Planetary mill and intermeshing toothed belt drive

Abstract

The invention relates to a laboratory scale planetary mill, sometimes also referred to as planetary ball mill, having obliquely inclined planetary shafts and a spatial or interleaved toothed belt drive and to a spatial or interleaved toothed belt drive for such a planetary mill or for other applications, wherein the toothed belt drive has non-parallel drive and output shafts.

Description

TECHNICAL FIELD

[0001] The present invention relates to a laboratory scale planetary mill, sometimes also referred to as planetary ball mill, in particular with obliquely inclined planetary axes and spatially or staggered toothed belt drive for driving the grinding stations or grinding cup receptacles, and to a spatially or staggered toothed belt drive for such a planetary mill or, if necessary, for other applications. BACKGROUND

[0002] Laboratory scale planetary ball mills are used for grinding samples, for example in process analysis. Planetary mills, sometimes also referred to as ball mills or planetary ball mills, are described, for example, in the patent applications DE 197 12 905 A1, DE 10 2006 006 529 A1, DE 10 2006 018 325 A1, DE 10 2006 047 481 A1, DE 10 2006 047 480 A1 and DE 10 2006 047 479 A1. In DE 10 2006 047 498 A1 a ball mill with a cooling device is described, wherein the cooling channels extend at least partially inside the bottom and / or the annular wall of the cup-shaped receptacle. More recent planetary mills are described, for example, in DE 10 2010 044 254 A1, DE 10 2012 009 983 A1, DE 10 2012 009 985 A1, DE 10 2012 009 982 A1, DE 10 2012 009 984 A1, DE 10 2012 009 987 A1. In addition, an overview of currently available laboratory scale planetary mills can be found on the applicant's website www.fritsch.de.

[0003]

[0004]

[0005]

[0006] In a planetary (ball) mill, the grinding cups as planet carriers are arranged eccentrically with respect to a sun axis (sometimes also referred to as central axis) and, on the one hand, are in rotational movement around the sun axis on a circular orbit and, on the other hand, are in rotational movement around their own axis, i.e. the eccentric planetary axis. By the rotational and the rotational movement of the grinding cups, varying centrifugal forces directed radially outwards are exerted on the grinding material loaded into the grinding cups. Typically, grinding bodies, for example grinding balls, are added to the grinding material, which crush the grinding material with high efficiency by impact action and friction action.

[0007] ​​​With a certain size of the rotating components and a certain rotational speed, flight trajectories for grinding material and grinding bodies can be generated in planetary ball mills. The grinding material and grinding bodies then move laterally through the grinding cup until they hit the inner wall of the grinding cup. Thereafter, the grinding material and grinding bodies can be carried over a distance on the inner circumference of the grinding cup until the resulting forces ensure the aforementioned lateral acceleration and the grinding material and grinding bodies perform a flight movement through the grinding cup. This is also referred to as "catapulting concept". If the ball mill works in the catapulting concept, particularly high grinding results can be achieved at high rotational speeds.

[0008] Planetary ball mills are characterized at least by a fast and efficient comminution. They can be used widely and are ideal for loss-free fine comminution up to the nanometer range. The grinding can be carried out dry, in suspension or under protective gas, depending on the requirements of the task. They are also very suitable for homogenizing emulsions and pastes or for mechanical alloying in materials research. However, this nanoscale comminution requires a relatively high energy requirement and can lead to undesired heating in the grinding material due to the grinding process. However, some substances are temperature-sensitive so that they cannot be comminuted in current planetary ball mills. Other substances can only be comminuted after embrittlement.

[0009] Usually, in planetary mills, the sun shaft and the planet shafts extend parallel. However, for specific applications, it can be desirable that the planet shafts are inclined with respect to the sun shaft, however, this can lead to significant design difficulties.

[0010] From EP 2 457 645 A1 a centrifuge is known, wherein the rotation axis of the container holder is inclined. The entire rotation device is arranged in a compartment, which is provided with cooling / heating tubes. The drive of the container holder is realized by a bevel gear transmission. An effective cooling of the grinding cup thus seems not possible. Furthermore, the drive device shown here appears complex, maintenance-intensive and unsmooth in operation. Furthermore, the rotating system has a large mass.

[0011] From US 7,744,027 B2 a planetary ball mill is known, wherein the cup is encircled in a ring made of an elastic material at the upper end of the cup and is placed in rotation frictionally by the friction between the cup and the encircling elastic ring. This drive device appears less reliable and can have a slip and a high wear. There is no synchronization and in fact the rotational speed and the power are considered to be strictly limited.

[0012] A centrifugal treatment device for stirring and defoaming is known from EP 2 722 088 B1. The drive is effected by means of a gear transmission which is located above the storage container. The construction appears to be complex, cost-intensive and to have a low running smoothness. Furthermore, the fixing of the container appears to be difficult and limits the accessibility to the container. This arrangement of the gear transmission appears to be disadvantageous in principle.

[0013] A stirring / emptying device is known from DE 11 2004 001 671 B4 which stirs and empties thoroughly kneaded objects by simultaneous rotation and revolution of the container, wherein the device comprises a tightly sealable container which is connected to a vacuum pump by means of a suction pipe. A second rotary drive comprises a reversing wheel and a pulley and a circular belt, wherein the pulley ratio is 1 : 1. A similar drive device with such a circular belt is shown in JP 2009-268955 A. The circular belt appears to be a special product which is cost-intensive and disadvantageous in terms of spare parts supply. Furthermore, such a drive device appears to be unsuitable for high power requirements. Furthermore, the drive device is designed as a 1 : 1 rotational speed ratio. Neither a speed increaser nor a speed reducer is provided or can be easily implemented. Furthermore, such a drive device appears to be susceptible to wear and the transmittable force appears to be small. Furthermore, it is considered that the rotational speed and the power are strongly limited, but this can be sufficient for the device, i.e. for stirring and emptying or kneading.

[0014] An effective cryogenic grinding or monitoring of the grinding process during operation appears to be hardly possible or completely impossible with any known device.

[0015] Furthermore, cryogenic vibration mills and cryogenic mills with magnetic drive are known, but they are only able to grind very small sample quantities and have insufficient grinding power. Furthermore, the magnetically driven mills have the disadvantage that the grinding is carried out with special magnetic plungers and the ground material should not be magnetic. SUMMARY

[0016] It is an object of the present application to provide a planetary mill with obliquely inclined planetary shafts whose drive avoids or at least mitigates the disadvantages mentioned at the outset.

[0017] A further aspect of the object is to provide a planetary mill with obliquely inclined planetary shafts which has a reliable synchronous drive between the carrier device as sun element and the grinding cup, which works without slip and largely uses commercially common construction elements.

[0018] Another aspect of the object is to provide a planetary mill with obliquely inclined planetary shafts, which has a synchronous drive between the carrier device as a sun element and the grinding cup, which operates smoothly, with low wear, robust and cost-effective, and by means of which a high grinding power can be achieved at the same time.

[0019] Another aspect of the object is to provide a planetary mill with obliquely inclined planetary shafts, which has a synchronous drive between the carrier device as a sun element and the grinding cup, wherein the drive of the grinding cup housing is directly carried out by the rotation of the carrier device, and the direct drive of the grinding cup housing directly combines the drive shaft and the output shaft, which extend obliquely to each other, and a transmission ratio or reduction ratio not equal to 1 into one and the same drive device, in particular with a unique drive element.

[0020] Another aspect of the object is to provide a synchronous transmission which operates smoothly, with low wear and reliably, which is suitable for spatially complex drive geometries, in particular with obliquely extending shafts and / or transmission or reduction devices, which extend obliquely, in common planes or twisted to each other.

[0021] Another aspect of the object is to provide a planetary mill, which can effectively and in particular durably cool the grinding stock during the grinding process.

[0022] Another aspect of the object is to provide a planetary mill, with which an undesired heating of the grinding stock during the grinding process can be prevented or at least reduced, for example in order to grind temperature-sensitive test samples with high quality and / or high grinding power, and preferably in order to be able to carry out a durable cryogenic grinding with the planetary mill, i.e. to provide a cryogenic planetary mill.

[0023] Another aspect of the object is to provide a planetary mill, which has a high grinding power and at the same time enables the observation and / or access to the interior of the grinding cup housing and / or the grinding cup during the rotation of the carrier device and the grinding cup housing, for example in order to be able to drip a liquid cryogenic cooling medium into the grinding cup or the grinding cup housing, or to be able to monitor the grinding process with a camera.

[0024] The object is achieved by the subject matter of the independent claims. Advantageous refinements of the application are defined in the dependent claims.

[0025] Planetary mill with toothed belt drive having non-parallel axes and staggered spaces

[0026] According to one aspect of the application, a laboratory-scale planetary mill, sometimes also referred to as planetary ball mill or laboratory planetary ball mill, comprises a carrier device as a sun element rotating about a sun axis and at least one grinding cup accommodation arranged axially offset on the carrier device with respect to the sun axis and rotating about a planet axis with respect to the carrier device. At least one grinding cup can be loaded into the grinding cup accommodation and clamped or locked therein, whereby it performs a combined rotational and gyroscopic motion. The grinding cup accommodation and the grinding cup clamped or locked therewith are in gyroscopic motion about the sun axis with the rotational speed of the carrier device and at the same time in rotational motion about their own axis, i.e. the planet axis.

[0027] The rotation of the carrier device as a sun element about the sun axis is driven by an electric drive motor, for example with a main drive belt. The rotation of the grinding cup accommodation about the planet axis is driven as a synchronous drive device by a toothed belt with respect to the carrier device in order to ensure a structurally fixedly defined rotational speed ratio between the sun rotation and the planet rotation. In contrast, the main drive belt for the carrier device does not necessarily need to be a synchronous belt, for example a wedge belt or a triangular rib belt or another enveloping drive can be used for this purpose, since a wedge belt or a triangular rib belt drive is inexpensive and can withstand slipping in this position. However, it should not be excluded that a toothed belt or a completely different drive is also used for the main drive belt.

[0028] The planetary mill has non-parallel rotational axes and obliquely inclined grinding cups, that is to say the grinding cup accommodation and the grinding cup clamped or keyed thereto and the planet axis are obliquely inclined with respect to the sun axis at an inclination angle, precisely preferably viewed from below or from the grinding cup bottom to the grinding cup opening, obliquely inwardly inclined, so that the opening of the grinding cup is closer to the sun axis than the bottom of the grinding cup. The planet axis and the sun axis run non-parallel to each other, in particular obliquely with respect to each other, in three-dimensional space. "Oblique" is understood here as meaning that the axes run non-parallel and not perpendicular to each other. "Oblique" in three-dimensional space includes on the one hand an inclination in a common plane, or on the other hand a twist but not perpendicular, i.e. non-parallel, not perpendicular and not intersecting in three-dimensional space.

[0029] In order to drive the planet axes inclined at an angle, the toothed-belt drive has a drive shaft and an output shaft which are not parallel to one another or a drive toothed-belt pulley and an output toothed-belt pulley which are not parallel to one another. The toothed-belt drive drives the grinding cup receptacle directly, in particular, so that no further transmission is required between the output toothed-belt pulley and the grinding cup receptacle in order to achieve the axial inclination in the planetary drive. In other words, the toothed belt transfers the rotational movement directly from the sun shaft to the inclined planet axes, wherein the output toothed-belt pulley is arranged coaxially to the planet axes or the grinding cup receptacle and is fixedly connected to the grinding cup receptacle. The toothed belt thus achieves the drive of the grinding cup receptacle and at the same time itself achieves the commutation of the rotational drive of the grinding cup receptacle to the angle of inclination of the grinding cup receptacle. To this end, the toothed belt extends interdigitated, in particular multiple times, between the sun shaft and the inclined planet axes.

[0030] Preferably, the central sun shaft is configured as a central main shaft, also referred to as central axis, which is fixedly connected to the housing, on which the carrier device is rotatably supported as a sun element, for example by means of a ball bearing. The drive toothed-belt pulley for the toothed-belt drive is preferably fixedly connected coaxially to the central shaft and thus positionally fixed relative to the device housing. The main output belt pulley is fixedly connected coaxially to the carrier device and is driven by the main drive belt, so that the carrier device rotates together with the drive toothed-belt pulley about the fixed central shaft. Here, the grinding station or the grinding cup receptacle supported in the carrier device spaced apart from the central shaft entrains about the fixed central shaft, so that the grinding station or the grinding cup receptacle revolves about the sun shaft. The toothed belt for driving the grinding station or the grinding cup receptacle to rotate is thus driven by the relative rotation of the carrier device relative to the drive toothed-belt pulley, which is fixed relative to the device housing, and in turn drives the output toothed-belt pulley, which is fixed on the grinding cup receptacle and is likewise inclined with the grinding cup receptacle, at a defined speed ratio. The rotation of the grinding cup receptacle is thus carried out by the synchronous drive by means of the toothed belt relative to the rotation of the carrier device, more precisely preferably in the opposite direction.

[0031] In an advantageous manner, a cost-effective, commercially common, commercially available toothed belt can be used to drive the grinding cup receptacle relative to the carrier device. The toothed belt constitutes a slip-free synchronous drive for the planetary rotation of the grinding cup receptacle relative to the sun rotation of the carrier device and at the same time accommodates the inclination of the planet axes or the grinding cup receptacle relative to the central shaft. Furthermore, with the planetary grinding machine a high grinding power and a narrow distribution width can be achieved. For example, an average particle size of up to <0.1 μιη can be achieved.

[0032] According to the definition customary in the art, a toothed belt (sometimes also referred to as synchronous belt or control belt in engine technology) is a drive belt with toothings that run in a form-fit manner in toothed pulleys. Toothed belts combine the properties of chains and flat belts. On the inner side of the toothed belt, teeth are formed that engage with a specific toothed belt pulley. As a material for the teeth, for example, elastomers such as rubber, chloroprene rubber, hydrogenated acrylonitrile butadiene rubber (HNBR [1]) or polyurethane can be considered. Toothed belts are particularly advantageous compared to wedge belts and flat belts, which work exclusively by force fit, since high forces can be transmitted with a small pretension and without slipping.

[0033] A toothed belt is understood here to be a commercially customary toothed belt with a plurality of flatly arranged side by side pull wires and an overall flat cross section, which is toothed transversely on one or both flat sides (single-sided toothed belt or double-sided toothed belt). The teeth engage in a form-fit manner into corresponding transverse grooves as drive toothed belt pulleys and output toothed belt pulleys and form a form-fit synchronous drive. The pull wires are typically composed of a plurality of flatly arranged side by side traction cords, for example steel cords, which are embedded in a base material, for example an elastomer or a polyurethane, and here form a load-carrying strip with a flat cross section. The teeth, which extend transversely to the pull wires, for example have a trapezoidal or semicircular cross section.

[0034] The toothed belt drive for the grinding station or grinding cup receptacle here is a so-called spatial or interlaced toothed belt drive. In the case of an interlaced toothed belt drive, the flat toothed belt extends interlaced in the return run between the toothed belt pulleys and optionally further rollers. This has the advantage that, on the one hand, the use of further drives, for example gearwheels for compensating shaft inclination, can be dispensed with and, on the other hand, the use of expensive and, if necessary, costly or easily worn or fragile special belts, by means of which small amounts of power can be transmitted, can be dispensed with. The toothed belt in particular does not have a rotationally symmetrical cross section and furthermore extends interlaced in order to compensate for shaft inclination in the drive and possible transmission ratios.

[0035] Such commercially customary (standardized) toothed belts are commercially available at many manufacturers, for example at Walther Flender (www.walther-flender.de), Optibelt (www.optibelt.com) or H. AG (www.hfag.ch) and possibly in accordance with certain standards, for example ISO 13050, DIN 7721 or ISO 5296. Here, for example, toothed belts T or HDT, for example HTD5, can be used. The use of commercially customary toothed belts has particular advantages in terms of costs, spare parts availability and reliability compared to special belts.

[0036] Furthermore, such an intermeshing direct "offset toothed-belt drive" operates smoothly, low-noise, with little wear and maintenance, is reliable, slip-free and durable.

[0037] The toothed-belt drive is thus in particular configured as an intermeshing toothed-belt drive. The drive toothed-belt pulley is preferably arranged coaxially with the sun shaft, and the output toothed-belt pulley is preferably arranged coaxially with the inclined planet shaft below the grinding cup receptacle and fixedly connected thereto, wherein the toothed belt extends at least once, preferably even multiply, intermeshingly between the drive toothed-belt pulley and the drive toothed-belt pulley, wherein the drive toothed-belt pulley and the output toothed-belt pulley are inclined obliquely relative to one another.

[0038] Preferably, the planet shaft or the output toothed-belt pulley is inclined relative to the drive toothed-belt pulley or the central shaft by an angle a of between 5°, if necessary 10°, to 75°, preferably between 25° and 60°, particularly preferably 37.5° + / - 10° or 37.5° + / - 5°.

[0039] Further preferably, the intermeshing toothed-belt drive with non-parallel shafts has a transmission ratio, and the output toothed-belt pulley, which is obliquely inclined relative to the drive toothed-belt pulley, has a smaller diameter than the drive toothed-belt pulley according to the transmission ratio, wherein the teeth are fewer.

[0040] Particularly preferably, the relative rotational speed ratio between the rotation of the carrier device and the grinding cup receptacle has a value in the range of 1 : 1.5 and 1 : 5. In this advantageous manner, a high grinding power of the planetary grinding machine can be achieved.

[0041] Preferably, the rotation of the carrier device and the grinding cup receptacle is counter-rotational, and the relative rotational speed ratio between the rotation of the carrier device and the grinding cup receptacle is in particular between 1 : -1.5 and 1 : -5. In particular, not only the transmission ratio but also the counter-rotation is generated directly by the toothed-belt drive with non-parallel shafts, i.e. by one and the same toothed belt, that is to say, the obliquely relative to one another inclined drive toothed-belt pulley and the output toothed-belt pulley of the toothed-belt drive for driving the inclined grinding cup receptacle rotate counter-rotational with one transmission ratio, in particular with a rotational speed ratio of 1 : -1.5 to 1 : -5.

[0042] It has been shown that, in particular by combining the counter-rotation of the planetary rotation of the grinding cup relative to the revolution around the sun shaft, the rotational speed ratio and / or the inclination, a high grinding power can be achieved, in particular when using grinding bodies, for example grinding balls, which leave the grinding cup wall and are thrown laterally through the grinding cup (projectile concept). The counter-rotational rotation is advantageously inherent to such a direct toothed-belt drive.

[0043] The planetary grinding machine can be configured as a single grinding machine, which has only one grinding cup receptacle which is inclined inwards as seen from below and upwards and one, in particular adjustable, counterweight. This has the advantage that the grinding cup can be arranged internally to such an extent that, due to the small spacing of the planetary shafts relative to the sun shaft and the combination of the inclination of the grinding cup, the grinding cup intersects the sun shaft at the upper end of the grinding cup or the grinding cup extension, if necessary, by means of the grinding cup extension. On the other hand, the bottom of the grinding cup is also remote from the sun shaft, so that the grinding cup bottom does not intersect the sun shaft. Thereby, a favourable dynamic situation can be achieved in rotation, with which a high grinding power and a synergistic combination of the cutting of the sun shaft by the grinding cup can be achieved. However, the planetary grinding machine can also be configured as a double planetary grinding machine with two opposite grinding stations or can also have further grinding stations, for example as a fourfold grinding machine, wherein some or all of the planetary shafts extend inclined relative to the sun shaft, respectively.

[0044] Preferably, the toothed belt drive for the grinding cup receptacle comprises a first and / or a second reversing roller with a first or second reversing roller shaft. The first and second reversing or tensioning rollers are preferably arranged on opposite sides of the toothed belt drive, i.e. the first reversing roller (toothed or non-toothed) is arranged on the slack return section side and the second reversing roller is arranged on the load return section side, or vice versa. With the reversing or tensioning rollers, which do not perform a driving function nor an output function, but only a reversing of the toothed belt, the toothed belt can be suitably reversed in order to compensate for the inclination of the driving and output toothed belt wheels and to distribute the stagger of the toothed belt on both sides of the reversing rollers

[0045] According to one preferred embodiment, the driving toothed belt wheel is thus arranged coaxially with the sun shaft and the output toothed belt wheel is arranged coaxially with the inclined planetary shaft and is fixedly connected with the grinding cup receptacle. The toothing of the toothed belt running on the driving toothed belt wheel and the output toothed belt wheel engages in a form-fitting manner into the toothing of the driving toothed belt wheel and the output toothed belt wheel, and as already implemented above, the toothed belt has a plurality of pull wires next to each other, which have a generally flat cross section with a toothed flat side (inner side) and a non-toothed or, if necessary, likewise toothed back side (outer side).

[0046] The cut-out of the toothed belt at the driving toothed belt wheel is in particular not parallel to the cut-in of the toothed belt at the output toothed belt wheel, and the toothed belt extends staggered therebetween. Furthermore, the cut-out of the toothed belt at the output toothed belt wheel is in particular not parallel to the cut-in of the toothed belt at the driving toothed belt wheel, and the toothed belt likewise extends staggered therebetween.

[0047] Furthermore, the first and the second reversing roller shafts extend, in particular, non-axially, preferably obliquely to one another, and / or at least one or both extend twisted and obliquely to the sun axis and / or at least one or both extend twisted and obliquely to the oblique planetary axis. Axes which extend "obliquely" to one another are understood here as meaning that the axes neither run parallel to one another nor perpendicular to one another, but obliquely, i.e. at an oblique angle to one another. The axes can extend obliquely to one another at an oblique angle in a common plane and intersect in this common plane, or extend obliquely and twisted in three-dimensional space. In the case of twisted axes, the angle or oblique position angle between the axes can be determined in a projection plane which extends perpendicular to the shortest connecting line between the twisted axes.

[0048] The oblique position angle of the first and / or the second reversing roller shafts relative to the sun axis and / or the planetary axis, or the oblique position angle of the midplane of the first and / or the second reversing roller relative to the midplane of the drive wheel and / or the output wheel, is between 1° and 89° or between 91° and 179°, respectively.

[0049] In other words, the slack run and the load run are each divided into two run sections by the first or the second reversing roller. The staggering of the toothed belt in the free run can advantageously be kept within reasonable limits, and a smooth running of the toothed belt drive can be achieved without the risk of the toothed belt "slipping off" the toothed belt wheels or the reversing rollers.

[0050] Further preferably, the toothed belt is staggered between the drive toothed belt wheel and the first reversing roller, between the first reversing roller and the output toothed belt wheel, between the output toothed belt wheel and the second reversing roller and / or between the second reversing roller and the drive toothed belt wheel, wherein the staggering is preferably less than 90°, in particular less than 60°, in particular less than 45°, in particular less than 30°, respectively.

[0051] According to one embodiment, the first reversing roller adjusts the angular deviation of the parallelism or coaxiality of the cut-out on the drive toothed belt wheel and the cut-in on the output toothed belt wheel in such a way that the first reversing roller deflects the action line of the toothed belt in three-dimensional space from the direction of the cut-out on the drive toothed belt wheel towards the direction of the cut-in on the output toothed belt wheel, and wherein the staggering of the toothed belt is distributed between the drive toothed belt wheel and the output toothed belt wheel, and / or the second reversing roller adjusts the angular deviation of the parallelism or coaxiality of the cut-out on the output toothed belt wheel and the cut-in on the drive toothed belt wheel in such a way that the second reversing roller deflects the action line of the toothed belt in three-dimensional space from the direction of the cut-out on the output toothed belt wheel towards the direction of the cut-in on the drive toothed belt wheel, and wherein the staggering of the toothed belt is distributed between the output toothed belt wheel and the drive toothed belt wheel.

[0052] Preferably, at least one, several or all of the following criteria are met:

[0053] the cut-out of the toothed belt at the drive toothed belt pulley and the cut-in of the toothed belt at the output toothed belt pulley,

[0054] the cut-out of the toothed belt at the output toothed belt pulley and the cut-in of the toothed belt at the second reversing roller,

[0055] the cut-out of the toothed belt at the first reversing roller and the cut-in of the toothed belt at the drive toothed belt pulley,

[0056] the cut-out of the toothed belt at the second reversing roller and the cut-in of the toothed belt at the drive toothed belt pulley

[0057] extend at an oblique angle to each other, i.e. at an angle which is not equal to 90° and not equal to 180° and not equal to a further multiple of 90°, however, wherein the angle is preferably smaller than 180°.

[0058] It is further preferred that the cut-out of the toothed belt at the drive toothed belt pulley and the cut-in of the toothed belt at the output toothed belt pulley and / or the cut-out of the toothed belt at the output toothed belt pulley and the cut-in of the toothed belt at the drive toothed belt pulley extend at an oblique angle to each other, i.e. at an angle which is not equal to 90° and not equal to 180° and not equal to a further multiple of 90°, however, wherein the angle is preferably smaller than 180°.

[0059] According to one preferred embodiment, at least one, several or all of the following criteria are met:

[0060] the cut-out of the toothed belt at the drive toothed belt pulley extends coaxially with respect to the cut-in of the toothed belt at the first reversing roller and the toothed belt is interleaved between the drive toothed belt pulley and the first reversing roller,

[0061] the cut-out of the toothed belt at the first reversing roller extends coaxially with respect to the cut-in of the toothed belt at the output toothed belt pulley and the toothed belt is interleaved between the first reversing roller and the output toothed belt pulley,

[0062] the cut-out of the toothed belt at the output toothed belt pulley extends coaxially with respect to the cut-in of the toothed belt at the second reversing roller and the toothed belt is interleaved between the output toothed belt pulley and the second reversing roller,

[0063] the cut-out of the toothed belt at the second reversing roller extends coaxially with respect to the cut-in of the toothed belt at the drive toothed belt pulley and the toothed belt is interleaved between the second reversing roller and the drive toothed belt pulley.

[0064] The first and / or second reversing roller shaft preferably extends torsionally and in particular not perpendicularly to the drive toothed belt pulley shaft and / or the output toothed belt pulley shaft.

[0065] It is further preferred that the drive toothed-belt pulley shaft and the output toothed-belt pulley shaft extend obliquely relative to one another in a common plane and intersect in this common plane, and that the shaft of the first and / or second deflection roller does not run parallel, in particular obliquely, relative to the common plane of the drive toothed-belt pulley shaft and the output toothed-belt pulley shaft and, in particular, intersects this plane.

[0066] With the aforementioned preferred features, the geometrically desired structural relationships for a planetary mill with obliquely inclined planetary shafts can be realized in an advantageous manner.

[0067] Preferably, at least one of the deflection rollers, namely the first and / or second deflection roller, is arranged on the toothed side inside the toothed belt and deflects the toothed belt outward away from the connecting line of the drive toothed-belt pulley and the output toothed-belt pulley or away from the common plane of the drive pulley axis and the output pulley axis and / or deflects the toothed belt obliquely downward relative to an imaginary connecting line between the midpoints of the drive toothed-belt pulley and the output toothed-belt pulley.

[0068] According to a preferred structural form of the planetary mill drive, the toothed-belt drive comprises a holding cross with intersecting arms, wherein the drive toothed-belt pulley, the output toothed-belt pulley and the first and second deflection rollers are each rotatably supported on opposite ends of the intersecting arms of the holding cross. In an advantageous manner, a stable holding structure for the interleaved toothed-belt drive can be thus provided.

[0069] Preferably, the spatial arrangement of the drive toothed-belt pulley and the output toothed-belt pulley and the first and second deflection rollers has a convex, rounded quadrilateral shape that bends in space around the connecting line of the first and second deflection rollers at an oblique angle, in particular without turning over.

[0070] It has proven advantageous for the planetary mill that the spatial arrangement consisting of the drive toothed-belt pulley and the output toothed-belt pulley and the first and second deflection rollers is mirror-symmetrical relative to the common plane of the drive toothed-belt pulley shaft and the output toothed-belt pulley shaft. Particularly preferably, the arrangement here has a rounded kite quadrilateral shape that bends in space around the connecting line of the first and second deflection rollers at an oblique angle. In this respect, it is also referred to herein as a "spatially bent quadrilateral toothed-belt drive".

[0071] One aspect of the present application also relates to a laboratory device having non-parallel rotational axes, comprising:

[0072] a carrier device rotatable about a sun axis,

[0073] at least one cup receptacle for accommodating a cup, wherein the cup receptacle is arranged on the carrier device in axial offset to the sun axis and can be rotated relative to the carrier device about the planetary axis,

[0074] a drive device for driving the rotation of the carrier device and the cup receptacle, wherein the rotation of the cup receptacle is driven synchronously relative to the rotation of the carrier device by means of a toothed-belt drive,

[0075] and, if necessary, further features of the planetary mill described herein,

[0076] wherein the planetary axis extends non-parallel to the sun axis, and

[0077] wherein the toothed-belt drive has a non-parallel drive shaft and output shaft.

[0078] Although the interlaced toothed-belt drive disclosed herein was developed specifically as a synchronous drive for a cup receptacle of a planetary mill having a bevelled planetary axis, it has been shown that such an interlaced toothed-belt drive, which has a very special tilted arrangement of toothed-belt pulleys or shafts, if necessary, can also be applied in other fields of drive technology. One aspect of the present disclosure therefore relates to an interlaced toothed-belt drive of this type independent of its particularly advantageous use in a planetary mill having a bevelled planetary axis. On the other hand, further embodiments and alternative features of the particularly bevelled interlaced toothed-belt drive are also disclosed below, which can in principle be combined with the features of a toothed-belt drive for a planetary mill and vice versa.

[0079] Toothed belt drive with non-parallel axes and staggered spaces

[0080] According to one aspect of the present invention, a particular toothed-belt drive is proposed, which has non-parallel shafts and an interlacing in the toothed belt. In line with the understanding of the person skilled in the art, a toothed belt is understood to be a toothed belt having a plurality of pull wires embedded next to one another in plastic, which has an overall flat cross section, which is provided on one or both flat sides with teeth transversely to the circumferential direction in order to be positively engaged into corresponding grooves of toothed-belt pulleys, as has been set out above. The interlacing of the toothed belt in this case means that the entirety of the pull wires of the toothed belt are twisted helically along their running direction.

[0081] The interlaced toothed-belt drive here comprises:

[0082] as a first toothed belt pulley, which is a drive toothed belt pulley, having a first toothed belt pulley midplane and a first toothed belt pulley axis extending perpendicular to the first toothed belt pulley midplane, and as a second toothed belt pulley, which is an output toothed belt pulley, having a second toothed belt pulley midplane and a second toothed belt pulley axis extending perpendicular to the second toothed belt pulley midplane, or vice versa,

[0083] a toothed belt running on the first and second toothed belt pulleys and having its toothing engaged in a form-fitting manner in the toothing of the first and second toothed belt pulleys, and

[0084] a first reversing pulley having a first reversing pulley axis and a second reversing pulley having a second reversing pulley axis, wherein the first and second reversing pulleys can be toothed or toothless respectively and are arranged on opposite sides of the toothed belt drive, that is to say the first reversing pulley is arranged on the slack run side of the toothed belt drive and the second reversing pulley is arranged on the load run side,

[0085] wherein the first and second toothed belt pulley axes extend non-parallel to one another and preferably form an angle of more than 5°, in particular more than 10°, in particular more than 20°,

[0086] wherein the cut-out of the toothed belt at the first toothed belt pulley extends non-parallel to the cut-in of the toothed belt at the second toothed belt pulley and the cut-out of the toothed belt at the second toothed belt pulley extends non-parallel to the cut-in of the toothed belt at the first toothed belt pulley,

[0087] wherein the toothed belt runs in four runs,

[0088] between the first toothed belt pulley and the first reversing pulley,

[0089] between the first reversing pulley and the second toothed belt pulley,

[0090] between the second toothed belt pulley and the second reversing pulley, and

[0091] between the second reversing pulley and the first toothed belt pulley, respectively, in a staggered manner, and

[0092] wherein at least one, several or all of the following criteria are met:

[0093] i) the first reversing pulley axis 144 extends obliquely with respect to the first toothed belt pulley midplane 36a,

[0094] ii) the first reversing pulley axis 144 extends obliquely with respect to the second toothed belt pulley midplane 42a,

[0095] iii) the second reversing roller shaft 146 extends obliquely with respect to the first toothed belt pulley midplane 36a,

[0096] iv) the second reversing roller shaft 146 extends obliquely with respect to the second toothed belt pulley midplane 42a,

[0097] v) the first and second reversing roller shafts 144, 146 extend non- coaxially with respect to one another.

[0098] Preferably, at least one, several or all of the aforementioned criteria i) to iv) and criterion v) are met. Preferably, at least two of the aforementioned criteria i) to iv) and criterion v) are met.

[0099] Here, oblique is to be understood as an oblique angle, that is to say an angle which is neither parallel nor perpendicular, that is to say an angle which is not equal to 0°, not equal to 90° and not equal to 180° and not equal to any other multiple of 90°, wherein the deviation is greater than the usual tolerances. For example, the deviation of the oblique angle from a multiple of 0° or 90° can be, for example, greater than or equal to 1°, preferably greater than or equal to 2°, preferably greater than or equal to 3°, that is to say the oblique angle can be, for example, between 1° and 89° or between 91° and 179°, preferably between 2° and 88° or between 92° and 178°, preferably between 3° and 87° or between 93° and 177°.

[0100] Preferably, both the first and the second reversing roller are arranged on the toothed side within the interior of the toothed belt and deflect the toothed belt outwardly away from an imaginary connecting line between the centre points of the first and second toothed belt pulleys, respectively, or away from the other reversing roller, respectively, wherein, inter alia, a kite-shaped quadrilateral is produced.

[0101] Alternatively, the first reversing roller is arranged on the toothed side in the interior of the toothed belt and deflects the toothed belt outwardly, that is to say away from the connecting line of the first and second toothed belt pulleys or away from the second reversing roller, and the second reversing roller is arranged on the back of the toothed belt outside the toothed belt and deflects the toothed belt inwardly, that is to say towards the first reversing roller, or vice versa. This arrangement can also be referred to as a Knie-in-Knie arrangement.

[0102] With both arrangements, it is possible to increase the length of the return section in order to limit the transverse forces and to keep the skew of the toothed belt within the permissible limit values.

[0103] The minimum ratio between the shaft spacing C and the toothed belt width b can thus be kept at least 5:1 for a skew of 90° in both arrangements, wherein the minimum ratio can likewise be reduced accordingly for a skew of less than 90°. In an advantageous manner, the transverse forces can thus be kept within the permissible limits.

[0104] The first and second toothed belt pulley shafts extend especially obliquely, i.e. at an oblique angle to each other.

[0105] Preferably, the first and second toothed belt pulley shafts extend as follows:

[0106] i) the first and second toothed belt pulley shafts extend non-parallel in a common plane and intersect in the common plane, and the first and second toothed belt pulley have different sizes, so that a transmission ratio or a reduction ratio is produced, or

[0107] ii) the first and second toothed belt pulley shafts extend obliquely to each other in a common plane and intersect in the common plane at an oblique angle, or

[0108] iii) the first and second toothed belt pulley shafts extend twisted and non- perpendicular to each other.

[0109] Preferably, the angle between the first and second toothed belt pulley shafts or between the first and second toothed belt pulley midplanes is between 5° and 85° or between 175° and 95°, especially between 10° and 80° or between 170° and 100°, especially between 25° and 75° or between 155° and 105°, especially between 25° and 50° or between 155° and 130°.

[0110] A twisted arrangement can thus even be realized. In the case of a twisted shaft, the angle between the shafts can be determined, for example, between the projections of these shafts in a projection plane which extends perpendicular to the shortest connecting line between the two twisted shafts.

[0111] Furthermore, especially at least one, several, especially at least two or all of the following criteria are met:

[0112] the first reversing roller shaft extends twisted and non-perpendicularly with respect to the first toothed belt pulley shaft,

[0113] the first reversing roller shaft extends twisted and non-perpendicularly with respect to the first toothed belt pulley shaft,

[0114] the second reversing roller shaft extends twisted and non-perpendicularly with respect to the first toothed belt pulley shaft,

[0115] the second reversing roller shaft extends twisted and non-perpendicularly with respect to the first toothed belt pulley shaft,

[0116] Twisted and non-perpendicular is to be understood as two shafts which extend twisted with respect to each other in three-dimensional space and whose projections in a projection plane which extends perpendicular to the shortest connecting line between the twisted shafts extend non-perpendicularly or at an oblique angle to each other.

[0117] The toothed-belt drive can additionally or alternatively be implemented with a transmission ratio or reduction ratio, i.e. a transmission ratio / reduction ratio not equal to 1:1, in which the first toothed-belt pulley as drive toothed-belt pulley has a larger or smaller diameter than the second toothed-belt pulley as output toothed-belt pulley, or vice versa.

[0118] The cut-out of the toothed belt on the first toothed-belt pulley extends obliquely, in particular in a common plane, with respect to the cut-in of the toothed belt on the second toothed-belt pulley, and / or the cut-in of the toothed belt on the first toothed-belt pulley extends obliquely, in particular in a common plane, with respect to the cut-out of the toothed belt on the second toothed-belt pulley.

[0119] By means of the moving reversing rollers in the structure, the interlacing in the separate return sections can be reduced, whereby, on the one hand, a synergistic combination of the reversing and adaptation of the angle of inclination is achieved, and, on the other hand, a compact structural approach is achieved. Here, the interlacing of the toothed belt in the following return sections is less than 90°, in particular less than 45°, respectively,

[0120] Between the first toothed-belt pulley and the first reversing roller,

[0121] Between the first reversing roller and the second toothed-belt pulley,

[0122] Between the second toothed-belt pulley and the second reversing roller and / or

[0123] Between the second reversing roller and the first toothed-belt pulley.

[0124] The first reversing roller adjusts the angular deviation of the parallelism or coaxiality of the cut-out and cut-in on the first toothed-belt pulley or the second toothed-belt pulley, in particular in such a way that the first reversing roller deflects the action line of the toothed belt in three-dimensional space from the direction of the cut-out on the first toothed-belt pulley towards the direction of the cut-in on the second toothed-belt pulley, and wherein the interlacing of the toothed belt is distributed between the cut-out of the first toothed-belt pulley and the cut-in of the second toothed-belt pulley, and / or the second reversing roller adjusts the angular deviation of the parallelism or coaxiality of the cut-out and cut-in on the second toothed-belt pulley or the first toothed-belt pulley, in particular in such a way that the second reversing roller deflects the action line of the toothed belt in three-dimensional space from the direction of the cut-out on the second toothed-belt pulley towards the direction of the cut-in on the first toothed-belt pulley, and wherein the interlacing of the toothed belt is distributed between the cut-out of the second toothed-belt pulley and the cut-in of the first toothed-belt pulley.

[0125] Here, in particular at least one, several or all of the following criteria are met:

[0126] The cut-out and cut-in of the toothed belt on the first toothed-belt pulley,

[0127] the cut-out of the toothed belt on the second toothed belt wheel and the cut-in of the toothed belt on the second deflection roller,

[0128] the cut-out of the toothed belt on the first deflection roller and the cut-in of the toothed belt on the second toothed belt wheel,

[0129] the cut-out of the toothed belt on the second toothed belt wheel and the cut-in of the toothed belt on the second deflection roller,

[0130] extend at an oblique angle to each other, i.e. at an angle which is not equal to 90°, not equal to 180° and not equal to a further multiple of 90°, however, the angle is preferably less than 180°, respectively.

[0131] It is further preferred that the cut-out of the toothed belt on the first toothed belt wheel and the cut-in of the toothed belt on the second toothed belt wheel and / or the cut-out of the toothed belt on the second toothed belt wheel and the cut-in of the toothed belt on the first toothed belt wheel extend at an oblique angle to each other, i.e. at an angle which is not equal to 90°, not equal to 180° and not equal to a further multiple of 90°, however, the angle is preferably less than 180°, respectively.

[0132] It is preferred that at least one, several or all of the following criteria are met:

[0133] the cut-out of the toothed belt at the first toothed belt wheel and the cut-in of the toothed belt at the first deflection roller extend coaxially and the toothed belt is interlaced between the first toothed belt wheel and the first deflection roller,

[0134] the cut-out of the toothed belt at the first deflection roller and the cut-in of the toothed belt at the second toothed belt wheel extend coaxially and the toothed belt is interlaced between the first deflection roller and the second toothed belt wheel,

[0135] the cut-out of the toothed belt at the second toothed belt wheel and the cut-in of the toothed belt at the second deflection roller extend coaxially and the toothed belt is interlaced between the second toothed belt wheel and the second deflection roller,

[0136] the cut-out of the toothed belt at the second deflection roller and the cut-in of the toothed belt at the first toothed belt wheel extend coaxially and the toothed belt is interlaced between the second deflection roller and the first toothed belt wheel.

[0137] It is preferred that the first deflection roller shaft and the second deflection roller shaft extend non-coaxially, in particular obliquely.

[0138] According to a preferred embodiment, the first deflection roller shaft and the second deflection roller shaft extend obliquely relative to each other in a common plane and intersect in the common plane.

[0139] It is further preferred that the first and second toothed pulley shafts not only extend obliquely relative to each other in a common plane and intersect in this common plane, but that the space arrangement made up of the first and second toothed pulleys and the first and second deflection rollers is additionally mirror-symmetrical relative to this common plane of the first and second toothed pulley shafts, so that this arrangement has the shape of a rounded kite-shaped quadrangle that is bent in space, among other things.

[0140] According to one exemplary embodiment, a third and a fourth deflection roller are arranged on one side of the belt drive, wherein the first or second deflection roller and the third and fourth deflection rollers are arranged next to each other and have parallel shafts and / or lie in a common plane, and wherein the toothed belt runs without interleaving between these deflection rollers lying in a common plane. Here, the one in the middle of the three deflection rollers lying in a common plane, for example the third or fourth deflection roller, can be a tensioning roller that is linearly movable in this common plane.

[0141] Planetary mill with cooling device

[0142] According to another aspect of the application, the planetary mill comprises:

[0143] a carrier device that is rotatable about a sun axis as a sun element,

[0144] at least one grinding station having a grinding cup receptacle for inserting a grinding cup, wherein the grinding cup receptacle is arranged on the carrier device axially offset from the sun axis and is rotatable about a planet axis relative to the carrier device,

[0145] a drive motor for driving the rotation of the carrier device and the grinding cup receptacle, so that the grinding cup receptacle and the grinding cup that can be inserted into the grinding cup receptacle run through a combined orbital and rotational trajectory in operation, and

[0146] a cooling device having a cooling medium line and a cooling medium metering opening for metering cooling medium into the grinding cup receptacle and / or into the grinding cup inserted into the grinding cup receptacle.

[0147] In this way, the grinding stock can be actively and metered cooled during rotation in an advantageous manner, and in particular low-temperature grinding can be achieved. Low-temperature grinding is suitable, for example, for grinding foodstuffs, powder coatings, additives in viscosity control, polymers, in particular thermoplastic plastics, or in tire recycling.

[0148] For example, in the case of thermoplastic resins, excessively high processing temperatures in a planetary ball mill can lead to problems with the particle size being outside the specification. In the recycling process, for example, un-specified and post-industrial waste of thermoplastic plastics is reprocessed and other compounds are added as fillers in order to improve the toughness and strength properties of the resin matrix. This process requires uniform fine particles. Variations in the particle size can therefore affect the efficiency of the process. When the processing temperature is raised in an undesirable manner, the production rate also decreases. If the temperature becomes too high, the resin can even partially melt and clog the mill. These problems can also be avoided with the present application.

[0149] In particular, the cooling medium is metered from above into the grinding cup accommodation and / or into the grinding cup inserted into the grinding cup accommodation during rotation of the carrier device and the grinding cup accommodation, so that the metering can take place with the aid of gravity, if necessary.

[0150] Here, the cooling medium metering opening is preferably arranged above the carrier device, and the cooling medium is guided through the cooling medium line to the cooling medium metering opening above the carrier device and flows out of the cooling medium metering opening into the cavity above the rotating carrier device during rotation of the carrier device and the grinding cup accommodation and then enters from above into the rotating grinding cup accommodation and / or into the rotating grinding cup.

[0151] Thus, in an advantageous manner, the cooling medium does not need to be guided through the carrier device from below through complex rotary channels, ring distributors, etc., but can be metered directly from above into the grinding cup accommodation and / or the grinding cup, despite the swiveling and rotating movement.

[0152] It is furthermore advantageous that the cooling medium line and the cooling medium metering opening can be arranged positionally fixed relative to the device housing of the planetary mill and do not co-rotate with the carrier device or the grinding cup accommodation, which significantly simplifies the delivery of the cooling medium.

[0153] In particular, a grinding cup having a grinding cup interior is inserted into the grinding cup accommodation, and in operation, that is to say during rotation of the carrier device and the grinding cup accommodation, the grinding stock is comminuted in the grinding cup interior, preferably with the aid of grinding bodies, for example grinding balls, grinding chips or grinding rings. Thus, a device for grinding, that is to say for finely comminuting grinding stock, is concerned, and not only a mixing or degassing device, etc. Here, the cooling medium is metered from above from the cooling medium metering opening into the grinding cup interior and / or into the gap between the wall of the grinding cup accommodation and the grinding cup during rotation of the carrier device and the grinding cup accommodation.

[0154] By dropping the cooling medium into the grinding cup, direct cooling of the grinding sample and grinding bodies during the comminution process can be achieved. This direct cooling is particularly effective, since the grinding bodies, for example grinding balls, can reach very high temperature peaks on the point of impact (projectile concept) of up to 600°C, if necessary, and can likewise be directly cooled there. When the cooling medium is not allowed to come into contact with the grinding stock, for example in order to avoid contamination of the grinding stock, it is particularly advantageous for the cooling medium to be dripped from above into the gap between the grinding cup and the grinding cup receptacle. Nevertheless, effective external cooling of the grinding cup can also always be achieved.

[0155] Preferably, the grinding cup receptacle and / or the grinding cup insertable into the grinding cup receptacle has a dosing opening on its respective upper axial end, and the cooling medium dosing opening is at least temporarily directly located vertically above the dosing opening during rotation of the carrier device and the grinding cup receptacle, so that the cooling medium can automatically, inter alia. by means of gravity, reach downward into the dosing opening, in particular fall, drip, flow and / or spray. This includes, for example, the advantage that the cooling medium can be dosed finely.

[0156] Furthermore, in a grinding cup receptacle which is inclined inwardly and obliquely from below to above or in an obliquely inwardly inclined grinding cup, the cooling medium is accelerated toward the bottom of the grinding cup receptacle or the grinding cup due to the component of the centrifugal force generated by the rotation of the carrier device which acts axially with respect to the inclined planetary shaft, which is significantly stronger than gravity.

[0157] Preferably, the planetary grinding mechanism is configured as a cryogenic planetary grinding machine and the cooling medium dosing opening is configured as a nozzle and the cooling medium is a liquid refrigerant. The liquid refrigerant can flow, drip and / or spray from the nozzle into the grinding cup receptacle and / or the grinding cup insertable into the grinding cup receptacle, which also enables precise dosing.

[0158] The liquid refrigerant has a boiling point far below room temperature and reaches the grinding cup receptacle and / or the grinding cup insertable into the grinding cup receptacle in a preferably liquid cryogenic state during rotation of the carrier device and the grinding cup receptacle. There it can evaporate and the gas formed there can escape into the ambient air through openings in the grinding cup receptacle and / or the grinding cup. Thereby a large amount of heat can be removed from the grinding station in a dosed manner, if necessary including the energy of the phase change, that is to say the cooling device has a high and dosable cooling power.

[0159] Preferably, the liquid refrigerant in liquid state is dosed into the interior of the grinding cup and remains there at least temporarily in a liquid aggregate state, so that at least temporarily a wet grinding, i.e. a cryogenic wet grinding, by the liquid refrigerant takes place.

[0160] The liquid refrigerant particularly preferably comprises liquid nitrogen or consists substantially of liquid nitrogen only.

[0161] Liquid nitrogen has a boiling point of 77 K at standard pressure and is particularly suitable for grinding materials which are otherwise difficult to grind, such as, for example, some thermoplastics, polyolefins and some biological samples or spices, etc.

[0162] Furthermore, since nitrogen does not support combustion, it can contribute to making the grinding safer. Nitrogen is inert and does not react with other materials or hardly reacts with other materials under normal conditions. Thus, with liquid nitrogen, in particular, undesirable reactions with the grinding stock, the grinding bodies and / or the material of the grinding cup receptacle or the grinding cup can be avoided.

[0163] Furthermore, liquid nitrogen does not form carbonic acid on contact with water, so that the pH value of the grinding stock is not changed in an undesirable manner even on direct contact.

[0164] Cryogenic grinding, in particular with the heat generated in the grinding process being conducted away using liquid nitrogen, can achieve, for example, a finer, more uniform particle size distribution and a higher production quantity in many products compared to conventional grinding methods. This can be applicable, for example, to adhesives, waxes, carpets, colour concentrates, pigments, composites, granules, pharmaceuticals, plastics, powder coatings, metals, multi-component materials, rubbers, spices and herbs.

[0165] According to an embodiment, a temperature sensor for measuring the temperature of the grinding cup receptacle, of the grinding cup and / or directly of the grinding stock and / or of the grinding bodies can be included. The temperature sensor can be arranged, for example, on the grinding cup receptacle and / or on a grinding cup which can be inserted into the grinding cup receptacle or be configured as a contactless temperature sensor, for example an infrared sensor which is directed into the grinding cup receptacle or into the grinding cup. In an advantageous manner, the temperature can thus be monitored directly in the region of the grinding cup and / or at the grinding cup receptacle. The transmission of the measured values of the rotating planetary system can be achieved, for example, by a wireless radio connection.

[0166] According to a further preferred embodiment, the planetary grinding mill comprises an electronic control device with a user interface. The user can set the operating parameters which are currently customary for the planetary grinding mill, for example, by means of the user interface, for example a touch display, such as setting the rotational speed and / or the grinding duration. In an advantageous manner, the user can now control the cooling, for example by means of the cooling medium flow, by means of the user interface. For example, in a simple control, an interval of opening times can be set for the cooling medium valve. In the case of active temperature regulation, a setpoint value for the desired grinding temperature can be set, in particular in the cryogenic range.

[0167] Certain ground materials, such as spices, are especially temperature sensitive. The heat generated during grinding can cause the spices to lose their volatile oils, which can impair the quality of the spices by making them less aromatic and less flavorful, and can change their color. If the spices are not handled at sufficiently low temperatures, the oils and fats in the spices can cause clumping and can even clog the grinder. Control of the cooling and the operating temperature, for example by means of control of the flow of the liquid refrigerant, can help to avoid these problems.

[0168] Preferably, the control device comprises a regulating loop, wherein the temperature measured by the temperature sensor is fed back as an actual value and compared to a setpoint value, and wherein the regulating loop actively regulates the temperature on the grinding cup receptacle and / or the grinding cup in such a way that the control device uses the amount of liquid refrigerant delivered to the cooling medium metering opening via the cooling medium line as a regulating value. Thus, the temperature can be actively and precisely regulated in an advantageous manner to the low-temperature temperature setpoint value preselected by the user.

[0169] Preferably, the grinding cup receptacle and / or the grinding cup inserted into the grinding cup receptacle has a metering-in opening at the axial end of the upper portion, and the cooling medium metering opening is centrally arranged above the carrier device in the region of the sun axis. In particular, the grinding cup receptacle and / or the grinding cup inserted into the grinding cup receptacle intersects the sun axis, so that the metering-in opening is vertically below the cooling medium metering opening in each arbitrary rotational position of the carrier device and the grinding cup receptacle. Thereby, at any time during the rotation of the carrier device and the grinding cup receptacle, cooling medium can be metered into the grinding cup receptacle and / or into the grinding cup from the cooling medium metering opening through the axial metering-in opening by gravity, in particular vertically from above, in particular the cooling medium can flow, drip or spray from above through the axial metering-in opening.

[0170] According to one preferred embodiment, the planetary grinder comprises the following first and second grinding cup variants:

[0171] i) the first grinding cup variant intersects the sun axis when inserted into the grinding cup receptacle and has an axial metering-in opening of the upper portion, wherein the metering-in opening is vertically below the cooling medium metering opening in each arbitrary rotational position of the carrier device and the grinding cup receptacle, and cooling medium is introduced into the interior of the grinding cup through the metering-in opening, so that at any time during the rotation of the carrier device and the grinding cup receptacle cooling medium can be metered from the cooling medium metering opening into the interior of the grinding cup through the axial metering-in opening.

[0172] ii) The second grinding cup variant does not itself intersect the sun axis when it is inserted into the grinding cup receptacle, but only the grinding cup receptacle intersects the sun axis. In this second grinding cup variant, moreover, there is a gap between the radial circumferential wall of the grinding cup and the grinding cup receptacle at least, and the grinding cup receptacle has an axial metering opening, wherein the metering opening is located vertically below the cooling medium metering opening in each arbitrary rotational position of the carrier device and the grinding cup receptacle, and cooling medium is introduced into the gap through the metering opening, so that cooling medium can be metered from the cooling medium metering opening into the gap through the axial metering opening at any time during the rotation of the carrier device and the grinding cup receptacle.

[0173] Here, the user can choose between the first and second grinding cup variants, and depending on which of the two grinding cup variants is inserted into the grinding cup receptacle, either the cooling medium can be metered into the interior of the grinding cup (first grinding cup variant) or into the gap between the grinding cup and the grinding cup receptacle (second grinding cup variant), depending on whether the grinding stock should come into direct contact with the cooling medium.

[0174] The planetary mill thus comprises a grinding cup set, which comprises both, the first and second grinding cup variants, and the first and second grinding cup variants can be selectively inserted into the grinding cup receptacle in order to selectively introduce cooling medium into the interior of the grinding cup or into the gap between the grinding cup and the grinding cup receptacle, depending on the grinding cup variant used. Of course, the planetary mill can initially only be provided with one of the grinding cup variants, and the user can purchase the other grinding cup variant as an accessory if required.

[0175] Preferably, the grinding cup receptacle and the planetary shaft are inclined at an angle of inclination with respect to the sun axis, more precisely, obliquely inwardly toward the sun axis as seen from below. Thereby, the upper end of the grinding cup receptacle can be closer to the sun axis than the bottom of the grinding cup receptacle. This simplifies the structure of an arrangement in which the grinding cup receptacle and / or the grinding cup intersect the sun axis at the respective upper end. However, it is also conceivable in principle, particularly in the case of a single-body mill, that the grinding cup receptacle is also arranged so that the sun axis is intersected in the case of parallel axes.

[0176] If the planetary shaft is inclined with respect to the sun axis in the cooled planetary mill, it is particularly advantageous if the rotation of the grinding cup receptacle is driven synchronously with respect to the rotation of the carrier device by means of a staggered toothed-belt drive, wherein the toothed-belt drive has non-parallel drive and output shafts, which particularly extend coaxially with respect to the sun axis or the planetary shaft.

[0177] The cooling described herein, in particular the (cryogenic) cooling medium, for example, is dosed directly into the interior of the grinding cup, can also be applied in other laboratory mills, for example, in swing mills or other mills. The laboratory mill comprises:

[0178] at least one grinding cup receptacle for inserting a grinding cup; drive means for driving a movement of the grinding cup, for example, a planetary movement or a swing movement, in order to grind a grinding stock filled into the grinding cup by means of grinding bodies; and

[0179] a cooling device with a cooling medium dosing opening for dosing a cooling medium into the grinding cup receptacle and / or directly into the interior of a grinding cup inserted into the grinding cup receptacle during a movement of the grinding cup, i.e. during an operation of the laboratory mill,

[0180] and, if necessary, the other features of the planetary mill described herein.

[0181] Planetary mill with tilted planetary axes and open mill cup receptacle or open mill cup

[0182] According to another aspect of the present disclosure, a planetary mill comprises:

[0183] a carrier device as a sun element, which is rotatable about a sun axis;

[0184] at least one grinding station with a grinding cup receptacle for inserting a grinding cup, wherein the grinding cup receptacle is arranged on the carrier device offset in axial direction with respect to the sun axis and is rotatable about a planet axis with respect to the carrier device;

[0185] a drive motor for driving the rotation of the carrier device and the grinding cup receptacle, so that the grinding cup receptacle and a grinding cup insertable into the grinding cup receptacle in operation run on a circular orbit about the sun axis and at the same time rotate about the planet axis, i.e. on a combined orbit and rotation trajectory,

[0186] wherein the grinding cup receptacle and the planet axis are inclined at an inclination angle with respect to the sun axis,

[0187] wherein the grinding cup receptacle has an upper end on which the grinding cup is inserted and has a lower end axially opposite the upper end, seen from below to above, the planet axis is inclined inwardly in the direction of the sun axis,

[0188] wherein the grinding cup receptacle and / or the grinding cup inserted into the grinding cup receptacle remains open upwardly during the rotation of the carrier device and the grinding cup receptacle.

[0189] By the inclined position of the grinding cup, that is to say, the inclined position of the upper end portion inwards towards the sun axis, a component of the centrifugal force is generated which accelerates the grinding bodies and the grinding stock towards the cup bottom. Surprisingly, it has been shown that the combined centrifugal force resulting from the surrounding and rotational movement keeps the grinding stock and the grinding bodies in the grinding cup even without a grinding cup cover or at least with a grinding cup cover having openings, if necessary, and that the grinding stock does not fly upwards out of the grinding cup as in the case of a planetary grinding machine with parallel axes, in which the grinding cup with this inwards inclined grinding cup can even remain open upwards during operation, if necessary. This effect can be utilized in various ways. In addition, the effect can be used, for example, during operation, for cooling media to be able to drip from above into the interior of the grinding cup or into the grinding cup receptacle. However, the effect can also be used for monitoring the grinding process from above, for example, with a camera.

[0190] Preferably, the grinding cup inserted into the grinding cup receptacle has an axial upper end portion and has an axial opening on its upper end portion which remains open during the rotation of the carrier device and the grinding cup receptacle, wherein the axial opening of the grinding cup intersects the sun axis so that an observation into the interior of the grinding cup and / or a media addition can be achieved from above through the axial opening of the grinding cup in each arbitrary rotational position of the carrier device and the grinding cup receptacle, and / or the grinding cup receptacle has an axial opening on its upper end portion which remains open during the rotation of the carrier device and the grinding cup receptacle, wherein the axial opening of the grinding cup receptacle intersects the sun axis so that an observation into the interior of the grinding cup receptacle, in particular into the area around the outer wall of the grinding cup, and / or a media addition can be achieved from above through the axial opening of the grinding cup receptacle in each arbitrary rotational position of the carrier device and the grinding cup receptacle.

[0191] Thus, depending on the design of the grinding cup receptacle and the grinding cup, it is advantageously possible to selectively drip cooling media vertically from above into the interior of the grinding cup or into the grinding cup receptacle during operation, for example, and / or to take pictures of the interior of the grinding cup and / or of the grinding cup receptacle, for example, with a camera.

[0192] Preferably, the grinding cup is rotationally fixed in the grinding cup receptacle during operation of the planetary grinding machine, for example, latched or clamped, so that the power input for the grinding of the grinding stock in the grinding cup is more efficient.

[0193] The grinding power of the planetary grinding machine is sufficiently large, in particular, to be able to grind the grinding stock in the grinding cup, i.e., to significantly comminute and not only to mix or degas the material, by means of the grinding bodies, for example, grinding balls, which are loaded into the grinding cup together with the grinding stock.

[0194] Preferably, the drive motor for this has a motor power of at least 300 W, preferably at least 500 W, preferably at least 1 kW, in particular in the range of 300 W to 3 kW, preferably in the range of 500 W to 2.5 kW, preferably in the range of 1 kW to 2 kW.

[0195] Preferably, the maximum rotational speed of the rotation of the carrier device is at least 700 min -1 , preferably at least 800 min -1 , preferably at least 900 min -1 , preferably at least 1000 min -1 , preferably at least 1100 min -1 and / or at most 1800 min -1 , preferably at most 1400 min -1 , preferably at most 1200 min -1 .

[0196] Preferably, the relative rotational speed ratio between the rotation of the carrier device and the grinding cup receptacle has a value of between 1 : 1.2 and 1 : 5, preferably between 1 : 1.5 and 1 : 3, preferably in the range of 1 : 2 + / - 0.5.

[0197] Further preferably, the carrier device and the grinding cup receptacle rotate counter-rotating to one another, and the relative rotational speed ratio between the rotation of the carrier device and the grinding cup receptacle is between 1 : -1.2 and 1 : -5, preferably between 1 : -1.5 and 1 : -3, preferably in the range of 1 : -2 + / - 0.5.

[0198] In an advantageous manner, an efficient grinding can be achieved in particular with a planetary mill in this range, in particular when working in a catapulting concept and nevertheless still being able to grind with an upwardly open grinding cup.

[0199] The relative inclination of the planetary axes relative to the sun axis is preferably in the range of 15° to 70°, preferably in the range of 25° to 60°, preferably in the range of 37.5° + / - 10°, in particular in the range of 37.5° + / - 5°.

[0200] The spatial arrangement can be well achieved in an advantageous manner with a single-body mill, i.e. by a planetary mill which has only one grinding cup receptacle and one in particular adjustable counterweight for compensating for the unbalance of the carrier device.

[0201] Preferably, the grinding cup receptacle has a bottom, and the bottom of the grinding cup receptacle in particular does not intersect the sun axis. Likewise, the grinding cup bottom of a grinding cup inserted into the grinding cup receptacle preferably does not intersect the sun axis. Structural advantages as well as advantages in terms of grinding power can thus be achieved.

[0202] A drive device, in particular a toothed-belt drive device, for the grinding cup receptacle, preferably arranged below the grinding cup receptacle.

[0203] According to an exemplary embodiment, the grinding cup receptacle has a bottom, and a shaft stub extends coaxially to the planetary shaft obliquely downward from the bottom of the grinding cup receptacle. The shaft stub is rotatably supported below the bottom of the grinding cup receptacle, for example by a ball bearing, and below the bottom of the grinding cup receptacle, an output wheel of the planetary drive device is fixed to the shaft stub, in order to drive the grinding cup receptacle in rotation about the oblique planetary shaft when the carrier device is rotated.

[0204] Preferably, the rotation of the grinding cup receptacle is driven in synchronization and directly with respect to the rotation of the carrier device by means of an intermeshing toothed-belt drive device, and the toothed-belt drive device preferably has drive and output shafts which extend obliquely to one another.

[0205] According to one embodiment, a camera and / or a contactless temperature sensor, for example an infrared sensor, can be included which is arranged above the grinding cup receptacle and, if necessary, points vertically or obliquely from above into the interior of the grinding cup receptacle and / or into the interior of a grinding cup inserted into the grinding cup receptacle, in order to optically or according to temperature permanently monitor and / or photograph the interior of the grinding cup receptacle and / or the interior of a grinding cup inserted into the grinding cup receptacle during the rotation of the carrier device and the grinding cup receptacle. By optical monitoring of the grinding process, for example, special knowledge about the grinding parameters or characteristics of the grinding can be determined. With the temperature sensor, the temperature of the grinding stock can be measured directly.

[0206] For grinding particular samples, a cooling device for metering a cooling medium into the grinding cup receptacle and / or into the interior of a grinding cup can also be advantageous.

[0207] As previously described, the cooling device can comprise a cooling medium line and a cooling medium metering opening in the center of the region of the sun shaft, and the cooling medium is introduced into the central region on the sun shaft above the grinding cup receptacle or above the grinding cup by means of the cooling medium line, and during the rotation of the carrier device and the grinding cup receptacle, the cooling medium can be metered from the cooling medium metering opening into the grinding cup receptacle and / or into the interior of a grinding cup from above through the upper opening of the grinding cup receptacle or the grinding cup.

[0208] As described above, the cooling medium metering opening can be configured as a nozzle, and the cooling medium can be a liquid refrigerant, such as liquid nitrogen. The liquid refrigerant preferably flows from above through the nozzle, dripping or spraying into the grinding cup housing and / or the grinding cup, and evaporates within the grinding cup housing or grinding cup. The resulting gas can escape into the ambient air through the opening in the grinding cup housing and / or the grinding cup.

[0209] One aspect of the invention also relates to a laboratory apparatus comprising:

[0210] The support device is rotatable about the sun axis.

[0211] At least one cup receiving portion for inserting a cup, wherein the cup receiving portion is arranged axially offset on the support device relative to the sun axis and is rotatable relative to the support device about the planetary axis.

[0212] A drive device for rotating the carrier and the cup holder, thereby causing the cup holder and the cups that can be inserted into the cup holder to follow a combined orbital and rotational trajectory during operation.

[0213] And, where necessary, other features of the planetary grinder described herein, wherein, in particular, the cup housing and the planetary axis are tilted at an angle (α) relative to the sun axis.

[0214] The cup-containing portion has an upper end and a lower end opposite to the upper end, and when viewed from below, the planetary axis is obliquely inclined inward in the direction of the solar axis, and / or

[0215] The cup receiving portion and / or the cup inserted into the cup receiving portion intersect the sun axis with their respective upper ends. Attached Figure Description

[0216] The invention will now be described in detail with reference to embodiments and the accompanying drawings, wherein the same and similar elements partially have the same reference numerals, and features of different embodiments can be combined with each other. In addition to Fig. 8-11 In some of the accompanying drawings, for simplicity, the teeth of the toothed belt are not shown. Among them:

[0217] Fig. 1 A three-dimensional view showing an embodiment of a planetary ball mill is provided.

[0218] Fig. 2 A three-dimensional illustration showing the rotating components and drive mechanism of another embodiment of a planetary ball mill.

[0219] Fig. 3 It shows Fig. 2 Front view of the rotating components and drive unit of a planetary ball mill.

[0220] Fig. 4 partial cutaway front view of a planetary ball mill with a grinding jar holder and a grinding jar,

[0221] Fig. 5 the same, but with a different grinding jar holder or grinding jar, Fig. 4

[0222] Fig. 6 the same, but with a different grinding jar holder or grinding jar, Fig. 5

[0223] Fig. 7 the same, but with a different grinding jar holder or grinding jar, Fig. 6

[0224] Fig. 8 three-dimensional view of one embodiment of a directly interleaved toothed belt drive with non-parallel axes for a planetary ball mill,

[0225] Fig. 9 front view of the toothed belt drive of Fig. 8

[0226] three-dimensional view of another embodiment of a directly interleaved toothed belt drive with non-parallel axes for a planetary ball mill, Fig. 10

[0227] bottom view of the toothed belt drive of Fig. 11 Fig. 10 different illustrations of an embodiment of a directly interleaved toothed belt drive with non-parallel drive and output shafts for a planetary ball mill,

[0228] Fig. 12 different illustrations of another embodiment of a directly interleaved toothed belt drive with non-parallel drive and output shafts for a planetary ball mill,

[0229] Fig. 13 different views of an embodiment of a directly interleaved toothed belt drive with obliquely extending, twisted drive and output shafts and a transmission ratio,

[0230] Fig. 14 different views of another embodiment of a directly interleaved toothed belt drive with obliquely extending, twisted drive and output shafts and a transmission ratio,

[0231] Fig. 15 ​​​​​

[0232] Fig. 16 An exemplary schematic structural diagram showing the spatial arrangement of the mid-planes of the drive and output toothed pulley wheels,

[0233] Fig. 17 An exemplary schematic structural diagram as in Fig. 16 with structural points A and B for the reversing rollers,

[0234] Fig. 18 An exemplary schematic structural diagram as in Fig. 17 with a rounding at structural point B for the reversing rollers,

[0235] Fig. 19 An exemplary schematic structural diagram as in Fig. 17 with an additional configuration of reversing rollers,

[0236] Fig. 20 An exemplary schematic structural diagram as in Fig. 19 but for a knee sleeve knee arrangement,

[0237] Fig. 21 A side view of the bearing arrangement of another embodiment of a planetary ball mill, which is in the form of a double planetary mill having two tilted grinding stations or grinding cup receptacles and two directly interleaved toothed belt drive arrangements,

[0238] Fig. 22 A front view of the rotating components and drive arrangement of the planetary ball mill of Fig. 21 ,

[0239] Fig. 23 A top view of the rotating components and drive arrangement of the planetary ball mill of Fig. 21 ,

[0240] Fig. 24 A complex interleaved toothed belt drive with transmission ratio and linear tensioning rollers is shown,

[0241] Fig. 25 A photograph inside the rotating grinding cup of one embodiment of a cryogenic planetary ball mill is shown,

[0242] Fig. 26 A measured particle size distribution of a PP test sample ground with one embodiment of a cryogenic planetary ball mill is shown,

[0243] Fig. 27 A measured particle size distribution of a PP test sample ground with a cooled magnetically driven mill is shown,

[0244] Fig. 28 A measured particle size distribution of a PP test sample ground with a cooled oscillating mill is shown. DETAILED DESCRIPTION

[0245] With reference to Fig. 1 , a laboratory scale planetary mill or planetary ball mill 1 has a device housing 12 with a user interface 14, for example a touch display, with a display. Rotating components of the planetary ball mill 1, for example a carrier device 28 with one or more rotating grinding stations 2 or planets, motor drives and electronic control devices for controlling the functions of the planetary ball mill 1, are located within the device housing 12. The device housing 12 can be opened and closed by means of a housing cover 13 in order to ensure, on the one hand, the accessibility of the grinding stations 2 arranged in a housing interior 15 in the case of a stationary carrier device 28 and, on the other hand, to reliably enclose the housing interior 15 in which the carrier device 28 rotates and in which one or more grinding stations 2 revolve and rotate when the planetary mill 1 is in operation. The planetary ball mill 1 is dimensioned as a laboratory device and can be placed, for example, on a laboratory table using feet 16. Such a laboratory planetary ball mill 1 is used, in particular, for finely comminuting, in particular brittle, samples in process analysis. The grinding cup 64 of the laboratory planetary mill 1 has a volume of 50 ml to 1000 ml, preferably 80 ml to 500 ml.

[0246] With reference to Fig. 2 and Fig. 3 , the planetary ball mill 1 has a base plate 18 on which the rotating components and the drive devices are mounted and supported. A drive motor 22 is mounted on the base plate 18, which drive motor drives a main pulley 26 in rotation via a main drive belt 24. The main drive belt 24 can be a triangular belt or a triangular ribbed belt. Slippage at the main drive belt 24 is secondary, so that the use of a synchronous belt is not mandatory here, although this should not be ruled out either. It is therefore also conceivable that the main drive belt 24 is configured as a toothed belt.

[0247] The main drive pulley 26 is rigidly connected to a carrier device 28, which carrier device 28 performs a sun rotation about a sun axis S. For this purpose, the carrier device 28 and the main pulley 26 of the central ball bearing 32 are supported on a central shaft 34. The central shaft 34, in turn, is rigidly connected to the base plate 18 or the device housing 12. As a result, the drive motor 22 drives the carrier device 28 as a sun element in rotation about the fixed central shaft 34 by means of the belt drive 24, 26.

[0248] The drive cogged pulley 36 is coaxial and rigidly connected to the central shaft 34. When the carrier device 28 is rotated by the belt drive 24, 26, the cogged belt 38 is driven by the position-fixed drive cogged pulley 36 and in turn drives the output cogged pulley 42 on the grinding station 2. Thereby, the grinding station 2 is carried around the central shaft 34 or sun shaft S by the carrier device 28 and at the same time additionally rotated around its own axis, i.e. the planetary shaft P. The planetary grinding machine 1 is configured as a planetary grinding machine 1 with non-parallel rotational axes S and P. The output cogged pulley 42 is arranged obliquely to the drive cogged pulley 36 or central shaft 34 and coaxially to the planetary shaft P, thereby forming a directly intermeshing cogged belt drive 50 with non-parallel drive and output shafts. The output cogged pulley 42 oblique to the drive cogged pulley 36 has a smaller diameter than the drive cogged pulley 36, thereby forming a directly intermeshing cogged belt drive 50 with non-parallel drive and output shafts and an integrated gear ratio in one and the same direct cogged belt drive 50. In the present example, the cogged belt 38 is also reversed and tensioned out by two cogged reversing rollers 44, 46 in order to accommodate the obliquity of the cogged belt drive 50 between the obliquely arranged drive and output cogged pulleys 36, 42. Here, the shafts of the reversing rollers 44, 46 obliquely, more precisely even torsionally, extend not only with respect to the drive shaft (sun shaft S) but also with respect to the output shaft (planetary shaft P) in order to smoothly transition the cut-in and cut-out of the cogged belt 38 into and out of each other. The cogged belt 38 here intermeshingly extends in all four return sections 52a-d.

[0249] With the directly, spatially intermeshing cogged belt drive thus generated for the oblique grinding station 2 or oblique grinding cup receptacle 62, a simple, reliable, cost-effective, smooth and low-maintenance drive can be provided for a planetary ball mill with an oblique planetary shaft.

[0250] In Fig. 2 and 3 the embodiments shown are so-called single grinding machines, which have only a unique grinding station 2 or grinding cup receptacle 62 and a counterweight 63 arranged on the opposite side of the sun shaft S. In the present illustration, the counterweight 63 is fixed, but it is advantageous to use a radially and if necessary also axially adjustable counterweight 63 in order to improve the running smoothness.

[0251] With reference to Fig. 4 to Fig. 7The planetary grinder 1 is constructed as a cryogenic planetary (spherical) grinder. The cryogenic planetary grinder 1 has a cooling device 110 by which a cryogenic cooling medium 6, such as liquid nitrogen (LN2), can be directly dripped into the grinding cup 64 and / or the grinding cup receiving portion 62. For this purpose, the cooling device 110 has a cooling medium reservoir 112 into which a reserve of the cryogenic cooling medium 6, such as liquid nitrogen (LN2), can be injected and stored for a certain period of time. The cooling medium reservoir 112 may, for example, include a vacuum bottle or other insulated container. A cooling medium conduit 114 leads from the cooling medium reservoir 112 to a cooling medium metering opening in the form of a cooling medium nozzle 116, from which the cryogenic cooling medium 6, especially liquid nitrogen, exits and drips into the grinding station 2. The amount of cooling medium 6 can be controlled, for example, by a solenoid valve 118, or by a control device 4 of the cryogenic planetary grinder 1. To provide active feedback temperature regulation, the grinding cup 64 or the grinding cup housing 62 may have a temperature sensor 122, which transmits the measured temperature data to the radio interface 124 of the control device 4, for example, via a wireless connection. This forms an active feedback regulation loop for temperature regulation. The user can set a desired low-temperature rated temperature on the user interface 14, which is actively regulated by the regulation loop by adjusting the amount of liquid nitrogen dripped as the regulation value via a solenoid valve 118.

[0252] As shown here, the cooling medium outlet or cooling medium nozzle 116 can be arranged coaxially with the sun axis, so that the liquid cooling medium 6 drips down the sun axis S coaxially by gravity. Since the planetary axis P is tilted relative to the sun axis S, the upper end 62a of the grinding cup container 62 or the upper end 64a of the grinding cup 64 is closer to the sun axis S than the bottom 62b of the grinding cup container or the bottom 64b of the grinding cup.

[0253] exist Fig. 4 In the example, the grinding cup 64 has a tubular extension 66 such that the upper end 64a of the grinding cup, in the form of the extension 66, intersects the sun axis S. The grinding cup 64 or the grinding cup extension 66 has an opening 64c at its upper free end 64a, which also intersects the sun axis S, allowing the cooling medium to drip directly and vertically through the opening 64c and thus into the interior 64d of the grinding cup. In the example shown, the grinding cup 64 has a grinding cup lid 68 with a central opening 68c that communicates with the extension 66 and the upper grinding cup opening 64c, allowing the cooling medium dripping into the upper grinding cup opening 64c to reach the interior 64d of the grinding cup 64.

[0254] Although in the present example a liquid cryogenic cooling medium is used, which is gaseous or evaporated at room temperature and standard pressure, and the generated gas can escape from the grinding cup 64, other cryogenic cooling media can also be used depending on the application, such as for example dry ice, as long as they are compatible with the materials of the grinding cup, the grinding bodies (see Fig. 25 ) and the grinding stock (not shown).

[0255] With reference to Fig. 5 , the embodiment shown here has a closed grinding cup cover 68, and the communication connection for the input of cooling medium leads from the upper opening of the extension tube 66 into the gap 72 between the circumferential radial outer wall 64e of the grinding cup 64 and the circumferential radial outer wall 62e of the grinding cup receptacle 62. The gap 72 can also extend into the intermediate chamber 74 between the grinding cup bottom 64b and the grinding cup receptacle bottom 62b.

[0256] In the present example, the axial opening on the upper end of the grinding station 2 or planet is thus the axial opening 62c of the grinding cup receptacle, through which the cooling medium reaches into the grinding station 2, wherein at this opening 62c the cooling medium can also be added or dripped perpendicularly coaxially to the sun shaft S into the grinding cup receptacle 62. However, it is also conceivable that the cooling medium nozzle 116 is arranged eccentrically and inclinedly sprays into the opening 62c or 64c at a certain cooling medium pressure.

[0257] Furthermore, the planetary ball mill 1 can have a camera 76 and / or an infrared sensor 77, which is fixed with a holding device 78 on the carrier device 28 and rotates with the carrier device 28 or sun wheel. The camera 76 or infrared sensor 77 can "see" directly into the grinding cup 64 or grinding cup receptacle 62 coaxially to the planet shaft P through the upper opening 62c or 64c, that is to say durably during the operation of the planetary mill, that is to say during the rotation of the carrier device 28 and the grinding cup receptacle 62.

[0258] With reference to Fig. 6 , the grinding cup 64 is configured axially so long that it intersects the sun shaft S also without the extension 66, in order to be able to let the cooling medium 6 drip directly into the interior 64d of the grinding cup 64. Thus, the extension 66 can be dispensed with in this embodiment. In other words, the grinding cup 64 with or without the extension 66 has an upper axial opening 64c, which intersects the sun shaft S and through which the cooling medium can be introduced.

[0259] With reference to Fig. 7The grinding cup housing 62 can also be configured so long that its upper opening 62c, without the extension 66, also intersects the sun axis S in order to deliver cooling medium into the gap 72 between the grinding cup housing 62 and the grinding cup 64. The grinding cup cover 68 can be designed to be closed Fig. 5 ) or open Fig. 7 ).

[0260] A further advantage of the grinding cup 64 inclined obliquely inwards towards the sun axis S is that in general it is possible to work with open grinding cups 64. Due to the axial inclination of the planetary, wherein the upper edge 64a of the grinding cup 64 is closer to the sun axis S than the grinding cup bottom 64b, the grinding stock and grinding bodies do not leave the grinding cup 64 despite this as in the case of an axial parallel arrangement.

[0261] In summary, the grinding sample can thus be embrittled in direct contact with liquid nitrogen Fig. 4 and 6 ) or indirectly via the grinding cup wall 64e Fig. 5 and 7 . With open grinding cups 64 and direct introduction of LN2 into the interior 64d of the grinding cup 64, the sample can be cooled faster and with less LN2. On the other hand, it can occur in this case that from a certain particle size (the smaller the stronger) the sample particles are dragged outwards with the escaping nitrogen. For this reason, too, or in the case where the sample should not come into direct contact with liquid nitrogen, indirect cooling through the grinding cup wall 64e Fig. 5 and Fig. 7 ) can be advantageous. In order to retrofit from direct to indirect cooling, if necessary, neither the grinding cup housing 62 nor the grinding container needs to be changed, but if necessary a further grinding cup cover 68 and / or a further extension 66 is sufficient to cool the grinding cup from the outside (for example Fig. 4 - Fig. 5 ).

[0262] As previously described, the interleaved toothed belt drive 50 is located below the support device 28 and below the grinding cup housing 62. The output toothed pulley 42 is fixed to the lower end 82a of the shaft 82, which merges into the upper substrate 84 on the grinding cup housing side, and the grinding cup housing 62 is fixed, for example, screwed onto the upper substrate. Below the grinding cup housing 62, more precisely between the bottom 62b of the grinding cup housing 62 and the output toothed pulley 42, the entire grinding station 2 or planetary structure 90 is rotatably supported on the support device 28 coaxially with the inclined planetary shaft P by ball bearings 92. The grinding cup housing 62 rotates freely upwards. Here, especially above the grinding cup 64, there is no support for the grinding cup housing 62. Specifically, the grinding cup housing 62 is supported only at its lower end.

[0263] The spatially interlaced toothed belt drive mechanism described here, and the inclined support below the grinding cup housing 62, offer multiple advantages over the supports and transmission mechanisms listed in the preamble of the specification.

[0264] Reference Fig. 8 to Fig. 11 An exemplary embodiment of an interlaced toothed belt drive with non-parallel drive and output shafts is shown. The drive toothed belt pulley 36, the output toothed belt pulley 42, and the first and second reversing rollers 44, 46 are respectively disposed on the free ends 154 of the two interlaced retaining arms 152 of a retaining cross 150 and are ball-bearing supported thereon. In this example, the retaining cross 150 is manufactured using a 3D printing method. The interlaced arms 152 are partially bent to achieve the desired axial tilt between the sun axis S and the planetary axis P. Fig. 8 to Fig. 9 In the illustrated embodiment, the first and second reversing rollers 44, 46 are toothed reversing rollers and tension the toothed belt 38 outwards. This has the advantage that the return sections 52a-d of the toothed belt 38 can be lengthened, thereby reducing the crossover of the toothed belt 38. However, referring to… Fig. 10-11 Reversing can also be achieved using non-toothed reversing rollers 44, 46 at the back side 38b of the toothed belt 38. The inner side 38a or the inner flat side of the toothed belt 38 is transversely toothed to form teeth 39, as is customary. Here, commercially available HTD5 toothed belts are used, which either have standardized non-circular teeth 39 only on the inner flat side 38a (single-toothed belt) or on both the inner flat side 38a and the outer flat side 38b (double-toothed belt). Different toothed pulleys or reversing rollers may be constructed with or without flanged pulleys 162, depending on the arrangement. Fig. 8-11 In the two examples, the arrangement and tilt of the first and second reversing rollers 44, 46 are chosen such that the cut-in and cut-out transitions coaxially with each other, as will be explained in more detail below.

[0265] Reference is made to Fig. 12 , the drive shaft 136 and the output shaft 142 are inclined to each other at an inclination angle. In the present example, the inclination angle or inclination position angle a is approximately 35° (see also Fig. 3 ). With regard to the planetary grinding machine 1, the drive shaft 136 corresponds to the sun shaft S and the output shaft 142 corresponds to the planet shaft P. It has proven, however, that such a spatially intermeshing toothed belt drive 50 with non-parallel shafts 136, 142 and, if necessary, a transmission ratio or reduction ratio ≠ 1 has fundamental significance and can also be used in other fields of drive technology or generally as a toothed belt drive 50 and not only for a planetary grinding machine 1.

[0266] In principle, the drive shaft 136 of the drive toothed belt pulley 36 is perpendicular to the midplane 36a of the drive toothed belt pulley and the output shaft 142 is perpendicular to the midplane 42a of the output toothed belt pulley 42. In Fig. 12 the example shown, the drive shaft 136 and the output shaft 142, although arranged obliquely to each other at an inclination angle a ≠ 0, lie in one common plane, which in the top left view in Fig. 12 is the plane of the paper. Thus, in this example, the drive shaft 136 and the output shaft 142, although obliquely to each other in space and intersecting in the common plane, are not twisted to each other.

[0267] In other arrangements, however, such as in Fig. 14 , the drive shaft 136 and the output shaft 142 can also be twistedly (and not perpendicularly), i.e. obliquely and twistedly to each other in three-dimensional space, that is to say, the drive shaft 136 and the output shaft 142 are not parallel (and not perpendicular) to each other and do not intersect in three-dimensional space.

[0268] Fig. 15 Another example is shown, in which the drive shaft 136 and the output shaft 142 obliquely to each other in a common plane and intersect in the common plane.

[0269] Again with reference to Fig. 12 , the commutating roller shafts 144, 146 are also inclined with respect to each other. In the present example, the commutating roller shafts 144, 146 are not twisted to each other, but also intersect in a common plane, which in the example of Fig. 12 extends perpendicular to the common plane of the drive shaft 136 and the output shaft 142 due to the symmetrical arrangement. However, the commutating roller shafts 144, 146 can also be twisted to each other. But in Fig. 12In the embodiment shown in the figures, the reversing rollers 144, 146 both extend not only perpendicularly but also twistedly with respect to the drive shaft 136 and with respect to the output shaft 142. By means of the first and second reversing rollers 44, 46, the toothed belt is reversed in the four return sections 52a, 52b, 52c, 52d and is interleaved in such a way that the cut-outs and cut-ins on the toothed belt wheels or rollers 36, 42, 44, 46 transition coaxially into one another. Thus, the cut-out 36b on the drive toothed belt wheel 36 transitions coaxially into the cut-in 44c on the first reversing roller 44. Furthermore, the cut-out 44b on the first reversing roller 44 transitions coaxially into the cut-in 42c on the output toothed belt wheel 42. Furthermore, the cut-out 42b on the output toothed belt wheel 42 transitions coaxially into the cut-in 46c on the second reversing roller 46, and the cut-out 46c on the second reversing roller transitions coaxially into the cut-in 36c on the drive toothed belt wheel 36. Thus, by means of the multiply obliquely twisted arrangement formed by the obliquely inclined drive shaft 136 and output shaft 142 and the obliquely inclined reversing rollers 44, 46, a smooth running of the fourfold interleaved toothed belt 38 on the spatially obliquely twisted toothed belt transmission 50 can be achieved, without the toothed belt 38 slipping off the toothed belt wheels or rollers 36, 42, 44, 46.

[0270] Fig. 13-15 Further embodiments of the spatially obliquely interleaved toothed belt transmission 50 are shown in different arrangements.

[0271] With reference to Fig. 16-20 In order to construct the spatially obliquely twisted, in this example even twisted, toothed belt transmission 50, first the drive toothed belt wheel 36 and the output toothed belt wheel 42 are placed obliquely to one another freely in space, corresponding to the desired arrangement of the drive shaft 136 and the output shaft 142 on the drive side. The shafts 136 and 142 can be oblique in a common plane or oblique and twisted to one another, depending on the application.

[0272] By the oblique arrangement of the two shafts 136, 142, the intersection line 172 of the two toothed belt wheel midplanes 36a, 42a is generated. The spatial positioning of the reversing rollers 44, 46 is then determined. To this end, the run-in and run-out of the toothed belt 38 into and out of the respective toothed belt wheels 36, 42 tangentially to the respective toothed belt wheels 36, 42 is provided. The run of the toothed belt 38 is drawn on the respective midplanes 36a, 42a of the toothed belt wheels 36, 42. In order to wind the toothed belt 38, instead of the addendum circle diameter of the toothed belt wheels 36, 42, the effective diameter of the toothed belt wheels is reasonably employed. This has the advantage that the overall length of the toothed belt 38 is determined later. The "free" end of the "toothed belt rays" running out of the toothed belt wheels 36, 42 intersects in a point each, which lies on the intersection line 172 of the two midplanes 36a, 42a. These points areFig. 17 Points A and B on the intersection line 172.

[0273] Then, auxiliary planes are created for each reversing configuration to be established on the toothed belt 38. (Refer to...) Fig. 18 Taking point B as an example, surface 174 is defined by two "toothed belt rays" that meet at point B. This constructed plane then becomes the intermediate plane 46a of the reversing roller 46 to be constructed. Furthermore, a "rounding" is now performed on this surface for the two "rays" that meet at point B. This rounding is performed using the effective circle diameter of the reversing roller 46 to be constructed. For this purpose, the diameter of the reversing roller 46 is used plus twice the distance between the toothed belt back 38b and the line of action (neutral axis) of the toothed belt. This rounding, or the center point of this rounding, now represents an axis point of the reversing roller 46 to be constructed. Now, the axis position of the reversing roller 46 to be constructed is clearly given by the intermediate plane 46a (the axis 146 is perpendicular to this intermediate plane by definition) and this axis point. Therefore, the reversing roller 46 can be installed accordingly.

[0274] For in Fig. 12 The exemplary arrangement shown has two reversing rollers 44, 46, and the reversing roller 44 is treated in the same manner immediately following at point A.

[0275] With the reversing rollers 44 and 46 constructed in this way, the toothed belt 38 now has optimal entry points 36c, 42c, 44c, 46c and exit points 36b, 42b, 44b, 46b on all toothed pulleys or reversing rollers 36, 42, 44, 46. Advantageously, the reversing rollers 44 and 46 can influence, and in particular reduce, the toothed belt crossover in the return sections 52a-d. That is, for example, if the reversing roller 46 moves to the right in the upper right view, the two return sections 52c, 52d become longer above and below the reversing roller 46, and furthermore, the crossover in the return sections 52c, 52d is reduced, both of which are beneficial to the service life of the toothed belt 38. When positioning the reversing rollers 44 and 46, care should be taken only to ensure that the winding of the drive toothed pulley 36 and the output toothed pulley 42 does not become too small; however, this can be adjusted accordingly in the design described above. Therefore, the stagger of each individual loop segment 52a-d can be kept relatively small, and as mentioned above, can be structurally influenced by the designer within certain limits.

[0276] The designer can thus design the inclined space-folding toothed-belt drive 50 relatively freely according to the desired geometric drive and output ratio. Here, a configuration for the inclined space-folding toothed-belt drive 50 can always be found in which the toothed belt 38 is correctly reversed and is not squeezed in any location in one direction, but rather the toothed belt 38 always strives to remain in the median plane 36a, 42a, 44a, 46a of the toothed-belt wheel or reversing roller 36, 42, 44, 46. It is thus possible, if necessary, even to dispense with the flange belt wheel 162.

[0277] It is also possible, as shown for example in Fig. 15 and Fig. 20 , one of the reversing rollers, in this example the first reversing roller 44, is placed onto the toothed-belt back 38b and here tensions the toothed belt 38 not outward, but rather inward, in Fig. 20 : point of structure A) in order to create a "knee-suit knee arrangement".

[0278] The reversing rollers 44, 46 can also be used for the readjustment of the toothed belt 38, however this is not necessary depending on the application. If necessary, one or, if necessary, both reversing rollers 44, 46 can be fixed positionally variably and the toothed belt 38 can be readjusted by moving one or both reversing rollers 44, 46. At least one, if necessary both, reversing rollers 44, 46 can thus form an adjustable tensioning roller, respectively.

[0279] With reference to Fig. 24 , a third and fourth reversing roller, i.e. two further reversing rollers 202, 204, can be inserted into the return section, if necessary. In the example shown, the third and fourth reversing rollers 202, 204 are inserted between the second reversing roller 46 and the drive toothed-belt wheel 36. The second reversing roller 46 and the two additional reversing rollers 202, 204 are here arranged with parallel axes and are arranged in a common plane. This has the advantage that, if a tensioning roller is necessary, here for example the third reversing roller 202 as tensioning roller can be moved linearly outward in order to tension in this common plane without having to change the inclination.

[0280] With reference to Fig. 21 to Fig. 23 , by means of the inclined space-folding toothed-belt drive 50, it is also possible to configure a planetary ball mill with more than one grinding station 2, i.e. more than one planet. In Fig. 21-23The example shown illustrates a dual planetary grinder 1, wherein two grinding stations 2 each have a grinding cup receiving portion 62, the grinding cup receiving portion having a planetary axis P, and the two grinding stations are respectively inclined relative to each other and inclined relative to the sun axis S. In the example shown, two drive wheels 36 are fixed on a central sun axis 34, and the drive wheels drive the rotation of the grinding station 2 or the grinding cup receiving portion 62 as described above, via two independent, spatially interlaced, inclined toothed belt drive devices 50.

[0281] In this example, it is advantageous to tilt the sun axis S obliquely relative to the substrate 18 or the device housing 12, such that at a specific location 182, the planetary axis P extends perpendicularly to the substrate 18. This can be advantageous for inserting and removing the grinding cup 64.

[0282] Reference Fig. 25 You can see how to use camera 76, for example... Fig. 6 In the illustrated embodiment, photographs (or videos) can be taken directly into the open grinding cup 64 during the rotation of the carrier 28 and the grinding station 2. The photographs clearly show how the grinding balls 70 (in this test run, no material is being ground) fly across the grinding cup 64 during reverse rotation and in the projectile configuration. Such studies, for example, demonstrate that the crushing effect of the grinding balls can be particularly effective when they roll against the grinding cup wall and the sample rotates around them. This photographic or video recording enables unexpected monitoring and research possibilities and allows for a deeper understanding of the grinding process within the planetary grinder 1.

[0283] refer to Fig. 26 Curve 192 shows the use of 22. The particle size distribution of a polypropylene pellet (PP) sample was measured. The sample was ground at low temperature using the first functional mode of a low-temperature planetary ball mill 1. Fig. 27 and 28 The particle size distributions 194 and 196 after similar grinding are shown, but using a magnetically driven cryogenic grinder or a cryogenic oscillating grinder. It can be clearly seen that higher fineness or significantly better grinding results can be achieved using the planetary grinder 1 disclosed herein.

[0284] Furthermore, in the planetary mill 1 disclosed herein grinding can advantageously be carried out with an open grinding cup and / or the refrigerant can be metered as required, if desired even directly into the interior of the grinding cup. Furthermore, it is also possible to carry out the grinding using non-metallic grinding bodies, for example ceramic grinding balls or agate grinding balls, which can be advantageous for certain samples and which are not possible, for example, with a magnetically driven mill. If the grinding stock is flushed with liquid nitrogen, this can even result in a low-temperature wet grinding at least temporarily. The mixing of the grinding stock can thereby be improved. Furthermore, the formation of lumps and / or the sticking of the grinding stock on the grinding cup wall can be reduced.

[0285] Furthermore, in the planetary mill 1 disclosed herein, it is possible to grind significantly larger amounts of sample at one time than, for example, in a swing mill or a magnetically driven mill. In general, the grinding volume of the grinding cup 64 of the inventive planetary mill 1 can be greater than or equal to 50 ml, greater than or equal to 100 ml, greater than or equal to 250 ml, greater than or equal to 500 ml, if necessary even up to 1000 ml or more.

[0286] In summary, a planetary mill 1 or a toothed belt drive 50 is thereby provided which has a plurality of advantageous technical aspects which can be realized jointly or independently of one another. The toothed belt drive 50 can be used, for example, also for other than the planetary mill 1. The planetary mill 1 can be provided with a cooling device for low temperatures which can introduce a cooling medium directly into the grinding cup receptacle 62 or the grinding cup 64. If necessary, the grinding cup 64 can remain open at the top during grinding and a coolant can be metered into the grinding cup 64 and / or the grinding cup receptacle 62 and / or the grinding process can be monitored by video technology during rotation. If necessary, it is even possible to fill or replenish the grinding cup 64 with grinding stock during rotation of the carrier device 28 and the grinding cup 64. While all these aspects advantageously act jointly where possible, they can also be realized and solve technical problems independently of one another and each aspect has specific advantages in itself.

[0287] It will be obvious to a person skilled in the art that the embodiments described above are to be understood as exemplary and that the application is not limited to these embodiments, but can vary in many ways without deviating from the scope of protection of the claims. It can further be seen that the features, regardless of whether they are disclosed in the description, the claims, the drawings or in another way, also define, individually, important components of the application. Even if they are jointly described with other features.

[0288] Furthermore, the features described in connection with the aspects of the planetary mill with a non-parallel shaft and a spatially interleaved toothed belt drive, such a spatially interleaved toothed belt drive with non-parallel shafts, the planetary mill with a cooling device and / or the planetary mill with inclined planetary shafts and an open mill cup receptacle or an open mill cup can be combined with each other in an alternative manner.

[0289] In another aspect, the present application discloses a plurality of inventive aspects, for example a planetary mill with a particular spatially interleaved toothed belt drive, such a toothed belt drive, a grinding station with a mill cup receptacle that can be operated with an upwardly open mill cup and / or an upwardly open mill cup and / or a cryogenic cooling device for active cooling during the grinding process in a planetary mill. It is apparent that these aspects of the invention, in particular, can be implemented both jointly and separately from each other and produce corresponding advantages.

Claims

1. A planetary grinding mill (1) with non-parallel rotating shafts, comprising: A support device (28) capable of rotating around the sun axis (S), At least one grinding cup receiving portion (62) for inserting the grinding cup (64), wherein the grinding cup receiving portion (62) is arranged axially offset on the support device (28) relative to the sun axis (S) and is rotatable relative to the support device (28) about the planetary axis (P). A drive device (22) for driving the rotation of the bearing device (28) and the grinding cup receiving part (62), wherein the rotation of the grinding cup receiving part (62) is driven synchronously with respect to the rotation of the bearing device (28) by means of a toothed belt drive (50). In this configuration, the planetary axis (P) does not extend parallel to the solar axis (S), and The toothed belt drive (50) for the grinding cup receiving part (62) has a non-parallel drive shaft (136) and output shaft (142). The toothed belt drive (50) is configured as an interleaved toothed belt drive (50), and includes a first reversing roller (44) having a first reversing roller shaft (144) and a second reversing roller (46) having a second reversing roller shaft (146), wherein the first reversing roller (44) and the second reversing roller (46) are arranged on opposite sides of the toothed belt drive (50). The first reversing roller (144) and the second reversing roller (146) extend obliquely relative to each other. The toothed belt drive (50) includes a drive toothed belt pulley (36) and an output toothed belt pulley (42). The drive toothed belt pulley is arranged coaxially with the sun axis (S), and the output toothed belt pulley is arranged coaxially with the inclined planetary axis (P). The toothed belt (38) extends alternately between the drive toothed pulley (36) and the first reversing roller (44), between the first reversing roller (44) and the output toothed pulley (42), between the output toothed pulley (42) and the second reversing roller (46), and between the second reversing roller (46) and the drive toothed pulley (36).

2. The planetary grinding mill (1) according to claim 1, in, The planetary axis (P) is tilted at an angle (α) between 5° and 75° relative to the solar axis (S).

3. The planetary grinding mill (1) according to claim 1, in, The toothed belt drive (50) with a non-parallel drive shaft (136) and output shaft (142) has a transmission ratio, and the output toothed belt pulley (42) which is inclined relative to the drive toothed belt pulley (36) has fewer teeth and a smaller diameter than the drive toothed belt pulley (36) according to the transmission ratio.

4. The planetary grinding mill (1) according to claim 1, in, The rotation of the support device (28) and the grinding cup receiving part (62) is in opposite directions.

5. The planetary grinding mill (1) according to claim 4, in, The relative speed ratio between the rotation of the bearing device (28) and the rotation of the grinding cup receiving part (62) is between 1:-1.5 and 1:-5.

6. The planetary grinding mill (1) according to claim 1, in, The planetary grinder (1) is constructed as a single grinder having only one grinding cup receiving part (62) that is obliquely inward when viewed from below and a counterweight (63), or as a double planetary grinder having two planetary axes (P) that are obliquely inward relative to the sun axis (S).

7. The planetary grinding mill (1) according to claim 6, in, The counterweight (63) is adjustable.

8. The planetary grinding mill (1) according to claim 1, in, The teeth of the toothed belt (38) operating on the drive toothed pulley (36) and the output toothed pulley (42) are engaged in a form-fit manner with the teeth of the drive toothed pulley (36) and the output toothed pulley (42). The toothed belt (38) cuts out (36b) on the drive toothed pulley (36) at a point not parallel to the toothed belt (38) cuts in (42c) on the output toothed pulley (42), and the toothed belt (38) extends interlaced therebetween. Wherein, the cutout (42b) of the toothed belt (38) on the output toothed pulley (42) is not parallel to the cutout (36c) of the toothed belt (38) on the drive toothed pulley (36), and the toothed belt (38) extends interlaced therebetween, and The first and second reversing rollers (144, 146) extend obliquely relative to the sun axis (S) and / or obliquely relative to the inclined planetary axis (P).

9. The planetary grinding mill (1) according to claim 8, in, The first and second reversing rollers (144, 146) are tilted at angles between 1° and 89° or between 91° and 179° relative to the sun axis (S) and / or planet axis (P).

10. The planetary grinding mill (1) according to claim 1, in, The toothed belt (38) is staggered by less than 90° in at least one of the following return segments: between the drive toothed pulley (36) and the first reversing roller (44), between the first reversing roller (44) and the output toothed pulley (42), between the output toothed pulley (42) and the second reversing roller (46), and between the second reversing roller (46) and the drive toothed pulley (36).

11. The planetary grinding mill (1) according to claim 10, in, The toothed belt (38) has an interlacing angle of less than 60° in at least one of the return segments.

12. The planetary grinding mill (1) according to claim 11, in, The toothed belt (38) has an interlacing angle of less than 45° in at least one of the return segments.

13. The planetary grinding mill (1) according to claim 12, in, The toothed belt (38) has an overlap of less than 30° in at least one of the return segments.

14. The planetary grinding mill (1) according to claim 1, in, The first reversing roller (44) adjusts the angular deviation of the parallelism between the cutout (36b) on the drive toothed pulley (36) and the cut-in (42c) on the output toothed pulley (42) by the first reversing roller (44) causing the line of action of the toothed belt (38) to reverse in three-dimensional space from the direction of the cutout (36b) on the drive toothed pulley (36) to the direction of the cut-in (42c) on the output toothed pulley (42), and wherein the staggering of the toothed belt (38) between the drive toothed pulley (36) and the output toothed pulley (42) is distributed, and / or The second reversing roller (46) adjusts the angular deviation of the parallelism between the cutout (42b) on the output toothed pulley (42) and the cut-in (36c) on the drive toothed pulley (36) by the second reversing roller (46) causing the line of action of the toothed belt (38) to change direction in three-dimensional space from the direction of the cutout (42b) on the output toothed pulley (42) to the direction of the cut-in (36c) on the drive toothed pulley (36), and the toothed belt (38) is distributed between the output toothed pulley (42) and the drive toothed pulley (36).

15. The planetary grinding mill (1) according to claim 1, in, Meets at least one of the following criteria: The toothed belt (38) cuts out (36b) and cuts in (36c) on the drive toothed pulley (36). The toothed belt (38) cuts out (42b) and cuts in (42c) on the output toothed pulley (42). The toothed belt (38) cuts out (44b) and cuts in (44c) on the first reversing roller (44). The toothed belt (38) extends at an angle relative to each other at the cutout (46b) and cutout (46c) on the second reversing roller (46).

16. The planetary grinding mill (1) according to claim 1, in, The cut-out (36b) of the toothed belt (38) on the drive toothed pulley (36) and the cut-in (42c) of the toothed belt (38) on the output toothed pulley (42) and / or The toothed belt (38) cuts out (42b) on the output toothed pulley (42) and the toothed belt (38) cuts in (36c) on the drive toothed pulley (36) extend at an inclined angle to each other.

17. The planetary grinding mill (1) according to claim 1, in, Meets at least one of the following criteria: The toothed belt (38) extends coaxially at the cutout (36b) on the drive toothed pulley (36) and the cutout (44c) on the first reversing roller (44), and the toothed belt (38) intersects between the drive toothed pulley (36) and the first reversing roller (44). The toothed belt (38) extends coaxially at the cutout (44b) on the first reversing roller (44) and the cutout (42c) on the output toothed pulley (42), and the toothed belt (38) is interlaced between the first reversing roller (44) and the output toothed pulley (42). The toothed belt (38) extends coaxially at the cutout (42b) on the output toothed pulley (42) and the cutout (46c) on the second reversing roller (46), and the toothed belt (38) intersects between the output toothed pulley (42) and the second reversing roller (46). The toothed belt (38) extends coaxially at the cutout (46b) on the second reversing roller (46) and the cutout (36c) on the drive toothed pulley (36), and the toothed belt (38) is interlaced between the second reversing roller (46) and the drive toothed pulley (36).

18. The planetary grinding mill (1) according to claim 1, in, The first and / or second reversing rollers (144, 146) extend torsionally relative to the drive shaft (136) and / or relative to the output shaft (142).

19. The planetary grinding mill (1) according to claim 1, in, The drive shaft (136) and the output shaft (142) extend at an angle to each other in a common plane and intersect in the common plane.

20. The planetary grinding mill (1) according to claim 19, in, The first and / or second reversing rollers (144, 146) extend obliquely relative to the common plane of the drive shaft (136) and the output shaft (142).

21. The planetary grinding mill (1) according to claim 1, in, At least one of the reversing rollers is disposed on the toothed side inside the toothed belt (38) and reverses the toothed belt (38) outward in a manner away from the imaginary connecting line between the midpoint of the drive toothed pulley (36) and the output toothed pulley (42).

22. The planetary grinding mill (1) according to claim 1, in, The toothed belt drive (50) includes a retaining cross with crossed arms, wherein the drive toothed pulley (36), the output toothed pulley (42), and the first and second reversing rollers (44, 46) are rotatably supported on opposite ends of the crossed arms.

23. The planetary grinding mill (1) according to claim 1, in, The spatial arrangement of the drive toothed pulley (36) and the output toothed pulley (42), as well as the first and second reversing rollers (44, 46), is mirror-symmetric with respect to the common plane of the drive shaft (136) and the output shaft (142).

24. The planetary grinding mill (1) according to claim 23, in, The spatial arrangement has the shape of a rounded quadrilateral that bends at an inclined angle around the connecting line of the first and second reversing rollers (44, 46) in space.

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