EP3969181B1 - Device for movement-tolerant and material-elastic coupling of a milling chamber to an eccentric shaft of a disc-type vibratory mill - Google Patents

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. Furthermore, the invention relates to the use of a movement-tolerant coupling material-elastic linkage unit for a vibrating disk mill. Last but not least, the invention also relates to a manufacturing method for the material-elastic linkage unit. In particular, the invention relates to a device and a method or a use according to the preamble of the respective independent or subordinate claim.

BACKGROUND

Vibrating disc mills are used to comminute solids as finely as possible, in particular to prepare the comminuted or ground solids for material analysis (e.g. X-ray fluorescence analysis XRF, atomic absorption spectroscopy AAS, near-infrared spectroscopy NIR, inductively coupled plasma mass spectrometry ICP-MS).

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

Unfortunately, grinding with vibratory disc mills has so far only been a less efficient grinding process in many applications. Due to friction losses in particular, there is a risk that individual components of the mill will overheat. This causes temperature inhomogeneities. Strength Temperature differences have a negative effect on the grinding result. In particular, individual components of the mill can be disadvantageously strained as a result, in particular in such a way that relative movements are made more difficult or the desired vibration cannot be achieved optimally. Disadvantageous effects such as inhomogeneous grinding results (high inhomogeneity with regard to the particle sizes in the ground charge) often cannot be avoided. This is particularly disadvantageous when the ground batch is to be used for a material analysis; the latter will then also become less precise. Last but not least, such stresses 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 mill's bearings.

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

There is still potential for optimization when it comes to 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 disc mill can be optimized, in particular with regard to the storage of components of the vibratory disc mill, in particular with regard to temperature differences, especially in vibratory disc mills with eccentric shaft drive, especially with regard to tensions between the individual components. In a narrower sense, the task can also be seen as optimizing the components of the mill that are related to the vibration excitation or their operating behavior.

This object is achieved by a vibratory disk mill device according to claim 1. Advantageous exemplary embodiments are listed in the subclaims.

The device shown is a vibrating disc mill device for comminuting input material, in particular input material with a particle size of less than 20 mm, in particular less than 10 mm, in particular set up for grinding the input material to particle sizes of less than 75 μm (pre-grinding), in particular less than 10 μm (finish grinding), with: a mill housing ; a grinding system which is arranged in the mill housing in a swinging manner and has a grinding chamber and with at least one grinding stone which is 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 synchronous or synchronously revolving 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 linkage unit. This enables a movement-tolerant or position-tolerant connection of the grinding chamber to the eccentric shafts, as a result of which the operating behavior of the mill can be optimized.

The feed preferably has a particle size of less than 20 mm.

The particle size of the starting material is particularly preferably between 20 mm and 75 μm. The feedstock is preferably reduced to particle sizes of less than 75 microns, particularly preferably ground to particle sizes of less than 10 microns. The starting material is preferably ground to particle sizes of more than 0.5 μm, more preferably to particle sizes of more than 1 μm, very preferably to particle sizes of more than 2 μm.

For the purposes of the invention, particle size is to be understood as the mean particle size, with larger and smaller particles being encountered with a decreasing probability the further the size deviates from the mean size.

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

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

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

Steel provides the advantage that large forces can be permanently transmitted even at elevated temperatures. In addition, the grinding vessel or the grinding chamber can be shrunk into it by means of a linkage unit made of steel. In addition, steel can also fulfill a thermal conductivity function, in particular for reducing the temperature in the grinding vessel.

“Material-elastic” is to be understood as meaning a functionality integrated into the material for compensating for stresses or positional tolerances, in particular a joint-free functionality 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 “material-elastic”. The “material-elastic” functionality also requires a relative movement, in particular, 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 variables of the overall system: geometry (in particular diameter); weights (grinding vessel, grinding stone and grist); Eccentric measure (grinding vessel, grinding stone and material to be ground); speeds; temperatures; to be complied with
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 the invention, the material-elastic linkage unit is material-elastic due to at least one section mounted elastically between the grinding chamber and the eccentric shafts, namely elastically in the radial direction, in particular with a bending moment or a bending stiffness, which / which is preferably in the radial direction is at least one power of ten smaller than the rigidity of the coupled power-carrying components (in particular grinding chamber; bearings; eccentric shafts; base plate). In this way it is also possible to specifically set which movements are to be tolerated at which point in the arrangement. A section mounted in a flexible manner can in particular be understood as a section mounted resiliently by bending in the elastic region of the material used. A flexible mounting in the sense of the present invention is to be understood in particular as a mounting in which the movement/positional tolerance is essentially or even exclusively ensured by bending of 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 torsion 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 does not run spirally in the manner of a spring, but which extends between the coupling points or bearing points to be connected, 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 due to at least one section mounted in a flexible manner between the grinding chamber and the eccentric shafts, in particular with a bending moment or a bending stiffness which/which is at least one power of ten smaller than the stiffness, in particular in the circumferential direction of the coupled power-carrying components (in particular the milling chamber; bearings; eccentric shafts; base plate).

In particular, a respective material-elastic section of the material-elastic link unit can extend without twisting 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/designated 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, for example, 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 made to vibrate, in particular horizontal vibrations in an at least approximately horizontal plane. The grinding ring and grinding stone rotate inside the mill and perform a relative movement against each other and against the grinding vessel. The sample material can be crushed by impact, pressure and friction.

The balancing mass unit can be offset relative to the base plate, in particular offset by 180°. The balancing mass unit has a mass in the range of a few kilograms, for example.

Grinding vessels (grinding chambers), for example, have an inside diameter of 100 mm to 300 mm. The wall thickness of the grinding vessels is, for example, in the range from 5 mm to 20 mm. For example, a grinding vessel receptacle has external dimensions in the range from 110 mm to 350 mm. 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 receptacle. With a temperature difference of, for example, 70 °C and a pitch circle diameter of the eccentric shaft of, for example, 300 mm, there is a dimensional deviation of approx. 0.25 mm. With such proportions, the length of flexible or materially elastic sections of the linkage unit(s) is, for example, in the range from 50 mm to 500 mm. With these sizes/lengths, good/effective cushioning or Position compensation take place. The centrifugal forces that occur during operation amount to a few kilonewtons [kN].

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

According to one exemplary embodiment, the material-elastic linkage unit is made 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 linkage unit can be coupled to the eccentric shafts 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 together with the balancing mass element(s). As a result, the linkage unit can also be integrated in an advantageous structural design in an expedient manner, in particular in the form of a one-piece disk.

The compensating mass elements can also be mounted on 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 be able to compensate for tilting moments. According to an advantageous variant, at least two levels are each with at least one Compensation mass element provided, which are arranged above and below the grinding vessel.

According to one embodiment, the material-elastic linkage unit couples the grinding chamber in at least one coupling point per eccentric shaft to the respective eccentric shaft in a movement-tolerant manner, in particular by means of a bearing mount for arranging a bearing for the respective eccentric shaft, the at least one coupling point being offset in the circumferential direction in relation to a coupling point or force application 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 extension. Advantageous bending properties can also be provided as a result.

According to one exemplary embodiment, the material-elastic linkage unit couples the grinding chamber in at least one coupling point for each eccentric shaft by means of a material-elastic section configured as a material-elastic arm to the respective eccentric shaft in a movement-tolerant manner, with the material-elastic arm being a one-piece, integral part of the material-elastic linkage unit, in particular in the configuration as a preferably massive bending beam-like one material section. A particularly robust arrangement can also be ensured in this way. The bending beam-like material section preferably has no hollow spaces or cavities.

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

According to one exemplary embodiment, the material-elastic link unit or at least one 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 a risk of material failure. The massive configuration also provides the advantage that even with a comparatively stiff material, a high level of bending softness can be set or achieved in the material-elastic section. The respective material-elastic section preferably has no hollow spaces or cavities. The respective material-elastic section preferably has an exclusively convex cross-sectional profile contour.

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

According to one exemplary embodiment, the material-elastic link unit has at least three material-elastic arms (three-arm configuration), which each extend in the circumferential direction around one/the grinding chamber receptacle of the material-elastic link unit, in particular in a symmetrical arrangement around the grinding chamber receptacle, and which each extend on its free end have a bearing mount, and which each have a free length from the center point of the bearing mount to a pivot point (or pivot section or center of a pivot section) on the milling 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 linkage unit can have, for example, 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 storage with regard to bending movements. This also allows great variability with regard to the optimization of the linkage unit for a particular application, for example with regard to the choice of material.

According to one embodiment, the material-elastic linkage unit couples the grinding chamber to at least one coupling point per eccentric shaft by means of a material-elastic arm to the respective eccentric shaft, with the respective material-elastic arm having a length in the range of 50 % to 150% of the diameter of the milling chamber receptacle, in particular 80% to 120% of the diameter of the milling chamber receptacle. This also allows a good length for material-elastic movement tolerance, especially for bending movements.

According to one embodiment, the radial distance between a/the respective bearing mount of the elastic link unit, in particular the radial distance of a/the center point of the bearing mount for the grinding chamber mount, is smaller than the diameter of the grinding chamber mount of the elastic link unit, in particular smaller than half the diameter or smaller than the radius of the milling chamber mount. As a result, an arrangement with flexible, but pressure-resistant, material-elastic sections can also be favored.

At least one compensation hole for stress compensation in the material of the respective arm can be provided at a transition between a/the grinding chamber receptacle of the material-elastic link unit and a/the respective material-elastic arm of the material-elastic link unit. As a result, the material-elastic function, in particular bending elasticity, can also be implemented with comparatively stiff, robust materials. The position and size of the compensation hole can be adapted to the respective material or application. The balancing hole also allows fine adjustment of the mass distribution.

According to one exemplary embodiment, there is an inner radius at/at a transition between the grinding chamber receptacle and the respective material-elastic arm formed, in particular an inner radius in the range of 10% to 25% of the cross-sectional width of the arm. According to one exemplary 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. As a result, a robust arrangement with a further optimized stress and force profile can be provided in each case.

According to one embodiment, the material-elastic linkage unit has a/the grinding chamber mount for the grinding chamber, which grinder chamber mount completely surrounds the grinder chamber in the circumferential direction, with the grinder chamber mount preferably being designed as a circular cross-section or as a cylindrical mount in the manner of a bushing . In this way, a maximum-area force transmission can be achieved with minimal pressure/stress peaks.

According to one exemplary embodiment, the material-elastic link unit is designed as a comparatively flat disk, in particular with a uniform thickness (extension in the axial longitudinal direction), in particular with a uniform thickness of both the arms and one/of the grinding chamber receptacle of the material-elastic link unit. This also provides variability in terms of material selection. As a result, the structural design can also be further optimized. For example, the thickness of the link unit is comparable to the thickness of balancing mass units or retaining clips. As a result, the linkage 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 predefined plane. In this case, the bending moment can be greater about a first axis than about a second axis, in particular by a significant factor which is chosen to be large enough that the relative movement is forced into the desired plane.

According to one exemplary embodiment, the material-elastic linkage unit is set up to couple the grinding chamber to the eccentric shafts in a material-elastic manner 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 , in particular flexible. This can also ensure effective power transmission.

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

The aforementioned object is also achieved according to the invention by a material-elastic linkage unit according to claim 14. This provides the aforementioned advantages.

For example, the grinding chamber receptacle can be cut out of a plate forming the linkage unit, in particular by plasma cutting. Any rework can be limited in particular to rework on bores and transition radii.

In the following, an aspect will be specifically discussed, which relates to a phase offset and the generation or adjustment/regulation of the nature of the vibrations, with 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 linkage unit and the measures relating to the phase offset that are also described here. The optimization of the mill based on measures for the material-elastic mounting of the chamber can be implemented in a particularly expedient manner using the measures described here with regard to the phase offset.

In the vibratory disk mill device described above, the balancing mass unit can be coupled to the eccentric shaft drive in such a way that a phase offset of greater than 180°, in particular greater than 185°, can be set between a/the eccentric maximum of the balancing mass unit and a/the eccentric maximum of the grinding chamber. In this way, an operating behavior that is advantageous for many operating situations can be ensured. In particular, smooth running of the mill can be ensured even when the load varies greatly. Last but not least, the range of operating or usage types for a specific mill type can be broadened.

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 millstone and chamber, chamber and balancing masses, and/or input material (varying mass) and generally the vibrating technical 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 of more than 180°, the counterweight system can lag behind the rotary movement of the grinding system by at least 5°, for example. According to the invention, this offset can be specified and adjusted. In this way, in particular with varying loading and with regard to variations in the movement behavior of the grinding stone, an optimization of vibration 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 of greater than 180° can ensure a certain buffering function to avoid disadvantageous vibration states in the event of a lagging imbalance in 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 balancing by means of an offset of exactly 180°, the offset being measured in relation to the eccentric maximum of the balancing masses and the eccentric maximum of the milling chamber. However, it has now been shown that this balancing strategy only enables insufficient, unsatisfactory optimization.

Mills with unbalanced drives that have been used to date usually have a vibration behavior that is characterized by a spring-damper system. It has now been shown that adjustment to the position of the grinding stone is comparatively difficult or indefinable.

The invention can therefore optionally also include the concept of setting the offset between the maximum eccentric of the balancing masses and the maximum eccentric of the grinding chamber to be unequal to 180°, with a preferably trailing grinding stone being/is made to oscillate in such a way that, in particular, even with varying loads and/or varying relative positions of the vibrating components, in particular of the grinding stone, a smooth running that is as constant as possible or a vibrational excitation that is as constant as possible 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 grinder type to be used flexibly. The practicality is improved.

Only a single eccentric maximum is preferably provided for each 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 easily realizable concept of vibrational optimization with a predefined relative arrangement of the eccentric maximum is to be preferred, i.e. without cam control. Nevertheless, in individual cases, the technical measures can be expanded to include such a cam control, if desired.

An induced movement is to be understood as “lagging” here, in particular the free movement of the millstone induced due to 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 compensating mass elements is more advantageous than just one compensating mass element, in particular with regard to different altitudes or additional tilting moments (to be avoided).

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

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

It has been shown that in order to further optimize the 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 grinding stone 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 also take place in particular by mechanical coupling, for example 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 one exemplary embodiment, the phase offset can be set in such a way that the eccentric maximum of the balancing mass unit lags behind the eccentric maximum of the grinding chamber or is arranged in chronological order. Varying operating conditions can be compensated particularly effectively by such a negative offset of the balancing mass unit by more than half a turn.

According to one exemplary embodiment, the balancing mass unit is controlled/can be controlled as a function of the control 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 balancing in the opposite direction.

An offset, in particular a lag, by a rotation angle of 185° to 200° can in particular provide the advantage that the expected relative displacements of relative positions or centers of mass are compensated with a good degree of probability or with particularly good effectiveness. It has been shown that a distance of 5° to 20° of half a turn can ensure compensation, particularly with a good safety factor, without having to deviate too much from the concept of counter-vibrating masses. In other words: In this range of deviation from exactly 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 is carried out in such a way that the regulated relative angle of rotation or phase offset of the balancing mass unit compensates for different relative positions of the at least one grinding stone relative to the eccentric maximum in partial load and full load operation, in particular for the purpose of compensating for changes in the operating state between idle and full load. The range of applications can also be broadened as a result, in particular with regard to the type and quantity of the input material.

With a higher load (e.g. with a relatively large grinding resistance), the phase shift between the eccentric maximum and the current location/position of the grinding stone is relatively greater.

According to one exemplary embodiment, the balancing mass unit can be adjusted in terms of the angle of rotation or phase offset, in particular by providing at least one eccentric disc on at least one eccentric shaft, in particular an eccentric disc that can be positioned in a relative rotational position to the eccentric shaft. As a result, a large degree of 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 adjusted. In particular, a matching means such as a feather key can promote the adjustability that is expedient in the present context. For example, the adjustability can also be ensured by a toothed shaft, a cone clamp and/or a locking bolt.

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

According to one exemplary embodiment, the angle of rotation or phase offset of the balancing mass unit can be regulated as a function of vibrations of the vibratory disk mill device, in particular by detecting accelerations in at least one spatial direction. In this way, for example, it is also possible to actively react 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 phase shift control takes place. For example, a cam control/regulation can be implemented. A multi-ring eccentric bearing, in particular a five-ring eccentric bearing, can optionally also be implemented, for example. The latter can simplify readjustment during operation.

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

According to one 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 start-up of the machine). A relatively large grindstone relative to the dimensions of the chamber also provides the advantage that phase control can be adjusted in a particularly effective manner. At a ratio greater than 60%, such effects are particularly noticeable. It has been shown that a ratio greater than 85% can have a disadvantageous effect, particularly with regard to the usable free volume.

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

The grinding stone rolls inside the grinding chamber. If the diameter of the grinding stone is at least 50% of the inner diameter of the grinding chamber, the mill can run particularly quietly and safely.

Optimization measures based on the definition of size ratios can also ensure, in particular, that the machine starts up reliably. The grinding stone can be stimulated into a desired rolling movement in a comparatively short start-up phase and can be kept in a smooth, stable run.

According to one embodiment, the eccentric maximum 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 start-up of the machine). A relatively strong eccentric shaft (comparatively large eccentricity) relative to the dimensions of the chamber also provides the advantage of a clear, unambiguous phase independent of a current configuration or loading of the chamber. At a ratio greater than 4%, the benefits are even more noticeable. It has been shown that a ratio greater than 8% may have adverse effects, particularly in terms of reaction forces or inertia or variability in operating conditions.

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

The grinding chamber and the balancing masses have, in particular, eccentrically offset fastening 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 by a factor of at least 1.2 to 3. The comparatively large eccentricity of the balancing mass unit means that the balancing masses (their mass) can be reduced, which is also advantageous for the constructive Requirements, for example, with regard to the dimensioning of the bearings.

It has been shown that the balancing weights 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 be described in particular on the basis of relative geometric size 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 eccentric maximum of the grinding chamber. As a result, a particularly advantageous compromise for the operating behavior can be achieved, in particular by means of purely device-related measures. It has been shown that particularly advantageous smooth running can be ensured in this way, in particular largely independently of the loading of the mill (amount and type of feedstock). There is an option to deviate from these ratios, for example for certain types of mills or for certain loads.

The impact or impulse exerted on the grinding stone can be defined by the size of the eccentric (or by the extent of the eccentricity) when the grinding chamber is excited. Because a large grinding stone has to cover a comparatively short distance to the opposite wall of the grinding chamber, a positive effect on the reliable start-up of the mill can also be ensured based on the conditions described here. However, only a small amount of free volume (little freedom of movement) is available for a comparatively maximally large grinding stone, 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 starting and for continuous operation. The eccentric maximum can be specified in a geometric manner, for example, 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 controlling the vibrations of a vibratory disc mill device when comminuting input material, in particular input material with a particle size of less than 20 mm or less than 10 mm. in particular in a vibratory disk mill device as described above, wherein the oscillating movement of the vibratory disk mill device is generated by means of an eccentric shaft drive comprising at least two eccentric shafts in an oscillating grinding system with a grinding chamber and with at least one grinding stone arranged in an oscillating manner in the grinding chamber, with an imbalance compensation by means of at least one on the eccentric shafts -Drive coupled balancing mass unit takes place; wherein the vibrational regulation of the oscillating movement takes place by regulating a phase offset between an eccentric maximum of the balancing mass unit and an 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 advantages mentioned above.

According to one embodiment, the phase offset is adjusted in such a way that the eccentric maximum of the balancing mass unit lags behind the eccentric maximum of the grinding chamber or is arranged in chronological order. This mode of operation has proven to be particularly advantageous, in particular with regard to widely varying loads on the mill (e.g. a wide range of type and quantity of feedstock).

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. As a result, a particularly variable operating behavior can be achieved (referred to here as vibrational system elasticity). A phase shift control can be used in particular in Depending on the control of the eccentric shaft drive and / or on 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 receptacle. The grinding stone 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 grinding stone in partial load and full load operation are compensated for relative to the eccentric maximum, in particular relative to the eccentric maximum 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 to a large extent independently of the operating state specified by the drive.

According to one embodiment, the rotational angle or phase offset of the balancing mass unit is adjusted, in particular by positioning or actively positioning at least one eccentric disk on at least one eccentric shaft in a rotational position relative to the eccentric shaft (adjustment of the relative position to optimize vibration). 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 controlled as a function of vibrations of the vibrating disk mill device, in particular by detecting acceleration parameters in at least one spatial direction and evaluating them for the vibration control. This also enables active counter-regulations in response to current operating situations.

FIGURE DESCRIPTION

Fig. 1

eine Scheibenschwingmühlenvorrichtung in einer perspektivischen Gesamtansicht;

Fig. 2

eine Ansicht auf eine Unterseite eines Mahlsystems einer Scheibenschwingmühlenvorrichtung;

Fig. 3A, 3B, 3C

jeweils in einer perspektivischen Ansicht eine materialelastische Kopplung zwischen Exzenterwellen und Mahlkammer einer Scheibenschwingmühlenvorrichtung gemäß einem Ausführungsbeispiel;

Fig. 4A, 4B

in einer Draufsicht und in einer perspektivischen Seitenansicht eine materialelastische Anlenkereinheit mit materialelastischen Abschnitten/Armen gemäß einem Ausführungsbeispiel;

Fig. 5

eine Scheibenschwingmühle gemäß dem Stand der Technik;

Fig. 6A, 6B, 6C

jeweils in schematischer Darstellung Kraftvektoren in einem Kräftediagramm bei unterschiedlichem Versatz, je nach Betriebszustand der Scheibenschwingmühlenvorrichtung;

Fig. 7A, 7B, 7C, 7D

in unterschiedlichen Ansichten jeweils eine Exzenterwelle zur Verwendung in einer Scheibenschwingmühlenvorrichtung gemäß einem Ausführungsbeispiel;

Fig. 8

in einer perspektivischen Ansicht eine Scheibenschwingmühlenvorrichtung gemäß einem Ausführungsbeispiel.

Further features and advantages of the invention result from the description of at least one exemplary embodiment with reference to drawings and from the drawings themselves

1

a vibrating disc mill device in a perspective overall view;

2

a view of an underside of a grinding system of a vibratory disk mill device;

Figures 3A, 3B, 3C

in each case a perspective view of a material-elastic coupling between the eccentric shafts and the grinding chamber of a vibratory disk mill device according to an exemplary embodiment;

Figures 4A, 4B

in a plan view and in a perspective side view, a material-elastic linkage unit with material-elastic sections/arms according to an embodiment;

figure 5

a prior art vibratory disc mill;

Figures 6A, 6B, 6C

in each case a schematic representation of force vectors in a force diagram with different offsets, depending on the operating state of the vibratory disk mill device;

Figures 7A, 7B, 7C, 7D

in different views each an eccentric shaft for use in a vibrating disk mill device according to an embodiment;

8

in a perspective view, a vibratory disc mill device according to an embodiment.

DETAILED DESCRIPTION OF THE FIGURES

In the case of reference symbols that are not explicitly described in relation to a single figure, reference is made to the other figures.

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

A vibrating disc mill device 10 comprises a mill housing 11 in which a grinding system 13 is arranged, to which input material can be supplied via a material feed 12 . The starting material is ground and can then be removed at a material discharge 19 . The grinding system 13 arranged in between comprises a grinding chamber 13.1 with at least one grinding stone, the grinding chamber 13.1 being held in a position relative to a base plate 13.5 by means of at least one retaining clip 13.3 fastened to a plurality of domes 13.4. An eccentric shaft drive 14 is coupled to a plurality of eccentric shafts 15 and drives at least one of the eccentric shafts 15 . A balancing mass unit 16 with a plurality of balancing mass elements 16.1 is used for mass balancing.

A material-elastic linkage unit 17 is arranged in particular in an arrangement under the retaining clip 13.3 and between at least two balancing mass elements 16.1 and is material-elastically coupled to the eccentric shafts 15. The linkage unit 17 couples/couples the grinding chamber 13.1 in a material-elastic manner, in particular in a flexible manner, to the shafts 15. For this purpose, the linkage unit 17 has a grinding-chamber receptacle 17.1, in particular in an at least approximately central arrangement. The material-elastic coupling can be ensured to a large extent or also essentially via a plurality of material-elastic sections 17.3, here in particular in the form of a free arm which also extends in the circumferential direction.

In one of the possible configurations, the respective material-elastic section 17.3 has in particular: a transition 17.2 between the grinding chamber receptacle 17.1 and the free section of the arm, a compensation hole 17.4 (in particular to compensate for masses or stresses during relative movements), an inner radius 17.5 and a Rounding 17.6, in particular optimized in each case with regard to minimizing stress peaks at the transition 17.2, at least one bearing mount 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 shaft 15, and a pivot point or pivot area (or geometric center) one Articulation section 17.9 at the respective transition 17.2. A/the bearing 18 for the corresponding eccentric shaft 15 can be enclosed in the respective bearing receptacle 17.7, for example by positive and/or frictional engagement. The area which defines the grinding chamber receptacle 17.1, in particular an annular area 17.11 around it, can be made of material that is rigid, for example also through material post-treatment or material differentiation.

Geometric specifications are explained below.

D17.1 Diameter of grinding chamber mount; d17 free length of the material-elastic section 17.3, in particular in the circumferential direction u; r radial direction; r1 free radial distance of the bearing mount, in particular with respect to the grinding chamber mount; z Height direction or longitudinal direction (axial direction); z17 thickness of linkage unit; α Circumferential angle or offset in the circumferential direction between pivot point 17.9 and bearing mount 17.7.

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

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

The Figure 3A , 3B , 3C show the arrangement of a material-elastic linkage unit 17 integrated between two balancing mass units 16, 16.1 and a retaining clip 13.3. Both the linkage unit 17 and the balancing mass units 16 and the retaining clip 13.3 are coupled to the eccentric shafts 15. 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 approximately 85°.

The Figure 4A , 4B show the individual sections of an integral, solid one-piece material-elastic link unit 17 with flexible arms 17.3 in the radial direction. A grinding chamber receptacle 17.1 is centered defines a comparatively materially stiff area 17.11. The transitions between this material-rigid area 17.11 (or the articulation section 17.9) and the respective arms 17.3 are all rounded (particularly areas 17.2, 17.5, 17.6). Further measures that optimize mass distribution or stress distribution or force flow can be ensured, for example, by the compensation hole 17.4 shown in the respective arm. The respective bearing mount 17.7 is provided by an integral, one-piece solid ring section 17.71, the center of which defines the coupling point 17.8 (center point of the eccentric shaft).

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

figure 5 shows a vibrating disc mill 1 without a linkage unit (prior art). The grinding system is connected to the eccentric shafts without any material-elastic coupling.

The following figures deal specifically with an aspect which relates to a phase offset and the generation or adjustment/regulation of the nature of the vibrations, with a combination with the features described above being able to provide a particularly far-reaching vibration-optimized mill.

The Figures 6A, 6B, 6C illustrate different operating states, each as a function of a phase offset ω, with a resulting force vector of a resulting imbalance being set individually in each case.

In Figure 6A a vibrational state that requires optimization is illustrated. The angle of rotation or phase shift 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 of the imbalance force of the grinding chamber points in a different direction than a force vector F2 of the imbalance force of the grinding stone. A force vector F3 of the imbalance force of the balancing mass unit points in the opposite direction to F1 (phase offset exactly 180°).

The angle of rotation or phase shift ω13 of the grinding stone is plotted between F1 and F2 .

Effect: A comparatively large/long force vector Fn for the residual imbalance occurs.

In Figure 6B an oscillation state optimized in terms of oscillation by phase shift optimization is illustrated. F3 points at an angle other than 180° opposite to F1 (phase shift, for example, about 195° or 200°; Figure 6B is not exactly to scale).

The angle of rotation or phase offset ω16 of the balancing mass unit is plotted here between F1 and F3 for the sake of simplicity.

Effect: A residual imbalance becomes zero or can be leveled out according to the invention, in particular by the phase offset ω16 being adjusted accordingly.

In Figure 6C illustrates a further operating state in which a (comparatively small) residual imbalance Fn that still exists is not leveled out or is deliberately not readjusted, in particular since the phase offset of the grinding stone ω13 varies comparatively greatly. However, the phase offset ω16 of the balancing mass unit is selected according to the invention (here, for the purpose of illustration, corresponding to that phase offset in Figure 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 of the balancing mass unit. This can also save a complex readjustment.

Effect: Depending on the extent of the offset, the comparatively small/short force vector Fn is aligned in a first or in a second, opposite direction and ideally oscillates around a mean value of zero with only a small deflection.

The Figures 7A, 7B, 7C, 7D show an eccentric shaft 15 in different views and configurations. In Figure 7A it can be seen that individual cams each comprise a disk 15.1, which can be arranged with a predefinable offset or angle of rotation relative to the other cams or disks. The individual cams or disks can be positioned relative to one another, for example by means of connecting means 15.2 (for example screw connections or fitting means).

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

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

In Figures 7C and 7D different phase offsets are illustrated. Figure 7C illustrates an offset of 180° (identified as disadvantageous according to the invention). Figure 7D FIG. 12 illustrates, by way of example, an offset (identified as advantageous according to the invention) of ±20° with respect to the exactly opposite arrangement in FIG Figure 7C (180 °), corresponding to 200 °. Such an offset can be implemented relatively between the cam for the chamber and the respective cam for the balancing mass unit(s), either permanently predefined or adjustable during operation or during breaks in operation or when the mill is reconfigured (optional readjustment).

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

Reference list:

1

vibratory disc mill

10

vibratory disc mill device

11

mill housing

12

material feed

13

grinding system

13.1

grinding chamber

13.3

retaining clip

13.4

dome or spacer element

13.5

base plate

14

Eccentric shaft drive

15

eccentric shaft

15.1

Eccentric shaft disc or eccentric disc

16

balancing mass unit

16.1

balancing mass element

17

material-elastic link unit

17.1

Grinding Chamber Recording

11/17

material-rigid area

17.2

Transition to the grinding chamber recording

17.3

material-elastic section, in particular free arm

17.4

balancing hole

17.5

inner radius

17.6

rounding off

17.7

Stock pickup

17.71

ring section

17.8

coupling point

17.9

Pivot point or pivot section or middle of a pivot section

18

Bearing for eccentric shaft

19

material discharge

20

control/regulation device

21

Measuring unit, in particular 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 grinding stone

F3

Force vector imbalance force balancing mass unit

Fn

Residual imbalance force vector

D17.1

Diameter of the grinding chamber mount

d17

free length

right

radial direction

r1

radial distance of the bearing mount

and

circumferential direction

e.g

Height direction or longitudinal direction (axial direction)

z17

Thickness of link assembly

a

Circumferential angle or offset in the circumferential direction

ω

Angle of rotation or phase shift (small omega)

ω13

Angle of rotation or phase shift grinding stone

ω16

Angle of rotation or phase shift balancing mass unit

Claims (14)

1. A vibratory disk mill device (10) for comminution of feed material, especially feed material of particle size less than 20 mm or less than 10 mm, especially set up for grinding the feed material to particle sizes less than 75 µm, having:

   - a mill housing (11);

   - a mill system (13) disposed in a vibratorily mobile manner in the mill housing (11) and having a grinding chamber (13.1) and having at least one grindstone arranged so as to be movable within the grinding chamber (13.1);

   - at least one eccentric shaft drive (14) which is mounted within the mill housing (11) and generates the vibrating motion in the grinding chamber (13.1), and at least two eccentric shafts (15), especially at least two synchronously running eccentric shafts (15),

   - a balancing mass unit (16) connected to the eccentric shaft drive (14) and set up to balance out the imbalance;

   wherein the grinding chamber (13.1) is coupled to the eccentric shafts (15) by means of at least one inherently elastic link unit (17), characterized in that the inherently elastic link unit (17) is inherently elastic by virtue of at least one section (17.3) mounted in a flexurally elastic manner between the grinding chamber (13.1) and the eccentric shafts (15), wherein the inherently elastic link unit (17) is flexurally elastic in radial direction (r).
2. The vibratory disk mill device (10) as claimed in claim 1, characterized in that the inherently elastic link unit (17) is flexurally elastic in radial direction (r) with a bending moment or bending stiffness at least one factor of ten smaller, especially in radial direction (r), than the stiffness of the coupled force-bearing components.
3. The vibratory disk mill device (10) as claimed in either of the preceding claims, characterized in that the inherently elastic link unit (17) comprises or provides a grinding chamber receptacle (17.1), especially in a one-piece integral configuration, especially integrated into the inherently elastic link unit (17) in a central arrangement; and/or wherein the inherently elastic link unit (17) is fashioned from a prefabricated semifinished product, especially in a completely solid configuration.
4. The vibratory disk mill device (10) as claimed in any of the preceding claims, characterized in that the inherently elastic link unit (17) couples the grinding chamber (13.1) to the respective eccentric shaft (15) in a movement-tolerant manner at at least one coupling point (17.8) per eccentric shaft (15), especially by means of a bearing receptacle (17.7) for arrangement of a bearing for the respective eccentric shaft (15), wherein the at least one coupling point (17.8) is arranged with an offset (α) in circumferential direction (u) in relation to a link point or force introduction point on the grinding chamber (13.1), especially with an offset in the range of a circumferential angle α of 30° to 120°, especially in at least approximately tangential extent.
5. The vibratory disk mill device (10) as claimed in any of the preceding claims, characterized in that the inherently elastic link unit (17) couples the grinding chamber (13.1) to the respective eccentric shaft (15) in a movement-tolerant manner at at least one coupling point (17.8) per eccentric shaft (15) by means of an inherently elastic section configured as a free arm (17.3), wherein the inherently elastic arm (17.3) is integrated into the inherently elastic link unit (17) in a one-piece manner, especially configured as a flexible beam-like material section.
6. The vibratory disk mill device (10) as claimed in any of the preceding claims, characterized in that the inherently elastic link unit (17) or at least one respective inherently elastic section (17.3) of the inherently elastic link unit (17) is in a solid configuration.
7. The vibratory disk mill device (10) as claimed in any of the preceding claims, characterized in that the inherently elastic link unit (17) has at least three inherently elastic sections each configured as a free arm (17.3), each of which extends in circumferential direction (u) around a/the grinding chamber receptacle of the inherently elastic link unit (17), especially in symmetric arrangement around the grinding chamber receptacle, and each has a bearing receptacle (17.7) at its free end, and each has a free length (d17) from the center of the bearing receptacle (17.7) up to a link point (17.9) on the grinding chamber receptacle corresponding to a circumferential angle α of at least 30° to 45°, especially corresponding to a circumferential angle α of at least 45° to 60°, especially a free length (d17) in the range from at least 50% to 90% of the diameter of the grinding chamber receptacle, especially at least 75% to 90% of the diameter of the grinding chamber receptacle (D17.1); and/or wherein the inherently elastic link unit (17) couples the grinding chamber (13.1) to the respective eccentric shaft (15) at at least one coupling point (17.8) per eccentric shaft (15) by means of a/the inherently elastic section, in each case configured as a free arm (17.3), wherein the respective inherently elastic arm (17.3) has a length from a transition to the grinding chamber receptacle up to the free end of the arm (17.3) in the range from 50% to 150% of the diameter of the grinding chamber receptacle (D17.1), especially 80% to 120% of the diameter of the grinding chamber receptacle (D17.1).
8. The vibratory disk mill device (10) as claimed in any of the preceding claims, characterized in that the inherently elastic link unit (17) includes a/the grinding chamber receptacle (17.1) for the grinding chamber (13.1) that fully surrounds the grinding chamber (13.1) in circumferential direction (u), wherein the grinding chamber receptacle is preferably configured as a receptacle having a circular cross section or as a cylindrical receptacle in the form of a sleeve.
9. The vibratory disk mill device (10) as claimed in any of the preceding claims, characterized in that the radial distance (r1) of a/the respective bearing receptacle (17.7) of the inherently elastic link unit (17), especially the radial distance (r1) of a/the center of the bearing receptacle (17.7) from the grinding chamber receptacle, is less than the diameter of the grinding chamber receptacle (D17.1) of the inherently elastic link unit (17), especially less than half the diameter of the grinding chamber receptacle (D17.1).
10. The vibratory disk mill device (10) as claimed in any of the preceding claims, characterized in that the inherently elastic link unit (17) takes the form of a flat disk, especially having uniform thickness, especially having uniform thickness both of inherently elastic sections/arms and of a/the grinding chamber receptacle of the inherently elastic link unit (17).
11. The vibratory disk mill device (10) as claimed in any of the preceding claims, characterized in that the inherently elastic link unit (17) is set up to couple the grinding chamber (13.1) to the eccentric shafts (15) in an inherently elastic manner with movement tolerances of less than 1 mm, preferably less than 0.5 or 0.3 or 0.2 mm, especially with these movement tolerances each in radial direction (r1).
12. The vibratory disk mill device (10) as claimed in any of the preceding claims, characterized in that the balancing mass unit (16) is coupled to the eccentric shaft drive (14) in such a way that a phase offset ω of greater than 180°, especially greater than 185°, can be established between a/the eccentric maximum of the balancing mass unit (16) and a/the eccentric maximum of the grinding chamber (13.1).
13. The vibratory disk mill device (10) as claimed in claim 12, characterized in that the phase offset ω is adjustable in such a way that the eccentric maximum of the balancing mass unit (16) lags behind the eccentric maximum of the grinding chamber (13.1); and/or wherein the balancing mass unit (16) can be actuated as a function of the actuation of the eccentric shaft drive (14) in such a way that a phase offset ω in the range from 185° to 200° can be established; and/or wherein the actuation is effected in such a way that the established phase offset ω of the balancing mass unit (16) balances different relative positions of the at least one grindstone relative to the eccentric maximum in part-load and full-load operation, especially for the purpose of balancing changes in the state of operation between idling and full load; and/or wherein the balancing mass unit (16) is adjustable in terms of the phase offset ω, especially in that at least one eccentric disk (15.1) is provided on at least one eccentric shaft (15), especially an eccentric disk that can be positioned in a relative rotation position to the eccentric shaft (15); and/or wherein the eccentric maximum of the grinding chamber (13.1) is at least 2% of the internal diameter of the grinding chamber (13.1), especially 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), especially at least by a factor of 1.2 to 3.
14. An inherently elastic link unit (17) set up for inherently elastic coupling of a grinding chamber (13.1) to at least one eccentric shaft (15) in a vibratory disk mill device (10) as claimed in any of the preceding claims, characterized in that the inherently elastic link unit (17) has been produced by recessing a bearing receptacle (17.7) for the eccentric shaft (15) and by recessing a grinding chamber receptacle, with at least one inherently elastic section (17.3) of reduced crosssectional area formed in each case between the receptacles, especially in a one-piece solid plate that forms the one-piece integrated inherently elastic link unit (17).

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