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EP0022537B1 - Machine pour le broyage d'objets encombrants - Google Patents

Machine pour le broyage d'objets encombrants Download PDF

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Publication number
EP0022537B1
EP0022537B1 EP80103867A EP80103867A EP0022537B1 EP 0022537 B1 EP0022537 B1 EP 0022537B1 EP 80103867 A EP80103867 A EP 80103867A EP 80103867 A EP80103867 A EP 80103867A EP 0022537 B1 EP0022537 B1 EP 0022537B1
Authority
EP
European Patent Office
Prior art keywords
rotor
cutting edges
machine
stator
rotation
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.)
Expired
Application number
EP80103867A
Other languages
German (de)
English (en)
Other versions
EP0022537A1 (fr
Inventor
Kurt Rössler
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.)
Osnabruecker Metallwerke J Kampschulte & Co KG GmbH
OSNABRUCKER METALLWERKE J KAMPSCHULTE GmbH and Co KG
Original Assignee
Osnabruecker Metallwerke J Kampschulte & Co KG GmbH
OSNABRUCKER METALLWERKE J KAMPSCHULTE GmbH and Co KG
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 Osnabruecker Metallwerke J Kampschulte & Co KG GmbH, OSNABRUCKER METALLWERKE J KAMPSCHULTE GmbH and Co KG filed Critical Osnabruecker Metallwerke J Kampschulte & Co KG GmbH
Priority to AT80103867T priority Critical patent/ATE1569T1/de
Publication of EP0022537A1 publication Critical patent/EP0022537A1/fr
Priority to DE19813125934 priority patent/DE3125934A1/de
Application granted granted Critical
Publication of EP0022537B1 publication Critical patent/EP0022537B1/fr
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C18/00—Disintegrating by knives or other cutting or tearing members which chop material into fragments
    • B02C18/0084—Disintegrating by knives or other cutting or tearing members which chop material into fragments specially adapted for disintegrating garbage, waste or sewage

Definitions

  • the invention relates to a machine for crushing lumpy objects, in particular bulky wood or other waste or bulky waste parts, in an embodiment according to the preamble of claim 1 or claim 2.
  • the cutting edges of the rotor have the same length as one another. Each cutting edge of the rotor runs through one and the same ring work surface for all cutting edges.
  • the cutting edges of the stator which cooperate with the cutting edges of the rotor within one and the same comminution stage, also have the same length and accordingly an overlap with the ring working surface of the rotor cutting edges.
  • the cutting edges can have an inclined position relative to one another for a point-wise progressing cut from inside to outside or from outside to inside. Such alignment of the cutting edges in the known machine, however, only leads to a point-wise progressive severing of an object reaching between two interacting cutting edges if it is relatively soft and therefore easy to cut or approximately leaf-shaped.
  • the invention has for its object to provide a machine of the type mentioned, which crushes the objects to be shredded within one and the same shredding stage in a force-saving manner and with reduced risk of blockages in a plurality of successive partial cutting operations.
  • the machine according to the invention is characterized by the features specified in the characterizing part of claim 1.
  • a second solution to this problem is achieved by the features specified in the characterizing part of claim 2.
  • the machine according to the invention creates, with structurally extremely simple means, an effective comminution of even objects of great bulk and / or material strength, the machine working with considerably reduced drive power as a result of the force distribution on the graded separation processes and with significantly lower loads on the machine components.
  • the machine is particularly reliable and has a longer service life. Downtimes due to blockages are also significantly reduced or eliminated.
  • the machine is made up of an upright jig 1, which can be filled from above and is square in its upper main part, which merges in its lower region into a funnel 2 with a circular funnel wall with a horizontal cross section.
  • the receptacle 1.2 stands on footrests 3.
  • a stationary guide element 4 on the inside of the funnel wall. Furthermore, a transport and primary crusher element 5 rotates within the funnel 2. Under the oem funnel is one with the ones to be chopped up Shredding device 6 to be loaded.
  • the guide member 4 consists of three guide webs 7, 8 and 9 fastened, preferably welded, to the inside of the funnel wall, which can be arranged one behind the other or, as shown, individually spaced apart.
  • Each guide web 7, 8 and 9 has a leg 10 projecting approximately horizontally into the funnel space, the outer edge 11 of which follows the course of the funnel wall, the straight or, if appropriate, slightly inwardly curved inner edge 12 of which connects two funnel wall points 13, 14 approximately in a sinew shape, the underside thereof has a support leg 15 which is oriented approximately parallel to the vertical center axis of the container and which is offset outwards with respect to the inner edge 12 of the leg 10 and which therefore has the general cross-sectional shape of a slightly asymmetrical T.
  • Each guide web 7, 8 or 9 extends with respect to the vertical axis of the container over a central angle, which generally falls below 90 ° C., along the funnel wall and has a more or less sloping profile depending on the type of objects to be crushed. It is understood that the distance, number and arrangement of such guide bars are variable over a wide range.
  • the inner edge 12 forms a leading and at the same time crushing abutment edge, the support leg 15 serving on the one hand for strengthening and on the other hand for preventing parts from jamming in the region between the funnel wall and the leg 10. All edges and boundary lines of the guide bars emerge from the funnel wall and merge into it again.
  • a lower stator 21 of the comminution device 6 is screwed on the underside to a ring fianch body 20 provided at the lower end of the funnel 2 and is connected to the roughly shell-shaped or pot-shaped housing 22 of the comminution device 6 by means of stud bolts (not shown in more detail).
  • the rotor 24 receives its drive by means of a bevel gear 26 on a shaft 27 which is in turn rotatably mounted in the housing 22 and which has a drive wheel 28 firmly connected to it on the outside in the form of a toothed chain wheel, a flat or a V-belt pulley or the like. carries, depending on what drive power is to be transmitted from an electric or internal combustion engine, not shown, via chain or belt to the rotor 24.
  • the rotor 24 On its lateral lateral surface, the rotor 24 carries a horizontal transport ring 29, which is surrounded by an upstanding ring 30 fastened between the ring flange body 20 and the housing 22. This ring 30 delimits on the outside a discharge duct 31 for shredded material, which is closed except for a discharge opening 32.
  • the transport and pre-crushing member 5 is fastened, which in this way rotates driven by the rotor.
  • the transport and pre-crushing element 5 in the machine design according to FIGS. 1 and 2 consists of a horizontal flange plate 51 on which a vertical support axis 52 is fastened.
  • This support shaft 52 has an upper support surface 53, which is inclined approximately according to the inclination of the funnel wall, on which a correspondingly inclined plate 54 is fastened.
  • support webs 55 are attached to the support shaft 52, which extend from the flange plate 51 to the underside of the plate 54 and are welded to the parts 51, 52, 54.
  • the plate 54 is partially provided with step profiles 57, 58 and 59 on the edge. which can vary in size and shape of the steps.
  • step profiles 57, 58 and 59 on the edge. which can vary in size and shape of the steps.
  • the step surfaces 57 ' face away from the direction of rotation, while in the profile 58 the step surfaces 58' and in the profile 59 the step surfaces 59 'point in the direction of rotation.
  • the rotor 24 consists of a rotating body with a cylindrical outer surface 241, from which a collar 242 protrudes to support and fix the transport ring 29 on the underside. While the lateral surface 241 merges into the bevel gear ring 23 at the bottom, a conical surface 243 adjoins at the top, which rises towards the center of the rotor and is delimited on the inside by a central central region 244, the horizontal surface 33 of which is connected to the transport and Primary crushing device 5 is used.
  • the approximately radial boundary edges of the flat surfaces of the ribs 245 form cutting edges 248 of the rotor 24 in its first comminution stage. As usual, they can be formed by separate cutting elements inserted on or in the ribs, which can be replaced when worn.
  • the cutting edges 248 are stepped in length, run in a plane perpendicular to the axis of rotation 25 of the rotor 24 and pass through an imaginary ring work surface, the width of which is determined by the length of the longest cutting edge 248, which is shown in FIG Observer facing front rib 245 is located.
  • the first rib 245 located in the direction of rotation to the right of the central region 244 in FIG. 4 presents cutting edges 248, the length of which corresponds to a fraction of the width of the imaginary ring work surface. Contrary to the direction of rotation, the length of the cutting edges 248 now increases in steps from rib to rib, the number of gradations in the example according to FIG. 4 being ten, but can easily deviate downwards or upwards in a wide range.
  • a plurality of groups of cutting edges graded in length can also be provided on the rotor 24 one behind the other in the direction of rotation.
  • the radially inner end points of the cutting edges 248 all lie on an imaginary inner circular arc, which forms the inner boundary line of the ring work surface and in the illustrated example coincides with the outer circumferential line of the connecting surface 33.
  • a reverse arrangement is also conceivable, in which all outer end points of the cutting edges lie on the outer boundary line of the ring work surface coaxial with the rotor axis of rotation and have a length gradation towards the inside.
  • the rotor 24 On its outer edge, the rotor 24 also has additional cutting edges 247 which are arranged regularly distributed over the circumference and are formed by cams 249 forming a cutting ring. These additional cutting edges 247 lie in a plane which is axially offset downwards from the ring working surface of the cutting edges 248 and is also oriented perpendicular to the rotor axis of rotation 25 and which coincides with the surface of the cams 249 emerging from the conical surface 243.
  • the additional cutting edges 247 which are of equal length to one another, end on the outside on the outer surface 241 of the rotor.
  • FIG. 5 illustrates the upper stator 19 of the machine according to FIGS. 1 and 2, the design of which is matched to the rotor 24 according to FIG. 4.
  • This stator 19 consists of a plate body 190 with an arc-shaped outer edge 191, a spiral arc-shaped inner edge 192 and a straight end edge 193.
  • the plate body 190 On its underside, the plate body 190 carries blocks 194 with cutting edges 195. These blocks are or have correspondingly shaped interchangeable cutting elements on the underside.
  • the plate body 190 of the stator 19 is connected to the funnel 2 using the screw holes 196 on the underside thereof.
  • the stator 19 which is shown obliquely from below in FIG.
  • the cutting edges 195 are also stepped in length, the length of the cutting edges increasing in the direction of rotation shown for the rotor.
  • the cutting edges 195 of the stator 19 overlap to an increasing extent with the ring working surface of the rotor cutting edges 248, the maximum amount of cutting edge length and thus overlap in the block 194 being reproduced from the left in fifth place.
  • the stator 19 has on blocks 197 which are arranged downstream of the block 194 with a greater cutting edge length at a distance in the direction of rotation of the rotor, further cutting edges 198 which decrease in length again in steps. These cutting edges are of particular importance when the direction of rotation of the rotor 24 is reversed, as is desirable shortly after the machine is blocked.
  • the cutting edges 195 protrude radially inward beyond the inner edge 192 of the plate body 190 of the stator 19, while on the other hand the cutting edges 198 project beyond the end edge 193.
  • the lower or second stator 21 comprises a square plate 211, cut off at the corners, with a large central bore 212.
  • the plate 211 is attached to the ring flange body 20 at the lower end of the funnel using fastening bores 213 by means of stud bolts 2 attached.
  • Fig. 6. which shows the stator 21 obliquely from below, the underside of the triangle forms an inner cone 215, from which un project out cam 216 with approximately radial cutting edges 217. These delimit flat surfaces of the cams 216 and run in a plane perpendicular to the axis of rotation 25 of the rotor.
  • the cutting edges 217 of the stator 21 form the counter edges interacting with the additional cutting edges 247 of the rotor 24 in the second comminution stage.
  • FIG. 7 shows a rotor 124 of a modified design, which is formed on the underside up to the cylindrical jacket 121 with collar 122 corresponding to the rotor 24.
  • the conical surface 123 of the rotor 124 is inclined downwards from the outside inwards, i.e. designed as an inner cone.
  • the inner conical surface 123 is delimited by a cylindrical central region 125, the upper side of which, in turn, forms the flat connecting surface 33 for the transport and primary crushing element 5 which is perpendicular to the axis of rotation 25 of the rotor.
  • Radially directed ribs 126 with cutting edges 127 are formed or attached to the cylindrical central region 125, which gradually increase in length from a first, shortest rib 126 in the opposite direction of rotor rotation.
  • the rotor 124 is in turn provided with additional cutting edges 128 of equal length that are regularly spaced over the circumference, which are located in a common plane with the stepped cutting edges 127 and are located on cams 129 that extend from the inner conical surface 123 project up.
  • the radially inner end point of all cutting edges 127 of the rotor lies on an inner boundary line of the ring work surface through which the cutting edges 124 pass, but, as already mentioned above in relation to FIG. 4, it is also possible for all the outer end points of the cutting edges 127 to be on one instead outer boundary line of an imaginary ring work surface coaxial with the axis of rotation 26 of the rotor, in which case the cutting edges become stepped inwards counter to the direction of rotation of the rotor.
  • FIG. 8 illustrates a stator 34 matched to the rotor 124 according to FIG. 7 in an oblique view from below. Since all cutting edges 127 and 128 lie in a common plane in the rotor 124 according to FIG. 7, the stator 34 according to FIG. 8 forms a kind of a summary of the stators 19 and 21 according to FIGS. 5 and 6, but in such a way that the cutting edges 341 of the blocks 342, the cutting edges 343 of the blocks 344 and the cutting edges 345 of the blocks 346 are all likewise arranged in a common, perpendicular to the axis of rotation 26 of the associated rotor 124 according to FIG.
  • the conical surface 215 present in the stator 21 according to FIG. 6 is, however, dispensed with, since such a one is not required for chip guidance, which is taken over by the rotor 124 according to FIG.
  • FIG. 9 illustrates a further modified rotor 35, which corresponds formally to the rotor 24 in its lower region, but has a flat upper side 351 that runs perpendicular to the axis of rotation of the rotor.
  • the ribs 353 with their cutting edges 352 stepped in length are provided with inclined partial surfaces 354 arranged upstream in the direction of rotation, which correspond to the inclined partial surfaces 246 in the rotor: in FIG. 4.
  • the height of the ribs 353 or the distance between the plane receiving the cutting edges 352 and the surface 351 of the rotor can be selected depending on the requirements of the objects to be shredded. 4, the cone height also affects the height of the ribs 245.
  • FIG. 10 shows to the right of the rotor axis of rotation 25 in a simplified partial section a rotor 124 according to FIG. 7 with a stator 34 according to FIG. 8 on the underside of the ring flange body 20.
  • FIG. 10 illustrates a simplified partial section 4 together with a lower stator 21 according to FIG. 6 for the second size reduction stage.
  • an embodiment similar to that of the stator 34 according to FIG. 8 has been selected in FIG. 10 and, in order to limit the passage of chips through the free spaces between the blocks of the stator provided with the cutting edges, an exchangeable one surrounding them provided on the underside of the plate 211 fixed ring 36.
  • FIG. 11 illustrates a further modified rotor design 37, which largely corresponds to that of FIG.
  • a spiral rib 372 starting from the cylindrical central region 371 is provided on the rotor 37, on and along which blocks 373 with knife edges 374 are arranged, which are approximately radial Have alignment.
  • the surfaces of the blocks 373 with the cutting edges 374 lie together with the surfaces of the edge-side cams 375 with their cutting edges 376 in a common plane oriented perpendicular to the axis of rotation 25 of the rotor.
  • the inner end points of the cutting edges 374 lie on a spiral curve starting and widening at a distance from the axis of rotation 25 of the rotor, which at the same time forms an outer boundary line for an inside, in turn, spiral-shaped free space running on the front side to the cutting edges 374.
  • the radially outer end points of the cutting edges 374 also lie on a spiral curve, which with a corresponding gradation the cutting edge lengths are extended more counter to the direction of rotation or, as in the limit case shown, runs parallel to the spiral curve for the inner end points, in which case the cutting edges 374 have the same length among themselves.
  • FIGS. 12 and 13 illustrate a modified transport and pre-crushing element 40 for materials that are particularly flexible to a certain extent.
  • a connecting flange plate 401 there is in turn a vertical support axis 402 with support webs 403 attached to it.
  • the upper end is chamfered in a roof shape in accordance with the inclination of the funnel wall.
  • Two upper plates 404, 405, which are arranged offset by 180 ° in the circumferential direction, extend from this upper end of the support axis 402 and extend obliquely downwards in opposite directions.
  • a lower plate 406, 407 is located below each of the upper plates 404, 405.
  • the plate 406 forms a plate pair with the plate 404, which is located on one side to an axial plane 408 through the support axis 402.
  • the plate 406 is aligned parallel to the plate 404 and assumes a position which has been achieved by displacement parallel to a plane perpendicular to the plane of the plate 404. The above applies accordingly to the plate pair 405, 407.
  • the plates 404, 405, 406 and 407 can be rigidly connected to the supporting axis 402 and the support webs 403. Instead, there is also the possibility, only schematically indicated in FIG. 12, of hinging the plates about the folding axis to the supporting axis or the supporting webs, a possible folding axis being indicated for the plate 404 at 409 and one for the plate 406 at 410 is. Corresponding folding axes are then also provided for the plates 405, 407.
  • all panels have a straight trailing edge 411 and an arcuate, e.g. elliptical.
  • Leading edge 412 instead of a curved front edge, a e.g. rectangular plate shape can be provided.
  • the plates are all provided with a step profile 413 in the area of their front edge and in the vicinity of their respective lower end.
  • the machine described above works as follows: Objects to be shredded into the receptacle 1 with a funnel 2, the workable dimensions of which are determined by the dimensions of the receptacle, are detected in the circulation area of the transport and pre-breaker 5 and against the walls of the receptacle and of the funnel 2 including the guide webs 7, 8, 9 of the guide member 4 arranged therein, pressed, deformed or broken as an abutment.
  • the support legs 15 of the guide webs 7, 8, 9 prevent material from jamming, since they form a repellent angle together with the legs 10.
  • the transport and pre-crushing element 5 projects with its uppermost tip 56 upwards beyond this area.
  • the plate 54 of the member 5, which is inclined approximately parallel to the bevel of the funnel wall, and the steps 59 'of the step profiles 59 pointing in the direction of rotation enable the member 5 to rotate in the filled hopper 2 and lie in front of the steps 59' without great effort Deforming, breaking or tearing objects due to approximately punctiform loading, but in any case transporting them.
  • the step surfaces 7 ', 58' act like a whisk.
  • step surfaces 58 While the upper step surfaces 58 'lift the objects with their tips and push them upwards, they are pressed down by the step surfaces 57 with their tips. In the receptacle and in particular in the funnel 2, this results in a constant circulation of the objects contained, which on the one hand leads to the fact that they mutually pre-shred each other, while on the other hand a sticking is prevented.
  • the driver or crushing tip 56 detects, in particular, large objects in order, in turn, to shred them in particular in cooperation with the crushing edges of the guide element 4.
  • the guide element 4 fulfills a double function in that it acts on the one hand with its edges as a crushing abutment when the organ 5 moves towards these edges, and on the other hand it assumes a guiding effect when the element 5 with its plate 54 along the guide element 4 passes over it moved away. From the method of operation described above, it can be seen that the transport and pre-crushing element 5 is particularly well suited for the pre-crushing of breakable objects, such as those e.g. Display particle boards, boards, beams, pallets, boxes, fruit crates, dry shrubbery, tree sections, etc. For other items, e.g. wet, flexible wood, veneer wood, straw, cardboard, etc., a transport and primary crushing device 40 according to FIGS.
  • the further rotating rotor 24 now splinters and splits the material through its ribs 245 provided with the cutting edges 248 and distributes the split or splitted material distributing in front of the respective ribs up to the cylindrical central region 244 splitted or split material to the point at which a cutting edge 248 of a corresponding rib 245 meets a cutting edge 195 on a block 194 of the stator 19 which is graduated in length, after which the point cut material is then cut from the inside out.
  • the material is pushed from the inside to the outside under the stator 19. The space widening radially outwards between the blocks 194 of the stator prevents the cut material from jamming.
  • the cut material is conveyed towards the outer edge of the rotor 24 by gravity, by the conical shape of the rotor top 243 and by centrifugal force.
  • the co-rotating material now tries to get tangentially between the cams 216 of the second, lower stator 21. If it has a suitable piece size, it slides between two cams 216, where it is pressed downwards by the conical surface 215 and in front of the cutting edges 217 of the cams 216. A new cutting process then takes place between these and the cutting edges 247 of the cams 249 of the rotor in a second comminution stage.
  • pieces of material comminuted that do not yet fit between the cams 216 of the stator 21 are, as it were, scooped up by the inclined surfaces 246 lying in front of the ribs 245 in the free spaces in front of the ribs and are again fed to the cutting edges 248 of the ribs 245 of the rotor 24 and cut.
  • the material located in front of the cams 249 of the rotor 24 and cut in the second size reduction stage is conveyed by centrifugal force and pressing material from the inside to the outside onto the transport ring 29, which in turn conveys it to the ejection opening 32, through which it is ejected by centrifugal action.
  • a stripper (not shown) can be provided in the region of the ejection opening, which strippers such materials from the transport ring 29.
  • the design and arrangement of the transport and pre-crushing element 5 is also matched to such relatively low speeds, which would cause undesirable unbalance phenomena at higher speeds due to its eccentricity.
  • higher speeds such as may be desirable in the case of lighter shredding work, in order to ensure a higher output, it is advisable to design the transport and pre-crushing device according to FIGS. 12 and 13.
  • a rotor is also primarily designed 7 with the associated stator according to FIG. 8.
  • a rotor 35 designed in accordance with FIG. 9 is used in particular in the treatment of production waste and rejects, such as those e.g. Represent plastic containers, lead frames of sealing materials, etc.
  • the rotor 35 provided with a flat upper side 351 has, in connection with the design of the ribs 353 with their cutting edges 352, a particularly high gripping capacity which counteracts their evasion in the case of easily deformable materials.
  • This rotor 35 can cooperate with the normal stator 19 according to FIG.
  • the rotor 37 according to FIG. 11 is particularly interesting in such special cases. Because the arrangement of the inner and outer end points of the cutting edges 374 on a spiral line in connection with the inner spiral free space results in a gradation of the cutting edges acting in both directions of rotation of the rotor 37.
  • a stator belonging to the rotor according to FIG. 11 would be similar to that according to FIG. 5, in which two blocks 197 with opposite length gradations of the cutting edges 198 are already provided.
  • Modification options for adapting the comminution device 6 to different types of objects are also available in the other configuration of the rotors and the associated stators.
  • a finer or coarser grading system is created, which, like a change in the depth of the free spaces in front of the cutting edges, affects the degree of crushing and the gripping capacity.
  • the depth of the free spaces in front of the cutting edges one can theoretically choose such a small depth that the cutting plane of the rotor is only formed by cutting edges which have a sawtooth-like cutting profile, but which, regardless of this, still change in length stepwise. In this case, a very fine length gradation ratio is also created.
  • a variable size also forms the cross-sectional angle of the cutting edges, which can be varied in the range from an obtuse to an acute angle. Furthermore, the cutting edges can also have an arcuate course instead of the straight course shown everywhere.
  • a transport and pre-crushing element can also be provided, as shown in FIG. 14.
  • the transport and pre-crushing element 500 illustrated in FIG. 14 has a supporting axis 501 which can be fastened coaxially to a rotor, for example the rotor 24, by means of a flange plate 502 and which carries at its upper end a horizontal cross plate 503 which is firmly connected, for example welded, to it.
  • This cross plate 503 protrudes beyond the support axis 501 and has at one end an obliquely downward angled bend 504 oriented approximately perpendicular to the funnel wall of the funnel 2.
  • the transverse plate 503 is provided with a sloping, approximately parallel to the funnel wall plate 505 connected, which extends on the one hand to the supporting axis 501 and on the other hand projects a little above the level of the transverse plate.
  • Plate 505 has two lower ones Extensions 506, 507, one of which extends the plate 505 in front of the support axis 501 and of which the other is angled upwards and in turn extends upstream of the support axis 501 to the cross plate 503.
  • the end of the extension 506 projecting laterally beneath the cross plate 503 can be connected to a node plate 506 ′ which is arranged approximately at the height of the cross plate 503 and connected to it.
  • the inclined plate 505 with its extensions 506, 507 assumes a strength-related striving of the transverse plate 503 with respect to the supporting axis 501 and has the transport and breaking effect of a worm-spiral segment.
  • the extensions 506 and 507 support this effect as well as the stability of the construction.
  • Such basic training of the transport and primary crushing device can be used in machines of the type according to the invention which are mainly loaded with lumpy, not too bulky objects for comminution.
  • the cross plate 503 carries at its transition to the plate 505 a vertical bearing axis 508 on which a tension arm support 509 is freely rotatably mounted, to which at least one horizontal tension arm 511 is attached. If the tension arm carrier is only equipped with a single tension arm 511, the tension arm can be firmly connected to the tension arm carrier 509, e.g. be welded.
  • the tension arm carrier 509 carries two (or also three or more) tension arms 511, these are preferably hinged to the tension arm carrier 509 about a folding axis 510 and are moved from their approximately horizontal position into an approximately vertical alternative position in an angular range freely swiveling from approximately 180 °.
  • Such a transport and pre-crushing element forms a universal element that can not only effectively transport veneer sections, cardboard boxes, foils and similar light flat objects and reduce them, but in particular is also able to handle large and bulky objects such as pallets, plates, etc. break and transport, whereby any mixed operation with such objects is possible.
  • Objects entered into the receptacle 1 with a funnel 2 impart a reciprocating movement to the pull arms 511 due to the eccentric position and the free rotatability of the pull arm carrier 509, in which the pull arms 511 alternately advance into the collection of the filled objects and are moved back inward, whereby they take objects caught by them with such waiting movements towards the center of the container or funnel.
  • these objects reach the area of action of the transverse plate 503, 504 and then that of the plate 505, through which the objects are transported, possibly with a breaking effect, primarily to the cutting plane of the first cutting stage due to the screw-conveying effect of the plate 505.
  • the pull arms can move from their horizontal position to a vertical avoidance position due to their folding possibility, which is particularly desirable when together with or instead of of light flat objects heavy and solid parts, e.g. Chipboard or the like, are abandoned.
  • the tension arms 511 which are preferably provided with hook-like projections 513 on the upper and lower sides, always endeavor to return to their horizontal position according to FIG. 14.
  • Stop buffers 512 attached to the pull arm 511 on both sides support the pull arm 511 in the horizontal position and in the approximately vertical avoidance position on their pull arm support 509, which stop buffers 512 can also serve to reduce noise if they are e.g. Plastic or similar material.

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  • Engineering & Computer Science (AREA)
  • Environmental & Geological Engineering (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Pulverization Processes (AREA)
  • Vending Machines For Individual Products (AREA)

Claims (23)

1. Machine pour broyer des objets en morceaux, en particulier des chutes volumineuses de bois ou de matières analogues ou des déchets volumineux, comportant un récipient récepteur (1) vertical formant un entonnoir (2) dans sa partie inférieure, un organe de guidage (7, 8, 9) à la face interne de la paroi de l'entonnoir, un organe de transport et de concassage préliminaire (5 ; 40) entraîné en rotation à l'intérieur de l'entonnoir (2) et un dispositif de broyage (6) en dessous de l'entonnoir (2), qui comporte un rotor (24 ; 124 ; 35 ; 37) présentant plusieurs arêtes de coupe (248 ; 127 ; 352 ; 374), entraîné en rotation autour d'un axe vertical (25) et relié rigidement, dans la zone centrale (33) de sa face supérieure, à l'organe de transport et de concassage préliminaire (5), ainsi qu'au moins un stator (19 ; 34) relié à l'entonnoir (2) et offrant pour sa part des arêtes de coupe (195 ; 341), les arêtes de coupe (248 ; 127 ; 352 ; 374) du rotor (24 ; 124 ; 35 ; 37) étant situées dans un plan perpendiculaire à l'axe de rotation (25) du rotor, étant disposées à distance les unes derrière les autres dans le sens de rotation et tournées vers l'arrière d'espaces libres s'étendant sur toute leur longueur et balayant une surface de travail annulaire imaginaire coaxiale à l'axe de rotation (25) du rotor (24 ; 124 ; 35 ; 37) qui est chevauchée par les arêtes de coupe (195 ; 341) du stator (19 ; 34) disposées, vu en plan et dans le sens de rotation du rotor (24 ; 124 ; 35 ; 37) à distance les unes derrière les autres et tournées vers l'arrière d'espaces libres s'étendant sur toute leur longueur, caractérisée en ce que la longueur des arêtes de coupe (248 ; 127 ; 352 ; 374) du rotor (24 ; 124 ; 35 ; 37) qui appartiennent à un étage de broyage est échelonnée et va en augmentant dans le sens contraire au sens de rotation du rotor jusqu'à la largeur de la surface de travail annulaire.
2. Machine pour broyer des objets en morceaux, en particulier des chutes volumineuses de bois ou de matières analogues ou des déchets volumineux, comportant un récipient récepteur (1) vertical formant un entonnoir (2) dans sa partie inférieure, un organe de guidage (7, 8, 9) à la face intérieure de la paroi de l'entonnoir, un organe de transport et de concassage préliminaire (5 ; 40) entraîné à l'intérieur de l'entonnoir (2) et un dispositif de broyage (6) en dessous de l'entonnoir (2) qui comporte un rotor (24 ; 124 ; 35 ; 37) présentant plusieurs arêtes de coupe (248 ; 127 ; 352 ; 374) entraîné en rotation autour d'un axe vertical (25) et relié rigidement, dans la zone centrale (33) de sa face supérieure, à l'organe de transport et de concassage préliminaire (5), ainsi qu'au moins un stator (19 ; 34) relié à l'entonnoir (2) et offrant pour sa part, des arêtes de coupe (195 ; 341) ; les arêtes de coupe (248 ; 127 ; 352 ; 374) du rotor (24 ; 124 ; 35 ; 37) étant situées dans un plan perpendiculaire à l'axe de rotation (25) du rotor, étant disposées à distance les unes derrière les autres dans le sens de rotation et tournées vers l'arrière a'espaces libres s'étendant sur toute leur longueur et balayant une surface de travail annulaire imaginaire coaxiale à l'axe de rotation (25) du rotor (24 ; 124 35 ; 37) qui chevauche les arêtes ae coupe (195 ; 341) du stator (19 ; 34) disposées, vu en plan et dans le sens de rotation du rotor (24 ; 124 ; 35 ; 37) à distance les unes derrière les autres et tournées vers l'arrière d'espaces libres s'étendant sur toute leur longueur, caractérisée en ce que ie stator (19 ; 34) présente des arêtes de coupe (195 ; 341) échelonnées en longueur qui appartiennent à un étage ae broyage et qui chevauchent de manière croissante la surface de travail annulaire des arêtes de coupe du rotor.
3. Machine suivant la revendication 1, caractérisée en ce que le stator (19 ; 34) présente des arêtes de coupe (i95 ; 341) appartenant à un étage de broyage et écheionnées en longueur, qui chevauchent de manière croissante la surface de travail annulaire des arêtes de coupe du rotor.
4. Machine suivant la revendication 2 ou 3, caractérisée en ce que le stator (19 ; 34) présente après son arête de coupe la plus longue d'autres arêtes de coupe (198 ; 343) de longueur décroissante par échelons espacées l'une de l'autre.
5. Machine suivant l'une quelconque des revendications 1, 3 ou 4, caractérisée en ce que les arêtes de coupe (248 ; 127 ; 352 ; 374) du rotor (24 ; 124; 35 ; 37) échelonnées en longueur forment un groupe réparti sur une partie seulement de l'ensemble de la périphérie du rotor.
6. Machine suivant la revendication 5, caractérisée en ce que le rotor (24 ; 124 ; 35 ; 37) présente plusieurs groupés d'arêtes de coupe échelonnées en longueur disposées les unes derrière les autres dans le sens de rotation.
7. Machine suivant l'une quelconque des revendications 1 ou 3 à 6, caractérisée en ce que les points d'extrémité radialement internes des arêtes de coupe (248 ; 127 ; 352) échelonnées du rotor (24 ; 124 ; 34) appartenant à un groupe sont tous situés sur la ligne de délimitation interne de la surface de travail annulaire qui les parcourt.
8. Machine suivant l'une quelconque des revendications 1 ou 3 à 6, caractérisée en ce que les points d'extrémité radialement internes des arêtes de coupe (374) du rotor (37) qui font partie d'un groupe sont situés sur une courbe spiralée qui va en s'élargissant et qui débute à distance de l'axe de rotation (25) du rotor, cette courbe formant également une ligne de délimitation extérieure pour un espace libre interne qui fait face aux arêtes de coupe du rotor.
9. Machine suivant l'une quelconque des revendications 1 ou 3 à 8, caractérisée en ce que le rotor (24) présente, dans une zone adjacente vers l'extérieur à sa zone de jonction centrale (33, 244) à l'organe de transport et de concassage préliminaire (5 ; 40), une surface conique (243) inclinée vers le bas de l'intérieur vers l'extérieur.
10. Machine suivant la revendication 9, caractérisée en ce que le rotor (24) présente, sur son bord extérieur, des arêtes de coupe auxiliaires (247) de longueurs égales, régulièrement réparties sur sa périphérie, qui sont situées dans un plan perpendiculaire à l'axe de rotation (25) du rotor et décalées vers le bas et qui forment un deuxième étage de broyage du dispositif de broyage (6) avec des arêtes de coupe (217) d'un deuxième stator (21) qui y sont associées.
11. Machine suivant l'une quelconque des revendications 1 ou 3 à 8, caractérisée en ce que le rotor (124 ; 37) présente, dans une zone adjacente vers l'extérieur à sa zone de jonction centrale (125 ; 371) pour l'organe de transport et de concassage préliminaire (5 ; 40), une surface conique (123) qui s'incline vers le bas de l'extérieur vers l'intérieur.
12. Machine suivant la revendication 11, caractérisée en ce que le rotor (124 ; 37) présente sur son bord extérieur des arêtes de coupe auxiliaires (128 ; 376) de longueurs égales qui sont réparties régulièrement sur sa périphérie, qui sont situées dans le plan des arêtes de coupe échelonnées (127 ; 374) du rotor et qui forment avec des arêtes de coupe (217 ; 345) d'un deuxième stator (21 ; 34) qui y sont associées un deuxième étage de broyage du dispositif de broyage (6).
13. Machine suivant la revendication 10 ou 12, caractérisée par un anneau (36) fixé de manière amovible, entourant extérieurement les arêtes de coupe (217 ; 345) du deuxième stator (21 ; 34) et délimitant une ouverture pour la matière coupée qui passe dans les espaces libres de traversée allant de l'intérieur vers l'extérieur entre les arêtes de coupes du deuxième stator.
14. Machine suivant l'une quelconque des revendications 1 à 13, caractérisée en ce que l'organe de guidage (4) sur la paroi interne de l'entonnoir (2) est formé d'au moins une ailette de guidage (7 ; 8 ; 9) inclinée vers le bas et posée sur la paroi de l'entonnoir, qui présente une aile (10) faisant saillie à peu près horizontalement dans l'espace de l'entonnoir, dont le bord extérieur (11) épouse la forme de la paroi de l'entonnoir, .dont le bord intérieur (12) relie deux points (13, 14) de !a paroi de l'entonnoir et qui, à sa face inférieure, comporte une aile de support (15) orientée à peu près parallèlement à l'axe de rotation (25) du rotor, reliée à la paroi de l'entonnoir et décalée vers l'extérieur par rapport au bord intérieur.
15. Machine suivant la revendication 14, caractérisée en ce que l'organe de guidage (4) est formé de plusieurs ailettes de guidage (7 ; 8 ; 9) adjacentes les unes aux autres ou espacées les unes des autres, dont l'angle au centre est chaque fois inférieur à 90°.
16. Machine suivant l'une quelconque des revendications 1 à 15, caractérisée en ce que l'organe de transport et de concassage préliminaire (5) est formé d'une plaque oblique (54) en substance plane et à peu près parallèle à la paroi de l'entonnoir, qui est pourvue, le long de ses zones marginales, de profils à gradins (57 ; 58 ; 59) dont les surfaces de gradins sont par groupe tournées vers le sens de rotation de la plaque ou opposées à celui-ci.
17. Machine suivant l'une quelconque des revendications 1 à 15, caractérisée en ce que l'organe de transport et de concassage préliminaire (40) est fait de deux paires de plaques (404 ; 406 ; 405 ; 407) orientées à peu près parallèlement dans une paire et supportées avec un décalage de 180° par un axe de support tournant (402), parmi lesquelles les plaques supérieures (404, 405) d'une paire partent chaque fois à peu près de l'extrémité supérieure de l'axe de support et s'étendent obliquernent vers le bas et vers l'extérieur, et les plaques inférieures (405, 407) de chaque paire occupent chaque fois une position décalée parallèlement des plaques supérieures, les plaques présentant dans leur ensemble un bord antérieur (412) accusant un profil à gradins (413) dans sa zone inférieure et un bord postérieur droit (411) qui coïncide chaque fois à peu près avec un plan axial (408) passant par l'axe de support.
18. Machine suivant la revendication 15, caractérisée en ce que les plaques supérieures et inférieures (404 ; 405 ; 406 ; 407) des deux paires de plaques sont supportées chaque fois autour d'un axe de rabattement (409, 410) de manière à pouvoir être rabattues contre l'axe de support (52).
19. Machine suivant l'une quelconque des revendications 1 à 15, caractérisée en ce que l'organe de transport et de concassage préliminaire (500) présente un axe de support (501) pouvant être fixé coaxialement sur un rotor au moyen d'un plateau formant bride (502), cet axe (501) portant une plaque transversale horizontale (503) qui s'étend sur l'axe de support des deux côtés de celui-ci, présente à une extrémité une languette (504) orientée obliquement vers le bas, à peu près perpendiculairement à la paroi de l'entonnoir et est relié à son extrémité opposée à une plaque (505) s'étendant obliquement vers le haut et orientée à peu près parallèlement à la paroi de l'entonnoir, qui d'une part, s'étend vers le bas jusqu'à l'axe de support et d'autre part, fait saillie vers le haut au-dessus du plan de la plaque transversale.
20. Machine suivant la revendication 19, caractérisée en ce que la plaque (505) comporte deux saillies inférieures (506, 507) dont l'une s'étend vers le bas dans le prolongement de la plaque devant l'axe de support (501) et l'autre est couaée vers le haut et s'étend pour sa part, vers le haut vers la plaque transversale devant l'axe de support.
21. Machine suivant la revendication 19 ou 20, caractérisée en ce que la plaque transversale (503) porte, au niveau de sa transition vers la plaque (505), un axe de tourillonnement vertical (508) sur lequel un support de bras de traction (509) est monté de manière à pouvoir tourner librèment, ce support portant au moins un bras de traction (511) à peu près horizontal.
22. Machine suivant ia revendication 21, caractérisée en ce que le ou les bras de traction sont articulés au support (509) de manière à pouvoir se rabattre autour d'un axe de rabattement (510) et peuvent pivoter librement, à partir d'une position à peu près horizontale, d'environ 180° oans une position d'évitement à peu près verticaie.
23. Machine suivant la revendication 21 ou 22, caractérisée en ce que le ou les bras de traction (511) sont pourvus de saillies a'accrocnage (513) sur leurs côtés inférieur et/ou supérieur.
EP80103867A 1979-07-14 1980-07-08 Machine pour le broyage d'objets encombrants Expired EP0022537B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AT80103867T ATE1569T1 (de) 1979-07-14 1980-07-08 Maschine zum zerkleinern von stueckigen gegenstaenden.
DE19813125934 DE3125934A1 (de) 1980-07-08 1981-07-01 Maschine zum zerkleinern von stueckigen gegenstaenden

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2928471 1979-07-14
DE2928471A DE2928471C2 (de) 1979-07-14 1979-07-14 Maschine zum Zerkleinern von stückigen Gegenständen

Publications (2)

Publication Number Publication Date
EP0022537A1 EP0022537A1 (fr) 1981-01-21
EP0022537B1 true EP0022537B1 (fr) 1982-09-22

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP80103867A Expired EP0022537B1 (fr) 1979-07-14 1980-07-08 Machine pour le broyage d'objets encombrants

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US (2) US4387858A (fr)
EP (1) EP0022537B1 (fr)
AT (1) ATE1569T1 (fr)
CA (1) CA1156993A (fr)
DE (1) DE2928471C2 (fr)
NO (1) NO149022C (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3125934A1 (de) * 1980-07-08 1982-06-03 Osnabrücker Metallwerke J.Kampschulte GmbH & Co KG, 4500 Osnabrück Maschine zum zerkleinern von stueckigen gegenstaenden
DE3125309C2 (de) * 1981-06-27 1986-07-24 Kurt 4513 Belm Rößler Zerkleinerungsvorrichtung für Abfälle
US4678127A (en) * 1983-01-26 1987-07-07 Cumpston Edward H Pumped flow attrition disk zone
DE3611691A1 (de) * 1986-04-08 1987-10-15 Kurt Roessler Zerkleinerungsvorrichtung
US4767065A (en) * 1987-01-12 1988-08-30 Jjw, Inc. Material pulverizing apparatus
DE8716200U1 (de) * 1987-04-01 1988-07-28 Rößler, Kurt, 4550 Bramsche Zerkleinerungsvorrichtung
US4767069A (en) * 1987-04-09 1988-08-30 Kim Chong S Multipurpose pulverizer device
AU2116788A (en) * 1987-08-28 1989-03-02 Sterling Grinding Company Incorporated Apparatus for processing material
US5326942A (en) * 1993-02-09 1994-07-05 Schmid Jerry W Noise suppression muffler for moisture laden exhaust gases & method
US6053441A (en) * 1997-09-04 2000-04-25 Bolton-Emerson Americas, Inc. Toroidal flow pulper for difficult materials
US6499681B1 (en) * 2000-06-21 2002-12-31 Mitsuru Maruyama Crushing device in a crusher of an earthmover for crushing chunks of concrete into fine pieces
EP2492405B1 (fr) * 2011-02-23 2018-04-11 BioTrans AG Dispositif d'élimination des déchets pour déchets de cuisine organiques et entraîneur pour un tel dispositif d'élimination des déchets

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US194776A (en) * 1877-09-04 Improvement in machines for preparing corn-fodder
US1045763A (en) * 1911-04-13 1912-11-26 Jeffrey Mfg Co Crusher.
US1874079A (en) * 1929-07-26 1932-08-30 Travis Process Corp Dispersion machine
CH179943A (de) * 1934-03-13 1935-09-30 Lengweiler Eugen Maschine zum Schnitzeln von Nahrungsmitteln aller Art.
US2297604A (en) * 1941-09-18 1942-09-29 William W Bateman Ice breaking and sizing machine
DE953671C (de) * 1955-02-05 1956-12-06 Bernhard Wiewelhove Zusatzwerkzeug fuer mit Auswerferfluegeln versehene Vorrichtungen zum Zerkleinern landwirtschaftlicher Saftfutterpflanzen
DE2255694C3 (de) * 1972-11-14 1981-07-23 Krupp-Koppers Gmbh, 4300 Essen Einrichtung zum Zerkleinern größerer Schlackenstücke, die bei der Vergasung von festen Brennstoffen anfallen
US3933317A (en) * 1973-03-13 1976-01-20 Virgilio Rovere Grinding mill
DE2701897C3 (de) * 1977-01-19 1980-01-10 Max Frost Maschinen- Und Apparatebau, 1000 Berlin Vorrichtung zum Zerkleinern von Abfällen unterschiedlicher Art, insbesondere von Industrieabfällen und Sperrmüll

Also Published As

Publication number Publication date
ATE1569T1 (de) 1982-10-15
NO802108L (no) 1981-01-15
NO149022C (no) 1984-02-01
CA1156993A (fr) 1983-11-15
DE2928471C2 (de) 1982-03-11
EP0022537A1 (fr) 1981-01-21
NO149022B (no) 1983-10-24
US4387858A (en) 1983-06-14
DE2928471A1 (de) 1981-01-22
US4440352A (en) 1984-04-03

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