EP0256147A1 - Disc mill - Google Patents

Disc mill Download PDF

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Publication number
EP0256147A1
EP0256147A1 EP86111171A EP86111171A EP0256147A1 EP 0256147 A1 EP0256147 A1 EP 0256147A1 EP 86111171 A EP86111171 A EP 86111171A EP 86111171 A EP86111171 A EP 86111171A EP 0256147 A1 EP0256147 A1 EP 0256147A1
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EP
European Patent Office
Prior art keywords
crushing
disc
bearing housing
crusher according
flange
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP86111171A
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German (de)
French (fr)
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EP0256147B1 (en
Inventor
Ivan Vassilev Dipl.-Ing. Genev
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
N I I PO TSCHERNA METALURGIA
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N I I PO TSCHERNA METALURGIA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to DE19863623751 priority Critical patent/DE3623751A1/en
Application filed by N I I PO TSCHERNA METALURGIA filed Critical N I I PO TSCHERNA METALURGIA
Priority to AT86111171T priority patent/ATE48767T1/en
Priority to EP86111171A priority patent/EP0256147B1/en
Publication of EP0256147A1 publication Critical patent/EP0256147A1/en
Application granted granted Critical
Publication of EP0256147B1 publication Critical patent/EP0256147B1/en
Expired legal-status Critical Current

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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
    • B02C7/00—Crushing or disintegrating by disc mills
    • B02C7/005—Crushers with non-coaxial toothed discs with intersecting axes

Definitions

  • the invention relates to a disc crusher with a crusher housing and a crushing disc rotatably mounted therein, over which a crushing cone is rotatably mounted in an inclined manner in a bearing housing to form a radial crushing gap, the bearing housing with the crushing cone being guided axially displaceably and axially adjustable supporting surfaces being provided against which the bearing housing is braced by means of springs supported on spring stops.
  • Such a disk crusher known from DE-OS 26 06 485 has a horizontally lying, flat crushing disk with a vertical axis of rotation within a crusher housing. Above this crushing disc, a crushing cone is mounted at an incline such that there is a radially and horizontally extending, linear crushing gap with a constant height on one side of the crushing disc. The axes of rotation of the crushing disc and crushing cone intersect on the surface of the crushing disc in the middle. Both the crushing disc and the crushing cone are driven by electric motors, in the same direction and at the same speed.
  • the material to be crushed is applied via an almost vertical inlet channel on the side of the crushing disc opposite the crushing gap and then transported from the crushing disc into the crushing gap on the other side.
  • the crushing then takes place in the crushing gap.
  • a rake located in front of the inlet pipe in the direction of rotation, the broken material is then discharged outwards from the breaking disk into an outlet pipe.
  • the material to be crushed therefore only passes the crushing gap once.
  • the crushing cone is stored in a bearing housing.
  • the bearing housing rests by means of an outer circumferential flange on support surfaces in the form of support nuts which are screwed onto stud bolts projecting outwards from the crusher housing and fixed thereon.
  • the stud bolts run parallel to the axis of rotation of the crushing cone and penetrate the flange.
  • Spring stops are provided at their free ends, helical springs under pressure being provided between these spring stops and the flange of the bearing housing. In this way, the flange and thus the bearing housing and the crushing cone are pressed down towards the crushing disc, the respective position of the support nuts determining the clear height of the crushing gap.
  • the invention is therefore based on the object of improving the disc crusher of the type mentioned at the outset with regard to the suspension of the crushing cone in such a way that even fractions are obtained at different crushing gap heights.
  • a flange of the bearing housing by stud bolts, which run freely through holes in the flange and through the springs, and via an upper and lower flange body with the upper housing part that the upper and have lower flange body opposing external threads and are surrounded on the outside by an adjusting nut, which has threads on the inner surface which correspond to the threads of the upper and lower flange body, that the adjusting nut has a ring gear which is connected to an adjusting gear and a fixing gear, and that on a key is attached to the lower end of the bearing housing and sits in a groove on the inner surface of the lower flange body.
  • the spring stops are rigidly connected to the support surface (s) - and no longer to the crusher housing itself. Due to this design, the distance between the support surface (s) and the spring stops no longer changes when the support surface (s) is adjusted to change the crushing gap, so that the spring preload with which the bearing housing is pressed against the support surface (s) is independent of the height of the crushing gap always remains constant. This has a correspondingly positive impact on the crushing result.
  • the spring stops are fastened to stud bolts which sit in the support surface.
  • the springs are expediently designed as helical or cup springs surrounding the stud bolts.
  • the spring stops should be axially adjustable.
  • the support surface (s) is or are expediently screwed onto stud bolts provided with adjusting threads. They can then be designed as support nuts, for example, which are countered with another nut on the other side.
  • the support surface have a neck portion surrounding the bearing housing and provided with a thread, a nut being screwed onto the thread, said nut being rotatably engaged with a stationary housing part.
  • the height of the support surface is adjusted by turning the nut surrounding the bearing housing, the bearing housing being well guided through the neck section.
  • the adjusting nut should advantageously engage the stationary housing part via a counter thread.
  • an anti-rotation device is also expediently provided, for example in the form of a feather key or the like.
  • the tip of the crushing cone and the center of the crushing disc are connected on the one hand by a centering body and on the other hand by a bore which bears against the inside thereof.
  • a centering body is designed as a centering cone arranged in the crushing disc, which lies in the cylindrical bore in the crushing cone with line contact.
  • the centering body is designed as a centering cylinder arranged in the crushing cone, which lies in the conically widening bore in the crushing disc with line contact.
  • the bearing housing is displaceable transversely to the axis of rotation of the crushing cone in a plane formed by the crushing gap and the axis of rotation.
  • the crushing cone can be offset in the plane of the crushing gap with respect to the crushing disc in order to be able to compensate for uneven wear on the jacket of the crushing cone.
  • the angle of inclination of the working surface of the crushing disc can be 0 ° to 90 °.
  • the disc crusher 1 shown in FIGS. 1 and 2 has a crusher housing 2 which consists of an upper housing part 3, a central housing part 4 and a lower housing part 5. The latter rests on a foot part 6.
  • a flat crushing disk 7 is arranged within the crusher housing 2 and rests on an axial bearing 8 which is surrounded on the outside by a seal 9.
  • a bearing shaft 10 is fastened to the underside of the crushing disk 7 and is guided radially in a downward extension 11 of the lower housing part 5 by means of two ball bearings 12, 13.
  • the extension 11 is closed at the top and bottom by two lids 14, 15.
  • At the lower end of the bearing shaft 10 there is a belt pulley 16, via which the breaker pulley 7 can be rotated by means of a V-belt drive (not shown here). The drive takes place via an electric motor that cannot be seen.
  • a crushing cone 17 is arranged above the crushing disc 7, the back of which is connected to a bearing shaft 18.
  • the axis of rotation of the bearing shaft 18 and the radial surface line of the crushing cone 17 enclose an acute angle ⁇ , the bearing shaft 18 being inclined such that the surface line of the crushing cone 17 running to the left in the plane of the drawing runs horizontally and thus parallel to the surface of the crushing disk 7.
  • the bearing shaft 18 of the crushing cone 17 is supported by a total of three ball bearings 20, 21, 22 in a bearing housing 23, namely by an upper ball bearing 20, which absorbs downward axial forces and radial forces, one designed as an axial bearing for receiving upward axial forces Ball bearing 21 and a lower ball bearing 22 for absorbing radial forces.
  • the interior surrounded by the bearing housing 23 is essentially closed off by two covers 24, 25.
  • a pulley 26 is also attached, which is driven by an electric motor 28 via a V-belt drive 27.
  • a cover 29 supports this part of the disc breaker 1. With the help of this electric motor 28, the crushing cone 17 is set in rotation.
  • the electric motor 28 is screwed via a support 30 to a flange 31 which is integrally formed on the outside of the bearing housing 23.
  • FIG. 1 The support of the flange 31 and thus of the bearing housing 23 on the upper housing part 3 is shown in FIG. 1 in two alternatives, one alternative to the left of the axis of rotation of the bearing shaft 18 and the other alternative to the right thereof.
  • the bearing housing 23 surrounds two flange bodies 32, 33 arranged one above the other.
  • the lower flange body 33 is fixedly connected to the housing top part 3 by means of three screws 34 distributed over the circumference.
  • a key 35 ensures thereby for a non-rotatable but axially loose connection between the bearing housing 23 and the lower flange body 33.
  • the upper flange body 32 is arranged at a distance from the lower one.
  • Both flange bodies 32, 33 have threads 36, 37 running in opposite directions on their lateral surfaces, over which an adjusting nut 38 which surrounds the two threads 36, 37 and surrounds the bearing housing 23 extends.
  • On the outside of a gear rim 39 is rotatably fixed, via which the adjusting nut 38 can be rotated. Because the two threads 36, 37 run in opposite directions, the distance between the two flange bodies 32, 33 can be adjusted in a simple manner in the axial direction.
  • the crushing cone 17 can thus also be moved back and forth in the axial direction via the flange 31 and the bearing housing 23, with the result that the height of the crushing gap 19 changes accordingly.
  • the second alternative shown on the right-hand side has a one-piece flange part 40 with two flange sections 41, 42.
  • the lower flange section 42 is fastened to the upper housing part 3 in a height-adjustable manner via a plurality of stud bolts 43 - only one of which can be seen here.
  • each stud bolt 43 is screwed into the upper housing part 3 and fixed by a lock nut 44.
  • An adjusting element 45 is screwed onto the stud bolt 43, on which the lower flange section 42 is supported.
  • the flange part 40 can be fixed in the respectively set height by a further lock nut 46 resting on the upper side of the flange section 42.
  • the lock nut 46 is loosened, so that the adjusting element 45 is then rotated in one direction or the other can. The same applies to the other, not visible stud bolts.
  • the flange 31 is pressed with its underside against the upper flange body 31 (left alternative) or the upper flange section 41 of the flange part 40 (right alternative) by means of eight helical springs 47, 48 distributed over the circumference - only two can be seen in FIG. 1 .
  • the coil springs 47, 48 are supported via spring stops 49, 50 on stud bolts 51, 52 which pass through the flange 30 and are screwed and fixed in the upper flange body 31 or the upper flange section 41. In this way, the spring preload of the coil springs 47, 48 remains unchanged regardless of the adjustment of the crushing cone 17 in the axial direction - be it by means of the adjusting nut 38 or by means of the adjusting elements 45.
  • a centering cone 53 is arranged in the center of the crushing disk 7, as the partial sectional illustration in FIG. 1 shows, which consists of two cylindrical parts located within the crushing disk 7 and a conically tapering part projecting beyond the surface of the crushing disk 7.
  • the centering cone 53 engages in a coaxial bore 54 in the tip of the crushing cone 17 such that a surface line of the centering cone 53 has line contact with the inner surface of the bore 54. In this way, the crushing cone 17 can be supported on the centering cone 53, so that radial evasive movements due to the load in the crushing gap 19 are avoided.
  • FIG. 4 shows an alternative to the embodiment shown in FIG. 1 for centering in an off position Section shown.
  • a centering sleeve 55 is screwed into the crushing disk 7, which has a conically widening inner wall 57 at its upper end.
  • a centering cylinder 58 bears against this inner wall 57 and is displaceably guided in a coaxial bore 59 in the crushing cone 17.
  • the lower end of the centering cylinder 58 is provided with a chamfer 60, the angle of which is dimensioned such that the chamfer 60 lies flat against the conical inner wall 57. In this way, the crushing cone 17 is supported in both radial directions.
  • FIG. 2 shows in the side view that the disc crusher 1 shown in FIG. 1 additionally sits with its foot part 6 on a wedge-shaped seat 61 and this on a horizontal base frame 62.
  • the arrangement on the wedge-shaped seat 61 has the result that the entire disc crusher 1 is inclined at an angle ⁇ of 0 to 90 ° with respect to the horizontal.
  • the crushing disk 7 thus also has a corresponding inclination, as can be seen from the broken line.
  • the outlet 64 is located just behind the crushing gap 19, approximately at the lowest point of the crushing disk 7. Due to the inclination of the crushing disk 7 and the centrifugal forces, the broken material is here directly into the Outlet 64 spun off without the need for an additional rake, which is subject to high wear, as in the case of the known disk breakers.
  • Figure 3 shows a cross section through the bearing housing 23. It can be seen that the flange body 33 has an approximately triangular shape and is fastened by three screws 34 to the upper housing part 3, which is not visible here. In this case, the first alternative shown on the left in FIG. 1 is shown throughout.
  • the lower flange body 33 has for the passage of the screws 34 in each case elongated holes 65, 66, 67, which in the direction of the crushing gap 19, i. H. extend parallel to the plane of the drawing of Figure 1.
  • elongated holes 65, 66, 67 which in the direction of the crushing gap 19, i. H. extend parallel to the plane of the drawing of Figure 1.

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

Abstract

1. Disc crusher having a crusher housing (2) in which there is mounted a crushing disc (7) connected with a rotary drive (16) and in which there is arranged at an incline, for the purpose of forming a radial crushing gap (19) with the crushing disc (7), a crushing cone (17) which is connected with a rotary drive (26, 27, 28) and is mounted in a bearing housing (23) which is adjustable in relation to the crusher housing (2) for the purpose of varying the crushing gap (19), and having a flange (31) which is provided on the bearing housing (23) and which is displaceable on stay bolts (51) which extend through openings in the flange (31) and with which there are associated springs (48) which are supported under initial tension at the flange (31) and at spring stops (50) supported in an axially adjustable manner by the stay bolts (51), characterised by an upper flange body (32) surrounding the bearing housing (23) and provided with an external thread (37), on which body the stay bolts (51) are fixed and against which body the flange (31) of the bearing housing (23) is pressed by means of the springs (48) ; by a lower flange body (33) which is arranged at a distance from the upper flange body (32), surrounds the bearing housing (23), is fixed (34) on an upper housing portion (3) of the crusher housing (2), is connected by way of an adjusting spring element (35) with the bearing housing (23) in a rotationally secure, but axially displaceable manner and is provided with an external thread (36) which runs in opposition to the external thread (37) of the upper flange body (32) ; and by an adjusting nut (38) which is in threaded engagement with the external threads (37, 36) of the upper and lower flange body (32, 33) and supports on its outside in a rotationally secure manner a toothed ring (39) for the engagement with an adjusting and fixing gear unit.

Description

Die Erfindung betrifft einen Scheibenbrecher mit einem Brechergehäuse und einer darin drehbar gelagerten Brech­scheibe, über der in einem Lagergehäuse ein Brechkegel unter Bildung eines radialen Brechspaltes geneigt dreh­bar gelagert ist, wobei das Lagergehäuse mit dem Brech­kegel axial verschieblich geführt und axial verstell­bare Abstützflächen vorgesehen sind, gegen die das Lager­gehäuse mittels sich an Federanschlägen abstützenden Federn verspannt ist.The invention relates to a disc crusher with a crusher housing and a crushing disc rotatably mounted therein, over which a crushing cone is rotatably mounted in an inclined manner in a bearing housing to form a radial crushing gap, the bearing housing with the crushing cone being guided axially displaceably and axially adjustable supporting surfaces being provided against which the bearing housing is braced by means of springs supported on spring stops.

Ein solcher aus der DE-OS 26 06 485 bekannter Scheiben­brecher hat innerhalb eines Brechergehäuses eine horizon­tal liegende, ebene Brechscheibe mit vertikaler Drehachse. Oberhalb dieser Brechscheibe ist ein Brechkegel derart ge­neigt gelagert, daß sich ein radial und horizontal er­streckender, linearer Brechspalt mit konstanter Höhe auf einer Seite der Brechscheibe ergibt. Die Drehachsen von Brechscheibe und Brechkegel schneiden sich auf der Ober­fläche der Brechscheibe in deren Mitte. Sowohl Brechschei­be als auch Brechkegel werden von Elektromotoren angetrie­ben, und zwar gleichsinnig und mit gleicher Drehzahl.Such a disk crusher known from DE-OS 26 06 485 has a horizontally lying, flat crushing disk with a vertical axis of rotation within a crusher housing. Above this crushing disc, a crushing cone is mounted at an incline such that there is a radially and horizontally extending, linear crushing gap with a constant height on one side of the crushing disc. The axes of rotation of the crushing disc and crushing cone intersect on the surface of the crushing disc in the middle. Both the crushing disc and the crushing cone are driven by electric motors, in the same direction and at the same speed.

Das zu brechende Gut wird über einen nahezu senkrecht verlaufenden Einlaßkanal auf der dem Brechspalt gegen­überliegenden Seite der Brechscheibe aufgebracht und von der Brechscheibe dann in den Brechspalt auf der anderen Seite transportiert. Im Brechspalt findet dann die Zerkleinerung statt. Mittels eines in Drehrichtung vor dem Einlaßrohr befindlichen Rechen wird anschließend das gebrochene Gut von der Brechscheibe nach außen in ein Auslaßrohr abgeführt. Das zu brechende Gut passiert also nur einmal den Brechspalt.The material to be crushed is applied via an almost vertical inlet channel on the side of the crushing disc opposite the crushing gap and then transported from the crushing disc into the crushing gap on the other side. The crushing then takes place in the crushing gap. By means of a rake located in front of the inlet pipe in the direction of rotation, the broken material is then discharged outwards from the breaking disk into an outlet pipe. The material to be crushed therefore only passes the crushing gap once.

Der Brechkegel ist in einem Lagergehäuse gelagert. Das La­gergehäuse ruht mittels eines außen umlaufenden Flansches auf Abstützflächen in Form von Abstützmuttern, die auf von dem Brechergehäuse nach außen vorstehende und an die­sem fixierte Stehbolzen geschraubt sind. Die Stehbolzen verlaufen achsparallel zur Drehachse des Brechkegels und durchdringen den Flansch. An ihren freien Enden sind Fe­deranschläge vorgesehen, wobei zwischen diesen Federan­schlägen und dem Flansch des Lagergehäuses auf Druck bean­spruchte Schraubenfedern vorgesehen sind. Auf diese Weise werden der Flansch und damit das Lagergehäuse und der Brech­kegel nach unten in Richtung auf die Brechscheibe ge­drückt, wobei die jeweilige Stellung der Abstützmuttern die lichte Höhe des Brechspaltes bestimmen. Durch Drehen der Abstützmuttern läßt sich das Lagergehäuse und damit der Brechkegel nach oben oder nach unten axial verfahren, wodurch die lichte Höhe des Brechspaltes eingestellt wer­den kann.The crushing cone is stored in a bearing housing. The bearing housing rests by means of an outer circumferential flange on support surfaces in the form of support nuts which are screwed onto stud bolts projecting outwards from the crusher housing and fixed thereon. The stud bolts run parallel to the axis of rotation of the crushing cone and penetrate the flange. Spring stops are provided at their free ends, helical springs under pressure being provided between these spring stops and the flange of the bearing housing. In this way, the flange and thus the bearing housing and the crushing cone are pressed down towards the crushing disc, the respective position of the support nuts determining the clear height of the crushing gap. By turning the support nuts, the bearing housing and thus the crushing cone can be moved axially upwards or downwards, whereby the clear height of the crushing gap can be adjusted.

Diese konstruktive Ausgestaltung der vorge­spannten Festlegung des Lagergehäuses hat zur Folge, daß eine Verstellung der Abstützmuttern eine Änderung der Vor­spannkraft der Schraubenfedern nach sich zieht. Die An­preßkraft ist somit abhängig von der jeweils eingestell­ten Höhe des Brechspaltes, wobei die Anpreßkraft um so größer ist, je höher der Brechspalt ist. Dies ist für das Brechergebnis von erheblichem Nachteil, da die Nachgie­bigkeit des Brechkegels mit kleiner werdendem Brechspalt größer wird, und umgekehrt.This structural design of the preloaded fixing of the bearing housing has the consequence that an adjustment of the support nuts leads to a change in the preload force of the coil springs. The contact pressure is therefore dependent on the respectively set height of the crushing gap, the contact force being greater the higher the crushing gap. This is of considerable disadvantage for the crushing result, since the flexibility of the crushing cone increases as the crushing gap becomes smaller, and vice versa.

Ein weiterer Nachteil ist darin zu sehen, daß die bisher bekannte Lagerung des Brechkegels nicht befrie­digend ist. Bei ungleichmäßiger Verteilung des zu brechenden Gutes auf der Brechscheibe kommt es zu Verkantungen des Brechkegels, also zu einer radialen Ausweichbewegung mit der Folge, daß die erhaltenen Fraktionen nicht der Anforderungen ent­sprechen.Another disadvantage is that so far known storage of the crushing cone is not satisfactory. If the material to be crushed is distributed unevenly on the crushing disc, the crushing cone is tilted, that is to say a radial evasive movement with the result that the fractions obtained do not meet the requirements.

Der Erfindung liegt somit die Aufgabe zugrunde, den Scheibenbrecher der eingangs genannten Art be­züglich der Aufhängung des Brechkegels so zu ver­bessern, daß auch bei unterschiedlichen Brechspalt­höhen gleichmäßige Fraktionen erhalten werden.The invention is therefore based on the object of improving the disc crusher of the type mentioned at the outset with regard to the suspension of the crushing cone in such a way that even fractions are obtained at different crushing gap heights.

Diese Aufgabe wird bei dem Scheibenbrecher der eingangs genannten Art dadurch gelöst, daß ein Flansch des Lagergehäuses durch Stehbolzen, die frei durch Bohrungen im Flansch und durch die Federn laufen, und über einen oberen und unteren Flanschkörper mit dem Gehäuseoberteil ver­bunden ist, daß der obere und untere Flansch­körper gegenläufige Außengewinde aufweisen und außen von einer Verstellmutter umfaßt sind, welche auf der Innenfläche Gewinde hat, welche den Gewinden des oberen und unteren Flansch­körpers entsprechen, daß die Verstellmutter einen Zahnkranz aufweist, der mit einem Ver­stellgetriebe und einem Fixiergetriebe verbunden ist, und daß am unteren Ende des Lagergehäuses eine Paßfeder angebracht ist, welche in einer Nut auf der Innenfläche des unteren Flanschkörpers sitzt.This object is achieved in the disk crusher of the type mentioned in that a flange of the bearing housing by stud bolts, which run freely through holes in the flange and through the springs, and via an upper and lower flange body with the upper housing part that the upper and have lower flange body opposing external threads and are surrounded on the outside by an adjusting nut, which has threads on the inner surface which correspond to the threads of the upper and lower flange body, that the adjusting nut has a ring gear which is connected to an adjusting gear and a fixing gear, and that on a key is attached to the lower end of the bearing housing and sits in a groove on the inner surface of the lower flange body.

Erfindungsgemäß sind somit die Federan­schläge starr mit der bzw. den Abstütz­fläche(n) - und nicht mehr mit dem Brecher­gehäuse selbst - verbunden. Aufgrund dieser Gestaltung ändert sich bei einer Höhenver­stellung der Abstützfläche(n) zur Ver­änderung des Brechspaltes nicht mehr der Ab­stand zwischen der Abstützfläche(n) und den Federanschlägen, so daß die Federvorspannung, mit der das Lagergehäuse gegen die Abstütz­fläche(n) gedrückt wird, unabhängig von der Höhe des Brechspaltes immer konstant bleibt. Dies hat entsprechend positive Auswirkungen auf das Brechergebnis.According to the invention, the spring stops are rigidly connected to the support surface (s) - and no longer to the crusher housing itself. Due to this design, the distance between the support surface (s) and the spring stops no longer changes when the support surface (s) is adjusted to change the crushing gap, so that the spring preload with which the bearing housing is pressed against the support surface (s) is independent of the height of the crushing gap always remains constant. This has a correspondingly positive impact on the crushing result.

In Ausbildung der Erfindung ist vorgesehen, daß die Federanschläge an Stehbolzen befestigt sind, die in der Abstützfläche sitzen. Zweckmäßigerweise sind die Federn als die Stehbolzen umgebende Schrauben- oder Teller­federn ausgebildet. Zur Einstellbarkeit der Federvorspannung sollten die Feder­anschläge axial verstellbar angeordnet sein.In an embodiment of the invention it is provided that the spring stops are fastened to stud bolts which sit in the support surface. The springs are expediently designed as helical or cup springs surrounding the stud bolts. To adjust the spring preload, the spring stops should be axially adjustable.

In Abweichung von den bisher bekannten Schraubenfedern besteht auch die Möglich­keit, hydropneumatische Federn zu verwenden, wobei zur Einstellung der Federvorspannung der Füllgrad der hydropneumatischen Federn mit Hydrauliköl veränderbar sein sollte. Der Vorteil dieser Ausführung besteht darin, daß die Federvorspannung auf einfache und schnelle Weise verändert werden kann.In deviation from the previously known coil springs, there is also the possibility of using hydropneumatic springs use, the degree of filling of the hydropneumatic springs should be changeable with hydraulic oil to adjust the spring preload. The advantage of this design is that the spring preload can be changed quickly and easily.

Die Abstützfläche(n) ist bzw. sind zweckmäßigerweise auf mit Verstellgewinden versehenen Stehbolzen aufgeschraubt. Sie können dann beispielsweise als Abstützmuttern ausge­bildet sein, die auf der anderen Seite mit einer weiteren Mutter gekontert werden.The support surface (s) is or are expediently screwed onto stud bolts provided with adjusting threads. They can then be designed as support nuts, for example, which are countered with another nut on the other side.

In Abweichung dazu ist vorgeschlagen, daß die Abstützflä­che einen das Lagergehäuse umgebenden und mit einem Gewin­de versehenen Halsabschnitt hat, wobei auf das Gewinde eine Mutter geschraubt ist, die mit einem ortsfesten Ge­häuseteil drehbar in Eingriff steht. Durch Drehen der das Lagergehäuse umgebenden Mutter wird die Abstützfläche in ihrer Höhe verstellt, wobei das Lagergehäuse durch den Halsabschnitt gut geführt wird. Vorteilhafterweise sollte die Verstellmutter mit dem ortsfesten Gehäuseteil über ein Gegengewinde in Eingriff stehen.In deviation from this, it is proposed that the support surface have a neck portion surrounding the bearing housing and provided with a thread, a nut being screwed onto the thread, said nut being rotatably engaged with a stationary housing part. The height of the support surface is adjusted by turning the nut surrounding the bearing housing, the bearing housing being well guided through the neck section. The adjusting nut should advantageously engage the stationary housing part via a counter thread.

Zwischen Lagergehäuse und ortsfestem Gehäuseteil ist zweckmäßigerweise zusätzlich noch eine Verdrehsicherung vorgesehen, beispielsweise in Form einer Paßfeder oder dergleichen.Between the bearing housing and the stationary housing part, an anti-rotation device is also expediently provided, for example in the form of a feather key or the like.

Um den Brechkegel besser abstützen zu können, ist gemäß der Erfindung vorgesehen, daß die Spitze des Brechkegels und die Mitte der Brechscheibe durch einerseits einen Zen­trierkörper und andererseits eine an diesem mit der Innen­seite anliegende Bohrung verbunden sind. Dabei sind zwei verschiedene Alternativen denkbar. Bei der ersten Alterna­ tive ist der Zentrierkörper als in der Brechscheibe ange­ordneter Zentrierkegel ausgebildet, der in der zylin­drisch ausgebildeten Bohrung im Brechkegel mit Linienbe­rührung anliegt. Bei der zweiten Alternative ist der Zen­trierkörper als im Brechkegel angeordneter Zentrierzylin­der ausgebildet, der in der kegelförmig sich verbreitern­den Bohrung in der Brechscheibe mit Linienberührung an­liegt. In beiden Fällen wird der Brechkegel nunmehr beid­seitig einmal durch das Lagergehäuse und andererseits durch den Zentrierkörper abgestützt, so daß ein Auswei­chen des Brechkegels nicht mehr möglich ist.In order to be able to better support the crushing cone, it is provided according to the invention that the tip of the crushing cone and the center of the crushing disc are connected on the one hand by a centering body and on the other hand by a bore which bears against the inside thereof. Two different alternatives are conceivable. At the first alterna tive the centering body is designed as a centering cone arranged in the crushing disc, which lies in the cylindrical bore in the crushing cone with line contact. In the second alternative, the centering body is designed as a centering cylinder arranged in the crushing cone, which lies in the conically widening bore in the crushing disc with line contact. In both cases, the crushing cone is now supported on both sides by the bearing housing and on the other hand by the centering body, so that evasion of the crushing cone is no longer possible.

Nach der Erfindung ist schließlich vorgesehen, daß das Lagergehäuse quer zur Drehachse des Brechkegels in einer von Brechspalt und Drehachse gebildeten Ebene verschieb­lich ist. Auf Grund dieser Ausbildung kann der Brechkegel in der Ebene des Brechspaltes gegenüber der Brechscheibe versetzt werden, um ungleichmäßigen Verschleiß auf dem Man­tel des Brechkegels ausgleichen zu können. Der Neigungswinkel der Arbeitsfläche der Brechscheibe kann 0° bis 90° betragen.According to the invention it is finally provided that the bearing housing is displaceable transversely to the axis of rotation of the crushing cone in a plane formed by the crushing gap and the axis of rotation. On the basis of this design, the crushing cone can be offset in the plane of the crushing gap with respect to the crushing disc in order to be able to compensate for uneven wear on the jacket of the crushing cone. The angle of inclination of the working surface of the crushing disc can be 0 ° to 90 °.

Anhand von Zeichnungen wird ein Ausführungsbeispiel der Erfindung näher erläutert. Es zeigen:

  • Fig. 1 einen Schnitt durch den Scheibenbrecher in der von beiden Drehachsen und dem Brechspalt gebildeten Ebene;
  • Fig. 2 eine Seitenansicht des Scheibenbrechers von Figur 1 in Richtung des Brechspal­tes gemäß Pfeil A in Fig. 1;
  • Fig. 3 einen Querschnitt durch das Lagergehäuse des Scheibenbrechers gemäß Fig. 1 und 2 und
  • Fig. 4 vergrößert eine Zentriereinrichtung des Brechkegels im Scheibenbrecher.
An exemplary embodiment of the invention is explained in more detail with reference to drawings. Show it:
  • 1 shows a section through the disc crusher in the plane formed by both axes of rotation and the crushing gap.
  • FIG. 2 shows a side view of the disk breaker from FIG. 1 in the direction of the crushing gap according to arrow A in FIG. 1;
  • Fig. 3 shows a cross section through the bearing housing of the disc breaker according to FIGS. 1 and 2 and
  • Fig. 4 enlarges a centering device of the crushing cone in the disc crusher.

Der in den Figuren 1 und 2 dargestellte Scheibenbrecher 1 weist ein Brechergehäuse 2 auf, das aus einem Gehäuseober­teil 3, einem Gehäusemittelteil 4 und einem Gehäuseunter­teil 5 besteht. Letzteres ruht auf einem Fußteil 6.The disc crusher 1 shown in FIGS. 1 and 2 has a crusher housing 2 which consists of an upper housing part 3, a central housing part 4 and a lower housing part 5. The latter rests on a foot part 6.

Innerhalb des Brechergehäuses 2 ist eine ebene Brechschei­be 7 angeordnet, die auf einem Axiallager 8 ruht, das außenseitig von einer Dichtung 9 umgeben ist. An der Un­terseite der Brechscheibe 7 ist eine Lagerwelle 10 befe­stigt, die in einem nach unten gehenden Fortsatz 11 des Gehäuseunterteils 5 mittels zweier Kugellager 12, 13 ra­dial geführt ist. Der Fortsatz 11 ist oben und unten von zwei Deckeln 14, 15 abgeschlossen. Am unte­ren Ende der Lagerwelle 10 befindet sich eine Riemenschei­be 16, über die die Brechscheibe 7 mittels eines hier nicht näher dargestellten Keilriementriebes in Drehung versetzt werden kann. Der Antrieb erfolgt dabei über einen nicht zu sehenden Elektromotor.A flat crushing disk 7 is arranged within the crusher housing 2 and rests on an axial bearing 8 which is surrounded on the outside by a seal 9. A bearing shaft 10 is fastened to the underside of the crushing disk 7 and is guided radially in a downward extension 11 of the lower housing part 5 by means of two ball bearings 12, 13. The extension 11 is closed at the top and bottom by two lids 14, 15. At the lower end of the bearing shaft 10 there is a belt pulley 16, via which the breaker pulley 7 can be rotated by means of a V-belt drive (not shown here). The drive takes place via an electric motor that cannot be seen.

Oberhalb der Brechscheibe 7 ist ein Brechkegel 17 angeord­net, dessen Rückseite mit einer Lagerwelle 18 verbunden ist. Die Drehachse der Lagerwelle 18 und die radiale Man­tellinie des Brechkegels 17 schließen einen spitzen Win­kel β ein, wobei die Lagerwelle 18 derart geneigt ist, daß die in der Zeichnungsebene nach links verlaufende Man­tellinie des Brechkegels 17 horizontal und damit parallel zur Oberfläche der Brechscheibe 7 verläuft. Dabei besteht zwischen dieser Mantellinie und der Brechscheibe 7 ein ra­ dial verlaufender Brechspalt 19, der sich praktisch über die gesamte linke Hälfte der Brechscheibe 7 erstreckt und auf Grund der Parallelität konstante Höhe hat.A crushing cone 17 is arranged above the crushing disc 7, the back of which is connected to a bearing shaft 18. The axis of rotation of the bearing shaft 18 and the radial surface line of the crushing cone 17 enclose an acute angle β, the bearing shaft 18 being inclined such that the surface line of the crushing cone 17 running to the left in the plane of the drawing runs horizontally and thus parallel to the surface of the crushing disk 7. There is a ra between this surface line and the crushing disc 7 dial-running crushing gap 19, which extends practically over the entire left half of the crushing disc 7 and has a constant height due to the parallelism.

Die Lagerwelle 18 des Brechkegels 17 ist über insgesamt drei Kugellager 20, 21, 22 in einem Lagergehäuse 23 gela­gert, und zwar durch ein oberes Kugellager 20, das nach unten gerichtete Axialkräfte und Radialkräfte aufnimmt, ein als Axiallager zur Aufnahme von nach oben gerichteten Axialkräften ausgebildetes Kugellager 21 und ein unteres Kugellager 22 zur Aufnahme von Radialkräften. Der vom Lagergehäuse 23 umgebene Innenraum ist durch zwei Deckel 24, 25 im wesentlichen abgeschlossen.The bearing shaft 18 of the crushing cone 17 is supported by a total of three ball bearings 20, 21, 22 in a bearing housing 23, namely by an upper ball bearing 20, which absorbs downward axial forces and radial forces, one designed as an axial bearing for receiving upward axial forces Ball bearing 21 and a lower ball bearing 22 for absorbing radial forces. The interior surrounded by the bearing housing 23 is essentially closed off by two covers 24, 25.

Am oberen Ende der Lagerwelle 18 ist gleichfalls eine Rie­menscheibe 26 angebracht, die über einen Keilriemenan­trieb 27 von einem Elektromotor 28 angetrieben ist. Eine Abdeckhaube 29 stützt diesen Teil des Scheibenbrechers 1. Mit Hilfe dieses Elektromotors 28 wird der Brechkegel 17 in Drehung versetzt. Der Elektromotor 28 ist über eine Stütze 30 an einem Flansch 31 angeschraubt, welcher an der Außenseite des Lagergehäuses 23 angeformt ist.At the upper end of the bearing shaft 18, a pulley 26 is also attached, which is driven by an electric motor 28 via a V-belt drive 27. A cover 29 supports this part of the disc breaker 1. With the help of this electric motor 28, the crushing cone 17 is set in rotation. The electric motor 28 is screwed via a support 30 to a flange 31 which is integrally formed on the outside of the bearing housing 23.

Die Abstützung des Flansches 31 und damit des Lagergehäu­ses 23 am Gehäuseoberteil 3 ist in Figur 1 in zwei Alter­nativen dargestellt, wobei die eine Alternative links von der Drehachse der Lagerwelle 18 und die andere Alternati­ve rechts davon zu sehen ist.The support of the flange 31 and thus of the bearing housing 23 on the upper housing part 3 is shown in FIG. 1 in two alternatives, one alternative to the left of the axis of rotation of the bearing shaft 18 and the other alternative to the right thereof.

Bei der ersten Alternative auf der linken Seite umgeben das Lagergehäuse 23 zwei übereinander angeordnete Flansch­körper 32, 33. Der untere Flanschkörper 33 ist mittels dreier über dem Umfang verteilter Schrauben 34 fest mit dem Gehäuseoberteil 3 verbunden. Eine Paßfeder 35 sorgt dabei für eine drehfeste, aber axial lose Verbindung zwi­schen Lagergehäuse 23 und unterem Flanschkörper 33. Der obere Flanschkörper 32 ist im Abstand zum unteren ange­ordnet.In the first alternative on the left side, the bearing housing 23 surrounds two flange bodies 32, 33 arranged one above the other. The lower flange body 33 is fixedly connected to the housing top part 3 by means of three screws 34 distributed over the circumference. A key 35 ensures thereby for a non-rotatable but axially loose connection between the bearing housing 23 and the lower flange body 33. The upper flange body 32 is arranged at a distance from the lower one.

Beide Flanschkörper 32, 33 weisen auf ihren Mantelflächen gegenläufige Gewinde 36, 37 auf, über die sich eine in beide Gewinde 36, 37 einfassende, das Lagergehäuse 23 um­gebende Verstellmutter 38 erstreckt. Auf deren Außenseite ist drehfest ein Zahnkranz 39 befestigt, über den die Ver­stellmutter 38 verdreht werden kann. Aufgrund der Gegen­läufigkeit der beiden Gewinde 36, 37 läßt sich der Ab­stand der beiden Flanschkörper 32, 33 in axialer Richtung auf einfache Weise verstellen. Über den Flansch 31 und das Lagergehäuse 23 kann damit auch der Brechkegel 17 in axialer Richtung hin- und herbewegt werden, was zur Folge hat, daß sich die Höhe des Brechspaltes 19 entsprechend verändert.Both flange bodies 32, 33 have threads 36, 37 running in opposite directions on their lateral surfaces, over which an adjusting nut 38 which surrounds the two threads 36, 37 and surrounds the bearing housing 23 extends. On the outside of a gear rim 39 is rotatably fixed, via which the adjusting nut 38 can be rotated. Because the two threads 36, 37 run in opposite directions, the distance between the two flange bodies 32, 33 can be adjusted in a simple manner in the axial direction. The crushing cone 17 can thus also be moved back and forth in the axial direction via the flange 31 and the bearing housing 23, with the result that the height of the crushing gap 19 changes accordingly.

Die auf der rechten Seite gezeigte, zweite Alternative weist einen einteiligen Flanschteil 40 mit zwei Flanschab­schnitten 41, 42 auf. Der untere Flanschabschnitt 42 ist über mehrere Stehbolzen 43 - von denen hier nur einer zu sehen ist - am Gehäuseoberteil 3 höhenverstellbar befe­stigt. Hierzu ist jeder Stehbolzen 43 in das Gehäuseober­teil 3 eingeschraubt und durch eine Kontermutter 44 fixiert. Auf den Stehbolzen 43 ist ein Verstellelement 45 aufgeschraubt, auf das sich der untere Flanschabschnitt 42 abstützt. Durch eine an der Oberseite des Flanschab­schnittes 42 anliegende, weitere Kontermutter 46 ist der Flanschteil 40 in der jeweils eingestellte Höhe fixier­bar. Zum Verstellen der Höhe des Flanschteils 40 wird die Kontermutter 46 gelöst, so daß dann das Verstellelement 45 in der einen oder anderen Richtung gedreht werden kann. Entsprechend verfährt man bei den übrigen, nicht sichtbaren Stehbolzen.The second alternative shown on the right-hand side has a one-piece flange part 40 with two flange sections 41, 42. The lower flange section 42 is fastened to the upper housing part 3 in a height-adjustable manner via a plurality of stud bolts 43 - only one of which can be seen here. For this purpose, each stud bolt 43 is screwed into the upper housing part 3 and fixed by a lock nut 44. An adjusting element 45 is screwed onto the stud bolt 43, on which the lower flange section 42 is supported. The flange part 40 can be fixed in the respectively set height by a further lock nut 46 resting on the upper side of the flange section 42. To adjust the height of the flange part 40, the lock nut 46 is loosened, so that the adjusting element 45 is then rotated in one direction or the other can. The same applies to the other, not visible stud bolts.

Der Flansch 31 wird mittels acht über den Umfang verteil­ter Schraubenfedern 47, 48 - nur zwei sind in Figur 1 zu sehen - mit seiner Unterseite gegen den oberen Flansch­körper 31 (linke Alternative) bzw. den oberen Flanschab­schnitt 41 des Flanschteils 40 (rechte Alternative) ge­drückt. Die Schraubenfedern 47, 48 stützen sich über Fe­deranschläge 49, 50 an Stehbolzen 51, 52 ab, die durch den Flansch 30 hindurchgehen und in dem oberen Flanschkör­per 31 bzw. den oberen Flanschabschnitt 41 eingeschraubt und fixiert sind. Auf diese Weise bleibt die Federvorspan­nung der Schraubenfedern 47, 48 unabhängig von der Ver­stellung des Brechkegels 17 in axialer Richtung - sei es mittels der Verstellmutter 38 oder mittels der Verstell­elemente 45 - unverändert.The flange 31 is pressed with its underside against the upper flange body 31 (left alternative) or the upper flange section 41 of the flange part 40 (right alternative) by means of eight helical springs 47, 48 distributed over the circumference - only two can be seen in FIG. 1 . The coil springs 47, 48 are supported via spring stops 49, 50 on stud bolts 51, 52 which pass through the flange 30 and are screwed and fixed in the upper flange body 31 or the upper flange section 41. In this way, the spring preload of the coil springs 47, 48 remains unchanged regardless of the adjustment of the crushing cone 17 in the axial direction - be it by means of the adjusting nut 38 or by means of the adjusting elements 45.

In der Mitte der Brechscheibe 7 ist - wie die Teilschnitt­darstellung in Figur 1 zeigt - ein Zentrierkegel 53 ange­ordnet, der aus zwei zylindrischen, innerhalb der Brech­scheibe 7 befindlichen Teilen und einem konisch zulaufen­den, über die Oberfläche der Brechscheibe 7 vorstehenden Teil besteht. Der Zentrierkegel 53 faßt in eine koaxiale Bohrung 54 in der Spitze des Brechkegels 17 derart ein, daß eine Mantellinie des Zentrierkegels 53 Linienberüh­rung mit der Innenfläche der Bohrung 54 hat. Auf diese Weise kann sich der Brechkegel 17 an dem Zentrierkegel 53 zusätzlich abstützen, so daß radiale Ausweichbewegungen auf Grund der Belastung im Brechspalt 19 vermieden wer­den.A centering cone 53 is arranged in the center of the crushing disk 7, as the partial sectional illustration in FIG. 1 shows, which consists of two cylindrical parts located within the crushing disk 7 and a conically tapering part projecting beyond the surface of the crushing disk 7. The centering cone 53 engages in a coaxial bore 54 in the tip of the crushing cone 17 such that a surface line of the centering cone 53 has line contact with the inner surface of the bore 54. In this way, the crushing cone 17 can be supported on the centering cone 53, so that radial evasive movements due to the load in the crushing gap 19 are avoided.

In Figur 4 ist eine Alternative zu der in Figur 1 darge­stellten Ausführungsform für die Zentrierung in einem Aus­ Schnitt dargestellt. In die Brechscheibe 7 ist hier an­statt des Zentrierkegels 53 eine Zentrierhülse 55 einge­schraubt, die an ihrem oberen Ende eine konisch sich er­weiternde Innenwandung 57 aufweist. An dieser Innenwan­dung 57 liegt ein Zentrierzylinder 58 an, der in einer ko­axialen Bohrung 59 im Brechkegel 17 verschieblich geführt ist. Dabei ist das untere Ende des Zentrierzylinders 58 mit einer Fase 60 versehen, deren Winkel so bemessen ist, daß die Fase 60 flächig an der konischen Innenwandung 57 anliegt. Auf diese Weise ist der Brechkegel 17 in beiden radialen Richtungen abgestützt.FIG. 4 shows an alternative to the embodiment shown in FIG. 1 for centering in an off position Section shown. Instead of the centering cone 53, a centering sleeve 55 is screwed into the crushing disk 7, which has a conically widening inner wall 57 at its upper end. A centering cylinder 58 bears against this inner wall 57 and is displaceably guided in a coaxial bore 59 in the crushing cone 17. The lower end of the centering cylinder 58 is provided with a chamfer 60, the angle of which is dimensioned such that the chamfer 60 lies flat against the conical inner wall 57. In this way, the crushing cone 17 is supported in both radial directions.

Figur 2 läßt in der Seitenansicht erkennen, daß der in Fi­gur 1 dargestellte Scheibenbrecher 1 mit seinem Fußteil 6 zusätzlich auf einem keilförmigen Sitz 61 und dieser auf einem horizontalen Grundrahmen 62 sitzen. Die Anordnung auf dem keilförmigen Sitz 61 hat zur Folge, daß der gesam­te Scheibenbrecher 1 um einen Winkel α von 0 bis 90° gegenüber der Horizontalen geneigt ist. Eine entsprechende Neigung hat damit auch die Brechscheibe 7, wie sich aus der gestrichelten Darstellung ersehen läßt. Rechts von der Brechscheibe 7 befindet sich nahe dem Brechspalt 19 ein Einlaß 63, dessen unterer Teil etwa die Neigung der Brechscheibe 7 hat. Auf Grund dessen fällt das zu brechende Gut praktisch unmittelbar in den Brechspalt 19 und kann somit nicht von der sich schnell drehenden Brechscheibe 7 abgeschleudert werden. Außerdem wird ein gleichmäßigerer Abrieb über die Breite des Brech­spaltes 19 erreicht.FIG. 2 shows in the side view that the disc crusher 1 shown in FIG. 1 additionally sits with its foot part 6 on a wedge-shaped seat 61 and this on a horizontal base frame 62. The arrangement on the wedge-shaped seat 61 has the result that the entire disc crusher 1 is inclined at an angle α of 0 to 90 ° with respect to the horizontal. The crushing disk 7 thus also has a corresponding inclination, as can be seen from the broken line. To the right of the crushing disk 7 there is an inlet 63 near the crushing gap 19, the lower part of which has approximately the inclination of the crushing disk 7. Because of this, the material to be crushed practically falls directly into the crushing gap 19 and therefore cannot be thrown off by the rapidly rotating crushing disk 7. In addition, a more uniform abrasion is achieved across the width of the crushing gap 19.

Kurz hinter dem Brechspalt 19 in etwa an der tiefsten Stelle der Brechscheibe 7 befindet sich der Auslaß 64. Auf Grund der Neigung der Brechscheibe 7 und der Zentrifu­galkräfte wird hier das gebrochene Gut unmittelbar in den Auslaß 64 abgeschleudert, ohne daß es hierzu - wie noch bei den vorbekannten Scheibenbrechern - eines zusätzli­chen Rechens bedarf, der hohem Verschleiß unterworfen ist.The outlet 64 is located just behind the crushing gap 19, approximately at the lowest point of the crushing disk 7. Due to the inclination of the crushing disk 7 and the centrifugal forces, the broken material is here directly into the Outlet 64 spun off without the need for an additional rake, which is subject to high wear, as in the case of the known disk breakers.

Figur 3 zeigt einen Querschnitt durch das Lagergehäuse 23. Es läßt sich ersehen, daß der Flanschkörper 33 eine etwa dreiecksförmige Gestalt hat und durch drei Schrauben 34 an dem hier nicht sichtbaren Gehäuseoberteil 3 befe­stigt ist. Dabei ist in diesem Fall die in Figur 1 links dargestellte, erste Alternative durchgängig gezeigt.Figure 3 shows a cross section through the bearing housing 23. It can be seen that the flange body 33 has an approximately triangular shape and is fastened by three screws 34 to the upper housing part 3, which is not visible here. In this case, the first alternative shown on the left in FIG. 1 is shown throughout.

Der untere Flanschkörper 33 weist für den Durchgang der Schrauben 34 jeweils Langlöcher 65, 66, 67 auf, die sich in Richtung des Brechspaltes 19, d. h. parallel zur Zeich­nungsebene der Figur 1, erstrecken. Auf diese Weise be­steht die Möglichkeit, das Lagergehäuse 23 mit dem Brech­kegel 17 in Richtung der Erstreckung des Brechspaltes 19 parallel zu verschieben, um ungleichmäßigen Abrieb am Brechkegel 17 ausgleichen zu können. Voraussetzung hier­für ist allerdings, daß in der Spitze des Brechkegels 17 und in der Mitte der Brechscheibe 7 nicht die in den Figu­ren 1 und 4 dargestellte Zentriereinrichtung vorgesehen ist, denn diese Zentriereinrichtung soll gerade solche Be­wegungen verhindern.The lower flange body 33 has for the passage of the screws 34 in each case elongated holes 65, 66, 67, which in the direction of the crushing gap 19, i. H. extend parallel to the plane of the drawing of Figure 1. In this way, it is possible to move the bearing housing 23 with the crushing cone 17 in parallel in the direction of the extent of the crushing gap 19 in order to be able to compensate for uneven abrasion on the crushing cone 17. A prerequisite for this, however, is that the centering device shown in FIGS. 1 and 4 is not provided in the tip of the crushing cone 17 and in the center of the crushing disk 7, because this centering device is intended to prevent such movements.

Claims (15)

1. Scheibenbrecher mit einem Brechergehäuse und einer darin drehbar gelagerten Brechscheibe, über der in einem Lagergehäuse ein Brechkegel unter Bildung eines radialen Brechspaltes geneigt drehbar ge­lagert ist, wobei das Lagergehäuse mit dem Brech­kegel axial verschieblich geführt und axial ver­stellbare Abstützflächen vorgesehen sind, gegen die das Lagergehäuse mittels sich an Federanschlägen abstützenden Federn verspannt ist, dadurch ge­kennzeichnet, daß ein Flansch (31) des Lagergehäuses (23) durch Stehbolzen (51, 52), die frei durch Bohrungen im Flansch (31) und durch die Federn (47, 48) laufen, und über einen oberen und unteren Flanschkörper (32, 33) mit dem Gehäuseober­teil (3) verbunden ist, daß der obere und untere Flanschkörper (32, 33) gegenläufige Außengewinde (36, 37) aufweisen und außen von einer Verstellmutter (38) umfaßt sind, welche auf der Innenfläche Gewinde hat, welche den Gewinden des oberen und unteren Flansch­körpers (32, 33) entsprechen, daß die Verstellmutter (38) einen Zahnkranz (39) aufweist, der mit einem Ver­stellgetriebe und einem Fixiergetriebe verbunden ist, und daß am unteren Ende des Lagergehäuses (23) eine Paßfeder (35) angebracht ist, welche in einer Nut auf der Innenfläche des unteren Flanschkörpers (33) sitzt.1. Disc crusher with a crusher housing and a crushing disc rotatably mounted therein, over which a crushing cone is rotatably mounted in a bearing housing to form a radial crushing gap, the bearing housing with the crushing cone being axially displaceably guided and axially adjustable support surfaces against which the bearing housing is provided is braced by means of springs supported on spring stops, characterized in that a flange (31) of the bearing housing (23) by means of stud bolts (51, 52) which run freely through bores in the flange (31) and through the springs (47, 48) , and via an upper and lower flange body (32, 33) is connected to the upper housing part (3) that the upper and lower flange body (32, 33) have opposing external threads (36, 37) and are surrounded on the outside by an adjusting nut (38) which has threads on the inner surface which correspond to the threads of the upper and lower flange bodies (32, 33), that the adjusting nut (38) has a ring gear (39) which is connected to an adjusting gear and a fixing gear, and that at the lower end of the bearing housing (23) a feather key (35) is attached, which in a groove the inner surface of the lower flange body (33) sits. 2. Scheibenbrecher nach Anspruch 1, dadurch gekenn­zeichnet, daß die Federanschläge (49, 50) an den Stehbolzen (51, 52) befestigt sind, die in der bzw. den Abstützfläche(n) (32, 41) sitzen.2. Disc crusher according to claim 1, characterized in that the spring stops (49, 50) on the stud bolts (51, 52) are attached, which sit in the or the support surface (s) (32, 41). 3. Scheibenbrecher nach Anspruch 2, dadurch ge­kennzeichnet, daß die Federn als die Stehbolzen (51, 52) umgebende Teller- oder Schrauben­federn (47, 48) ausgebildet sind.3. Disc crusher according to claim 2, characterized in that the springs as the stud bolts (51, 52) surrounding plate or coil springs (47, 48) are formed. 4. Scheibenbrecher nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Federanschläge (49, 50) axial verstellbar angeordnet sind.4. Disc crusher according to one of claims 1 to 3, characterized in that the spring stops (49, 50) are arranged axially adjustable. 5. Scheibenbrecher nach Anspruch 1 oder 2, dadurch ge­kennzeichnet, daß die Federn hydro­pneumatische Federn sind.5. Disc crusher according to claim 1 or 2, characterized in that the springs are hydropneumatic springs. 6. Scheibenbrecher nach Anspruch 5, dadurch ge­kennzeichnet, daß der Füllungsgrad der hydropneumatischen Federn mit Hydrauliköl veränder­bar ist.6. Disc crusher according to claim 5, characterized in that the degree of filling of the hydropneumatic springs is variable with hydraulic oil. 7. Scheibenbrecher nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Abstützfläche(n) (40, 41, 42) auf mit Verstellge­winden versehene Stehbolzen (43) aufgeschraubt ist bzw. sind.7. Disc crusher according to one of claims 1 to 6, characterized in that the support surface (s) (40, 41, 42) is screwed onto stud bolts (43) provided with adjusting threads. 8. Scheibenbrecher nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Ab­stützfläche(n) einen das Lagergehäuse (23) umgebenden und mit dem einen Außengewinde (36) versehenen Hals­ abschnitt (32) aufweist bzw. aufweisen und daß auf das Außengewinde (36) die Verstellmutter (38) ge­schraubt ist, die mit einem ortsfesten Gehäuseteil (33) drehbar in Eingriff steht.8. Disc crusher according to one of claims 1 to 6, characterized in that the support surface (s) surrounding the bearing housing (23) and with an external thread (36) provided neck Section (32) or have and that the adjusting nut (38) is screwed onto the external thread (36), which is rotatably engaged with a stationary housing part (33). 9. Scheibenbrecher nach Anspruch 8, dadurch ge­kennzeichnet, daß die Verstellmutter (38)mit dem Flanschkörper (33) in Form eines ortsfesten Gehäuseteils über das gegenläufige Außengewinde (37) in Eingriff steht.9. Disc crusher according to claim 8, characterized in that the adjusting nut (38) with the flange body (33) in the form of a stationary housing part on the opposite external thread (37) is engaged. 10. Scheibenbrecher nach Anspruch 8 oder 9, dadurch gekennzeichnet, daß zwischen dem Lager­gehäuse (23) und dem Flanschkörper (33) in Form des ortsfesten Gehäuseteils eine Verdrehsicherung (35) angeordnet ist.10. Disk crusher according to claim 8 or 9, characterized in that an anti-rotation device (35) is arranged between the bearing housing (23) and the flange body (33) in the form of the stationary housing part. 11. Scheibenbrecher nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß die Spitze des Brechkegels (17) und die Mitte der Brechscheibe (7) einerseits durch einen Zentrierkörper (53, 58) und andererseits durch eine an diesen mit der Innenseite anliegende Bohrung (54, 57) verbunden sind.11. Disc crusher according to one of claims 1 to 10, characterized in that the tip of the crushing cone (17) and the center of the crushing disc (7) on the one hand by a centering body (53, 58) and on the other hand through a bore adjacent to this with the inside (54, 57) are connected. 12. Scheibenbrecher nach Anspruch 11, dadurch ge­kennzeichnet, daß der Zentrierkörper als in der Brechscheibe angeordneter Zentrierkegel (53) ausgebildet ist, der in der zylindrisch ausgebildeten Bohrung (54) im Brechkegel (17) mit Linienberührung anliegt.12. Disc crusher according to claim 11, characterized in that the centering body is designed as a centering cone (53) arranged in the crushing disc, which lies in the cylindrical bore (54) in the crushing cone (17) with line contact. 13. Scheibenbrecher nach Anspruch 11, dadurch ge­kennzeichnet, daß der Zentrierkörper als im Brechkegel (17) angeordneter Zentrierzylinder (58) ausgebildet ist, der in der kegelförmig sich verbrei­ternden Bohrung (57) in der Brechscheibe (7) mit mit Linienberührung anliegt.13. Disc crusher according to claim 11, characterized in that the centering body is formed as a centering cylinder (58) arranged in the crushing cone (17), which in the conically widening bore (57) in the crushing disc (7) with line contact. 14. Scheibenbrecher nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, daß das Lagergehäuse (23) quer zur Drehachse des Brechkegels (17) in einer von Brechspalt (19) und den Dreh­achsen gebildeten Ebene verschieblich ist.14. Disc crusher according to one of claims 1 to 13, characterized in that the bearing housing (23) is displaceable transversely to the axis of rotation of the crushing cone (17) in a plane formed by the crushing gap (19) and the axes of rotation. 15. Scheibenbrecher nach einem der Ansprüche 1 bis 14, dadurch gekennzeichnet, daß der Neigungswinkel (α) der Arbeitsfläche der Brechscheibe (7) 0 bis 90° beträgt.15. Disc crusher according to one of claims 1 to 14, characterized in that the angle of inclination (α) of the working surface of the crushing disc (7) is 0 to 90 °.
EP86111171A 1985-07-19 1986-08-12 Disc mill Expired EP0256147B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE19863623751 DE3623751A1 (en) 1985-07-19 1986-07-14 Disc crusher
AT86111171T ATE48767T1 (en) 1986-08-12 1986-08-12 DISC BREAKER.
EP86111171A EP0256147B1 (en) 1986-08-12 1986-08-12 Disc mill

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP86111171A EP0256147B1 (en) 1986-08-12 1986-08-12 Disc mill

Publications (2)

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EP0256147A1 true EP0256147A1 (en) 1988-02-24
EP0256147B1 EP0256147B1 (en) 1989-12-20

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ID=8195334

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EP86111171A Expired EP0256147B1 (en) 1985-07-19 1986-08-12 Disc mill

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EP (1) EP0256147B1 (en)
AT (1) ATE48767T1 (en)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003039845A1 (en) * 2001-11-07 2003-05-15 Elektropohony Spol. S.R.O. Device for reduction of hollow objects volume
JP2004318064A (en) * 2002-11-08 2004-11-11 Canon Inc Method for manufacturing toner particles
JP2004326030A (en) * 2003-04-28 2004-11-18 Canon Inc Method for manufacturing toner particle and method for manufacturing toner
US7131604B2 (en) * 2002-07-16 2006-11-07 M. Technique Company, Ltd. Processing apparatus and method for fluid, and deaerator therewith
CN101612533B (en) * 2002-07-16 2013-01-23 M技术株式会社 Processing apparatus and method for fluid, and deaerator therewith
CN108772137A (en) * 2018-06-27 2018-11-09 衡东县鸿达湘莲种植专业合作社 A kind of lotus seeds grinding device
CN111451438A (en) * 2020-04-30 2020-07-28 榆林学院 Sand mixing device for casting machine

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4199113A (en) * 1975-02-26 1980-04-22 Dso "Cherna Metalurgia" Disc-type apparatus for crushing hard materials

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4199113A (en) * 1975-02-26 1980-04-22 Dso "Cherna Metalurgia" Disc-type apparatus for crushing hard materials

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003039845A1 (en) * 2001-11-07 2003-05-15 Elektropohony Spol. S.R.O. Device for reduction of hollow objects volume
US7131604B2 (en) * 2002-07-16 2006-11-07 M. Technique Company, Ltd. Processing apparatus and method for fluid, and deaerator therewith
US7278592B2 (en) 2002-07-16 2007-10-09 M Technique Co., Ltd. Processing apparatus and method for fluid, and deaerator therewith
CN1483515B (en) * 2002-07-16 2010-07-28 M技术株式会社 Processing apparatus and method for fluid, and deaerator with mecronizing device
CN101612533B (en) * 2002-07-16 2013-01-23 M技术株式会社 Processing apparatus and method for fluid, and deaerator therewith
JP2004318064A (en) * 2002-11-08 2004-11-11 Canon Inc Method for manufacturing toner particles
JP2004326030A (en) * 2003-04-28 2004-11-18 Canon Inc Method for manufacturing toner particle and method for manufacturing toner
CN108772137A (en) * 2018-06-27 2018-11-09 衡东县鸿达湘莲种植专业合作社 A kind of lotus seeds grinding device
CN111451438A (en) * 2020-04-30 2020-07-28 榆林学院 Sand mixing device for casting machine

Also Published As

Publication number Publication date
EP0256147B1 (en) 1989-12-20
ATE48767T1 (en) 1990-01-15

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