Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
  • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
  • B02C1/00—Crushing or disintegrating by reciprocating members
  • B02C1/02—Jaw crushers or pulverisers
  • B02C1/08—Jaw crushers or pulverisers with jaws coacting with rotating roller
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
  • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
  • B02C4/00—Crushing or disintegrating by roller mills
  • B02C4/10—Crushing or disintegrating by roller mills with a roller co-operating with a stationary member
  • B02C4/12—Crushing or disintegrating by roller mills with a roller co-operating with a stationary member in the form of a plate
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
  • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
  • B02C4/00—Crushing or disintegrating by roller mills
  • B02C4/28—Details
  • B02C4/32—Adjusting, applying pressure to, or controlling the distance between, milling members
  • B02C4/34—Adjusting, applying pressure to, or controlling the distance between, milling members in mills wherein a roller co-operates with a stationary member

Definitions

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

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• Engineering & Computer Science (AREA)
• Food Science & Technology (AREA)
• Mechanical Engineering (AREA)
• Crushing And Grinding (AREA)
• Crushing And Pulverization Processes (AREA)
• Rolls And Other Rotary Bodies (AREA)

Priority Applications (5)

Applications Claiming Priority (2)

Publications (2)

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ID=49759256

Family Applications (1)

Country Status (9)

Cited By (10)

Families Citing this family (5)

Citations (8)

Family Cites Families (8)

• 2012
  • 2012-10-29 DE DE102012110336.4A patent/DE102012110336A1/de not_active Withdrawn
• 2013
  • 2013-10-28 EP EP13802893.1A patent/EP2911797B1/de active Active
  • 2013-10-28 PE PE2015000555A patent/PE20151303A1/es active IP Right Grant
  • 2013-10-28 AU AU2013339535A patent/AU2013339535B2/en active Active
  • 2013-10-28 BR BR112015009411-2A patent/BR112015009411B1/pt active IP Right Grant
  • 2013-10-28 WO PCT/EP2013/072465 patent/WO2014067882A2/de active Application Filing
  • 2013-10-28 DK DK13802893.1T patent/DK2911797T3/en active
  • 2013-10-28 CN CN201380068691.2A patent/CN104903001B/zh active Active
• 2015
  • 2015-04-24 CL CL2015001073A patent/CL2015001073A1/es unknown

Patent Citations (8)

Non-Patent Citations (2)

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