EP0022537B1 - Apparatus for the comminution of bulky objects - Google Patents

Abstract

A machine for comminuting bulk objects such as wood or the like includes a receptor forming in its lower part, a funnel, a guide means at the inner side of the funnel, a comminuting device below the funnel, and a transport and pre-breaking means within the funnel and rotating therein with the comminuting device. The comminuting device includes a rotor rotatable about a vertical axis and having a plurality of cutting edges and at least one stator mounted on the funnel and also having cutting edges. The cutting edges of the rotor traverse an annular working plane which is perpendicular to the rotational axis of the rotor with the annular working plane overlapping with the cutting edges of the stator. The rotor cutting edges, when viewed from the top and in the rotational direction of the rotor, are arranged at distances behind each other and in the back of free spaces extending along their lengths, the length of the cutting edges of the rotor being graduated and increasing in a direction opposite to the rotational direction of the rotor and up to the width of the annular working plane.

Description

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.

In a known machine of this type (DE-A-2701 897), 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.

However, if a relatively rigid and at the same time thicker and wider object or a plurality of such objects simultaneously get between a cutting edge of the rotor and the cutting edge of the stator closest in the direction of rotation, the comminution in this comminution stage takes place in one the entire dimension of the object or objects in the cutting plane practically all of a sudden, sudden process that causes high peak loads and often blockages of the machine, which have adverse consequences for the machine components and the shredding process.

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.

According to a first solution to this problem, 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. With regard to further refinements, reference is made to claims to 23, wherein no priority of a prior application is claimed for the subject matter of FIGS. 14 and claims 19 to 23.

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.

• Figur 1 eine Maschine in einem senkrechten, das Transport- und Vorbrechorgan ausnehmenden Schnitt,
• Figur 2 eine Draufsicht auf die Maschine nach Fig. 1,
• Figur3 eine schaubildliche Einzeldarstellung des Transport- und Vorbrechorgans der Maschine nach Fig. 1,
• Figur 4 eine schaubildliche Darstellung des Rotors der Maschine nach Fig.1,
• Figur 5 eine schaubildliche Darstellung eines ersten Stators in der Maschine nach Fig. 1,
• Figur6 eine schaubildliche Darstellung eines zweiten Stators in der Maschine nach Fig. 1,
• Figur7 eine schaubildliche Darstellung eines abgewandelten Rotors,
• Figur eine schaubildliche Darstellung eines an den Rotor nach Fig. 7 angepaßten Stators,
• Figur 9 eine schaubildliche Darstellung eines weiteren abgewandelten Rotors,
• Figur 10 eine Ausschnittdarstellung zur Veranschaulichung der Spanführung bei verschiedenen Rotor-Stator-Kombinationen.
• Figur 11 eine schaubildliche Darstellung eines weiteren abgewandelten Rotors,
• Figur 12 eine Seitenansicht einer zweiten, abgewandelten Ausführung des Transport- und Vorbrechorgans,
• Figur 13 eine Draufsicht zu Fig. 12,
• Figur 14 eine schaubildliche Einzeidarstellung einer dritten Ausführung des Transport-und Vorbrechorgangs.

Several embodiments of the object of the invention are illustrated in more detail in the drawing. In detail show:

• FIG. 1 shows a machine in a vertical section excluding the transport and primary crushing element,
• FIG. 2 shows a top view of the machine according to FIG. 1,
• FIG. 3 shows a diagrammatic individual representation of the transport and pre-breaking element of the machine according to FIG. 1,
• FIG. 4 shows a diagram of the rotor of the machine according to FIG. 1,
• FIG. 5 shows a diagram of a first stator in the machine according to FIG. 1,
• FIG. 6 shows a diagram of a second stator in the machine according to FIG. 1,
• FIG. 7 shows a diagrammatic representation of a modified rotor,
• FIG. 1 shows a diagrammatic representation of a stator adapted to the rotor according to FIG. 7,
• FIG. 9 shows a diagrammatic representation of a further modified rotor,
• FIG. 10 shows a cutout illustration to illustrate the chip guidance in different rotor-stator combinations.
• FIG. 11 shows a diagram of a further modified rotor,
• FIG. 12 shows a side view of a second, modified embodiment of the transport and primary crusher,
• FIG. 13 shows a top view of FIG. 12,
• FIG. 14 shows a diagrammatic representation of a third embodiment of the transport and pre-crushing process.

As can be seen in particular from FIG. 1, 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.

There is 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.

In the embodiment of the machine illustrated in FIGS. 1 and 2, 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.

In the interior of the funnel 2 there are also support plates 16 in the form of oval lip cutouts which adjoin one another along a straight edge 17 and, in the rest, have straight edges 18 which point towards the funnel bottom. These edges 18 essentially correspond (and except for protruding parts presenting cutting edges) to the shape of the upper stator 19 pointing towards the funnel interior as one of the components of the comminution device 6.

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 of the comminution device 6, which is provided on the underside with a bevel gear ring 23, is rotatably mounted in the housing 22 about a vertical axis of rotation 25, the axis of rotation 25 of the rotor 24 coinciding with the central axis of the container. 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. 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.

On an upper horizontal central surface 33 of the rotor 24, the transport and pre-crushing member 5 is fastened, which in this way rotates driven by the rotor.

As can be seen in particular in FIG. 1, 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. In order to stiffen this plate 54, 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. At the upper end of the plate 54, which has an eccentric basic arrangement with respect to the support axis 52, there is a driver and break corner 56, the surface of which can be seen in FIG. 3 and can make an angle between 0 and approximately 45 ° with the rotor axis of rotation. In the embodiment shown, this angle is 45 ''. 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. In the step profile 57, 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.

As can be seen in FIG. 4, 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.

Ridges 245, which are approximately radially directed, protrude upward from surface 243, the rear surfaces of which extend in the direction of rotation and the end faces of which are perpendicular. The rear surfaces of the ribs 245, which are located on the back of free spaces, comprise a lower surface which rises obliquely against the direction of rotation Inclined surface part 246, which merges upwards into a vertical surface part 246 '. 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. The cutting edges 248 of the rotor 24, which are graded in length, form a group which is distributed only over part of the entire rotor circumference and which, in the example shown, is distributed over a central angle of approximately 270 ° of the rotor. Instead of such a group, 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.

In the embodiment according to FIG. 4, 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. Instead of the resulting extension of the cutting edges towards the outside, 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.

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. Together with the cutting edges of the lower stator 21 which are assigned to them and will be described below, they form a second size reduction stage of the size reduction device 6, insofar as this is necessary because of the desired degree of size reduction. However, the additional cutting edges 247 can also be omitted, e.g. makes the rotor design according to FIG. 9 clear.

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. 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. In the illustration of the stator 19, which is shown obliquely from below in FIG. 5, it can clearly be seen that 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. In front of each of the blocks 194 there is a space that extends radially inwards and outwards and ensures a full cut over the entire cutting edge length of all cutting edges 195.

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.

As can be seen in FIG. 6, 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. On the underside of the plate 211 there is a ring extension 214 with a triangular cross section. According to 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. In contrast 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. In the central region of the rotor 124, 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. At its outer edge, 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.

In this embodiment, too, 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. On this surface there is an attachment or rotor part which forms cutting edges 351 and which corresponds in its basic design and function to that in the central region of the rotor 24 according to FIG. 4. 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.

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. To the left of the rotor axis 25, FIG. 10 illustrates a simplified partial section 4 together with a lower stator 21 according to FIG. 6 for the second size reduction stage. Instead of the inner conical surface 215 of the stator 21 according to FIG. 6, 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.

Finally, FIG. 11 illustrates a further modified rotor design 37, which largely corresponds to that of FIG. Instead of the ribs starting from the cylindrical central region in the rotor according to FIG. 7 with their corresponding cutting edges, 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.

Finally, FIGS. 12 and 13 illustrate a modified transport and pre-crushing element 40 for materials that are particularly flexible to a certain extent. On 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.

In the example shown, 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. In order to prevent bridges from forming in the area of the transition from the upper part 1 of the receptacle to its funnel 2, 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. 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. 12 and 13 is more favorable, because the two upper plates 404 and 405 run with their outer ends close to the funnel wall and grip thin objects , pull them inwards and transfer them to the lower plates 406, 407. The strong bending that occurs causes the materials to be stressed beyond their bending or tear strength, with the result that they also break or tear. The lower plates 406, 407 finally push the objects located in their area downwards to the comminution device 6. By increasing and appropriately arranging guide bars corresponding to guide bars 7, 8 and 9, an optimal pre-shredding in the funnel area can be ensured for each special type of object to be shredded.

If the objects have reached a certain piece size due to the pre-shredding, they get between the organization by gravity and the transport and guiding effect NEN 5 or 40 and 4 in the cutting area of the rotor 24 and the stators 19, 21st

Longer or thicker pieces, some of which still rest on the wall of the funnel, are drawn in tangentially through the rotating rotor 24 until a part rests on the free conical surface 243 and the first smaller ribs 245 can grip. Once these have been gripped, the longer or thicker pieces are pulled under the stator 19 until they get caught on the blocks 194. 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. During the cutting or shearing process, 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. In the first 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. In the case of possibly moist materials, a stripper (not shown) can be provided in the region of the ejection opening, which strippers such materials from the transport ring 29.

The above-described mode of operation of the machine according to FIGS. 1 and 2 makes it clear that this machine can carry out the heaviest shredding work. To illustrate the situation, it should be pointed out that in the case of a medium-sized machine, the receptacle volume of the receptacle is approximately 6 m ³ . In order to apply the large forces required to carry out the comminution, a correspondingly large reduction is required, which produces correspondingly low speeds for the rotor. At such low speeds for the rotor, its conical surface 243 is important for proper material transport in the area of the shredding device in order to support the centrifugal effect. 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. For 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. At such a higher speed, a rotor is also primarily designed 7 with the associated stator according to FIG. 8. These result in a structural simplification with otherwise the same drawing in and cutting working method. However, the material transport differs as a result of the inner-conical configuration of the rotor surface 123. This must be brought about exclusively by centrifugal force, which has to convey the materials comminuted in the first comminution stage by the cutting edges 127, 341 to the cams 129. Pieces which are not yet of sufficient size for a subsequent comminution in the second comminution stage are pushed up by the centrifugal force on the cams 129 and are then prevented from rotating by the stator 34, so that the material pieces accumulate in front of the stator until they are gripped again by the ribs 126 and re-shredded in the first shredding stage.

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.

In principle, in all cases, all rotor-stator combinations can cause the rotor to lock up, for example due to steel parts, an unfortunate accumulation objects that are difficult to shred etc. In such a case, the machine is automatically switched off and reversed after a short, technically-related downtime, ie reversed in the direction of rotation of the rotor. This clears the blockage so that the machine can then be switched back to normal operation. Such a reversing mode of operation is irrelevant for an operation with comminution of normal objects, since blockages occur very rarely there. However, there are also special cases that occur, for example, with rubber objects. Due to its compactness as a block and its high toughness, rubber forces more frequent reversals, which would lead to an undesirable reduction in performance in the machine designs with rotors according to FIGS. 4, 7 and 9. 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. A stator derived from the stator 19 according to FIG. 5 for the rotor according to FIG. 11 would receive a further spiral edge 192 with an opposite curvature instead of the edge 193 and would be provided with a cutting edge trim under this second part which is spirally delimited on the inside Reverse rotation of the rotor 11 _; would correspond to the stock shown in FIG. 5 for the forward run. If the machine is blocked or excessively braked in the forward direction of the rotor when crushing rubber parts, the machine is switched over and continued with the direction of rotation of the rotor reversed until a blockage or excessive braking occurs again. The shredding performance achieved in such an operation hardly differs from a continuous operation with only one direction of rotor rotation for the shredding operations. All the rotors shown have cutting edges for the first size reduction, which belong to a single group. In particular in the case of rotors with very large diameters, several such groups can also be provided on one rotor, it also being possible to increase the length gradation in one group from the inside out and in another group from the outside in.

For very fine comminution, it can also be advantageous to increase the number of rows of additional cutting edges in the area of the outer edge of the rotor. With further rows of rings of additional cutting edges, which would have to be arranged on the same rotor, there would accordingly be further comminution stages through which the material would be conveyed by centrifugal force.

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. By changing the number of cutting edges graded in length for the first crushing stage, 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. When specifying 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.

The angular position of the cutting edges of the stator to those of the rotor, by means of which the cutting angle can be increased or decreased, offers further possibilities for change. It is only important to note that the point cut function is retained.

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.

It should also be mentioned that in the case of cutting edges of rotor and stator which are graded in length, the cutting edges present an equal total length, which results in uniform wear or a long general service life.

Instead of transport and primary crushing elements 5; 40, as illustrated in more detail in FIGS. 3 and 12, 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. At its opposite end, 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.

However, in cases in which particularly light, large-area or large-volume objects such as veneer sections, large cardboard boxes, foils etc. are to be shredded, which are given in place of or at the same time with lumpy objects, there is a slight risk that such particularly difficult objects Place it more or less flat on the funnel wall and prevent it from being effectively transported to the shredding stage. For such cases, 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. If, as shown in FIG. 14, 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. As a result, 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. If there is too much accumulation of material in front of these arms during an outward movement of the pull arms 511, 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. Due to their gravity, 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.

Claims (23)

1. A machine for comminuting lumpy objects, particularly bulky wood or other waste or rubbish, comprising an upright receiving container (1) having a funnel (2) in its lower portion, a guide means (7, 8, 9) on the inside of the funnel wall, a rotating conveying and preliminary breaking member (5 ; 40) driven inside the funnel (2) and a comminuting device (6) beneath the funnel (2), which comminuting device comprises a rotor (24 ; 124 ; 35 ; 37) having a number of cutting edges (248 ; 127; 352 ; 374), which rotor is arranged to be driven in rotation about a vertical axis (25) and which is rigidly connected to the conveying and preliminary breaking member (5) in the central region (33) of its upper side, and at least one stator (19 ; 34) which is connected to the funnel (2) and which in turn presents cutting edges (195 ; 341), the cutting edges (248 ; 127 ; 352 ; 374) of the rotor (24 ; 124 ; 35 ; 37) being situated in a plane extending perpendicular to its axis of rotation (25) and spaced apart one behind the other in the direction of rotation of the rotor, the cutting edges of the rotor lying at the back of free spaces extending respectively over the lengths of the cutting edges (248 ; 127 ; 352 ; 374) of the rotor and moving in an imaginary annular working surface which is coaxial with the axis of rotation (25) of the rotor (24 ; 124 ; 35 ; 37), which imaginary annular working surface is overlapped by the cutting edges (195 ; 341) of the stator (19 ; 34), the cutting edges (195 ; 341) of the stator being spaced apart one behind the other as seen in plan view and in the direction of rotation of the rotor (24 ; 124 ; 35 ; 37), the cutting edges (195 ; 341) of the stator lying at the back of free spaces extending respectively over their lengths, characterised in that the lengths of the cutting edges (248 ; 127 ; 352 ; 374) of the rotor (24 ; 124 ; 35 ; 37) in one comminuting stage are increased stepwise, counter to the direction of rotation of the rotor, up to the width of said annular working surface.

2. A machine for comminuting lumpy objects, particulary bulky wood or other waste or rubbish, comprising an upright receiving container (1) having a funnel (2) in its lower portion, a guide means (7, 8, 9) on the inside of the funnel wall, a rotating conveying and preliminary breaking member (5 ; 40) driven inside the funnel (2) and a comminuting device (6) beneath the funnel (2), which comminuting device comprises a rotor (24 ; 124 ; 35 ; 37) having a number of cutting edges (248 ; 127 ; 352 ; 374), which rotor is arranged to be driven in rotation about a vertical axis (25) and which is rigidly connected to the conveying and preliminary breaking member (5) in the central region (33) of its upper side, and at least one stator (19 ; 34) which is connected to the funnel (2) and which in turn presents cutting edges (195; 341), the cutting edges (248 ; 127 ; 352 ; 374) of the rotor (24 ; 124 ; 35 ; 37) being situated in a plane extending perpendicular to its axis of rotation (25) and spaced apart one behind the other in the direction of rotation of the rotor, the cutting edges of the rotor lying at the back of free spaces extending respectively over the lengths of the cutting edges (248 ; 127 ; 352 ; 374) of the rotor and moving in an imaginary annular working surface which is coaxial with the axis of rotation (25) of the rotor (24 ; 124 ; 35 ; 37), which imaginary annular working surface is overlapped by the cutting edges (195 ; 341) of the stator (19 ; 34), the cutting edges (195 ; 341) of the stator being spaced apart one behind the other as seen in plan view and in the direction of rotation of the rotor (24 ; 124 ; 35 ; 37), the cutting edges (195 ; 341) of the stator lying at the back of free spaces extending respectively over their lengths, characterised in that the cutting edges (195 ; 341) of the stator (19 ; 34) in. one comminuting stage are graduated in length so as to increasingly overlap the annular working surface of the rotor cutting edges.

3. A machine as claimed in claim 1, characterised in that the cutting edges (195 ; 341) of the stator (19 ; 34) in one comminuting stage are graduated in length so as to increasingly overlap the annular working surface of the rotor cutting edges.

4. A machine as claimed in claim 2 or 3, characterised in that the stator (19 ; 34) comprises further cutting edges (198 ; 343) spaced apart from and following that of said cutting edges having the greatest length, said further cutting edges having a decreasing graduated length.

5. A machine as claimed in any one of claims 1, 3 or 4 characterised in that the cutting edges (248 ; 127 ; 352 ; 374) of the rotor (24 ; 124 ; 35 ; 37) which are graduated in length are disposed in a group distributed over a portion only of the total periphery of the rotor.

6. A machine as claimed in claim 5, characterised in that the rotor (24 ; 124 ; 35 ; 37) comprises a plurality of groups of cutting edges which are graduated in length and arranged one behind the other in the direction of rotation.

7. A machine as claimed in claim 1 or any one of claims 3 to 6, characterised in that the radially inner ends of the graduated cutting edges (248 ; 127 ; 352) of the rotor (24 ; 124 ; 34) belonging to one group are all situated on the inner boundary line of the annular working surface in which they travel.

8. A machine as claimed in ciaim 1 or any one of claims 3 to 6, characterised in that the radially inner ends of the cutting edges (374) of the rotor (37), belonging to one group, are situated on a spiral curve which begins with spacing from the axis of rotation (25) of the rotor and widens out and which at the same time forms an outer boundary line for an inner free space extending at the ends of the cutting edges of the rotor.

9. A machine as claimed in ciaim 1 or any one of claims 3 to 8, characterised in that the rotor (24) comprises a surface (243) falling conically from the inside outwards in a region adjacent its central region (33, 244) connected to the conveying and preliminary breaking member (5 ; 40).

10. A machine as claimed in claim 9, characterised in that the rotor (24) comprises, at its outer edge, additionai cutting edges (247) of the same length as one another, which edges are distributed regularly around the periphery of the rotor, the additional cutting edges (247) lying in a plane offset downwards perpendicuiar to the axis of rotation (25) of the rotor and forming, together with associated cutting edges (217) of a second stator (21), a second comminuting stage of the comminuting device (6).

11. A machine as claimed in claim 1 or any one of claims 3 to 8, characterised in that the rotor (124 ; 37) comprises a surface (123) falling conically inwards from the outside in a region adjoining externally its centrai connecting region (125 ; 371) for the conveying and preliminary breaking member (5 40).

12. A machine as claimed in claim 11, characterised in that the rotor (124 ; 37) comprises, at its outer edge, additicnalcutting edges (128 ; 376) of the same length as one another which edges are distributed regularly, with spacing, around the periphery of the rotor, the additional cutting edges (128 ; 376) being situated in the plane of the graduated cutting edges (127 ; 374) of the rotor and forming with associated cutting edges (217 ; 345) of a second stator (21 ; 34) a second comminuting stage of the comminuting device (6).

13. A machine as claimed in claim 10 or 12, characterised by an interchangeable ring (36) surrounding the cutting edges (217 ; 345) of the second stator (21 ; 34) externally to limit the passage of cut material passing through free spaces continuous from the insides outwards and disposed between the cutting edges of the second stator.

14. A machine as claimed in any preceding claim characterised in that the guide means (4) on the inside of the funnel wall is formed by at least one downwardly inclined guide member (7:8:9) comprising a part (10) which projects substantially horizontally into the funnel space, the outer edge (11) of the part (10) following the course of the funnel wall and the inner edge (12) of the part (10) connecting two points (13, 14) on the funnel wall, and at the under side of said part (10) a supporting arm (15) directed substantially parallel to the axis of rotation (25) of the rotor, the supporting arm (15). being set back outwards in relation to the inner edge (12) of the part (10) and being connected to the funnel wall.

15. A machine as claimed in claim 14, characterised in that the guide means (4) consists of a plurality of guide members (7 ; 8 ; 9) which adjoin one another or which are spaced apart, the sector angle of the guide members being less than 90° in each case.

16. A machine as claimed in any preceding claim characterised in that the conveying preliminary breaking member (5) consists of a substantially plane plate (54) which is set obliquely substantial parallel to the funnel wall and which is provided, along marginal regions, with step profiling (57 ; 58 ; 59), the step surfaces of which face in the direction of rotation of the plate or in a direction away from the direction of rotation of the plate. -

17. A machine as claimed in any of claims 1 to 15, characterised in that the conveying and preliminary breaking member (40) consists of two pairs of substantially parallel plates (404 ; 406 ; 405 ; 407) which are carried, offset by 180°, on a rotatable supporting shaft (402), the upper plate (404 ; 405) of each pair originating from the upper end of the supporting shaft and falling obliquely towards the outside, and the lower plate (405 ; 407) of each pair assuming a parallel displaced position in relation to the upper plate, the front edge (412) of each plate having a stepped profile (413) in its lower region and the rear edge (411) of each plate being straight and substantially coinciding with an axial plane (408) through the supporting shaft.

18. A machine as claimed in claim 15, characterised in that the upper and lower plates (404 ; 405 ; 406 ; 407) of both pairs of plates are each pivotally supported about a pivot axis (409 ; 410) on the supporting schaft (52).

19. A machine as claimed in any one of claims 1 to 15, characterised in that the conveying and preliminary breaking member (500) comprises a supporting shaft (501) secured coaxially to the rotor by means of a flange plate (502) and on which a horizontal transverse plate (503) is fitted which projects beyond the supporting shaft at both sides and comprises, at one end, an angled portion (504) extending obliquely downwards and aligned substantially perpendicular to the funnel wall, the plate (503) being connected, at its opposite end, to a plate (505) which extends obliquely upwardly and downwardly and which is aligned substantially parallel to the funnel wall, the plate (505) extending obliquely downwardly to the supporting shaft (501) and obliquely upwardly above the plane of the transverse plate (503).

20. A machine as claimed in claim 19, characterised in that the plate (505) has two lower extensions (506 ; 507) one of which forms a downward extension of the plate in front of the supporting shaft (501) and the other of which is bent upwards at an angle and in turn extends upwardly above the plane of the transverse plate in front of the supporting shaft.

21. A machine as claimed in claim 19 or 20, characterised in that the transverse plate (503) carries, at its transition to the plate (505), a vertical bearing shaft (508) on which is mounted for free rotation a pusher-arm carrier (509) carrying at least one substantially horizontal pusher arm (511).

22. A machine as claimed in claim 21, characterised in that the pusher arm or arms are articulated on the pusher-arm carrier (509) for pivoting about a pivot axis (510) and can be swung freely through about 180° out of their substantially horizontal position into a substantially vertical position.

23. A machine as claimed in claim 21 or 22, characterised in that the pusher arm or arms (511) are provided with hook-like extensions (513) at their under side and/or at their upper side.

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