WO2021144191A1 - Vorrichtung und verfahren zum mahlen von einsatzmaterial - Google Patents
Vorrichtung und verfahren zum mahlen von einsatzmaterial Download PDFInfo
- Publication number
- WO2021144191A1 WO2021144191A1 PCT/EP2021/050209 EP2021050209W WO2021144191A1 WO 2021144191 A1 WO2021144191 A1 WO 2021144191A1 EP 2021050209 W EP2021050209 W EP 2021050209W WO 2021144191 A1 WO2021144191 A1 WO 2021144191A1
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- WO
- WIPO (PCT)
- Prior art keywords
- roller
- force
- axis
- loose
- pivot axis
- Prior art date
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- 239000000463 material Substances 0.000 title claims abstract description 44
- 238000000034 method Methods 0.000 title claims abstract description 16
- 238000003801 milling Methods 0.000 title abstract description 5
- 238000000227 grinding Methods 0.000 claims description 138
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C4/00—Crushing or disintegrating by roller mills
- B02C4/02—Crushing or disintegrating by roller mills with two or more rollers
-
- 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
Definitions
- the invention relates to a device and a method for grinding input material, in particular a device in the form of a roller mill, with a fixed roller and a loose roller, the loose roller being displaceable relative to the fixed roller.
- the rollers can be mounted and supported on a frame, in particular together on a common frame.
- roller press devices designed as material-bed roller mills for feedstock in the form of minerals or mining material are affected.
- so-called roller presses are also affected, for example with a drive power in the range of at least 200 KW to 5,000 KW.
- the invention relates to a device and a method according to the preamble of the respective independent or co-ordinate claim.
- Input material such as limestone, clinker, ore or similar rocks are ground using roller presses (also commonly known as “roller press”).
- roller presses also commonly known as “roller press”.
- the rollers are usually mounted on the one hand in a fixed manner and on the other hand so that they can be shifted in translation.
- a hydraulic force exerted on the loosely mounted loose roller in the direction of the grinding gap causes a translational displacement relative to the contact point of the rollers, or an application of force in the grinding gap.
- the loose roller is acted upon in a translational direction at at least two points, also in order to be able to prevent torques.
- roller presses usually have a fixed roller and a loose roller, the loose roller being translationally displaceable relative to the fixed roller, and the rollers being mounted and supported in a frame.
- a lower and an upper frame part are provided, on each of which a (translational) slide bearing is provided for the loose roller.
- additional stabilizing actuators are often required.
- roller press Even with a comparatively large size of the roller press and large acting forces and moments or impulses, it is not trivial from a structural point of view to use a roller press for the broadest possible range of operating states or to interpret different input materials.
- the question of how reaction forces can or should be transferred from the rollers to the frame and passed on to the foundation justifies great engineering efforts.
- the design requirements are particularly high with regard to high continuous loads.
- the roller press must also be as robust as possible with regard to skew, overload or similar negative effects. For example, exact adjustability and exact relative alignment of the roller axes therefore also remain an important factor for many roller types with regard to the selection of an advantageous overall design concept.
- the effort that has to be invested in the design of the frame (supporting structure) and in the support of the force introduction points as well as in terms of advantageous force flow paths is also comparatively high.
- the roller presses and the bearings used are subject to very high loads and stresses even if they are designed with a high safety factor.
- skewing cannot be effectively avoided in all cases, or a certain skewing desired within the narrowest possible tolerance limits cannot be set with sufficient accuracy.
- a misalignment of one of the axes (in particular the contact axis) in the range of 0 to 10 millimeters (mm) or a maximum of 15 mm is affected.
- the drive power of the rather large, heavy roller presses is, for example, in the range of 2x 150-200 KW, i.e. in total for example 350 KW, but can also be significantly larger, for example 2x 3000 KW.
- the spatial dimensions in the three spatial directions can be, for example, two to four meters each. However, significantly larger or smaller designs can also be implemented or are in use; In particular, scaling can take place individually for a particular application depending on the input material to be treated.
- the present invention is largely independent scalable by the respective roller type; The present invention has a particularly advantageous effect, particularly in the case of comparatively large roller presses.
- DE 102015 114992 A2 describes a roller press for grinding regrind, the rollers or rollers being mounted in such a way that changing the rollers can be simplified, in particular in that a line of action of a resulting operating force extends in a half-space within a supporting structure, with a Losroller cooperates with pivoting devices, which pivot around a pivot bearing as a lever on both sides.
- DE 102015 114998 A2 also describes a roller press for grinding material to be ground, the rollers being mounted for a simplified change of the loose roller, in particular with a pivot axis of a lever on both sides in an advantageous arrangement below a force application point at one end of the lever, and with the axis of the Rolling loose below the swivel axis.
- a machine having a drive roller and a driven roller which are connected to a central part of a circular connecting wire.
- the ends of the drive roller and the driven roller are coaxially connected to an end shaft.
- a swivel arm is mounted on a rotating shaft via a swivel shaft.
- the rotating shaft is mounted on a swivel bearing seat.
- An output shaft is connected to a reduction gear that is mounted on the swing arm.
- a swing arm pressure plate is connected to an upper part of a machine frame and fills gas into a compressed air bag.
- a high-pressure roller press with pendulum suspension is known from DE 102013010220 A1.
- DE 102015 110033 A1 a material bed roller mill with two rollers rotating in opposite directions and two roller holders pivotably connected to the foundation is known.
- the object of the invention is to provide a device and a method with the features described above, with which the grinding of feedstock can be further optimized, or with which individual rollers for milling feedstock can be used in combination with one another in a particularly expedient manner.
- it is also the task to provide a robust device with the simplest and most robust structural design possible, even with comparatively high reaction forces and heavy loads, whereby misalignment can also be reduced or even largely avoided, or with which misalignment can be defined at least within a very narrow tolerance range can.
- a roller press device set up for grinding input material (for example ground material in the form of minerals), in particular in the form of a roller mill, specifically as a material bed roller mill, with: a fixed roller with an at least approximately stationary roller axis; a loosely mounted loose roller with a roller axis which can be arranged in a variable position in a predefinable position relative to the fixed roller; a frame supporting at least the fixed roller and optionally also the loose roller; at least one force application unit acting on the loose roller at a force application point; wherein the fixed and loose rollers for applying a grinding force (resulting roller force in the grinding gap) and for mutual contact at a roller contact point or for defining a grinding gap for the input material can be stored and positioned relative to one another, in particular by means of the force application unit; and wherein the loose roller with the position-variable roller axis can be pivoted about a pivot axis in the manner of a one-sided lever against the fixed roller in such
- this provides a robust arrangement and enables a comparatively stress-free, variable positioning of the rollers relative to one another.
- high efficiency can also be ensured, in particular also energetic efficiency. It can also meet particularly high design requirements in an elegant, simple manner.
- the pivotable mounting of the loose roller also provides great advantages with regard to the introduction and application of force, in particular in the case of very massive rollers.
- the forces made available in particular hydraulic forces
- the amount of force required, and thus ultimately also the energy required can be minimized.
- the entire device can also be made leaner, i.e. with less effort in terms of material, costs and total weight.
- a hydraulic force to be installed can also be minimized; the effort for hydraulic fittings and pressure-resistant lines and adapters can be noticeably reduced.
- the position-variable roller axis can be pivotably positioned in the grinding gap with a comparatively small actuation force.
- the pivot axis also defines a pivot point of the one-sided lever.
- the stationary roller axis can optionally also be / remain completely stationary without any provided displacement mechanism, that is to say for all conceivable operating conditions or operating states.
- a loose roller in the broader sense is to be understood as that roller which can be actively positioned relative to the fixed roller and is also mounted locally displaceable for relative displacement.
- a fixed roller is to be understood analogously as a roller that is mounted in a stationary manner without any local displacement being provided.
- the fixed roller can also be mounted in a pivot bearing.
- the terms chosen here for fixed and floating bearings are independent of any mechanical or kinematic requirements for static / dynamic determination. The terms chosen here primarily serve to illustrate the two different roller types.
- the pivot axis is arranged on the tangent of the fixed roller and the loose roller at the roller contact point, provided that there is a roller contact point due to a grinding gap of zero through direct contact between the fixed roller and the loose roller. If the grinding gap is zero different, so the pivot axis between the tangent of the fixed roller is arranged at the intersection of the connecting line between the stationary roller axis and the variable position of the roller axis and the tangent of the loose roller at the intersection of the connection line between the stationary roller axis and the variable position of the roller axis.
- between the tangents also includes lying on at least one of the tangents, which results in particular in the special case of a grinding gap of zero, since in this special case both tangents coincide and the pivot axis is thus arranged on both coincident tangents.
- the pivot axis can lie in particular on the tangent of the fixed roller at the intersection of the connecting line between the stationary roller axis and the variable-position roller axis, since this would allow a variable grinding gap from zero.
- the grinding gap is small compared to the diameter of the fixed roller and the diameter of the loose roller, so that the assumption of a grinding gap of zero can be within the scope of the tolerances.
- the grinding gap can also assume negative values, which are then limited to a maximum of the depth at which the rollers mesh with one another.
- the arrangement according to the invention in particular also enables the frame to be used in an advantageous manner.
- conventional, proven designs and constructions of the frame can also be implemented for the arrangement according to the invention.
- the arrangement according to the invention is preferably set up for drive powers in the range of at least 200 KW to 5,000 KW.
- the bearings used are set up in particular to intercept and pass on impulses and reaction forces which are exerted on the rollers and bearings by ground material in the form of minerals or stones or the like during grinding. Measures that are advantageous or feasible in terms of system technology, process technology and construction can be specified or restricted by this area of application. The person skilled in the art must also look for particularly adequate measures specifically for the desired field of application.
- a (purely) mechanical misalignment suppression can advantageously be dispensed with in a roller device according to the invention.
- Hydraulic measures to suppress misalignment can also be at least partially dispensed with.
- the arrangement according to the invention also provides the advantage that skew simply thanks to the type and Way the storage of the rollers relative to each other and thanks to a pivoting movement of the loose roller can be effectively reduced or even completely avoided.
- a one-sided lever or a one-sided lever arrangement is to be understood as an arrangement in which only one end of the lever is pivoted and the lever is arranged on the other side in the pivot bearing.
- the load arm and the force arm coincide.
- With the one-sided lever only one end of the lever is subjected to force. There is only one point of application of force, and pivoting the lever does not result in any force or torque being generated at the other end of the lever. Rather, a pivot bearing is provided at the other end (pivot point) for pivoting the lever about the pivot bearing.
- a point of action or an interaction point or a mechanical interface is arranged on the route between the pivot bearing and the end of the lever. In other words: there is no swinging countermovement.
- the point of application of force is arranged, for example, on a bearing block of the loose roller or between bearing blocks of the loose roller, the bearing blocks preferably being coupled when force is applied between the bearing blocks, in particular in such a way that a hydraulic force can be transmitted to the bearing blocks via the coupling.
- bearing bushes, roller bearings or similar rotary bearing elements can be provided as bearing blocks.
- the jewels are used in particular to hold the bearings and to transmit the reaction forces to the bearings.
- a coupling of two or more jewels is not absolutely necessary. However, if a misalignment is to be completely prevented, coupling the jewels can be particularly effective.
- the coupling can be implemented, for example, in that the two bearing blocks and at least one component for the coupling consist of a cast part.
- the coupling can also be realized by a connection (for example screwed) of a steel tube / steel frame with the bearing blocks.
- a connection for example screwed
- the point of application of force can, for example, lie between the two bearing blocks, or a force application point is nevertheless provided for each bearing block.
- the invention is also based on the concept of ensuring a positioning of a loose roller relative to a fixed roller by means of a one-sided lever arrangement only by translational actuation. Rotary adjusting movements or, for example, the use of eccentrics are not required. According to the invention, a comparatively slim, simple construction with comparatively few interacting components and few relative movements can therefore be provided. In this way, a structural adaptation or scaling can also take place in a simple manner.
- the terms “fixed” and “loose” relate in particular to an operating state for grinding input material.
- the fixed roller is usually not displaced during grinding, but can nevertheless be mounted in such a way that, for example, the fixed roller can be displaced for assembly purposes.
- the loose roller is positioned.
- the inventive concept can, however, also be transferred to two rollers that are detached from one another.
- the roller press device is designed as a material bed roller mill. It has been shown that the advantages according to the invention described here can also be implemented particularly advantageously in the case of a material-bed roller mill.
- the distance r Abs between the pivot axis and the connecting line between the stationary roller axis and the variably arranged roller axis along a right-angled on the connecting line between the stationary roller axis and the variably arranged roller axis and straight line lying through the pivot axis corresponds at least 0.15 times the sum of the radius of the fixed roller r Fixed and the radius of the loose roller n_ 0s and at most 1 times the sum of the radius of the fixed roller r Fixed and the radius of the loose roller ri_ 0s .
- the distance r Abs between the pivot axis and the connecting line between the stationary roller axis and the locally adjustable roller axis along a perpendicular line on the connecting line between the stationary roller axis and the spatially variable roller axis and the straight line through the pivot axis corresponds to at least 0.2 times the sum of the radius of the Fixed roller rFest and the radius of the loose roller n_ 0 s and at most 0.8 times the sum of the radius of the fixed roller r Fixed and the radius of the loose roller ri_ 0s .
- the distance r Abs between the pivot axis and the connecting line between the stationary roller axis and the variable position roller axis along a perpendicular line on the connection line between the stationary roller axis and the variable position roller axis and the straight line through the pivot axis corresponds to at least 0, 25 times the sum of the radius of the fixed roller rFest and the radius of the loose roller n_ 0 s and at most 0.75 times the sum of the radius of the fixed roller r Fixed and the radius of the loose roller ri_ 0s .
- the distance r Abs between the pivot axis and the connecting line between the stationary roller axis and the variably arranged roller axis along a right-angled on the connecting line between the stationary roller axis and the variably arranged roller axis and straight line through the pivot axis corresponds to at least 0 , 25 times the sum of the radius of the fixed roller rFest and the radius of the loose roller n_ 0 s and at most 0.6 times the sum of the radius of the fixed roller r Fixed and the radius of the loose roller ri_ 0s .
- the distance between the pivot axis and the point of application of force corresponds to 1 to 5 times the distance between the pivot axis and the connection line between the stationary roller axis and the variable position roller axis along a right angle on the connection line between the stationary roller axis and the roll axis, which can be arranged in a variable manner, and the straight line lying through the pivot axis.
- the virtual lever between the point of application of force and the pivot axis is 1 to 5 times as long as the distance between the roller contact point and the pivot axis.
- the distance between the pivot axis and the point of application of force corresponds to 1.5 times to 4 times the distance between the pivot axis and the connecting line between the stationary roller axis and the variable position roller axis along a right-angled on the connecting line between the stationary roller axis Roller axis and the variable-location roller axis and straight line lying through the pivot axis.
- the distance between the pivot axis and the point of application of force corresponds to 1.5 to 3 times the distance between the pivot axis and the connecting line between the stationary roller axis and the variably arranged roller axis along a right angle on the connecting line between the stationary roller axis and the roll axis, which can be arranged in a variable manner, and the straight line lying through the pivot axis.
- the distance between the pivot axis and the point of application of force corresponds to 1.75 times to 2.75 times the distance between the pivot axis and the connection line between the stationary roller axis and the variable position roller axis along a right angle on the connection line between the stationary mounted roller axis and the variable positionable roller axis and lying through the pivot axis straight line.
- the distance between the pivot axis and the point of application of force corresponds to 2 to 2.5 times the distance between the pivot axis and the connecting line between the stationary roller axis and the variable position roller axis along a right angle on the connecting line between the stationary roller axis and the roll axis, which can be arranged in a variable manner, and the straight line lying through the pivot axis.
- the angle between the vector between the pivot axis and the point of application of force and the vector between the pivot axis and the connecting line between the stationary roller axis and the locally variable roller axis is along a right angle on the connecting line between the stationary roller axis and the locally adjustable roller axis and straight line lying through the pivot axis.
- the angle is between 80 ° and 100 °, preferably between 85 ° and 95 °, particularly preferably 90 °.
- the grinding gap is not equal to zero.
- the grinding gap is between a minimum value xo. min and a maximum value xo. max adjustable in grinding mode.
- the shortest distance between the pivot axis is preferably between half the minimum value xo. min and half the maximum value xo. max set.
- the minimum value xo can particularly preferably be. min be zero.
- the one-sided lever comprises the straight connecting line between the point of application of force and the pivot axis.
- “includes” here means that the straight connection is within of the mechanical lever.
- the force is guided directly and in a straight line through the one-sided lever.
- the one-sided lever is therefore not U-shaped or parabolic, omitting the direct connecting line between the point of application of force and the pivot axis.
- the roll axis which can be arranged in a variable manner, runs through the one-sided lever.
- variable position of the roller axis is spaced a maximum of 0.1 times the length of the straight connecting line between the point of application of force and the pivot axis from the straight connection line between the point of force application and the pivot axis; the position of the roller axis which can be arranged in a variable position is particularly preferably a maximum of 0.02 times the length of the straight connecting line between the point of application of force and the pivot axis is spaced apart from the straight connecting line between the point of application of force and the pivot axis.
- the force is exerted on the point of application of force at an angle of 75 ° to 105 ° to the connecting line between the stationary roller axis and the variable-position roller axis.
- the force is preferably applied to the point of application of force at an angle of 85 ° to 95 ° to the connecting line between the stationary roller axis and the variable-position roller axis, particularly preferably the force is applied to the point of application of force at an angle of 90 ° to the connection line between the stationary roller axis and the roll axis that can be arranged in a variable manner. It is particularly preferable for the force to be applied from the bottom to the top. This enables a particularly compact design.
- the roller contact point is arranged in a section between the force application point and the pivot axis and / or is arranged at a distance from the pivot axis less than the length of the unilateral lever, the roller contact point defining a load arm of the unilateral lever.
- a contact point defined by the feed material can also be understood as a roller contact point, i.e. with a noticeably large grinding gap.
- the roller contact point can also be understood as an effective force transmission point in the grinding gap.
- the position-variable roller axis can be displaced on a curved movement path relative to the fixed roller, in particular on a circular path. This enables, for example, an adjustment of the relative roller position in the grinding gap.
- the position-variable roller axis can be positioned relative to the fixed roller by a rotary adjusting movement about the pivot axis.
- the position-variable roller axis is arranged in a lever section extending from the pivot axis between the force application point and the pivot axis, namely at a distance from the pivot axis less than or equal to half the lever length.
- the pivot axis and the point of application of force can form a lever arrangement in which the loose roller can be positioned as a one-sided lever around the pivot axis, the roller contact point being arranged at an effective lever distance from the pivot axis which is less than or equal to half the lever length between the point of application of force and the pivot axis. This enables a good force effect in the grinding point, in particular with comparatively low forces in the point of application.
- the pivot axis is aligned at least approximately parallel to the stationary roller axis.
- the pivot axis is optionally aligned exactly parallel to the stationary roller axis and / or to the position-variable roller axis.
- the position-variable roller axis can be pivoted on a circular path around the pivot axis, in particular with an exactly circular movement path around an instantaneous pole located on the swivel axis (instantaneous pole in the broader sense, since the swivel axis does not necessarily have to be displaceable).
- the pivot axis or a corresponding pivot bearing can additionally also be displaceable in a translatory manner.
- the trajectory is not a circular path, but a curve, flattened due to superimposed translation.
- a translational shift can provide further options for adapting operating parameters or for the relative arrangement of the roller axes. As far as the size of a grinding gap is concerned, however, it is usually sufficient if it can be varied in the range of only a few millimeters, which can already be ensured by pivoting.
- the position-variable roller axis can be pivoted about the pivot axis in such a way that the position-variable roller axis can be positioned in at least two spatial directions (x, z) relative to the stationary roller axis, in particular with x and z coordinates (or x- coordinates that differ from the stationary roller axis). and z-position).
- the variation in the z-direction also provides the advantage that not only the size but also the The geometry of the grinding gap can be varied.
- the ground material can advantageously be ground even if the configuration is very inhomogeneous.
- Bearing blocks that are not coupled to one another can, for example, also pivot to different degrees, in particular in order to be able to set a misalignment or an effect corresponding to that of a misalignment.
- a grinding gap can be generated which does not run parallel, but opens differently from one end of the roller to the other end.
- the loose roller is pivotably mounted within the frame (or internally of the frame) and is supported on the frame.
- a foundation or the interface for it can also be provided at least partially by means of the frame.
- An arrangement within the frame is also to be understood as an arrangement in which the frame is only provided on one side in the z-direction, in particular only on the underside of the rollers.
- An arrangement within the frame is also to be understood in particular as an arrangement in which the frame completely overlaps the rollers in at least one spatial direction.
- the pivot axis can be arranged at a distance from at least one of the roller axes which is less than or equal to the distance from the fixed bearings of the fixed roller to the stationary roller axis. This favors support in the frame. Furthermore, an advantageous force distribution can be ensured even with comparatively small lever lengths.
- At least one of the rollers is supported and mounted on the frame independently of the other roller, in particular in a plane running through the grinding gap. This also provides an advantageous arrangement with regard to the flow of force and relative movement paths.
- At least one of the rollers is supported in a plane running through the grinding gap. Last but not least, this also provides good variability with regard to the arrangement of the point of application of force or with regard to the direction of force application.
- the roller axes when the rollers are in contact at the roller contact point, are arranged relative to the pivot axis in such a way that a connecting line through these three axes forms a triangle in a plane running orthogonally thereto, in particular a preferably at least approximately isosceles triangle, preferably with the base angles the connecting line between the roller axes each less than 50 degrees, in particular less than 45 degrees, preferably less than 40 degrees, more preferably less than 35 degrees.
- the three axes advantageously define an at least approximately isosceles triangular arrangement, in particular with the pivot axis as a point pointing downwards.
- This symmetrical arrangement of the roller axes relative to the pivot axis, with the pivot axis as close as possible to the roller axes, also provides an advantageous lever ratio and can enable structural simplifications, in particular also a common storage (nevertheless preferably independent of one another) on the same pivot axis or at least approximately in the same Position on the frame.
- the base angle of the (for example isosceles) triangular arrangement can also fluctuate in a range of approximately 15 °, preferably only 10 ° or only 5 ° around the values mentioned here.
- the base angle can also be selected individually for a respective application in a value range of 45 ° plus minus 15 °.
- An alignment of the one-sided lever can be less than 90 ° relative to the horizontal plane, in particular less than 45 °, for example in the range from 20 ° to 40 °.
- the pivot angle alignment corresponds to the base angle of the triangular arrangement.
- the pivot axis is arranged below the stationary roller axis, in particular at a distance of at most half the roller diameter (maximum distance corresponds to the radius of the fixed roller and / or the loose roller). This also provides an advantageous arrangement with regard to the interaction of the application of force and gravitational forces.
- the one-sided lever arrangement is advantageously designed in such a way that the gravitational force acting in the roll center of gravity or in the center of gravity of the entire pivotable arrangement acts against the application of force.
- the load arm of the one-sided lever is defined on the one hand by the reaction force at the roller contact point and on the other hand by the gravitational force acting in the center of gravity.
- the loose roller is thus mounted on one side around the pivot axis in such a way that both the reaction force at the roller contact point and the gravitational force counteract an application of force at the point of application (on the force arm of the lever).
- This provides good reactivity and can also improve the grinding characteristics, in particular by supporting the return movement (increasing grinding gap) driven by gravity. Especially since gravity resets the roller or the grinding gap tends to open rather than close, it is also possible to dispense with a device for opening the gap (minimized outlay in terms of device technology).
- the loose roller is pivotably mounted and arranged in such a way that the gravitational force acting in the center of gravity of the loose roller acts on the load arm of the one-sided lever in a manner that enlarges the grinding gap in the direction of a return movement.
- an advantageous grinding behavior can also be achieved.
- good reactivity can be ensured, and wedging or blocking in the case of, for example, particularly hard or large input material can be effectively avoided.
- the loose roller or the position-variable roller axis is aligned at least approximately parallel to the fixed roller and is mounted in (at least) two bearing blocks, the bearing blocks of the loose roller being rotatably fixed at one point (in particular about the pivot axis) and at another point (coupling point or Support point) are coupled.
- Such an optional coupling of the jewels also enables a particularly effective fight against misalignment.
- the further point (coupling point or support point) is preferably arranged at a distance from the pivot axis.
- a coupling can in particular take place in a mechanical or hydraulic manner, in particular by means of a cross connection, cast element and / or torsion shaft (mechanical), or by means of cross-connected hydraulic cylinders (hydraulic).
- a hydraulic cylinder acting or aligned in the longitudinal direction (component of the force application unit) for applying force to the loose roller is provided for each bearing block.
- the hydraulic cylinder (s) of the force application unit acting on the bearing blocks of the (respective) roller (s) can be connected on the oil side.
- the force application unit can have a hydraulic cylinder arranged or acting between two bearing blocks of the loose roller.
- Bearing blocks of the (respective) roller (s) can have a guide in the longitudinal direction of the bearing block. The guide serves in particular to hold the bearing blocks in a predefined plane, in particular with regard to a rotation, in particular to prevent the bearing blocks from twisting (axial forces also act on the rollers in the x direction).
- the guide can stabilize or stiffen a parallelogram arrangement of the bearing blocks of the loose roller.
- the loose roller can be acted upon hydraulically on one side tangentially around the loose roll at a further point (force application point) above or below the roll axis in such a way that the hydraulic application causes a torque about the pivot axis and defines the grinding force / roll force.
- both the point of application of force and the pivot axis as well as the fixed bearing for the fixed roller are geometrically arranged in such a way that a connecting line through these points or components, or an area delimited accordingly by these points, is geometrically at a horizontal distance of a maximum of twice the roller diameter Rolls (or the diameter of a / the relatively larger roll) and runs at a vertical distance of a maximum of a factor of 1.5, in particular a maximum of a factor of 1.2 of the roll diameter of the rolls or of a / the relatively larger roll, in particular with the connecting line (contour , Course) or a corresponding area circumference contour in cross section orthogonal to the pivot axis in the form of a triangle or square, each with corner angles less than 180 °.
- the introduction of force and the interception and transmission of reaction forces can be limited locally to a very narrow area (in particular, only one-sided frame), or the area delimited by the force and bearing points is at least very compact and can be traced back to an advantageous basic geometric shape, which enables a compact, stable frame.
- the invention is also based on the concept of forming a force triangle with advantageous lever lengths and with an advantageous arrangement of the force introduction points, the bearing and reaction forces also being transmitted to this force triangle.
- the longest side of the triangle of forces can be provided by the one-sided lever extending between the pivot axis and the application of force.
- the roller contact point, the force application point and the pivot axis are arranged relative to one another in such a way that a lever ratio of the distance between the force application point and the pivot axis to the distance between the force application point and the roller contact point of at least a factor of 2 can be set.
- the position-variable roller axis, the force application point and the pivot axis can be arranged relative to one another in such a way that a lever ratio of the distance between the force application point and the pivot axis to the distance between the position-variable roller axis and the pivot axis of at least a factor of 2 can be set.
- this arrangement also provides a high level of effectiveness or efficiency.
- At least the loose roller is dimensioned and / or arranged in the frame in such a way that a free space in the z-direction relative to the frame is ensured.
- the dimensions of the structure displaced with the loose roller in the z-direction can be smaller than the dimensions of the fixed structure of the fixed roller in the z-direction. In this way, in particular, a free space which is advantageous for a wide range of movement / swiveling can also be created.
- the loose roller is acted upon at a single point of application or at least at a single radial distance in the tangential direction around the roll axis and around the pivot axis, in particular in a (hydraulic) effective direction at least approximately orthogonal to the roll axis, in particular in the vertical (z) or horizontal direction (x) Direction of action with horizontally aligned roller axes and horizontally aligned plane (xy) through the roller axes.
- the loose roller can be pivotably positioned about the pivot axis relative to the fixed roller, in particular by setting a (preferably hydraulic) force which is at least approximately tangentially oriented on one side at the point of application.
- a (preferably hydraulic) force which is at least approximately tangentially oriented on one side at the point of application.
- the force applied is skewed relative to the roller axis.
- the loose roller can be freely positioned in the frame at least in one pivoting direction, in particular at least relative to a frame part on the underside or additionally also relative to an upper frame part of the frame.
- the frame part on the underside can in particular be coupled directly to a foundation.
- the loose roller is pivotably mounted about a pivot point (pivot axis) which is arranged in a plane exactly below or above the roller contact point of the fixed roller and the loose roller, i.e. exactly halfway Distance between the two roller axes.
- the pivot axis is arranged perpendicular to the grinding gap.
- the roller press device is advantageously set up to initiate the pivoting movement exclusively by actuation or application of force in the translational direction, that is to say without a torque or without a rotary actuating movement.
- the force is applied at least approximately in an orthogonal and / or parallel direction relative to the reaction force (contact force) on the rollers.
- this also provides comparatively simple, robust kinematics.
- the pivot axis is arranged in a plane which extends parallel to the roller axes, in particular in a plane running through the grinding gap or exactly through the roller contact point, in particular in a plane running in the vertical direction.
- This arrangement which is at least symmetrical in the x-direction relative to the roller axes, provides advantages with regard to the support of the rollers and with regard to the flow of forces, in particular even with rollers of at least approximately the same size.
- the z-position in the vertical direction can be selected largely freely, in particular with regard to a particularly advantageous frame construction and / or an optionally common support of both rollers on the pivot axis.
- the loose roller can be positioned / positionable relative to the fixed roller in such a way that the pivot axis is arranged in an x-section between the grinding gap (or the roller contact point) and the roller axis of the loose roller (i.e. offset in the x-direction towards the position-variable roller axis), in particular at an x-distance to the position-variable roller axis of at least 2/3 of the x-distance between the position-variable roller axis and the roller contact point or grinding gap (in particular at an x-distance of at least 2/3 of the loose roller radius), preferably at least 3 ⁇ of this x-distance.
- this also provides an advantageous balance of power.
- a symmetrical x-arrangement of the pivot axis in the grinding gap can optionally also be varied, in particular by an x-offset in the direction of the position-variable roller axis.
- a force triangle that can be realized by the arrangement according to the invention is formed by the points P1, P2 and P3.
- the arrangement of the respective roller axis is less important in this context.
- the area spanned by the triangle of forces preferably only covers the loose roller (or its cross-sectional area) and that the roller axis of the loose roller is optionally enclosed by the triangle of forces.
- dimensioning Aspects are taken into account. The larger the distance P2 / P3 is selected in relation to the distance P1 / P3, the smaller the hydraulic cylinders or force application actuators can be designed. On the other hand, the load in point P3 also increases.
- a ratio of at least approximately 1 to 2 can be preferred, especially if the number of cylinders (actuators) should be as small as possible (especially halved compared to the prior art, i.e. especially compared to translational actuation). In many cases, cost aspects are also of great importance, so that the ratio of the distances can also be optimized with regard to costs. If the costs of the construction for the bearing point P3 increase more than the costs for the cylinders, the ratio will be chosen to be smaller, and vice versa. In this respect, the ratio can also be selected in the individual case in a range from, for example, 1: 1 to 1: 3, in particular 1: 1.5 to 1: 2.5, preferably 1: 2. The person skilled in the art can find an optimum for a particular application based on the present disclosure as a function of prioritized boundary conditions.
- one / the contact line of the two rollers (without feedstock in the grinding gap) or the center line (central longitudinal axis) of the grinding gap changes the least in height when the pivot axis in the x-direction is / is arranged close to the grinding gap. That is, such a more or less aligned arrangement (aligned in the z-direction) of the grinding gap center and pivot axis makes it possible to keep the two roller axes at least approximately in the same height position, even when the gap width is varied.
- the grinding gap thus opens as horizontally as possible, which is also advantageous with regard to a material feed from above (gravity-driven feed of the input material).
- the (preferably hydraulic) application of force about the pivot axis takes place by means of at least one plunger, in particular by means of a plunger with a tilting device, in particular by means of a plunger with a hydrostat as a tilting device.
- the force application unit can comprise, for example, at least one plunger or plunger piston or valve piston.
- plungers also offer the advantage of a particularly compact design.
- the cylinder type can be selected individually optimized for the application.
- the pivot axis is arranged on the frame, in particular in a pivot bearing integrated into the frame, in particular on a frame part on the underside. Last but not least, this also provides structural advantages and has a favorable effect on the flow of forces and moments.
- the fixed roller can be mounted, for example, in at least one bearing with the same z-coordinate as the pivot axis.
- the fixed roller is mounted, in particular mounted, on at least one / the lower frame part and optionally also on one / the upper frame part of the frame.
- the fixed roller can optionally be supported in the z-direction only on one side.
- the pivot axis is arranged in at least one spatial direction at a distance (in particular z-distance or height distance) from the fixed and / or the position-variable roller axis, which is less than or equal to the radius of the fixed roller and / or the loose roller, in particular less than a factor of 0, 8 or less than 0.7 of the radius of the loose roller. This also provides an advantageous force distribution.
- At least one fixed bearing of the fixed roller is arranged at the level of the pivot axis (same z coordinate). It has been shown that this makes it possible to minimize moments of force, in particular with regard to forces in the x-direction (grinding forces or reaction forces in the grinding gap). This also favors an advantageous frame construction.
- the fixed roller is mounted in at least one bearing with the same z-coordinate as the pivot axis, that is to say at the same height position.
- the fixed bearing can also be designed in the manner of a stop for a pivoting movement or comprise the stop; then the fixed bearing primarily fulfills a function as a stop or stop.
- a structural design with a fixed bearing, which is arranged at the level of the pivot axis in order to generate a counterforce, provides advantages with regard to the distribution of forces and stress on the frame.
- the horizontal grinding force creates a horizontal reaction force on the bearing blocks of the loose roller and fixed roller.
- the bearing blocks can be connected to one another at the pivot point or near the pivot point, it is possible to cancel or compensate for these reaction forces at these points.
- the base frame can be relieved or can optionally also be designed to be slimmer (with corresponding cost advantages).
- the pivot axis is arranged in a pivot bearing, which is formed by bearing components that are set up for the corresponding pivoting movement, in particular for pivoting movements in such an angular range that a gap between the two rollers can be set up to 200 mm, in particular for maximum Gap sizes between 80 mm and 200 mm, depending on the series.
- a plummer block housing is screwed to the base frame.
- a bolt passed through the bearing bore connects the bearing parts of the loose and fixed roller.
- the pivot bearing is designed, for example, as a maintenance-free or particularly low-maintenance pivot bearing with a Teflon fabric coating.
- the loose roller moves, for example, in a comparatively small angular range between +/- 1 mm and +/- 5 mm.
- the pivot bearing can be optimized for the load operating range of pivot angles in the range of +/- 1 mm to +/- 5 mm. Significantly larger swivel angles are not necessarily required, at least under load.
- a maintenance-free pivot bearing is preferably installed in a pivot bearing housing.
- the housing is fastened to the base frame, for example (in particular screwed, welded).
- the pivot bearing can also be installed in a bearing block.
- the swivel axis is fixed on one or both sides by a bearing block in the base frame.
- the fixed roller is supported or mounted on the frame, in particular in a frame part on the underside.
- the fixed roller can optionally also be supported or mounted on an upper frame part.
- frames and actuators previously used for translational displacement of the loose roller can optionally also be used for the pivot bearing according to the invention, or existing devices can be converted or retrofitted.
- the force is applied in the same direction as the resulting grinding force / roller force (contact force between the rollers), in particular with the force application point at least approximately at an effective lever distance which is at least twice as large as the lever distance between the pivot axis and the roller contact point. In this way, good efficiency and sensitive force metering can also be ensured.
- the lever force (in particular hydraulic force) applied at the force application point is aligned at least approximately in the direction of the grinding force, in particular exactly in the direction of the grinding force, in particular in the horizontal effective direction. This allows the effect at the contact point of the rollers to be set and controlled particularly well.
- the hydraulic force in one direction of action is a maximum of 40 °, preferably a maximum of 35 °, more preferably a maximum of 30 ° deviating from the direction of the grinding force (contact force on the rollers), in particular in one direction of action at least approximately parallel to the grinding force, in particular in horizontal effective direction.
- This variability is advantageous, for example, when the grinding gap is to be set in a wide range of sizes.
- the one-sided lever between the force application point and the pivot axis is formed by the relative arrangement of the roller contact point and the pivot axis and the force application point in such a way that the lever distance between the force application point and the pivot axis is greater than a factor of 2 of the distance between the position-variable roller axis and the pivot axis.
- the effective lever distance between the point of application of force and the position-variable roller axis can be greater than or equal to the effective lever distance between the position-variable roller axis and the pivot axis, in particular at least a factor of 1.2 to a factor of 1.5 greater, for example a factor of 2. This also provides a good lever -Effect.
- the load of the loose roller is supported against the weight force acting on the loose roller by the application of force upwards, in particular vertically upwards, in particular orthogonally to the contact force in the roller contact point.
- force upwards in particular vertically upwards, in particular orthogonally to the contact force in the roller contact point.
- this also provides good reactivity with regard to the positioning of the loose roller; this can also mean careful storage with a long service life favor.
- the lever length of the one-sided lever or power arm can be chosen largely freely.
- the force application unit is supported on the underside in the frame, in particular in a frame part on the underside.
- An underside support is to be understood as a support below the roll axes.
- the frame part on the underside can be coupled / can be coupled to a foundation. This also provides an advantageous flow of force directly out of the frame, so that the frame can be designed to be comparatively slim.
- the application of force (in particular hydraulic force) is not aligned in the direction of the grinding force / roller force, but at an angle greater than 45 °, in particular in an effective direction at least 50 °, preferably at least 55 °, more preferably at least 60 ° different from the direction of the grinding force / roller force, in particular in an effective direction at least approximately orthogonal to the grinding force / roller force, in particular in the vertical (z) effective direction.
- the application of force to the loose roller takes place in particular exclusively at one / the point of application of force below the roller axes. This also enables an advantageous arrangement of the individual components relative to one another from a structural point of view.
- the fixed roller is mounted on a pivot axis, in particular about the same pivot axis as the loose roller, the fixed roller being lockable in at least one fixed bearing with respect to a pivoting movement, in particular in a fixed bearing (stop) for forwarding grinding / roller contact forces.
- a fixed bearing stop
- the term “fixed roller” is to be interpreted in such a way that the fixed roller is the roller on which a reaction force is generated, which is caused by the force acting on the loose roller.
- the fixed roller should not shift; nevertheless it can be advantageous to also mount the fixed roller in a / the pivot bearing, although this mounting is provided for the reaction forces without relative movement of the fixed roller in the frame (in particular via a stop).
- the fixed roller can be supported on the same height coordinate as the pivot axis in at least one fixed bearing in order to transmit grinding / roller contact forces.
- the fixed bearing is set up in particular to absorb forces in the circumferential direction about the pivot axis.
- the fixed bearing can in particular also have a stop.
- the fixed roller can also be mounted on the pivot axis. Last but not least, this also has advantages in terms of compensating for grinding forces and bearing forces.
- the frame is designed without an upper frame part, in particular exclusively comprising at least one underside / underside frame part, the rollers being supported and mounted on the underside.
- Both the loose roller and the fixed roller can be supported and / or mounted in a frame part which extends exclusively below the roller axes. This also makes it possible to ensure an advantageous flow of force / torque.
- a frame (11) which supports at least the fixed roller and optionally also the loose roller;
- a frame (11) which supports at least the fixed roller and optionally also the loose roller;
- the loose roller is supported on the one hand in the pivot axis, and on the other hand the loose roller is supported on the other side by its center of gravity in at least one point of application of force on the frame, in particular on a frame part below.
- a frame (11) which supports at least the fixed roller and optionally also the loose roller;
- the aforementioned object is also achieved in particular by a method for grinding input material (for example ground material in the form of minerals), in particular by means of a roller press device described above, with the steps of: driving at least one fixed roller with at least approximately stationary roller axis and one loosely mounted loose roller with a roller axis that can be arranged in a variable manner; Applying force to the loose roller to apply a grinding force and to position the loose roller relative to the fixed roller;
- the loose roller with the variable roller axis is pivoted about a pivot axis by the application of force in the manner of a one-sided lever and the relative position of the loose roller is defined relative to the fixed roller, the force being applied at a force application point of the one-sided lever, in particular at a Force application point which is at least as far apart, preferably further apart, from the position-variable roller axis as / than the position-variable roller axis from the pivot axis.
- the driving is described here as an example for both rollers. Optionally, only one of the rollers is driven.
- the loose roller is moved in the (rotational) direction of the application of force during the pivoting movement. In this way, a compact arrangement in a stable frame with advantageous force transmission can also be ensured.
- the force is applied to the force arm of the one-sided lever, the loose roller being pivoted relative to the fixed roller in such a way that the loose roller contacts the fixed roller in the section of the force arm and defines the load arm through the roller contact point or through the contact material / regrind (load arm falls on one-sided lever together with the power arm).
- This also provides an advantageous controllability realizable.
- the reactivity and / or the force effectiveness of the arrangement can be optimized in a simple manner via the selection of the lever ratios.
- the force is applied at an angle of at least 60 °, preferably at least 75 ° or a maximum of 30 °, preferably a maximum of 15 ° to the grinding force (reaction force at the roller contact point), in particular at least approximately orthogonal to the grinding force or at least approximately in the direction of the grinding force, respectively opposite to the grinding force (reaction force).
- various advantages of the present invention can also be realized particularly well if the force is applied at least approximately in the horizontal and / or at least approximately in the vertical direction, with reference to an arrangement of the two roller axes in a horizontal plane.
- two advantageous force application concepts can be implemented alternatively or also in combination with one another, in particular with at least approximately vertical and / or horizontal force application.
- different advantageous variants for the design of the frame can be implemented for each individual case.
- the application of force (in particular by means of hydraulic cylinders) in at least an approximately vertical direction is particularly advantageous, in particular with regard to a force transmission (reaction force of the rollers) directly into the foundation.
- the inventive mounting around the pivot axis also enables the structural concept that the force from the grinding gap is passed directly into the foundation via the force application points, in particular at least approximately in the vertical direction, so that a force diversion from the horizontal force direction to the vertical force direction in any Frame parts is no longer required or can largely be omitted.
- the force is applied at an angle of at least 60 °, preferably at least 75 ° to the grinding force (reaction force at the roller contact point), in particular at least approximately orthogonally to the grinding force or at least approximately in the vertical direction, in particular vertically upwards.
- the frame can be open at the top.
- the force is applied at an angle of a maximum of 30 °, preferably a maximum of 15 ° to the grinding force (reaction force at the roller contact point), in particular at least approximately parallel to the grinding force or at least approximately in the horizontal direction.
- this also favors the implementation of the roller concept according to the invention in conventional frames, in particular with a minimized number of actuators, in particular also without the risk of jamming or wedging translational guides, especially when forces are minimized thanks to advantageous leverage ratios.
- the roller concept according to the invention can also be implemented, for example, by comparatively simple retrofitting of existing systems.
- the force is applied (in particular exclusively) at an angle of a maximum of 15 ° or a maximum of 10 ° to the grinding force, in particular at least approximately in the direction of the grinding force or opposite to the grinding force, in particular in an at least approximately horizontal plane.
- the force is applied (in particular exclusively) at an angle of at least 75 ° or at least 80 ° to the grinding force, in particular at least approximately orthogonal to the direction of the grinding force, in particular in an at least approximately vertical plane.
- the force is applied in such a way that a force arm of the unilateral lever (effective lever distance between pivot axis and force application point) is implemented which is at least twice as long as the load arm of the unilateral lever (effective lever distance between pivot axis and position-variable roller axis), in particular at least a factor 2.5 or a factor of 3 as long.
- a good force effect can also be achieved; in particular, the energy required to provide a predefined application can be effectively minimized.
- the roller contact force takes place by regulating the application of force at a point of application of force at a single predefined distance from the pivot axis. In this way, a particularly slim arrangement can also be provided.
- the loose roller is positioned relative to the fixed roller exclusively by the pivoting movement, that is to say without translational displacement.
- the pivoting movement can also be initiated exclusively by an actuation or application of force in the translational direction, that is to say without torque or without a rotary actuating movement.
- the rollers are mounted and supported in such a way that reaction forces to the grinding force are either on the same horizontal plane as the pivot axis and / or as the force application point or at least approximately parallel for the reaction force in the grinding gap are passed into the frame, or in at least approximately vertical direction and / or at least approximately orthogonal to the reaction force in the grinding gap at a counter bearing of the loose roller in the frame.
- this also provides advantageous force flow paths or a compact or even particularly stable frame arrangement. In particular, moments of force can be minimized. Forces in the x direction can be directed into the frame largely without any moments.
- the aforementioned object is also achieved in particular by a control / regulating device set up to carry out a method described above, the control / regulating device being set up to control / regulating the driving of the fixed roller and / or the loose roller and being set up to control / Regulating the application of force to the loose roller, the control / regulating device being in communication with or comprising a measuring device, the control / regulating device being set up to apply force at the point of application of force on the loose roller in an arrangement in FIG Type of a one-sided lever to control / regulate a / the pivot axis of the loose roller, in particular by controlling and regulating at least one force application unit with hydraulic actuator, in particular for positioning the loose roller by a predefined pivoting movement.
- the aforementioned object is also achieved according to the invention in particular by using a pivot axis for supporting a loose roller of a material bed roller mill relative to at least one further roller of the material bed roller mill, in particular relative to a fixed roller, by applying force around the pivot axis in the manner of a unilateral lever and by pivoting the loose roller on the power arm of the one-sided lever, in particular for supporting a loose roller of a previously described roller press device, in particular in a previously described method, in particular with the pivot axis in an arrangement in the grinding gap (or in alignment in a vertical plane running through the grinding gap) or at least approximately at the same x-distance to the roller axes (i.e. in at least approximately symmetrical x-position between the roller axes).
- the pivot axis can be mounted in one or more pivot bearings, in particular on a common frame below the roller axes.
- FIG. 1 shows a roller or roller press arrangement according to the prior art
- FIG. 2 in a partially sectioned side view in a schematic representation
- FIG. 3 in a partially sectioned side view in a schematic representation
- Fig. 5 is a schematic representation of a roller press device with a
- Triangular arrangement according to exemplary embodiments.
- a roller press or a roller press device 10 for grinding input material M is arranged in / on a frame 1, 11 and comprises at least one fixed roller 2 and at least one loose roller 3.
- the loose roller is supported in a translatory manner in at least one slide bearing 4.
- the frame 11 comprises for example a frame part 11a on the underside / underside and a frame part 11b on the top or on the top.
- the fixed roller is mounted in at least one (fixed) bearing 12.
- a loose bearing 13 for the loose roller is designed as a pivot bearing.
- a counter bearing 14 for absorbing reaction forces can be provided, in particular comprising a stop on which the fixed roller can be supported against reaction forces.
- a force application unit 15 in particular with at least one hydraulic actuator (for example plunger with tilting device)
- a one-sided lever arrangement 16 can be applied for the purpose of pivoting movement of the loose roller about the pivot axis. The force is introduced at the force arm 16.1 of the one-sided lever and transmitted to the fixed roller via the load arm 16.2.
- the load arm extends from the pivot axis therein Direction as the power arm, and is formed in particular between the pivot axis and the center of gravity of the loose roller or all components wasted together with the loose roller.
- a control / regulating device 20 is coupled to a measuring device 21, in particular comprising a swivel angle sensor.
- d1 effective distance or lever arm between the pivot axis and the position-variable roller axis in particular the distance orthogonal to the direction of force in the x or z direction
- d2 effective distance or lever arm between the position-variable roller axis and the point of application of force in particular the distance in the x- or z-direction
- d3 lateral distance of the pivot axis from the position-variable roller axis in particular the distance in the x-direction
- d4 lateral distance between the pivot axis and the stationary roller axis in particular the distance in the x direction
- d5 distance between pivot axis and frame or frame part on the underside in particular in the z-direction
- F2 vector
- hydraulic hydraulic force exerted on the loose roller, in particular in the z-direction against the direction of gravity
- X0 grinding gap in particular the yz plane through the roller contact point; y2 stationary roller axis; y3 position-variable roller axis;
- FIG. 1 shows a previously known roller press in which the loose roller is mounted in a translatory manner in the frame 1 above and below in a slide bearing.
- a translational displacement of the loose roller against the fixed roller in particular by applying force at at least two force introduction points, also leads to reaction forces in the fixed bearings 12.
- the force is applied in this example at two points (above and below the center of gravity of the loose roller), in particular by means of cylinders, in particular in each case in the horizontal direction corresponding to the translational displacement direction (or in the direction in which the translational sliding bearing extends).
- This type of application of force is owed in particular to the most symmetrical possible force profile in the frame.
- the contact point of the rollers in the grinding gap is therefore also at least approximately in the center of the frame, at least with respect to the z-direction or with respect to the two illustrated force application points (force vector arrows F1, corresponding to the force exerted on the loose roller).
- FIG. 2 shows a first variant for forming a one-sided lever arrangement 16 according to the present inventive concept.
- the application of force at point P2 takes place essentially in the horizontal direction (in particular only at a single force application point), the load arm being approximately half as long as the force arm (d1 approximately equal to d2).
- the loose roller is pivoted by the application of force.
- the pivot axis P3 (pivot point for the pivoting movement) is arranged at least approximately in the grinding gap XO (d3 approximately equal to d4), that is to say at the same x-coordinate.
- the application of force can either take place at just one point or at several points. In other words: In contrast to the structure according to FIG. 1, no symmetrical arrangement of two force application cylinders is required.
- Fig. 2 the effective lever length is also indicated (dashed line), in projection orthogonal to the application of force, namely on the one hand the force arm 16.1 (relatively narrow for the purpose of illustration), the length of which is defined by the position of the force application point P2, and on the other hand the load arm 16.2 (relatively wider for the purpose of illustration), the length of which is defined by the force transmission point P1 or by the contact point of the rollers in the grinding gap.
- the pivoting movement is illustrated by the back and forth arrow about the pivot axis P3, 13. Depending on the load condition and size or particle spectrum of the input material, a pivoting movement during operation can be more or less strong.
- the loose roller 3 is therefore held in the frame between points P2 and P3.
- a force is only transmitted between the loose roller and the frame at these points, and indirectly also via the contact point P1.
- the at least one force application unit 15 can also be set up to actuate in both directions of action (opposite pivoting directions) (in particular both tensile and compressive forces).
- actuation is only carried out against the fixed roller, in particular since the loose roller can advantageously be pivoted back (purely) by gravity. Last but not least, this also favors fast, reactive and thus low-stress operating behavior, even with comparatively massive, heavy rolls.
- the way in which the force is applied in the grinding gap can thereby also be adapted or optimized in a comparatively simple manner, in particular as a function of the material used.
- no great force is required to move the loose roller back out of the grinding gap (to the left in FIG. 1). This, too, can provide advantages with regard to the construction of the frame and / or the selection of the drives / actuators.
- a ratio P2 / P3 to P1 / P3 of at least approximately 1 to 2 can be preferred, in particular if the number of cylinders (force actuation actuators) should be as low as possible (based on a translational bearing: in particular should be halved). In many cases, cost aspects are also of great importance so that the ratio of the distances will also be optimized with regard to costs. If the costs of the construction for the bearing point P3 increase more than the costs for the cylinders, the ratio will be chosen to be smaller, and vice versa. In this respect, the ratio can also be selected in the individual case in a range from, for example, 1: 1 to 1: 3, in particular 1: 1.5 to 1: 2.5, preferably 1: 2.
- FIG. 3 shows a second variant for forming a one-sided lever arrangement 16 according to the present inventive concept.
- the application of force at point P2 takes place essentially in the vertical direction or essentially orthogonally to the reaction force F at the roller contact point (in particular also at least approximately orthogonally to an extension plane of the lower frame part or a foundation), the load arm 16.2 being significantly shorter than half of the force arm 16.1 (z-distance P1 to P3 ⁇ x- Distance P2 to P3).
- the pivot axis P3 is arranged in the grinding gap XO (distance d3 approximately equal to distance d4).
- the loose roller can be mounted in a particularly reactive manner with regard to a return movement, and the pivot axis can be relieved at least to a certain extent with regard to the weight of the loose roller.
- a frame section can be designed comparatively weakly laterally outside of the loose roller or can be omitted completely.
- a power transmission from the loose roller to the frame can in particular also take place by means of a diagonally connecting support or similar cross member between the loose roller and the frame, in particular by means of a frame support 11.1 or strut, in particular with a directional specification for the force flow.
- Such a cross support is advantageously connected directly or indirectly to an underside of the frame or also directly to a foundation.
- the transmission of force from the loose roller to the frame can be deflected in this way, in particular with a predetermined direction into the foundation. Effect:
- the transmission of forces can take place in a very low-stress manner, and the frame can be designed accordingly slim.
- FIG. 4 shows a third variant for forming a one-sided lever arrangement 16 according to the present inventive concept.
- FIG. 4 illustrates several aspects which can each be advantageous in themselves, but which do not necessarily have to be implemented in combination with one another, in particular the following aspects: advantageously slim structure; advantageous power flow path; advantageous force coupling with a / the foundation (not shown; below frame part 11a); synergetic support of the rollers, in particular advantageous use of the pivot axis 13 as a common bearing axis (in particular for the purpose of compensating for reaction forces).
- the application of force at point P2 takes place essentially in the vertical direction or at least approximately orthogonally to the reaction force at the roller contact point, the load arm 16.2 being approximately half as long as the force arm (d1 approximately equal to d2).
- the pivot axis P3 is arranged in the grinding gap XO (d3 approximately equal to d4), that is to say in the same x position below the roller contact point.
- the fixed roller can optionally be mounted about the same pivot axis P3 or on the same pivot axis P3 as the loose roller and is supported against reaction forces about the pivot axis on the counter bearing 14. Active relative positioning is preferably only carried out by the loose roller 3.
- the counter bearing 14 can, however, optionally also be a fixed bearing to which the fixed roller is coupled in a stationary manner (for example screwed to a frame Jewel 14).
- a relative movement of the fixed roller is, as the expression “fixed roller” also makes clear, not necessarily necessary, that is, not even when the pivot axis is used as a bearing axis for the fixed roller.
- the construction shown in FIG. 4 optionally also provides the constructive advantage that the pivot axis of the loose roller can also be used to support the fixed roller, in particular with regard to force compensation in the x direction.
- the frame 11 has only one frame part 11a arranged on the underside. This can advantageously be coupled directly to a foundation (not shown), which, in particular in the case of very massive, large roller devices, favors an advantageous transmission of force. In particular, no weight force components or reaction forces caused by the grinding process have to be introduced laterally into a frame. From FIG. 4 it can also be seen in particular that a configuration of the frame 11 without a frame part on the top provides further advantages, for example with regard to general accessibility and / or with regard to material supply M.
- Fig. 5 describes, generally with reference to all the previously described exemplary embodiments according to the invention, a relative arrangement of the axes (pivot axis and roller axes) relative to one another according to a triangular arrangement (with the triangular geometry of an inverted triangle), with the purely geometrically explanatory dashed line in relation to the pivot axis 13 symmetrical arrangement of the roller axes y2, y3 is indicated.
- An at least approximately isosceles triangle TR is defined by the respective axis y2, y3, 13 as the corner point, the base angle a advantageously being as small as possible.
- the isosceles triangular arrangement TR results in particular when the rollers are in direct contact (grinding gap at least approximately zero, or nonexistent). If the rollers are spaced apart from one another, for example due to feedstock in the grinding gap, the base angle is correspondingly smaller.
- the base angle ⁇ of the triangular arrangement TR is still comparatively large, in particular in the range of 45 °;
- the base angle a is comparatively small, in particular in the range of only approx. 25 ° to 35 °.
- the pivot axis is advantageously arranged at a (z) distance smaller than half the roller diameter to the roller axes.
- the base angle ⁇ can assume an amount in the range from 20 to 50 degrees (or in individual cases even up to 60 degrees).
- triangular arrangement TR it has been shown that by means of such a triangular arrangement TR, numerous advantages of the invention can generally be ensured in each case in the different exemplary embodiments, regardless of the specific application.
- the structural concept according to the invention can therefore advantageously also be implemented specifically by means of such triangular arrangements TR, in particular with the size of the base angle or with the relative arrangement of the pivot axis in each case as a structural design parameter.
- the relative x-position and / or relative z-position of the pivot axis can also be adapted individually, for example slightly offset relative to the axis of rotation of the loose roller and shifted out of the grinding gap.
- the triangular arrangement TR is preferably an isosceles triangular arrangement.
- the triangular arrangement TR is not necessarily only an isosceles triangular arrangement; rather, it is within the scope of expert adaptation to optimize the two base angles at least within a narrow range of variation for the respective application.
- the one-sided lever (one-sided lever arrangement) 16 is indicated schematically in each case by a dashed line, which extends from the pivot axis 13 to / to a force application point P2.
- the respective effective lever length (Fig. 2) is to be measured in terms of amount, in particular, orthogonally to the direction of force.
- the section in which the one-sided lever is formed can be individually defined depending on the specifically selectable position for the force application point, as can the length of the lever and the length ratio between the force - and load arm. Regardless of this, the loose roller is arranged both in the area of the load arm and in the area of the force arm, or these areas overlap (one-sided lever arrangement without a free load arm, i.e. without a rocker).
- FIG. 6 shows, in a greatly simplified manner, only the fixed roller 2 and the loose roller 3 in relation to the pivot axis P3.
- a connecting line is drawn between the stationary roller axis y2 and the variable-position roller axis y3. At the roller contact point P1, this connecting line intersects the fixed roller 2 and the loose roller 3.
- the tangent of the fixed roller 2 and the loose roller 2 is perpendicular to this connecting line and runs through the pivot axis P3.
- Fig. 7 very extremely oversized grinding gap XO is shown. In reality, the grinding gap XO will be very much smaller than the radius of the fixed roller 2 and the radius of the loose roller 3. The distance between the fixed roller 2 and the loose roller 3 now results in two spaced tangents.
- the pivot axis P3 is arranged exactly in the middle between the tangents in the example shown.
- TR isosceles triangle a base angle ß alignment of the one-sided lever relative to the horizontal plane
Landscapes
- Engineering & Computer Science (AREA)
- Food Science & Technology (AREA)
- Crushing And Grinding (AREA)
- Rolls And Other Rotary Bodies (AREA)
- Grinding Of Cylindrical And Plane Surfaces (AREA)
- Crushing And Pulverization Processes (AREA)
- Rolling Contact Bearings (AREA)
- Press Drives And Press Lines (AREA)
Abstract
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN202180009091.3A CN115315315A (zh) | 2020-01-14 | 2021-01-08 | 用于研磨输入材料的设备和方法 |
AU2021208299A AU2021208299B9 (en) | 2020-01-14 | 2021-01-08 | Device and method for milling input material |
BR112022011712A BR112022011712A2 (pt) | 2020-01-14 | 2021-01-08 | Dispositivo e método para a moagem de material de entrada |
PE2022001090A PE20221431A1 (es) | 2020-01-14 | 2021-01-08 | Dispositivo y procedimiento para la molienda de material de alimentacion |
CA3163282A CA3163282A1 (en) | 2020-01-14 | 2021-01-08 | Apparatus and method for grinding feedstock and also open-loop/closed-loop control device and use |
US17/792,678 US20230042116A1 (en) | 2020-01-14 | 2021-01-08 | Device and method for milling input material |
EP21700191.6A EP4090468B1 (de) | 2020-01-14 | 2021-01-08 | Vorrichtung und verfahren zum mahlen von einsatzmaterial |
Applications Claiming Priority (12)
Application Number | Priority Date | Filing Date | Title |
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BE20205022A BE1027984B1 (de) | 2020-01-14 | 2020-01-14 | Vorrichtung und Verfahren zum Mahlen von Einsatzmaterial sowie Steuerungs-/Regelungseinrichtung und Verwendung |
DE102020200402.1 | 2020-01-14 | ||
BE20205023A BE1027987B1 (de) | 2020-01-14 | 2020-01-14 | Vorrichtung und Verfahren zum Mahlen von Einsatzmaterial sowie Steuerungs-/Regelungseinrichtung und Verwendung |
DE102020200401.3 | 2020-01-14 | ||
BE20205020A BE1027983B1 (de) | 2020-01-14 | 2020-01-14 | Vorrichtung und Verfahren zum Mahlen von Einsatzmaterial sowie Steuerungs-/Regelungseinrichtung und Verwendung |
DE102020200404.8 | 2020-01-14 | ||
DE102020200402.1A DE102020200402A1 (de) | 2020-01-14 | 2020-01-14 | Vorrichtung und Verfahren zum Mahlen von Einsatzmaterial sowie Steuerungs-/Regelungseinrichtung und Verwendung |
BE2020/5020 | 2020-01-14 | ||
BE2020/5023 | 2020-01-14 | ||
DE102020200404.8A DE102020200404A1 (de) | 2020-01-14 | 2020-01-14 | Vorrichtung und Verfahren zum Mahlen von Einsatzmaterial sowie Steuerungs-/Regelungseinrichtung und Verwendung |
DE102020200401.3A DE102020200401A1 (de) | 2020-01-14 | 2020-01-14 | Vorrichtung und Verfahren zum Mahlen von Einsatzmaterial sowie Steuerungs-/Regelungseinrichtung und Verwendung |
BE2020/5022 | 2020-01-14 |
Publications (1)
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WO2021144191A1 true WO2021144191A1 (de) | 2021-07-22 |
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PCT/EP2021/050209 WO2021144191A1 (de) | 2020-01-14 | 2021-01-08 | Vorrichtung und verfahren zum mahlen von einsatzmaterial |
Country Status (9)
Country | Link |
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US (1) | US20230042116A1 (de) |
EP (1) | EP4090468B1 (de) |
CN (1) | CN115315315A (de) |
AU (1) | AU2021208299B9 (de) |
BR (1) | BR112022011712A2 (de) |
CA (1) | CA3163282A1 (de) |
CL (1) | CL2022001589A1 (de) |
PE (1) | PE20221431A1 (de) |
WO (1) | WO2021144191A1 (de) |
Citations (9)
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DE3224249A1 (de) | 1981-07-16 | 1983-01-27 | Giacomo 17047 Vado Ligure Savona Ferrero | Walzenmuehle |
GB2103107A (en) | 1980-12-04 | 1983-02-16 | Robinson And Son Plc Thomas | Mounting arrangement for a grinding roll |
DE3724742A1 (de) | 1987-07-25 | 1989-02-02 | Westfaelische Maschbau Gmbh | Walzenbrecher mit festwalze und loswalze |
DE3818540A1 (de) | 1988-05-31 | 1989-12-07 | Rieter Werke Haendle | Walzwerk mit verstellbarem walzenspalt fuer keramische massen |
DE102013010220A1 (de) | 2013-06-18 | 2014-12-18 | Khd Humboldt Wedag Gmbh | Hochdruck-Walzenpresse mit Pendelaufhängung |
CN104998714A (zh) | 2015-08-10 | 2015-10-28 | 福建美斯拓机械设备有限公司 | 一种对辊式粉碎制砂机 |
DE102015110033A1 (de) | 2015-06-23 | 2016-12-29 | Gebr. Pfeiffer Se | Gutbett-Walzenmühle |
DE102015114998A1 (de) | 2015-09-07 | 2017-03-09 | Mbe Coal & Minerals Technology Gmbh | Rollenpresse |
DE102015114992A1 (de) | 2015-09-07 | 2017-03-09 | Mbe Coal & Minerals Technology Gmbh | Rollenpresse |
Family Cites Families (3)
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DE2540269B2 (de) * | 1975-09-10 | 1980-12-18 | Kloeckner-Humboldt-Deutz Ag, 5000 Koeln | Einstellbare Stützvorrichtung für die Loswalze einer Walzenmühle |
CN2296764Y (zh) * | 1997-05-01 | 1998-11-11 | 杨宏琰 | 摇臂型辊式原料制备设备 |
US6685118B1 (en) * | 2000-12-19 | 2004-02-03 | Robert M. Williams, Jr. | Two roll crusher and method of roller adjustment |
-
2021
- 2021-01-08 PE PE2022001090A patent/PE20221431A1/es unknown
- 2021-01-08 WO PCT/EP2021/050209 patent/WO2021144191A1/de active Application Filing
- 2021-01-08 EP EP21700191.6A patent/EP4090468B1/de active Active
- 2021-01-08 CN CN202180009091.3A patent/CN115315315A/zh active Pending
- 2021-01-08 CA CA3163282A patent/CA3163282A1/en active Pending
- 2021-01-08 US US17/792,678 patent/US20230042116A1/en active Pending
- 2021-01-08 AU AU2021208299A patent/AU2021208299B9/en active Active
- 2021-01-08 BR BR112022011712A patent/BR112022011712A2/pt unknown
-
2022
- 2022-06-14 CL CL2022001589A patent/CL2022001589A1/es unknown
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2103107A (en) | 1980-12-04 | 1983-02-16 | Robinson And Son Plc Thomas | Mounting arrangement for a grinding roll |
DE3224249A1 (de) | 1981-07-16 | 1983-01-27 | Giacomo 17047 Vado Ligure Savona Ferrero | Walzenmuehle |
DE3724742A1 (de) | 1987-07-25 | 1989-02-02 | Westfaelische Maschbau Gmbh | Walzenbrecher mit festwalze und loswalze |
DE3818540A1 (de) | 1988-05-31 | 1989-12-07 | Rieter Werke Haendle | Walzwerk mit verstellbarem walzenspalt fuer keramische massen |
DE102013010220A1 (de) | 2013-06-18 | 2014-12-18 | Khd Humboldt Wedag Gmbh | Hochdruck-Walzenpresse mit Pendelaufhängung |
DE102015110033A1 (de) | 2015-06-23 | 2016-12-29 | Gebr. Pfeiffer Se | Gutbett-Walzenmühle |
CN104998714A (zh) | 2015-08-10 | 2015-10-28 | 福建美斯拓机械设备有限公司 | 一种对辊式粉碎制砂机 |
DE102015114998A1 (de) | 2015-09-07 | 2017-03-09 | Mbe Coal & Minerals Technology Gmbh | Rollenpresse |
DE102015114992A1 (de) | 2015-09-07 | 2017-03-09 | Mbe Coal & Minerals Technology Gmbh | Rollenpresse |
Also Published As
Publication number | Publication date |
---|---|
CN115315315A (zh) | 2022-11-08 |
EP4090468A1 (de) | 2022-11-23 |
PE20221431A1 (es) | 2022-09-21 |
AU2021208299A1 (en) | 2022-08-18 |
BR112022011712A2 (pt) | 2022-09-06 |
US20230042116A1 (en) | 2023-02-09 |
CL2022001589A1 (es) | 2023-01-20 |
EP4090468B1 (de) | 2024-04-10 |
AU2021208299B2 (en) | 2023-07-20 |
CA3163282A1 (en) | 2021-07-22 |
AU2021208299B9 (en) | 2023-07-27 |
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