EP2307144B1 - Feed device with two rotary valves which are variable independently of each other - Google Patents

Feed device with two rotary valves which are variable independently of each other Download PDF

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Publication number
EP2307144B1
EP2307144B1 EP09780041.1A EP09780041A EP2307144B1 EP 2307144 B1 EP2307144 B1 EP 2307144B1 EP 09780041 A EP09780041 A EP 09780041A EP 2307144 B1 EP2307144 B1 EP 2307144B1
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EP
European Patent Office
Prior art keywords
shaft
nip
pressure roller
roller press
variable
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Not-in-force
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EP09780041.1A
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German (de)
French (fr)
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EP2307144A1 (en
Inventor
Alex Nickel
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KHD Humboldt Wedag AG
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KHD Humboldt Wedag AG
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Publication of EP2307144A1 publication Critical patent/EP2307144A1/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
    • B02C4/00—Crushing or disintegrating by roller mills
    • B02C4/28—Details
    • B02C4/286—Feeding devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides

Definitions

  • the invention relates to a high-pressure roller press for high-pressure comminution of millbase with a feeding device which controls the millbase in the nip between two rollers of the high-pressure roller press gives up.
  • the nip is wider than the largest extent of the crushed regrind, it is important to load the nip so that at the same time a certain amount of the millbase passes through the nip. If the nip is charged with too little amount per unit of time, then in extreme cases, the material to be ground no longer crushed or the high-pressure roller press acts much like a crusher. On the other hand, if too much is added to the nip, it may happen that the high-pressure roller press is overloaded and begins to vibrate.
  • the nip increases and decreases in resonant frequency and the rotational speed varies with resonant frequency, since in an overload, the rollers of the high-pressure roller press are repeatedly braked by the excessive amount of ground material and accelerated by the drive motors again. Therefore, in the high-pressure crushing in the nip is to ensure that the nip is applied to a suitable extent with millbase.
  • the actual task quantity But depends strongly on the nature of the ground material. The parameters to be considered and worth mentioning are the particle size distribution, the mean grain size and the uniformity of the available ground material flow on the nip. For the task on the nip so the material to be ground or 'feed material' must be supplied evenly from above into the nip.
  • the type of material feed has a major influence on the smooth running of the high-pressure roller press. To improve the intake conditions and to ensure a uniform distribution of the drive power to the drive motors of the high-pressure roller press, therefore, the function of a feeder over the nip is steadily improved.
  • German patent application DE 34 38 310 A1 discloses a device for equalizing the task of feedstock via a feed gate into a crushing machine, wherein the feed material is deflected several times.
  • German Offenlegungsschrift DE 40 06 971 A1 discloses a feeder for filling granular solids in a crushing machine, wherein a pipe resonator is disposed between a hopper and the crushing machine.
  • German Offenlegungsschrift discloses DE 196 32 9 76 A1 a feeder which divides the feedstock through a screen into two fractions and dispenses the fractions from different sides onto the nip of a high pressure roller press.
  • the object of the invention is to improve the effect of the feeder in relation to the intake behavior of the entire high-pressure roller press and to optimize it in relation to a uniform distribution of the drive power to different drive motors of the high-pressure roller press.
  • the object of the invention is achieved in that the feeding device of the high-pressure roller press has at least two rotary valves whose position can be varied independently of one another.
  • the feeding device Due to the presence of at least two rotary valves, the feeding device according to the invention makes it possible to adapt to the changing requirements with changing material properties of the feed material. So it is possible to symmetrically open and close the two rotary valves, so as to give up a certain, average total amount per unit time on the high-pressure roller press. In addition to this pure dosing by a uniform opening around the center of the feeder centered on the nip of the high-pressure roller press, it is also possible to adjust the two rotary valve so that the center of the opening between the at least two rotary valves is not located above the center of the nip, but laterally offset to. This makes it possible to vary not only the task quantity but also the precise task location. Especially when starting the high-pressure roller press this adjustment makes it easy to achieve the optimum operating condition of the high-pressure roller press.
  • the rotary valves are arranged on a variable in height above the nip shaft.
  • the fact that the shaft can be varied in height, and thus the rotary valve can be the bulk cone, which emerges from the feeder, within the limits of the natural cone of material, which is determined by the material properties of the feed, on the one hand and through change the mechanical movement of the cone from below through the rotating rollers of the high-pressure roller press, on the other side.
  • This possibility of variation also offers the operating personnel to form the optimum material cone over the nip, so that a low-vibration and as low as possible energy-consuming operation of the high-pressure roller press is possible.
  • the invention is provided in a further embodiment that the shaft is provided with an exchangeable inner lining as abrasion protection. If the abrasion protection has been removed during operation, it is possible to replace the inner lining, which, like two interposed pits, intermesh with comparatively little effort, and thus the shaft, which besides its shaft effect also has to dissipate mechanical forces, is protected against destruction.
  • the rotary valves are adjustable according to the invention via a hydraulic system.
  • the hydraulic operation has proved advantageous because it is robust enough to withstand the harsh conditions to withstand the grinding of brittle goods. It is provided that the hydraulic system engages the rotary valve on one side and engages with the other side of the telescopic hydraulic system at the height of the nip variable shaft. If the supply lines for the hydraulic systems are long enough and flexible, it is possible to raise and lower the height-variable shaft above the nip, with the hydraulic systems traveling with the shaft for opening and closing the rotary valves.
  • the position of the variable in height above the nip shaft is adjusted according to the invention via a further hydraulic system, wherein it has proved to be advantageous if at least one hydraulic system is arranged on two opposite sides of the shaft.
  • These hydraulic systems lift the entire shaft, on which a funnel-shaped plate is arranged, in which conveyor belts or other conveying members drop the feed.
  • the feed material located in the hopper is raised or lowered again.
  • the shaft is telescopically formed, and the hopper does not travel with the shaft.
  • the telescopic shaft collapses and extends depending on the direction in which the shaft moves, however, it has proved to be more advantageous if just this telescopic arrangement of the shaft is not performed.
  • Abrasive material can collect too easily in the telescopic attachment and disturb the telescope function.
  • variable in height above the nip shaft is adjustable via a hydraulic system in height above the nip, wherein the hydraulic system on the one hand on a rack system which accommodates the variable in height over the nip shaft, and on the other hand engages at the height above the nip variable shaft.
  • the hydraulic systems for raising and lowering the shaft engage on the one hand as close as possible to the shaft itself and on the other hand as close as possible to a vertical struts of a rack system, within which the shaft up and moved to prevent buckling of the shaft in the rack system under mechanical stress.
  • the hydraulic system is almost vertical or slightly inclined vertically.
  • the linear bearing consists in its simplest form of a U-profile, which is arranged with its opening to the outside on the shaft, and in which engages a horizontal support, which extends from the rack system to the linear bearing; while the support is firmly connected to the rack system.
  • the reverse arrangement is possible in which the support is attached to the shaft and engages in a linear bearing on the frame system.
  • FIG. 1 A high-pressure roller press 100 is shown on which a feeding device 200 according to the present invention is placed.
  • the high-pressure roller press 100 two rollers 101 and 102, wherein roller 102 is largely hidden in this view, and the two rollers 101 and 102 form a nip 103, which passes through the feedstock 104, not shown here the feedstock 104 is crushed during the passage of the nip 103 by the high pressure prevailing therein.
  • the rollers 101 and 102 are in large-sized bearings 110, 111, 112 and the in FIG. 1 bearing hidden by the drawing view 113 (visible in FIG FIG.
  • both rollers 101 and 102 are designed as idler rollers or one of the rollers 101 and 102 is a fixed roller and the other roller is a loose roller, wherein the idler roller is arranged movably within the machine frame 120 relative to the hard roller is.
  • rollers 101 and 102 rotate in opposite directions, in which example the front roller 101 has the direction of rotation indicated by arrow 123 and the second roller 102 has a corresponding opposite direction of rotation. So that the rollers 101 and 102 do not slip and do not grind against one another and thus rapidly wear out strongly, but press exclusively, it is provided that the rollers 101 and 102 rotate as much as possible with the same, but opposite rotational speed without relative slippage.
  • the feeder device 200 is fixed by means of a rack system 201, wherein the rack system 201 forms a cage within which a height-adjustable shaft 202 above the nip 103 is arranged.
  • Shaft 202 is mounted in linear bearings 210, 211, 212 and 213 and is connected to the frame system 201 via hydraulic rams 220, 221, 222 and a hydraulic ram 223 concealed in this view.
  • the hydraulic rams 220, 221, 222 and 223 extend telescopically, thus lifting the shaft 202 out of the rack system 201.
  • a larger hopper is arranged, in which conveyors or other transport devices pour feed 104, which is applied by the feeder 200 uniformly on the nip 103.
  • conveyors or other transport devices pour feed 104, which is applied by the feeder 200 uniformly on the nip 103.
  • the feeder 200 is as a Einzelgewerk in FIG. 2 illustrated and explained in detail.
  • the rack system 201 can be seen, within which a variable in height above the nip 103 shaft 202 is received, the shaft 202 is connected via hydraulic rams 220, 221, 222 and 223 to the rack system 201.
  • the various hydraulic rams 220, 221, 222 and 223 each depend on a vertical struts 240, 241, 242 and 243 and attack the shaft 202 in its immediate vicinity.
  • the thus diagonal arrangement of the hydraulic rams 240, 241, 242 and 243 is in FIG. 2 to be taken clearly.
  • the well 202 is supported in linear bearings 210, 211, 212, 213, with four horizontal supports 250, 251, 252 and 253 attached to the well 202, each in one of the linear bearings 210, 211, 212, 213 intervene.
  • the two rotary valves 230 and 231 which are opened and closed independently of each other by hydraulic ram 260 accompanying with the shaft 202 and the hydraulic ram 261 corresponding thereto and concealed in this view.
  • the hydraulic rams 260 and 261 engage at one end on the shaft 202 and each with a different end of the hydraulic ram 260 and 261 on the rotary valves 230 and 231.
  • the shaft 202 inserted into the rack system 201 is in FIG. 3 in a side view, from which the function of the hydraulic rams 220, 221 and the concealed hydraulic rams 222 and 223 for raising and lowering the entire shaft 202 on the one hand and the function of the hydraulic rams 260 and 261 on the other hand for opening and closing the rotary valve 230 and 231 better apparent .
  • FIG. 3 clearly show that the center of the opening between the two rotary valves 230 and 231, depending on the position of the rotary valve 230 and 231 also located next to the center above the nip 103 (103 ').
  • the rotary valve 230, 231 give the material to be ground 104 centrally above the nip 103 on the high-pressure roller press 100 and give non-symmetrical position the material to be ground 104 out of the center (103 ') above the nip 103 on the high-pressure roller press 100
  • FIG. 4 is shown a lower part of the shaft 202, which is shown here without hydraulic ram 220, 221, 222 and 223 and without hydraulic rams 260 and 261.
  • the rack system 201 is separable from the bay 202 by releasing the hydraulic rams 220, 221, 222, and 223 from the rack system 201.
  • FIG. 5 is the thus separated rack system 201 shown without moving elements and in FIG. 5 as shown mounted in the machine frame 120 of a high-pressure roller press.
  • the shaft 202 is hooked into the rack system 201, in which the hydraulic rams 220, 221, 222 and 223 connect and support the shaft 202 with the rack system 201.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Grinding (AREA)

Description

Die Erfindung betrifft eine Hochdruckrollenpresse zur Hochdruckzerkleinerung von Mahlgut mit einer Aufgabevorrichtung, welche das Mahlgut kontrolliert in den Walzenspalt zwischen zwei Walzen der Hochdruckrollenpresse aufgibt.The invention relates to a high-pressure roller press for high-pressure comminution of millbase with a feeding device which controls the millbase in the nip between two rollers of the high-pressure roller press gives up.

Zur Zerkleinerung von sprödem Mahlgut schlug Schönert in 1977 in der deutschen Auslegeschrift DE 27 08 053 vor, das Mahlgut nicht klassisch zu zermahlen, sondern durch Hochdruckbeanspruchung in einem Walzenspalt das Mahlgut zunächst zu Schülpen zu pressen, wobei das Gefüge des Mahlguts zerberstet. Die aus dem Walzenspalt austretenden Schülpen können in einem weiteren Schritt unter Aufwendung von vergleichsweise wenig Energie in ihre Einzelbestandteile zerlegt werden. Das Pressen unter hohem Druck im Walzenspalt und das anschließende Desagglomerieren der verpressten Schülpen beansprucht weniger Energie zur Zerkleinerung pro Masseneinheit Mahlgut als ein herkömmliches Mahlverfahren. Durch diese Art der Zerkleinerung sind hohe Mahlfeinheiten erreichbar, wobei hierzu ein Umlauf des Mahlguts notwendig ist. Da der Walzenspalt aber breiter ist als die größte Ausdehnung des zerkleinerten Mahlguts, ist es wichtig, den Walzenspalt so zu beschicken, dass gleichzeitig eine bestimmte Menge des Mahlguts den Walzenspalt passiert. Wird der Walzenspalt mit einer zu geringen Menge pro Zeiteinheit beschickt, so wird im Extremfall das Mahlgut gar nicht mehr zerkleinert oder die Hochdruckrollenpresse wirkt ähnlich wie ein Brecher. Wird hingegen eine zu große Menge auf den Walzenspalt gegeben, kann es passieren, dass die Hochdruckrollenpresse überlastet ist und anfängt, zu vibrieren. Bei der Vibration vergrößert und verkleinert sich der Walzenspalt in Resonanzfrequenz und auch die Umlaufgeschwindigkeit variiert mit Resonanzfrequenz, da bei einer Überlastung die Walzen der Hochdruckrollenpresse wiederkehrend durch das in zu hohem Maße vorhandene Mahlgut gebremst und durch die Antriebsmotoren wieder beschleunigt werden. Daher ist bei der Hochdruckzerkleinerung im Walzenspalt dafür Sorge zu tragen, dass der Walzenspalt in geeignetem Maße mit Mahlgut beaufschlagt wird. Die tatsächliche Aufgabemenge hängt aber stark von der Beschaffenheit des Mahlguts ab. Die hierzu zu beachtenden und erwähnenswerten Parameter sind die Korngrößenverteilung, die mittlere Korngröße und die Gleichmäßigkeit des zur Verfügung stehenden Mahlgutstroms auf den Walzenspalt. Zur Aufgabe auf den Walzenspalt muss also das Mahlgut oder auch 'Aufgabegut' von oben gleichmäßig in den Walzenspalt zugeführt werden.For the comminution of brittle regrind Schönert proposed in 1977 in the German design DE 27 08 053 Not to grind the regrind classically, but by high pressure stress in a nip, the millbase first to squeegee, whereby the structure of the millbase breaks up. The slugs emerging from the nip can be broken down into their individual constituents in a further step with the expenditure of comparatively little energy. Pressing under high pressure in the nip and then deagglomerating the compressed slugs requires less energy for comminution per unit mass of millbase than a conventional milling process. By this type of crushing high grinding fineness can be achieved, for which purpose a circulation of the ground material is necessary. However, since the nip is wider than the largest extent of the crushed regrind, it is important to load the nip so that at the same time a certain amount of the millbase passes through the nip. If the nip is charged with too little amount per unit of time, then in extreme cases, the material to be ground no longer crushed or the high-pressure roller press acts much like a crusher. On the other hand, if too much is added to the nip, it may happen that the high-pressure roller press is overloaded and begins to vibrate. During vibration, the nip increases and decreases in resonant frequency and the rotational speed varies with resonant frequency, since in an overload, the rollers of the high-pressure roller press are repeatedly braked by the excessive amount of ground material and accelerated by the drive motors again. Therefore, in the high-pressure crushing in the nip is to ensure that the nip is applied to a suitable extent with millbase. The actual task quantity But depends strongly on the nature of the ground material. The parameters to be considered and worth mentioning are the particle size distribution, the mean grain size and the uniformity of the available ground material flow on the nip. For the task on the nip so the material to be ground or 'feed material' must be supplied evenly from above into the nip.

Wesentlichen Einfluss auf den ruhigen Lauf der Hochdruckrollenpresse hat die Art der Materialbeschickung. Zur Verbesserung der Einzugsverhältnisse und um eine gleichmäßige Verteilung der Antriebsleistung auf die Antriebsmotoren der Hochdruckrollenpresse zu sichern, wird daher die Funktion einer Aufgabevorrichtung über dem Walzenspalt stetig verbessert.The type of material feed has a major influence on the smooth running of the high-pressure roller press. To improve the intake conditions and to ensure a uniform distribution of the drive power to the drive motors of the high-pressure roller press, therefore, the function of a feeder over the nip is steadily improved.

Die deutsche Offenlegungsschrift DE 34 38 310 A1 offenbart eine Vorrichtung zur Vergleichmäßigung der Aufgabe von Aufgabegut über eine Aufgabeschleuse in eine Zerkleinerungsmaschine, wobei das Aufgabegut mehrfach umgelenkt wird.The German patent application DE 34 38 310 A1 discloses a device for equalizing the task of feedstock via a feed gate into a crushing machine, wherein the feed material is deflected several times.

In der deutschen Offenlegungsschrift DE 40 06 971 A1 wird eine Aufgabevorrichtung zum Einfüllen von körnigen Feststoffen in eine Zerkleinerungsmachine offenbart, wobei zwischen einem Trichter und der Zerkleinerungsmaschine ein Pfeifenresonator angeordnet ist.In the German Offenlegungsschrift DE 40 06 971 A1 discloses a feeder for filling granular solids in a crushing machine, wherein a pipe resonator is disposed between a hopper and the crushing machine.

Schließlich offenbart die deutsche Offenlegungsschrift DE 196 32 9 76 A1 eine Aufgabevorrichtung, welche das Aufgabegut durch ein Sieb in zwei Fraktionen aufteilt und die Fraktionen von verschiedenen Seiten auf den Walzenspalt einer Hochdruckrollenpresse aufgibt.Finally, the German Offenlegungsschrift discloses DE 196 32 9 76 A1 a feeder which divides the feedstock through a screen into two fractions and dispenses the fractions from different sides onto the nip of a high pressure roller press.

Aufgabe der Erfindung ist, die Wirkung der Aufgabevorrichtung in Bezug auf das Einzugsverhalten der gesamten Hochdruckrollenpresse zu verbessern und in Bezug auf eine gleichmäßige Verteilung der Antriebsleistung auf verschiedene Antriebsmotoren der Hochdruckrollenpresse zu optimieren.The object of the invention is to improve the effect of the feeder in relation to the intake behavior of the entire high-pressure roller press and to optimize it in relation to a uniform distribution of the drive power to different drive motors of the high-pressure roller press.

Die erfindungsgemäße Aufgabe wird dadurch gelöst, dass die Aufgabevorrichtung der Hochdruckrollenpresse mindestens zwei Drehschieber aufweist, deren Stellung unabhängig voneinander variierbar ist.The object of the invention is achieved in that the feeding device of the high-pressure roller press has at least two rotary valves whose position can be varied independently of one another.

Durch die Präsenz von mindestens zwei Drehschiebern ermöglicht die erfindungsgemäße Aufgabevorrichtung eine Anpassung an die sich mit ändernden Materialeigenschaften des Aufgabematerials wechselnden Anforderungen. So ist es möglich, die beiden Drehschieber symmetrisch zu öffnen und zu schließen, um so eine bestimmte, mittlere Gesamtmenge pro Zeiteinheit auf die Hochdruckrollenpresse aufzugeben. Neben dieser reinen Dosierfunktion durch ein gleichmäßiges Öffnen um den Mittelpunkt der Aufgabevorrichtung mittig über dem Walzenspalt der Hochdruckrollenpresse ist es auch möglich, die beiden Drehschieber so einzustellen, dass die Öffnungsmitte zwischen den mindestens zwei Drehschiebern nicht über der Mitte des Walzenspaltes angeordnet ist, sondern seitlich versetzt dazu. Hierdurch ist es möglich, nicht nur die Aufgabemenge, sondern auch noch den genauen Aufgabeort zu variieren. Gerade beim Starten der Hochdruckrollenpresse erleichtert diese Einstellmöglichkeit, schnell den optimalen Betriebszustand der Hochdruckrollenpresse zu erreichen.Due to the presence of at least two rotary valves, the feeding device according to the invention makes it possible to adapt to the changing requirements with changing material properties of the feed material. So it is possible to symmetrically open and close the two rotary valves, so as to give up a certain, average total amount per unit time on the high-pressure roller press. In addition to this pure dosing by a uniform opening around the center of the feeder centered on the nip of the high-pressure roller press, it is also possible to adjust the two rotary valve so that the center of the opening between the at least two rotary valves is not located above the center of the nip, but laterally offset to. This makes it possible to vary not only the task quantity but also the precise task location. Especially when starting the high-pressure roller press this adjustment makes it easy to achieve the optimum operating condition of the high-pressure roller press.

In Ausgestaltung der Erfindung ist vorgesehen, dass die Drehschieber an einem in der Höhe über dem Walzenspalt variierbaren Schacht angeordnet sind. Dadurch, dass der Schacht in der Höhe variierbar ist, und damit auch die Drehschieber, lässt sich der Schüttkegel, der aus der Aufgabevorrichtung heraustritt, in den Grenzen des natürlichen Schüttkegels, der durch die Materialeigenschaften des Aufgabeguts vorgegeben ist, auf der einen Seite und durch die mechanische Bewegung des Schüttkegels von unten durch die sich drehenden Walzen der Hochdruckrollenpresse, auf der anderen Seite, verändern. Auch diese Variationsmöglichkeit bietet dem Bedienungspersonal, den optimalen Schüttkegel über dem Walzenspalt auszubilden, so dass ein vibrationsarmer und ein möglichst gering energieverzehrender Betrieb der Hochdruckrollenpresse möglich ist.In an embodiment of the invention, it is provided that the rotary valves are arranged on a variable in height above the nip shaft. The fact that the shaft can be varied in height, and thus the rotary valve, can be the bulk cone, which emerges from the feeder, within the limits of the natural cone of material, which is determined by the material properties of the feed, on the one hand and through change the mechanical movement of the cone from below through the rotating rollers of the high-pressure roller press, on the other side. This possibility of variation also offers the operating personnel to form the optimum material cone over the nip, so that a low-vibration and as low as possible energy-consuming operation of the high-pressure roller press is possible.

Um den Schacht vor übermäßiger Abrasion durch Erze oder durch nicht zerkleinerten Zementklinker zu schützen, ist in weiterer Ausgestaltung der Erfindung vorgesehen, dass der Schacht mit einer austauschbaren Innenauskleidung als Abrasionsschutz versehen ist. Wenn im Betrieb der Abrasionsschutz abgetragen ist, so lässt sich mit vergleichsweise geringem Aufwand die Innenauskleidung, die wie zwei ineinander gestapelte Schächte ineinander liegen, austauschen und somit ist der Schacht, der neben seiner Schachtwirkung außerdem noch mechanische Kräfte ableiten muss, vor Zerstörung geschützt.In order to protect the shaft against excessive abrasion by ores or by not crushed cement clinker, the invention is provided in a further embodiment that the shaft is provided with an exchangeable inner lining as abrasion protection. If the abrasion protection has been removed during operation, it is possible to replace the inner lining, which, like two interposed pits, intermesh with comparatively little effort, and thus the shaft, which besides its shaft effect also has to dissipate mechanical forces, is protected against destruction.

Die Drehschieber sind erfindungsgemäß über ein Hydrauliksystem verstellbar. Zwar ist es auch möglich, eine andere Antriebsart zu wählen, jedoch hat sich die Hydraulikbedienung als vorteilhaft erwiesen, weil sie robust genug ist, um den rauen Bedingungen bei der Vermahlung spröden Guts zu widerstehen. Dabei ist vorgesehen, dass das Hydrauliksystem an dem Drehschieber auf der einen Seite angreift und mit der anderen Seite des teleskopartigen Hydrauliksystems an dem in der Höhe über dem Walzenspalt variierbaren Schacht angreift. Sofern die Versorgungsleitungen für die Hydrauliksysteme lang genug und flexibel sind, ist es möglich, den in der Höhe über dem Walzenspalt variierbaren Schacht anzuheben und abzusenken, wobei die Hydrauliksysteme zur Öffnung und Schließung der Drehschieber mit dem Schacht mitreisen.The rotary valves are adjustable according to the invention via a hydraulic system. Although it is also possible to choose a different type of drive, however, the hydraulic operation has proved advantageous because it is robust enough to withstand the harsh conditions to withstand the grinding of brittle goods. It is provided that the hydraulic system engages the rotary valve on one side and engages with the other side of the telescopic hydraulic system at the height of the nip variable shaft. If the supply lines for the hydraulic systems are long enough and flexible, it is possible to raise and lower the height-variable shaft above the nip, with the hydraulic systems traveling with the shaft for opening and closing the rotary valves.

Die Stellung des in der Höhe über dem Walzenspalt variierbaren Schachtes wird erfindungsgemäß über ein weiteres Hydrauliksystem eingestellt, wobei es sich als vorteilhaft erwiesen hat, wenn mindestens je ein Hydrauliksystem auf zwei gegenüberliegenden Seiten des Schachtes angeordnet ist. Diese Hydrauliksysteme heben den gesamten Schacht an, auf dem ein trichterförmiges Blech angeordnet ist, in welchen Förderbänder oder andere Förderorgane das Aufgabegut abwerfen. Beim Absenken oder Anheben des in der Höhe über dem Walzenspalt variierbaren Schachtes wird somit der gesamte Trichter mitsamt Inhalt, dem im Trichter befindlichen Aufgabegut, angehoben oder wieder abgesenkt. Neben dem Absenken und Anheben der gesamten Trichteranordnung ist es auch möglich, dass der Schacht teleskopartig ausgebildet ist, und der Trichter nicht mit dem Schacht mitreist. Dabei schiebt sich der teleskopartige Schacht zusammen und verlängfert sich, je nachdem, in welche Richtung sich der Schacht bewegt, jedoch hat es sich als vorteilhafter erwiesen, wenn gerade diese teleskopartige Anordnung des Schachtes nicht ausgeführt wird. Zu leicht kann sich abrasives Aufgabegut im Teleskopgeschiebe sammeln und die Teleskopfunktion stören.The position of the variable in height above the nip shaft is adjusted according to the invention via a further hydraulic system, wherein it has proved to be advantageous if at least one hydraulic system is arranged on two opposite sides of the shaft. These hydraulic systems lift the entire shaft, on which a funnel-shaped plate is arranged, in which conveyor belts or other conveying members drop the feed. When lowering or raising the variable in height above the nip shaft thus the entire hopper together with content, the feed material located in the hopper is raised or lowered again. In addition to lowering and raising the entire hopper assembly, it is also possible that the shaft is telescopically formed, and the hopper does not travel with the shaft. In this case, the telescopic shaft collapses and extends depending on the direction in which the shaft moves, however, it has proved to be more advantageous if just this telescopic arrangement of the shaft is not performed. Abrasive material can collect too easily in the telescopic attachment and disturb the telescope function.

In Ausgestaltung der Erfindung ist vorgesehen, dass der in der Höhe über dem Walzenspalt variierbare Schacht über ein Hydrauliksystem in der Höhe über dem Walzenspalt verstellbar ist, wobei das Hydrauliksystem einerseits an einem Gestellsystem, welches den in der Höhe über dem Walzenspalt variierbaren Schacht aufnimmt, und andererseits am in der Höhe über dem Walzenspalt variierbaren Schacht angreift.In an embodiment of the invention, it is provided that the variable in height above the nip shaft is adjustable via a hydraulic system in height above the nip, wherein the hydraulic system on the one hand on a rack system which accommodates the variable in height over the nip shaft, and on the other hand engages at the height above the nip variable shaft.

Die Hydrauliksysteme zum Anheben und Absenken des Schachts greifen einerseits möglichst nah an dem Schacht selbst an und andererseits möglichst nah an einem vertikalen Streben eines Gestellsystems an, innerhalb dessen sich der Schacht auf-und ab bewegt, um ein Einknicken des Schachtes im Gestellsystem bei mechanischer Belastung zu vermeiden. Je nach vorhandenem Zwischenraum zwischen Schacht und Gestellsystem ist so das Hydrauliksystem nahezu vertikal oder leicht vertikal geneigt ausgerichtet.The hydraulic systems for raising and lowering the shaft engage on the one hand as close as possible to the shaft itself and on the other hand as close as possible to a vertical struts of a rack system, within which the shaft up and moved to prevent buckling of the shaft in the rack system under mechanical stress. Depending on the existing gap between the shaft and rack system so the hydraulic system is almost vertical or slightly inclined vertically.

Da der Schacht innerhalb des Gestellsystems durch das Hydrauliksystem angehoben und wieder abgesenkt wird, ist es von Vorteil, wenn der Schacht durch ein Linearlager innerhalb des Gestellsystems abgestützt ist und beim Anheben und wieder Absenken innerhalb des Linearlagers auf und abgleitet. Das Linearlager besteht in seiner einfachsten Form aus einem U-Profil, das mit seiner Öffnung nach außen auf dem Schacht angeordnet ist, und in welches eine horizontale Stütze eingreift, welche vom Gestellsystem bis zum Linearlager reicht; dabei ist die Stütze mit dem Gestellsystem fest verbunden. Auch die umgekehrte Anordnung ist möglich, in welcher die Stütze an dem Schacht befestigt ist und in ein Linearlager am Gestellsystem eingreift.Since the shaft is raised and lowered within the rack system by the hydraulic system, it is advantageous if the shaft is supported by a linear bearing within the rack system and slides up and down during lifting and lowering again within the linear bearing. The linear bearing consists in its simplest form of a U-profile, which is arranged with its opening to the outside on the shaft, and in which engages a horizontal support, which extends from the rack system to the linear bearing; while the support is firmly connected to the rack system. The reverse arrangement is possible in which the support is attached to the shaft and engages in a linear bearing on the frame system.

Die Erfindung wird anhand der folgenden Figuren näher erläutert.The invention will be explained in more detail with reference to the following figures.

Es zeigen:

Figur 1
eine Hochdruckrollenpresse mit aufgesetzter Aufgabevorrichtung gemäß der vorliegenden Erfindung,
Figur 2
die erfindungsgemäße Aufgabevorrichtung,
Figur 3
eine seitliche Ansicht auf die Aufgabevorrichtung,
Figur 4
der untere Teil des Schachts der Aufgabevorrichtung als Detail,
Figur 5
die Hochdruckrollenpresse gemäß Figur 1 mit aufgesetztem Gestellsystem der Aufgabevorrichtung.
Show it:
FIG. 1
a high-pressure roller press with attached feeding device according to the present invention,
FIG. 2
the feed device according to the invention,
FIG. 3
a side view of the feeder,
FIG. 4
the lower part of the tray of the feeder as a detail,
FIG. 5
the high pressure roller press according to FIG. 1 with attached rack system of the feeder.

In Figur 1 ist eine Hochdruckrollenpresse 100 abgebildet, auf welche eine Aufgabevorrichtung 200 gemäß der vorliegenden Erfindung aufgesetzt ist. Dabei weist die Hochdruckrollenpresse 100 zwei Walzen 101 und 102 auf, wobei Walze 102 in dieser Ansicht größtenteils verdeckt ist, und die beiden Walzen 101 und 102 bilden einen Walzenspalt 103 aus, den das hier nicht dargestellte Aufgabegut 104 passiert, wobei das Aufgabegut 104 während der Passage des Walzenspaltes 103 durch den darin herrschenden hohen Druck zerkleinert wird. Um die hohen Kräfte, die bei der Hochdruckzerkleinerung anfallen, aufnehmen zu können, sind die Walzen 101 und 102 in groß dimensionierten Lagern 110, 111, 112 und dem in Figur 1 durch die Zeichnungsansicht verdeckten Lager 113 (sichtbar in Figur 5) gelagert, und die Lager 110, 111, 112 sowie 113 sind ihrerseits in einem Maschinenrahmen 120 aufgenommen, der die vier Lager 110, 111, 112 und 113 gleitend fixiert. Gleitend fixiert bedeutet, dass die beiden Walzen 101 und 102 horizontal verfahrbar sind, um Passagen von nicht zerkleinerbarem Material durch den Walzenspalt 103 ausweichen zu können. Für die gleitende Lagerung sind je nach Ausführungsform der Hochdruckrollenpresse 100 beide Walzen 101 und 102 als Losrollen ausgeführt oder eine der Walzen 101 und 102 ist eine Festwalze und die jeweils andere Walze ist eine Loswalze, wobei die Loswalze gegenüber der Festwalze beweglich innerhalb des Maschinenrahmens 120 angeordnet ist. Zur Hochdruckzerkleinerung ist vorgesehen, dass die Walzen 101 und 102 gegenläufig rotieren, wobei in diesem Beispiel die vordere Walze 101 die Rotationsrichtung, die durch Pfeil 123 angedeutet ist, aufweist und die zweite Walze 102 dazu korrespondierend eine gegenläufige Rotationsrichtung aufweist. Damit die Walzen 101 und 102 keinen Schlupf aufweisen und nicht gegeneinander mahlen und somit schnell stark abnutzen, sondern ausschließlich pressen, ist vorgesehen, dass die Walzen 101 und 102 möglichst mit der gleichen, aber gegenläufigen Umdrehungsgeschwindigkeit ohne relativen Schlupf rotieren.In FIG. 1 A high-pressure roller press 100 is shown on which a feeding device 200 according to the present invention is placed. In this case, the high-pressure roller press 100 two rollers 101 and 102, wherein roller 102 is largely hidden in this view, and the two rollers 101 and 102 form a nip 103, which passes through the feedstock 104, not shown here the feedstock 104 is crushed during the passage of the nip 103 by the high pressure prevailing therein. In order to be able to absorb the high forces that occur in the high-pressure comminution, the rollers 101 and 102 are in large-sized bearings 110, 111, 112 and the in FIG. 1 bearing hidden by the drawing view 113 (visible in FIG FIG. 5 ), and the bearings 110, 111, 112 and 113 are in turn received in a machine frame 120 which slidably fixes the four bearings 110, 111, 112 and 113. Slidably fixed means that the two rollers 101 and 102 are horizontally movable in order to avoid passages of non-comminutable material through the nip 103 can. Depending on the embodiment of the high-pressure roller press 100, both rollers 101 and 102 are designed as idler rollers or one of the rollers 101 and 102 is a fixed roller and the other roller is a loose roller, wherein the idler roller is arranged movably within the machine frame 120 relative to the hard roller is. For high-pressure crushing it is provided that the rollers 101 and 102 rotate in opposite directions, in which example the front roller 101 has the direction of rotation indicated by arrow 123 and the second roller 102 has a corresponding opposite direction of rotation. So that the rollers 101 and 102 do not slip and do not grind against one another and thus rapidly wear out strongly, but press exclusively, it is provided that the rollers 101 and 102 rotate as much as possible with the same, but opposite rotational speed without relative slippage.

An den oberen Traversen 121 und 122 ist die Aufgabevorrichtung 200 mit Hilfe eines Gestellsystems 201 fixiert, wobei das Gestellsystem 201 einen Käfig ausbildet, innerhalb dessen ein in der Höhe über dem Walzenspalt 103 variierbarer Schacht 202 angeordnet ist. Schacht 202 ist dabei in Linearlagern 210, 211, 212 und 213 gelagert und ist mit dem Gestellsystem 201 über Hydraulikstempel 220, 221, 222 und einem in dieser Ansicht verdeckten Hydraulikstempel 223 verbunden. Um den Schacht 202 anzuheben, fahren die Hydraulikstempel 220, 221, 222 und 223 teleskopartig aus und heben so den Schacht 202 aus dem Gestellsystem 201 hervor. In Ausführung der Erfindung ist vorgesehen, dass oben am Schacht 202 ein größerer Trichter angeordnet ist, in welchen Förderbänder oder andere Transportvorrichtungen Aufgabegut 104 schütten, welches durch die Aufgabevorrichtung 200 gleichmäßig auf den Walzenspalt 103 aufgegeben wird. Neben der Variation der Höhe des Schachtes 202 über dem Walzenspalt 103 ist es auch möglich, die Öffnung des Schachtes 202 nach unten zum Walzenspalt 103 durch zwei Drehschieber 230 und 231 zu variieren.At the upper traverses 121 and 122, the feeder device 200 is fixed by means of a rack system 201, wherein the rack system 201 forms a cage within which a height-adjustable shaft 202 above the nip 103 is arranged. Shaft 202 is mounted in linear bearings 210, 211, 212 and 213 and is connected to the frame system 201 via hydraulic rams 220, 221, 222 and a hydraulic ram 223 concealed in this view. To lift the shaft 202, the hydraulic rams 220, 221, 222 and 223 extend telescopically, thus lifting the shaft 202 out of the rack system 201. In the embodiment of the invention it is provided that at the top of the shaft 202, a larger hopper is arranged, in which conveyors or other transport devices pour feed 104, which is applied by the feeder 200 uniformly on the nip 103. In addition to the variation of the height of the shaft 202 above the nip 103, it is also possible to vary the opening of the shaft 202 down to the nip 103 by two rotary valves 230 and 231.

Die Aufgabevorrichtung 200 ist als Einzelgewerk in Figur 2 dargestellt und im Detail näher erläutert. Deutlich ist das Gestellsystem 201 erkennbar, innerhalb dessen ein in der Höhe über dem Walzenspalt 103 variierbarer Schacht 202 aufgenommen ist, wobei der Schacht 202 über Hydraulikstempel 220, 221, 222 und 223 mit dem Gestellsystem 201 verbunden ist. Um zu vermeiden, dass der Schacht 202 unter Last eines nicht eingezeichneten Trichters, der auf den Schacht 202 aufgesetzt ist, einknickt, stützen sich die verschiedenen Hydraulikstempel 220, 221, 222 und 223 je an einem vertikalen Streben 240, 241, 242 und 243 ab und greifen den Schacht 202 in seiner unmittelbarer Nähe an. Die hierdurch diagonale Anordnung der Hydraulikstempel 240, 241, 242 und 243 ist in Figur 2 deutlich zu entnehmen. Um den vertikalen Weg des Schachts 202 zu stabilisieren, ist der Schacht 202 in Linearlagern 210, 211, 212, 213 gelagert, wobei vier waagrechte Stützen 250, 251, 252 und 253, die an dem Schacht 202 befestigt sind, jeweils in eines der Linearlager 210, 211, 212, 213 eingreifen. Unterhalb der der Lagerung in vier Linearlagern 210, 211, 212, 213 ist der Schacht 202 mit weiteren Stützen 254, 255, 257 und der in dieser Zeichnung verdeckten Stütze 256 in unteren Linearlagern 214, 215, 217 und dem in dieser Zeichnung verdeckten Linearlager 216 gelagert, wobei nur die nach vorne rechts gewandten Linearlager 215 und 217 in Figur 2 sichtbar sind. In Umkehr zu der oben beschriebenen Kombination aus Linearlagern 210, 211, 212, 213 und Stützen 250, 251, 252 und 253 sind die korrespondierenden unteren Stützen 254, 255, 257 und die nicht sichtbare Stütze 256 an dem Schacht 202 befestigt und die unteren Linearlager 214, 215, 217 und 218 stützen sich an den vertikalen Streben 240, 241, 242 und 243 ab.The feeder 200 is as a Einzelgewerk in FIG. 2 illustrated and explained in detail. Clearly the rack system 201 can be seen, within which a variable in height above the nip 103 shaft 202 is received, the shaft 202 is connected via hydraulic rams 220, 221, 222 and 223 to the rack system 201. In order to avoid that the shaft 202 buckles under load of a not-shown funnel, which is placed on the shaft 202, the various hydraulic rams 220, 221, 222 and 223 each depend on a vertical struts 240, 241, 242 and 243 and attack the shaft 202 in its immediate vicinity. The thus diagonal arrangement of the hydraulic rams 240, 241, 242 and 243 is in FIG. 2 to be taken clearly. To stabilize the vertical path of the well 202, the well 202 is supported in linear bearings 210, 211, 212, 213, with four horizontal supports 250, 251, 252 and 253 attached to the well 202, each in one of the linear bearings 210, 211, 212, 213 intervene. Below the storage in four linear bearings 210, 211, 212, 213 of the shaft 202 with further supports 254, 255, 257 and hidden in this drawing support 256 in lower linear bearings 214, 215, 217 and concealed in this drawing linear bearing 216th stored, with only the right-facing linear bearings 215 and 217 in FIG. 2 are visible. In reversal to the above-described combination of linear bearings 210, 211, 212, 213 and supports 250, 251, 252 and 253, the corresponding lower supports 254, 255, 257 and the invisible support 256 are secured to the well 202 and the lower linear bearings 214, 215, 217 and 218 are supported on the vertical struts 240, 241, 242 and 243.

An der unteren Öffnung des Schachts 202 befinden sich die zwei Drehschieber 230 und 231, die durch mit dem Schacht 202 mitreisende Hydraulikstempel 260 und dem dazu korrespondierenden und in dieser Ansicht verdeckten Hydraulikstempel 261 unabhängig voneinander geöffnet und geschlossen werden. Dazu greifen die Hydraulikstempel 260 und 261 mit einem Ende an dem Schacht 202 an und mit jeweils einem anderen Ende des Hydraulikstempels 260 und 261 an den Drehschiebern 230 und 231. Dadurch, dass die beiden Hydraulikstempel 260 und 261 unabhängig voneinander aus- und eingefahren werden können, ist die Stellung der beiden Drehschieber 230 und 231 so einstellbar, dass die Mitte der Öffnung zwischen den beiden Drehschiebern 230 und 231 sich nicht direkt über dem Walzenspalt 103 im in eine Hochdruckrollenpresse 100 eingebauten Zustand befindet. Diese Einstellbarkeit lässt genug Spielraum, eine mit dieser Aufgabevorrichtung 200 ausgerüstete Hochdruckrollenpresse 100 ohne Vibrationen in einem optimalen Betriebszustand zu betreiben.At the lower opening of the shaft 202 there are the two rotary valves 230 and 231, which are opened and closed independently of each other by hydraulic ram 260 accompanying with the shaft 202 and the hydraulic ram 261 corresponding thereto and concealed in this view. For this purpose, the hydraulic rams 260 and 261 engage at one end on the shaft 202 and each with a different end of the hydraulic ram 260 and 261 on the rotary valves 230 and 231. The fact that the two hydraulic rams 260 and 261 can be independently extended and retracted , is the position of the two rotary valves 230 and 231 adjustable so that the center of the opening between the two rotary valves 230 and 231 is not located directly above the nip 103 in the installed in a high-pressure roller press 100 state. This adjustability leaves enough latitude to operate a high pressure roller press 100 equipped with this feeder 200 without vibration in an optimum operating condition.

Um eine übermäßig schnelle Abnutzung durch Abrasion zu vermeiden, ist vorgesehen, den Schacht 202 mit einer Innenauskleidung 203 zu versehen, die in den Schacht 202 eingesetzt und am Flansch 204 befestigt ist. Ein jeweils korrespondierender Abrasionsschutz 232 und 233 ist auf den Innenseiten der Drehschieber 230 und 231 vorhanden, um die erheblichen abrasiven Kräften ausgesetzten Drehschieber 230 und 231 vor vorzeitiger Abnutzung zu schützen.In order to avoid excessively rapid wear by abrasion, it is provided to provide the shaft 202 with an inner lining 203, which is inserted into the shaft 202 and fixed to the flange 204. A respective corresponding Abrasionsschutz 232 and 233 is provided on the inner sides of the rotary valve 230 and 231 to protect the considerable abrasive forces exposed rotary valve 230 and 231 from premature wear.

Der in das Gestellsystem 201 eingesetzte Schacht 202 ist in Figur 3 in einer Seitenansicht dargestellt, aus der die Funktion der Hydraulikstempel 220, 221 und den verdeckten Hydraulikstempeln 222 und 223 zum Anheben und Absenken des gesamten Schachts 202 einerseits und die Funktion der Hydraulikstempel 260 und 261 andererseits zum Öffnen und Schließen der Drehschieber 230 und 231 besser hervorgeht. Durch die Seitenansicht ist Figur 3 deutlich zu entnehmen dass sich die Mitte der Öffnung zwischen beiden Drehschiebern 230 und 231, je nach Stellung der Drehschieber 230 und 231 auch neben der Mitte über dem Walzenspalt 103 befinden kann (103'). Dabei ist vorgesehen, dass die Drehschieber 230, 231 bei symmetrischer Stellung das Mahlgut 104 mittig über dem Walzenspalt 103 auf die Hochdruckrollenpresse 100 aufgeben und bei nicht symmetrischer Stellung das Mahlgut 104 außerhalb der Mitte (103') über dem Walzenspalt 103 auf die Hochdruckrollenpresse 100 aufgebenThe shaft 202 inserted into the rack system 201 is in FIG. 3 in a side view, from which the function of the hydraulic rams 220, 221 and the concealed hydraulic rams 222 and 223 for raising and lowering the entire shaft 202 on the one hand and the function of the hydraulic rams 260 and 261 on the other hand for opening and closing the rotary valve 230 and 231 better apparent , Through the side view is FIG. 3 clearly show that the center of the opening between the two rotary valves 230 and 231, depending on the position of the rotary valve 230 and 231 also located next to the center above the nip 103 (103 '). It is envisaged that the rotary valve 230, 231 give the material to be ground 104 centrally above the nip 103 on the high-pressure roller press 100 and give non-symmetrical position the material to be ground 104 out of the center (103 ') above the nip 103 on the high-pressure roller press 100

In Figur 4 ist ein unterer Teil des Schachtes 202 dargestellt, der hier ohne Hydraulikstempel 220, 221, 222 und 223 sowie ohne Hydraulikstempel 260 und 261 abgebildet ist. Durch die Lagerung der Drehschieber 230 und 231 in den Lagern 234 und 235 und der Ausgestaltung der Stirnflächen 236 und 237 der beiden Drehschieber 230 und 231 ist sichergestellt, dass sich die Drehschieber 230 und 231 bei einer Stellung, in welcher sich die Öffnung zwischen beiden Drehschiebern 230 und 231 außerhalb der Mitte über dem Walzenspalt 103 befindet, nicht gegenseitig sperren.In FIG. 4 is shown a lower part of the shaft 202, which is shown here without hydraulic ram 220, 221, 222 and 223 and without hydraulic rams 260 and 261. By the bearing of the rotary valve 230 and 231 in the bearings 234 and 235 and the configuration of the end faces 236 and 237 of the two rotary valves 230 and 231 it is ensured that the rotary valve 230 and 231 at a position in which the opening between the two rotary valves 230 and 231 located outside the center above the nip 103, do not lock each other.

Das Gestellsystem 201 ist vom Schacht 202 trennbar, indem die Hydraulikstempel 220, 221, 222 und 223 vom Gestellsystem 201 gelöst werden. In Figur 5 ist das so abgetrennte Gestellsystem 201 ohne sich bewegende Elemente dargestellt und in Figur 5 als in den Maschinenrahmen 120 einer Hochdruckrollenpresse montiert abgebildet. Nach Montage des Gestellsystems 201, das exakt mittig über den Walzenspalt 103 der Hochdruckrollenpresse ausgerichtet ist, wird der Schacht 202 in das Gestellsystem 201 eingehängt, in dem die Hydraulikstempel 220, 221, 222 und 223 den Schacht 202 mit dem Gestellsystem 201 verbinden und stützen.The rack system 201 is separable from the bay 202 by releasing the hydraulic rams 220, 221, 222, and 223 from the rack system 201. In FIG. 5 is the thus separated rack system 201 shown without moving elements and in FIG. 5 as shown mounted in the machine frame 120 of a high-pressure roller press. After mounting the rack system 201, which is aligned exactly centered on the nip 103 of the high-pressure roller press, the shaft 202 is hooked into the rack system 201, in which the hydraulic rams 220, 221, 222 and 223 connect and support the shaft 202 with the rack system 201.

BEZUGSZEICHENLISTELIST OF REFERENCE NUMBERS

100100 HochdruckrollenpresseHigh-pressure roller press 203203 Innenauskleidunginner lining 233233 Abrasionsschutzabrasion 234234 Lagercamp 101101 Walzeroller 204204 Flanschflange 235235 Lagercamp 102102 Walzeroller 204'204 ' Flanschflange 236236 Stirnflächeface 103103 Walzenspaltnip 210210 Linearlagerlinear bearings 237237 Stirnflächeface 104104 Aufgabegutfeed 211211 Linearlagerlinear bearings 240240 Strebenpursuit 110110 Lagercamp 212212 Linearlagerlinear bearings 241241 Strebenpursuit 111111 Lagercamp 213213 Linearlagerlinear bearings 242242 Strebenpursuit 112112 Lagercamp 214214 Linearlagerlinear bearings 243243 Strebenpursuit 113113 Lagercamp 215215 Linearlagerlinear bearings 250250 Stützesupport 120120 Maschinenrahmenmachine frame 216216 Linearlagerlinear bearings 251251 Stützesupport 217217 Linearlagerlinear bearings 252252 Stützesupport 121121 Traversetraverse 220220 Hydraulikstempelhydraulic ram 253253 Stützesupport 122122 Traversetraverse 221221 Hydraulikstempelhydraulic ram 254254 Stützesupport 123123 Rotationsrichtungdirection of rotation 222222 Hydraulikstempelhydraulic ram 255255 Stützesupport 200200 Aufgabevorrichtungfeeder 223223 Hydraulikstempelhydraulic ram 256256 Stützesupport 230230 Drehschieberrotary vane 257257 stützesupport 201201 Gestellsystemrack system 231231 Drehschieberrotary vane 260260 Hydraulikstempelhydraulic ram 202202 Schachtshaft 232232 Abrasionsschutzabrasion 261261 Hydraulikstempelhydraulic ram

Claims (7)

  1. High-pressure roller press (100) for the high-pressure comminution of grinding stock (104), with a feed device which delivers the grinding stock (104) in a controlled manner into the roller nip (103) between two rollers (101, 102) of the high-pressure roller press (100),
    characterized in that
    the feed device (200) has at least two rotary valves (230, 231), the position of which can be varied independently of one another.
  2. High-pressure roller press according to Claim 1,
    characterized in that
    the rotary valves (230, 231), when symmetrically positioned, deliver the grinding stock (104) centrally above the roller nip (103) onto the high-pressure roller press (100) and, when non-symmetrically positioned, deliver the grinding stock (104) outside the center above the roller nip (103) onto the high-pressure roller press (100).
  3. High-pressure roller press according to Claim 1 or 2,
    characterized in that the rotary valves (230, 231) are disposed on a shaft (202) which is variable in height above the roller nip (103).
  4. High-pressure roller press according to Claim 3,
    characterized in that
    the shaft (202) is provided with an exchangeable inner lining (203) as an abrasion protection.
  5. High-pressure roller press according to one of Claims 3 to 4,
    characterized in that
    the rotary valves (230, 231) are respectively adjustable by means of a hydraulic system (260, 261), wherein the respective hydraulic system (260, 261) acts respectively upon a rotary valve (230, 231) and upon the shaft (202) which is variable in height above the roller nip (103), wherein the respective hydraulic system (260, 261) travels along with the shaft (202) which is variable in height above the roller nip (103).
  6. High-pressure roller press according to one of Claims 1 to 5,
    characterized in that
    the shaft (202) which is variable in height above the roller nip (103) is adjustable in height by means of a hydraulic system (220, 221, 222, 223), wherein the hydraulic system (220, 221, 222, 223), on the one hand, acts upon a rack system (201) which receives the shaft (202) which is variable in height above the roller nip (103), and, on the other hand, acts upon the shaft (202) which is variable in height above the roller nip (103).
  7. High-pressure roller press according to one of Claims 3 to 6,
    characterized in that
    the shaft (202) which is variable in height above the roller nip (103) is mounted in at least one linear bearing (210, 211, 212, 213).
EP09780041.1A 2008-07-09 2009-06-30 Feed device with two rotary valves which are variable independently of each other Not-in-force EP2307144B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202008009234 2008-07-09
PCT/EP2009/058211 WO2010003850A1 (en) 2008-07-09 2009-06-30 Feed device with two rotary valves which are variable independently of each other

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Publication Number Publication Date
EP2307144A1 EP2307144A1 (en) 2011-04-13
EP2307144B1 true EP2307144B1 (en) 2013-09-18

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Country Status (11)

Country Link
US (1) US8439288B2 (en)
EP (1) EP2307144B1 (en)
CN (1) CN102137720B (en)
AU (1) AU2009268180B2 (en)
BR (1) BRPI0915701A2 (en)
CA (1) CA2729880C (en)
CL (1) CL2009001544A1 (en)
DK (1) DK2307144T3 (en)
PE (1) PE20110473A1 (en)
WO (1) WO2010003850A1 (en)
ZA (1) ZA201008402B (en)

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US8439288B2 (en) 2013-05-14
EP2307144A1 (en) 2011-04-13
PE20110473A1 (en) 2011-07-09
AU2009268180A1 (en) 2010-01-14
WO2010003850A1 (en) 2010-01-14
ZA201008402B (en) 2011-12-28
US20110114772A1 (en) 2011-05-19
CN102137720A (en) 2011-07-27
BRPI0915701A2 (en) 2015-10-27
CL2009001544A1 (en) 2010-04-05
DK2307144T3 (en) 2014-01-13
CN102137720B (en) 2013-06-05
CA2729880A1 (en) 2010-01-14
AU2009268180B2 (en) 2014-04-10
CA2729880C (en) 2017-08-01

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