EP4360760A1 - Brechaggregat und verfahren zur einstellung des brechspalts eines brechaggregats - Google Patents

Brechaggregat und verfahren zur einstellung des brechspalts eines brechaggregats Download PDF

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Publication number
EP4360760A1
EP4360760A1 EP23201158.5A EP23201158A EP4360760A1 EP 4360760 A1 EP4360760 A1 EP 4360760A1 EP 23201158 A EP23201158 A EP 23201158A EP 4360760 A1 EP4360760 A1 EP 4360760A1
Authority
EP
European Patent Office
Prior art keywords
impact
gap
crushing
rocker
crushing unit
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.)
Pending
Application number
EP23201158.5A
Other languages
German (de)
English (en)
French (fr)
Inventor
Felix Löhr
Christian Schlecht
Christian WELLER
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.)
Kleemann GmbH
Original Assignee
Kleemann GmbH
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
Application filed by Kleemann GmbH filed Critical Kleemann GmbH
Publication of EP4360760A1 publication Critical patent/EP4360760A1/de
Pending legal-status Critical Current

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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
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/02—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft
    • B02C13/06—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft with beaters rigidly connected to the rotor
    • B02C13/09—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft with beaters rigidly connected to the rotor and throwing the material against an anvil or impact plate
    • B02C13/095—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft with beaters rigidly connected to the rotor and throwing the material against an anvil or impact plate with an adjustable anvil or impact 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
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/13—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft and combined with sifting devices, e.g. for making powdered fuel
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/26—Details
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/26—Details
    • B02C13/286—Feeding or discharge
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/26—Details
    • B02C13/31—Safety devices or measures
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/26—Details
    • B02C13/286—Feeding or discharge
    • B02C2013/28609—Discharge means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/26—Details
    • B02C13/286—Feeding or discharge
    • B02C2013/28618—Feeding means
    • B02C2013/28636—Feeding means of conveyor belt type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C21/00—Disintegrating plant with or without drying of the material
    • B02C21/02—Transportable disintegrating plant

Definitions

  • the invention relates to a crushing unit, in particular an impact crusher, with an impact rotor and with at least one pivotably mounted impact rocker, wherein a crushing gap is formed between the impact rotor and the impact rocker, wherein the impact rocker can be pivoted along an adjustment path by means of at least one gap adjustment means in order to adjust a gap width of the crushing gap, and wherein the impact rocker is mounted in such a way that its weight acts in the direction of a reduction of the crushing gap.
  • a crushing unit in particular an impact crusher, with an impact rotor and with at least one pivotably mounted impact rocker, wherein a crushing gap is formed between the impact rotor and the impact rocker, wherein the impact rocker can be pivoted along an adjustment path by means of at least one gap adjustment means in order to adjust a gap width of the crushing gap, and wherein the impact rocker is mounted in such a way that its weight acts in the direction of a reduction of the crushing gap.
  • the invention also relates to a method for adjusting the crushing gap of a crushing unit.
  • An impact crusher with a rotor provided inside a housing is known.
  • the rotor is mounted so that it can rotate around an axis and has several impact bars distributed over its circumference, which define an impact circle of the impact crusher.
  • An impact swing is also provided inside the housing. suspended so as to be pivotable about an axis.
  • a crushing gap is formed between an end of the impact arm facing away from the suspension and the impact circle.
  • a device is also provided with which pivoting of the impact arm towards the impact circle can be limited.
  • This device has a shaft which is connected to the impact arm at the end by means of a pivot connection. The shaft is guided through an opening in the housing in the area of a stop. Outside the housing, the shaft is accommodated in a sleeve.
  • the shaft and the sleeve can be adjusted relative to one another via a threaded connection so that a free length of the shaft between the sleeve and the pivot connection with the impact arm can be adjusted. If the sleeve rests on a stop, the pivoting path of the impact arm towards the impact circle is limited.
  • a pre-tensioning device is also provided which exerts a force on the impact arm in the direction of the impact circle and thus towards the stop.
  • the pre-tensioning device has a hydraulic cylinder in which a piston rod is guided. The piston rod is pivotally connected to the impact arm facing away from the cylinder. To adjust the gap width of the crushing gap, the pre-tensioning device is first relieved. The relative position of the stop is then adjusted by adjusting the shaft and the sleeve relative to each other.
  • the disadvantage of known impact crushers is that the crushing gap can only be changed by adjusting a fixed stop. To do this, for example, a hydraulic cylinder must first be relieved of pressure. The position of the stop must then be changed, for example using a thread. This means that it is not possible to adjust the crushing gap during crushing operation. Instead, crushing operation must be interrupted, which causes downtime during operation and therefore costs. Furthermore, the process of adjusting the crushing gap is complex and time-consuming.
  • the object of the invention is to provide a crushing unit with a high level of operational reliability, which enables a simplified adjustment of the crushing gap, preferably during operation.
  • the object of the invention is also to provide a method for adjusting the crushing gap of a crushing unit, which enables a simplified adjustment of the crushing gap, preferably during operation.
  • the object concerning the crushing unit is achieved in that at least one holding device is provided which flexibly counteracts a pivoting of the impact rocker in the direction of the impact rotor with a holding force.
  • the holding force of the holding device can thus prevent the impact rocker from accidentally coming into contact with the impact rotor, for example due to its gravity, in particular with any impact bars provided on the impact rotor. In this sense, the holding device thus forms a stop.
  • the holding force of the holding device can act, for example, between the impact arm and a mechanically stable element of the crushing unit.
  • the holding device is connected in a suitable manner directly or indirectly to a crusher housing of the crushing unit or to a chassis of a higher-level material processing device.
  • the impact rocker can be pivotally mounted directly or indirectly on the same element or the same structural unit.
  • the holding force of the holding device is flexible, a hard impact of the impact arm against the stop is prevented if, for example, the impact arm suddenly falls from an initially held swivel position in the direction of the impact rotor.
  • the impact arm suddenly falls from an initially held swivel position in the direction of the impact rotor.
  • the gap adjustment device fails, in particular the gap adjustment device.
  • the impact arm deviates from its original swivel position and, after deviating, moves back towards the impact rotor.
  • a flexible holding force of the holding device also offers the advantage that it can be designed in such a way that it can be at least partially overcome by the gap adjustment means. In contrast to a fixed stop, this makes it possible to set a desired gap width, in particular at least partially against the holding force, without manually adjusting a fixed stop.
  • the gap adjustment means counteracts the holding force of the holding device at least along parts of the adjustment path in order to reduce the gap width of the crushing gap.
  • the crushing gap can be adjusted during operation, while a high level of operational safety is nevertheless ensured by the fact that unintentional contact between the impact arm and the impact rotor is reliably prevented by the holding device.
  • a crushing unit according to the invention can, for example, be part of a material processing device, in particular a mobile material processing device.
  • a material processing device can, in addition to the Crushing unit may have additional components, such as a feeding unit, a material feeding device, one or more screening units, one or more conveying devices such as belt conveyors and/or a chassis.
  • the holding device has a flexible clamping element.
  • the flexible clamping element can, for example, provide a flexible holding force of the holding device.
  • the tensioning element can preferably be designed to be spring-elastic.
  • the tensioning element it is possible for the tensioning element to be designed as a spring.
  • Possible designs of the tensioning element can thus be, for example, various types of compression or tension springs, in particular helical, barrel, conical, torsion, leaf or disc springs. It is also conceivable that the tensioning element achieves its flexibility due to a selected tension cross-section or a selected flexible material.
  • An advantageous variant of the invention can be such that the holding device has a tension element which is connected on the one hand to the impact rocker and on the other hand to the tensioning element, and that the tension element transmits a force between the tensioning element and the impact rocker.
  • a tension element can comprise, for example, a rod or flexible element, in particular a rope.
  • the tension element advantageously transfers at least predominantly a tensile force and preferably no or only limited compressive forces, which in particular reduces the risk of buckling.
  • the clamping element has a swing-side end region and a second end region.
  • the clamping element can, for example, be connected directly or indirectly to the crusher housing with its swing-side end region, in particular be attached to it and/or supported on it.
  • the swing-side end region of the clamping element can be spaced from the second end region and/or preferably provided opposite it on the clamping element.
  • the tension element has a coupling region on the swing arm side and a coupling region on the tensioning element side.
  • the two coupling regions can, for example, be spaced apart from one another and/or preferably provided at opposite end regions of the tension element.
  • the tension element can preferably be connected to the impact swing in its swing-side coupling area.
  • this connection pivotable.
  • Such a pivotable connection can be achieved, for example, by providing a holding section on the impact swing that can accommodate a fastening element, wherein the fastening element can be a pin or a bolt, for example.
  • the swing-side coupling area can in turn have a bearing receptacle for receiving the fastening element.
  • the tension element is fixed to the tension element with its coupling area on the tension element side, a connection between the tension element and the impact rocker is created in a structurally simple manner.
  • the coupling area on the tension element side can be fixed to the tension element in a detachable or non-detachable manner, in particular it can be connected in a force-fitting, form-fitting or material-fitting manner. It is conceivable that a screw, weld, adhesive or clamp connection is provided.
  • a preferred embodiment of the invention can be characterized in that the tensioning element is designed as a compression spring, that the tensioning element is attached with its swing-side end region to a crusher housing of the Crushing unit is supported directly or indirectly, and that the tension element is fixed with its clamping element-side coupling region to the second end region of the clamping element.
  • the pulling element and/or the tensioning element can be arranged at least partially in easily accessible areas of the crushing unit, in particular at least partially outside the crusher housing. This can facilitate assembly and/or maintenance work on the holding device and/or other components of the crushing unit.
  • at least the coupling area on the tensioning element side and/or the second end area is/are arranged in easily accessible areas of the crushing unit, in particular at least partially outside the crusher housing.
  • the tensioning element is designed as a tension spring, that the tensioning element is connected directly or indirectly with its second end region to a crusher housing of the crushing unit, and that the tensioning element is fixed with its tensioning element-side coupling region to the swing-arm-side end region of the tensioning element.
  • one holding device of the crushing unit has a tensioning element designed as a compression spring and another holding device has a tensioning element designed as a tension spring.
  • design specifications such as available installation space can be taken into account in this way. It is conceivable that, depending on the installation location, holding devices with tension or compression springs are easier to install.
  • a variant of the invention can be characterized in that the tension element has a flexible element, in particular a rope, particularly preferably a wire rope, or a chain.
  • a flexible element offers the advantage that it requires less space when the distance between the tensioning element and the impact arm is shortened, in particular when the latter is moved away from the impact rotor.
  • a rigid element, such as a rod, could in this case be unfavorably protrude at least partially from the crusher housing. In particular, if the impact arm is suddenly deflected due to an overload, a rigid tension element that suddenly protrudes from the crusher housing could pose a significant safety risk.
  • a minimum permissible gap width of the crushing gap is provided, that a clamping force of the clamping element is in balance with the effect of the weight of the impact rocker or is greater than the effect of the weight when the minimum permissible gap width is present.
  • a minimum permissible gap width of the crushing gap can in particular represent a desired safety distance between the impact rocker and the impact rotor, in particular between the impact rocker and the impact circle. Since the impact rocker is mounted in such a way that its weight acts in the direction of reducing the crushing gap, it is advantageous if the clamping force of the clamping element is sufficient to prevent further pivoting beyond the minimum gap width.
  • the clamping force of the clamping element still has an excess force in the direction of increasing the gap width when there is a minimum distance between the impact rocker and the impact rotor. Accordingly, the equilibrium position in which the clamping force of the clamping element is in balance with the effect of the weight of the impact rocker can be present when the gap width is larger than the minimum permissible. It is preferred if the excess force is low so that the force required by the gap adjustment means to adjust the gap width of the crushing gap is not increased excessively.
  • the gap adjustment means can therefore be dimensioned efficiently.
  • a stable design of the crushing unit can be achieved if it is provided that a fastening section is provided on the crusher housing and that at least one gap adjustment means and at least one holding device are held on the fastening section.
  • the fastening section can be reinforced to absorb high forces.
  • the fastening section can have a higher mechanical stability than other elements of the crusher housing.
  • the fastening section can also be designed in such a way that suitable connection points for fastening means for attaching gap adjustment means(s) and/or holding device(s) are provided.
  • the fastening section has a plate-shaped upper support element and a plate-shaped lower support element spaced apart therefrom, the two support elements being connected by means of at least two connecting elements.
  • This provides a particularly rigid fastening section.
  • the two support elements each offer suitable connection levels for the gap adjustment means and/or the holding device(s). A simple and stable design can be achieved in particular if the fastening section forms a rectangular hollow profile.
  • the gap adjustment means is arranged in a central region, preferably in the middle, relative to a longitudinal extension of the impact rocker oriented in the direction of a rotation axis of the impact rotor. This enables the introduction of force from the gap adjustment means into the impact rocker in an optimal manner. In particular, the occurrence of undesirable bending moments on the impact rocker is prevented or at least reduced.
  • At least one holding device is arranged on both sides of the gap adjustment means. This creates redundancy that reliably prevents unintentional contact between the impact rocker and the impact rotor. It is also conceivable that the holding devices can be made smaller if several sensibly arranged holding devices are provided. In particular, assembly advantages can arise if the clamping elements have, for example, spring-elastic elements, in particular springs, which can be used with a lower clamping force can be dimensioned. Particularly preferably, the holding devices can be arranged symmetrically to the gap adjustment means.
  • a preferred embodiment of the invention can be characterized in that the swing-side end region of the tensioning element is supported on the lower support element, that the lower support element has a first opening, wherein the tension element is guided through the first opening, preferably that the upper support element has a second opening through which the tension element and/or the tensioning element is/are guided.
  • a crushing unit according to the invention can be such that the gap adjustment means has an adjusting element, preferably in the form of a hydraulic cylinder, and that the gap adjustment means has a transmission element that is adjustable relative to the adjusting element, preferably in the form of a piston rod.
  • the adjusting element is particularly preferably provided in the form of a double-acting hydraulic cylinder.
  • the gap adjustment means can thus hold the impact rocker at a desired distance from the impact rotor during normal operation or a desired crushing gap can be maintained.
  • hydraulic gap adjustment means it is also conceivable that mechanical, electromechanical or electrical gap adjustment means are used.
  • an overload device which interacts with the gap adjustment means and which causes or at least enables a widening of the crushing gap in the event of an overload situation, wherein the overload device is preferably designed hydraulically, in particular as a pressure relief valve or bursting plate, or mechanically, for example as a pressure plate.
  • a hydraulic overload device for example an overpressure safety device, in particular a pressure relief valve in a hydraulic circuit, preferably in a common hydraulic circuit with the gap adjustment device.
  • an overload for example due to unbreakable material in the crushing chamber, a large force is exerted on the impact rocker, which is ultimately transferred to the gap adjustment device. This can cause the pressure within the adjusting element, in particular the hydraulic cylinder, to rise above a specified maximum pressure.
  • An overload device that allows this high pressure to be reduced now enables the impact rocker to deflect so that the unbreakable material can leave the crushing chamber.
  • gap adjustment device and a mechanical overload device or vice versa is also conceivable.
  • the gap adjustment device and the overload device do not have to be based on the same operating principle, for example hydraulic, electrical and/or mechanical.
  • a pressure plate for example, which is arranged in the force flow between the impact rocker and the gap adjustment means, can serve as a mechanical overload device.
  • the pressure plate can preferably have a predetermined breaking point. If an excessive force is exerted by the impact rocker on the gap adjustment means in the event of an overload, the pressure plate can preferably break at the predetermined breaking point so that the impact rocker can give way.
  • the impact rocker is pivotably attached to the/a housing of the crushing unit by means of a rocker bearing, that the/a tension element of the holding device is pivotally connected to a holding section of the impact rocker, that the/a transmission element of the gap adjustment means is pivotally connected to a coupling section of the impact rocker, and that the holding section and coupling section are arranged in a half of the longitudinal extension of the impact rocker opposite the rocker bearing, preferably an opposite first third.
  • the gap adjustment means and/or the holding device have to apply lower forces than if they were connected to the impact rocker closer to the rocker bearing.
  • holding devices and/or gap adjustment means are connected to the impact swing arm in a position which, with respect to the position of the swing arm bearing, offers a favorable lever arm for force transmission to the impact swing arm.
  • Figure 1 shows a material processing device 1 in the form of a crushing plant.
  • the material processing device is designed as a mobile material processing device and therefore has chassis 1.5. However, it is also conceivable that the material processing device 1 is a stationary material processing device 1.
  • the material processing device 1 has a chassis 1.1, which supports the machine components or at least a part of the machine components At its rear end, the chassis 1.1 has a boom 1.2. A material feed area is formed in the area of the boom 1.2.
  • the material feed area comprises a feed hopper 2 and a material feed device 9.
  • the feed hopper 2 can be formed at least partially by hopper walls 2.1, which run in the direction of the longitudinal extension of the material processing device 1, and a rear wall 2.2 running transversely to the longitudinal extension.
  • the feed hopper 2 leads to a material feed device 9.
  • the material feed device 9 can, as shown in the present embodiment, have a conveyor trough that can be driven by means of a vibration drive. Material to be shredded can be filled into the material processing device 1 via the feed hopper 2, for example by means of a wheel loader, and fed onto the conveyor trough.
  • This screening unit 3 can also be referred to as a pre-screening arrangement. At least one screening deck 3.1, 3.2 is arranged in the area of the screening unit 3. In the present embodiment, two screening decks 3.1, 3.2 are used.
  • a partial fraction of the material to be crushed is screened out on the upper screen deck 3.1.
  • This partial fraction already has a sufficient grain size and no longer needs to be crushed in the material processing device 1.
  • this screened partial fraction can be guided in a bypass channel 3.5 past a crushing unit 10.
  • a further fine particle fraction can be screened out from the fraction that accrues below the screen deck 3.1.
  • This fine particle fraction can be guided below the screen deck 3.2 to a side discharge belt 3.4. From the The fine particle fraction is discharged via the side discharge belt 3.4 and conveyed to a stockpile 7.2 located to the side of the machine.
  • the screening unit 3 can be a vibrating screen with a screen drive 3.3.
  • the screen drive 3.3 causes the screen deck 3.1 and/or the screen deck 3.2 to vibrate. Due to the inclined arrangement of the screen decks 3.1, 3.2 and in conjunction with the vibrating movements, material is transported on the screen decks 3.1, 3.2 in the direction of the crushing unit 10 or the bypass channel 3.5.
  • the material to be crushed coming from the screen deck 3.1 is fed to the crushing unit 10, as Figure 1 can be recognized.
  • the crushing unit 10 can be designed, for example, in the form of a rotary impact crushing unit.
  • the crushing unit 10 then has an impact rotor 11 which is driven by a drive 12.
  • the rotation axis 17 of the impact rotor 11 runs horizontally in the direction of the image depth.
  • the impact rotor 11 can, for example, be equipped with impact bars 11.2 on its outer circumference. Opposite the impact rotor 11, wall elements, preferably in the form of impact rockers 20, can be arranged. When the impact rotor 11 rotates, the material to be shredded is thrown outwards by means of the impact bars 11.2. This material hits the impact rockers 20 and is shredded due to the high kinetic energy. If the material to be shredded has a sufficient grain size that allows the material particles to be guided through a crushing gap 15 between the impact rockers 20 and the radially outer ends of the impact bars 11.2, the shredded material leaves the crushing unit 10 via the crusher outlet 16.
  • the crushed material coming from the crushing unit 10 is combined with the material coming from the bypass channel 3.5 and brought to a belt conveyor 1.3.
  • the material can be removed from the working area of the crushing unit 10 using the belt conveyor 1.3.
  • the belt conveyor 1.3 can have an endlessly rotating conveyor belt that has a load strand 1.6 and an empty strand 1.7.
  • the load strand 1.6 serves to catch and transport away the broken material that falls out of the crusher outlet 16 of the crushing unit 10.
  • the conveyor belt can be deflected between the load strand 1.6 and the empty strand 1.7 by means of deflection rollers 1.4.
  • guides, in particular support rollers can be provided in order to change the conveying direction of the conveyor belt, to give the conveyor belt a certain shape and/or to support the conveyor belt.
  • the belt conveyor 1.3 has a belt drive by means of which the belt conveyor 1.3 can be driven.
  • the belt drive can preferably be arranged at the discharge end 1.9 or in the area of the discharge end 1.9 of the belt conveyor 1.3.
  • the belt conveyor 1.3 can be connected to a control device by means of a control line, for example by means of the belt drive.
  • One or more additional belt conveyors 6 and/or a return conveyor 8 can be used, which in principle have the same design as the belt conveyor 1.3. In this respect, reference can be made to the above explanations.
  • a magnet 1.8 can be arranged above the load strand 1.6.
  • the magnet 1.8 can be used to lift iron parts out of the broken material and move them out of the conveying area of the belt conveyor 1.3.
  • a screening device 5 can be arranged in the transport direction after the belt conveyor 1.3.
  • the screening device 5 has a screen housing 5.1 in which at least one screen deck 5.2 is accommodated. Below the screen deck 5.2 there is a The lower housing section 5.3 serves as a collecting space for the material screened out on the screen deck 5.2.
  • the housing base 5.3 creates a spatial connection to another belt conveyor 6 via an opening.
  • the other belt conveyor 6 forms its feed area 6.1, whereby the screened material in the feed area 6.1 is guided onto the load strand of the other belt conveyor 6.
  • the other belt conveyor 6 conveys the screened material to its discharge end 6.2. From there, the screened material reaches a stockpile 7.1.
  • the material not screened out on the screen deck 5.2 of the secondary screening device 5 is conveyed from the screen deck 5.2 to a stitch belt 5.4.
  • the stitch belt 5.4 can also be designed as a belt conveyor, so that reference can be made to the statements made above with regard to the belt conveyor 1.3.
  • the transport direction of the stitch belt 5.4 runs in Figure 1 in the direction of the image depth.
  • the stub conveyor 5.4 transfers the non-screened material, which is also referred to as oversize, to the feed area 8.1 of the return conveyor 8.
  • the return conveyor 8 which can be designed as a belt conveyor, conveys the oversize in the direction of the feed hopper 2.
  • the return conveyor 8 transfers the oversize into the material flow, namely into the material feed area. The oversize can thus be fed back to the crushing unit 10 and broken down to the desired particle size.
  • FIG 2 shows a schematic perspective view of a crushing unit 10.
  • the crushing unit 10 can have a crusher housing 70.
  • a crushing chamber 16.1 can be formed within the crusher housing 70 (see Figure 4 ).
  • the crusher housing 70 can have a crusher inlet 14 in the form of an opening, which allows the material to be crushed to be fed into the crushing chamber 16.1.
  • a crusher outlet 16 can be provided in the form of a further opening in the crusher housing 70. Crushed material can leave the crushing chamber 16.1 through the crusher outlet 16.
  • the crusher housing 70 can be used to safely guide the material flow from the crusher inlet 14 through the crushing unit 10 to the crusher outlet 16 by preventing material to be crushed or already crushed from leaving the crushing chamber 16.1, for example from the side.
  • the crusher housing 70 can prevent access to the crushing chamber 16.1, at least during crushing operation. This effectively reduces the risk of injury due to direct access to the crushing chamber 16.1 and/or ejected rock material.
  • a curtain 14.1 can be provided in the area of the crusher inlet 14. In particular, this can consist of chains. The curtain 14.1 can protect against material being thrown out of the crushing chamber 16.1 through the crusher inlet 14.
  • an impact rotor 11 can be mounted so as to be rotatable about a rotation axis 17.
  • the impact rotor 11 can have a rotor shaft 11.3 (see in particular Fig.4 ), which can be supported by means of rotor bearings 18.
  • the rotor bearings 18 can be provided and/or attached to the crusher housing 70.
  • a drive 12 can be provided by means of which the impact rotor 11 can be driven.
  • it can be an electric drive.
  • other drive concepts are also conceivable, for example hydraulic drives or an internal combustion engine.
  • the drive 12 can drive the impact rotor 11 via a transmission, for example a gear transmission or a belt drive.
  • a direct drive is also conceivable.
  • the crushing unit 10 can have a fastening section 40, which can serve to fasten a gap adjustment means 30 and/or a holding device 50. This will be discussed in more detail elsewhere.
  • an impact rocker 20 can be provided within the crushing chamber 16.1.
  • the impact rocker 20 can be pivotably mounted about a rocker axis 21.1.
  • the impact rocker 20 has a rocker shaft 21.2 which is mounted by means of a rocker bearing 21.
  • the rocker bearing 21 can be provided and/or fastened to the crusher housing 70.
  • the impact rocker 20 can be mounted in such a way that its weight acts in the direction of a reduction in the crushing gap 15, i.e. in a pivoting direction of the impact rocker 20 towards the impact rotor 11. This effect can result from the rocker axis 21.1 being arranged, as shown, in the plane of the image above and/or laterally offset from a center of mass of the impact rocker 20.
  • the swing shaft 21.2 can be provided in a bearing-side end region 20.1 of the impact swing 20.
  • the impact swing 20 can have a swing body 22.
  • the swing body 22 can have a base body 23.
  • the base body 23 can preferably be designed as a curved plate, as can be seen from the figures.
  • the impact rocker 20 can also have at least one impact plate 24.
  • the impact plate 24 is preferably made of a resistant material and is more preferably connected to the impact rocker 20 in an exchangeable manner. As shown here, the impact plate 24 can preferably be provided at least in an end region 20.2 of the impact rocker 20 on the crushing gap side. An edge 24.1 of the impact plate 24 can thus delimit a crushing gap 15 on the side of the impact rocker 20 (see also Fig.4 ). However, it is also conceivable that no impact plate 24 is provided, or that a baffle plate 24 is not provided in the region of the edge 24.1. In this case, the edge 24.1 can also be formed by the swing body 22, in particular by the base body 23.
  • the swing arm body 22 can also have longitudinal reinforcements 28 on a rear side 23.2 facing away from the impact surface 23.1.
  • the longitudinal reinforcements 28 can be designed as ribbing.
  • the longitudinal reinforcements 28 can be designed as one piece with the base body 23, or can be connected to it in a form-fitting, material-fitting or force-fitting manner. In particular, a welded connection is conceivable.
  • the longitudinal reinforcements 28 can serve to increase the bending stiffness in the direction of a longitudinal extension of the impact swing arm 20 from the bearing-side end region 20.1 to the crushing gap-side end region 20.2.
  • transverse reinforcements 27 can also be provided on the swing arm body 22 in a similar manner and design.
  • the crushing unit 10 can have a gap adjustment means 30.
  • the gap adjustment means 30 can have an adjusting element 32 and a transmission element 31.
  • the transmission element 31 can be adjustable relative to the adjusting element 32.
  • the gap adjustment means 30 can be a hydraulic gap adjustment means 30.
  • the actuating element 32 can thus be designed as a hydraulic cylinder.
  • a piston can be guided within the hydraulic cylinder.
  • the transmission element 31 can be designed as a piston rod that is coupled to the piston.
  • the transmission element 31 can preferably be pivotally connected to the impact rocker 20.
  • a coupling section 25 can be provided on the impact rocker 20.
  • the coupling section 25 can be provided, for example, between two longitudinal stiffeners 28.
  • the longitudinal stiffeners 28 have opposite holes through which a fastening element 25.1 can be guided.
  • the Fastening element 25.1 can then be guided through a corresponding bore on the transmission element 31 to establish a pivotable connection.
  • the adjusting element 32 of the gap adjustment means 30 can be fixed, for example, to the crusher housing 70.
  • fastening means 33 can be provided for this purpose, which can be designed as bearing blocks, as in the present case.
  • the fastening means 33 can be clamped, for example, with screws 34 to the crusher housing 70, in particular to the fastening section 40.
  • the fastening means 33 can accommodate projections provided on the adjusting element 32. This allows the adjusting element 32 to pivot about a pivot axis 32.1.
  • the gap adjustment means 30 can thus be pivotably mounted on the impact rocker 20 on the one hand and on the crusher housing 70 on the other. Since the coupling section 25 of the impact rocker 20 moves on a circular path when pivoting, in particular when adjusting the crushing gap 15, such pivotability of the gap adjustment means 30 can be particularly advantageous.
  • a pivoting movement of the impact rocker 20 can be effected by adjusting the transmission element 31 relative to the adjusting element 32.
  • the adjusting element 32 is advantageously designed to be double-acting, in particular as a double-acting hydraulic cylinder. This makes it possible to reduce or increase the crushing gap 15 by applying appropriate pressure to the respective chambers of the hydraulic cylinder. Furthermore, it is easy to ensure a constant crushing gap 15 during operation by means of a double-acting hydraulic cylinder.
  • the crushing unit 10 can have an overload device 35.
  • the overload device 35 be designed as a hydraulic overload device 35.
  • the overload device 35 can be coupled directly or indirectly to the actuating element 32.
  • the overload device 35 can have a pressure relief valve that opens when the hydraulic pressure in one of the chambers of the hydraulic cylinder is too high. This can reduce the pressure. Excessive pressure can result from unbreakable material, for example a particularly large and/or hard object, being in the crushing chamber 16.1. This unbreakable material can then exert a large force on the impact rocker 20.
  • the overload device 35 can thus ensure that the impact rocker 20 can move away from the impact rotor 11 in such a case.
  • the impact rotor 11 and the holding device 50 are shown in more detail.
  • the impact rotor 11 can have a base body 11.1.
  • Impact bars 11.2 can be provided on the base body 11.1 distributed over the circumference.
  • the impact bars 11.2 can be detachably and thus replaceably connected to the base body 11.1.
  • An impact circle 19 can be formed on the outermost circumference of the impact rotor 11.
  • the impact circle 19 is formed by the orbit of the radially outer ends of the impact bar 11.2.
  • the impact bars 11.2 can be made of a particularly robust, in particular wear-resistant material, or at least have such a material in the region of their radially outer ends.
  • the crushing gap 15 can be formed between the impact circle 19 and a crushing gap-side end region 20.2 of the impact rocker 20, in particular an edge 24.1 of the impact rocker 20.
  • the holding device 50 can have a tensioning element 52 and a tensioning element 51.
  • the tensioning element 51 can be pivotally coupled to the impact swing arm 20 in a swing-side coupling region 51.1.
  • a holding section 26 can be provided on the impact swing arm 20 for this purpose. Similar to the coupling section 25, the holding section 26 can be provided, for example, between two longitudinal stiffeners 28. In particular, it can be provided that the longitudinal stiffeners 28 are opposite Have holes through which a fastening element 26.1 can be guided. The fastening element 26.1 can then be guided through a corresponding hole on the tension element 51 in order to produce a pivotable connection.
  • the tension element 51 can have a flexible element.
  • a rope in particular a wire rope or a chain, is used as the tension element 51.
  • a suitable connection means for example a rope clamp, can then be provided in the coupling area 51.1 on the swing arm side.
  • a rigid element for example in the form of a rod, is used as the tension element 51.
  • the tension element 51 can also have a clamping element-side coupling area 51.2 facing away from the swing-arm-side coupling area 51.1. This can be designed similarly to the swing-arm-side coupling area 51.1.
  • a force-transmitting connection with the clamping element 52 can be produced with the clamping element 52 coupling area 51.2, for example with a second end area 52.2 of the clamping element 52.
  • the force-transmitting connection between the tension element 51 and the tension element 52 is not shown in detail in the figures. Depending on the design of the tension element 51 and the tension element 52, different types of connection can be considered. If, according to the embodiment shown, the tension element 51 is designed as a cable and the tension element 52 is designed as a spring, the tension element 51 can have, for example, a cable clamp in its tension element-side coupling area 51.2. This can be detachably or permanently connected to the second end area 52.2. It is conceivable that a tension element 52 designed as a spring has a spring bearing in its second end area 52.2, for example in the form of an end plate, to which the tension element-side coupling area 51.2 of the tension element 51 can be fixed.
  • tension element 51 is designed as a rigid element, it may be advantageous to provide a pivotable connection with the tensioning element 52.
  • the tensioning element 52 can be supported on the crusher housing 70. In particular, as shown in the figures, it can be supported on a fastening section 40 of the crusher housing 70.
  • the tensioning element 52 can be designed as a compression spring and rest on the fastening section 40 with its spring end located in the swing arm-side end region 52.1.
  • the tensioning element 52 can cause a compressive force supported on the crusher housing 70 in a direction away from the rocker, which can be transmitted to the impact rocker 20 via the tension element 51.
  • a holding force can be exerted on the impact rocker 20 with the holding device 50, which counteracts a pivoting of the impact rocker 20 towards the impact rotor 11.
  • the tensioning element 52 is designed as a tension spring.
  • the tensioning element 51 can be coupled to the swing-side end region 52.1.
  • the tensioning element 52 can be coupled with its second end region 52.2 to the crusher housing 70, in particular to the fastening section 40.
  • a tensile force can thus be introduced from the tensioning element 52 via the tensioning element 51 into the impact swing 20.
  • a tensioning element 51 can be dispensed with, wherein the tensioning element 52 can, for example, be connected directly to the impact swing 20 with its swing-side end region 52.1.
  • the tension element 51 itself is designed to be flexible, in particular to be spring-elastic, preferably designed as a tension spring or to have a tension spring.
  • a tension element 52 can be dispensed with, so that the holding device 50 has a tension element 51, but no separate tension element 52.
  • the tension element 51 can then, as previously described, be connected to the impact swing arm 20 with its swing-side coupling area 51.1.
  • the Tension element 51 can be connected to the crusher housing 70, in particular to the fastening section 40. Thus, a tensile force can be transmitted between the crusher housing 70 and the impact rocker 20 by means of the tension element 51.
  • the tensioning element 52 is provided as a helical compression spring.
  • the tensioning element 51 can then be guided through the spring in a space-saving manner. Accordingly, the tensioning element 51 can be accommodated within the spring at least between the swing-side end region 52.1 and the second end region 52.2 of the tensioning element 52.
  • the swing-side end region 52.1 of the tensioning element 52 can be supported on a support element 41, 42 of the fastening section 40.
  • the support element 41, 42 can have an opening 44, 45 through which the tensioning element 51 can be guided.
  • the fastening section 40 can have a hollow cross-section, in particular a rectangular hollow cross-section.
  • an upper support element 41 and a lower support element 42 each in the form of a plate, for example, can be provided.
  • the upper support element 41 can end with an outer surface of the crusher housing 70.
  • the lower support element 42 can be arranged at a distance in the direction of the crushing chamber 16.1 and preferably parallel to it.
  • the support elements 41, 42 can be connected by means of connecting elements 43, for example in the form of side walls.
  • the tensioning element 52 can be supported with its swing-side end region 52.1 on the lower support element 42.
  • the lower support element 42 can have a first opening 44 through which the tension element 51 can be guided.
  • the upper support element 41 can have a second opening 45 through which the tensioning element 52 and the tension element 51 can be guided. Accordingly, the tensioning element 52 and the pulling element 51 can protrude at least partially from the crusher housing 70.
  • the second end region 52.2 of the tensioning element 52 and the tensioning element-side coupling region 51.2 of the pulling element 51 can therefore be easily accessible outside the crusher housing 70.
  • the connection region between the pulling element 51 and the tensioning element 52 can therefore be located outside the crusher housing 70.
  • At least one gap adjustment means 30 can be arranged in a central region of the impact rocker 20, in relation to its transverse extent.
  • the transverse extent of the impact rocker 20 can be aligned parallel to its rocker axis 21.1 and/or parallel to the rotation axis 17 of the rotor shaft 11.3.
  • at least two holding devices 50 can be provided. These are particularly preferably arranged along the transverse extent on both sides of the gap adjustment means 30, and more preferably arranged symmetrically to this.
  • An extension oriented perpendicular to the transverse extension of the impact rocker 20 and, for example, along the impact surface 23.1 can represent a longitudinal extension of the impact rocker 20.
  • the gap adjustment means 30 and the holding device(s) 50 can preferably be arranged in a region of a half of the longitudinal extension opposite the rocker bearing 21, in particular an opposite third.
  • the holding device 50 exerts a holding force on the impact rocker 20, which counteracts a pivoting of the impact rocker 20 towards the impact rotor 11.
  • a defined minimum width of the A width of the crushing gap 15 is provided, which can be, for example, a selected safety distance between the impact circle 19 and the impact rocker 20, in particular the edge 24.1.
  • the holding force of the holding device 50 keeps the impact rocker 20 at least in equilibrium when the minimum width of the crushing gap 15 is present.
  • the holding force preferably has an excess force in this position too, so that the equilibrium position is present at a distance between the impact rocker 20 and the impact rotor 11 that is greater than the intended minimum distance.
  • the gap adjustment means 30 is used to set a desired gap width of the crushing gap 15 in accordance with the existing requirements, for example in accordance with the material to be crushed and/or the desired end product.
  • the transmission element 31 is adjusted relative to the adjusting element 32 so that the impact rocker 20 can be pivoted towards the impact rotor 11 to reduce the crushing gap or away from the impact rotor 11 to enlarge the crushing gap 15.
  • the gap adjustment means 30 thus works against the holding force of the holding device 50 at least over parts of the adjustment path.
  • the holding force of the holding device 50 works together with the gap adjustment means 30 in a supporting manner at least over parts of the adjustment path. It is particularly advantageous that the holding device 50 does not have to be adjusted here because it exerts a flexible holding force that can be overcome by the gap adjustment means 30.
  • the crushing gap 15 can be adjusted to a desired size during operation by means of the gap adjustment means 30.
  • the gap width of the crushing gap 15 is kept largely constant by the gap adjustment means 30, which is preferably double-acting.
  • the gap adjustment means 30 can thus exert a holding force on the impact rocker 20, which can prevent pivoting both towards and away from the impact rotor 11. Now situations can arise in which the holding force of the gap adjustment means 30 is no longer present or at least no longer sufficient to prevent pivoting towards the impact rotor 11.
  • such a situation can arise due to a failure of the gap adjustment means 30.
  • a hydraulic system can fail so that the actuating element 32 (hydraulic cylinder) becomes depressurized.
  • an overload of the crushing unit 10 can occur, for example, if a non-crushable element is located in the crushing chamber 16.1. Such an element can exert very large forces on the impact rocker 20, which push it in a direction away from the impact rotor 11. These large forces are at least partially transmitted to the gap adjustment means 30 by the transmission element 31. In such a case, an overload device 35 can prevent damage to the crushing unit 10 by allowing the impact rocker 20 to deflect.
  • this can be a hydraulic overload device 35.
  • the overload situation causes the pressure inside a chamber of the actuating element 32, which is designed as a hydraulic cylinder, to rise.
  • the overload device 35 can be, for example, a pressure relief valve that allows the actuating element 32 to be relieved of pressure at a certain overload pressure. This enables the impact rocker 20 to deflect and the non-breakable element can, if necessary, leave the crushing chamber 16.1, which can resolve the overload situation.
  • the gap adjustment means 30 may not immediately be able to provide the required holding force to prevent the impact rocker 20 from pivoting onto the impact rotor 11, or in the worst case, the impact rocker 20 from hitting the impact rotor 11.
  • the holding device 50 offers an increase in operational safety, since it reliably prevents the impact rocker 20 from pivoting beyond a desired minimum distance from the impact rotor 11.
  • an undesirable contact between the impact rotor 11 and the impact rocker 20 can be reliably prevented by a crushing unit 10 according to the invention, while still allowing an adjustment of the gap width of the crushing gap 15 during operation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Grinding (AREA)
  • Crushing And Pulverization Processes (AREA)
EP23201158.5A 2022-10-28 2023-10-02 Brechaggregat und verfahren zur einstellung des brechspalts eines brechaggregats Pending EP4360760A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102022128778.5A DE102022128778B4 (de) 2022-10-28 2022-10-28 Brechaggregat und Verfahren zur Einstellung des Brechspalts eines Brechaggregats

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EP4360760A1 true EP4360760A1 (de) 2024-05-01

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Application Number Title Priority Date Filing Date
EP23201158.5A Pending EP4360760A1 (de) 2022-10-28 2023-10-02 Brechaggregat und verfahren zur einstellung des brechspalts eines brechaggregats

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US (1) US20240139751A1 (zh)
EP (1) EP4360760A1 (zh)
CN (1) CN117943165A (zh)
DE (1) DE102022128778B4 (zh)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3911086A1 (de) * 1988-10-10 1990-04-12 Gronholz Claus Prallbrecher
US8033489B2 (en) 2007-11-30 2011-10-11 Terex Pegson Limited Impact crusher
US10279354B2 (en) * 2014-10-24 2019-05-07 Mclanahan Corporation Impact crusher and curtain adjustment system
CN113751130A (zh) * 2021-08-11 2021-12-07 任科 一种可控碎粒式反击粉碎机

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE966555C (de) 1955-03-31 1957-08-22 Hazemag Hartzerkleinerung Zerkleinerungsvorrichtung
DE2331729A1 (de) 1973-06-22 1975-01-16 Babcock & Wilcox Ag Prallbrecher
US10960400B2 (en) 2017-04-26 2021-03-30 Kolberg-Pioneer, Inc. Apparatus and method for an apron return assembly

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3911086A1 (de) * 1988-10-10 1990-04-12 Gronholz Claus Prallbrecher
US8033489B2 (en) 2007-11-30 2011-10-11 Terex Pegson Limited Impact crusher
US10279354B2 (en) * 2014-10-24 2019-05-07 Mclanahan Corporation Impact crusher and curtain adjustment system
CN113751130A (zh) * 2021-08-11 2021-12-07 任科 一种可控碎粒式反击粉碎机

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DE102022128778A1 (de) 2024-05-08
DE102022128778B4 (de) 2024-05-16
US20240139751A1 (en) 2024-05-02
CN117943165A (zh) 2024-04-30

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