EP2911797B1 - Roller crusher - Google Patents

Roller crusher Download PDF

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Publication number
EP2911797B1
EP2911797B1 EP13802893.1A EP13802893A EP2911797B1 EP 2911797 B1 EP2911797 B1 EP 2911797B1 EP 13802893 A EP13802893 A EP 13802893A EP 2911797 B1 EP2911797 B1 EP 2911797B1
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EP
European Patent Office
Prior art keywords
wedge
swing arm
roller
roller crusher
crusher according
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EP13802893.1A
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German (de)
French (fr)
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EP2911797A2 (en
Inventor
Piotr SZCZELINA
Detlef Papajewski
Peter Schatz
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ThyssenKrupp Industrial Solutions AG
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ThyssenKrupp Industrial Solutions AG
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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
    • B02C1/00—Crushing or disintegrating by reciprocating members
    • B02C1/02—Jaw crushers or pulverisers
    • B02C1/08—Jaw crushers or pulverisers with jaws coacting with rotating roller
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C4/00—Crushing or disintegrating by roller mills
    • B02C4/10—Crushing or disintegrating by roller mills with a roller co-operating with a stationary member
    • B02C4/12—Crushing or disintegrating by roller mills with a roller co-operating with a stationary member in the form of a plate
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C4/00—Crushing or disintegrating by roller mills
    • B02C4/28—Details
    • B02C4/32—Adjusting, applying pressure to, or controlling the distance between, milling members
    • B02C4/34—Adjusting, applying pressure to, or controlling the distance between, milling members in mills wherein a roller co-operates with a stationary member

Definitions

  • the present invention relates to a roll crusher according to the features of claim 1.
  • the present invention relates to roll crushers in which the crushing material to be crushed is crushed between a roll and a laterally arranged rocker.
  • Such a roll crusher can be configured in particular as an eccentric roll crusher or as a roll crusher with a directly driven roll.
  • Eccentric roller crushers which are also referred to as “Rotex crushers” are, for example, from the magazine " Reprocessing Technique, Journal for the Processing of Solid Raw Materials ", Volume 5 (1964), No. 5, pages 242 to 247 such as " Processing Technique, Journal for the Processing of Solid Raw Materials ", Volume 6 (1966), Issue 3, pages 166 to 174 known.
  • the rocker is hung in the known embodiments of eccentric roller crushers obliquely above the roller and pivotable to adjust both the entrance slit and the exit slit can.
  • the rocker is fixed in position in order to be able to comminute the crushed material, in particular rock.
  • a Spaltinstellvorraum is initially provided.
  • eccentric roller crushers with an overload protection, which are arranged between the rocker and a fixed to the housing frame abutment.
  • the biasing force of the springs is chosen so that they do not spring under normal crushing. If, on the other hand, overloading of the crushing jaws is imminent, the rocker may recede against the force of the springs and thus widen the crushing space in order to be able to discharge any foreign bodies.
  • eccentric roll crushers may be provided on both sides of the roller a rocker.
  • the corresponding overload protection is then also provided on both wings.
  • Eccentric roller crushers with a spring overload protection are also from the DE 1 257 004 and the DE 2 733 379 A1 known.
  • the DE 1 889 686 discloses an eccentric roller crusher, in which an adjustment of the two sides of the roller arranged swing takes place via a simple adjusting spindle, so that there is a particularly simple embodiment. An overload protection is not realized.
  • the DE 1 875 346 describes an eccentric roller crusher in which the rockers are each supported via an adjusting device, which are equipped with a hydraulic and a spring. Again, the entire force acting on the end of the loop force is supported by the spring or the hydraulic, so that a correspondingly stable configuration is necessary.
  • the DE 2 747 257 A1 describes an eccentric roller crusher in which the rocker has an overload protection in the form of an electromagnet.
  • the electromagnet must be correspondingly large and be supplied with large currents.
  • the rocker can be released by switching off the electromagnet without a significant drag.
  • the present invention is not limited to an embodiment of the roll crusher as an eccentric roll crusher. So show the US 1,141,643 and the DE 1 077 037 generic roll crusher with a directly rotating driven roller. This roller interacts with a rocker, which is held by a spring-equipped upper load protection.
  • the CH 174149 A discloses a roller crusher according to the preamble of claim 1.
  • the present invention seeks to improve the construction and the functionality of an adjustment between rocker and fixed abutment.
  • the object is achieved by the characterizing features of claim 1.
  • the first position and the second position may in particular be a first end position and a second end position, between which the wedge is adjustable.
  • the adjusting device can be used to adjust the distance between the rocker and the roller and thus also the breaking gap relevant for the breaking.
  • the adjusting device has a wedge drive, with which the wedge between the first position and the second position is adjustable continuously or in a plurality of intermediate positions.
  • the adjusting device according to the invention with the wedge also allows the realization of an upper load protection, in which case the wedge is displaced in the direction of the second position at a predetermined force on the rocker to the distance between rocker and roller and thus the crushing space formed between rocker and roller to expand.
  • both functions namely the setting of the distance between rocker and roller and the provision of an overload protection combined in an adjusting device according to the invention.
  • the wedge is always urged by an adapted wedge shape of the gap between the contact surface and the counter surface in the direction of the second position.
  • the holding forces of the wedge on the contact surface and on the counter surface are smaller than the forces urging the gap in the direction of the second position, the wedge moves automatically after decoupling from a wedge drive or a holding device in the direction of second position.
  • the rocker then opens automatically, which damage can be avoided under all circumstances.
  • the wedge shape can achieve that the holding forces required to hold the wedge in a predetermined position within the gap are significantly less than the force transmitted by the rocker via the wedge to the abutment.
  • the holding force may be less than 20% of the force transmitted by the rocker via the wedge to the abutment.
  • the drive for the wedge can thus be dimensioned correspondingly small, at the same time a particularly good functionality is achieved.
  • the wedge is displaceable along an adjustment direction, which is essentially straight or slightly curved, depending on the embodiment, between the first position and the second position.
  • the adjustment direction with respect to a connecting line between the rocker axis and the wedge in the second position an angle of less than 30 °. The adjustment is thus so based on the swing arm axis then approximately in the radial direction.
  • the gap may also be equipped with a sliding coating or with sliding elements.
  • the contact surface and the mating surface wherein the friction properties of the selected combination of materials are crucial.
  • the adjustment can be designed purely mechanical or purely hydraulic, but also mechanical and hydraulic components can be combined.
  • the wedge may be fully released immediately upon overload with a bypass valve, so that the swingarm will then fully open without substantial drag.
  • a pressure relief valve can be used, wherein the rocker then opens at least against a substantially constant counterforce.
  • the wedge drive can also be designed mechanically.
  • the wedge may for example be moved by means of an adjusting spindle, a servomotor or the like, wherein a release of the gap takes place in the event of an overload by a mechanical decoupling of the wedge drive.
  • a mechanical predetermined breaking point can be provided, in which case the part, for example a connecting rod or an adjusting spindle, is to be replaced when it is put into operation again.
  • various overload protection can be combined with each other to allow a double or two-stage protection.
  • the alignment of the contact surface formed on the rocker rear side also changes during an adjustment of the rocker.
  • the abutment is formed by a rotation axis on which a counter element with the counter surface formed thereon is freely rotatable.
  • the adjusting device with the wedge can be suspended rotatably.
  • the Fig. 1a shows a schematic longitudinal section of a roll crusher according to the invention, which is designed as an example as an eccentric roll crusher.
  • the roll crusher comprises a housing frame 1, a rotatable roller 2, a rocker 4 mounted on a swinging axis 3 on the housing frame 1, a crushing space 5 between roller 2 and rocker 4 and an adjusting device 6 at a distance to the rocker axis 3 between the rocker 4 and a fixed to the housing frame 1 abutment 7 is arranged to allow rotation of the rocker 4 about the swing arm axis 3.
  • the Fig. 1b is different from the Fig. 1a only in the position of a wedge 8, wherein the wedge 8 in the Fig. 1a in a second position P2 and in the Fig. 1b is in a first position P1.
  • the wedge 8 can be positioned within the gap with a wedge drive 11 of the adjusting device 6 in order to change the distance between rocker 4 and roller 2 and thus the effective crushing gap.
  • the wedge 8, the contact surface 9 and the mating surface 10 are aligned with each other so that the wedge 8 is urged by the forces acting on the rocker 4 downwards so in the direction of the second position P2.
  • the wedge 8 may be adapted to move automatically after decoupling from the wedge drive 11 in the direction of the second position P2, ie downwards. It also results in the illustrated structural design, the advantage that the movement of the wedge 8 in the direction of the second position P2 is supported by the weight of the wedge 8.
  • a hydraulic wedge drive 11 is provided, in particular in the Fig. 2 is shown.
  • the wedge drive 11 comprises a hydraulic pressure cylinder 12 which is equipped with a bypass valve. With the previously described decoupling from the wedge drive 11, it is equated when the bypass valve of the pressure cylinder 12 opens at a preset pressure, thus releasing a movement of the wedge 8, whereby it is automatically moved in the direction of the second position P2.
  • the wedge 8 is equipped with sliding elements 13, wherein the sliding elements 13 abut against the contact surface 9 and on the counter surface 10.
  • a purely mechanical wedge drive can be provided, in which case an overload protection is provided, for example, by a mechanical predetermined breaking point.
  • the holding force which is required to hold the wedge 8 in a predetermined position of the gap, is significantly smaller than that transmitted by the rocker 4 via the wedge 8 on the abutment 7 force.
  • the holding force may be less than 20% of the transmitted force, for example. It can thus be seen that in comparison to the prior art, a considerably smaller design of the entire adjusting device 6 is possible.
  • an adjustment direction between the first position P1 and the second position P2 extends essentially in the radial direction, starting from the pivot axis 3.
  • the adjustment direction between the first position P1 and the second position P2 with respect to a connecting line between the rocker axis 3 and the wedge 8 in the second, remote from the swing axle 3 position P2 includes an angle ⁇ of less than 30 °.
  • Fig. 1a shows that upon rotation of the rocker 4 about the swing arm axis 3, the orientation of the contact surface 9 is changed.
  • the abutment 7 is formed by a rotation axis on which a in Fig. 2 illustrated counter-element 14 is freely rotatable, wherein the counter-surface 10 is a portion of the counter-element 14.
  • the wedge drive 11 with the wedge 8 connected thereto is also movable about a tilting axis 15.

Description

Die vorliegende Erfindung betrifft einen Walzenbrecher gemäss den Merkmalen des Anspruchs 1. Die vorliegende Erfindung bezieht sich auf Walzenbrecher, bei denen das zu zerkleinernde Brechgut zwischen einer Walze und einer seitlich dazu angeordneten Schwinge gebrochen wird. Ein solcher Walzenbrecher kann insbesondere als Exzenter-Walzenbrecher oder als Walzenbrecher mit direkt angetriebener Walze ausgestaltet sein.The present invention relates to a roll crusher according to the features of claim 1. The present invention relates to roll crushers in which the crushing material to be crushed is crushed between a roll and a laterally arranged rocker. Such a roll crusher can be configured in particular as an eccentric roll crusher or as a roll crusher with a directly driven roll.

Exzenter-Walzenbrecher, die auch als "Rotex-Brecher" bezeichnet werden, sind beispielsweise aus der Zeitschrift " Aufbereitungs-Technik, Zeitschrift für die Aufbereitung fester Rohstoffe", Jahrgang 5 (1964), Heft 5, Seiten 242 bis 247 sowie " Aufbereitungs-Technik, Zeitschrift für die Aufbereitung fester Rohstoffe", Jahrgang 6 (1966), Heft 3, Seiten 166 bis 174 bekannt. Die Schwinge ist bei den bekannten Ausgestaltungen von Exzenter-Walzenbrechern schräg oberhalb der Walze aufgehängt und verschwenkbar, um sowohl den Eintrittsspalt als auch den Austrittsspalt verstellen zu können. Während des Betriebs des Walzenbrechers wird die Schwinge jedoch in ihrer Position fixiert, um das Brechgut, insbesondere Gestein, zerkleinern zu können. Um den Spalt zu verstellen, ist zunächst eine Spalteinstellvorrichtung vorgesehen. Darüber hinaus kann es im Betrieb aber auch vorkommen, dass Fremdstoffe in das Brechgut gelangen, die zu hart sind und nicht gebrochen werden können. Es besteht dann die Gefahr, dass der Brechspalt verstopft oder sogar die üblicherweise mit Brechbacken besetzte Walze und die mit Brechbacken besetzte Schwinge beschädigt werden. Es ist deshalb bekannt, Exzenter-Walzenbrecher mit einer Überlastsicherung auszurüsten, die zwischen der Schwinge und einem mit dem Gehäuserahmen ortsfesten Widerlager angeordnet sind. Die Vorspannkraft der Federn ist so gewählt, dass diese bei normaler Brechbeanspruchung nicht durchfedern. Wenn dagegen eine Überbelastung der Brechbacken droht, kann die Schwinge gegen die Kraft der Federn zurückweichen und somit den Brechraum erweitern, um gegebenenfalls Fremdkörper ausschleusen zu können. Als nachteilig hat sich jedoch erwiesen, dass sehr große, stabile Federn zu Abstützung eingesetzt werden müssen, welche bei der normalen Brechbeanspruchung nicht durchfedern. Des Weiteren ist auch der Übergangsbereich aufgrund der typischen Federcharakteristik nur schwer einzustellen. Es besteht auch der Nachteil, dass bei dem Zurückfedern weiterhin sehr große Federkräfte wirken, so dass Beschädigungen nicht ausgeschlossen werden können. Schließlich kann bei dem Einsatz von Federn auch ein undefinierter Übergangsbereich vorhanden sein, bei dem die Federn nur zum Teil komprimiert werden, wobei dann ein undefinierter Betriebszustand resultiert, der beispielsweise über einen längeren Zeitraum zu einer fehlerhaften Korngröße des gebrochenen Brechgutes führen kann.Eccentric roller crushers, which are also referred to as "Rotex crushers" are, for example, from the magazine " Reprocessing Technique, Journal for the Processing of Solid Raw Materials ", Volume 5 (1964), No. 5, pages 242 to 247 such as " Processing Technique, Journal for the Processing of Solid Raw Materials ", Volume 6 (1966), Issue 3, pages 166 to 174 known. The rocker is hung in the known embodiments of eccentric roller crushers obliquely above the roller and pivotable to adjust both the entrance slit and the exit slit can. During operation of the roll crusher, however, the rocker is fixed in position in order to be able to comminute the crushed material, in particular rock. To adjust the gap, a Spaltinstellvorrichtung is initially provided. In addition, it can also happen in operation that foreign substances reach the crushed material, which are too hard and can not be broken. There is then the danger that the crushing gap becomes clogged or even the roll usually occupied with crushing jaws and the rocker arm occupied with crushing jaws are damaged. It is therefore known to provide eccentric roller crushers with an overload protection, which are arranged between the rocker and a fixed to the housing frame abutment. The biasing force of the springs is chosen so that they do not spring under normal crushing. If, on the other hand, overloading of the crushing jaws is imminent, the rocker may recede against the force of the springs and thus widen the crushing space in order to be able to discharge any foreign bodies. However, it has proven to be disadvantageous that very large, stable springs must be used for support, which does not spring under normal crushing. Furthermore, the transition region is difficult to adjust due to the typical spring characteristic. There is also the disadvantage that continue to act in the spring back very large spring forces, so that damage can not be excluded. Finally, with the use of springs, an undefined transition region may also be present in which the springs are only partially compressed, in which case an undefined operating state results which, for example, can lead to a faulty grain size of the crushed crushed material over a longer period.

Bei Exzenter-Walzenbrechern kann an beiden Seiten der Walze eine Schwinge vorgesehen sein. Die entsprechende Überlastsicherung ist dann auch an beiden Schwingen vorzusehen.In eccentric roll crushers may be provided on both sides of the roller a rocker. The corresponding overload protection is then also provided on both wings.

Exzenter-Walzenbrecher mit einer Federn aufweisenden Überlastsicherung sind auch aus der DE 1 257 004 und der DE 2 733 379 A1 bekannt.Eccentric roller crushers with a spring overload protection are also from the DE 1 257 004 and the DE 2 733 379 A1 known.

Die DE 1 889 686 offenbart einen Exzenter-Walzenbrecher, bei dem eine Verstellung der beiden seitlich der Walze angeordneten Schwingen über eine einfache Stellspindel erfolgt, so dass sich eine besonders einfache Ausgestaltung ergibt. Eine Überlastsicherung ist jedoch nicht verwirklicht.The DE 1 889 686 discloses an eccentric roller crusher, in which an adjustment of the two sides of the roller arranged swing takes place via a simple adjusting spindle, so that there is a particularly simple embodiment. An overload protection is not realized.

Die DE 1 875 346 beschreibt einen Exzenter-Walzenbrecher, bei dem die Schwingen jeweils über eine Verstelleinrichtung abgestützt sind, die mit einer Hydraulik und einer Feder ausgerüstet sind. Auch hier wird die gesamte auf das Ende der Schlinge wirkende Kraft über die Feder bzw. die Hydraulik abgestützt, so dass eine entsprechend stabile Ausgestaltung notwendig ist.The DE 1 875 346 describes an eccentric roller crusher in which the rockers are each supported via an adjusting device, which are equipped with a hydraulic and a spring. Again, the entire force acting on the end of the loop force is supported by the spring or the hydraulic, so that a correspondingly stable configuration is necessary.

Aus der WO 2007/01946 A2 ist bei einem Exzenter-Walzenbrecher die Abstützung über mehrere Hebel bekannt, so dass sich eine insgesamt aufwendige Konstruktion ergibt.From the WO 2007/01946 A2 In the case of an eccentric roller crusher, the support via a plurality of levers is known, resulting in an overall complex construction.

Die DE 2 747 257 A1 beschreibt einen Exzenter-Walzenbrecher, bei dem die Schwinge eine Überlastsicherung in Form eines Elektromagnets aufweist. Um ausreichende Haltekräfte zu erreichen, muss der Elektromagnet entsprechend groß dimensioniert sein und mit großen Strömen versorgt werden. Es ergibt sich allerdings der Vorteil, dass bei einer Überlastung der Schwinge kein weiterer Kraftanstieg bei dem Zurückweichen erfolgt. Vielmehr kann die Schwinge durch ein Abschalten des Elektromagneten ohne eine wesentliche Gegenkraft freigegeben werden. Schließlich besteht auch nicht die Gefahr unkontrollierter Schwingungen, wie sie bei Federn auftreten können.The DE 2 747 257 A1 describes an eccentric roller crusher in which the rocker has an overload protection in the form of an electromagnet. To achieve sufficient holding forces, the electromagnet must be correspondingly large and be supplied with large currents. However, there is the advantage that when the rocker is overloaded, there is no further increase in force during the retreat. Rather, the rocker can be released by switching off the electromagnet without a significant drag. Finally, there is no risk of uncontrolled vibrations, as they can occur in springs.

Die vorliegende Erfindung ist nicht auf eine Ausgestaltung des Walzenbrecherrs als Exzenter-Walzenbrecher beschränkt. So zeigen die US 1 141 643 und die DE 1 077 037 gattungsgemäße Walzenbrecher mit einer direkt rotierend angetriebenen Walze. Diese Walze wirkt mit einer Schwinge zusammen, die von einer mit Federn ausgerüsteten Oberlastsicherung gehalten ist.The present invention is not limited to an embodiment of the roll crusher as an eccentric roll crusher. So show the US 1,141,643 and the DE 1 077 037 generic roll crusher with a directly rotating driven roller. This roller interacts with a rocker, which is held by a spring-equipped upper load protection.

Die CH 174149 A offenbart einen Walzenbrecher gemäß dem Oberbegriff des Anspruchs 1. Vor dem Hintergrund des Standes der Technik liegt der vorliegenden Erfindung die Aufgabe zugrunde, die Konstruktion und die Funktionalität einer Verstelleinrichtung zwischen Schwinge und ortsfestem Widerlager zu verbessern.The CH 174149 A discloses a roller crusher according to the preamble of claim 1. Against the background of the prior art, the present invention seeks to improve the construction and the functionality of an adjustment between rocker and fixed abutment.

Die Aufgabe wird erfindungsgemäß durch die kennzeichnenden Merkmale des Anspruchs 1 gelöst. Bei der ersten Position und der zweiten Position kann es sich insbesondere um eine erste Endposition und eine zweite Endposition handeln, zwischen denen der Keil verstellbar ist. Durch den Einsatz eines Keils kann erreicht werden, dass ein Großteil der auf die Schwinge wirkenden Kraft über den Keil auf das ortsfeste Widerlager übertragen wird, ohne dass die Kräfte in gleichem Maße in einer Verstellrichtung des Keils wirken. Erfindungsgemäß unterscheidet sich also der Weg zwischen der ersten Position und der zweiten Position von der Richtung der Krafteinleitung von der Schwinge zu dem ortsfesten Widerlager.The object is achieved by the characterizing features of claim 1. The first position and the second position may in particular be a first end position and a second end position, between which the wedge is adjustable. By using a wedge can be achieved that a large part of the force acting on the rocker force is transmitted via the wedge on the fixed abutment without the forces act in the same extent in an adjustment direction of the wedge. According to the invention, therefore, the path between the first position and the second position differs from the direction of the introduction of force from the rocker to the fixed abutment.

Die Verstelleinrichtung kann dazu genutzt werden, den Abstand zwischen der Schwinge und der Walze und damit auch den für das Brechen relevanten Brechspalt einzustellen. Im Rahmen einer solchen Ausgestaltung weist die Verstelleinrichtung einen Keilantrieb auf, mit dem der Keil zwischen der ersten Position und der zweiten Position kontinuierlich oder in mehreren Zwischenpositionen einstellbar ist.The adjusting device can be used to adjust the distance between the rocker and the roller and thus also the breaking gap relevant for the breaking. In the context of such an embodiment, the adjusting device has a wedge drive, with which the wedge between the first position and the second position is adjustable continuously or in a plurality of intermediate positions.

Des Weiteren ermöglicht die erfindungsgemäße Verstelleinrichtung mit dem Keil auch die Realisierung einer Oberlastsicherung, wobei dann bei einer vorgegebenen Krafteinwirkung auf die Schwinge der Keil in Richtung der zweiten Position verschoben wird, um den Abstand zwischen Schwinge und Walze und damit den zwischen Schwinge und Walze gebildeten Brechraum zu erweitern. Üblicherweise sind beide Funktionen, nämlich die Einstellung des Abstandes zwischen Schwinge und Walze sowie die Bereitstellung einer Überlastsicherung in einer erfindungsgemäßen Verstelleinrichtung kombiniert.Furthermore, the adjusting device according to the invention with the wedge also allows the realization of an upper load protection, in which case the wedge is displaced in the direction of the second position at a predetermined force on the rocker to the distance between rocker and roller and thus the crushing space formed between rocker and roller to expand. Usually, both functions, namely the setting of the distance between rocker and roller and the provision of an overload protection combined in an adjusting device according to the invention.

Ausgehend von dem beschriebenen Grundkonzept der vorliegenden Erfindung ergeben sich verschiedene bevorzugte Weiterbildungen.Starting from the described basic concept of the present invention, there are various preferred developments.

So kann beispielsweise vorgesehen sein, dass der Keil durch eine angepasste Keilform des Spaltes zwischen der Anlagefläche und der Gegenfläche stets in Richtung der zweiten Position gedrängt wird.Thus, for example, be provided that the wedge is always urged by an adapted wedge shape of the gap between the contact surface and the counter surface in the direction of the second position.

Wenn ausgehend von einer solchen Ausgestaltung die Haltekräfte des Keils an der Anlagefläche sowie an der Gegenfläche kleiner sind als die Kräfte, welche den Spalt in Richtung der zweiten Position drängen, bewegt sich der Keil nach einer Entkopplung von einem Keilantrieb oder einer Halteeinrichtung selbsttätig in Richtung der zweiten Position. Im Falle einer solchen Entkopplung, die beispielsweise auf eine Störung oder eine Überlast zurückzuführen ist, öffnet die Schwinge dann selbsttätig, wodurch unter allen Umständen eine Beschädigung vermieden werden kann.If, starting from such an embodiment, the holding forces of the wedge on the contact surface and on the counter surface are smaller than the forces urging the gap in the direction of the second position, the wedge moves automatically after decoupling from a wedge drive or a holding device in the direction of second position. In the case of such a decoupling, which is due for example to a fault or overload, the rocker then opens automatically, which damage can be avoided under all circumstances.

Wie bereits zuvor erläutert, kann durch die Keilform erreicht werden, dass die Haltekräfte, welche erforderlich sind, um den Keil in einer vorgegebenen Position innerhalb des Spaltes zu halten, deutlich geringer als die von der Schwinge über den Keil auf das Widerlager übertragenen Kraft ist. Die Haltekraft kann beispielsweise weniger als 20 % der von der Schwinge über den Keil auf das Widerlager übertragenen Kraft betragen. Der Antrieb für den Keil kann damit entsprechend klein dimensioniert werden, wobei gleichzeitig eine besonders gute Funktionalität erreicht wird. Im Vergleich zu bekannten Verstelleinrichtungen ergibt sich zusammen mit der Reduzierung der auf die Verstelleinrichtung wirkenden Kräfte ein größerer Stellweg, um die Schwinge zu bewegen, wodurch der Abstand zwischen Walze und Schwinge mit einer größeren Genauigkeit eingestellt werden kann.As explained previously, the wedge shape can achieve that the holding forces required to hold the wedge in a predetermined position within the gap are significantly less than the force transmitted by the rocker via the wedge to the abutment. For example, the holding force may be less than 20% of the force transmitted by the rocker via the wedge to the abutment. The drive for the wedge can thus be dimensioned correspondingly small, at the same time a particularly good functionality is achieved. Compared to known adjusting results in conjunction with the reduction of the forces acting on the adjusting forces a greater travel to move the rocker, whereby the distance between the roller and rocker can be adjusted with greater accuracy.

Der Keil ist entlang einer je nach Ausgestaltung im Wesentlichen geraden oder leicht gekrümmten Verstellrichtung zwischen der ersten Position und der zweiten Position verschiebbar. Vorzugsweise schließt die Verstellrichtung gegenüber einer Verbindungslinie zwischen der Schwingenachse und dem Keil in der zweiten Position einen Winkel von weniger als 30° ein. Die Verstellung erfolgt also bezogen auf die Schwingenachse dann also in etwa in radialer Richtung.The wedge is displaceable along an adjustment direction, which is essentially straight or slightly curved, depending on the embodiment, between the first position and the second position. Preferably, the adjustment direction with respect to a connecting line between the rocker axis and the wedge in the second position an angle of less than 30 °. The adjustment is thus so based on the swing arm axis then approximately in the radial direction.

Um eine gute Beweglichkeit des Keils in dem Spalt zwischen Anlagefläche und Gegenfläche zu ermöglichen, kann der Spalt auch mit einer Gleitbeschichtung oder mit Gleitelementen ausgerüstet sein. Das Gleiche gilt auch für die Anlagefläche und die Gegenfläche, wobei die Reibungseigenschaften der ausgewählten Materialkombination ausschlaggebend sind.In order to allow a good mobility of the wedge in the gap between the contact surface and counter surface, the gap may also be equipped with a sliding coating or with sliding elements. The same applies to the contact surface and the mating surface, wherein the friction properties of the selected combination of materials are crucial.

Die Verstelleinrichtung kann rein mechanisch oder rein hydraulisch ausgestaltet sein, wobei aber auch mechanische und hydraulische Komponenten miteinander kombiniert werden können. Wenn der Keil beispielsweise hydraulisch angetrieben wird, kann der Keil bei einer Überlast mit einem Bypassventil sofort vollständig freigegeben werden, so dass die Schwinge dann ohne eine wesentliche Gegenkraft vollständig öffnet. Alternativ kann auch ein Überdruckventil eingesetzt werden, wobei die Schwinge dann zumindest gegen eine im Wesentlichen konstante Gegenkraft öffnet.The adjustment can be designed purely mechanical or purely hydraulic, but also mechanical and hydraulic components can be combined. For example, if the wedge is hydraulically driven, the wedge may be fully released immediately upon overload with a bypass valve, so that the swingarm will then fully open without substantial drag. Alternatively, a pressure relief valve can be used, wherein the rocker then opens at least against a substantially constant counterforce.

Alternativ kann der Keilantrieb auch mechanisch ausgeführt sein. Der Keil kann beispielsweise mittels einer Stellspindel, einem Stellmotor oder dergleichen verschoben werden, wobei eine Freigabe des Spaltes bei einer Überlast durch eine mechanische Entkopplung von dem Keilantrieb erfolgt. Im Rahmen einer besonders einfachen Ausgestaltung kann eine mechanische Sollbruchstelle vorgesehen sein, wobei dann das Teil, beispielsweise eine Verbindungsstange oder eine Stellspindel, bei der erneuten Inbetriebnahme zu ersetzen ist. Grundsätzlich können auch verschiedene Überlastsicherungen miteinander kombiniert werden, um eine doppelte oder zweistufige Absicherung zu ermöglichen.Alternatively, the wedge drive can also be designed mechanically. The wedge may for example be moved by means of an adjusting spindle, a servomotor or the like, wherein a release of the gap takes place in the event of an overload by a mechanical decoupling of the wedge drive. In the context of a particularly simple embodiment, a mechanical predetermined breaking point can be provided, in which case the part, for example a connecting rod or an adjusting spindle, is to be replaced when it is put into operation again. Basically, various overload protection can be combined with each other to allow a double or two-stage protection.

Im Rahmen der Erfindung ist zu berücksichtigen, dass sich bei einer Verstellung der Schwinge auch die Ausrichtung der an der Schwingenrückseite gebildeten Anlagefläche verändert. Um einer unterschiedlichen Ausrichtung der einander zugewandten Flächen folgen zu können, ist gemäß konstruktiven Ausgestaltung der Erfindung vorgesehen, dass das Widerlage von einer Drehachse gebildet ist, auf der ein Gegenelement mit der daran gebildeten Gegenfläche frei drehbar ist. Auch die Verstelleinrichtung mit dem Keil kann drehbar aufgehängt sein.In the context of the invention, it should be taken into account that the alignment of the contact surface formed on the rocker rear side also changes during an adjustment of the rocker. In order to be able to follow a different orientation of the surfaces facing each other, it is provided according to the structural design of the invention that the abutment is formed by a rotation axis on which a counter element with the counter surface formed thereon is freely rotatable. The adjusting device with the wedge can be suspended rotatably.

Die Erfindung wird im Folgenden anhand einer lediglich ein Ausführungsbeispiel darstellenden Zeichnung erläutert. Es zeigen:

Fig.1a
einen schematischen Längsschnitt eines erfindungsgemäßen Walzenbrechers,
Fig. 1b
der Walzenbrecher gemäß 1 a mit einer anderen Stellung einer Schwinge,
Fig. 2
eine Detailansicht einer in Fig. 1a und 1b dargestellten Verstelleinrichtung.
The invention will be explained in the following with reference to a drawing showing only one exemplary embodiment. Show it:
1a
a schematic longitudinal section of a roll crusher according to the invention,
Fig. 1b
the roller crusher according to 1 a with a different position of a rocker,
Fig. 2
a detailed view of an in Fig. 1a and 1b illustrated adjusting device.

Die Fig. 1a zeigt in einem schematischen Längsschnitt einen erfindungsgemäßen Walzenbrecher, der exemplarisch als Exzenter-Walzenbrecher ausgestaltet ist. Der Walzenbrecher umfasst einen Gehäuserahmen 1, eine drehbare Walze 2, eine an einer Schwingeachse 3 an dem Gehäuserahmen 1 gelagerte Schwinge 4, einen Brechraum 5 zwischen Walze 2 und Schwinge 4 und eine Verstelleinrichtung 6, die in einem Abstand zu der Schwingenachse 3 zwischen der Schwinge 4 und einem mit dem Gehäuserahmen 1 ortsfesten Widerlager 7 angeordnet ist, um eine Drehung der Schwinge 4 um die Schwingenachse 3 zu ermöglichen. Die Fig. 1b unterscheidet sich von der Fig. 1a lediglich in der Stellung eines Keils 8, wobei der Keil 8 in der Fig. 1a sich in einer zweiten Position P2 und in der Fig. 1b in einer ersten Position P1 befindet.The Fig. 1a shows a schematic longitudinal section of a roll crusher according to the invention, which is designed as an example as an eccentric roll crusher. The roll crusher comprises a housing frame 1, a rotatable roller 2, a rocker 4 mounted on a swinging axis 3 on the housing frame 1, a crushing space 5 between roller 2 and rocker 4 and an adjusting device 6 at a distance to the rocker axis 3 between the rocker 4 and a fixed to the housing frame 1 abutment 7 is arranged to allow rotation of the rocker 4 about the swing arm axis 3. The Fig. 1b is different from the Fig. 1a only in the position of a wedge 8, wherein the wedge 8 in the Fig. 1a in a second position P2 and in the Fig. 1b is in a first position P1.

Erfindungsgemäß weist die Verstelleinrichtung 6 den Keil 8 auf, der in einem Spalt zwischen einer an der Schwingenrückseite gebildeten Anlagefläche 9 und einer dem Widerlager 7 zugeordneten Gegenfläche 10 angeordnet ist. Der Keil 8 kann innerhalb des Spaltes mit einem Keilantrieb 11 der Verstelleinrichtung 6 positioniert werden, um den Abstand zwischen Schwinge 4 und Walze 2 und damit den effektiven Brechspalt zu verändern. Wenn der Keil 8 nach unten in Richtung einer zweiten Position bewegt wird, vergrößert sich der Abstand zwischen Walze 2 und Schwinge 4. Wenn der Keil 8 dagegen nach oben in Richtung einer ersten Position P1 bewegt wird, verringert sich der Spalt zwischen Walze 2 und Schwinge 4.According to the invention, the adjusting device 6, the wedge 8, which is arranged in a gap between a bearing surface 9 formed on the rocker rear side and a counter surface 7 associated with the abutment 7. The wedge 8 can be positioned within the gap with a wedge drive 11 of the adjusting device 6 in order to change the distance between rocker 4 and roller 2 and thus the effective crushing gap. When the wedge 8 is moved downwards towards a second position, the distance between the roller 2 and the rocker 4 increases. When the wedge 8 is moved upwards towards a first position P1, however, the gap between roller 2 and rocker is reduced 4th

Der Keil 8, die Anlagefläche 9 und die Gegenfläche 10 sind so zueinander ausgerichtet, dass der Keil 8 durch die auf die Schwinge 4 wirkenden Kräfte nach unten also in Richtung der zweiten Position P2 gedrängt wird. Insbesondere kann der Keil 8 dazu eingerichtet sein, sich nach einer Entkopplung von dem Keilantrieb 11 selbsttätig in Richtung der zweiten Position P2, also nach unten, zu bewegen. Es ergibt sich bei der dargestellten konstruktiven Ausgestaltung auch der Vorteil, dass die Bewegung des Keils 8 in Richtung der zweiten Position P2 durch die Gewichtskraft des Keils 8 unterstützt wird.The wedge 8, the contact surface 9 and the mating surface 10 are aligned with each other so that the wedge 8 is urged by the forces acting on the rocker 4 downwards so in the direction of the second position P2. In particular, the wedge 8 may be adapted to move automatically after decoupling from the wedge drive 11 in the direction of the second position P2, ie downwards. It also results in the illustrated structural design, the advantage that the movement of the wedge 8 in the direction of the second position P2 is supported by the weight of the wedge 8.

In dem dargestellten Ausführungsbeispiel ist ein hydraulischer Keilantrieb 11 vorgesehen, der insbesondere auch in der Fig. 2 dargestellt ist. Der Keilantrieb 11 umfasst einen hydraulischen Druckzylinder 12, der mit einem Bypass-Ventil ausgerüstet ist. Mit dem zuvor beschriebenen Entkoppeln von dem Keilantrieb 11 ist es gleichzusetzen, wenn das Bypass-Ventil des Druckzylinders 12 bei einem voreingestellten Druck öffnet und damit eine Bewegung des Keils 8 freigibt, wodurch dieser selbsttätig in Richtung der zweiten Position P2 bewegt wird.In the illustrated embodiment, a hydraulic wedge drive 11 is provided, in particular in the Fig. 2 is shown. The wedge drive 11 comprises a hydraulic pressure cylinder 12 which is equipped with a bypass valve. With the previously described decoupling from the wedge drive 11, it is equated when the bypass valve of the pressure cylinder 12 opens at a preset pressure, thus releasing a movement of the wedge 8, whereby it is automatically moved in the direction of the second position P2.

Der Fig. 2 ist in diesem Zusammenhang auch zu entnehmen, dass der Keil 8 mit Gleitelementen 13 ausgerüstet ist, wobei die Gleitelemente 13 an der Anlagefläche 9 sowie an der Gegenfläche 10 anliegen.Of the Fig. 2 can be seen in this context that the wedge 8 is equipped with sliding elements 13, wherein the sliding elements 13 abut against the contact surface 9 and on the counter surface 10.

Gemäß einer alternativen Ausgestaltung der Erfindung kann auch ein rein mechanischer Keilantrieb vorgesehen sein, wobei dann eine Überlastsicherung beispielsweise durch eine mechanische Sollbruchstelle bereitgestellt wird.According to an alternative embodiment of the invention, a purely mechanical wedge drive can be provided, in which case an overload protection is provided, for example, by a mechanical predetermined breaking point.

Durch die in der Fig. 1 a dargestellte Ausgestaltung wird erreicht, dass die Haltekraft, die erforderlich ist, um den Keil 8 in einer vorgegebenen Position des Spaltes zu halten, deutlich kleiner als die von der Schwinge 4 über den Keil 8 auf das Widerlager 7 übertragene Kraft ist. Die Haltekraft kann beispielsweise weniger als 20 % der übertragenen Kraft betragen. Es ist damit ersichtlich, dass im Vergleich zum Stand der Technik eine erheblich kleinere Auslegung der gesamten Verstelleinrichtung 6 möglich ist.By in the Fig. 1 a configuration shown is achieved, that the holding force, which is required to hold the wedge 8 in a predetermined position of the gap, is significantly smaller than that transmitted by the rocker 4 via the wedge 8 on the abutment 7 force. The holding force may be less than 20% of the transmitted force, for example. It can thus be seen that in comparison to the prior art, a considerably smaller design of the entire adjusting device 6 is possible.

Zu erkennen ist auch, dass eine Verstellrichtung zwischen der ersten Position P1 und der zweiten Position P2 ausgehend von der Schwingenachse 3 im Wesentlichen in radialer Richtung verläuft. Vorzugsweise schließt die Verstellrichtung zwischen der ersten Position P1 und der zweiten Position P2 gegenüber einer Verbindungslinie zwischen der Schwingenachse 3 und dem Keil 8 in der zweiten, von der Schwingenachse 3 entfernten Position P2 einen Winkel α von weniger als 30° ein.It can also be seen that an adjustment direction between the first position P1 and the second position P2 extends essentially in the radial direction, starting from the pivot axis 3. Preferably, the adjustment direction between the first position P1 and the second position P2 with respect to a connecting line between the rocker axis 3 and the wedge 8 in the second, remote from the swing axle 3 position P2 includes an angle α of less than 30 °.

Aus der Fig. 1a ergibt sich auch, dass bei einer Drehung der Schwinge 4 um die Schwingenachse 3 die Ausrichtung der Anlagefläche 9 verändert wird. Um dieser Veränderung der Ausrichtung folgen zu können, ist das Widerlager 7 von einer Drehachse gebildet, auf der ein in Fig. 2 dargestelltes Gegenelement 14 frei drehbar ist, wobei die Gegenfläche 10 ein Abschnitt des Gegenelementes 14 ist.From the Fig. 1a also shows that upon rotation of the rocker 4 about the swing arm axis 3, the orientation of the contact surface 9 is changed. In order to follow this change in orientation, the abutment 7 is formed by a rotation axis on which a in Fig. 2 illustrated counter-element 14 is freely rotatable, wherein the counter-surface 10 is a portion of the counter-element 14.

Gemäß der Fig. 1 a ist schließlich auch der Keilantrieb 11 mit dem daran angeschlossenen Keil 8 um eine Kippachse 15 beweglich.According to the Fig. 1 Finally, the wedge drive 11 with the wedge 8 connected thereto is also movable about a tilting axis 15.

Claims (9)

  1. Roller crusher comprising a housing frame (1), a rotatable roller (2), a swing arm (4) mounted on a swing arm axis (3) on the housing frame (1), a crushing chamber (5) between the roller (2) and the swing arm (4), and an adjusting device (6), which is arranged at a distance to the swing arm axis (3) between the swing arm (4) and a counter bearing (7) which is fixed relative to the housing frame (1), in order to enable a rotation of the swing arm (4) about the swing arm axis (3), wherein the adjusting device (6) has a wedge (8) arranged between the swing arm (4) and the counter bearing (7), wherein, in a second position (P2) of the wedge (8) in the gap, the distance formed between the swing arm (4) and the roller (2) is greater than in a first position (P1), characterized in that the wedge (8) bridges a gap between a contact surface (9) arranged on the back of a swing arm and a counter surface (10) assigned to the counter bearing (7), and wherein the counter bearing (7) is formed by a rotational axis, on which a counter element (14), with the thereon formed counter surfaces (10), is freely rotatable.
  2. Roller crusher according to Claim 1, characterized in that the wedge (8), as a result of a modified wedge shape of the gap, is pushed in the direction of the second position.
  3. Roller crusher according to Claim 1 or 2, characterized in that the adjusting device (6) has an overload protection.
  4. Roller crusher according to Claim 3, characterized in that the overload protection has a mechanical predetermined breaking point.
  5. Roller crusher according to Claim 3 or 4, characterized in that the overload protection has a hydraulic valve.
  6. Roller crusher according to Claim 2 and one of Claims 3 to 5, characterized in that the wedge (8) is designed to move, following decoupling from a wedge drive (11) or a retaining device, automatically in the direction of the second position.
  7. Roller crusher according to one of Claims 1 to 6, characterized in that the adjusting device (6) has a wedge drive (11), with which the wedge (8) is adjustable between the first position and the second position continuously or in a plurality of intermediate positions.
  8. Roller crusher according to one of Claims 1 to 7, characterized in that the wedge (8) is displaceable along a direction of adjustment between the first position and the second position, wherein the adjusting device (6) forms an angle of less than 30° in relation to a connecting line between the swing arm axis (3) and the wedge (8) in the second position.
  9. Roller crusher according to one of Claims 1 to 8, characterized in that the retaining force which is necessary to hold the wedge (8) in a predefined position within the gap is less than 20 % of the force transmitted from the swing arm (4) via the wedge (8) to the counter bearing (7).
EP13802893.1A 2012-10-29 2013-10-28 Roller crusher Active EP2911797B1 (en)

Applications Claiming Priority (2)

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DE102012110336.4A DE102012110336A1 (en) 2012-10-29 2012-10-29 roll crusher
PCT/EP2013/072465 WO2014067882A2 (en) 2012-10-29 2013-10-28 Roller crusher

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EP2911797B1 true EP2911797B1 (en) 2017-05-17

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Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PL70841Y1 (en) * 2017-08-21 2019-06-28 Skotarek Wieslaw Profit Machine for crushing mineral raw materials, preferably a jaw crusher
CN108067320A (en) * 2017-09-06 2018-05-25 广州凯柔进出口贸易有限公司 A kind of fertilizer processing unit (plant)
CN108067343A (en) * 2017-09-06 2018-05-25 广州凯柔进出口贸易有限公司 A kind of small-sized fertilizer crushes heating unit
CN109304232B (en) * 2018-06-27 2019-07-02 广东水电二局股份有限公司 Discarded concrete recycled fine aggregate tertiary crusher
CN108576915B (en) * 2018-07-06 2023-04-25 河南省新之林机电设备有限公司 High-precision roller gap adjusting device of sheet shredding and wrinkling forming equipment
CN109078724A (en) * 2018-09-27 2018-12-25 湖北力帝机床股份有限公司 Prebreaker and control method
CN111215186A (en) * 2020-03-21 2020-06-02 河南中誉鼎力智能装备有限公司 Horizontal gyratory crusher and intelligent control method thereof
CN111215185A (en) * 2020-03-21 2020-06-02 河南中誉鼎力智能装备有限公司 Double-cavity horizontal type gyratory crusher and intelligent control method thereof
DE102021213035A1 (en) 2021-11-19 2023-05-25 Thyssenkrupp Ag Eccentric roll crusher
WO2024069462A1 (en) 2022-09-29 2024-04-04 Flsmidth A/S Roll crusher with adjustable crushing gap
DE102022125159A1 (en) 2022-09-29 2024-04-04 FLSmidth Mining Technologies GmbH Roller crusher with adjustable crushing gap
LU502855B1 (en) 2022-09-29 2024-03-29 Flsmidth Mining Tech Gmbh Roller crusher with adjustable crushing gap
WO2024079707A1 (en) 2022-10-14 2024-04-18 Flsmidth A/S Two-stage processing plant
CN117680223B (en) * 2024-02-04 2024-04-19 黑龙江科技大学 Ore reducing mechanism is used in mining

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1141643A (en) 1913-06-23 1915-06-01 Allis Chalmers Mfg Co Roll-crusher.
DE455510C (en) * 1926-11-02 1928-02-03 August Mueller Stone crusher
GB405383A (en) * 1932-09-15 1934-02-08 Winget Ltd Improvements in crushing machines
CH174149A (en) * 1934-04-05 1934-12-31 Brun & Cie Jaw crusher.
FR773080A (en) * 1934-05-09 1934-11-10 Bouvier & Paul Atel Apparatus for crushing and grinding stone and all minerals or products
US2326215A (en) * 1938-12-12 1943-08-10 Nordberg Manufacturing Co Jaw crusher
US2605051A (en) * 1947-09-29 1952-07-29 Nelson H Bogie Rock crusher
US2588180A (en) * 1948-06-11 1952-03-04 Jr Samuel William Traylor Jaw crusher with hydraulic release and reset device
NL104570C (en) 1958-10-09
DE1875346U (en) 1961-08-19 1963-07-11 Weserhuette Ag Eisenwerk JAW ROLLER CRUSHERS WITH HYDRAULIC ADJUSTMENT DEVICE AND OVERLOAD SAFETY.
DE1889686U (en) 1964-01-02 1964-03-19 Weserhuette Ag Eisenwerk CRACKING JAW OF A CRUSHING MACHINE FOR ROCK AND THE LIKE. FABRICS.
DE1257004B (en) 1964-11-21 1967-12-21 Weserhuette Ag Eisenwerk Crushing chuck for shredding machines that work on the principle of pressure or crushing
DE2733379C3 (en) 1977-07-23 1980-07-31 Weserhuette Ag, 4970 Bad Oeynhausen Single roller crusher
DE2747257A1 (en) 1977-10-21 1979-04-26 Weserhuette Ag Eisenwerk Overload safety device for rotary crusher - uses electromagnets as supports to allow roller deflection for passage of hard bodies
DE3515261A1 (en) * 1985-04-27 1986-11-06 Untertage Maschinenfabrik Dudweiler Gmbh, 6602 Dudweiler Crusher device
US7411517B2 (en) 2005-06-23 2008-08-12 Ultima Labs, Inc. Apparatus and method for providing communication between a probe and a sensor

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BR112015009411A2 (en) 2017-07-04
DK2911797T3 (en) 2017-09-11
PE20151303A1 (en) 2015-10-14
CL2015001073A1 (en) 2015-11-06
AU2013339535A1 (en) 2015-05-14
CN104903001A (en) 2015-09-09
CN104903001B (en) 2017-03-15
DE102012110336A1 (en) 2014-04-30
WO2014067882A2 (en) 2014-05-08
AU2013339535B2 (en) 2018-03-15
EP2911797A2 (en) 2015-09-02
WO2014067882A3 (en) 2014-09-12
BR112015009411B1 (en) 2021-06-01

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