EP3969182B1 - Device and method for vibration-optimised coupling of a milling chamber to an eccentric shaft of a disc-type vibratory mill and a use - Google Patents

Description

TECHNICAL AREA

The invention relates to a device and a method for coupling a grinding chamber to eccentric shafts of an oscillating disk mill in a way that is optimized in terms of vibration. Last but not least, the invention also relates to the use of eccentric shafts with a predefined phase offset in a predefined phase offset range. 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, for example to prepare the comminuted or ground solids for a 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 input (inlet) and a material discharge (outlet). The grinder comprises, for example, a pot with a lid and grinding body (hereinafter "grinding stone"), where the grinding stones can be designed, for example, as stones, discs, lenses or rings. Vibrating disc mills can grind the solids based on pressure, impact and/or friction.

According to one type of vibrating disc mill, the grinding stone is set in motion by a drive with eccentric shafts.

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, for example, that individual components of the mill will overheat. This also explains, for example, temperature inhomogeneities, which can also 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, for example, inhomogeneous grinding results (particularly high inhomogeneity with regard to the particle sizes in the ground charge) can then often not 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, stresses of this kind in moving components or in bearings, in particular roller bearings, can be caused to such an extent that the mill only has a shorter service life or even suffers operational failures. In other words: Optimizing vibrations goes hand in hand with optimizing fixtures.

There is therefore interest in optimizing the mill as simply as possible, but nonetheless effectively. 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 or the anti-vibration bearings of the mill.

Against this background, there is particular interest in a further development of vibrating disk mills for the mineral sector, which must also be designed to accommodate larger amounts of material or varying amounts of material. In other words: the mineral sector in particular requires comparatively large systems with comparatively large unbalanced masses, whereby the respective vibration behavior can depend on the current load. Therefore, the requirement of optimized balancing of the mill is of great importance, especially in these plants. Desired effects: smooth running; optimized operating behavior; for example, doing without a complex system foundation, for example when installed in a laboratory.

From the DE 43 43 742 A1 a vibratory disc mill is known.

From the SU 1 433 499 A1 discloses a main crushing chamber located in the casing between the parallel eccentric shafts on their eccentric necks. Additional crushing chambers are mounted on additional eccentric collars. The additional eccentric necks are shifted in the angular direction and form a statically and dynamically balanced system with the crushing chamber. When using three crushing chambers, the eccentric necks are offset by 180 degrees. With two crushing chambers, the main crushing chamber is located in the annular crushing chamber opening.

From the DE 22 12 601 A1 a disk and ring vibratory mill is known.

From the US 2019/111 438 A1 a mill with a safety frame is known.

DESCRIPTION OF THE INVENTION

The object of the invention is to provide a device and a method with the features described above, with which the operation of a vibratory disc mill with an eccentric shaft drive can be optimized in terms of vibrations, in particular with regard to optimizing the vibrations of the entire device even with greatly varying loads . In a narrower sense, the task can also be seen as optimizing the components of the mill that are related to the vibration excitation and their operating behavior.

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

According to the invention, this object is achieved in particular by a vibrating disk mill device set up for comminuting input material, in particular input material with a particle size of less than 20 mm or less than 10mm, in particular set up for grinding the input material to particle sizes of less than 75µm, 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; and with 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 revolving eccentric shafts; and set up with at least one balancing mass unit coupled to the eccentric shaft drive for imbalance compensation; wherein the balancing mass unit is 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 an eccentric maximum of the balancing mass unit and an 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 grinding stone 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, for example by at least 5°. According to the invention, this offset can be specified and adjusted. In this way, in particular with varying loads and with regard to variations in Movement behavior of the millstone ensures vibration optimization, especially in terms 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 grinding 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 undefinable.

The invention is based on the concept of setting the offset between the maximum eccentricity of the balancing masses and the maximum eccentricity of the grinding chamber to be unequal 180°, with a preferably trailing grinding stone being set in motion in such a way that, in particular, even with varying loads and/or varying relative positions of the oscillating 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, the invention 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 the present invention is primarily based on the comparatively easily realizable concept of vibrational optimization with a predefined relative arrangement of the eccentric maximum, ie 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. However, a balancing mass element coupled to all shafts provides the advantage that the space between the shafts can also 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 phase offset can also be adjusted in particular by mechanical coupling, e.g. 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 or is temporally subordinate to the eccentric maximum of the grinding chamber. 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/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, in particular 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 for a more variable operating range of the mill can be ensured.

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 maximum eccentric 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 in that at least one eccentric disk is provided on at least one eccentric shaft, in particular an eccentric disk 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 design 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, for example, in particular a five-ring eccentric bearing, can optionally also be implemented. 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 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 grinding stone has a diameter of at least 50% of the inner diameter of the grinding chamber, the mill can run particularly smoothly 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% can be disadvantageous, particularly with regard to 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. With 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 reliable, 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, e.g. 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 based on the relative geometric dimensions of eccentric elements (e.g. disks).

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 It has been shown that a 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, eg for certain types of mills or with 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 way, e.g. by the diameter of an eccentric element (particularly a disk).

The aforementioned object is also achieved according to the invention by a disc vibratory mill device set up for comminuting input material, in particular input material with a particle size of less than 20 mm or less than 10 mm, in particular set up for grinding the input material to particle sizes of less than 75 μm, 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; and with 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 revolving eccentric shafts; and set up with at least one balancing mass unit coupled to the eccentric shaft drive for imbalance compensation; wherein the balancing mass unit is 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, the balancing mass unit being dependent on the control in this way of the eccentric shaft drive is controlled/can be controlled so that a phase offset can be set in the range from 185° to 200°, and wherein 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%. This results in numerous previously mentioned advantages.

The aforementioned object is also achieved according to the invention by a method for controlling the vibrations of a vibratory disk 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 described above, the vibrating movement of the vibratory disk mill device being controlled by means of an eccentric shaft drive at least two eccentric shafts are produced 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 being compensated for by means of at least one balancing mass unit coupled to the eccentric shaft drive; 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 set in such a way that the eccentric maximum of the balancing mass unit lags behind or is arranged in time after the eccentric maximum of the grinding chamber. This mode of operation has proven to be particularly advantageous, particularly with regard to widely varying loads on the mill (e.g. broad spectrum of type and quantity of input material).

The balancing mass unit can be/are 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 carried out in particular as a function of the activation 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 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 vibratory 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.

The above-mentioned object is also achieved according to the invention by a control/regulation device set up to carry out a method described above, the imbalance being compensated for by means of at least one balancing mass unit coupled to the eccentric shaft drive, in that a phase offset between the eccentric maxima of the balancing mass unit and the grinding chamber is not equal to 180 ° is set or actively regulated with a phase difference of at least 5° or at least 10° in relation to a 180° phase offset, the control/regulation device being coupled in particular to at least one measuring unit or including this. This results in the advantages mentioned above.

The aforementioned object is also achieved according to the invention by using eccentric shafts with a phase offset in a vibratory disk mill device, in particular in a vibratory disk mill device described above, for setting an operating state that is optimized in terms of vibration technology, the eccentric shafts on the one hand exciting a grinding chamber with at least one grinding stone arranged movably in the grinding chamber, and the eccentric shafts on the other hand stimulating at least one balancing mass unit, the eccentric shafts being coupled to the milling chamber and to the at least one balancing mass unit in such a way that a phase offset between the eccentric maxima of the at least one balancing mass unit and the milling chamber is not equal to 180, regardless of the operating state or the current loading of the milling chamber ° is ensured, especially in a range of 5 to 15° offset with respect to 180° phase offset. This results in the advantages mentioned above.

According to a further aspect of the present invention, a further vibration-related optimization can be carried out on a structural level by means of at least one material-elastic linkage unit. In particular, the grinding chamber can be coupled to the eccentric shafts by means of at least one material-elastic linkage unit. This also 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 further optimized, especially with greatly varying loading, ie with varying movement behavior of the grinding stone. On the one hand, the material-elastic linkage units can compensate for oscillation effects or equalize vibrations, on the other hand, stresses caused by temperature fluctuations or positional tolerances can also be minimized.

In the following, one aspect will be discussed in particular, which relates to the device-technical coupling of the chamber to the shafts, wherein a combination with the features described above can provide a particularly far-reaching vibration-optimized mill. In other words: A particularly far-reaching vibration-optimized mill can be realized by combining the measures regarding phase offset with measures based on a material-elastic linkage unit. Conversely, 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 regarding phase offset, for example by adjusting a corresponding operating behavior in the control technology for mills with a material-elastic linkage unit.

In the vibratory disk mill device described above, the grinding chamber can be 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, whereby the operating behavior of the mill can be optimized.

It has been shown 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).

In particular, it is also possible to benefit from the material-elastic properties of the linkage unit in connection with the setting of a phase offset.

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; tolerances to be observed. The masses and diameters as well as the maximum speed and the temperature difference of the components have a major influence.

According to one exemplary embodiment, the material-elastic linkage unit is material-elastic due to at least one section mounted in a flexurally elastic manner 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 is at least one power of ten smaller than the rigidity, in particular in the radial direction of the coupled power-carrying components (in particular the milling 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 storage differs from a spring storage by means of tension or compression springs and also differs from mounting by means of bending 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.

According to one exemplary embodiment, the material-elastic linkage unit includes or provides a grinding chamber receptacle, in particular in a one-piece, integral configuration, in particular integrated in a centric 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 provided, each with at least one balancing mass element, which are arranged above and below the grinding vessel.

According to one exemplary embodiment, the material-elastic linkage unit couples the grinding chamber in at least one coupling point for each 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 pivot point 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 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 example stiffness value is in the range of approx. 0.1mm to 0.3mm per 1000N 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 degree of bending softness can be set or achieved in the material-elastic section. Preferably, the respective material-elastic section no cavities 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 an articulation point (or articulation section or center of an articulation section) on the milling chamber mount corresponding to a circumferential angle of at least 30° to 45°, in particular corresponding a peripheral 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, for example, 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 storage with regard to bending movements. This also enables great variability with regard to the optimization of the linkage unit for a particular application, e.g. with regard to the choice of material.

According to one embodiment, the material-elastic linkage unit couples the grinding chamber in at least one coupling point per eccentric shaft by means of one/the material-elastic arm to the respective eccentric shaft, with the respective material-elastic arm extending from a transition to the grinding chamber receptacle to the free end of the arm has 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, 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 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 disc, in particular with a uniform thickness (extension in the axial longitudinal direction), in particular with a uniform thickness both of arms and of one/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 predefinable 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 selected 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 grinding chamber receptacle can be cut out, for example, from 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.

FIGURE DESCRIPTION

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

• Figures 1A, 1B, 1C 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 2A, 2B, 2C, 2D in different views each an eccentric shaft for use in a vibrating disk mill device according to an embodiment;
• 3 in a perspective view, a vibrating disc mill device according to an embodiment;
• 4 a vibrating disc mill device in a perspective overall view;
• figure 5 a view of an underside of a grinding system of a disc oscillating mill device;
• Figure 6A , 6B , 6C 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;
• Figure 7A , 7B in a plan view and in a perspective side view, a material-elastic linkage unit with material-elastic sections/arms 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, at least in part, may first be described together with reference to all reference numerals for ease of understanding. Details or special features shown in the respective figures are described individually.

The Figures 1A, 1B, 1C 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 1A 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 1B an oscillation state optimized in terms of oscillation by phase shift optimization is illustrated. F3 points at an angle not equal to 180° opposite to F1 (phase shift, for example, approx. 195° or 200°; Figure 1B 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 1C 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 1B ) that the resulting residual imbalance oscillates around the value zero. Such a mean value can be determined, for example, as an empirical value from standard 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 2A, 2B, 2C, 2D 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 discs 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 2 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 units. It has been shown that a particularly advantageous operating behavior can be realized if the middle cam couples the grinding chamber.

In Figure 2B the relative position of the individual cams or disks 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 2C and 2D different phase offsets are illustrated. Figure 2C illustrates an offset of 180° (identified as disadvantageous according to the invention). 2D FIG. 12 illustrates an offset of ±20° (identified as advantageous according to the invention) with respect to the exactly opposite arrangement according to FIG Figure 2C (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).

3 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.

The following figures deal specifically with an aspect which relates to a technical device coupling of the chamber to the shafts, with a combination with the features described above being able to provide a particularly far-reaching vibration-optimized mill.

In the 4 Vibrating disc mill device 10 shown comprises a mill housing 11, in which a grinding system 13 is arranged, which over a material task 12 input material can be supplied. 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 (not shown). 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 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) of an 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 non-positive engagement. The area which defines the grinding chamber receptacle 17.1, in particular an annular area 17.11 around it, can be made materially rigid, for example by 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 4 shows a vibrating disc mill device 10 with a grinding system 13 driven by eccentric shafts.

The figure 5 shows a grinding system 13 mounted on a base plate with three eccentric shafts 15, of which an eccentric shaft 15 is driven by a drive 14.

The Figure 6A , 6B , 6C show the arrangement of a material-elastic linkage unit 17 integrated between two balancing mass units 16, 16.1. Both the linkage unit 17 and the balancing mass units 16 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°. In Figure 6A the inner diameter D13.1 of the grinding chamber is also indicated, defined in particular by the inner walls of the grinding chamber on which the grinding stone rolls.

The Figure 7A , 7B 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 milling chamber receptacle 17.1 is defined centrally by a region 17.11 that is comparatively stiff in material. 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 means of 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 7B illustrates the comparatively small thickness z17 of the linkage unit (disc-like design).

The features of the link unit described here can be combined with the features described above with regard to the phase offset.

Reference list:

10

vibratory disc mill device

11

mill housing

12

material feed

13

grinding system

13.1

grinding chamber

14

Eccentric shaft drive

15

eccentric shaft

15.1

Eccentric shaft disc or eccentric disc

15.2

lanyard

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

D13.1

Inside diameter of grinding chamber

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 (18)

1. A vibratory disk mill device (10) for comminuting feed material, in particular feed material of a particle size of less than 20 mm or less than 10 mm, in particular designed for grinding the feed material to particle sizes of less than 75 µm, with:

   - a mill housing (11);

   - a grinding system (13), which is arranged in the mill housing in an oscillatory movable manner and has a grinding chamber (13.1) and at least one grindstone movably arranged in the grinding chamber;

   - at least one eccentric shaft drive (14), which is mounted in the mill housing and generates the vibrating movement in the grinding chamber, and at least two eccentric shafts (15), in particular at least two synchronously rotating eccentric shafts;

   - at least one balancing mass unit (16), which is coupled to the eccentric shaft drive and is designed for balancing an imbalance;

   characterized in that the balancing mass unit is 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 an eccentric maximum of the balancing mass unit and an eccentric maximum of the grinding chamber.
2. The vibratory disk mill device as claimed in claim 1, wherein the phase offset can be set 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 activated in dependence on the activation of the eccentric shaft drive (14) in such a way that a phase offset in the range from 185° to 200° can be set.
3. The vibratory disk mill device as claimed in claim 1 or 2, wherein the activation takes place in such a way that the adjusted phase offset of the balancing mass unit (16) balances out different relative positions of the at least one grindstone relative to the eccentric maximum in part-load and full-load operation, in particular for the purpose of balancing out changes in state between no-load and full-load operation.
4. The vibratory disk mill device as claimed in one of the preceding claims, wherein the balancing mass unit (16) can be set in the phase offset, in particular in that at least one eccentric disk (15.1) is provided on at least one eccentric shaft (15), in particular an eccentric disk that can be positioned in a relative rotational position with respect to the eccentric shaft.
5. The vibratory disk mill device as claimed in one of the preceding claims, wherein the phase offset of the balancing mass unit (16) can be controlled in dependence on vibrations of the vibratory disk mill device (10), in particular in that accelerations in at least one spatial direction are detected.
6. The vibratory disk mill device as claimed in one of the preceding claims, wherein the at least one grindstone has a diameter of at least 50% of the inside diameter of the grinding chamber (13.1), in particular in the range from 60% to 85%.
7. The vibratory disk mill device as claimed in one of the preceding claims, wherein the eccentric maximum of the grinding chamber (13.1) is at least 2% of the inside diameter of the grinding chamber, in particular in the range from 4% to 8%.
8. The vibratory disk mill device as claimed in one of the preceding claims, 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.
9. The vibratory disk mill device as claimed in one of the preceding claims, wherein the at least one grindstone has a diameter that is predefined by the inside diameter of the grinding chamber (13.1) minus a factor of 5 to 7 of the eccentric maximum of the grinding chamber.
10. The vibratory disk mill device (10) as claimed in one of the preceding claims, wherein the grinding chamber (13.1) is coupled to the eccentric shafts (15) by means of at least one inherently elastic link unit (17).
11. The vibratory disk mill device as claimed in claim 10, wherein the inherently elastic link unit is inherently elastic by virtue of at least one section (17.3) mounted in a flexurally elastic manner between the grinding chamber and the eccentric shafts, in particular in a flexurally elastic manner in the radial direction, in particular with a bending moment or bending stiffness that is less than the stiffness of the coupled force-bearing components, in particular in the radial direction (r), by at least a factor of ten; and/or wherein the inherently elastic link unit (17) comprises or provides a grinding chamber receptacle (17.1), in particular in a one-piece integral configuration, in particular integrated into the inherently elastic link unit in a central arrangement; and/or wherein the inherently elastic link unit is configured from a prefabricated semifinished product, in particular in a completely solid configuration; and/or wherein the inherently elastic link unit (17) couples the grinding chamber (13.1) to the respective eccentric shaft in a movement-tolerant manner at at least one coupling point (17.8) per 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 link point or force introduction point 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; and/or wherein the inherently elastic link unit couples the grinding chamber to the respective eccentric shaft in a movement-tolerant manner at at least one coupling point per eccentric shaft by means of an inherently elastic section configured as a free arm (17.3), wherein the inherently elastic arm is a one-piece integral part of the inherently elastic link unit, in particular configured as a flexural-beam-like material section; and/or wherein the inherently elastic link unit has a/the grinding chamber receptacle (17.1) for the grinding chamber, which fully surrounds the grinding chamber in the circumferential direction, wherein the grinding chamber receptacle is preferably configured as a receptacle having a circular cross section or as a cylindrical receptacle in the manner of a sleeve; and/or wherein the inherently elastic link unit takes the form of a flat disk, in particular with uniform thickness, in particular with uniform thickness both of inherently elastic sections/arms and of a/the grinding chamber receptacle of the inherently elastic link unit.
12. A method for vibrationally controlling a vibratory disk mill device (10) when comminuting feed material, in particular feed material of a particle size of less than 20 mm or less than 10 mm, in particular in the case of a vibratory disk mill device as claimed in one of the preceding claims, wherein the vibrating movement of the vibratory disk mill device is generated by means of an eccentric shaft drive (14) comprising at least two eccentric shafts (15) in an oscillatory movable grinding system (13) with a grinding chamber (13.1) and with at least one grindstone arranged in an oscillatory movable manner in the grinding chamber, wherein a balancing of an imbalance takes place by means of at least one balancing mass unit (16) coupled to the eccentric shaft drive;
    characterized in that the vibrational control of the vibrating movement takes place by controlling a phase offset between a/the eccentric maximum of the balancing mass unit (16) and a/the eccentric maximum of the grinding chamber (13.1), wherein the phase offset is set to an amount greater than 180°, in particular greater than 185°.
13. The method as claimed in claim 12, wherein the phase offset is set 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) is coupled to the eccentric shaft drive (14) in such a way that a phase offset in the range from 185° to 200° is set.
14. The method as claimed in one of the claims 12-13, wherein the phase offset of the balancing mass unit (16) is predefined or actively adjusted in such a way that different relative positions of the at least one grindstone in part-load and full-load operation are compensated relative to the eccentric maximum, in particular for the purpose of balancing out changes in state between no-load and full-load operation.
15. The method as claimed in one of the claims 12-14, wherein the balancing mass unit (16) is set in the phase offset, in particular in that on at least one eccentric shaft (15) at least one eccentric disk (15.1) is positioned, or is actively positioned, in a relative rotational position with respect to the eccentric shaft.
16. The method as claimed in one of the claims 12-15, wherein the phase offset of the balancing mass unit (16) is controlled in dependence on vibrations of the vibratory disk mill device (10), in particular in that acceleration parameters in at least one spatial direction are detected and evaluated for the vibration control.
17. An open-loop/closed-loop control device (20) designed for performing a method as claimed in one of the claims 12-16, wherein the balancing of an imbalance takes place by means of at least one balancing mass unit (16) coupled to the eccentric shaft drive (14), in that a phase offset between the eccentric maxima of the balancing mass unit (16) and the grinding chamber (13.1) unequal to 180° with a phase difference of at least 5° or at least 10° is set or actively adjusted in relation to a 180° phase offset, wherein the open-loop/closed-loop control device is in particular coupled to at least one measuring unit (21) or comprises it.
18. The use of eccentric shafts (15) with a phase offset in a vibratory disk mill device, in particular in a vibratory disk mill device (10) as claimed in one of claims 1 to 11, for setting a vibrationally optimized operating state, wherein the eccentric shafts on the one hand excite a grinding chamber (13.1) with at least one grindstone movably arranged in the grinding chamber, and wherein the eccentric shafts (15) on the other hand excite at least one balancing mass unit (16), wherein the eccentric shafts are coupled to the grinding chamber and to the at least one balancing mass unit in such a way that a phase offset between the eccentric maxima of the at least one balancing mass unit and the grinding chamber (13.1) unequal to 180°, in particular in a range from 5 to 15° offset in relation to 180° phase offset, is ensured independently of the operating state or the momentary loading of the grinding chamber.

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