WORKING BALL MILL

Description

[0001] The invention relates to a laboratory ball mill, in particular a vibrating mill, centrifugal ball mill or planetary ball mill, further in particular a planetary ball mill with a transmission ratio of 1:1, with at least one grinding cup holder for at least one grinding cup arranged on a machine part of the ball mill which is moved during the grinding operation of the ball mill, with a clamping device arranged on the moving machine part for transmitting a clamping force and / or a clamping torque to the grinding cup and / or to the grinding cup holder and with a coupling device with at least one coupling element, wherein an energy transfer from the stationary machine part to the moving machine part is provided via the coupling device to generate the clamping force.

[0002] From DE 10 2012 009 987 A1, a laboratory ball mill, in particular a planetary or centrifugal ball mill on a laboratory scale, is known, which is particularly suitable for larger grinding vessels on a laboratory scale, i.e., typically 160 ml, 250 ml, or even 500 ml, and allows for the automatic clamping of a grinding vessel to a grinding vessel holder. In the known laboratory ball mill, a support device rotates about a vertical central axis. The known mill has one or more grinding stations about a planetary axis offset parallel to the central axis, which is / are rotatably mounted on the support device. The grinding station has a receiving device or grinding vessel holder for at least one grinding vessel that can be filled with material to be ground and grinding media, in particular grinding balls.During grinding, the receiving device is guided around the central axis by the carrier device and also rotates – usually in the opposite direction to the carrier device – around the eccentrically mounted planetary axis. In addition, a drive for the carrier device and another drive for the grinding station are provided.

[0003] For the automatic axial clamping of the grinding vessel in the holding device, i.e., without manual application of clamping force, a motorized drive with an eccentric shaft as the coupling element is provided. Clamping is achieved by rotating the eccentric shaft, which acts from below against a grinding vessel base. The eccentric shaft is mounted in a transverse bore in a downward-extending pin of the clamping base. The pin engages in a corresponding coaxial bore in a bearing journal of a lower base section of the laboratory mill. The eccentric shaft transmits any change in height to the clamping base via needle bearings. The clamping base, via a spring assembly, lifts a pressure plate. The pressure plate, in turn, lifts the inserted grinding vessel against a pressure yoke above the grinding vessel, which acts as a stop for the grinding vessel lid, until all axial gaps in the clamping system are eliminated.The eccentric shaft is driven beyond its knee point to create self-locking in the tensioned state.

[0004] The grinding vessel is clamped by a motor. For this purpose, the known ball mill has a motor that is stationary and mounted on a fixed housing outside the support structure. The motor drives a drive shaft that is slotted at its inner end to engage with a transverse pin attached to the eccentric shaft when the grinding station is in a specific insertion and removal position and with the correct rotational orientation. When the slotted coupling is engaged, the motor can rotate the eccentric shaft to automatically clamp the grinding vessel axially or release the clamping force. Thus, the eccentric shaft only transmits energy from the motor drive located on the stationary machine part to the clamping mechanism on the moving machine part when the clamping force is generated.

[0005] Automatic grinding bowl clamping has the advantage that the force generated when releasing the clamping mechanism does not need to be applied by the user, but is automatically applied by the clamping motor. Furthermore, automatic grinding bowl clamping leads to greater user comfort and ensures a consistent and therefore reproducible clamping force with every clamping operation. It also increases safety against operator error.

[0006] The automatic grinding bowl clamping system used in the well-known ball mill has several disadvantages: Coupling the eccentric shaft to the drive motor requires the grinding station to be precisely oriented when the mill is at rest. Due to wear and / or contamination, the precise orientation required for coupling may not be achieved, making it difficult to connect the eccentric shaft to the motor's drive shaft. The self-locking mechanism of the eccentric shaft, generated by the grinding bowl clamping system, is intended to prevent the clamping from unintentionally releasing during grinding. However, wear can cause a shift in the position of the pivot point, potentially compromising the safety against unintentional release of the grinding bowl clamp.The arrangement and alignment of the motor and eccentric shaft relative to each other, as required for the coupling process, also necessitates a less compact design for the mill. Furthermore, the automatic clamping of the grinding bowl in the known mill is structurally complex. The energy and force transmission from the motor via the eccentric shaft and the other components of the clamping device interacting with the eccentric shaft requires a correspondingly robust design of the power transmission elements with a high component weight. As a result, the components moving during grinding experience high centrifugal forces, leading to high bearing and drive loads.

[0007] The object of the present invention is to provide a laboratory ball mill of the type mentioned at the outset, in particular designed as a laboratory vibrating mill, with the possibility of automatic grinding cup clamping, in which the grinding cup clamping is realized in a structurally simple manner with a lightweight and compact design of the laboratory mill.

[0008] Furthermore, a high level of reliability against unintentional loosening of the grinding cup clamp should be ensured.

[0009] In particular, the design of the automatic grinding cup clamping system should offer the possibility of clamping different grinding cup geometries, especially grinding cups with different grinding cup heights.

[0010] The aforementioned problems are solved by a ball mill with the features of claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.

[0011] In accordance with the mill known from DE 10 2012 009 987 A1, the mill according to the invention also provides a coupling element via which drive energy or drive force is transmitted from a stationary machine part of the mill to a machine part that moves during milling operation in order to generate the clamping force required for automatic clamping of the milling bucket. However, unlike the known mill, the invention provides that the coupling element is mechanically coupled or connected to both the stationary and the moving machine part (also) during milling operation.Preferably, a permanent, continuous, uninterrupted, and non-destructively separable connection of the coupling element to a power generation unit, in particular a motor drive, is provided on and / or attached to the stationary machine part of the ball mill and to the moving machine part of the ball mill. The inventive design of the automatic grinding bowl clamping mechanism can be implemented particularly advantageously in vibratory mills.

[0012] In particular, the force and / or energy transmission and transfer required to generate a clamping force and / or clamping torque via the coupling element is possible independently of the state of motion of the grinding bowl holder, and furthermore, independently of a specific angular position of a rocker arm connected to the grinding bowl holder of a vibrating mill, or independent of a specific rotational orientation of a support device carrying the grinding bowl holder. A preferably mechanical coupling via the coupling element can be provided both during grinding operation and at standstill. The coupling during grinding operation makes it particularly possible to transmit a drive force, drive torque, or drive energy via the coupling element from the stationary machine part of the mill to the moving machine part, even during grinding operation.to transmit in order to generate a clamping force and / or clamping torque even during milling operations. However, the invention also allows for the transmission of a drive force, drive torque, or drive energy only when the mill is stationary. In this case, a mechanical device, for example a safety coupling, can be provided to maintain a clamping state of the milling bowl during milling operations, independent of any force and / or energy transmission via the coupling element.

[0013] To generate a clamping force and / or a clamping torque, the clamping device of the mill according to the invention can, for example, have a spindle drive in a manner known per se, wherein a torque transmitted from the coupling device to the clamping device is converted into a translational adjusting movement of a threaded spindle or push rod.

[0014] The coupling device of the laboratory mill according to the invention is designed and configured for the transmission of energy and / or force or torque from the stationary machine part to the moving machine part of the mill during milling operation. In addition to the coupling element, the coupling device may include further components and devices, for example, at least one drive wheel on a drive side of the coupling device associated with the stationary machine part and / or at least one output wheel on an output side of the coupling device associated with the moving machine part. A torque generated by the output wheel can then be converted into a transverse movement of a threaded spindle or a push rod by means of a spindle device.However, it is also possible that components of the coupling device, for example an adjustable piston element, are transversely adjusted or moved by the transmission of drive energy and / or drive force from the coupling element, thereby generating an axial clamping force that can be transmitted directly or indirectly to the grinding cup.

[0015] During milling, relative movements occur between the moving machine part of the ball mill and the stationary machine part. For example, in the operation of vibrating mills, relative movements occur between the vibrating elements on which the grinding bowl holders are mounted, relative to the stationary mill structure. Relative movements between moving machine parts of the ball mill and stationary machine parts also occur in centrifugal ball mills or planetary ball mills due to their function. According to the invention, the compensation of relative movements can preferably be achieved solely via the coupling element. Particularly preferably, the compensation is achieved without technical articulated components as connections between rigid components or sections of the coupling element that are movable in a predetermined manner. To compensate for relative movements, the coupling element can, however, be designed to be movable in at least some of its dimensions.In this context, the coupling element can have at least two degrees of freedom of movement, each orthogonal to the main direction of movement, relative to the direction of movement of the coupling element when a clamping torque and / or clamping force is transmitted. Particularly preferably, the coupling element has free movement orthogonally to the main direction of movement. This is described in more detail below with reference to exemplary embodiments of the invention. This allows the inventive design of the automatic grinding bowl clamping system to be advantageously implemented, especially in vibratory mills, whereby vibrations occurring during grinding operations from the vibratory bowl oscillators of the vibratory mill, to which the grinding bowl holders are attached, relative to a stationary (housing) part of the vibratory mill, can be compensated for by the mobility of the coupling element.This makes it possible to avoid the occurrence of relevant component stresses, which are associated with the risk of component failure, in a structurally simple way.

[0016] A first and preferred embodiment of the invention relates to the mechanical transmission or transfer of kinetic energy from a motor drive arranged on the stationary machine part to the moving machine part via the coupling element. The clamping force and / or clamping torque is generated decentrally by the motor drive, which is stationary during the grinding operation of the ball mill. The motor power is available at the grinding bowl holder through a suitable design of the coupling. A compact and lightweight construction of the components required for the automatic clamping of the grinding bowl is possible. The reduced component mass allows for a higher payload of the moving machine part of the ball mill and / or a lower load on the drive provided for moving the moving machine part during grinding operation.A lower component mass means that during the grinding process, the components required for the automatic grinding cup clamping experience lower centrifugal forces on the moving part of the machine and can be designed to be more delicate.

[0017] Preferably, the coupling element can be a traction element of a traction drive, particularly a positive-locking one, for mechanical motion or force transmission. For motion or force transmission via the coupling element, at least one drive wheel or drive shaft of the motor drive can be provided on the drive side of the coupling device, and thus on the stationary machine part, and at least one output wheel or output shaft can be provided on the output side of the coupling device, or on the moving machine part. The transmission of drive torque from the motor drive is effected via the drive wheel, in particular a gear or gear assembly, and the transmission of output torque is effected indirectly or directly to the clamping device via the output wheel, in particular a gear or gear assembly.The output torque can be converted, for example, into a clamping force required for clamping the grinding bowl using a spindle device.

[0018] In a positive-locking traction drive, a chain from a chain drive or a toothed belt can be used as the coupling element to transmit torque through wheels with a corresponding positive-locking profile, in particular gears, from a drive shaft of the motor drive to the traction element or from the traction element to an output shaft on the moving machine part of the ball mill. Alternatively, a traction element of a friction-locking traction drive can also be used as the coupling element, whereby a tensioning torque is transmitted via a drive belt by frictional forces acting between the contact surfaces of the belt and pulleys. A push chain drive with a push element as the coupling element can also be used for motion or power transmission.

[0019] A particularly preferred embodiment is one in which the coupling element is designed as a ball or bead chain with a core and a plurality of balls or beads attached to the core, preferably at equal intervals. A bead chain drive is preferably provided, wherein the bead chain is connected on the drive side to a drive wheel for transmitting torque from a motor shaft of the motor drive and on the output side to a driven wheel for transmitting torque to the clamping device. The drive wheel and driven wheel can have recesses distributed around their circumference, adapted to the balls or beads of the bead chain. The output torque can be converted into a transverse clamping force for clamping the grinding bucket by means of a spindle device.The beaded chain allows hose bends in all spatial directions, so that the position of the output side of the beaded chain drive can be easily adapted to the structural conditions inside the ball mill and a compact design of the mill can be achieved.

[0020] To support cable forces, the bead chain can be guided by a hose in one or more hoses. The hose guide also serves a protective function for the bead chain. Preferably, the hose extends between a drive wheel and a driven wheel of the bead chain drive over the entire length of the bead chain, so that the bead chain is completely enclosed in the hose between the wheels. The drive wheel and / or the driven wheel can have a grooved running surface bounded by lateral flanks of the wheel, which contains recesses in its base. The bead chain is guided between these flanks in the area of ​​the wheels. This ensures support and precise guidance of the bead chain even adjacent to the hose guide in the wheel and wrap-around area.

[0021] For torque transmission between moving parts, with the possibility of compensating for relative movements between a stationary machine part and a moving machine part, a cardan shaft or a shaft that is at least partially flexible can alternatively be provided as a coupling element.

[0022] The coupling device can include a gear arrangement for torque conversion of a transmitted drive torque, particularly on the output side. A planetary gear, for example, can generate a higher torque on the output side. The gear arrangement can be self-locking, so that rotation is only possible in one direction. If the gear arrangement interacts with a spindle, a self-locking design for both the spindle and the gear is possible, thus ensuring protection against unintentional release of the grinding bucket clamping even if the power or torque transmission from the coupling element to the output gear is interrupted, for example, due to a broken bead chain.

[0023] To limit the force and / or torque transmission via the coupling element, an overload protection device can be provided, which can be designed in particular as a magnetic slip clutch and / or be arranged, in particular, on the output side of the coupling element. A sensor device with at least one sensor for detecting a clutch disengagement in the event of an overload can be provided, in particular for detecting slippage of a slip clutch. With a control and / or regulation device, control and / or regulation of a motor drive is then possible depending on a detected clutch disengagement.

[0024] To enable the transmission of energy and / or force or torque from the stationary machine part to different moving machine parts, for example two swing arms of a laboratory vibrating mill, several coupling devices, each with at least one coupling element, can be provided, wherein energy transmission from the stationary machine part to two separate (kinematically decoupled) moving machine parts is provided via the coupling devices, in particular wherein the coupling devices are coupled to a common drive arranged on the stationary machine part for energy transmission from the stationary machine part to the moving machine part or can be coupled via a coupling device.With most coupling devices, it is possible, for example, to transmit a clamping torque as needed from a motor drive on the stationary machine part to two clamping devices of a vibratory mill, which are arranged on different rockers of the vibratory mill. Each coupling device can have a drive wheel arranged on the stationary machine part, which is coupled to the motor shaft of the motor drive or can be coupled via a coupling device. Both drive wheels can be subjected to a torque via the motor shaft, with the torque transmission from each drive wheel to a driven wheel on the moving machine part via a coupling element assigned to each drive wheel, for example, a beaded chain. For example, several beaded chain drives can be implemented to transmit a rope force or...A clamping torque from a motor drive on the stationary machine part is transmitted via two beaded chains to output gears mounted on different moving machine parts. The transmitted torque is then transferred to a clamping device associated with each moving machine part for clamping the grinding bucket to that part. It is particularly preferred that the force or torque transmission occurs via two beaded chain drives from a motor drive to two output gears arranged on different rockers of a laboratory vibratory mill. This allows for the simple implementation of automatic grinding bucket clamping on two rockers of a laboratory mill, preferably with only one motor drive, while maintaining a compact mill design.

[0025] This provides the possibility of transmitting energy and / or force or torque from a stationary machine part to an identical moving machine part with multiple coupling devices. In particular, two coupling devices, each with at least one coupling element, can be provided, wherein energy transmission from the stationary machine part, especially from a common drive arranged on the stationary machine part, to an identical moving machine part is provided via each coupling device, particularly with a time delay. Specifically, energy transmission can be provided via the first coupling device to a clamping device for automatic clamping of the grinding bowl, and energy transmission via the second coupling device to a rotary drive for automatic rotation of the grinding bowl.

[0026] In particular, a clamping force or torque can be transmitted from the stationary machine part of the ball mill to a clamping device of a grinding bowl holder by means of a first coupling element of a first coupling device in order to effect automatic clamping of the grinding bowl. A further coupling element of a further coupling device can then transmit a drive force and / or drive torque to a rotary device for rotating the grinding bowl, wherein the rotary device is particularly configured for rotation after a controlled interruption of the grinding operation and at least partial release of the grinding bowl clamping.

[0027] With a multiple coupling elements, it is possible to transmit forces or torques of varying magnitudes from the stationary machine part to the same moving machine part or to different moving machine parts in order to drive different devices, such as a clamping device and a rotary device of a grinding cup holder.

[0028] Further aspects of the present invention relate to the transmission of hydraulic, pneumatic or electrical energy from the stationary machine part via appropriate coupling elements to a moving machine part of the laboratory mill.

[0029] For example, a compressor for supplying a compressed fluid, particularly compressed air, or a hydraulic power unit for supplying hydraulic fluid can be provided on the moving part of the machine. The coupling device is then connected to the compressor or the hydraulic power unit on the drive side. A compressed fluid, particularly compressed air, can also be drawn from a storage tank or pipe network, for example, a pressure vessel located near the laboratory mill and connected to it via a pressure line. The generation of a compressed fluid or hydraulic fluid preferably takes place outside the ball mill, which may have corresponding fluid connections to a pipe network for compressed fluid or hydraulic fluid, or to a compressor, a hydraulic power unit, or corresponding pressure vessels.Compressed air hoses or pressure lines, or even rigid pipes, can be used as coupling elements for energy transmission. To compensate for relative movements between moving machine parts and a stationary machine part, elastic deformation of the coupling element can be provided and / or at least one rotary feedthrough can be provided for a sealed connection.

[0030] On the output side, a pneumatic or hydraulic motor can be provided as part of the coupling device to convert hydraulic or pneumatic energy into mechanical work. By applying pressure to rotors or gears, pneumatic or hydraulic energy can be converted into rotational energy, so that the clamping forces and / or clamping torques required for clamping a grinding bucket can be generated on the output side. The coupling device can also include a force or energy converter in the form of a rotary vane or vane pump, whereby a rotary motion is generated by pressurizing a rotor or gear with compressed gas or air. Alternatively, a piston can be provided as an adjusting element, which is moved translationally by being pressurized with compressed gas or air. This allows the clamping forces and clamping torques required for clamping the grinding bucket to be generated.A rotor, a gear or gear assembly or the adjusting piston can then interact with a clamping device on the moving machine part or be part of the clamping device to generate the clamping forces and / or clamping moments required for automatic grinding bucket clamping.

[0031] It is also possible, in principle, to transfer electrical energy from the stationary machine part to the moving machine part via a power line acting as a coupling element. For example, an actuator can be mounted on the grinding bowl holder, converting an electrical signal into mechanical movements to generate drive torque and / or a driving force. This could, for instance, act as an electromechanical drive, powering a threaded spindle and / or moving a push rod of a clamping device, thus generating an axial clamping force. The actuator's electrical power supply can be drawn from the laboratory mill's operating power supply.

[0032] The transmission of hydraulic, pneumatic, or electrical energy from the stationary machine part via the coupling element to a moving machine part, in particular a grinding bowl holder, can be provided as an alternative or supplement to the mechanical transmission of kinetic energy via a coupling element. The energy transmitted by such a coupling element can be provided as forces and / or torques for clamping the grinding bowl and / or for rotating the grinding bowl when the grinding bowl is held in and / or on the grinding bowl holder and the clamping is released.

[0033] The invention is explained below by way of example using a preferred embodiment. The drawing shows Fig. 1 a schematic partial view, partially cut away, of a first embodiment of a vibratory mill according to the invention with a coupling device for energy transfer from a stationary machine part to a moving machine part, with a bead chain drive for generating a tension force for an automatic grinding bucket clamping, Fig. 2 a schematic partial view of the output side of a coupling device for energy transfer from a stationary machine part to a moving machine part with a bead chain drive, wherein an output wheel for a bead chain of the bead chain drive is provided on the output side of the coupling device, Fig.Fig. 3 A schematic partial view of the drive side of a coupling device for energy transmission from a stationary machine part to a moving machine part with a bead chain drive, wherein a drive wheel for a bead chain of the bead chain drive is provided on the drive side of the coupling device, Fig. 4 A schematic partial view of the output side of a coupling device for energy transmission from a stationary machine part to a moving machine part with a bead chain drive, wherein a planetary gear with a ring gear as an output wheel for a bead chain of the bead chain drive is provided on the output side of the coupling device, Fig. 5 A perspective partial view of the vibratory mill made of . Fig. 1 , Fig. 6 a partial exploded view of the vibrating mill made of Fig. 1 Fig. 7 a schematic partial view, partially cut away, of an alternative embodiment of a vibratory mill according to the invention with two coupling devices for force and / or torque transmission to two clamping devices arranged on different rockers of the vibratory mill, Fig. 8 a schematic partial view, partially cut away, of a further alternative embodiment of a vibratory mill according to the invention with two coupling devices for force and / or torque transmission to a clamping device for clamping the grinding bowl and to a rotary drive for rotating a grinding bowl, wherein the clamping device and the rotary drive are implemented on the same grinding bowl holder, Fig. 9 a perspective partial view of the in Fig. 8 shown swing mill, Fig. 10, which is in Fig. 9 The vibratory mill shown after a grinding bowl has been inserted into a grinding bowl holder on a rocker arm of the vibratory mill, with the clamping device and the rotary drive shown partially cut away, Fig. 11 a schematic partial view of the design of a coupling device on the output side with a slip clutch for limiting the possible torque transmission, Fig. 12 a perspective partial view of the output side of the coupling device made of Fig. 11 and Fig. 13 replacement image of the output side with schematic representation of the gear circuit diagram.

[0034] In Fig. 1 A partial view schematically shows a vibratory mill 1 with a stationary machine part 2 and a moving machine part 3 during milling operation. The moving machine part 3 is a rocker arm of the vibratory mill 1, on which a grinding cup holder 4 for at least one grinding cup 5 is arranged. The vibratory mill 1 preferably has two rockers, with a grinding cup holder 4 arranged on each rocker arm. The stationary machine part 2 can be a base plate, a housing, or a machine base frame of the vibratory mill 1, which is stationary during milling operation and remains fixed relative to the moving machine part 3 during milling.

[0035] In the illustrated embodiment, the grinding cup holder 4 has a base plate 7 with two retaining legs 8, 9. Furthermore, a clamping device 6 for clamping the grinding cup is provided on the grinding cup holder 4. The grinding cup clamping can be carried out, for example, with a clamping device that is described generically in DE 200 15 868 U1.

[0036] To transmit a clamping force to a grinding cup 5, for example, a Fig. 1 A schematically shown spindle drive is provided with a pressure piece 10. The pressure piece 10 is arranged to be rotationally fixed and is connected to a schematically shown threaded bolt 11. The threaded bolt 11 is in a threaded nut 31 ( Fig. 6 ) with internal thread. The threaded nut 31 has a coupling section 33 at the end facing away from the grinding cup 5 ( Fig. 6 ) with square geometry and is in a flanged bushing 34 ( Fig. 6 ) rotatably mounted. The threaded nut 31 can be rotationally fixed to a web wheel 20 via the coupling section 33 ( Fig. 6 ) of a planetary gear set provided on the output side. As described in detail below, the transmission of a torque to the threaded nut 31 leads to an axial adjustment of the threaded bolt 11 relative to the threaded nut 31 and thus to the transmission of a clamping force to the grinding cup 5 via the pressure piece 10.

[0037] As can be seen from Fig. 1 This results in a rotation-prevention element 38 being provided to prevent the pressure piece 10 from rotating.

[0038] How further developments will emerge Fig. 1 As a result, a coupling device 12 with a coupling element 13 is provided for the mechanical transmission of force and / or torque from a motor drive 14 arranged on the stationary machine part 2 to the moving machine part 3 or the rocker arm of the vibrating mill 1. In the illustrated embodiment, the coupling element 13 is a beaded chain or ball chain, which has a plurality of equally spaced beads 15 or balls arranged on a core. On the drive side or motor side, the coupling device 12 has a drive wheel 16 and on the output side or on the side of the grinding bucket holder 4, a driven wheel 17. For torque transmission, the driven wheel 16 is connected to a motor shaft 24 ( Fig. 6 The drive wheel 16 is kinematically coupled to the output wheel 17 via the beaded chain. A torque transmitted to the output wheel 17 via the beaded chain is converted into an axial adjustment movement of the pressure piece 10 via the spindle drive described above, in order to generate the clamping force required for the grinding bucket clamping.

[0039] The wheels 16, 17 each have a grooved running surface bounded by lateral flanks, the base of which contains recesses adapted to the beads 15 of the beaded necklace. This enables a reliable and quiet transmission of power or torque from the drive 14 to the tensioning device 6.

[0040] The design of the coupling device 12 as a bead chain drive allows for a compact construction of the vibratory mill 1 and a flexible arrangement of the drive 14 relative to the rocker arm of the vibratory mill 1. The clamping torque or clamping force is generated decentrally, with the motor power available at the grinding bowl holder 4. The multidimensional movement of the bead chain allows the drive 14 to be positioned relative to the rocker arm in a way that adapts to the structural conditions inside the vibratory mill 1. Thus, the available installation space inside the vibratory mill 1 can be optimally utilized for the automatic clamping of the grinding bowl.

[0041] The beaded chain, as a coupling element 13, can be guided in a tube 18, with the rope force being supported on the tube. The beaded chain allows the tube to bend in all directions. This allows relative movements between the stationary machine part 2 and the moving machine part 3, or the rocker arm of the vibratory mill 1, to be compensated for. The tube 18 can be made of PTFE or another low-friction plastic. Preferably, the tube 18 is slotted so that the beaded chain can be threaded in from the side. Furthermore, the tube 18 can be encased on the outside with another tube, which is particularly designed as a C-tube. The additional tube protects the inner tube 18 from kinking and bulging. In particular, it prevents the inner tube 18 from collapsing under high rope forces and, if the inner tube 18 collapses, the beaded chain from being torn out of the inner tube 18, causing the drive to jam.

[0042] Fig. 6 Figure 1 shows the construction of the coupling device 12 on the output side. A gear arrangement for torque conversion of the torque transmitted by the drive 14 can be provided on the output side. The gear arrangement can be configured according to... Fig. 6 and Fig. 4 The system may be designed as a single-stage planetary gear unit with, for example, four planet gears 21 arranged on a web 20 and a stationary sun gear 22, wherein the sun gear 22 interacts with the web 20 and the output gear 17 to generate a higher output torque. The output gear 17 is designed as a ring gear of the planetary gear unit. An output housing 19 is provided to accommodate the output gear 17. The sun gear 22 is rotationally fixed to a housing cover 23 of the output housing 19, preferably by positive locking. For this purpose, the sun gear 22 has several bores 36 ( Fig. 4 The bores enable a positive fit: The housing has pins that are inserted into the bores of the sun gear 22. The gear ratio of the planetary gear in a single-stage version can be between 1 and 2.5, for example 2.0. A multi-stage version of the planetary gear is also possible, with each stage preferably having a gear ratio between 1 and 2.5.

[0043] The bead chain drive can be self-locking, allowing the drive to be operated from only one direction. Preferably, a self-locking mechanism is provided for the spindle drive described above to convert a torque into an axial clamping force, and a self-locking mechanism is provided for the drive itself, so that even in the event of a mechanical interruption of the coupling element 13, for example, if the bead chain breaks, there is no risk of the grinding bucket clamping unintentionally releasing.

[0044] Alternatively, according to Fig. 2 However, it is also possible to use a direct drive for power transmission via the beaded chain or for torque generation on the output side of the coupling device 12, rather than a gear arrangement, whereby the rope force of the beaded chain is transmitted to an output wheel 17 designed as a solid wheel. This results in a lower output torque and a less complex design.

[0045] Fig. 3 and Fig. 6 Figure 1 shows the drive side of the coupling device 12, which is equipped with an electric drive 14. The drive shaft 24 is connected to the drive wheel 16 via a recess in a base plate 25. A housing cover 26 forms the upper termination. Torque is transmitted from the drive shaft 24 to the drive wheel 24. The transmission of torque to the output wheel 17 on the moving machine part 3 is effected via the beaded chain as a coupling element 13. The gear ratio between the output wheel 17 and the drive wheel 16 can be between 1 and 2.5, for example 2.0. Figure 2 shows the rest of the diagram. Fig. 5 the swing axle Y3.

[0046] Fig. 5 The image shows a detailed view of the vibratory mill 1 in its assembled state. As can be seen from... Fig. 5 As shown schematically, the torque axes Y1, Y2 on the output side and on the drive side of the coupling device 12 can be arranged at any angle α to each other due to the flexibility of the bead chain drive with the continuously circulating bead chain guided in the tubes 18.

[0047] Fig. 7 Figure 1 shows an alternative embodiment of a vibrating mill 1 according to the invention in a schematic partial representation, wherein two coupling devices 12 of essentially identical design are shown in the Fign. 1 bis 6 described type may be provided to realize a force and / or torque transmission, preferably from a common motor drive 14, via a motor shaft 24 to the coupling devices 12 and from these to two clamping devices 6 on different swing arms of the vibrating mill 1.

[0048] Furthermore, as in Fig. 7 schematically shown, a switching element 27, for example a coupling device, is provided to connect either one coupling device 12 or the other coupling device 12 to the motor shaft 24 and thus, as required, to tension or release the clamping devices 6 on the two swing arms independently of each other and, for example, with a time delay.

[0049] In Fig. 8 A schematic representation shows an arrangement in which several coupling devices 12 are provided for the transmission of force or torque from a stationary machine part 2 to a moving machine part 3, in particular to a rocker arm of the laboratory vibratory mill 1. Fig. 8 Two structurally identical coupling devices 12 can be provided for force and / or torque transmission. Each coupling device 12 is connected via a coupling element 13 to a motor drive 14 arranged on the stationary machine part 2 and associated with the respective coupling element 13. A first coupling device 12 is designed to transmit a force or drive torque to a clamping device 6 in order to automatically clamp a grinding bucket 5 in a grinding bucket holder 4. On the opposite side of the grinding bucket holder 4, a swivel or rotary drive 28 is provided, which makes it possible to rotate the grinding bucket 5 in its at least partially relaxed state for the purpose of standardizing the grinding results by transmitting force and / or torque from the clamping device 6 to the clamping device 6. Fig. 8 the further drive 14 shown on the left and the one in Fig. 8 The further coupling device 12, also shown on the left, can be rotated or swivelled.

[0050] As can be seen in particular from Fig. 9 The rotary device 28 can have a rotating element 37 that can be positively and / or non-positively connected to the grinding bowl 5 in order to rotate the grinding bowl 5 as required. The rotating element 37 can have a coupling geometry or key surface on its end face facing the grinding bowl 5, which positively engages and / or couples with a complementary coupling geometry or key surface projection on the adjacent end face of the grinding bowl 5 when the grinding bowl 5 is inserted into the grinding bowl holder 4. The grinding bowl 5 can be pivoted by preferably 180° by rotating the rotating element 37 via the complementary surfaces and surface projections.

[0051] A control system can be provided such that a clamped grinding bowl 5 is automatically at least partially relaxed and then automatically rotated, for example, after half the grinding time of a grinding process has elapsed. The rotated grinding bowl 5 is then automatically clamped again, and the grinding process continues. The automatic clamping and rotation of the grinding bowl, effected by force and / or torque transmission from the stationary machine part 2 via two coupling devices 12, is described in Fig. 8 schematically shown by the force arrow 29 and the torque arrow 30, where the arrow 29 indicates the direction of the clamping force when clamping the grinding cup 5 in the grinding cup holder 4 and the arrow 30 indicates a possible direction of rotation of the grinding cup 5 to equalize the grinding results.

[0052] An embodiment in which the force and / or torque transmission to a clamping device 6 and a rotary drive 28 is carried out as described above with two coupling devices 12 is not excluded, wherein the two coupling devices 12 are as in Fig. 7 described as being able to be coupled to an identical motor drive 14 via a coupling device or a switching element 27.

[0053] In the Fign. 9 und 10 Is the swing mill 1 from Fig. 8 each shown in a schematic view, whereby Fig. 9 the vibrating mill 1 before inserting a grinding cup 5 into the grinding cup holder 4 and Fig. 10 represents a grinding cup 5 in a clamped and partially rotated state. As shown in the Fig. 9 und 10 As shown, the right coupling device 12 can, for example, be used for power transmission from a first motor drive 14 to a clamping device 6, and the left coupling device 12 for power transmission from a second motor drive 14 to a rotary drive 28. The coupling devices 12 can have the same structural design. However, structural differences may exist with regard to the torque transmission from the respective bead chain drive to the clamping device 6 on the one hand and the rotary drive 28 on the other.

[0054] A direct drive is provided for transmitting the rope force and generating torque on the rotary drive 28 side, wherein the rope force is transmitted to a driven wheel 17 designed as a solid wheel. Torque conversion via a gearbox is preferably not provided on the rotary drive 28 side. In contrast, the transmission of the rope force and generating torque on the tensioning device 6 side is preferably carried out via a gearbox arrangement with a planetary gear unit. Fig. 4 shown species.

[0055] The drive 14 and the coupling device 12 are capable of generating high torques and the resulting clamping forces. An overload can be reliably prevented by means of a safety coupling, in particular a magnetic slip clutch. This is especially relevant when grinding bowls 5 of different lengths need to be clamped in the grinding bowl holder 4. The slip clutch protects the input and output gears 16, 17, as well as the beaded chain as a coupling element 13, from excessive stress.

[0056] In the further Fig. 11 It has been shown that the gear arrangement on the output side of the coupling device 12 can also be designed as a multi-stage gear unit, in particular as a multi-stage planetary gear unit. In a single-stage design, the gear ratio of the planetary gear unit can be, for example, between 1 and 2.5, for example 2.0. In a multi-stage design of the planetary gear unit, the gear ratio per stage can be between 1 and 2.5, for example 2.0. This allows a higher output torque to be transmitted.

[0057] The first gear stage is according to Fig. 13 Preferably formed by a driven gear 17, which is driven by the beaded chain as a coupling element 13 and is designed as a ring gear. The first driven gear 17 drives a connecting gear 20 or a planet carrier. A sun gear 22 is fixedly connected to a housing cover 23 and is therefore stationary. The connecting gear 20 is connected to another sun gear 22 of the second gear stage, which drives another connecting gear 20 of the second gear stage. Another ring gear 17a of the second gear stage is fixed. The torque transmission from the other connecting gear 20 to the threaded nut 31 is also shown schematically. A rotational movement of the threaded nut 31 is converted into a translational movement of the pressure piece 10. The fixed ring gear 17a of the second gear stage is only stationary if the torque of a slip element of the slip clutch is not exceeded.

[0058] As can be seen from Fig. 11 This results in, for example, ten magnets 32 being inserted into pockets distributed around the circumference on the end face of the further ring gear 17a of the second gear stage, adjacent to the grinding cup holder 4. These pockets are provided on the end face of the further ring gear 17a. An adjacent output housing 19 (see Fig. 12 The second ring gear 17a is also equipped with magnets, for example, four magnets, to generate a holding torque, so that the second ring gear 17a is held and stationary on the output housing 19 until an overload occurs. In the event of an overload, the second ring gear 17a slips by at least one position, and the magnetic field at a sensor 35 provided on the output housing 19 is momentarily interrupted. As soon as a signal interruption is detected, it is thus recognized that an overload has occurred. The sensor 35 can be a Hall sensor.

[0059] In particular, an overload event can be linked, in terms of control and / or regulation, to the pressure piece 10 reaching an end position. A control and / or regulation system with a corresponding control and / or regulation device can be provided, which evaluates the sensor signal from sensor 35. This makes it possible, in the case of a position-controlled and / or regulated drive 14, to link a signal interruption detected by sensor 35 or the slippage of the slip clutch with the reaching of a zero position or end position of a clamping element of the clamping device 6 and to provide this information for the control and / or regulation of the drive 14. If grinding buckets 5 with different grinding bucket lengths are to be used, it is possible to move or adjust the clamping element, for example the pressure piece 10 in this case, towards the grinding bucket 5 with the drive 14 until a zero position or end position is reached.The end position is detected by the slippage of the slip clutch. This makes it possible to reference the drive 14 for a grinding bucket 5 with a specific grinding bucket length to the detected zero position or end position. Depending on the end position or zero position detected for a specific grinding bucket length due to the occurrence of the overload condition, the drive 14 can then automatically move to the respective end position or zero position for all subsequent clamping operations until, when using grinding buckets 5 with a different grinding bucket length, a new end position or zero position is reached and detected by the sensor 35 through another signal interruption. This new end position or zero position then forms the reference position for all subsequent clamping operations.Control and / or regulation of the drive 14 is possible by detecting an overload case when the grinding bucket clamp is opened, if a clamping device, for example the pressure piece 10 in this case, is extended as far as possible when the grinding bucket clamp is released and strikes a component. This impact can then lead to slippage of the slip clutch and be detected as an overload case.

[0060] A separating disc, for example designed as a sliding, ring-shaped separating film, can be provided between the sensor 35 and the magnets 32. This prevents the magnets 32 from detaching from their mounting pockets in the output gear 17 and then impacting the sensor 35 in a form-fitting manner. The separating disc holds the magnets 32 in their mounting pockets, eliminating the need for adhesive bonding. The separating disc should be as thin and abrasion-resistant as possible to maximize the magnetic force and torque of the slip clutch. Bezugszeichenliste:

[0061] 1 Vibrating mill 2 Stationary machine part 3 Moving machine part 4 Grinding cup holder 5 Grinding cup 6 Clamping device 7 Base plate 8 Retaining leg 9 Retaining leg 10 Pressure piece 11 Threaded bolt 12 Coupling device 13 Coupling element 14 Drive 15 Bead 16 Drive gear 17 Output gear 17a Ring gear 18 Hose 19 Output housing 20 Step 21 Planetary gear 22 Sun gear 23 Cover 24 Motor shaft 25 Base plate 26 Housing cover 27 Switching element 28 Rotary drive 29 Arrow 30 Arrow 31 Threaded nut 32 Magnet 33 Coupling section 34 Bushing 35 Sensor 36 Bore 37 Rotating piece 38 Anti-rotation element

Claims

1. Laboratory ball mill (1), in particular a vibratory mill, centrifugal ball mill or planetary ball mill, more particularly a planetary ball mill having a transmission ratio of 1:-1, comprising at least one grinding jar holder (4) for at least one grinding jar (5), the grinding jar holder (4) being arranged on a machine part (3) of the ball mill (1) that is moved during milling operation of the ball mill (1), a clamping device (6) arranged on the moving machine part (3) for transmitting a clamping force to the grinding jar (5), and a coupling device (12) having at least one coupling element (13), wherein energy transmission from a stationary machine part (2) to the moving machine part (3) for generating the clamping force is provided via the coupling device (12), characterised in that the coupling element (13) is coupled to the stationary machine part (2) and to the moving machine part (3) during milling operation.

2. Laboratory ball mill (1) according to claim 1, characterised in that the coupling element (13) is movable at least in sections in a multidimensional manner in order to compensate for relative movements between the stationary machine part (2) and the moving machine part (3).

3. Laboratory ball mill (1) according to claim 1 or 2, characterised in that movement energy can be transmitted via the coupling element (13) from a motorized drive (14) arranged on the stationary machine part (2) to the moving machine part (3).

4. Laboratory ball mill (1) according to any one of the preceding claims, characterised in that the coupling element (13) is configured as a tensile member of a tensile-member drive, in particular a positive-engagement tensile-member drive.

5. Laboratory ball mill (1) according to any one of the preceding claims, characterised in that the coupling element (13) is configured as a chain of a chain drive, in particular a multidimensionally movable chain, more particularly a ball chain.

6. Laboratory ball mill (1) according to any one of the preceding claims, characterised in that the coupling element (13) is integrated into a hose guide.

7. Laboratory ball mill (1) according to any one of the preceding claims, characterised in that the coupling device (12) comprises a gear arrangement for torque conversion, in particular on the output side for torque increase.

8. Laboratory ball mill (1) according to any one of the preceding claims, characterised in that the coupling device (12) comprises an overload clutch, in particular designed as a magnetic slip clutch.

9. Laboratory ball mill (1) according to claim 8, characterised in that a sensor device having at least one sensor (35) for detecting clutch disengagement in an overload case is provided, in particular for detecting slipping of a slip clutch, and that a control and / or regulating device is provided for controlling and / or regulating the drive (15) as a function of a detected clutch disengagement.

10. Laboratory ball mill (1) according to any one of the preceding claims, characterised in that at least two coupling devices (12), each having at least one coupling element (13), are provided, wherein energy transmission from the stationary machine part (2) to two different moving machine parts (3) is provided via the coupling devices (12), in particular wherein the coupling devices (12) are couplable to a common drive (14) arranged on the stationary machine part (2) for energy transmission from the stationary machine part (2) to the moving machine parts (3).

11. Laboratory ball mill (1) according to any one of the preceding claims, characterised in that at least two coupling devices (12), each having at least one coupling element (13), are provided, wherein energy transmission from the stationary machine part (2), in particular from a common drive (14) arranged on the stationary machine part (2), more particularly in a time-offset manner, to the same moving machine part (3) is provided, in particular wherein energy is transmitted via the first coupling device (12) to the clamping device (6) and via the second coupling device (12) to a pivot drive (28).

12. Laboratory ball mill according to any one of the preceding claims, characterised in that hydraulic, pneumatic or electrical energy can be transmitted via the coupling element from the stationary machine part (2) to the moving machine part (3).