EP2098297B1 - Rotor and device for grinding feeder product - Google Patents

Rotor and device for grinding feeder product Download PDF

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Publication number
EP2098297B1
EP2098297B1 EP09002956.2A EP09002956A EP2098297B1 EP 2098297 B1 EP2098297 B1 EP 2098297B1 EP 09002956 A EP09002956 A EP 09002956A EP 2098297 B1 EP2098297 B1 EP 2098297B1
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EP
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Prior art keywords
rotor
discs
power transmission
rotor according
transmission elements
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EP09002956.2A
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German (de)
French (fr)
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EP2098297A2 (en
EP2098297A3 (en
Inventor
Hartmut Pallmann
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Pallmann Maschinenfabrik GmbH and Co KG
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Pallmann Maschinenfabrik GmbH and Co KG
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Publication of EP2098297A3 publication Critical patent/EP2098297A3/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • 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
    • B02C18/146—Disintegrating by knives or other cutting or tearing members which chop material into fragments with rotating knives within horizontal containers with a rotor comprising a plurality of axially contiguous disc-like segments each having at least one radially extending cutting element
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/02—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft
    • B02C13/04—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft with beaters hinged to the rotor; Hammer mills

Definitions

  • the invention relates to a rotor for comminuting feed material according to the preamble of patent claim 1 and to a device having such a rotor according to the preamble of patent claim 14.
  • the rotor is essentially composed of a shaft and rotor disks arranged thereon, over the circumference of which the comminution tools are distributed.
  • the crushing tools can be formed by knives, rigid or pendulum suspended hammers, shearing tools or the like.
  • the rotor is assigned a stator which is equipped with counter-blades, baffles or screen surfaces, or another rotor whose rotor disks interact with the rotor disks of the first rotor.
  • the feed material is fed radially to the rotor, where it is detected by the comminution tools and comminuted in cooperation with the stator tools or the second rotor.
  • the a generic device are diverse in nature and range from plastics of any kind on sheets, textiles and electronic waste to composite materials and scrap tires.
  • a large mechanical resistance is opposed to the rotor during the comminution operation, so that the transmission of power from the drive shaft to the rotor disks is of great importance.
  • a modular rotor structure with a certain number of rotatably mounted on the shaft rotor disks plays in view of the assembly of the rotor but also when replacing damaged or used rotor discs a large role, since the rotor can be broken down into smaller components, if necessary, on the one hand easier to handle and to replace the other targeted.
  • a rotor structure is especially used in conjunction with a frictionally generated Frictional connection between the drive shaft and rotor disks at the end requires that the driving force is transmitted safely and without slippage from one rotor disk to the next.
  • a device for crushing elastomers whose comminuting unit is formed by two rotors which are corrugated over their circumference.
  • the rotors are essentially each formed by a hollow cylinder whose axial ends are screwed to coaxial support disks, which in turn each sit rotationally fixed on a driven stub shaft.
  • the rotor thus has no continuous drive shaft.
  • a similarly constructed rotor is from the DE 199 28 034 A1 also known, in which instead of a continuous shaft only stub shafts are attached to the end faces of the rotor. Moreover, the rotor is formed by coaxially assembled discs, which are connected to each other axially via longitudinal latch.
  • the US 5,381,973 also discloses axial centering pins in the contact area of two adjacent rotor disks, which ensure that the individual rotor disks are seated in exactly the same position relative to one another on the drive shaft. This is important in the assembly of the rotor because the provided in the outer peripheral portion through holes must be exactly aligned axially so that later the waves can be easily inserted for pendulum suspension of the hammers. It is also proposed to replace the centering pins with temporary longitudinal rods until the rotor disks are finally connected to one another by weld seams.
  • a device for crushing of waste which has a horizontally disposed within a housing rotor.
  • the rotor consists of two solid cylindrical parts, which are non-rotatably mounted on a drive shaft and are combined by means of axial clamping rods to form a whole.
  • axial clamping rods In the lateral surface of the rotor depressions are arranged for the pivotable attachment of rackets, which get in the course of rotation, the crushing of the garbage.
  • the object of the invention is to improve known rotors and devices in view of the disadvantages described above, in particular, a rotor according to the invention should allow a compact design, a precise crushing and safe and economical operation.
  • the power transmission from the drive shaft to the rotor disks is generated by a frictional connection.
  • the available frictional surface and the contact pressure in the contact surface can be adjusted in this way by suitable design selection, the maximum transferable force.
  • the maximum transferable force corresponds to the force that does not cause any damage to the comminution device in the event of a sudden change in the speed of the rotor. If this force is exceeded, for example, if foreign matter in the feed material block the rotor, so it comes thanks to the invention even before damage to the rotor to a slip between the Rotor disks and the drive shaft. This has the enormous advantage for the operator of devices according to the invention to considerably reduce the risk of damage.
  • the invention additionally comprises force transmitting elements acting in the tangential direction and axially acting clamping elements to the drive torque in precise relative position of the rotor disks to each other from one rotor disk to the next Rotor disc to be transferred.
  • the frictional engagement elements of a device according to the invention are advantageously arranged in the interior of the outer rotor disks, so that a minimum overall length results in the axial direction, which overall is conducive to a compact construction of devices according to the invention.
  • drive shafts according to the invention can be dispensed with complementary form-fitting surfaces to achieve a positive connection between the drive shaft and rotor discs, it is possible according to the invention drive shafts simpler, faster and thus more economical to manufacture.
  • the frictional engagement elements consist of commercially available clamping sets. These therefore further contribute to the reduction of manufacturing costs.
  • the size of the forces to be transmitted can be preset.
  • the clamping elements acting in the axial direction are formed by a shaft nut which, when it is screwed onto the shaft, tensions the rotor disks against an annular stop or a further shaft nut at the other end of the shaft.
  • An especially preferred embodiment of the invention provides axial clamping anchors that penetrate the rotor disks in the axial direction and thus in the interior of the rotor lie. Since the clamping anchors can be countersunk in the anchoring region in the end faces of the rotor, a minimum length of the rotor is favored here, so that this embodiment can be combined in a special way with the above-mentioned clamping sets in order to achieve a compact design.
  • the power transmission elements each consist of a three-dimensional body, which is arranged in one of two adjacent rotor disks in the contact joint complementarily shaped cavity. In this way, a toothing of two rotor disks is achieved in order to enable the transmission of the drive torque.
  • the three-dimensional body can be formed, for example, by a bolt, a disk or a strip.
  • FIGS. 1a . 2a and 2b show a first embodiment of a rotor 1 according to the invention, for example, is suitable for effecting the comminution of feed material of various kinds within a shredder or a granulator.
  • a suitable for the use of the rotor 1 device is for example in the DE 102006056542 A1 whose contents are to be considered by reference as having been disclosed.
  • FIG. 1a shown rotor 1 has a continuous drive shaft 2 with a longitudinal axis 3, the free ends are intended to be rotatably supported in axle bearings of a device, not shown.
  • the drive shaft 2 is acted upon by a drive torque for generating a rotational movement.
  • the end faces 5 are under contact with each other.
  • the rotor disks 4 have a circular shape, with a central opening 6, which corresponds approximately to the outer diameter of the drive shaft 2 and thus allows the seat of the rotor disks 4 on the shaft 2.
  • the outer circumference 7 of the rotor discs 4 is provided with not shown processing tools, which may be formed for example of knives, strips, checker plates, fangs, shearing tools, pendulum or rigid hammers and the like.
  • FIG. 1a It can be seen that the individual rotor discs 4 are axially clamped together via a plurality of tie rods 8 to form a rigid unit, wherein the tie rods 8 are arranged axially parallel in a uniform circumferential distance on a circumferential circle lying concentrically to the longitudinal axis 3.
  • the radial distance of the tie rods 8 to the longitudinal axis 3 may be such that the tie rods 8 are located centrally between the edge of the opening 6 and the outer periphery 7.
  • the tie rods 8 are in the outer half of the rotor disks 4.
  • the necessary for generating the clamping force clamping nuts 9 lie completely in recesses on the rotor end faces 10th
  • FIG. 1b shows that the inner rotor discs 4 'may also be formed annular disc-shaped with a large central opening 6', that the rotor discs 4 'only with their flat end faces 5' together and without direct contact with the drive shaft 2.
  • Such a rotor 1 draws through material and weight savings and easier assembly.
  • force transmission elements are respectively arranged in the contact joints of two rotor disks 4, 4'.
  • FIGS. 3a to 3c show two different embodiments of suitable power transmission elements.
  • the force transmission elements of holes 11 are formed, which are introduced from the end faces 5, 5 'in the axial direction in the rotor disks 4, 4'.
  • the holes 11 of two adjacent rotor disks 4, 4 ' are axially opposite.
  • bolts 12 are inserted form-fitting as power transmission elements.
  • the power transmission elements according to FIG. 3b consist of circular recesses 13 in the end faces 5, 5 'of the rotor disks 4, 4', which in turn are axially opposite each other in pairs.
  • the frictional connection is completed by means of disks 12, which completely completes the cavity formed by two recesses 13 fill out.
  • the disks 12 can be slightly tapered from the center plane, starting at their free end, in order to facilitate assembly or disassembly.
  • the power transmission takes place via the peripheral surfaces of the recesses and discs, which cooperate for this purpose.
  • FIG. 2b A possible arrangement of the force transmission elements with respect to the longitudinal axis 3 is made Fig. 2b seen.
  • the power transmission elements can be located with the tie rods 8 on a circumferential circle and each can be arranged centrally between two tie rods 8.
  • the force transmission elements consist of annular grooves in the end faces 5, 5 ', which cooperate with complementary shaped rings.
  • the advantage of this variant lies in the possibility of being able to arrange the annular grooves and rings in each case concentrically around a tie rod 8, which results in a very space-saving design, which is particularly important for rotors with small diameters.
  • the force transmission elements consist of radially extending grooves in the end face of a rotor disk, engage in the complementarily shaped radially extending strips in the associated end face of an adjacent rotor disk.
  • FIG. 4a shows the relevant area in a partial section.
  • the rotor disks 4 each have a recess 16 in the region of the opening 6 starting from the rotor end side 10.
  • the recess 16 is for receiving one or determined a plurality of clamping sets 15.
  • Each clamping set 15 comprises a pressure sleeve 17 with an outer pressure ring 18, which rests against the rotor disk 4 and a radially spaced inner pressure ring 19, which rests on the circumference of the drive shaft 2.
  • Both pressure rings 18 and 19 have over their axial length a conically thickened in the central region wall, so that there is a double concave annular space.
  • FIG. 4b shown embodiment of a rotor 1 differs from the previously described only by the use of two clamping sets 15, which are arranged one behind the other in the axial direction.
  • two clamping sets 15 By using a plurality of clamping sets 15, it is possible to increase the maximum transmissible driving force from the drive shaft 2 to the rotor disk 4.

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

Description

Die Erfindung betrifft einen Rotor zum Zerkleinern von Aufgabegut gemäß dem Oberbegriff des Patentanspruchs 1 sowie eine Vorrichtung mit einem solchen Rotor gemäß dem Oberbegriff des Patentanspruchs 14.The invention relates to a rotor for comminuting feed material according to the preamble of patent claim 1 and to a device having such a rotor according to the preamble of patent claim 14.

Bei der Zerkleinerung von Stoffen haben sich Vorrichtungen mit einer einen Rotor umfassenden Zerkleinerungseinheit bewährt. Der Rotor setzt sich im Wesentlichen aus einer Welle und darauf angeordneten Rotorscheiben zusammen, über deren Umfang die Zerkleinerungswerkzeuge verteilt sind. Die Zerkleinerungswerkzeuge können dabei von Messern, starren oder pendelnd aufgehängten Hämmern, Scherwerkzeugen oder dergleichen gebildet sein. Im Regelfall ist dem Rotor ein Stator zugeordnet, der mit Gegenmessern, Prallflächen oder Siebflächen ausgestattet ist oder ein weiterer Rotor, dessen Rotorscheiben mit den Rotorscheiben des ersten Rotors in Interaktion treten. Das Aufgabegut wird dem Rotor radial aufgegeben, wo es von den Zerkleinerungswerkzeugen erfasst und im Zusammenwirken mit den Statorwerkzeugen oder dem zweiten Rotor zerkleinert wird.In the comminution of substances, devices with a comminution unit comprising a rotor have proven themselves. The rotor is essentially composed of a shaft and rotor disks arranged thereon, over the circumference of which the comminution tools are distributed. The crushing tools can be formed by knives, rigid or pendulum suspended hammers, shearing tools or the like. As a rule, the rotor is assigned a stator which is equipped with counter-blades, baffles or screen surfaces, or another rotor whose rotor disks interact with the rotor disks of the first rotor. The feed material is fed radially to the rotor, where it is detected by the comminution tools and comminuted in cooperation with the stator tools or the second rotor.

Die einer gattungsgemäßen Vorrichtung aufgebbaren Materialien sind vielfältiger Natur und reichen von Kunststoffen jeglicher Art über Bleche, Textilien und Elektronikschrott bis hin zu Verbundmaterialien und Altreifen. In Abhängigkeit von der Beschaffenheit des Aufgabeguts in Größe, Form und Materialeigenschaften wird dem Rotor während des Zerkleinerungsbetriebs ein großer mechanischer Widerstand entgegengesetzt, so dass der Kraftübertragung von der Antriebswelle auf die Rotorscheiben eine große Bedeutung zukommt.The a generic device aufbar materials are diverse in nature and range from plastics of any kind on sheets, textiles and electronic waste to composite materials and scrap tires. Depending on the nature of the feed material in size, shape and material properties, a large mechanical resistance is opposed to the rotor during the comminution operation, so that the transmission of power from the drive shaft to the rotor disks is of great importance.

Ein modularer Rotoraufbau mit einer bestimmten Anzahl an lösbar auf der Welle befestigten Rotorscheiben spielt im Hinblick auf den Zusammenbau der Rotors aber auch beim Austausch beschädigter oder verbrauchter Rotorscheiben eine große Rolle, da der Rotor bei Bedarf in kleinere Komponenten zerlegt werden kann, die sich zum einen leichter handhaben und zum anderen gezielt ersetzen lassen. Ein solcher Rotoraufbau setzt jedoch speziell in Verbindung mit einem durch Reibschluss erzeugten Kraftschluss zwischen Antriebswelle und endseitigen Rotorscheiben voraus, dass die Antriebskraft sicher und ohne Schlupf von einer Rotorscheibe auf die nächste übertragen wird.A modular rotor structure with a certain number of rotatably mounted on the shaft rotor disks plays in view of the assembly of the rotor but also when replacing damaged or used rotor discs a large role, since the rotor can be broken down into smaller components, if necessary, on the one hand easier to handle and to replace the other targeted. However, such a rotor structure is especially used in conjunction with a frictionally generated Frictional connection between the drive shaft and rotor disks at the end requires that the driving force is transmitted safely and without slippage from one rotor disk to the next.

Aus der WO 2006/064483 A2 ist eine Vorrichtung zum Zerkleinern von Elastomeren bekannt, deren Zerkleinerungseinheit von zwei Rotoren gebildet wird, die über ihren Umfang mit einer Riffelung versehen sind. Die Rotoren werden im Wesentlichen jeweils von einem Hohlzylinder gebildet, dessen axiale Enden mit koaxialen Tragscheiben verschraubt sind, die wiederum jeweils auf einem angetriebenen Wellenstummel drehfest sitzen. Der Rotor besitzt somit keine durchgehende Antriebswelle.From the WO 2006/064483 A2 For example, a device for crushing elastomers is known, whose comminuting unit is formed by two rotors which are corrugated over their circumference. The rotors are essentially each formed by a hollow cylinder whose axial ends are screwed to coaxial support disks, which in turn each sit rotationally fixed on a driven stub shaft. The rotor thus has no continuous drive shaft.

Ein ähnlich aufgebauter Rotor ist aus der DE 199 28 034 A1 bekannt, bei dem anstelle einer durchgehenden Welle ebenfalls nur Wellenstummel an den Stirnseiten des Rotors angebracht sind. Im übrigen ist der Rotor von koaxial zusammengefügten Scheiben gebildet, die axial über Längsriegel miteinander verbunden sind.A similarly constructed rotor is from the DE 199 28 034 A1 also known, in which instead of a continuous shaft only stub shafts are attached to the end faces of the rotor. Moreover, the rotor is formed by coaxially assembled discs, which are connected to each other axially via longitudinal latch.

Diese Konstruktionsarten eines Rotors erweist sich immer dann als nachteilig, wenn aufgrund gegebener Platzverhältnisse auf eine axial gedrungene Bauweise Wert gelegt wird. Durch das stirnseitige Ansetzen der Tragscheiben an den Rotor wird dessen Länge vergrößert, ohne einen Zugewinn an der für die Zerkleinerung wirksamen Arbeitsfläche zu erhalten. Darüber hinaus ist eine solche Konstruktion verhältnismäßig aufwändig in der Herstellung und Montage und führt bei Herstellungs- und Montageungenauigkeiten schnell zu einer Unwucht des Rotors und Einbußen bei der Rundlaufgenauigkeit. Hinzu kommt, dass es bei einer Überlastung des Rotors, beispielsweise bei dessen Blockieren infolge unbeabsichtigter Fremdkörperaufgabe, zu einer erheblichen Beschädigung der Zerkleinerungseinheit kommt, da zwischen der Antriebsseite und dem Rotor ein absoluter Kraftschluss hergestellt ist.This type of construction of a rotor always proves to be disadvantageous if given due to space constraints on an axially compact design value. By the frontal application of the support disks to the rotor whose length is increased without obtaining an increase in the working surface for comminuting effective. In addition, such a construction is relatively expensive to manufacture and assembly and leads to manufacturing and assembly inaccuracies quickly to an imbalance of the rotor and losses in the concentricity. In addition, it comes in an overload of the rotor, for example, when blocking due to unintentional foreign object task, to a significant damage to the crushing unit, as between the drive side and the rotor an absolute adhesion is established.

Eine alternative Lösung zur Übertragung der Antriebskraft von der Welle auf die Scheibe ist in der DE 39 30 041 A1 offenbart. Dort ist eine durchgehende Antriebswelle im Bereich des Sitzes der Rotorscheiben im Querschnitt sechskantförmig ausgebildet. Die Scheiben weisen eine dazu komplementäre zentrische Öffnung auf, so dass über den Formschluss eine Kraftübertragung von der Welle auf die Rotorscheibe gewährleistet ist. Eine andere Art des Formschlusses zur Kraftübertragung ist aus der DE 94 22 104 U1 bekannt. Die dort beschriebene Ausführungsform besitzt eine Antriebswelle, die an ihrem Außenumfang Axialnuten aufweist, die mit korrespondierenden Axialnuten am Innenumfang der einzelnen Scheiben einen zusammengesetzten Querschnitt ergeben, in den eine Passfeder eingesetzt ist.An alternative solution for transmitting the driving force from the shaft to the disc is in the DE 39 30 041 A1 disclosed. There is a continuous drive shaft in the region of the seat of the rotor disks in cross section hexagonal shaped. The discs have a complementary centric opening, so that over the positive connection a power transmission from the shaft is ensured on the rotor disk. Another type of positive connection for power transmission is from the DE 94 22 104 U1 known. The embodiment described therein has a drive shaft which has axial grooves on its outer circumference, which, with corresponding axial grooves on the inner circumference of the individual disks, result in an assembled cross section into which a feather key is inserted.

Auch diese beiden Lösungen führen zu einem absoluten Kraftschluss zwischen Antriebswelle und Rotorscheiben, so dass bei Überlastung der Vorrichtung eine Beschädigung der Zerkleinerungseinheit zu befürchten ist. Hinzu kommt, dass die Ausbildung passgenauer Nuten an Welle und Rotorscheiben einen erheblichen Mehraufwand bei der Herstellung und Montage bedeutet.These two solutions also lead to an absolute adhesion between the drive shaft and rotor disks, so that damage to the shredding unit is to be feared in case of overloading the device. In addition, the formation of precise grooves on the shaft and rotor discs means a significant overhead in the production and assembly.

Darüber hinaus ist es bekannt über einen Reibschluss die Antriebskraft aus der Antriebswelle auf die Rotorscheiben zu übertragen. Sowohl die EP 0 019 542 A1 als auch die US 5,381,973 offenbaren zu diesem Zweck Reib- oder Klemmeinrichtungen, die jeweils in einer ringförmigen Aufnahme an der Außenseite der stirnseitigen Rotorscheiben angeordnet sind und dabei die Antriebswelle unter Herstellung eines Reibschlusses umgreifen. Zur weiteren Kraftübertragung des Antriebsmoments auf die inneren Rotorscheiben offenbaren beide Dokumenten, dass benachbarte Rotorscheiben miteinander verschweißt sind, das heißt alle Rotorscheiben sind unlösbar miteinander verbunden und bilden so eine starre Rotoreinheit.In addition, it is known via a frictional connection to transmit the driving force from the drive shaft to the rotor discs. Both the EP 0 019 542 A1 as well as the US 5,381,973 disclose for this purpose friction or clamping devices, which are each arranged in an annular receptacle on the outer side of the front-side rotor discs and thereby engage around the drive shaft to produce a frictional engagement. For further transmission of the drive torque to the inner rotor discs, both documents disclose that adjacent rotor discs are welded together, that is, all rotor discs are permanently connected to each other and thus form a rigid rotor unit.

Die US 5,381,973 offenbart zudem axiale Zentrierstifte im Kontaktbereich zweier benachbarter Rotorscheiben, die sicherstellen, dass die einzelnen Rotorscheiben in exakt gleicher Lage zueinander auf der Antriebswelle sitzen. Dies ist bei der Montage des Rotors deshalb von Bedeutung, weil die im äußeren Umfangsbereich vorgesehenen Durchgangsbohrungen exakt axial fluchtend verlaufen müssen, damit später die Wellen zur pendelnden Aufhängung der Hämmer problemlos eingeschoben werden können. Weiter wird vorgeschlagen, die Zentrierstifte durch temporäre Längsstäbe zu ersetzen bis die Rotorscheiben durch Schweißnähte endgültig miteinander verbunden sind.The US 5,381,973 also discloses axial centering pins in the contact area of two adjacent rotor disks, which ensure that the individual rotor disks are seated in exactly the same position relative to one another on the drive shaft. This is important in the assembly of the rotor because the provided in the outer peripheral portion through holes must be exactly aligned axially so that later the waves can be easily inserted for pendulum suspension of the hammers. It is also proposed to replace the centering pins with temporary longitudinal rods until the rotor disks are finally connected to one another by weld seams.

Das Verschweißen der Rotorscheiben untereinander führt zwar zu einer sicheren Kraftübertragung des Antriebsmoments in alle Rotorscheiben, hat jedoch den Nachteil, dass alle Rotorscheiben eine starre unlösbare Rotoreinheit bilden, die bei der Demontage oder im Falle von Reparaturen nur schwer zu handhaben ist.Although the welding of the rotor disks with each other leads to a safe power transmission of the drive torque in all rotor disks, but has the disadvantage that all rotor disks form a rigid permanent rotor unit, which is difficult to handle during disassembly or repairs.

Aus der DE 2 146 362 A1 ist schließlich eine Vorrichtung zum Zerkleinern vom Müll bekannt, die einen innerhalb eines Gehäuses horizontal angeordneten Rotor aufweist. Der Rotor besteht aus zwei massiven zylindrischen Teilen, die drehfest auf einer Antriebswelle sitzen und mittels axialer Spannstäbe zu einem Ganzen zusammengefasst sind. In der Mantelfläche des Rotors sind Vertiefungen zur schwenkbaren Befestigung von Schlägern angeordnet, die im Zuge der Rotation die Zerkleinerung des Mülls besorgen.From the DE 2 146 362 A1 Finally, a device for crushing of waste is known, which has a horizontally disposed within a housing rotor. The rotor consists of two solid cylindrical parts, which are non-rotatably mounted on a drive shaft and are combined by means of axial clamping rods to form a whole. In the lateral surface of the rotor depressions are arranged for the pivotable attachment of rackets, which get in the course of rotation, the crushing of the garbage.

Vor diesem Hintergrund besteht die Aufgabe der Erfindung darin, bekannte Rotoren und Vorrichtungen im Hinblick auf die oben beschriebenen Nachteile zu verbessern, insbesondere soll ein erfindungsgemäßer Rotor einen kompakten Aufbau, eine präzise Zerkleinerung und einen sicheren und wirtschaftlichen Betrieb ermöglichen.Against this background, the object of the invention is to improve known rotors and devices in view of the disadvantages described above, in particular, a rotor according to the invention should allow a compact design, a precise crushing and safe and economical operation.

Diese Aufgabe wird durch einen Rotor mit den Merkmalen des Patentanspruchs 1 und eine Vorrichtung mit den Markmalen des Patentanspruchs 14 gelöst.This object is achieved by a rotor having the features of patent claim 1 and a device having the features of patent claim 14.

Vorteilhafte Ausführungsformen ergeben sich aus den Unteransprüchen.Advantageous embodiments will be apparent from the dependent claims.

Das Wesen der Erfindung liegt in der Kombination der im kennzeichnenden Teil des unabhängigen Patentanspruchs beschriebenen Konstruktionsmerkmale, die durch gegenseitige Einflussnahme in ihrem Zusammenwirken zu einem unerwartet präzise arbeitenden, gegen Überlastung geschützten und in seiner Bauform extrem kompakten Rotor führen, der dabei dennoch für seine Montage, Demontage, Reparatur oder Wartung einfach in seine Bestandteile zerlegbar ist.The essence of the invention lies in the combination of the design features described in the characterizing part of the independent claim, which lead by mutual influence in their interaction to an unexpectedly precise working, protected against overload and extremely compact in its design rotor, while still for its assembly, Disassembly, repair or maintenance is easily dismantled into its components.

Die Kraftübertragung von der Antriebswelle auf die Rotorscheiben wird durch einen Reibschluss erzeugt. In Abhängigkeit der am Reibschluss beteiligten Materialpaarung, der zur Verfügung stehenden Reibschlussfläche sowie des Anpressdrucks in der Kontaktfläche kann auf diese Weise durch geeignete konstruktive Auswahl die maximal übertragbare Kraft eingestellt werden. Die maximal übertragbare Kraft entspricht der Kraft, die bei plötzlicher Drehzahländerung des Rotors noch zu keinem Schaden an der Zerkleinerungsvorrichtung führt. Wird diese Kraft überschritten, beispielsweise wenn Fremdkörper im Aufgabegut den Rotor blockieren, so kommt es Dank der Erfindung noch bevor Schäden am Rotor entstehen zu einem Schlupf zwischen den Rotorscheiben und der Antriebswelle. Das hat für den Betreiber erfindungsgemäßer Vorrichtungen den enormen Vorteil, das Schadensrisiko erheblich zu reduzieren.The power transmission from the drive shaft to the rotor disks is generated by a frictional connection. Depending on the material pairing involved in the frictional engagement, The available frictional surface and the contact pressure in the contact surface can be adjusted in this way by suitable design selection, the maximum transferable force. The maximum transferable force corresponds to the force that does not cause any damage to the comminution device in the event of a sudden change in the speed of the rotor. If this force is exceeded, for example, if foreign matter in the feed material block the rotor, so it comes thanks to the invention even before damage to the rotor to a slip between the Rotor disks and the drive shaft. This has the enormous advantage for the operator of devices according to the invention to considerably reduce the risk of damage.

Da bei einem erfindungsgemäßen Rotor nicht alle Rotorscheiben im Reibschluss mit der Antriebswelle stehen, sondern nur die rotorendseitigen, umfasst die Erfindung zusätzlich in tangentialer Richtung wirkende Kraftübertragungselemente und axial wirkende Spannelemente, um das Antriebsmoment in präziser relativer Lage der Rotorscheiben zueinander von einer Rotorscheibe auf die nächste Rotorscheibe überzuleiten.Since in a rotor according to the invention not all the rotor disks are in frictional engagement with the drive shaft, but only the rotor end side, the invention additionally comprises force transmitting elements acting in the tangential direction and axially acting clamping elements to the drive torque in precise relative position of the rotor disks to each other from one rotor disk to the next Rotor disc to be transferred.

Die Reibschlusselemente einer erfindungsgemäßen Vorrichtung sind vorteilhafterweise im Inneren der äußeren Rotorscheiben angeordnet, so dass sich in axialer Richtung eine minimale Baulänge ergibt, was insgesamt einer kompakten Bauweise erfindungsgemäßer Vorrichtungen förderlich ist.The frictional engagement elements of a device according to the invention are advantageously arranged in the interior of the outer rotor disks, so that a minimum overall length results in the axial direction, which overall is conducive to a compact construction of devices according to the invention.

Da bei erfindungsgemäßen Antriebswellen auf komplementär ausgebildete Formschlussflächen zur Erzielung eines Formschlusses zwischen Antriebswelle und Rotorscheiben verzichtet werden kann, ist es möglich erfindungsgemäße Antriebswellen einfacher, schneller und damit wirtschaftlicher herzustellen.Since in drive shafts according to the invention can be dispensed with complementary form-fitting surfaces to achieve a positive connection between the drive shaft and rotor discs, it is possible according to the invention drive shafts simpler, faster and thus more economical to manufacture.

Gemäß einer bevorzugten Ausführungsform der Erfindung bestehen die Reibschlusselemente aus im Handel frei erhältlichen Spannsätzen. Diese tragen daher weiter zur Reduzierung der Herstellkosten bei. Durch die Verwendung mehrerer in axialer Richtung hintereinander angeordneter Spannsätze kann dabei die Größe der zu übertragenden Kräfte voreingestellt werden.According to a preferred embodiment of the invention, the frictional engagement elements consist of commercially available clamping sets. These therefore further contribute to the reduction of manufacturing costs. By using a plurality of clamping sets arranged one behind the other in the axial direction, the size of the forces to be transmitted can be preset.

In einer einfachen Ausführungsform der Erfindung werden die in axialer Richtung wirkenden Spannelemente von einer Wellenmutter gebildet, die bei ihrem Aufschrauben auf die Welle die Rotorscheiben gegen einen ringförmigen Anschlag oder eine weitere Wellenmutter am anderen Ende der Welle spannt. Eine demgegenüber besonders bevorzugte Ausführungsform der Erfindung sieht axiale Spannanker vor, die die Rotorscheiben in axialer Richtung durchdringen und somit im Inneren des Rotors liegen. Da die Spannanker im Verankerungsbereich in den Stirnseiten des Rotors versenkt sein können, wird auch hier eine minimale Baulänge des Rotors begünstigt, so dass sich diese Ausführungsform in besonderer Weise mit den vorstehend erwähnten Spannsätzen kombinieren lässt, um eine kompakte Bauweise zu erreichen.In a simple embodiment of the invention, the clamping elements acting in the axial direction are formed by a shaft nut which, when it is screwed onto the shaft, tensions the rotor disks against an annular stop or a further shaft nut at the other end of the shaft. An especially preferred embodiment of the invention provides axial clamping anchors that penetrate the rotor disks in the axial direction and thus in the interior of the rotor lie. Since the clamping anchors can be countersunk in the anchoring region in the end faces of the rotor, a minimum length of the rotor is favored here, so that this embodiment can be combined in a special way with the above-mentioned clamping sets in order to achieve a compact design.

Die Kraftübertragungselemente bestehen jeweils aus einem dreidimensionalen Körper, der in einem von zwei benachbarten Rotorscheiben in deren Kontaktfuge komplementär geformten Hohlraum angeordnet ist. Auf diese Weise wird eine Verzahnung zweier Rotorscheiben erreicht, um die Übertragung des Antriebsmoments zu ermöglichen. Der dreidimensionale Körper kann beispielsweise von einem Bolzen, einer Scheibe oder einer Leiste gebildet sein.The power transmission elements each consist of a three-dimensional body, which is arranged in one of two adjacent rotor disks in the contact joint complementarily shaped cavity. In this way, a toothing of two rotor disks is achieved in order to enable the transmission of the drive torque. The three-dimensional body can be formed, for example, by a bolt, a disk or a strip.

Die Erfindung wird nachstehend anhand eines in den Zeichnungen dargestellten Ausführungsbeispiels näher erläutert. Es zeigt

Fig. 1a
einen Längsschnitt durch eine erste Ausführungsform eines erfindungsgemäßen Rotors,
Fig. 1b
einen Längsschnitt durch eine zweite Ausführungsform eines erfindungsgemäßen Rotors,
Fig. 2a
eine Ansicht in axialer Richtung auf den in Fig. 1a dargestellten Rotor,
Fig 2b
einen Querschnitt durch den in Fig. 1a dargestellten Rotor entlang der Line II - 11,
Fig. 3a
einen Teilschnitt im Kontaktbereich zweier Rotorscheiben mit einer ersten Ausführungsform von Kraftübertragungselementen,
Fig. 3b
einen Teilschnitt im Anschlussbereich zweier Rotorscheiben mit einer zweiten Ausführungsform von Kraftübertragungselementen,
Fig. 3c
einen Teilschnitt durch die in Fig. 3b dargestellten Kraftübertragungselemente entlang der Linie III - III,
Fig. 4a
einen Teilschnitt durch den Kraftübertragungsbereich zwischen Rotorscheibe und Antriebswelle gemäß einer ersten Ausführungsform und
Fig. 4b
einen Teilschnitt durch den Kraftübertragungsbereich zwischen Rotorscheibe und Antriebswelle gemäß einer zweiten Ausführungsform.
The invention will be explained in more detail with reference to an embodiment shown in the drawings. It shows
Fig. 1a
a longitudinal section through a first embodiment of a rotor according to the invention,
Fig. 1b
a longitudinal section through a second embodiment of a rotor according to the invention,
Fig. 2a
a view in the axial direction on the in Fig. 1a represented rotor,
Fig. 2b
a cross section through the in Fig. 1a represented rotor along the line II - 11,
Fig. 3a
a partial section in the contact region of two rotor disks with a first embodiment of force transmission elements,
Fig. 3b
a partial section in the connection region of two rotor disks with a second embodiment of force transmission elements,
Fig. 3c
a partial section through the in Fig. 3b shown power transmission elements along the line III - III,
Fig. 4a
a partial section through the power transmission area between the rotor disk and drive shaft according to a first embodiment and
Fig. 4b
a partial section through the power transmission area between the rotor disk and drive shaft according to a second embodiment.

Die Figuren 1a, 2a und 2b zeigen eine erste Ausführungsform eines erfindungsgemäßen Rotors 1, der beispielsweise dazu geeignet ist, innerhalb eines Shredders oder einer Schneidmühle die Zerkleinerung von Aufgabegut unterschiedlichster Art zu bewirken. Eine für den Einsatz des Rotors 1 geeignete Vorrichtung ist beispielsweise in der DE 102006056542 A1 beschrieben, deren Inhalt durch Bezugnahme als mit offenbart anzusehen ist.The FIGS. 1a . 2a and 2b show a first embodiment of a rotor 1 according to the invention, for example, is suitable for effecting the comminution of feed material of various kinds within a shredder or a granulator. A suitable for the use of the rotor 1 device is for example in the DE 102006056542 A1 whose contents are to be considered by reference as having been disclosed.

Der in Figur 1a dargestellte Rotor 1 besitzt eine durchgehende Antriebswelle 2 mit Längsachse 3, deren freie Enden dazu bestimmt sind, in Achslagern einer nicht dargestellten Vorrichtung drehbar gehalten zu werden. Im Betrieb einer erfindungsgemäßen Vorrichtung wird die Antriebswelle 2 mit einem Antriebsmoment zur Erzeugung einer Rotationsbewegung beaufschlagt. Im mittleren Bereich sitzen auf der Antriebswelle 2 in koaxialer Anordnung hintereinander fünf Rotorscheiben 4, deren Stirnseiten 5 unter Kontakt aneinander liegen.The in FIG. 1a shown rotor 1 has a continuous drive shaft 2 with a longitudinal axis 3, the free ends are intended to be rotatably supported in axle bearings of a device, not shown. During operation of a device according to the invention, the drive shaft 2 is acted upon by a drive torque for generating a rotational movement. In the central region sit on the drive shaft 2 in a coaxial arrangement one behind the other five rotor disks 4, the end faces 5 are under contact with each other.

Wie aus den Figuren 2a und 2b ersichtlich, weisen die Rotorscheiben 4 eine kreisförmige Gestalt auf, mit einer zentralen Öffnung 6, die in etwa dem Außendurchmesser der Antriebswelle 2 entspricht und somit den Sitz der Rotorscheiben 4 auf der Welle 2 ermöglicht. Der Außenumfang 7 der Rotorscheiben 4 ist mit nicht dargestellten Bearbeitungswerkzeugen versehen, die beispielsweise von Messern, Leisten, Riffelplatten, Reißzähnen, Scherwerkzeugen, pendelnden oder starren Hämmern und dergleichen gebildet sein können.Like from the FIGS. 2a and 2b As can be seen, the rotor disks 4 have a circular shape, with a central opening 6, which corresponds approximately to the outer diameter of the drive shaft 2 and thus allows the seat of the rotor disks 4 on the shaft 2. The outer circumference 7 of the rotor discs 4 is provided with not shown processing tools, which may be formed for example of knives, strips, checker plates, fangs, shearing tools, pendulum or rigid hammers and the like.

In Figur 1a ist zu erkennen, dass die einzelnen Rotorscheiben 4 über mehrere Zuganker 8 zu einer starren Einheit axial zusammengespannt sind, wobei die Zuganker 8 achsparallel in einheitlichem Umfangsabstand auf einem konzentrisch zur Längsachse 3 liegenden Umfangskreis angeordnet sind. Der radiale Abstand der Zuganker 8 zur Längsachse 3 kann derart sein, dass die Zuganker 8 mittig zwischen dem Rand der Öffnung 6 und dem Außenumfang 7 liegen. Bei einem größeren radialen Abstand liegen die Zuganker 8 in der äußeren Hälfte der Rotorscheiben 4. Die zur Erzeugung der Spannkraft notwendigen Spannmuttern 9 liegen vollständig in Vertiefungen an den Rotorstirnseiten 10.In FIG. 1a It can be seen that the individual rotor discs 4 are axially clamped together via a plurality of tie rods 8 to form a rigid unit, wherein the tie rods 8 are arranged axially parallel in a uniform circumferential distance on a circumferential circle lying concentrically to the longitudinal axis 3. The radial distance of the tie rods 8 to the longitudinal axis 3 may be such that the tie rods 8 are located centrally between the edge of the opening 6 and the outer periphery 7. At a greater radial distance, the tie rods 8 are in the outer half of the rotor disks 4. The necessary for generating the clamping force clamping nuts 9 lie completely in recesses on the rotor end faces 10th

Aus Figur 1b geht hervor, dass die inneren Rotorscheiben 4' auch ringscheibenförmig ausgebildet sein können mit einer so großen zentrischen Öffnung 6', dass die Rotorscheiben 4' lediglich mit ihren planen Stirnseiten 5' aneinander liegen und ohne direkten Kontakt zur Antriebswelle 2. Ein solcher Rotor 1 zeichnet sich durch Material- und Gewichtseinsparungen sowie eine leichtere Montage aus.Out FIG. 1b shows that the inner rotor discs 4 'may also be formed annular disc-shaped with a large central opening 6', that the rotor discs 4 'only with their flat end faces 5' together and without direct contact with the drive shaft 2. Such a rotor 1 draws through material and weight savings and easier assembly.

Zur Sicherstellung der Kraftübertragung zwischen benachbarten Rotorscheiben 4, 4' während des Zerkleinerungsbetriebs, sind in den Kontaktfugen zweier Rotorscheiben 4, 4' jeweils Kraftübertragungselemente angeordnet.To ensure the transmission of force between adjacent rotor disks 4, 4 'during the comminution operation, force transmission elements are respectively arranged in the contact joints of two rotor disks 4, 4'.

Die Figuren 3a bis 3c zeigen zwei verschiedene Ausführungsformen geeigneter Kraftübertragungselemente. In Fig. 3a werden die Kraftübertragungselementen von Bohrungen 11 gebildet, die ausgehend von den Stirnseiten 5, 5' in axialer Richtung in die Rotorscheiben 4, 4' eingebracht sind. Dabei liegen die Bohrungen 11 zweier benachbarter Rotorscheiben 4, 4' sich axial gegenüber. In den durch die Bohrungen 8 gebildeten Gesamthohlraum sind Bolzen 12 als Kraftübertragungselemente formschlüssig eingesetzt.The FIGS. 3a to 3c show two different embodiments of suitable power transmission elements. In Fig. 3a the force transmission elements of holes 11 are formed, which are introduced from the end faces 5, 5 'in the axial direction in the rotor disks 4, 4'. The holes 11 of two adjacent rotor disks 4, 4 'are axially opposite. In the overall cavity formed by the holes 8 bolts 12 are inserted form-fitting as power transmission elements.

Die Kraftübertragungselemente gemäß Figur 3b bestehen aus kreisförmigen Vertiefungen 13 in den Stirnflächen 5, 5' der Rotorscheiben 4, 4', die sich wiederum paarweise axial gegenüberliegen. Der Kraftschluss wird mit Hilfe von Scheiben 12 vervollständigt, die den von zwei Vertiefungen 13 gebildeten Hohlraum vollständig ausfüllen. Am Außenumfang können die Scheiben 12 von der Mittelebene ausgehend zu ihrem freien Ende hin, jeweils leicht verjüngt sein um die Montage beziehungsweise Demontage zu erleichtern. Die Kraftübertragung erfolgt über die Umfangsflächen der Vertiefungen und Scheiben, die zu diesem Zweck zusammenwirken.The power transmission elements according to FIG. 3b consist of circular recesses 13 in the end faces 5, 5 'of the rotor disks 4, 4', which in turn are axially opposite each other in pairs. The frictional connection is completed by means of disks 12, which completely completes the cavity formed by two recesses 13 fill out. On the outer circumference, the disks 12 can be slightly tapered from the center plane, starting at their free end, in order to facilitate assembly or disassembly. The power transmission takes place via the peripheral surfaces of the recesses and discs, which cooperate for this purpose.

Eine mögliche Anordnung der Kraftübertragungselemente bezüglich der Längsachse 3 ist aus Fig. 2b ersichtlich. Dort erkennt man, dass die Kraftübertragungselemente mit den Zugankern 8 auf einem Umfangskreis liegen können und jeweils mittig zwischen zwei Zugankern 8 angeordnet sein können.A possible arrangement of the force transmission elements with respect to the longitudinal axis 3 is made Fig. 2b seen. There it can be seen that the power transmission elements can be located with the tie rods 8 on a circumferential circle and each can be arranged centrally between two tie rods 8.

Gemäß einer weiteren - nicht dargestellten - Ausführungsform der Erfindung bestehen die Kraftübertragungselemente aus Ringnuten in den Stirnseiten 5, 5', die mit komplementär geformten Ringen zusammenwirken. Der Vorteil dieser Variante liegt in der Möglichkeit, die Ringnuten und Ringe jeweils konzentrisch um einen Zugankern 8 anordnen zu können, was eine sehr platzsparende Bauweise ergibt, die vor allem bei Rotoren mit kleinen Durchmessern zum Tragen kommt.According to another - not shown - embodiment of the invention, the force transmission elements consist of annular grooves in the end faces 5, 5 ', which cooperate with complementary shaped rings. The advantage of this variant lies in the possibility of being able to arrange the annular grooves and rings in each case concentrically around a tie rod 8, which results in a very space-saving design, which is particularly important for rotors with small diameters.

Ebenfalls nicht dargestellt ist eine Variante, bei der die Kraftübertragungselemente aus sich radial erstreckenden Nuten in der Stirnseite einer Rotorscheibe bestehen, in die komplementär geformte radial verlaufende Leisten in der zugeordneten Stirnseite einer benachbarten Rotorscheibe eingreifen.Also not shown is a variant in which the force transmission elements consist of radially extending grooves in the end face of a rotor disk, engage in the complementarily shaped radially extending strips in the associated end face of an adjacent rotor disk.

Alle beschriebenen Arten von Kraftübertragungselementen führen zu einer Verzahnung zwischen den einzelnen Rotorscheiben 4, 4', wodurch sich zusammen mit den Zugankern 8 ein quasi monolithisches, aber dennoch wieder zerlegbares Gebilde ergibt, das auf der Antriebswelle 2 sitzt.All the described types of force transmission elements lead to a toothing between the individual rotor disks 4, 4 ', whereby, together with the tie rods 8, a quasi-monolithic, but nonetheless disassemblable structure results, which sits on the drive shaft 2.

Zur Übertragung der Antriebskräfte von der Antriebswelle 2 auf die Rotorscheiben 4, 4' dienen Reibschlusselemente in Form eines oder mehrerer Spannsätze 15. Figur 4a zeigt den maßgeblichen Bereich in einem Teilschnitt. Dort sieht man, dass die Rotorscheiben 4 im Bereich der Öffnung 6 ausgehend von der Rotorstirnseite 10 jeweils eine Ausdrehung 16 aufweisen. Die Ausdrehung 16 ist zur Aufnahme eines oder mehrerer Spannsätze 15 bestimmt. Jeder Spannsatz 15 umfasst eine Druckhülse 17 mit einem äußeren Druckring 18, der an der Rotorscheibe 4 anliegt und einem in radialem Abstand dazu angeordneten inneren Druckring 19, der am Umfang der Antriebswelle 2 anliegt. Beide Druckringe 18 und 19 weisen über ihre axiale Länge eine im Mittelbereich konisch verdickte Wandung auf, so dass sich ein im Querschnitt doppelt konkaver Ringraum ergibt.To transmit the drive forces from the drive shaft 2 to the rotor disks 4, 4 'are frictional engagement elements in the form of one or more clamping sets 15th FIG. 4a shows the relevant area in a partial section. There one sees that the rotor disks 4 each have a recess 16 in the region of the opening 6 starting from the rotor end side 10. The recess 16 is for receiving one or determined a plurality of clamping sets 15. Each clamping set 15 comprises a pressure sleeve 17 with an outer pressure ring 18, which rests against the rotor disk 4 and a radially spaced inner pressure ring 19, which rests on the circumference of the drive shaft 2. Both pressure rings 18 and 19 have over their axial length a conically thickened in the central region wall, so that there is a double concave annular space.

In diesen Ringraum sind sich axial gegenüberliegende Keilringe 20 und 21 eingesetzt, deren Keilflächen mit den schrägen Innenseiten der Druckringe 18 und 19 zusammenwirken. Die beiden Keilringe 18 und 19 sind von einer Vielzahl von Spannschrauben 20 durchdrungen, wobei durch Anziehen der Spannschrauben 20 eine Relativbewegung des Keilrings 18 in Richtung des Keilring 19 initiiert wird. In der Folge kommt es zu einem radialen Aufspreizen der Druckhülse 17 und dabei zur Erzeugung eines Reibschlusses in den Kontaktflächen zwischen Druckhülse 17 und Antriebswelle 2 einerseits und Druckhülse 17 und Rotorscheibe 4 andererseits.In this annular space axially opposite wedge rings 20 and 21 are used, the wedge surfaces with the oblique inner sides of the pressure rings 18 and 19 cooperate. The two wedge rings 18 and 19 are penetrated by a plurality of clamping screws 20, wherein by tightening the clamping screws 20, a relative movement of the wedge ring 18 in the direction of the wedge ring 19 is initiated. As a result, there is a radial spreading of the pressure sleeve 17 and thereby to produce a frictional connection in the contact surfaces between the pressure sleeve 17 and drive shaft 2 on the one hand and pressure sleeve 17 and rotor disk 4 on the other.

Die sich in Folge des radialen Anpressdrucks, der Größe der Kraftübertragungsfläche und des Reibungsbeiwerts ergebende Reibkraft kann als maximales Antriebsmoment auf die Rotorscheiben 4 übertragen werden. Durch gezieltes Anziehen der Spannschrauben 20 ist es somit möglich, die von der Antriebswelle 2 auf die Rotorscheiben 4 maximal übertragbare Kraft einzustellen. Bei Überschreiten dieser Kraft, beispielsweise durch Blockieren der Rotorscheibe 4, wird diese Kraft überschritten und es kommt zu einem Schlupf zwischen Antriebswelle 2 und Rotorscheiben 4, der größeren Schaden am Rotor 1 verhindert.The resulting in consequence of the radial contact pressure, the size of the force transmission surface and the coefficient of friction friction force can be transmitted to the rotor disks 4 as the maximum drive torque. By selectively tightening the clamping screws 20, it is thus possible to set the maximum of the drive shaft 2 on the rotor disks 4 transferable force. When this force is exceeded, for example by blocking the rotor disk 4, this force is exceeded and there is a slip between the drive shaft 2 and rotor disks 4, which prevents greater damage to the rotor 1.

Die in Figur 4b gezeigte Ausführungsform eines Rotors 1 unterscheidet sich von der zuvor beschriebenen lediglich durch den Einsatz zweier Spannsätze 15, die in axialer Richtung hintereinander angeordnet sind. Durch die Verwendung mehrerer Spannsätze 15 ist es möglich, die maximal übertragbare Antriebskraft von der Antriebswelle 2 auf die Rotorscheibe 4 zu steigern.In the FIG. 4b shown embodiment of a rotor 1 differs from the previously described only by the use of two clamping sets 15, which are arranged one behind the other in the axial direction. By using a plurality of clamping sets 15, it is possible to increase the maximum transmissible driving force from the drive shaft 2 to the rotor disk 4.

Claims (14)

  1. A rotor for a device for the comminution of input material, the device having a drive shaft (2) on which a predetermined number of rotor discs (4, 4') are positioned in a rotationally fixed manner and having grinding tools arranged about a circumference (7) of the rotor discs, wherein, between the rotor discs (4, 4') forming axial ends of the rotor (1) and the drive shaft (2) for transferring a torque, frictional connection elements are arranged, wherein power transmission elements are arranged in the contact surface between two adjacent rotor discs (4, 4') and wherein the rotor discs (4, 4') are clamped together with axially acting clamping elements.
  2. The rotor according to claim 1, wherein the frictional connection elements include of at least one clamping set (15).
  3. The rotor according to claim 1 or 2, wherein a plurality of clamping sets (15) are arranged in axial succession to preset the transmissible torque.
  4. The rotor according to one of the claims 1 to 3, wherein the clamping elements are formed by tension anchors (8), which penetrate the rotor discs (4, 4') axially.
  5. The rotor according to claim 4, wherein the tension anchors (8) are arranged on a common circumferential circle around a longitudinal axis (3).
  6. The rotor according to claim 5, wherein the tension anchors (8) are arranged at a radial distance from the longitudinal axis (3) in such a way that the tension anchors (8) are located centrally between the outer circumference (7) and an edge of the central opening (6) of the rotor discs (4, 4').
  7. The rotor according to one of the claims 1 to 6, wherein heads of the tension anchors (8) are sunk into a respective front face (5) of the end rotor discs (4).
  8. The rotor according to one of the claims 1 to 3, wherein the clamping elements are formed by a shaft nut at one end of the rotor (1) and an axial stop at the other end of the rotor (1) and wherein the rotor discs (4, 4') are configured to be clamped against the axial stop by the shaft nut.
  9. The rotor according to one of the claims 1 to 8, wherein the power transmission elements includes pins (12), rings, strips or discs (14), which, emerging from the contact surface between two adjacent rotor discs (4, 4'), extend into complementary indentations (11, 13) in one as well as the other rotor disc (4, 4').
  10. The rotor according to claim 9, wherein the power transmission elements are tapered toward their axial ends.
  11. The rotor according to claim 9 or 10, wherein the power transmission elements are arranged on a joint circumferential circle around the longitudinal axis (3).
  12. The rotor according to one of the claims 9 to 11, wherein the power transmission elements are located in a tangential direction, in each case, in a centre between two adjacent tension anchors (8).
  13. The rotor according to one of the claims 9 to 11, wherein the power transmission elements have an annular shape and each concentrically surrounds a tension anchor (8).
  14. A device for the comminution of input material with a comminution unit, wherein the comminution unit has a rotor (1) in accordance with one of the claims 1 to 13.
EP09002956.2A 2008-03-07 2009-03-02 Rotor and device for grinding feeder product Active EP2098297B1 (en)

Applications Claiming Priority (1)

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DE102008013232A DE102008013232A1 (en) 2008-03-07 2008-03-07 Apparatus for comminuting feed with a rotor

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EP2098297A3 EP2098297A3 (en) 2011-06-15
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CA (1) CA2657441C (en)
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WO2017055365A1 (en) 2015-09-29 2017-04-06 Khd Humboldt Wedag Gmbh Rotor for a disintegration device

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CA2657441A1 (en) 2009-09-07
US8066212B2 (en) 2011-11-29
DE102008013232A1 (en) 2009-09-17
EP2098297A2 (en) 2009-09-09
DK2098297T3 (en) 2015-04-27
CA2657441C (en) 2012-05-15
US20090224089A1 (en) 2009-09-10
EP2098297A3 (en) 2011-06-15

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