
  • the angle ⁇ can be defined or determined by 360° divided by the number of surface sections based on a circumference of the jacket.
  • the angle ⁇ can then consequently be the same for all protective caps forming the jacket.
  • the surface sections can then also each have the same radial length in relation to the circumference of the jacket. As a result, the flat surface sections can be produced even more easily.
  • the protective cap can be designed in such a way that surface normals of the surface sections can intersect in an axis of rotation of the rotor. In this way, a possible imbalance of the rotor can be prevented, with the casing of the rotor being able to be brought even closer to a circular shape.
  • a longitudinal groove can be formed in the blow bar, into which a projection engages within the receiving groove. Accordingly, a form-fitting reception or attachment of the blow bar can be particularly simple can be realized in the receiving groove.
  • the blow bar can then also be easily pushed into the longitudinal groove.
  • the projection within the receiving groove then reliably prevents the blow bar from falling out of the receiving groove in the radial direction.
  • the projection can be designed, for example, in the manner of a lug, in which case the lug can then engage in the longitudinal groove, which has a matching shape.
  • a build-up coating can be formed on the profile elements and at least partially on the surface sections of the wear elements adjoining the profile elements.
  • Such an application coating can consist of a wear-reducing, suitable coating material.
  • the application coating can also be formed by welding material onto the profile elements and the adjoining surface sections.
  • the protective cap can preferably form a fastening web with a hub for fastening the protective cap to or between support disks.
  • the fastening web can then be arranged in the radial direction relative to a surface section at right angles to this. If the rotor has axles that are pushed through openings in the support discs or if the support discs themselves form axles or projections, the protective cap can be easily placed with the hub on an axle and thus securely fastened.
  • wear elements are directly welded to one another.
  • a completely closed partial lateral surface can thus be formed for a protective cap. If the protective cap is made up of several elements, all of the elements can be welded to one another.
  • the impact edge can be formed particularly easily by a weld seam of the wear elements.
  • the weld can be opposite the material of the surface sections have a comparatively high hardness. Since the impact edge is expected to be more heavily stressed than the surface sections, premature wear of the impact edge can be avoided.
  • the wear elements can further have a hardness of 350 to 550 Brinell (HB).
  • HB Brinell
  • the hardness can be 430 to 550 Brinell. It can thus be ensured that the wear elements or the surface sections of the protective cap formed by the wear elements are sufficiently resistant to damage and wear.
  • the wear elements can be made particularly wear-resistant and yet inexpensive if they are made of fine-grain structural steel. Fine-grain structural steel is also particularly well suited to heat treatment to achieve a desired hardness.
  • the protective cap can have support elements, wherein the support elements can be arranged on a support side of the wear elements facing away from the partial lateral surface, such that the protective cap can be adapted to a shape of the support disks.
  • the support discs have a round or circular outer contour
  • the protective caps can then be adapted to the respective outer contour of the support discs by means of the support elements in such a way that the protective caps rest at least at two points on the support discs or their outer contour.
  • the protective caps can then be supported on the support disks by means of the support elements, and tilting of the protective caps or an undesired movement relative to the support disks can also be easily avoided. Provision can preferably be made to use three support elements for mounting a protective cap on an outer contour of a support disk. However, the protective cap can also rest against the support disks at other points of the protective cap where no support elements are arranged.
  • a fastening web of the protective cap can be formed from a connecting plate for the wear elements, with the connecting plate also being able to be reinforced with reinforcing plates. Consequently, the wearing elements can be connected to one another via the fastening bar, whereby the wearing elements can be welded to the fastening bar or the connecting plate.
  • the reinforcing plates can be arranged on both sides of the connecting plate and also connected or joined to both wearing elements. In this way it is also possible to realize a particularly good attachment of the protective cap to, for example, an axle of a rotor, since the axle can be passed through a through-opening in the connecting plate and the reinforcement plates.
  • the shell of the rotor can be polygonal in the radial direction, based on a cross section of the rotor.
  • the polygonal shape of the mantle can be further approximated to a circular shape.
  • the polygonal shape of the shell is selected depending on the type of feed material.
  • the jacket can have at least six protective caps in the radial direction, based on a cross section of the rotor.
  • the shell can be formed in the cross section of twelve straight surface sections.
  • the comminution machine according to the invention comprises a rotor according to the invention.
  • Advantageous embodiments of a comminution machine result from the dependent claims referring back to the device claim 1 .
  • the 1 shows a rotor 10 in a cross-sectional view.
  • the rotor 10 is arranged in a crushing machine, not shown here, and is formed from a rotor shaft 11, support disks 12 and impact tools 14 designed as a hammer 13.
  • the rotor 10 also includes protective caps 15 which form a cylindrical casing 16 of the rotor 10, with openings 17 for the hammers 13 being provided in the casing 16.
  • the protective caps 15 and the hammers 13 are fastened to axles 18 which are inserted into through-holes 19 in the support discs 12 and connect the further support discs, not shown here, to one another. Consequently, the protective caps 15 and the hammers 13 are fixed to the axles 18 between the supporting discs 12 .
  • the protective caps 15 lie on the support disks 12, the hammers 13 being mounted so that they can rotate freely and can swing through.
  • the rotor 10 can be rotated in a direction of rotation indicated by an arrow 20 .
  • feed material 22 to be crushed which can ricochet off a lateral surface 23 of the jacket 16 and reach an effective range of the hammers 13.
  • the protective caps 15 form a partial lateral surface 24 of the lateral surface 23 with two flat surface sections 25 .
  • the surface sections 25 are each formed from a plate-shaped wear element 26, the wear elements 26 being directly connected by means of a weld seam 27 are joined together.
  • the weld seam 27 here forms an impact edge 28 of the protective cap 15 or of the rotor 10 .
  • the 2 shows a protective cap 29 for a rotor with polygonal support disks, not shown in detail here, the protective cap 29 being formed from two plate-shaped wear elements 30 , a connecting plate 31 and reinforcing elements 32 .
  • the connecting plate 31 and the reinforcing plates 32 form a fastening web 33 with a through-opening 34 for an axle 35, shown here in outline, for fastening the protective cap 29 to the rotor.
  • the connecting plate 31, the reinforcement plates 32 and the wear elements 30 are connected to one another completely by means of welded joints, with the wear elements 30 in particular being connected directly to one another with a weld seam 36.
  • a wear material 37 is additionally applied to the weld seam 36 and forms an impact edge 38 .
  • the wearing elements 30 are connected to one another via the connecting plate 31 and the reinforcing plates 32 .
  • the connecting plate 31 and the reinforcing plates 32 or the fastening web 33 can be inserted in a gap (not shown) between two support disks of a rotor, with the wear elements 30 then resting with a contact side 39 on the respective support disks.
  • FIG. 1 shows a protective cap 40 which has wear elements 41 and a fastening web 42 for fastening to an axle 43.
  • the wear elements 41 are also connected directly via a weld seam 44 to an application of wear material 45 .
  • the protective cap 40 further comprises support elements 47 and 48 arranged on a support side 46 of the wear elements 41.
  • the support elements 47 are each arranged on radial ends 49 of the protective cap 40, the support elements 48 being arranged in the region of the weld seam 44.
  • the support elements 47 and 48 form concave support surfaces 50 or 51 for resting the protective cap 40 on a circular support disk, not shown here.
  • the 4 shows a detailed view of the rotor 10 from 1 here the protective cap 15 with the wear elements 26 are also supported on the support disk 12 via support elements 52 and 53 .
  • a surface normal 54 of the wear element 26 runs at an angle ⁇ /2 relative to a plane of symmetry 55 of the protective cap 15 .
  • the protective cap 15 rests on an outer circumference 58 of the support disk 12 via bearing surfaces 56 and 57 of the bearing elements 52 and 53 .
  • direct support points 59 are formed by contact of a support side 60 of the wear elements 26 with the outer circumference 58.
  • the protective cap 15 is spaced apart from the adjacent protective cap 15 by a gap 61 .
  • the figure 5 shows a basic sketch of a rotor 62 with a protective cap 63 and a support disk 64.
  • the dimension of a distance X results from a radius r of the support disk 64 divided by cos ⁇ - r.
  • the angle ⁇ is defined by a surface normal 65 of a surface section 66 of the protective cap 63 and a tangent 67 of the protective cap 63 , the tangent 67 and the surface normal 65 intersecting in an axis of rotation 68 of the rotor 62 .
  • the 6 shows a rotor 69 which, in contrast to the rotor 1 Has protective caps 70 with a blow bar 71.
  • the impact bars 71 protrude into a crushing chamber 72, so that the feed material 73 can bounce off the impact bar 71, as is indicated here, and can be crushed by impact.
  • the 7 shows a rotor 74 with protective caps 75, shown schematically here, and in particular support disks 76, which are polygonal in shape.
  • An outer contour 77 of the support disks 76 is adapted to a support side 78 of the protective cap 75 in such a way that the support side 78 rests completely against the outer contour 77 without any support elements would be required.
  • a casing 79 of the rotor 74 is formed by six protective caps 75 in relation to the cross section shown here.
  • the 8 shows a protective cap 80 which has two wear elements 81 and a fastening web 82 connecting the wear elements 81 .
  • the wear elements 81 are each spaced far enough from one another that profile elements 83 and 84 are arranged between the wear elements 81 and form a blow bar receptacle 85 in the form of a longitudinal groove 86 for a blow bar 87 .
  • the profile element 84 has a nose 88 which runs along the profile element 84 and which engages in a correspondingly designed groove 89 in the blow bar 87 .
  • An application coating 90 is also provided, which completely covers the profile elements 83 and 84 and at least partially covers the wear elements 81 .
  • the 9 shows a protective cap 91 which, like that in 8 described protective cap is designed, but like that in 3 protective cap described has support elements 92 and 93 .
  • the Figures 10 and 11 show a blow bar 94 and profile elements 95 and 96, each in enlarged side views.
  • the impact bar 94 has a groove 97 into which a nose 98 of the profile element 96 can engage.
  • the blow bar 94 is essentially rectangular and consists of fine-grain construction steel with a hardness of up to 550 Brinell.
  • the profile elements 95 and 96 are each directly welded to a support element 99 and wear elements 100 .
  • the profile elements 95 and 96 are spaced apart from one another to such an extent that a blow bar receptacle 101 is formed between the profile elements 95 and 96, into which the blow bar 94 can be pushed laterally.
  • the blow bar 94 is fixed in a form-fitting manner by the groove 97 and the lug 98 in the blow bar receptacle 101.
  • An applied coating 102 is also formed.
  • the 12 Figure 12 shows an enlarged view of the rotor 6 , where it can be seen that a surface normal 103 of wear elements 104 forms an angle ⁇ /2 to a plane of symmetry 105 of the protective cap 70 .
  • the surface normal 103 and the plane of symmetry 105 intersect with a rotation axis 106 of the rotor 69.
  • the angle ⁇ is chosen so that the impact bar 71 protrudes far into the crushing space 72, which can also be seen from the different heights of support elements 107 and 108 of the protective cap .
  • outer ends 109 of the protective cap 70 are designed to be less exposed and flattened with respect to the feed material 73 .
  • the 13 shows a basic representation of a rotor 110 with a protective cap 111 analogous to the representation of the rotor in FIG figure 5 .

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

Claims (13)

  1. Rotor (69, 74, 110) pour une machine de concassage, le rotor se composant d'un arbre de rotor (11) ayant des disques de support (76) espacés dans la direction axiale de l'arbre de rotor, des outils à percussion montés rotativement entre les disques de support du rotor et des capots de protection (70, 75, 80, 91, 111), les capots de protection étant fixés sur ou entre des disques de support, une enveloppe (79) du rotor en forme de cylindre avec des ouvertures pour les outils à percussion étant formée par une pluralité de capots de protection disposés radialement sur ou entre les disques de support, l'enveloppe formant des bords de percussion, le capot de protection ayant un bord de percussion, le bord de percussion étant formé par au moins un battoir (71, 87, 94), le capot de protection formant un logement de battoir (85, 101), le battoir étant monté sur le logement de battoir par liaison par forme et de manière échangeable,
    caractérisé en ce que
    le logement de battoir (85, 101) se compose de deux éléments profilés (83, 84, 95, 96) disposés entre ou sur des éléments d'usure (81, 100, 104), les éléments profilés formant une rainure de logement (86) pour le battoir (71, 87, 94).
  2. Rotor selon la revendication 1,
    caractérisé en ce que
    les battoirs (71, 87, 94) sont distribués sur l'enveloppe (79) à intervalles radiaux réguliers.
  3. Rotor selon la revendication 1 ou 2,
    caractérisé en ce que
    les battoirs (71, 87, 94) s'étendent sur l'enveloppe (79) dans la direction axiale.
  4. Rotor selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    les battoirs (71, 87, 94) dépassent radialement un diamètre extérieur moyen de l'enveloppe (79).
  5. Rotor selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le battoir (71, 87, 94) consiste en matériau coulé, en acier de construction à grains fins ou un insert en céramique, le battoir ayant une dureté de 350 Brinell à 550 Brinell (HB).
  6. Rotor selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le capot de protection (70, 75, 80, 91, 111) est formé par une pluralité d'éléments joints.
  7. Rotor selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le capot de protection (70, 75, 80, 91, 111) forme une surface d'enveloppe partielle d'une surface de l'enveloppe (79), la surface d'enveloppe partielle du capot de protection étant formée par au moins deux parties de surface plates.
  8. Rotor selon la revendication 7,
    caractérisé en ce que
    les parties de surface sont formées chacune par un élément d'usure (81, 100, 104) en forme de plaque.
  9. Rotor selon la revendication 7 ou 8,
    caractérisé en ce que
    les parties de surface sont disposées de telle manière que des normales de surface (103) des parties de surface forment un angle α l'une par rapport à l'autre.
  10. Rotor selon l'une quelconque des revendications précédentes,
    caractérisé en ce
    qu'une rainure longitudinale (89, 97) est formée dans le battoir (71, 87, 94), une saillie (88, 98) à l'intérieur de la rainure de logement (86) venant en prise dans ladite rainure longitudinale.
  11. Rotor selon la revendication 10,
    caractérisé en ce
    qu'un revêtement (90, 102) est formé sur les éléments profilés (83, 84, 95, 96) et au moins partiellement sur les parties de surface des éléments d'usure (81, 100, 104) adjacentes aux éléments profilés.
  12. Rotor selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    l'enveloppe (79) est polygonale dans la direction radiale.
  13. Machine de concassage comprenant un rotor (69, 74, 110) selon l'une quelconque des revendications précédentes.
EP14192208.8A 2014-04-04 2014-11-07 Rotor Active EP2926907B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014206555 2014-04-04

Publications (3)

Publication Number Publication Date
EP2926907A1 EP2926907A1 (fr) 2015-10-07
EP2926907C0 EP2926907C0 (fr) 2023-07-05
EP2926907B1 true EP2926907B1 (fr) 2023-07-05

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DE102014216452B4 (de) * 2014-04-04 2018-03-01 Craco Gmbh Zerkleinerungsmaschine

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FR2635022A1 (fr) * 1988-08-03 1990-02-09 Becker Arnaud Broyeur a ferrailles, notamment a ferrailles d'incineration

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GB1474005A (en) 1975-03-17 1977-05-18 Lindemann Maschfab Gmbh Hammer breakers
CH663162A5 (de) * 1984-09-06 1987-11-30 Thyssen Industrie Hammerbrechrotor.
FR2660213B1 (fr) * 1990-03-30 1993-03-19 Becker Arnaud Broyeur a marteaux, a alimentation centrale, pour le dechiquetage d'objets metalliques.
DE4343801A1 (de) 1993-12-22 1995-06-29 Lindemann Maschfab Gmbh Zerkleinerungsmaschine mit Rotor
DE9319599U1 (de) * 1993-12-22 1994-02-10 Lindemann Maschinenfabrik GmbH, 40231 Düsseldorf Zerkleinerungsmaschine mit Rotor
DE102005020441A1 (de) * 2005-04-29 2006-11-02 Silver Cay Worldwide Corp. Vorrichtung und Verfahren zum Behandeln von Verbundelementen
ITUD20080152A1 (it) * 2008-06-26 2009-12-27 Danieli Davy Distington Ltd Dispositivo di triturazione per un impianto di triturazione

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Publication number Priority date Publication date Assignee Title
FR2635022A1 (fr) * 1988-08-03 1990-02-09 Becker Arnaud Broyeur a ferrailles, notamment a ferrailles d'incineration

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EP2926907C0 (fr) 2023-07-05
ES2957793T3 (es) 2024-01-25

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