WO2024110484A1 - Dispositif de broyage pour des solides de dimensions importantes - Google Patents

Dispositif de broyage pour des solides de dimensions importantes Download PDF

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Publication number
WO2024110484A1
WO2024110484A1 PCT/EP2023/082594 EP2023082594W WO2024110484A1 WO 2024110484 A1 WO2024110484 A1 WO 2024110484A1 EP 2023082594 W EP2023082594 W EP 2023082594W WO 2024110484 A1 WO2024110484 A1 WO 2024110484A1
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WO
WIPO (PCT)
Prior art keywords
axis
shaft
rotation
shredding
crushing
Prior art date
Application number
PCT/EP2023/082594
Other languages
German (de)
English (en)
Inventor
Carsten LUCKS
Stephen TAPKEN
Paul Krampe
Hugo Vogelsang
Original Assignee
Vogelsang Gmbh & 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 Vogelsang Gmbh & Co. Kg filed Critical Vogelsang Gmbh & Co. Kg
Publication of WO2024110484A1 publication Critical patent/WO2024110484A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C18/00—Disintegrating by knives or other cutting or tearing members which chop material into fragments
    • B02C18/06—Disintegrating by knives or other cutting or tearing members which chop material into fragments with rotating knives
    • B02C18/14—Disintegrating by knives or other cutting or tearing members which chop material into fragments with rotating knives within horizontal containers
    • B02C18/142—Disintegrating by knives or other cutting or tearing members which chop material into fragments with rotating knives within horizontal containers with two or more inter-engaging rotatable cutter assemblies
    • 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
    • B02C18/06—Disintegrating by knives or other cutting or tearing members which chop material into fragments with rotating knives
    • B02C18/16—Details
    • B02C18/18—Knives; Mountings thereof
    • B02C18/182—Disc-shaped knives

Definitions

  • the invention relates to a comminution device for comminution of solids, comprising:
  • first shredding shaft with a plurality of toothed disks which are arranged axially spaced from one another along a first axis of rotation of the first shredding shaft
  • each toothed disk has a plurality of teeth distributed over the circumference with radially outwardly located tooth cutting edges which lie on an envelope, and between two adjacent toothed disks a gap is formed which is delimited radially inwardly by a gap circumferential base surface, - wherein the first comminution shaft is mounted in a comminution housing so as to be rotatable about the first axis of rotation.
  • Another aspect of the invention is a method for crushing materials.
  • Shredding devices of this type are used to shred solids such as branches or waste.
  • the solids are filled into a filling opening in the housing and fall onto the first shredding shaft due to gravity.
  • Shredding devices can also be arranged in a fluid flow, for example to cause solid shredding in the flow direction upstream of pumps, sieves, separators and to feed the downstream pump, the To protect the separator or the screening device from damage and to set it to an efficient operating point.
  • the solids are usually carried along in the fluid flow independently of gravity.
  • crushing devices can be designed with a single crushing shaft, which is then often supplemented by corresponding stationary scrapers and blades on the housing in order to achieve a favorable crushing effect with the single crushing shaft.
  • crushing devices with two or more crushing shafts are often used, in which the toothed disks of the crushing shafts mesh with one another, with the toothed disks of one crushing shaft engaging in the spaces between the toothed disks of the other crushing shaft. This achieves efficient crushing of the solids and at the same time ensures a high throughput.
  • twin-shaft shredder is already known from EP 3 538 278 B1.
  • Another twin-shaft shredder is already known from WO 2021/245124 A2.
  • These previously known twin-shaft shredders have a highly efficient shredding of solids and are specially designed to be able to carry out maintenance with little effort and to replace individual toothed disks of a shredding shaft or an entire shredding shaft.
  • elongated solids such as branches, sticks and flat solids such as foils as well as particulate solids can be shredded efficiently.
  • a shredding device with two shredding shafts is already known, in which a rotation axis can be adjusted by means of an eccentric adjustment device in order to achieve a reduction or enlargement of the cutting/grinding gap and in this way, for example, to compensate for wear.
  • the toothed disks have tooth cutting edges located on a circular surface around the rotation axis.
  • a shredding system is already known from DE 7818838U1, in which cutting disks of two parallel adjacent shafts interact, which rotate about two parallel axes of rotation. Between each two cutting disks, a spacer body is arranged on each of the shafts, which has an outer contour that is rotationally symmetrical about the axis of rotation. In some embodiments, the cutting disks have a contour that deviates from a circular shape and rotate about the axis of rotation located in the center of the cutting disks.
  • the disadvantage of this shredding system is that, due to the contour of the cutting disks and spacer bodies, it cannot prevent the cutting disks from digging only a limited distance into the material to be shredded, and the material then remains on the shafts without being shredded any further.
  • a shredding machine is already known from DE69608918T2 in which two rotating shafts are arranged in a funnel. A set of disc-shaped knives is attached to each shaft and rotates around the axis of rotation of the shaft. These knives provided on the shafts interact with fixed knives and cause a shredding effect between the rotating disc-shaped knives and the fixed knives.
  • a disadvantage of this shredding machine is that the interaction of the rotating knives with fixed knives results in low shredding efficiency and a risk of blockage.
  • the knives are arranged in such a way that when materials of high hardness or strength are to be shredded, a strong leverage effect is created on the knife, shaft and the knife-shaft connection, which can lead to a blockage of the rotational movement or damage to the torque-resistant connection between the shaft and knife.
  • a further disadvantage is that, due to the blades on the shaft being located only on one side of the axis of rotation, pieces of material up to a certain size can be unintentionally conveyed through the device without being shredded.
  • a shredding device is already known from CN113926555A, which has two shredding shafts.
  • Each of the two shredding shafts has eccentrically arranged cutting disks that interact with blades fixed to an inner wall of the shredding device.
  • the two shredding shafts rotate in opposite directions, which prevents a shredding effect in the area between the shafts and causes the material to be shredded to be conveyed from an inlet to an outlet opening in the outer area and conveys the material into shredding engagement with the fixed blades.
  • This shredding device has the disadvantage that it quickly becomes clogged in the conveying area of the material between the fixed disks and the cutting disks and has only a low shredding efficiency.
  • the invention is based on the object of achieving effective comminution of the entire solid even in the case of such large, block-like solids.
  • a comminution device of the type described above in which the tooth cutting edges of at least one of the toothed disks lie on an envelope which does not form a rotationally symmetrical shape, in particular a cylindrical surface around the first axis of rotation and/or at least one of the intermediate space circumferential base surfaces of the first comminution shaft does not form a rotationally symmetrical shape, in particular a cylindrical surface around the first axis of rotation.
  • the invention is based on the knowledge that the reduced crushing performance of solid blocks, which occurs after a certain period of time, is caused in many applications by the block-like solid resting on the peripheral surfaces of the gaps between the toothed disks after the toothed disks have cut far enough into the solid.
  • no further significant comminution effect takes place.
  • a hydrodynamic lubricating film can form between the toothed disks or the gaps and the solid, which also prevents the teeth from penetrating further into the solid and consequently no further comminution effect takes place.
  • a typical example in which both the first and the second effect can occur is the comminution of solids that are filled into the comminution device as a deep-frozen block.
  • an initial cutting effect takes place;
  • the solid block is supported and the molten liquid of the deep-frozen block causes a lubricating effect which prevents further crushing of the block or at least makes it considerably more difficult.
  • the comminution device is developed in such a way that, at least in the case of a toothed disk and/or at least in the case of an intermediate space circumferential base surface, the movement of the first comminution shaft does not produce a rotation of the envelope of the tooth cutting edges or the intermediate space circumferential base surface around the axis of rotation of the comminution shaft that is stationary relative to the housing of the comminution device and lies on a rotationally symmetrical, in particular on a cylindrical surface.
  • the envelope of the tooth cutting edges is to be understood here as the enveloping contour that connects the outer ends of the tooth cutting edges to one another in a continuous enveloping contour and consequently encloses the toothed disk.
  • the rotation axis around which the envelope and/or the intermediate space circumferential base surface do not form a cylindrical surface, is in particular stationary in the crushing housing.
  • the rotation axis can in particular be formed by a physically formed axis arrangement with axis bearings. In other embodiments, the rotation axis can also be formed by bearing elements, lever elements, curved guides and the like as a virtual rotation axis.
  • it can be provided separately, additionally or alternatively that the center of the surface of the envelope of the tooth cutting edges is spaced apart from the rotation axis.
  • the distance between the center of the surface of the envelope of the tooth cutting edges and the rotation axis can be more than 1% and less than 20%, in particular less than 10% of the maximum geometric extension of the envelope perpendicular to the rotation axis of the crushing shaft of the tooth cutting edges.
  • the envelope of the toothed disks from the two previously mentioned known two-shaft shredders of EP 3 538 278 B1 and WO 2021/245124 A2 represents a cylindrical surface because the tooth cutting edges are all arranged at the same radial distance from the axis of rotation of the shredding shaft and the axis of rotation is arranged stationary in the housing.
  • a movement or guidance of the tooth cutting edges on such a cylindrical surface does have the advantage that none of the tooth cutting edges wear out prematurely because they protrude prominently and therefore such two-shaft shredders achieve a long service life of the toothed disks.
  • any lubricating film that may form is regularly interrupted by this and the radial acceleration of the solid causes it to repeatedly hit the shredding shaft, so that the toothed cutting edges achieve effective shredding of the solid each time. Furthermore, by preventing the solid material from remaining stationary on the shredding shaft and instead allowing the solid material to move repeatedly in a vertical or horizontal direction within the housing, the solid material can be broken down into many individual pieces at an early stage, which can then be shredded quickly and efficiently by the shredding device.
  • the tooth cutting edges preferably lie on an envelope that deviates from a cylindrical surface in such a way that this envelope deviating from a cylindrical surface produces an effective up and down movement of a solid resting on the toothed disk, which is in contact with the toothed disk over a circumferential angle of approximately 30° to 45°, due to the deviation of the envelope from a cylindrical surface.
  • the deviation of the envelope from the cylindrical surface has a period of more than 30°, preferably more than 45°. In particular, the deviation can have a period of more than 90°.
  • the deviation from the envelope is not caused, for example, by a change in the radius of two immediately consecutive tooth cutting edges on the toothed disk that follow one another at an angle of less than 30°, less than 45° or less than 90°.
  • a toothed disk which, for example, has 36 tooth cutting edges evenly distributed over the circumference would therefore not achieve the inventive effect of a deviation from a cylinder surface with the desired period of more than 30°, more than 45° or more than 90° if, for example, only every second tooth or every third tooth is set back slightly radially.
  • the inventive deviation from the cylinder surface can be achieved if the radius of the tooth cutting edges is constantly reduced over four consecutive tooth cutting edges, since in this case a deviation from the cylinder surface is achieved over an angle of 40° when these tooth cutting edges rotate.
  • a corresponding deviation from the cylinder surface with a period of 90° can be achieved, thereby effectively causing an up and down movement of a block of solid material resting on the shredding shaft.
  • the tooth cutting edges are therefore arranged at different radii around the axis of rotation, so that not all tooth cutting edges run on a common circular path when the tooth cutting edge rotates around the axis of rotation. Instead, at least two tooth cutting edges run on different paths around the axis of rotation, with these two tooth cutting edges preferably being spaced apart by an angle of at least 30°, 45° or 90°.
  • the effect according to the invention can be achieved if only the envelope of the tooth cutting edges has such a deviation from a cylindrical surface around the axis of rotation or if only the intermediate space circumferential base surface has such a deviation from a cylindrical surface around the rotation axis.
  • both the envelope of the tooth cutting edges and the space circumferential base area have a circumferential movement that deviates from a cylindrical surface when the shredding shaft rotates.
  • the tooth cutting edges or the intermediate space circumferential base surfaces Due to the movement form of the tooth cutting edges and/or the intermediate space circumferential base surfaces, which arises due to their deviation from a cylindrical surface around the first axis of rotation, the tooth cutting edges or the intermediate space circumferential base surfaces lead to a radial movement of a body resting on the shredding shaft when rotating around the axis of rotation.
  • This radial movement can be triggered, for example, by the tooth cutting edges or the intermediate space circumferential base surface moving on an eccentric movement path to the axis of rotation; this movement path itself can then also be a cylindrical movement path.
  • the radial movement of a resting solid body can also be triggered by the fact that, although each individual tooth cutting edge moves on a cylindrical path around the axis of rotation, the multiple tooth cutting edges of a toothed disk distributed over the circumference are arranged at a different distance from the axis of rotation, i.e. a different radius from one another, so that a solid body resting in an angular range rests closer to the axis of rotation when it rests on tooth cutting edges that have a smaller radius than when it rests on tooth cutting edges that have a larger radius from the axis of rotation after the shredding shaft has rotated through a certain angle.
  • the radial movement triggered by the rotation of the shredding shaft in relation to a fixed angle of the shredding shaft in the housing is an oscillating radial movement, so a solid body resting in the angular range is moved radially back and forth.
  • This up and down movement or back and forth movement of the solid body which is superimposed on the circumferential cutting action of the tooth cutting edges, results in efficient comminution of the solid material and avoids the solid material resting on the comminution shaft, which is inefficient for comminution and which hinders the comminution effect of the tooth cutting edges due to lubrication effects and support effects.
  • the deviation of the envelope or the space circumferential base area from a cylinder surface around the axis of rotation results in a periodic radial movement of a solid resting on the shredding shaft.
  • This periodic movement can be designed in such a way that that in an embodiment in which both the envelope and the intermediate space circumferential base surface are designed to deviate from a cylindrical surface, these bring about a synchronous radial movement of the solid, that is to say, a synchronous radial movement in the same direction is brought about both by bearing against the envelope and by bearing against the intermediate space circumferential base surface.
  • the deviation from the cylindrical surface can also be designed such that the radial movement brought about by the envelope of the tooth cutting edges is phase-shifted to the radial movement brought about by the intermediate space circumferential base surface.
  • the solid is alternately radially lifted by the tooth cutting edges or the envelope on the one hand and the intermediate space circumferential base surface on the other, and is therefore not in contact with both the envelope and the intermediate space circumferential base surface at all times during the rotation of the comminution shaft.
  • phase shift results in a favorable impact effect when the solid is moved radially inward by the circumferential base surface of the gap and this radial inward movement is absorbed by the initial contact with the envelope of the tooth cutting edges and is reversed into a radial outward movement.
  • This phase-shifted deviation from the cylinder surface can result in further improved efficiency in the comminution of the solid.
  • the comminution device further comprises:
  • a second shredding shaft with a plurality of toothed disks which are arranged axially spaced apart from one another along a second axis of rotation of the second shredding shaft, and spaces between the toothed disks, wherein the toothed disks of the first shredding shaft engage in the spaces of the second shredding shaft and the toothed disks of the second shredding shaft engage in the spaces of the first shredding shaft, wherein the second shredding shaft is mounted in the shredding housing so as to be rotatable about the second axis of rotation.
  • the shredding device is equipped with a second shredding shaft, which also has toothed disks and spaces between the toothed disks.
  • a second shredding shaft and possibly also further shredding shafts can be provided in order to increase the shredding efficiency and the throughput through the shredding device.
  • the second shredding shaft and also Any additional crushing shafts can be designed in such a way that the envelope of the tooth cutting edges and the intermediate space circumferential base surface form a cylindrical surface around the second axis of rotation, i.e. this second crushing shaft and any additional crushing shafts are designed in a known manner and do not cause any radial movement of a solid resting on the crushing shaft.
  • the envelope and/or the intermediate space circumferential base surface have a geometric shape that differs from a cylindrical surface around the axis of rotation, so that the envelope and/or the intermediate space circumferential base surface trigger a radial movement of a solid resting on the crushing shaft.
  • the advantageous radial movement of the solid is achieved by both the first crushing shaft and the second crushing shaft. This can be done when the two shredding shafts move synchronously at the same speed, in such a way that the shredding shafts cause a synchronous, rectified radial movement in one direction when the two shredding shafts rotate, so that a solid resting on the two shredding shafts is raised and lowered on both sides at the same time by their movement.
  • the movement can also be out of phase, so that a solid resting on the two shredding shafts is raised by one shredding shaft and lowered by the other shredding shaft, thereby setting it into a pendulum motion.
  • a constant alternation between a synchronous lifting and a pendulum motion can take place in order to create an advantageous irregularity in the form of movement, which can effectively prevent a build-up that hinders the shredding effect.
  • the tooth cutting edges of the two shredding shafts preferably mesh with one another:
  • the direction of rotation of the two shredding shafts is preferably opposite and directed such that the tooth cutting edges in the intermediate area between the two shredding shafts move in the conveying direction through the shredding device and the material to be shredded is thus conveyed in this intermediate area from the inlet to the outlet opening. Outside this intermediate area, the tooth cutting edges therefore preferably move against the conveying direction through the shredding device.
  • the tooth cutting edges of several of the toothed disks of the first and/or comminution shaft lie on an envelope that does not form a cylindrical surface around the first or second axis of rotation and/or several of the intermediate space circumferential base surfaces of the first and/or comminution shaft do not form a cylindrical surface around the first or second axis of rotation.
  • the advantageous radial movement of the solid that rests on the comminution shaft can already be achieved by a single toothed disk whose tooth cutting edges lie on an envelope that deviates from the cylindrical surface around the axis of rotation, or a correspondingly designed intermediate space circumferential base surface.
  • such an isolated generation of the radial movement by only one toothed disk and/or only one intermediate space circumferential base surface can also be advantageous, for example in order to bring about a sudden contact with other toothed disks of the comminution shaft that are conventionally designed and whose envelope forms a cylindrical surface around the axis of rotation.
  • the force required for a radial movement of the solid body resting on the shredding shaft is distributed over several toothed disks or intermediate space circumferential base surfaces and thus the desired effect of the radial movement of the solid body can be exerted along the entire shredding shaft or a section thereof. It is particularly advantageous if all toothed disks are designed with a corresponding envelope that deviates from the cylindrical surface and/or all intermediate space circumferential base surfaces are designed with a corresponding geometry that deviates from the cylindrical surface. Alternatively, however, every second, third or nth toothed disk and/or intermediate space circumferential base surface can also be designed in a corresponding manner according to the invention.
  • the envelope and/or the intermediate space circumferential base surface which does not form a cylindrical surface around the first or second axis of rotation, is a cylindrical surface around a central axis which is eccentric to the axis of rotation, or has an oval cross-section, or a triangular, square or polygonal cross-section.
  • the geometry deviating from the cylindrical surface is achieved in that the envelope has an eccentric cylindrical surface or a stationary geometry deviating from a cylindrical surface.
  • An oval cross-section can be formed by sections of the envelope or the peripheral surface that are convex on all sides, but in the sense of the invention, a cross-section that has one or more straight or concave peripheral sections is also understood to be an oval cross-section.
  • a triangular, square or polygonal cross-section is also understood to mean a cross-section that, in the narrow sense, has three, four or more sharply formed corners. Furthermore, this is also understood to mean a cross-section that has three, four or more rounded corners.
  • the central axes of the cylinder surfaces which are eccentric to the first or second axis of rotation and around which the envelopes and/or the space circumferential base surfaces of several toothed disks or spaces arranged next to one another along the axis of rotation, lie on a line parallel to the axis of rotation or lie on a helical line around the axis of rotation, or the longitudinal axes of the oval cross sections of several toothed disks or spaces arranged next to one another along the first or second axis of rotation lie in one plane or form a spiral surface, or the corners of the triangular, square or polygonal cross sections of several toothed disks or spaces arranged next to one another along the first or second axis of rotation lie on a line parallel to the axis of rotation or lie on a helical line around the axis of rotation.
  • the envelopes of the tooth cutting edges and/or the circumferential base surfaces of the gaps lie along the longitudinal extension of the crushing shaft in a geometrically coordinated alignment which straight line or a helical line.
  • a geometric alignment along a straight line all toothed disks whose envelope deviates from a cylindrical surface or all circumferential base surfaces of the gaps that deviate from a cylindrical surface about the axis of rotation cause a solid body resting on the shredding shaft to be raised at the same angle and a solid body resting on the shredding shaft to be lowered at the same angle in the radial direction.
  • the envelope of the tooth cutting edges of the at least one toothed disk of the first shredding shaft which does not form a cylindrical surface around the second axis of rotation, engages in an intermediate space of the second shredding shaft, the intermediate space circumferential base surface of which does not form a cylindrical surface around the second axis of rotation.
  • two shredding shafts are arranged and designed in relation to one another such that the toothed disks, the envelope of which deviates from the cylindrical surface around the axis of rotation, engage in an intermediate space of the other shredding shaft, the peripheral base surface of which also deviates from a cylindrical surface around the axis of rotation of this shredding shaft.
  • this design allows a solid body resting on both shredding shafts to be moved in the radial direction both by the toothed disk of the first shredding shaft and by the peripheral base surface of the intermediate space of the second shredding shaft, into which this toothed disk of the first shredding shaft engages, when both shredding shafts rotate. Furthermore, this two-sided design can ensure that the gap that forms between the envelope of the toothed disk on the one hand and the circumferential base area of the gap on the other hand maintains a constant gap size during the rotation of both shredding shafts or that this gap size periodically increases and decreases during the rotation of the two shredding shafts.
  • a constant gap size can effectively prevent shredded solids above a certain size from passing through between the shredding shafts, thereby reliably maintaining a maximum size of the shredded components.
  • a periodic Although changing the gap size cannot prevent the passage of crushed solids that correspond to the maximum gap size within this periodic change, it leads to a crushing effect that is favorable for many types of solids due to the periodic reduction of the gap size, whereby certain solids can be effectively crushed.
  • the envelope and the intermediate space circumferential base surface are shaped in such a way that, during synchronous rotation of the first shredding shaft and the second shredding shaft, they are spaced apart from one another at a distance which changes over a full revolution of the first shredding shaft by less than 1/10, less than 1/20 and preferably less than 1/50 of the distance between the first and second rotational axes.
  • both the envelope of the tooth cutting edges of a toothed disk and the circumferential base surface of an intermediate space into which this toothed disk engages are formed in a geometry which differs from a cylindrical surface around the respective rotational axis and, when both shredding shafts rotate, a gap which forms between the envelope and the circumferential base surface is kept essentially constant.
  • Synchronous rotation is understood here to mean a fixed ratio of the rotational speeds of the shredding shafts which are in engagement with one another, which can be, for example, 1:1, 1:1, 25 or 1:2. Such synchronization can be achieved, for example, by a coupling gear or by synchronous control of the drive device if the shredding shafts are driven by separate drive devices.
  • the essentially constant gap size can be achieved with synchronous rotation of the two shredding shafts at the same speed by a correspondingly matching geometry of the envelope on the one hand and the circumferential base on the other.
  • such a constant gap size can be achieved by appropriately adapted geometries of the envelope and circumferential base; for example, a triangular envelope around a toothed disk of a shredding shaft that rotates at twice the speed of the other shredding shaft with a circumferential base with a hexagonal cross-section can achieve an essentially uniform gap size.
  • the distance i.e. the gap size
  • the distance can preferably also be set to be less than 1/10 of the distance between the two axes of rotation, for example, in preferred embodiments it is provided that the distance is less than 1/20, 1/25 or 1/50 of the distance between the two axes of rotation
  • providing a certain minimum gap size is also advantageous in order to achieve a throughput of shredded solids through the shredding shafts at a certain height.
  • the gap size is at least 1/100, preferably at least 1/50 or 1/20 of the distance between the two axes of rotation.
  • the first shredding shaft is mounted so as to rotate about a first drive axis
  • the first axis of rotation runs eccentrically to the first drive axis and rotates about the first drive axis
  • the second shredding shaft is mounted so as to rotate about a second drive axis
  • the second axis of rotation runs eccentrically to the second drive axis and rotates about the second drive axis.
  • the radial movement of the solid body resting on the shredding shaft is achieved by the shredding shaft executing a superimposed eccentric rotation about the axis of rotation.
  • the envelope of the tooth cutting edges and/or the circumferential base area of the gaps can form a cylindrical surface around the first or second drive axis and the shredding shafts can be driven in rotation about this drive axis.
  • a rotation about the axis of rotation which is superimposed on this rotation about the drive axis and is eccentric to the drive axis, then causes the radial movement according to the invention of a solid body resting on the shredding shaft.
  • the drive axis and the rotation axis preferably run parallel to each other.
  • the size of the gap between the envelope of a toothed disk and the circumferential base area of a gap into which this toothed disk engages can be kept constant by a synchronous movement of the two crushing shafts about the axis of rotation, whereby this can be achieved in this embodiment independently of the rotation speed of the two crushing shafts about the respective drive axis.
  • This achieves independent control of the rotation speed of the toothed cutting edges about the drive axis on the one hand and the radial movement of the solid body resting on the crushing shaft generated by the rotation about the eccentric axis of rotation on the other hand, which can bring about effective crushing.
  • the envelope and/or the intermediate space circumferential base surface of the first comminution shaft lies on a cylinder surface around the first drive axis and/or the envelope and/or the The intermediate circumferential base surface of the second crushing shaft lies on a cylindrical surface around the second drive axis.
  • This embodiment allows crushing shafts manufactured according to the conventional state of the art to be used and the crushing device according to the invention to be equipped with these crushing shafts by setting them in an eccentric rotational movement of the drive axis within the crushing device according to the invention.
  • the radial distance between the envelope and the intermediate space circumferential base area is constant over the entire circumference.
  • this radial distance constant, it is possible to reliably prevent crushed solids above a certain size from passing through between the crushing shafts and thus maintain a minimum degree of crushing.
  • such a constant distance can be maintained by correspondingly synchronous rotation of the first and second crushing shafts and a geometry of the envelope on the one hand and the circumferential base area on the other hand that is coordinated with this synchronous rotation with the same or different number of revolutions.
  • first and second shredding shafts are driven by a drive device at different speeds. Driving at different speeds has proven to be advantageous for the device according to the invention because this allows uniform wear to occur on all tooth cutting edges of the shredding shafts and avoids localized wear on individual tooth cutting edges or interacting areas of the two shredding shafts, which would lead to a premature need to replace the two shredding shafts.
  • a comminution device for comminution of materials comprising a first comminution shaft with a plurality of toothed disks which are arranged axially spaced apart from one another along a first axis of rotation of the first comminution shaft, wherein each toothed disk has a plurality of teeth distributed over the circumference with radially outwardly located tooth cutting edges which lie on an envelope, and between two adjacent toothed disks a gap is formed which is delimited radially inwardly by a gap circumferential base surface, wherein the first comminution shaft is mounted in a comminution housing so as to be rotatable about the first axis of rotation in that the tooth cutting edges of at least five adjacent Toothed discs lie on a straight line that runs parallel to the first axis of rotation.
  • the tooth cutting edges of at least five adjacent tooth disks are aligned in a line with one another. Accordingly, according to the invention, no thread-like course of all tooth cutting edges or other angular offset between all tooth cutting edges is provided, which is provided in previously known shredding devices in order to avoid excessive stress due to synchronous engagement of several tooth cutting edges on the solid to be shredded. Instead, at least one tooth of each tooth disk is aligned in a line over the length of at least five adjacent tooth disks. These at least five teeth of the five tooth disks lead to a synchronous engagement, which causes a larger block of solid material resting on the tooth disks to shatter.
  • tooth cutting edges of the at least five adjacent tooth disks are aligned in a straight line parallel to the axis of rotation. In this way, the fragmentation effect of a solid block lying on top caused by the synchronous engagement can be achieved at several angles of rotation of the shredding shaft. It should also be understood that the tooth cutting edges of preferably more than ten or more than twenty adjacent tooth disks lie along a straight line that is parallel to the axis of rotation. In this way, the fragmentation effect can also be exerted on solid blocks lying on top for a particularly long time.
  • the toothed disks of the shredding shaft are divided into two or more groups and, within each group, the tooth cutting edges of adjacent toothed disks lie along a straight line that is parallel to the axis of rotation, with the tooth cutting edges of the toothed disks of adjacent groups being offset from one another around the axis of rotation.
  • a group can have at least 5, 10 or 15 teeth and should not exceed a number of 10, 15, 20 or 25 toothed disks.
  • a further aspect of the invention is a method for comminuting materials, comprising the steps of: filling the material into a housing of a two-shaft shredder, subjecting the material to a comminution process by rotating first knife disks arranged on a first comminution shaft of the two-shaft shredder and preferably further by rotating second knife disks arranged on a second comminution shaft of the two-shaft shredder, which is characterized by repeated raising and lowering and/or horizontal displacement of the material by at least one knife disk and/or by at least one circumferential surface formed between the knife disks on the first and/or second comminution shaft, which delimits a gap between two toothed disks radially inward by moving tooth cutting edges arranged on the outer circumference of the at least one toothed disk and/or the circumferential surface on
  • the method according to the invention can particularly preferably be carried out with the previously explained comminution device.
  • the method according to the invention is characterized in that, on the one hand, a comminution effect is achieved by a rotation of toothed cutting edges on the circumference of a toothed disk, and as a result, a solid resting on the comminution shaft can be effectively comminuted. In particular, this can be done by using two intermeshing comminution shafts, as explained above.
  • the method according to the invention is further characterized in that the solid resting on the comminution shaft is repeatedly raised and lowered, which is achieved by the previously explained design of the envelope of the toothed cutting edges and/or the circumferential base area of the gaps in a geometry deviating from a cylindrical surface around the axis of rotation.
  • This repeated raising and lowering avoids stationary support and the formation of a lubricating film between the solid and the comminution shafts, and thus even large, block-like solids can be effectively comminuted, for example.
  • first shredding shaft rotates about a first axis arranged stationary in the housing and the second shredding shaft rotates about a second axis arranged stationary in the housing and the at least one toothed disk has a plurality of tooth cutting edges distributed over the circumference, which are arranged in different radii and/or the circumferential surface has a geometry deviating from a cylinder geometry about the first or second axis of rotation.
  • first shredding shaft rotates about a first rotation axis arranged in the housing, which runs eccentrically to a drive axis and rotates about the latter and/or the second shredding shaft rotates about a second rotation axis arranged in the housing, which runs eccentrically to a second drive axis and rotates about the latter.
  • This embodiment can be implemented effectively in particular by a single or two-shaft shredder in which the drive is provided by a planetary gear, in which the axis of rotation corresponds to the axis of rotation of a planetary gear and the drive axis corresponds to the axis of rotation of the sun gear or ring gear of the planetary gear.
  • a two-shaft or multi-shaft shredder can also be realized in which the two shredding shafts are coupled to two planetary gears of such a planetary gear or the multiple shredding shafts are coupled to multiple planetary gears of such a planetary gear and in this way carry out an eccentric movement around the axis of rotation and are set in rotation in a superimposed manner around their own drive axis, which corresponds to the axis of rotation of the planetary gears.
  • first toothed disks of the first comminution shaft engage in the spaces in the second comminution shaft and the second toothed disks of the second comminution shaft engage in the spaces in the first comminution shaft and during the rotation of the first and second comminution shafts, the smallest distance between the tooth cutting edges of each of the first toothed disks and the peripheral surface of the spaces in the second comminution shaft, in which the respective first toothed disk engages, changes over an entire revolution of the first toothed disk by less than 1/10 of the distance between the first and second rotational axes, and/or the smallest distance between the tooth cutting edges of each of the second toothed disks and the peripheral surface of the spaces in the first comminution shaft, in which the respective second toothed disk engages, changes over an entire revolution of the second toothed disk by less than 1/10 of the distance between the first and second rotational axes.
  • Fig. 1 is a perspective view of an embodiment of a comminution device according to the invention
  • Fig. 2 is a perspective view of two shredding shafts insertable into the shredding device according to a first embodiment
  • Fig. 3 is a side view of two shredding shafts insertable into the shredding device according to a second embodiment
  • Fig. 4a-c a schematic side view of a toothed disk for a comminution device according to the invention in three different embodiments according to the invention
  • Fig. 5 is a side view of a crushing device according to a sixth embodiment.
  • Fig. 6 is a side view of a crushing device according to a seventh embodiment.
  • a shredding device is designed as a two-shaft shredder 1 and has a gear section 2 and a shredding section 4.
  • gear section 2 both a drive motor 6 and a gear 8 are provided.
  • the gear 8 synchronizes the rotation of a first and a second shredding shaft 10, 12 and couples them to the drive motor 6.
  • the gear consists of two gears with different numbers of teeth (not shown) that mesh with each other. This creates an opposing rotary movement of the two shredding shafts 10, 12 about a first rotation axis 50 and a second rotation axis 60, which run at different speeds. Only the first shredding shaft 12 is directly coupled to the drive motor 6, the second shredding shaft 10 is driven exclusively via the gear 8.
  • the two shredding shafts 10, 12 are arranged in a housing 14 of the shredding section 4.
  • the housing 14 has an inlet opening 16 and an outlet opening 18, each of which can be connected to a pipe system or the like of a system.
  • the inlet opening 16 and the outlet opening 18 are opposite one another and are identical in their geometry. However, it should be understood that the inlet and outlet can also be different, e.g. in the case of so-called side rails.
  • the housing 14 is connected to the gear 8 via a flange 20.
  • the housing 14 can also be removed from the gear 8 via the flange 20.
  • the rotation axes 50, 60 are fixed to the housing 14.
  • Fig. 2 shows two crushing shafts 110, 112 which are in engagement with one another and which can be mounted in the crushing device according to Fig. 1.
  • Each of the two crushing shafts 110, 112 has a plurality of toothed disks 113a, b, c and 114a, b, c which are spaced axially from one another. Between each two toothed disks there is an intermediate space 115a, b, c and 116a, b, c. These intermediate spaces are delimited radially on the inside by a circumferential base surface 115a', b', c' and 116a', b', c'.
  • the toothed disks 113 of the first shredding shaft 110 are axially offset from the toothed disks 114 of the second shredding shaft 112 by an axial toothed disk thickness.
  • each toothed disk 113a, b, c of the first shredding shaft engages in a gap 116a, b, c of the second shredding shaft and conversely, each toothed disk 114a, b, c of the second shredding shaft engages in a gap 115a, b, c of the first shredding shaft.
  • Each toothed disk 113a, b, c, 114a, b, c has several teeth distributed over its circumference with radially outer tooth cutting edges. Fig.
  • the tooth cutting edges form an envelope that is defined by a continuous and harmonious, self-contained line that runs around these outer tooth cutting edges.
  • the envelope form a cylindrical surface or, in the side view shown, a circular line around the axis of rotation.
  • the first shredding shaft is mounted in the housing so as to rotate about an axis of rotation 150
  • the second shredding shaft is mounted in the housing so as to rotate about a second axis of rotation 160.
  • the envelope 230 of the tooth cutting edges 216a, b, c, ... is a cylindrical surface or circular line, but the central axis or the center point 231 of this cylindrical surface or circular line does not correspond to the axis of rotation 250, but is arranged eccentrically to it.
  • the circumferential base surface 240 of the gap is designed as a cylindrical surface, but the axis of this cylinder is congruent to the central axis 231 and is therefore also eccentric to the axis of rotation.
  • This embodiment of the toothed disk and the circumferential base surface of the gap is used in the two embodiments of Fig. 2 and Fig. 3. In the embodiment of Fig.
  • the toothed disks are arranged in the axial direction in such a way that the eccentricity with which the axis of the cylindrical envelope and the cylindrical circumferential base surface is related to the axis of rotation is arranged, the amount is constant along the entire shredding shaft, but the direction of the eccentricity changes along the axis of rotation, namely along a helical line. This results in a spiral arrangement of the toothed disks and the circumferential base surfaces along the axis of rotation for both shredding shafts.
  • the toothed disks of the shredding shafts all have the same number of teeth and the teeth are arranged at a consistent angle with respect to the axis of rotation on each of the toothed disks, resulting in an essentially straight line that only runs in a slight helical line due to the spiral eccentricity formed by the teeth in the axial direction.
  • the embodiment shown in Fig. 2 has an arrangement of the toothed disks and the circumferential base surfaces of the gaps that are not coordinated with one another in such a way that the distance between the envelopes of the toothed cutting edges and the circumferential base surfaces of the gap in which these toothed cutting edges engage remains constant during the rotation of the shredding shafts. Instead, this distance changes so much during the rotation of the shredding shafts that the toothed disks also come out of engagement with the gap of the other shaft, as can be seen in the left end area. As a result, the gap between the circumferential base surface of a gap and the teeth of a toothed disk engaging in it changes periodically between large and small during the rotation, which exerts a crushing and impact effect on the solids that promotes shredding.
  • toothed disks 1113a, 1114a according to the embodiment according to Fig. 4a with intermediate spaces 1115b, 1116a and circumferential base surfaces 1115a', 1116b' are also arranged on the two crushing shafts 1110, 1120, and the crushing shafts also rotate about rotation axes 1150, 1160 arranged in a fixed position in the crushing housing.
  • the eccentricity with which the cylinder axes of the envelopes of the tooth cutting edges and the circumferential base surfaces of the intermediate spaces are arranged around the rotation axis is also spiral, as in the embodiment according to Fig. 2.
  • Fig. 2 in the embodiment of Fig.
  • the toothed disks are arranged in such a way in an angular orientation that changes along the crushing shaft that a spiral course of the teeth results.
  • a spiral course of the teeth is advantageous for certain applications, for example when crushing particularly hard materials, as it enables simultaneous engagement of all or many teeth during one revolution of the shredding shafts is avoided and instead a staggered engagement of these tooth cutting edges in the solid material takes place.
  • Fig. 4b shows a second embodiment of a toothed disk.
  • the tooth cutting edges are designed alternately so that a tooth cutting edge 332a, b, c,... with a short radius always follows a tooth cutting edge with a long radius 331a, b, c,...
  • the envelope 330 of the tooth cutting edges is in this case formed by the outer tooth cutting edges 331a, b, c,... with a long radius.
  • This envelope 330 and the circumferential base surface 340 of the intermediate space are oval.
  • Fig. 4c shows a third embodiment of a toothed disk and a peripheral base surface, in which these are arranged as a rounded triangular shape.
  • the envelope 430 of the tooth cutting edges and the peripheral base surface 440 form a rounded, equilateral triangle, the center of which also lies in the rotation axis 450 of the comminution shaft.
  • Fig. 5 shows a third embodiment of the arrangement of toothed disks, circumferential base surfaces and comminution shafts in a comminution device according to the invention.
  • a total of four comminution shafts 510a-d are arranged, each of which rotates about a drive axis 580a, b, c, d.
  • Each of the comminution shafts has a plurality of toothed disks and corresponding intermediate spaces with circumferential base surfaces between the toothed disks.
  • toothed disks and the tooth cutting edges arranged thereon each form an envelope 530a, b, c, d, which forms a cylindrical surface around the drive axis 580a, b, c, d of the respective comminution shaft.
  • the circumferential base surface of the intermediate spaces of each of the four comminution shafts lies on a cylindrical surface around the drive axis 580 a, b, c, d of the respective comminution shaft.
  • Each of the four shredding shafts is coupled to a planetary gear 518 a, b, c, d of a planetary gear.
  • the planetary gear also has a sun gear and a ring gear in a known manner, which are arranged concentrically around a rotation axis 550.
  • the ring gear is fixed and the sun gear is driven by a drive motor into rotation about the rotation axis 550.
  • the four shredding shafts are also caused to rotate about the respective Drive axes and also rotate about the rotation axis 550.
  • each of the envelopes 530a, b, c, d around the tooth cutting edges and each of the circumferential base surfaces of the intermediate spaces does not have a cylindrical surface around the rotation axis 550 and an advantageous radial movement is exerted on a solid which rests radially on the comminution shafts.
  • Fig. 6 shows a seventh embodiment of the invention in which a first eccentrically rotating crushing shaft 610 is combined with a second, conventionally designed crushing shaft 620.
  • the first crushing shaft 610 rotates about a drive axis 680 and both the gap base areas and the envelopes of the toothed disks are each on a

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

Abstract

L'invention concerne un dispositif de broyage destiné à broyer des matériaux et comprenant un premier arbre de broyage doté d'une pluralité de disques dentés, qui sont montés axialement à une certaine distance les uns des autres le long d'un premier axe de rotation du premier arbre de broyage, chaque disque denté présentant plusieurs dents réparties sur la circonférence et munies de tranchants reposant radialement en direction de l'extérieur, qui se trouvent sur une enveloppante, et un espace intermédiaire, qui est délimité radialement vers l'intérieur par une surface de base périphérique d'espace intermédiaire, étant formé dans chaque cas entre deux disques dentés adjacents, le premier arbre de broyage étant monté rotatif autour du premier axe de rotation dans un carter de broyage, le dispositif de broyage se caractérisant en ce que les tranchants d'au moins un des disques dentés se trouvent sur au moins une enveloppante, qui ne forme pas de surface cylindrique autour du premier axe de rotation, et/ou qu'au moins une des surfaces de base périphériques d'espace intermédiaire du premier arbre de broyage ne formant pas de surface cylindrique autour du premier axe de rotation.
PCT/EP2023/082594 2022-11-21 2023-11-21 Dispositif de broyage pour des solides de dimensions importantes WO2024110484A1 (fr)

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DE202022106494.6 2022-11-21
DE202022106494.6U DE202022106494U1 (de) 2022-11-21 2022-11-21 Zerkleinerungsvorrichtung für größere Feststoffe

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Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7818838U1 (de) 1978-06-23 1979-11-08 Moco Maschinen- Und Apparatebau Gmbh & Co Kg, 6806 Viernheim Maschine zum zerkleinern von abfallstoffen
US4600158A (en) * 1981-06-30 1986-07-15 Matex Co., Ltd. Runner chopper
EP1072314A1 (fr) * 1999-07-22 2001-01-31 Sté Moditec Forme de la partie active d'un couteau pour broyeur à couteaux
DE69608918T2 (de) 1995-09-12 2001-02-08 Niro Ind As Horsens Zerkleinerungsvorrichtung
EP1172147A1 (fr) 2000-07-14 2002-01-16 New Activation Technology (NAT) AG Granulation
CN106914320A (zh) * 2017-03-28 2017-07-04 诸城市德创机械有限公司 一种动物肉尸撕碎机
CN110548578A (zh) * 2019-10-14 2019-12-10 湖北枝江峡江矿山机械有限责任公司 用于矿石破碎机的鼓组件及具有该鼓组件的矿石破碎机
DE102019120291A1 (de) 2019-07-26 2021-01-28 Takraf Gmbh Zerkleinerungsmaschinen zur Zerkleinerung von mineralischem oder nichtmineralischem Gut
EP3538278B1 (fr) 2016-11-14 2021-05-05 Hugo Vogelsang Maschinenbau GmbH Broyeur à deux arbres avec jeu de lames de coupe interchangeables et extrémités d'arbre détachables
WO2021245124A2 (fr) 2020-06-03 2021-12-09 Vogelsang Gmbh & Co. Kg Déchiqueteur à double arbre, à concept de maintenance horizontal
CN113926555A (zh) 2021-10-29 2022-01-14 中科深兰(福建)环境科技有限责任公司 一种用于粉碎的偏心轮机构固态废物处理装置及其使用方法

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7818838U1 (de) 1978-06-23 1979-11-08 Moco Maschinen- Und Apparatebau Gmbh & Co Kg, 6806 Viernheim Maschine zum zerkleinern von abfallstoffen
US4600158A (en) * 1981-06-30 1986-07-15 Matex Co., Ltd. Runner chopper
DE69608918T2 (de) 1995-09-12 2001-02-08 Niro Ind As Horsens Zerkleinerungsvorrichtung
EP1072314A1 (fr) * 1999-07-22 2001-01-31 Sté Moditec Forme de la partie active d'un couteau pour broyeur à couteaux
EP1172147A1 (fr) 2000-07-14 2002-01-16 New Activation Technology (NAT) AG Granulation
EP3538278B1 (fr) 2016-11-14 2021-05-05 Hugo Vogelsang Maschinenbau GmbH Broyeur à deux arbres avec jeu de lames de coupe interchangeables et extrémités d'arbre détachables
CN106914320A (zh) * 2017-03-28 2017-07-04 诸城市德创机械有限公司 一种动物肉尸撕碎机
DE102019120291A1 (de) 2019-07-26 2021-01-28 Takraf Gmbh Zerkleinerungsmaschinen zur Zerkleinerung von mineralischem oder nichtmineralischem Gut
CN110548578A (zh) * 2019-10-14 2019-12-10 湖北枝江峡江矿山机械有限责任公司 用于矿石破碎机的鼓组件及具有该鼓组件的矿石破碎机
WO2021245124A2 (fr) 2020-06-03 2021-12-09 Vogelsang Gmbh & Co. Kg Déchiqueteur à double arbre, à concept de maintenance horizontal
CN113926555A (zh) 2021-10-29 2022-01-14 中科深兰(福建)环境科技有限责任公司 一种用于粉碎的偏心轮机构固态废物处理装置及其使用方法

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