DE102019207222A1 - Device and method for the vibration-optimized coupling of a grinding chamber to eccentric shafts of a vibrating disc mill and use - Google Patents

Abstract

The invention relates to a vibratory disk mill device (10) for comminuting input material, comprising: a mill housing (11); a grinding system (13) arranged in the mill housing such that it can vibrate, with a grinding chamber (13.1) and with at least one grinding stone arranged movably in the grinding chamber; at least one eccentric shaft drive (14) mounted in the mill housing and generating the oscillating movement in the grinding chamber and at least two eccentric shafts (15); at least one balancing mass unit (16) coupled to the eccentric shaft drive, designed to compensate for unbalance; the balancing mass unit being coupled to the eccentric shaft drive in such a way that a phase offset greater than 180 °, in particular greater than 185 °, can be set between the eccentric maximum of the balancing mass unit and the eccentric maximum of the grinding chamber. This enables vibration-optimized operating conditions. The invention also relates to a method for the vibration control of a vibrating disk mill device and the use of eccentric shafts (15) with a phase offset.

Description

TECHNICAL AREA

The invention relates to a device and a method for the vibration-optimized coupling of a grinding chamber to eccentric shafts of a vibrating disk mill. Last but not least, the invention also relates to the use of eccentric shafts with a predefined phase offset in a predefinable 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 subsidiary claim.

BACKGROUND

Vibrating disc mills are used to crush solids as finely as possible, for example to provide the crushed or ground solids for material analysis (e.g. XRF, AAS, NIR, ICP-MS).

Vibrating disc mills usually have a grinder which is arranged in a housing between a material feed (inlet) and a material discharge (outlet). The grinder comprises, for example, a pot with a lid and grinding body (hereinafter "grinding stone"), the grinding stones e.g. can be designed as stones, discs, lenses or a ring. Vibratory 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.

Grinding with vibrating disc mills has unfortunately been an inefficient grinding process in many applications. In particular due to frictional losses, e.g. the risk of individual components of the grinder becoming very hot. This also causes temperature inhomogeneities, for example, which can also have a negative effect on the grinding result. In particular, individual components of the mill can be adversely braced as a result, in particular in such a way that relative movements are made difficult or the desired oscillation cannot be optimally achieved. Adverse effects such as Inhomogeneous grinding results (in particular high inhomogeneity with regard to the particle sizes in the ground batch) can then often not be avoided. This is particularly disadvantageous when the ground batch is to be used for a material analysis; the latter is then unfortunately also less precise. Last but not least, such tension can also be caused in moving components or in bearings, in particular roller bearings, to such an extent that the mill only has a shortened service life or even suffers operational failures. In other words: Vibration optimization goes hand in hand with device optimization.

There is therefore interest in optimizing the mill as simply as possible, but still effective. 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 to the vibration-related mounting of the mill.

Against this background, there is also particular interest in further developing vibratory 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. For this reason, the requirement of optimized balancing of the mill is of great importance, especially in these systems. Desired effects: smooth running; optimized operating behavior; For example, dispensing with a complex system foundation, for example when installing in a laboratory.

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 vibrating disc mill with an eccentric shaft drive can be optimized in terms of vibration, in particular with regard to vibration optimization 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 related to the vibration excitation or 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 feed material, in particular feed material with a particle size of less than 20 mm or less than 10 mm, in particular set up for grinding Feed material to particle sizes smaller than 75 µm, with: a mill housing; a grinding system arranged in the mill housing such that it can oscillate, with a grinding chamber and with at least one grinding stone arranged movably in the grinding chamber; 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 rotating eccentric shafts; and with at least one balancing mass unit coupled to the eccentric shaft drive, set up to compensate for unbalance; the balancing mass unit being coupled to the eccentric shaft drive in such a way that a phase offset greater than 180 °, in particular greater than 185 °, can be set between one / the eccentric maximum of the balancing mass unit and one / the eccentric maximum of the grinding chamber. In this way, an operating behavior which is advantageous for many operating situations can be ensured.

In particular, smooth running of the mill can be ensured even with greatly varying loads. Last but not least, the spectrum of types of operation or use for a particular type of mill can be expanded.

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

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

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

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

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

The invention is based on the concept of setting the offset between the eccentric maximum of the balancing masses and the eccentric maximum of the grinding chamber not equal to 180 °, with a preferably lagging grinding stone being / is vibrated in such a way that, in particular, even with varying loads and / or varying relative positions of the vibrating components, in particular of the millstone, a smooth running that is as constant as possible or a vibration-related 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 type of mill to be used in a flexible manner. The practicality is improved.

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

According to one embodiment, the angle of rotation or phase offset of the balancing mass unit can be regulated as a function of vibrations of the vibrating disk mill device, in particular by detecting accelerations in at least one spatial direction. In this way, it is also possible, for example, to react actively to current operating situations.

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

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

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

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

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

By means of optimization measures based on the definition of size relationships, a safe start-up of the machine can in particular also be ensured. The grinding stone can be excited into a desired rolling movement in a comparatively short start-up phase and kept in a smooth, stable run.

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

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

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

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

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

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

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

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

ITEM The aforementioned object is also achieved according to the invention by a vibratory disk mill device set up for comminuting feedstock, in particular feedstock with a particle size of less than 20mm or less than 10mm, in particular designed for grinding the feedstock to particle sizes of less than 75μm, with: a mill housing; a grinding system arranged in the mill housing such that it can oscillate, with a grinding chamber and with at least one grinding stone arranged movably in the grinding chamber; 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 rotating eccentric shafts; and with at least one balancing mass unit coupled to the eccentric shaft drive, set up to compensate for unbalance; The balancing mass unit is coupled to the eccentric shaft drive in such a way that a phase offset greater than 180 °, in particular greater than 185 °, can be set between one / the eccentric maximum of the balancing mass unit and one / the eccentric maximum of the grinding chamber, the balancing mass unit depending on the control of the eccentric shaft drive that a phase offset can be set in the range from 185 ° to 200 °, and 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 advantages mentioned above.

The aforementioned object is also achieved according to the invention by a method for the vibration control of a vibratory disk mill device when comminuting feed material, in particular feed material with a particle size of less than 20 mm or less than 10 mm, in particular in the case of a vibrating disk mill device described above, the vibratory movement of the vibrating disk mill device comprising at least an eccentric shaft drive two eccentric shafts are produced in an oscillating grinding system with a grinding chamber and with at least one grinding stone arranged oscillating in the grinding chamber, imbalance compensation being carried out by means of at least one balancing mass unit coupled to the eccentric shaft drive; The vibrational regulation of the vibratory movement takes place by regulating a phase offset between one / the eccentric maximum of the balancing mass unit and one / the eccentric maximum of the grinding chamber, the phase offset being set to an amount greater than 180 °, in particular greater than 185 °. This results in the aforementioned advantages.

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

The balancing mass unit can be coupled to the eccentric shaft drive in this way / be that a phase offset in the range of 185 ° to 200 ° is set, i.e. in a range of at least 5 ° to a maximum of 20 ° deviation from exactly opposite excitation. In this way, a particularly variable operating behavior can be achieved (here figuratively referred to as vibration-related system elasticity). A phase offset regulation can take place in particular as a function of the 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 holder. The millstone can assume a rotation angle offset of a maximum of approx. 90 °.

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

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

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

The aforementioned object is also achieved according to the invention by a control / regulating device set up to carry out a method described above, the imbalance compensation being carried out by means of at least one compensating mass unit coupled to the eccentric shaft drive, in which a phase offset between the eccentric maxima of the compensating 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 / regulating device being coupled in particular to or including at least one measuring unit. This results in the aforementioned advantages.

The above-mentioned object is also achieved according to the invention by using eccentric shafts with a phase offset in a vibrating disk mill device, in particular in a vibrating disk mill device described above, for setting an operating state that is optimized in terms of vibration, the eccentric shafts on the one hand exciting a grinding chamber with at least one millstone movably arranged in the grinding chamber, and The eccentric shafts on the other hand excite at least one balancing mass unit, the eccentric shafts being 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 is unequal to 180 regardless of the operating state or the current loading of the grinding chamber ° is ensured, in particular in a range of 5 to 15 ° offset with respect to 180 ° phase offset. This results in the aforementioned advantages.

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

In the following, an aspect is specifically dealt with which relates to the device-related coupling of the chamber to the shafts, 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, when the measures are combined with regard to phase offset, with Measures based on a material-elastic link unit can be implemented. Vice versa, the optimization of the mill based on measures for material-elastic mounting of the chamber can be implemented in a particularly expedient manner by means of the measures described here with regard to phase offset, for example by setting a corresponding operating behavior in terms of control technology in mills with material-elastic articulation unit.

In the case of 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 link unit. This enables a movement-tolerant or position-tolerant connection of the grinding chamber to the eccentric shafts, whereby the operating behavior of the mill can be optimized.

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

A correspondingly desired damping can already be ensured by means of the material-elastic link unit (s) alone.

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

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

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

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

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

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

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

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

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

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

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

The balancing mass elements can also be stored via the eccentric shafts and move out of phase with the grinding unit. The balancing mass elements are optimally arranged on the level of the grinding vessel (grinding chamber), in particular in order to also be able to compensate for tilting moments. According to an advantageous variant, 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 embodiment, the material-elastic articulation unit couples the grinding chamber in at least one coupling point per eccentric shaft with movement tolerance to the respective eccentric shaft, in particular by means of a bearing receptacle for the arrangement of a bearing for the respective eccentric shaft, the at least one coupling point being offset in the circumferential direction with respect to an articulation point or force introduction point is arranged on the grinding chamber, in particular with an offset in the range of a circumferential angle of 30 ° to 120 °, in particular in an at least approximately tangential extent. This also makes it possible to provide advantageous technical bending properties.

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

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

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

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

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

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

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

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

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

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

According to one embodiment, the material-elastic link unit has a / the grinding chamber receptacle for the grinding chamber, which grinding chamber receptacle completely surrounds the grinding chamber in the circumferential direction, the Grinding chamber receptacle is preferably designed as a circular cross-section or as a cylindrical receptacle in the manner of a socket. As a result, a maximum areal force transmission with minimal pressure / tension peaks can be achieved.

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

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

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

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

Figure list

• 1A, 1B, 1C jeweils in schematischer Darstellung Kraftvektoren in einem Kräftediagramm bei unterschiedlichem Versatz, je nach Betriebszustand der Scheibenschwingmühlenvorrichtung;
• 2A, 2B, 2C, 2D in unterschiedlichen Ansichten jeweils eine Exzenterwelle zur Verwendung in einer Scheibenschwingmühlenvorrichtung gemäß einem Ausführungsbeispiel;
• 3 in einer perspektivischen Ansicht eine Scheibenschwingmühlenvorrichtung gemäß einem Ausführungsbeispiel;
• 4 eine Scheibenschwingmühlenvorrichtung in einer perspektivischen Gesamtansicht;
• 5 eine Ansicht auf eine Unterseite eines Mahlsystems einer Scheibenschwingm üh lenvorrichtung;
• 6A, 6B, 6C jeweils in einer perspektivischen Ansicht eine materialelastische Kopplung zwischen Exzenterwellen und Mahlkammer einer Scheibenschwingmühlenvorrichtung gemäß einem Ausführungsbeispiel;
• 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 emerge from the description of at least one exemplary embodiment on the basis of drawings and from the drawings themselves

• 1A , 1B , 1C each in a schematic representation of force vectors in a force diagram with a different offset, depending on the operating state of the vibrating disk mill device;
• 2A , 2 B , 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 disk mill device according to an embodiment;
• 4th a vibrating disk mill device in a perspective overall view;
• 5 a view of an underside of a grinding system of a Scheibenschwingm üh lenvorrichtung;
• 6A , 6B , 6C each in a perspective view of a material-elastic coupling between the eccentric shafts and the grinding chamber of a vibrating disk mill device according to an embodiment;
• 7A , 7B in a top view and in a perspective side view, a material-elastic link 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 with reference to an individual figure, reference is made to the other figures.

For the sake of easier understanding, the figures can initially be described together with reference to all reference symbols, at least in part. Details or special features shown in the respective figures are described individually.

The 1A , 1B , 1C illustrate different operating states, each depending on a phase offset ω , whereby a resulting force vector of a resulting imbalance is set individually in each case.

In 1A a vibration state that needs to be optimized is illustrated. The angle of rotation or phase offset ω13 of the grinding stone depends on the grinding conditions, in particular the load dependent. An operating state with a comparatively large residual imbalance is shown.
A force vector F1 the imbalance force of the grinding chamber points in a different direction than a force vector F2 the imbalance force of the millstone. A force vector F3 the imbalance force of the balancing mass unit points opposite to F1 (phase offset exactly 180 °).
The angle of rotation or phase offset ω13 of the millstone is plotted between F1 and F2.
Effect: A comparatively large / long force vector Fn for the residual unbalance.

In 1B a vibrational state that has been optimized in terms of vibration technology through phase offset optimization is illustrated. F3 points at an angle not equal to 180 ° opposite to F1 (phase offset, for example approx. 195 ° or 200 °; 1B is not exactly to scale).
The angle of rotation or phase offset ω16 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 according to the invention, in particular by changing the phase offset ω16 is / will be set accordingly.

In 1C illustrates another operating state in which a (comparatively small) residual imbalance still exists Fn is not leveled or is deliberately not readjusted, especially because of the phase offset of the millstone ω13 varies comparatively strongly. However, the phase shift is ω16 the balancing mass unit is selected according to the invention in such a way (here for the purpose of illustration corresponding to that phase offset in 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 normal operation of the mill over a predefined operating period, in particular for the purpose of specifying a single, predefined advantageous phase offset ω16 the balancing mass unit. This can also save time-consuming readjustment.
Effect: Depending on the size of the offset, the comparatively small / short force vector is Fn Aligned in a first or in a second opposite direction and ideally oscillates around a mean value zero with only a small deflection.

The 2A , 2 B , 2C , 2D show an eccentric shaft 15th in different views and configurations. In 7A it can be seen that individual cams each have a disc 15.1 include, which can be arranged with a predefinable offset or angle of rotation relative to the further cams or disks. The individual cams or discs can be connected, for example, by means of connecting means 15.2 Position (e.g. screw connections or fitting means) relative to one another.

The example of 2 shows a shaft with three cams. In particular, one of the cams interacts with the grinding chamber, and the other two cams are each coupled to one of two balancing mass units. It has been shown that a particularly advantageous operating behavior can be achieved if the middle cam couples the grinding chamber.

In 2 B the relative position of the individual cams or disks is further clarified. In particular, serial assembly of individual machine elements can be provided, in particular in such a way that the disks can optionally be retrofitted.

In 2C and 2D phase offsets of different sizes are illustrated. 2C illustrates an offset of 180 ° (identified as disadvantageous according to the invention). 2D illustrates an example of an offset of ± 20 ° (identified as advantageous according to the invention) with respect to the exactly opposite, opposite arrangement according to FIG 2C (180 °), corresponding to 200 °. Such an offset can therefore be implemented relatively between the cam for the chamber and the respective cam for the balancing mass unit (s), either permanently predefined or also adjustable during operation or during breaks or when the mill is reconfigured (optional readjustment).

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

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

In the 4th Vibrating disc mill device shown 10 includes a mill housing 11 , in which a grinding system 13 is arranged, which has a material task 12 Feed material can be supplied. The feed material is ground and can then be fed to a material discharge 19th can be removed. The grinding system arranged in between 13 includes a grinding chamber 13.1 with at least one millstone (not shown). An eccentric shaft drive 14th is on a plurality of eccentric shafts 15th coupled and drives at least one of the eccentric shafts 15th at. A balancing mass unit 16 with a plurality of balancing mass elements 16.1 serves to balance the masses.

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

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

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

The 4th shows a vibratory disk mill device 10 with a grinding system driven by eccentric shafts 13 .

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

The 6A , 6B , 6C show the arrangement of a material-elastic link unit 17th integrated between two balancing mass units 16 , 16.1 . Both the linkage unit 17th as well as the balancing mass units 16 are on the eccentric shafts 15th coupled. The three coupling material-elastic sections 17.3 each extend in the circumferential direction u over an angle α in the range from 60 to 100 °, in particular approx. 85 °. In 6A is also the inside diameter D13 .1 of the grinding chamber indicated, in particular defined by the inner walls of the grinding chamber on which the grinding stone rolls.

The 7A , 7B show the individual sections of an integral, massive one-piece material-elastic link unit 17th with arms that are flexible in the radial direction 17.3 . A grinding chamber holder is in the center 17.1 due to a comparatively rigid area 11/17 Are defined. The transitions between this materially rigid area 11/17 (or the articulation section 17.9 ) and the respective arms 17.3 are all rounded (especially areas 17.2 , 17.5 , 17.6 ). Further measures optimizing mass distribution or stress distribution or force flow can be implemented, for example, through the compensation hole shown 17.4 be ensured in the respective arm. The respective camp recording 17.7 is by an integral one-piece solid ring section 17.71 provided, the center of which is the coupling point 17.8 (Center of the eccentric shaft).

7B illustrates the comparatively small thickness z17 the link unit (disc-like design).

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

List of reference symbols

10

Vibrating disc mill device

11

Mill housing

12

Material feed

13th

Grinding system

13.1

Grinding chamber

14th

Eccentric shaft drive

15th

Eccentric shaft

15.1

Eccentric shaft disk or eccentric disk

15.2

Lanyard

16

Balancing mass unit

16.1

Balancing mass element

17th

material-elastic link unit

17.1

Grinding chamber mount

11/17

material stiff area

17.2

Transition to the grinding chamber holder

17.3

material elastic section, especially free arm

17.4

Compensation hole

17.5

Inner radius

17.6

Rounding off

17.7

Camp recording

17.71

Ring section

17.8

Coupling point

17.9

Articulation point or articulation section or center of an articulation section

18th

Bearings for eccentric shaft

19th

Material discharge

20th

Control / regulating device

21st

Measuring unit, in particular an acceleration sensor

F1

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

F2

Force vector imbalance force millstone

F3

Force vector imbalance force balancing mass unit

Fn

Force vector residual unbalance

D13.1

Inner diameter grinding chamber

D17.1

Diameter of the grinding chamber holder

d17

free length

r

radial direction

r1

radial distance of the bearing seat

u

Circumferential direction

z

Vertical direction or longitudinal direction (axial direction)

z17

Thickness of the link unit

α

Circumferential angle or offset in the circumferential direction

ω

Angle of rotation or phase offset (small omega)

ω13

Angle of rotation or phase offset of the millstone

ω16

Angle of rotation or phase offset compensation mass unit

Claims (18)

Vibrating disc mill device (10) for comminuting feedstock, in particular feedstock with a particle size of less than 20mm or less than 10mm, in particular set up for grinding the feedstock to particle sizes of less than 75 µm, with: a mill housing (11); - a grinding system (13) arranged in the mill housing such that it can vibrate, with a grinding chamber (13.1) and with at least one grinding stone arranged movably in the grinding chamber; -at least one eccentric shaft drive (14) mounted in the mill housing and generating the oscillating movement in the grinding chamber and at least two eccentric shafts (15), in particular at least two synchronously rotating eccentric shafts; -at least one balancing mass unit (16) coupled to the eccentric shaft drive set up to compensate for unbalance; characterized in that the balancing mass unit is coupled to the eccentric shaft drive in such a way that a phase offset greater than 180 °, in particular greater than 185 °, can be set between one / the eccentric maximum of the balancing mass unit and one / the eccentric maximum of the grinding chamber. Vibrating disc mill device according to Claim 1 , the phase offset being adjustable such that the maximum eccentric of the balancing mass unit (16) lags the maximum of the eccentric of the grinding chamber (13.1); and / or wherein the balancing mass unit (16) can be controlled as a function of the control of the eccentric shaft drive (14) in such a way that a phase offset in the range of 185 ° to 200 ° can be set. Vibrating disc mill device according to Claim 1 or 2 The control takes place in such a way that the regulated phase offset of the balancing mass unit (16) compensates for different relative positions of the at least one millstone relative to the maximum eccentric in part load and full load operation, in particular for the purpose of compensating for changes in operating conditions between idle and full load. Vibrating disk mill device according to one of the preceding claims, the phase offset of the balancing mass unit (16) being adjustable, in particular by at least one eccentric disk (15.1) being provided on at least one eccentric shaft (15), in particular an eccentric disk that can be positioned in the relative rotational position to the eccentric shaft. Vibratory disk mill device according to one of the preceding claims, wherein the phase offset of the balancing mass unit (16) in Can be regulated as a function of vibrations of the vibrating disk mill device (10), in particular by detecting accelerations in at least one spatial direction. Vibrating disc mill device according to one of the preceding claims, wherein the at least one grinding stone has a diameter of at least 50% of the inner diameter of the grinding chamber (13.1), in particular in the range from 60% to 85%. Vibrating disk mill device according to one of the preceding claims, the eccentric maximum of the grinding chamber (13.1) being at least 2% of the inner diameter of the grinding chamber, in particular in the range from 4% to 8%. Vibrating disc mill device according to 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. Vibrating disc mill device according to one of the preceding claims, wherein the at least one grinding stone has a diameter which is predefined by the inner diameter of the grinding chamber (13.1) minus a factor of 5 to 7 of the maximum eccentric of the grinding chamber. Vibratory disk mill device (10) according to one of the preceding device claims, the grinding chamber (13.1) being coupled to the eccentric shafts (15) by means of at least one material-elastic link unit (17). Vibratory disk mill device according to the preceding device claim, the material-elastic link unit being material-elastic by at least one section (17.3) that is flexibly mounted between the grinding chamber and the eccentric shafts, in particular flexurally elastic in the radial direction, in particular with a bending moment or a flexural rigidity which, in particular, in the radial direction ( r) is at least one power of ten smaller than the rigidity of the coupled force-carrying components; and / or wherein the material-elastic articulation unit (17) comprises or provides a grinding chamber receptacle (17.1), in particular in a one-piece, integral design, in particular in a central arrangement integrated in the material-elastic articulation unit; and / or wherein the material-elastic link unit is configured from a prefabricated semi-finished product, in particular in a completely solid configuration; and / or wherein the material-elastic link unit (17) couples the grinding chamber (13.1) in at least one coupling point (17.8) per eccentric shaft with movement tolerance to the respective eccentric shaft, in particular by means of a bearing receptacle for arranging a bearing for the respective eccentric shaft, the at least one The coupling point is arranged with an offset (a) in the circumferential direction in relation to an articulation 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 in at least an approximately tangential extent; and / or wherein the material-elastic link unit couples the grinding chamber in at least one coupling point per eccentric shaft by means of a material-elastic section in the form of a free arm (17.3) in a movement-tolerant manner to the respective eccentric shaft, the material-elastic arm being a one-piece, integral component of the material-elastic link unit, in particular in the embodiment as a bending beam-like material section; and / or wherein the material-elastic link unit has a / the grinding chamber receptacle (17.1) for the grinding chamber, which completely surrounds the grinding chamber in the circumferential direction, wherein the grinding chamber receptacle is preferably designed as a circular cross-section or as a cylindrical receptacle in the manner of a socket ; and / or wherein the material-elastic link unit is designed as a flat disk, in particular with a uniform thickness, in particular with a uniform thickness of both material-elastic sections / arms and of a / the grinding chamber receptacle of the material-elastic link unit. Method for the vibration control of a vibrating disk mill device (10) when comminuting feedstock, in particular feedstock with a particle size of less than 20mm or less than 10mm, in particular in a vibrating disk mill device according to one of the preceding claims, wherein the vibratory movement of the vibrating disk mill device by means of an eccentric shaft drive (14) comprising at least two Eccentric shafts (15) are produced in a vibratory grinding system (13) with a grinding chamber (13.1) and with at least one grinding stone arranged in the grinding chamber so that they can vibrate, an imbalance compensation being carried out by means of at least one balancing mass unit (16) coupled to the eccentric shaft drive; characterized in that the vibrational regulation of the vibratory movement takes place by regulating a phase offset between one / the eccentric maximum of the balancing mass unit (16) and one / the eccentric maximum of the grinding chamber (13.1), the phase offset being set to an amount greater than 180 °, in particular greater than 185 ° becomes. Method according to the preceding method claim, wherein the phase offset is set such that the eccentric maximum of the balancing mass unit (16) corresponds to the eccentric maximum lags behind 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. Method according to one of the preceding method claims, wherein the phase offset of the balancing mass unit (16) is predefined or actively regulated in such a way that different relative positions of the at least one millstone are compensated in part load and full load operation relative to the maximum eccentric, in particular for the purpose of compensating for changes in the operating state between idle and full load. Method according to one of the preceding method claims, wherein the balancing mass unit (16) is set in phase offset, in particular by at least one eccentric disk (15.1) being positioned or actively positioned on at least one eccentric shaft (15) in a relative rotational position to the eccentric shaft. Method according to one of the preceding method claims, wherein the phase offset of the balancing mass unit (16) is controlled as a function of vibrations of the vibrating disk mill device (10), in particular by detecting acceleration parameters in at least one spatial direction and evaluating them for the vibration control. Control / regulating device (20) set up to carry out a method according to one of the preceding method claims, the imbalance compensation being carried out by means of at least one balancing mass unit (16) coupled to the eccentric shaft drive (14) by creating a phase offset between the eccentric maxima of the balancing mass unit (16) and the grinding chamber (13.1) is set or actively regulated unequal to 180 ° with a phase difference of at least 5 ° or at least 10 ° in relation to a 180 ° phase offset, the control / regulating device being coupled in particular to at least one measuring unit (21) or this includes. Use of eccentric shafts (15) with a phase offset in a vibrating disk mill device, in particular in a vibrating disk mill device (10) according to one of the devices claims 1 to 11 , for setting an operating state that is optimized in terms of vibrations, the eccentric shafts on the one hand exciting a grinding chamber (13.1) with at least one millstone movably arranged in the grinding chamber, and the eccentric shafts (15) on the other hand exciting at least one balancing mass unit (16), the eccentric shafts in such a way to the The grinding chamber and the at least one balancing mass unit are coupled to ensure a phase offset between the eccentric maxima of the at least one balancing mass unit and the grinding chamber (13.1), regardless of the operating state or the current loading of the grinding chamber, unequal 180 °, in particular in a range from 5 to 15 ° offset in relation to 180 ° phase offset.

Images