DE102019207228A1 - Device for movement-tolerant material-elastic coupling of a grinding chamber to eccentric shafts of a vibrating disc mill and use - Google Patents

Abstract

The invention relates to a vibratory disk mill device (10) for comminuting input material, in particular input material with a particle size of less than 20 mm, in particular designed for grinding the input material to particle sizes of less than 75 μm, with: a mill housing (11); a grinding system (13) arranged in the mill housing such that it can vibrate, with a grinding chamber (13.1) and with at least one grinding stone arranged movably in the grinding chamber; at least one eccentric shaft drive (14) mounted in the mill housing and generating the oscillating movement in the grinding chamber and at least two eccentric shafts (15); a balancing mass unit (13) connected to the eccentric shaft drive, set up to compensate for unbalance; wherein the grinding chamber (13.1) is coupled to the eccentric shafts (15) by means of at least one material-elastic link unit (17). This also enables improved operating conditions. The invention also relates to the use of an articulation unit for the material-elastic mounting of the grinding system of the vibratory disk mill.

Description

TECHNICAL AREA

The invention relates to a device for the movement-tolerant material-elastic coupling of a grinding chamber to eccentric shafts of a vibrating disk mill. The invention also relates to the use of a movement-tolerant coupling, material-elastic articulation unit for a vibrating disc mill. Last but not least, the invention also relates to a production method for the material-elastic link unit. In particular, the invention relates to a device and a method or a use according to the preamble of the respective independent or subsidiary claim.

BACKGROUND

Vibrating disc mills are used for the finest possible comminution of solids, in particular for the purpose of providing the comminuted or ground solids for material analysis (e.g. XRF, AAS, NIR, ICP-MS).

Vibrating disc mills usually have a grinder which is arranged in a housing between a material feed (inlet) and a material discharge (outlet). The grinder includes, for example, a pot with a lid and grinding body, which z .B. can be designed as stones, discs, lenses or a ring. Vibratory disc mills can grind the solids based on pressure, impact and / or friction.

Grinding with vibrating disc mills has unfortunately been an inefficient grinding process in many applications. Due to friction losses in particular, there is a risk that individual components of the mill will become very hot. This causes temperature inhomogeneities. Large temperature differences have a negative effect on the grinding result. In particular, individual components of the mill can be adversely braced as a result, in particular in such a way that relative movements are made difficult or the desired oscillation cannot be optimally achieved. Adverse effects like z .B. Inhomogeneous grinding results (high inhomogeneity with regard to the particle sizes in the ground batch) can then often not be avoided. This is particularly disadvantageous when the ground batch is to be used for a material analysis; the latter is then unfortunately also less precise. Last but not least, such tension can also be caused in moving components or in bearings, in particular roller bearings, that the mill only has a shortened service life or even suffers operational failures.

There is therefore interest in optimizing the mill in order to avoid such disadvantages. One of the conceivable measures is cooling to reduce temperature inhomogeneities. In many cases, however, this measure alone cannot bring about a satisfactory optimization. Other measures relate directly to the bearings of the mill.

DE 2 212 601 A1 describes a vibratory disk and ring mill with individually driven eccentric shafts, at least one eccentric shaft being resiliently mounted by the eccentric shaft being connected to the base frame or to the grinding container of the mill by means of spring bodies. For the resilient mounting, a rubber block can be used to accommodate a bearing bush. The respective rubber block is arranged on the side of the base plate.

There is still potential for optimization when optimizing storage.

DESCRIPTION OF THE INVENTION

The object of the invention is to provide a device with the features described above, with which the operation of a vibrating disk mill can be optimized, in particular with regard to the storage of components of the vibrating disk mill, in particular with regard to temperature differences, especially in vibrating disk mills Eccentric shaft drive, especially with regard to tension between the individual components. In a narrower sense, the task can also be seen as optimizing the components of the mill related to the vibration excitation or their operating behavior.

This object is achieved by a device according to the independent patent claim and by a use according to the independent claim. Advantageous exemplary embodiments are listed in the subclaims.

According to the invention, this object is achieved in particular by a vibrating disk mill device for comminuting input material, in particular input material with a particle size of less than 20mm, in particular less than 10mm, in particular designed for grinding the input material to particle sizes of less than 75 .mu.m (pre-grinding), in particular less than 10 .mu.m (final grinding), with: a mill housing ; a grinding system arranged in the mill housing such that it can oscillate, with a grinding chamber and with at least one grinding stone arranged movably in the grinding chamber; at least one in the mill housing eccentric shaft drive mounted on bearings and generating the oscillating movement in the grinding chamber and at least two eccentric shafts, in particular at least two synchronous or synchronously rotating eccentric shafts; a balancing mass unit connected to the eccentric shaft drive, set up to compensate for unbalance;
wherein the grinding chamber is coupled to the eccentric shafts by means of at least one material-elastic link unit. This enables a movement-tolerant or position-tolerant connection of the grinding chamber to the eccentric shafts, whereby the operating behavior of the mill can be optimized.

The invention is based on the knowledge that the mounting of the eccentric shafts can be optimized in a particularly effective manner in that the bearings of the eccentric shafts are elastically coupled to the chamber. It has been shown that by means of one or more linkage units, on the one hand, the centrifugal forces, which are dependent on the speed, can be transferred directly to the eccentric shafts, but on the other hand, the forces and torques caused by thermal expansion and tolerances can also be compensated. The use of one or more material-elastic link units also has the advantage that active control of any stiffness or elasticity parameters is not required. A correspondingly desired damping can already be ensured by means of the material-elastic link unit (s) alone.

A grinding ring is usually also arranged in the grinding chamber. The mill housing defines a system boundary from the environment to a material feed and to a material discharge of the disk vibratory mill.

The material-elastic articulation unit has, for example, a sheet metal plate or is formed thereby, in particular by at least one metallic plate. This also provides the advantage that no complex post-processing operations are necessary for material-elastic sections of the link unit. The following can be mentioned as advantageous materials for the linkage unit: steel, aluminum, composite fiber material.

Steel has the advantage that large forces can be transmitted permanently even at elevated temperatures. In addition, the grinding vessel or grinding chamber can be shrunk into it by means of a steel linkage unit. In addition, steel can also perform a heat conduction function, in particular to lower the temperature in the grinding vessel.

In this context, “material-elastic” is to be understood as a functionality integrated into the material to compensate for tensions or positional tolerances, in particular a functionality without joints without relative movement of parts relative to one another. In particular, a relatively lower rigidity of a first material section in relation to a relatively higher rigidity of a second material section or material region can be defined as “materially elastic”. The “material-elastic” functionality in particular also requires a relative movement, so that a “material-elastic” section also has a movement tolerance.

It has been shown that the rigidity or the “material-elastic” functionality can be adjusted in particular with regard to the following parameters or sizes of the overall system: geometry (in particular diameter); Weights (grinding jar, millstone and grist); Eccentric measure (grinding vessel, grinding stone and grist); Speeds; Temperatures; to be observed
Tolerances. The masses and diameters as well as the maximum speed and the temperature difference of the components have a major influence.

A possible embodiment of the drive concept which is preferred for many applications consists in coupling one of the eccentric shafts to a drive and allowing the other eccentric shafts to rotate freely.

According to one embodiment, the material-elastic link unit is material-elastic by at least one flexurally elastically mounted section between the grinding chamber and the eccentric shafts, in particular flexurally elastic in the radial direction, in particular with a bending moment or a flexural rigidity which, in particular in the radial direction, is at least one power of ten less than the rigidity the coupled power-carrying components (in particular grinding chamber; bearings; eccentric shafts; base plate). This also makes it possible to specifically set which movements are to be tolerated at which point in the arrangement. A section that is supported in a flexurally elastic manner can in particular be understood as a section that is supported by bending in the elastic region of the material used. A flexurally elastic mounting in the sense of the present invention is to be understood in particular as a mounting in which the movement / position tolerance is ensured essentially or even exclusively by bending the coupling element. This mounting differs from a spring mounting by means of tension or compression springs and also differs from a mounting by means of spiral springs, in particular when the material-elastic section provides an integral functionality of the linkage unit, ie is not provided as a separate spring. For example, the material-elastic section is designed as a single strand of material, which is not spiral in the manner of a spring, but which extends between the coupling points or bearing points to be connected to one another, in particular on an at least approximately direct path between two connection points.

Optionally, the material-elastic linkage unit can also be material-elastic in the circumferential direction around the grinding chamber by / due to at least one section that is flexibly mounted between the grinding chamber and the eccentric shafts, in particular with a bending moment or a flexural rigidity which, in particular in the circumferential direction, is at least one power of ten smaller than the rigidity the coupled power-carrying components (in particular grinding chamber; bearings; eccentric shafts; base plate).

In particular, a respective material-elastic section of the material-elastic linkage unit can extend without winding between the coupling points or bearing points to be connected to one another. This also provides good multi-directional storage properties.

The respective material-elastic section can also be described / referred to as a bending rod. The material-elastic sections are preferably of different stiffness in at least two directions of movement, primarily soft or material-elastic in the radial direction. The material-elastic sections are preferably to be arranged vertically / orthogonally to the radial direction, in particular exactly in the circumferential direction.

The electric motor mounted on the base plate can z .B. Drive an eccentric shaft drive via a toothed belt. As a result, an eccentric bearing can be set in rotation, and the grinding tools can be set in oscillation, in particular in horizontal oscillations in at least an approximately horizontal plane. The grinding ring and the grinding stone rotate inside the mill and move relative to each other and against the grinding vessel. The sample material can be crushed by impact, pressure and friction.

The balancing mass unit can be arranged offset with respect to the base plate, in particular offset by 180 °. The balancing mass unit has z .B. a mass in the range of a few kilograms.

Have grinding vessels (grinding chambers) z .B. an inside diameter of 100mm to 300mm. The wall thickness of the grinding vessels is z .B. in the range from 5mm to 20mm. A grinding vessel holder has z .B. External dimensions in the range from 110mm to 350mm. In particular due to manufacturing tolerances and due to thermal expansion during operation, there are dimensional differences between the eccentric shafts and the grinding vessel holder. With a temperature difference of z .B. 70 ° C and a pitch circle diameter of the eccentric shafts of z .B. 300mm results in a deviation of approx. 0.25mm. With such proportions, the length of flexible or material-elastic sections of the link unit (s) is z .B. in the range from 50mm to 500mm. With these sizes / lengths, good / effective damping or position compensation can take place. The centrifugal forces occurring during operation are z .B. a few kilonewtons [kN].

According to one embodiment, the material-elastic articulation unit comprises or provides a grinding chamber receptacle, in particular in a one-piece, integral design, in particular in a central arrangement integrated into the material-elastic articulation unit. According to one embodiment, the material-elastic link unit comprises at least one material-stiff area, in particular for a grinding chamber receptacle, with at least one material-elastic section coupling the material-elastic area to the respective eccentric shaft in a material-elastic manner and in particular in a radial direction movement-tolerant way. This also provides a robust integral arrangement in each case.

According to one embodiment, the material-elastic link unit is designed from a prefabricated semi-finished product, in particular in a completely solid configuration. Last but not least, this also provides robustness and longevity and enables the material-elastic section (s) to be easily adapted to the respective application.

In particular, the material-elastic articulation unit can be coupled to the eccentric shaft together with the balancing mass element (s) in an arrangement above or below a balancing mass element of the balancing mass unit or in an arrangement between at least two balancing mass elements. In this way, the link unit can also be integrated in an expedient manner into an advantageous structural design, in particular in the form of a one-piece disk.

The balancing mass elements can also be stored via the eccentric shafts and move out of phase with the grinding unit. The balancing mass elements are optimally arranged on the level of the grinding vessel (grinding chamber), in particular in order to also be able to compensate for tilting moments. According to an advantageous variant, there are at least two levels each provided with at least one balancing mass element, which are arranged above and below the grinding vessel.

According to one embodiment, the material-elastic articulation unit couples the grinding chamber in at least one coupling point per eccentric shaft with movement tolerance to the respective eccentric shaft, in particular by means of a bearing receptacle for the arrangement of a bearing for the respective eccentric shaft, the at least one coupling point being offset in the circumferential direction with respect to an articulation point or force introduction point is arranged on the grinding chamber, in particular with an offset in the range of a circumferential angle of 30 ° to 120 °, in particular in an at least approximately tangential extent. This also makes it possible to provide advantageous technical bending properties.

According to one embodiment, the material-elastic link unit couples the grinding chamber in at least one coupling point per eccentric shaft by means of a material-elastic section in the form of a material-elastic arm movement-tolerant to the respective eccentric shaft, the material-elastic arm being a one-piece, integral component of the material-elastic link unit, in particular in the form of a preferably massive bending beam-like one Material section. A particularly robust arrangement can hereby also be ensured. The bending beam-like material section preferably has no cavities or cavities.

Thanks to a configuration of the material-elastically coupling articulation unit (s) as sections or components similar to bending bars, the radial rigidity in the corresponding section can be greatly reduced. An exemplary stiffness value is z .B. in the range of approx. 0.1mm to 0.3mm per 1000N radial force on the eccentric shafts. This stiffness value can be defined, for example, as “flexible” or “material-elastic”, in particular with regard to the other force-carrying components.

According to one exemplary embodiment, the material-elastic link unit or at least a respective material-elastic section of the material-elastic link unit is solid, in particular with an exclusively convex cross-sectional profile contour. This can also minimize the risk of material failure. The massive design also provides the advantage that, even with a comparatively stiff material, great flexural softness can be set or achieved in the material-elastic section. The respective material-elastic section preferably does not have any cavities or cavities. The respective material-elastic section preferably has an exclusively convex cross-sectional profile contour.

The cross-sectional profile can taper outward towards the free end.

According to one embodiment, the material-elastic link unit has at least three material-elastic arms (three-armed configuration), which each extend in the circumferential direction around a / the grinding chamber receptacle of the material-elastic link unit, in particular in a symmetrical arrangement around the grinding chamber receptacle, and which are each at its free Have a bearing receptacle at the end, and each of which has a free length from the center of the bearing receptacle to an articulation point (or articulation section or center of an articulation section) on the grinding chamber receptacle corresponding to a circumferential angle of at least 30 ° to 45 °, in particular corresponding a circumferential angle of at least 45 ° to 60 °, in particular a free length in the range of at least 50% to 90% of the diameter of the grinding chamber receptacle, in particular at least 75% to 90% of the diameter of the grinding chamber receptacle. This results in structural and vibration-related advantages, particularly in connection with three or more eccentric shafts.

The material-elastic link unit can z .B. have at least three material-elastic sections which together span a circumferential angle of at least 120 °, 150 ° or 180 ° around the grinding chamber. This favors a storage with regard to bending movements. This also enables great variability in terms of optimizing the linkage unit for a particular application, z .B. regarding the choice of material.

According to one embodiment, the material-elastic link unit couples the grinding chamber in at least one coupling point per eccentric shaft by means of a material-elastic arm to the respective eccentric shaft, the respective material-elastic arm having a length in the range of 50 from a transition to the grinding chamber receptacle to the free end of the arm Has% to 150% of the diameter of the grinding chamber holder, in particular 80% to 120% of the diameter of the grinding chamber holder. This also enables a good length for material elastic movement tolerance, in particular for bending movements.

According to one embodiment, the radial distance between a / the respective bearing Reception of the material-elastic link unit, in particular the radial distance from a / the center point of the bearing seat to the grinding chamber seat, smaller than the diameter of the grinding chamber seat of the material-elastic link unit, in particular less than half the diameter or smaller than the radius of the grinding chamber seat . An arrangement with flexurally elastic, but compression-stiff material-elastic sections can hereby also be favored.

At a transition between a / the grinding chamber receptacle of the material-elastic articulation unit and a / the respective material-elastic arm of the material-elastic articulation unit, at least one compensation hole for tension compensation in the material of the respective arm can be provided. In this way, the material-elastic function, in particular a flexural elasticity, can also be realized with comparatively stiff, robust materials. The position and size of the compensation hole can be adapted to the respective material or application. The compensation hole also enables fine adjustment of the mass distribution.

According to one embodiment, an inner radius is formed on / at a transition between the grinding chamber receptacle and the respective material-elastic arm, in particular an inner radius in the range from 10% to 25% of the cross-sectional width of the arm. According to one embodiment, a / the transition between the grinding chamber receptacle and the respective material-elastic arm is rounded in both circumferential directions or has a rounding. In this way, a robust arrangement with a further optimized stress and force curve can be provided in each case.

According to an exemplary embodiment, the material-elastic link unit has a grinding chamber receptacle for the grinding chamber, which grinding chamber receptacle completely surrounds the grinding chamber in the circumferential direction, the grinding chamber receptacle preferably being designed as a circular cross-section or as a cylindrical receptacle in the manner of a bushing . In this way, a maximum areal force transmission can be achieved with minimal pressure / tension peaks.

According to one embodiment, the material-elastic link unit is designed as a comparatively flat disc, in particular with a uniform thickness (extension in the axial longitudinal direction), in particular with a uniform thickness of both the arms and the grinding chamber receptacle of the material-elastic link unit. This also provides variability in terms of material selection. In this way, the structural design can also be further optimized. For example, the thickness of the linkage unit is comparable to the thickness of balancing mass units or retaining clips. As a result, the link unit can also be well integrated in a constructive and functional manner. By means of a disk-like configuration, the material-elastic mounting can also be adjusted with regard to a desired two-dimensionality. In other words: a bending movement in particular can be forced or aligned bidirectionally in a predefinable plane. The bending moment can be greater about a first axis than about a second axis, in particular by a significant factor which is selected to be so large that the relative movement is forced into the desired plane.

According to one embodiment, the material-elastic link unit is set up to couple the grinding chamber elastically to the eccentric shafts with movement tolerances of less than 1 mm, preferably less than 0.5 or 0.3 or 0.2 mm, in particular with these movement tolerances in the radial direction , especially flexible. Effective force transmission can also be ensured in this way.

The vibratory disk mill device preferably has the eccentric shaft drive as the single drive for all eccentric shafts, the eccentric shaft drive being arranged eccentrically with respect to the grinding chamber. This drive concept has proven to be particularly advantageous in connection with the linkage unit.

ITEM The aforementioned object is also achieved according to the invention by a vibrating disk mill device for comminuting input material, in particular input material with a particle size of less than 20 mm, in particular designed for grinding the input material to particle sizes of less than 75 μm, in particular less than 10 μm, with: a mill housing; a grinding system arranged in the mill housing such that it can oscillate, with a grinding chamber and with at least one grinding stone arranged movably in the grinding chamber; at least one eccentric shaft drive mounted in the mill housing and generating the oscillating movement in the grinding chamber and at least two eccentric shafts, in particular at least two synchronously rotating eccentric shafts; a balancing mass unit connected to the eccentric shaft drive, set up to compensate for unbalance; wherein the grinding chamber is coupled to the eccentric shafts by means of at least one material-elastic link unit, wherein the material-elastic link unit comprises or provides a grinding chamber receptacle, in particular in a one-piece integral design, in particular in a central arrangement integrated into the material-elastic link unit, the material-elastic link unit in the grinding chamber at least one coupling point per eccentric shaft coupled with movement tolerance to the respective eccentric shaft, in particular by means of a bearing mount for Arrangement of a bearing for the respective eccentric shaft, the at least one coupling point being arranged with an offset in the circumferential direction in relation to an articulation point or force introduction point on the grinding chamber. This results in numerous advantages mentioned above. In particular, the offset is in the range of a circumferential angle of 30 ° to 120 °; however, the offset is optionally also smaller, z .B. depending on the number and / or length and / or geometry of material-elastic sections used.

The above-mentioned object is also achieved according to the invention by a material-elastic link unit designed for material-elastic coupling of a grinding chamber to at least one eccentric shaft in a vibratory disk mill device described above, the material-elastic link unit being produced by removing a bearing receptacle for the eccentric shaft and by removing a grinding chamber receptacle , wherein at least one material-elastic, cross-sectional area-reduced section is formed between the receptacles, in particular in a one-piece solid plate which forms a one-piece, integral material-elastic link unit. This provides the aforementioned advantages.

The grinding chamber holder can z .B. can be separated from a plate forming the linkage unit, in particular by plasma cutting. Any reworking can be limited in particular to reworking holes and transition radii.

The above-mentioned object is also achieved according to the invention by using at least one material-elastic link unit in a vibrating disc mill for material-elastic mounting of a plurality of eccentric shafts during the comminution of input material, the eccentric shafts being elastically coupled to a grinding chamber of the vibrating disc mill by means of the material-elastic link unit, in particular when comminuting input material with a particle size of less than 20 mm, in particular when grinding the input material to particle sizes of less than 75 μm, in particular less than 10 μm, in particular in a vibratory disk mill device described above. This provides the aforementioned advantages.

In the following, an aspect is specifically dealt with which relates to a phase offset and the generation or setting / regulating the type and manner of the vibrations, a combination with the features described above being able to provide a particularly far-reaching vibration-optimized mill. In other words: a particularly far-reaching vibration-optimized mill can be achieved with a combination of the material-elastic link unit and the measures also described here with regard to phase offset. The optimization of the mill based on measures for materially elastic mounting of the chamber can be implemented in a particularly expedient manner by means of the measures described here with regard to phase offset.

In the case of the vibrating disc mill device described above, the balancing mass unit can be coupled to the eccentric shaft drive in such a way that a phase offset greater than 180 °, in particular greater than 185 °, can be set between the maximum eccentric of the balancing mass unit and the maximum eccentric of the grinding chamber. In this way, an operating behavior which is advantageous for many operating situations can be ensured. In particular, smooth running of the mill can be ensured even with greatly varying loads. Last but not least, the spectrum of types of operation or use for a particular type of mill can be expanded.

It has been shown that it is advantageous if the offset is not exactly 180 °. By setting an offset deviating from 180 °, the vibrational interplay of grinding stone and chamber, chamber and balancing masses, and / or input material (varying mass) and generally the vibrating device components of the mill can be optimized.

The balancing mass unit can be coupled to the eccentric shaft drive in such a way that the desired phase offset can be set as a function of the activation of the eccentric shaft drive.

In particular, with an offset greater than 180 °, the countermass system can lag behind the rotary movement of the grinding system, for example by at least 5 °. This offset can be specified and regulated according to the invention. In this way, in particular with varying loads and with regard to variations in the movement behavior of the millstone, an optimization of vibration technology can be ensured, in particular in the sense of a buffer function. In other words: it has been shown that the angular offset according to the invention greater than 180 ° can ensure a certain buffer function to avoid disadvantageous oscillation states in the event of a lagging imbalance of the balancing mass unit. Last but not least, this also enables a particularly wide range of applications for the respective mill.

In contrast to this, a previous measure consisted in realizing a balancing by means of an exactly 180 ° offset, the offset in relation to the maximum eccentric of the balancing weights and the eccentric maximum of the grinding chamber is dimensioned. However, it has now been shown that this balancing strategy only enables an inadequate, unsatisfactory optimization.

Mills with unbalance drives used up to now usually have a vibration behavior that is characterized by a spring-damper system. It has now been shown that matching the position of the millstone is comparatively difficult or indefinable.

The invention can therefore optionally also include the concept of setting the offset between the eccentric maximum of the balancing masses and the eccentric maximum of the grinding chamber not equal to 180 °, with a preferably lagging grinding stone being / is vibrated in such a way that, in particular, even with varying loads and / or varying relative positions of the vibrating components, in particular of the millstone, a steady, quiet run possible or a constant vibration excitation is ensured, in particular under varying loads or speeds.

In particular, this also enables changes in the operating state to be compensated for between idling and full load in a particularly simple and effective manner. This allows a single type of mill to be used in a flexible manner. The practicality is improved.

Only a single eccentric maximum is preferably provided per revolution, which is predetermined by the offset of individual diameters on the eccentric shafts. Optionally, several eccentric maxima could be realized, for example, by means of a cam control, but in many situations the comparatively easy to implement concept of vibration optimization with a predefined relative arrangement of the eccentric maximum is preferable, i.e. without cam control. Nevertheless, the technical measures can be expanded to include such a cam control in individual cases, if desired.

In this context, “lagging” is to be understood as an induced movement, in particular the free movement of the millstone induced by imbalances.

The balancing mass unit comprises, for example, two balancing mass elements, in particular in the form of two rings, in an arrangement above and below the grinding chamber. It has been shown that the use of at least two balancing mass elements is more advantageous than just one balancing mass element, in particular with regard to different heights or to additional (to be avoided) tilting moments.

The respective balancing mass element does not necessarily have to be connected to all eccentric shafts; rather, at least one individual balancing mass element can also be arranged on each shaft. However, a balancing mass element coupled to all shafts provides the advantage that the space between the shafts can also be used for a counter mass.

• - Verhältnis Mahlsteingröße zu Mahlkammergröße; und/oder
• - Verhältnis Exzenter Mahlaggregat (antreibende Komponente) zu Mahlkammergröße.

It has been shown that in order to further optimize operating behavior, in particular to optimize the start-up behavior of the mill, at least one dependency or at least one ratio from the following group must be predefined:

• - Ratio of millstone size to grinding chamber size; and or
• - Ratio of the eccentric grinding unit (driving component) to the size of the grinding chamber.

The setting of the phase offset can in particular also be achieved by mechanical coupling such as z .B. by means of feather keys, in particular on the respective eccentric shaft.

A coupling of the balancing mass unit to the eccentric shaft drive can also be understood as a coupling of the balancing mass unit to at least one eccentric shaft. In particular, all eccentric shafts have exactly the same phase offset.

According to an exemplary embodiment, the phase offset can be set in such a way that the maximum eccentric of the balancing mass unit lags or is chronologically behind the maximum eccentric of the grinding chamber. Such a negative offset of the balancing mass unit by more than half a revolution allows varying operating conditions to be compensated particularly effectively.

According to one exemplary embodiment, the balancing mass unit is activated / controllable as a function of the activation of the eccentric shaft drive in such a way that a phase offset in the range from 185 ° to 200 ° can be set. It has been shown that this offset is particularly advantageous, in particular also with regard to counter-rotating unbalance compensation.

An offset, in particular a lag, by an angle of rotation of 185 ° to 200 ° can in particular provide the advantage that the relative displacements of relative positions or centers of mass to be expected with good probability or compensated if the effectiveness is particularly good. It has been shown that a distance of 5 ° to 20 ° of half a revolution can ensure compensation, in particular with a good safety factor, without having to deviate too much from the concept of counter-oscillating masses. In other words: In this area of deviation from exactly the opposite vibration, a more tolerant, broadly compensating vibration behavior can be ensured for a more variable operating range of the mill.

According to one embodiment, the control takes place in such a way that the regulated relative angle of rotation or phase offset of the compensating mass unit compensates for different relative positions of the at least one millstone relative to the maximum eccentric in part load and full load operation, in particular for the purpose of compensating for changes in the operating state between idle and full load. In this way, the range of applications can also be broadened, in particular with regard to the type and quantity of the input material.

With a higher load (e.g. with a relatively high grinding resistance) the phase offset between the eccentric maximum and the current position of the grinding stone is relatively greater.

According to one embodiment, the angle of rotation or phase offset of the compensating mass unit is adjustable, in particular by providing at least one eccentric disk on at least one eccentric shaft, in particular an eccentric disk that can be positioned in the relative rotational position to the eccentric shaft. In this way, a large variability can also be provided by means of comparatively simple structural measures. The same types of measures are preferably taken on all eccentric shafts; in particular, at least one eccentric disk is provided on each eccentric shaft.

The adjustability of the balancing mass unit can be ensured, for example, by mechanical connections by means of which a predefined offset can be set. In particular, a passport means such as z .B. A feather key facilitates the adjustability that is useful in the present context. For example, the adjustability can also be ensured by a toothed shaft, a conical clamp and / or a locking bolt.

Rotation of the eccentric disks relative to the shaft can also take place during operation, in particular in the sense of a fine adjustment.

According to one embodiment, the angle of rotation or phase offset of the balancing mass unit can be regulated as a function of vibrations of the vibrating disk mill device, in particular by detecting accelerations in at least one spatial direction. This can z .B. actively respond to current operating situations.

In particular, the vibrations can be detected by means of a plurality of multi-axis acceleration sensors. For example, at least one threshold value is defined, in particular in relation to at least one of a plurality of horizontal spatial axes, above which threshold value a phase offset control takes place. For example, cam control can be implemented. Optionally can also z .B. a multiple-ring eccentric bearing, in particular a five-ring eccentric bearing, can be implemented. The latter can simplify readjustment during operation.

For example, an acceleration sensor on the base plate can record the vibration speeds, in particular in the horizontal direction. For example, at least one multi-axis acceleration sensor is provided, in particular set up for integrated measurement / detection of horizontal vibration speeds.

According to one exemplary embodiment, the at least one grinding stone has a diameter of at least 50% of the inner diameter of the grinding chamber, in particular in the range from 60% to 85%. In this way, in particular, a start-up process can also be optimized (safe machine start-up). A relatively large millstone relative to the dimensions of the chamber also provides the advantage that a phase control can be set in a particularly effective manner. Such effects are particularly noticeable at a ratio greater than 60%. It has been shown that a ratio greater than 85% can have a disadvantageous effect, in particular with regard to the usable free volume.

The size dimensions of the grinding chamber can in particular be described by those surfaces or walls on which the grinding stone rolls.

The grinding stone rolls off the inside of the grinding chamber. With a diameter of the grinding stone of at least 50% of the inner diameter of the grinding chamber, the mill can run particularly smoothly and safely.

By means of optimization measures based on the definition of size relationships, a safe start-up of the machine can in particular also be ensured. The millstone can be turned into a Desired rolling motion can be stimulated and kept in a smooth, stable run.

According to one embodiment, the maximum eccentric of the grinding chamber is at least 2% of the inner diameter of the grinding chamber, in particular in the range from 4% to 8%. In this way, in particular, a start-up process can also be optimized (safe machine start-up). A relatively strong eccentric shaft (comparatively large eccentricity) relative to the dimensions of the chamber also provides the advantage of a clear, unambiguous phase regardless of the current configuration or loading of the chamber. With a ratio greater than 4%, the advantages are even more noticeable. It has been shown that a ratio greater than 8% can have a disadvantageous effect, in particular with regard to reaction forces or inertia or variability of the operating conditions.

It has been shown that by specifying a minimum dimension for the eccentricity when the grinding chamber is excited, the mode of operation of the grinding stone can be positively influenced. In particular, eccentric disks for the grinding chamber have an eccentricity (or an eccentric maximum) of at least 2% of the inner diameter of the grinding chamber. The term eccentric maximum can thus be understood synonymously with the geometric eccentricity of a geometric measure on the shafts. By means of this minimum dimension, in particular the impact (or impulse) exerted by the grinding chamber on the grinding stone can be set sufficiently large, in particular also with regard to a safe, advantageous start-up of the mill.

The grinding chamber and the balancing masses have, in particular, eccentrically offset attachment points on the eccentric shafts. The eccentrics can have a different phase offset and a different eccentricity on the shafts.

According to one embodiment, the eccentric maximum of the balancing mass unit is greater than the eccentric maximum of the grinding chamber, in particular at least by a factor of 1.2 to 3 Requirements e.g. can affect the dimensioning of the bearings.

It has been shown that the balancing masses can be reduced by such a size factor of the two eccentricities. A factor of up to 3 provides a good compromise, also in terms of design effort.

The ratios of the maxima can in particular be described on the basis of relative geometric dimensions of eccentric elements (e.g. discs).

According to one embodiment, the at least one grinding stone has a diameter which is predefined by the inner diameter of the grinding chamber minus a factor of 5 to 7 of the maximum eccentric of the grinding chamber. This makes it possible to achieve a particularly advantageous compromise for the operating behavior, in particular by means of purely device-related measures. It has been shown that in this way particularly advantageous running smoothness can be ensured, in particular, largely independently of the load on the mill (amount and type of feedstock). Optionally, these conditions can be deviated from, z .B. for certain types of mills or for certain loads.

The size of the eccentric (or the extent of the eccentricity) when the grinding chamber is excited can define the impact or impulse exerted on the grinding stone. Because a large grinding stone has to travel a comparatively short distance to the opposite wall of the grinding chamber, based on the conditions described here, a positive effect for a safe start-up of the mill can also be ensured. However, a comparatively maximally large millstone has only a little free volume (little freedom of movement) available, so that a rolling movement is restricted. It has been shown that in this area of tension, the range from 5 to 7 for the factor described above can ensure a good compromise for reliable start-up and optimal grinding operation. In other words: With this special variant of the size ratios, an advantageous setting can be ensured both for start-up and for continuous operation. The eccentric maximum can thereby z .B. be predetermined in a geometrical manner by the diameter of an eccentric element (in particular a disk).

In the context described above, a method for setting a phase offset or for operating the mill with a predefinable phase offset can also be used, in particular a method for the vibration control of a vibrating disc mill device when comminuting input material, in particular input material with a particle size of less than 20mm or less than 10mm, in particular for a vibratory disk mill device described above, the oscillating movement of the vibratory disk mill device by means of an eccentric shaft drive comprising at least two eccentric shafts in one An oscillating grinding system is produced with a grinding chamber and with at least one grinding stone arranged oscillating in the grinding chamber, an imbalance compensation taking place by means of at least one balancing mass unit coupled to the eccentric shaft drive; The vibrational regulation of the vibratory movement takes place by regulating a phase offset between one / the eccentric maximum of the balancing mass unit and one / the eccentric maximum of the grinding chamber, the phase offset being set to an amount greater than 180 °, in particular greater than 185 °. This results in the aforementioned advantages.

According to one embodiment, the phase offset is set in such a way that the eccentric maximum of the balancing mass unit lags or is chronologically behind the eccentric maximum of the grinding chamber. This operating mode has proven to be particularly advantageous, particularly with regard to greatly varying loads on the mill ( z .B. wide range of type and amount of input material).

The balancing mass unit can be coupled to the eccentric shaft drive in such a way that a phase offset in the range of 185 ° to 200 ° is set, i.e. in a range of at least 5 ° to a maximum of 20 ° deviation from exactly opposite excitation. In this way, a particularly variable operating behavior can be achieved (here figuratively referred to as vibration-related system elasticity). A phase offset regulation can take place in particular as a function of the control of the eccentric shaft drive and / or of the relative arrangement of eccentrics.

It has been shown that the effects according to the invention become less advantageous from a rotational offset of more than 200 °. The main mass of the oscillating system is provided by the grinding vessel with its holder. The millstone can assume a rotation angle offset of a maximum of approx. 90 °.

According to one embodiment, the angle of rotation or phase offset of the balancing mass unit is predefined or actively regulated in such a way that different relative positions of the at least one millstone in partial and full load operation are compensated relative to the maximum eccentric, in particular relative to the maximum eccentric of the grinding chamber, in particular for the purpose of compensating for changes in the operating state between idle and Full load. As a result, smooth running can also be ensured largely independently of the operating state specified by the drive.

According to one embodiment, the balancing mass unit is set in the angle of rotation or phase offset, in particular by positioning or actively positioning at least one eccentric disk on at least one eccentric shaft in the rotational position relative to the eccentric shaft (adjustment of the relative position for vibration optimization). As a result, the operating behavior can also be predefined in a robust manner by means of simple measures.

According to one embodiment, the angle of rotation or phase offset of the balancing mass unit is regulated as a function of vibrations of the vibrating disk mill device, in particular by recording acceleration parameters in at least one spatial direction and evaluating them for the vibration regulation. This also enables active counter-regulation in response to current operating situations.

Figure list

• 1 eine Scheibenschwingmühlenvorrichtung in einer perspektivischen Gesamtansicht;
• 2 eine Ansicht auf eine Unterseite eines Mahlsystems einer Scheibenschwingm üh lenvorrichtung;
• 3A, 3B, 3C jeweils in einer perspektivischen Ansicht eine materialelastische Kopplung zwischen Exzenterwellen und Mahlkammer einer Scheibenschwingmühlenvorrichtung gemäß einem Ausführungsbeispiel;
• 4A, 4B in einer Draufsicht und in einer perspektivischen Seitenansicht eine materialelastische Anlenkereinheit mit materialelastischen Abschnitten/Armen gemäß einem Ausführungsbeispiel;
• 5 eine Scheibenschwingmühle gemäß dem Stand der Technik;
• 6A, 6B, 6C jeweils in schematischer Darstellung Kraftvektoren in einem Kräftediagramm bei unterschiedlichem Versatz, je nach Betriebszustand der Scheibenschwingmühlenvorrichtung;
• 7A, 7B, 7C, 7D in unterschiedlichen Ansichten jeweils eine Exzenterwelle zur Verwendung in einer Scheibenschwingmühlenvorrichtung gemäß einem Ausführungsbeispiel;
• 8 in einer perspektivischen Ansicht eine Scheibenschwingmühlenvorrichtung gemäß einem Ausführungsbeispiel.

Further features and advantages of the invention emerge from the description of at least one exemplary embodiment on the basis of drawings and from the drawings themselves

• 1 a vibrating disk mill device in a perspective overall view;
• 2 a view of an underside of a grinding system of a Scheibenschwingm üh lenvorrichtung;
• 3A , 3B , 3C each in a perspective view of a material-elastic coupling between the eccentric shafts and the grinding chamber of a vibrating disk mill device according to an embodiment;
• 4A , 4B in a plan view and in a perspective side view a material-elastic link unit with material-elastic sections / arms according to an embodiment;
• 5 a vibratory disk mill according to the prior art;
• 6A , 6B , 6C each in a schematic representation of force vectors in a force diagram with a different offset, depending on the operating state of the vibrating disk mill device;
• 7A , 7B , 7C , 7D in different views, each an eccentric shaft for use in a vibrating disk mill device according to an embodiment;
• 8th in a perspective view a vibrating disk mill device according to an embodiment.

DETAILED DESCRIPTION OF THE FIGURES

In the case of reference symbols that are not explicitly described with reference to an individual figure, reference is made to the other figures.

The figures are first described together. A specific description is then provided for each figure.

A vibratory disk mill device 10 includes a mill housing 11 , in which a grinding system 13 is arranged, which has a material task 12 Feed material can be supplied. The feed material is ground and can then be fed to a material discharge 19th can be removed. The grinding system arranged in between 13 includes a grinding chamber 13.1 with at least one grinding stone, the grinding chamber 13.1 by means of at least one on several domes 13.4 attached retaining clip 13.3 in a position relative to a base plate 13.5 is held. An eccentric shaft drive 14th is on a plurality of eccentric shafts 15th coupled and drives at least one of the eccentric shafts 15th at. A balancing mass unit 16 with a plurality of balancing mass elements 16.1 serves to balance the masses.

A material-elastic link unit 17th is particularly in an arrangement under the retaining clip 13.3 and between at least two balancing mass elements 16.1 arranged and material-elastic on the eccentric shafts 15th coupled. The link unit 17th couples / couples the grinding chamber 13.1 material-elastic, in particular flexurally elastic, to the shafts 15th . To this end, the link unit 17th a grinding chamber holder 17.1 on, especially in an at least approximately centric arrangement. The material-elastic coupling can be carried out to a large extent or also essentially over a plurality of material-elastic sections 17.3 be ensured, here in particular in a configuration as a free arm, which also extends in the circumferential direction.

The respective material elastic section 17.3 has in one of the possible configurations in particular: a transition 17.2 between the grinding chamber holder 17.1 and the free portion of the arm, a balance hole 17.4 (in particular to compensate for masses or stresses in relative movements), an inner radius 17.5 and a rounding 17.6 , in particular each optimized with regard to minimizing voltage peaks at the transition 17.2 , at least one camp recording 17.7 with a ring section 17.71 in an arrangement at the free end of the respective arm, a coupling point 17.8 to the wave 15th , and an articulation point or articulation area (or geometric center) of an articulation section 17.9 at the respective transition 17.2 . In the respective warehouse mount 17.7 can a / the warehouse 18th for the corresponding eccentric shaft 15th be framed, for example by form and / or force fit. The area that the grinding chamber receptacle 17.1 defined, in particular an annular area 11/17 around it can be made material-rigid, for example also by material post-treatment or material differentiation.

Geometric information is explained below. D17.1 diameter of the grinding chamber holder; d17 free length of the material elastic section 17.3 , especially in the circumferential direction u ; r radial direction; r1 free radial spacing of the bearing seat, in particular with respect to the grinding chamber seat; z Vertical direction or longitudinal direction (axial direction); z17 Thickness of the link unit; α Circumferential angle or offset in the circumferential direction between the articulation point 17.9 and stock recording 17.7 .

The 1 shows a vibratory disk mill device 10 with a grinding system driven by eccentric shafts 13 .

The 2 shows one on a baseplate 13.5 mounted grinding system 13 with three eccentric shafts 15th , one of which is an eccentric shaft 15th by a drive 14th is driven.

The 3A , 3B , 3C show the arrangement of a material-elastic link unit 17th integrated between two balancing mass units 16 , 16.1 and a clip 13.3 . Both the linkage unit 17th as well as the balancing mass units 16 and the clip 13.3 are on the eccentric shafts 15th coupled. The three coupling material-elastic sections 17.3 each extend in the circumferential direction u over an angle α in the range from 60 to 100 °, in particular approx. 85 °.

The 4A , 4B show the individual sections of an integral, massive one-piece material-elastic link unit 17th with arms that are flexible in the radial direction 17.3 . A grinding chamber holder is in the center 17.1 due to a comparatively rigid area 11/17 Are defined. The transitions between this materially rigid area 11/17 (or the articulation section 17.9 ) and the respective arms 17.3 are all rounded (especially areas 17.2 , 17.5 , 17.6 ). Further measures optimizing mass distribution or stress distribution or force flow can be implemented, for example, through the compensation hole shown 17.4 be ensured in the respective arm. The respective camp recording 17.7 is by an integral one-piece solid ring section 17.71 provided, the center of which is the coupling point 17.8 (Center of the eccentric shaft).

4B illustrates the comparatively small thickness z17 the link unit (disc-like design).

5 shows a vibrating disc mill 1 without link unit (state of the art). The grinding system is connected to the eccentric shafts without material-elastic coupling.

In the following figures, an aspect is specifically dealt with which relates to a phase offset and the generation or setting / regulation of the type and manner of the vibrations, a combination with the features described above being able to provide a particularly far-reaching vibration-optimized mill.

The 6A , 6B , 6C illustrate different operating states, each depending on a phase offset ω , whereby a resulting force vector of a resulting imbalance is set individually in each case.

In 6A a vibration state that needs to be optimized is illustrated. The angle of rotation or phase offset ω13 of the grinding stone depends on the grinding conditions, in particular on the load. An operating state with a comparatively large residual imbalance is shown.
A force vector F1 the imbalance force of the grinding chamber points in a different direction than a force vector F2 the imbalance force of the millstone. A force vector F3 the imbalance force of the balancing mass unit assigns opposite F1 (Phase offset exactly 180 °).
The angle of rotation or phase offset ω13 the millstone is between F1 and F2 applied.
Effect: A comparatively large / long force vector Fn for the residual unbalance.

In 6B a vibrational state that has been optimized in terms of vibration technology through phase offset optimization is illustrated. F3 assigns opposite at an angle other than 180 ° F1 (Phase shift, for example approx. 195 ° or 200 °; 6B is not exactly to scale).
The angle of rotation or phase offset ω16 the balancing mass unit is between here for the sake of simplicity F1 and F3 plotted.
Effect: A residual imbalance becomes zero or can be leveled according to the invention, in particular by changing the phase offset ω16 is / will be set accordingly.

In 6C illustrates another operating state in which a (comparatively small) residual imbalance still exists Fn is not leveled or is deliberately not readjusted, especially because of the phase offset of the millstone ω13 varies comparatively strongly. However, the phase shift is ω16 the balancing mass unit is selected according to the invention in such a way (here for the purpose of illustration corresponding to that phase offset in 6B) that the resulting residual imbalance oscillates around the value zero. Such a mean value can be determined, for example, as an empirical value from normal operation of the mill over a predefined operating period, in particular for the purpose of specifying a single, predefined advantageous phase offset ω16 the balancing mass unit. This can also save time-consuming readjustment.
Effect: Depending on the size of the offset, the comparatively small / short force vector is Fn Aligned in a first or in a second opposite direction and ideally oscillates around a mean value zero with only a small deflection.

The 7A , 7B , 7C , 7D show an eccentric shaft 15th in different views and configurations. In 7A it can be seen that individual cams each have a disc 15.1 include, which can be arranged with a predefinable offset or angle of rotation relative to the further cams or disks. The individual cams or discs can be connected, for example, by means of connecting means 15.2 Position (e.g. screw connections or fitting means) relative to one another.

The example of 7th shows a shaft with three cams. In particular, one of the cams interacts with the grinding chamber, and the other two cams are each coupled to one of two balancing mass units. It has been shown that a particularly advantageous operating behavior can be achieved if the middle cam couples the grinding chamber.

In 7B the relative position of the individual cams or disks is further clarified. In particular, serial assembly of individual machine elements can be provided, in particular in such a way that the disks can optionally be retrofitted.

In 7C and 7D phase offsets of different sizes are illustrated. 7C illustrates an offset of 180 ° (identified as disadvantageous according to the invention). 7D illustrates an example of an offset of ± 20 ° (identified as advantageous according to the invention) with respect to the exactly opposite, opposite arrangement according to FIG 7C (180 °), corresponding to 200 °. Such an offset can therefore be implemented relatively between the cam for the chamber and the respective cam for the balancing mass unit (s), either permanently predefined or also adjustable during operation or during breaks or when the mill is reconfigured (optional readjustment).

8th shows a vibratory disk mill device 10 with control / regulation device 20th and with at least one measuring unit 21st , in particular comprising at least one acceleration sensor.

List of reference symbols

1

Vibrating disc mill

10

Vibrating disc mill device

11

Mill housing

12

Material feed

13th

Grinding system

13.1

Grinding chamber

13.3

Retaining clip

13.4

Dome or spacer element

13.5

Base plate

14th

Eccentric shaft drive

15th

Eccentric shaft

15.1

Eccentric shaft disk or eccentric disk

16

Balancing mass unit

16.1

Balancing mass element

17th

material-elastic link unit

17.1

Grinding chamber mount

11/17

material stiff area

17.2

Transition to the grinding chamber holder

17.3

material elastic section, especially free arm

17.4

Compensation hole

17.5

Inner radius

17.6

Rounding off

17.7

Camp recording

17.71

Ring section

17.8

Coupling point

17.9

Articulation point or articulation section or center of an articulation section

18th

Bearings for eccentric shaft

19th

Material discharge

20th

Control / regulating device

21st

Measuring unit, in particular an acceleration sensor

F1

Force vector imbalance force grinding chamber (or grinding system without grinding stone and without balancing mass unit)

F2

Force vector imbalance force millstone

F3

Force vector imbalance force balancing mass unit

Fn

Force vector residual unbalance

D17.1

Diameter of the grinding chamber holder

d17

free length

r

radial direction

r1

radial distance of the bearing seat

u

Circumferential direction

z

Vertical direction or longitudinal direction (axial direction)

z17

Thickness of the link unit

α

Circumferential angle or offset in the circumferential direction

ω

Angle of rotation or phase offset (small omega)

ω13

Angle of rotation or phase offset of the millstone

ω16

Angle of rotation or phase offset compensation mass unit

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• DE 2212601 A1 [0006]

Claims (16)

Vibrating disc mill device (10) for comminuting feedstock, in particular feedstock with a particle size of less than 20mm or less than 10mm, in particular set up for grinding the feedstock to particle sizes of less than 75 µm, with: a mill housing (11); - a grinding system (13) arranged in the mill housing such that it can vibrate, with a grinding chamber (13.1) and with at least one grinding stone arranged movably in the grinding chamber; -at least one eccentric shaft drive (14) mounted in the mill housing and generating the oscillating movement in the grinding chamber and at least two eccentric shafts (15), in particular at least two synchronously rotating eccentric shafts; -a balancing mass unit (16) connected to the eccentric shaft drive, set up to compensate for unbalance; characterized in that the grinding chamber (13.1) is coupled to the eccentric shafts (15) by means of at least one material-elastic link unit (17). Vibrating disc mill device according to Claim 1 , the material-elastic link unit being material-elastic by at least one section (17.3) that is flexibly mounted between the grinding chamber and the eccentric shafts, in particular flexurally elastic in the radial direction, in particular with a bending moment or a flexural rigidity which, in particular in the radial direction (r), is at least one power of ten is smaller than the rigidity of the coupled force-carrying components. Vibratory disk mill device according to one of the preceding claims, wherein the material-elastic link unit (17) comprises or provides a grinding chamber receptacle (17.1), in particular in a one-piece, integral design, in particular in a central arrangement integrated into the material-elastic link unit; and / or wherein the material-elastic link unit is configured from a prefabricated semi-finished product, in particular in a completely solid configuration. Vibratory disk mill device according to one of the preceding claims, wherein the material-elastic link unit (17) couples the grinding chamber (13.1) in at least one coupling point (17.8) for each eccentric shaft with movement tolerance to the respective eccentric shaft, in particular by means of a bearing receptacle for the arrangement of a bearing for the respective eccentric shaft, wherein the at least one coupling point is arranged with an offset (α) in the circumferential direction in relation to a point of articulation or force application point on the grinding chamber, in particular with an offset in the range of a circumferential angle of 30 ° to 120 °, in particular in at least an approximately tangential extent. Vibratory disk mill device according to one of the preceding claims, wherein the material-elastic link unit couples the grinding chamber in at least one coupling point per eccentric shaft by means of a material-elastic section in the form of a free arm (17.3) in a movement-tolerant manner to the respective eccentric shaft, the material-elastic arm being an integral part of the material-elastic link unit , in particular in the form of a bending beam-like material section. Vibratory disk mill device according to one of the preceding claims, wherein the material-elastic link unit or at least a respective material-elastic section of the material-elastic link unit is of solid design. Vibratory disk mill device according to one of the preceding claims, wherein the material-elastic link unit has at least three material-elastic sections each in the form of a free arm (17.3) which each extend in the circumferential direction around a / the grinding chamber receptacle of the material-elastic link unit, in particular in a symmetrical arrangement around the grinding chamber -Recording, and which each have a bearing seat (17.7) at its free end, and which each have a free length (d17) from the center of the bearing seat to a point of articulation on the grinding chamber seat corresponding to a circumferential angle of at least 30 ° to 45 °, in particular corresponding to a circumferential angle of at least 45 ° to 60 °, in particular a free length in the range of at least 50% to 90% of the diameter of the grinding chamber receptacle, in particular at least 75% to 90% of the diameter of the grinding chamber receptacle ; and / or wherein the material-elastic link unit couples the grinding chamber in at least one coupling point per eccentric shaft by means of a / the material-elastic section in each case designed as a free arm to the respective eccentric shaft, the respective material-elastic arm from a transition to the grinding chamber receptacle to the free end of the Arms has a length in the range from 50% to 150% of the diameter of the grinding chamber holder, in particular 80% to 120% of the diameter of the grinding chamber holder. Vibrating disk mill device according to one of the preceding claims, in particular according to Claim 9 , wherein the radial distance from a respective bearing seat of the material-elastic linkage unit, in particular the radial distance (r1) from a center point of the bearing seat to the grinding chamber seat, is smaller than the The diameter of the grinding chamber receptacle of the material-elastic link unit is, in particular, smaller than half the diameter of the grinding chamber receptacle. Vibratory disk mill device according to one of the preceding claims, wherein the material-elastic link unit has a / the grinding chamber receptacle (17.1) for the grinding chamber, which completely surrounds the grinding chamber in the circumferential direction, the grinding chamber receptacle preferably as a circular cross-section or as a cylindrical receptacle of the type a socket is designed. Vibratory disk mill device according to one of the preceding claims, wherein the material-elastic link unit is designed as a flat disc, in particular with a uniform thickness, in particular with a uniform thickness of both material-elastic sections / arms and of a / the grinding chamber receptacle of the material-elastic link unit. Vibratory disk mill device according to one of the preceding claims, wherein the material-elastic link unit is set up to couple the grinding chamber with movement tolerances of less than 1 mm, preferably less than 0.5 or 0.3 or 0.2 mm, to the eccentric shafts, in particular with them Movement tolerances in each case in the radial direction. Vibrating disk mill device (10) for comminuting input material, in particular input material with a particle size of less than 20 mm, in particular designed for grinding the input material to particle sizes of less than 75 μm, with: a mill housing (11); - a grinding system (13) arranged in the mill housing such that it can vibrate, with a grinding chamber (13.1) and with at least one grinding stone arranged movably in the grinding chamber; -at least one eccentric shaft drive (14) mounted in the mill housing and generating the oscillating movement in the grinding chamber and at least two eccentric shafts (15); -a balancing mass unit (16) connected to the eccentric shaft drive, set up to compensate for unbalance; characterized in that the grinding chamber (13.1) is coupled to the eccentric shafts (15) by means of at least one material-elastic link unit (17), the material-elastic link unit (17) comprising or providing a grinding chamber receptacle (17.1), in particular in a one-piece, integral design , in particular in a central arrangement integrated into the material-elastic link unit, the material-elastic link unit (17) coupling the grinding chamber (13.1) in at least one coupling point (17.8) per eccentric shaft with movement tolerance to the respective eccentric shaft, in particular by means of a bearing mount for the arrangement of a bearing for the respective eccentric shaft, the at least one coupling point being arranged with an offset (α) in the circumferential direction in relation to a pivot point or force introduction point (17.9) on the grinding chamber. Material-elastic link unit set up for material-elastic coupling of a grinding chamber to at least one eccentric shaft in a vibrating disc mill device according to one of the preceding claims, wherein the material-elastic link unit is produced by removing a bearing receptacle for the eccentric shaft and by removing a grinding chamber receptacle, with at least between the receptacles a material-elastic cross-sectional area reduced section is formed, in particular in a one-piece solid plate which forms a / the one-piece integral material-elastic linkage unit. Vibrating disc mill device (10) according to one of the Claims 1 to 12 , the balancing mass unit being coupled to the eccentric shaft drive in such a way that a phase offset greater than 180 °, in particular greater than 185 °, can be set between one / the eccentric maximum of the balancing mass unit and one / the eccentric maximum of the grinding chamber. Vibrating disc mill device according to the preceding device claim, the phase offset being adjustable such that the maximum eccentric of the balancing mass unit (16) lags the maximum of the eccentric of the grinding chamber (13.1); and / or wherein the balancing mass unit (16) can be controlled as a function of the control of the eccentric shaft drive (14) in such a way that a phase offset in the range from 185 ° to 200 ° can be set; and / or wherein the control takes place in such a way that the regulated phase offset of the compensating mass unit (16) compensates for different relative positions of the at least one millstone relative to the maximum eccentric in partial load and full load operation, in particular for the purpose of compensating for changes in operating conditions between idle and full load; and / or wherein the phase offset of the balancing mass unit (16) is adjustable, in particular by providing at least one eccentric disk (15.1) on at least one eccentric shaft (15), in particular an eccentric disk that can be positioned in the relative rotational position to the eccentric shaft; and / or wherein the maximum eccentric of the grinding chamber (13.1) is at least 2% of the inner diameter of the grinding chamber, in particular in the range from 4% to 8%; and / or wherein the eccentric maximum of the balancing mass unit (16) is greater than the eccentric maximum of the grinding chamber (13.1), in particular at least by a factor of 1.2 to 3. Use of at least one material-elastic link unit in a vibrating disc mill for the material-elastic mounting of a plurality of eccentric shafts during the comminution of input material, wherein the eccentric shafts are material-elastically coupled to a grinding chamber of the vibrating disc mill by means of the material-elastic connection unit, in particular when comminuting input material with a particle size of less than 20mm, in particular when grinding the feedstock to particle sizes of less than 75 µm, in particular in a vibratory disk mill device according to one of the preceding claims.

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