EP3019276B1 - Rührwerkskugelmühle mit axialkanälen - Google Patents

Rührwerkskugelmühle mit axialkanälen Download PDF

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Publication number
EP3019276B1
EP3019276B1 EP14752251.0A EP14752251A EP3019276B1 EP 3019276 B1 EP3019276 B1 EP 3019276B1 EP 14752251 A EP14752251 A EP 14752251A EP 3019276 B1 EP3019276 B1 EP 3019276B1
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EP
European Patent Office
Prior art keywords
grinding
agitator
agitator shaft
ball mill
auxiliary
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP14752251.0A
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German (de)
English (en)
French (fr)
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EP3019276A1 (de
Inventor
Horst Pausch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Netzsch Feinmahltechnik GmbH
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Netzsch Feinmahltechnik GmbH
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Priority to PL14752251T priority Critical patent/PL3019276T3/pl
Publication of EP3019276A1 publication Critical patent/EP3019276A1/de
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C17/00—Disintegrating by tumbling mills, i.e. mills having a container charged with the material to be disintegrated with or without special disintegrating members such as pebbles or balls
    • B02C17/16—Mills in which a fixed container houses stirring means tumbling the charge
    • B02C17/161—Arrangements for separating milling media and ground material
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C17/00—Disintegrating by tumbling mills, i.e. mills having a container charged with the material to be disintegrated with or without special disintegrating members such as pebbles or balls
    • B02C17/16—Mills in which a fixed container houses stirring means tumbling the charge
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C17/00—Disintegrating by tumbling mills, i.e. mills having a container charged with the material to be disintegrated with or without special disintegrating members such as pebbles or balls
    • B02C17/16—Mills in which a fixed container houses stirring means tumbling the charge
    • B02C17/163—Stirring means

Definitions

  • the invention relates to an agitator ball mill with a grinding container according to the preamble of claim 1.
  • the invention also relates to a method for grinding with an agitator ball mill according to the preamble of claim 9.
  • Agitator ball mills are used to comminute and homogenize solid particles, with auxiliary grinding bodies being intensively moved by means of a stirring shaft.
  • the solid particles are crushed by impact, pressure, shear and friction.
  • agitator ball mills can be distinguished with regard to a horizontal or vertical alignment of the grinding chamber.
  • the auxiliary grinding bodies are activated by the agitator shaft, which can be equipped with agitators such as rods or discs.
  • the grinding chamber is usually filled to seventy to ninety percent with auxiliary grinding bodies in the size range from 0.03 to 9 mm in diameter.
  • the product to be ground flows continuously from a product inlet axially through the grinding chamber to a product outlet.
  • the auxiliary grinding bodies are then separated from the product flow by means of a separation system.
  • the throughput and the size of the grinding media are limited in closed agitator ball mills by a separating device.
  • the auxiliary grinding bodies should be securely retained in the grinding container and must not lead to grinding body compression or clogging even at high throughputs.
  • the separation devices can be designed in a known manner as gap systems, centrifugal systems or as external separation systems.
  • Known gap systems are, for example, sieve cartridges or gap tubes, which can be arranged at different points in the grinding chamber.
  • Centrifugal systems are also known from the prior art as dynamic separating devices in which the auxiliary grinding bodies are accelerated radially, as a result of which they are transported back into the grinding container due to the acting centrifugal force.
  • Such dynamic separation devices can, for example be formed by a cage rotating around a screen. They are used in particular with high throughput rates and when using very small grinding media.
  • Another agitator ball mill known from the prior art with a grinding media separation system includes a separating sieve with the aid of which the auxiliary grinding bodies are to be held in the grinding chamber.
  • the grinding media separation system is formed for this purpose from a rectangular, box-shaped sieve frame, a lower curved separating sieve with a rectangular shape and a grinding media collecting sieve located at a distance above.
  • the actual separation of the grinding media is realized by the rectangular separating sieve, which is fastened by means of holding elements on two opposite sides to the sieve frame, which is inserted into the grinding container with the two sieves as a closed structural unit.
  • EP 1 468 739 A1 discloses, in which the separating device is arranged in front of a material outlet and is formed from a separating element and a drive element driving this.
  • the separating element has two circular disks arranged coaxially to the chamber axis, between which several conveying or vane elements are arranged, symmetrically distributed around the center of the disk and leading inwards from the edge of the disk, which create a counter pressure on the material-grinding media mixture when the agitator ball mill is in operation generate, so that due to the centrifugal force and the different specific density, the auxiliary grinding bodies are separated from the product and transported back into the interior.
  • the separating devices for agitator ball mills known from the prior art can prevent auxiliary grinding bodies from entering the product outlet, but practice has shown that there is an increased concentration of auxiliary grinding bodies in the area of the separating device.
  • the actual grinding process does not take place in this area, but in the grinding chamber in an area in front of the separating device.
  • the low concentration of auxiliary grinding bodies in the particularly effective grinding area causes a reduced grinding performance, which can lead to unsatisfactory grinding results.
  • an agitator ball mill with a dynamic separating device is known, the separating device not only having radial openings but also axial openings through which a mixture of ground material and auxiliary grinding bodies can flow into a separating chamber of the separating device.
  • the grinding disks of the agitator are provided with axial through openings in their outer edge areas.
  • Agitator ball mills with a very similar structure are also from the U.S. Patents 5,797,550 and 5 333 804 known.
  • agitator ball mill with a dynamic separation device is in the DE 10 2007 043 670 A1 disclosed.
  • the separating device is arranged within the agitator shaft of the agitator ball mill, the agitating shaft having radial openings which extend axially over the area in which the separating device is arranged.
  • the invention is based on the object of specifying a device of the type mentioned at the beginning which enables an improved distribution of the auxiliary grinding bodies in the grinding chamber.
  • an agitator ball mill which has the features specified in patent claim 1.
  • the agitator shaft is provided with at least one recess which enlarges the dynamic separating device, which extends in the axial direction into the grinding chamber and is designed as described.
  • the invention is based on the idea that for a uniform distribution of the auxiliary grinding bodies in the grinding chamber, the separating device and the agitator shaft can bring about the return of the auxiliary grinding bodies into the grinding chamber by means of a suitable design and coupling.
  • the return of the auxiliary grinding bodies should in particular be able to take place as far as possible without an expensive redesign of the grinding container or by diverting the auxiliary grinding bodies outside the grinding container.
  • the dynamic separating device is coupled to the agitator shaft in such a way that at least one recess of the separating device is axially widened such that the widened recess extends into the grinding chamber in an axial direction in a region of the agitating shaft.
  • recesses are made in the agitator shaft, which are connected to the recesses in the separating device and expand them.
  • some of the auxiliary grinding bodies can be conveyed back into the grinding chamber through the recess in the agitator shaft.
  • the area of the recesses of the separating device is preferably smaller in the axial direction than the area with the widening recess.
  • the auxiliary grinding bodies are conveyed further into the grinding chamber in the axial direction through a thus shortened separation area or an extended area outside this separation area, so that the dwell time of the auxiliary grinding bodies in the grinding chamber is effectively increased.
  • the widening recess preferably runs axially parallel to the axis of rotation of the agitator shaft. It is particularly advantageous that the manufacturing outlay for making such a recess in the agitator shaft is comparatively low.
  • the widening recess extends at least partially in the axial direction in a helical or helical manner around the axis of rotation of the agitator shaft.
  • the flow velocity and thus also an exit location or re-entry location of the auxiliary grinding bodies into the grinding chamber can be positively influenced.
  • the helical recess runs counter to the direction of rotation of the agitator shaft, the flow speed increases in the axial direction towards the product inlet, whereby the re-entry point of the auxiliary grinding bodies can be shifted to a front area of the grinding chamber near the product inlet.
  • the widening recess extends essentially over the entire length of the agitator shaft. This means that the auxiliary grinding bodies can also be distributed over the entire length of the agitator shaft in the grinding chamber.
  • the distribution of the auxiliary grinding bodies can be influenced in an advantageous manner, for example by means of a suitably selected cross section of the channel.
  • the flow channel is introduced into the agitator shaft as a groove, at least in sections. It is also conceivable, for example, that the flow channel is made as a bore in the agitator shaft in an axial area near the separating device and is designed as a groove in a section near the product inlet.
  • the auxiliary grinding bodies are thereby guided in the axial direction through a flow channel and only exit into the grinding chamber near the product outlet.
  • the number of flow channels corresponds to the number of recesses in the separating device.
  • the even distribution of the auxiliary grinding bodies is further improved by the plurality of flow channels distributed over the circumference of the agitator shaft. With regard to this, it is also considered to be advantageous if the flow channels run parallel to one another.
  • auxiliary grinding bodies can additionally flow into the grinding chamber through a section of the agitator shaft coupled to the separating device.
  • experience has shown that during the grinding process there is an increased concentration of the auxiliary grinding bodies in the vicinity of the separating device, which means that the concentration of auxiliary grinding bodies decreases in the area of the agitator shaft.
  • the aim is to achieve the most uniform possible distribution of the auxiliary grinding bodies in the grinding chamber in order to allow the grinding process to run effectively.
  • a material to be ground for example in liquid form
  • a material to be ground is continuously fed into the interior of the grinding chamber via an inlet channel and conveyed in this together with the auxiliary grinding bodies to the product outlet.
  • the auxiliary grinding bodies are separated from the grinding material in the area of the product outlet by means of the separating device and the grinding material is conveyed out of the grinding container via the outlet channel.
  • the auxiliary grinding bodies flow from the separating device along the agitator shaft back into the grinding chamber, due to the fact that the resistance for the auxiliary grinding bodies, caused by the continuously conveyed grinding stock, is reduced due to the inventive design of the separating device and agitator shaft.
  • the exit location or exit area of the auxiliary grinding bodies is preferably set by setting and coordinating the agitator shaft speed, the cross-sectional shape of the return channels and / or the alignment of the widening recess in the agitator shaft.
  • the setting and coordination can be done manually or automatically via a control loop. Since the exit point is also dependent, among other things, on the throughput rate and thus the flow rate, which can change from grinding process to grinding process depending on the particular task and requirements for the grinding result, it should be adaptable. For example, it has been found that the exit point can move disadvantageously in the direction of the separating device at a comparatively high throughput rate.
  • the displacement of the exit point can be counteracted by a suitable choice of the speed of the agitator shaft and / or the configuration of the return channels.
  • the agitator shaft has at least one recess which extends in the axial direction and which is assigned to a dynamic separating device.
  • the recess is designed as a flow channel and is suitable for guiding auxiliary grinding bodies back into the grinding chamber.
  • the stirrer shaft has an end section on the separating device side, with which a connection of the flow channel to at least one of the recesses of the separating device can be established.
  • the dynamic separation device can be driven both by the agitator shaft and by means of a separate device.
  • the separating device is designed in such a way that the mixture formed from the auxiliary grinding bodies and the ground and / or dispersed material can flow to the product outlet via the recesses of the separating device.
  • part of the rotational energy is transferred to the auxiliary grinding bodies, whereupon the grinding bodies used for grinding are separated from the grinding material and transported back into the interior of the grinding chamber due to the radial centrifugal force and the different density.
  • the ground material itself passes through the separating device and leaves the grinding chamber via the outlet channel.
  • the grinding stock must overcome a relative pressure against the centrifugal force when flowing through the separating device, which is applied by a feed pump connected to the inlet channel of the agitator ball mill.
  • the auxiliary grinding bodies must move in the opposite direction to the flow generated by the feed pump The grinding chamber can be transported back, which in the known agitator ball mills usually leads to a build-up of the auxiliary grinding bodies in the area of the separating device.
  • the auxiliary grinding bodies can escape via these recesses.
  • the widening recess in the agitator shaft is introduced into the agitator shaft as a flow channel and at least in sections in the form of a groove.
  • the flow channel can be designed as a bore in the agitator shaft, at least in sections. This makes it possible for the auxiliary grinding bodies to flow in a certain direction and, for example, through a suitable combination of groove and bore, for the auxiliary grinding bodies to emerge from the agitator shaft only at a certain location.
  • At least one radially extending longitudinal wall of the flow channel is angled in such a way that a further radial force component caused by the angled channel wall acts on the auxiliary grinding bodies in the flow channel in addition to the centrifugal force.
  • a build-up of the auxiliary grinding bodies can thus be prevented by the auxiliary grinding bodies leaving the flow channel again relatively quickly.
  • the increased radial acceleration of the auxiliary grinding bodies resulting therefrom means that they are conveyed further in the radial direction into the grinding chamber, which contributes to an improved distribution of the auxiliary grinding bodies in the cross section of the grinding chamber.
  • at least one channel wall runs helically in the axial direction in order, for example, to allow the auxiliary grinding bodies to emerge again first or to a greater extent in a specific area of the grinding chamber.
  • the grinding elements of the agitator shaft are designed as grinding disks and have at least one opening close to the center, which is made as a continuous recess in the grinding disk.
  • Spacer sleeves are arranged between the grinding disks. The grinding disks are clamped axially with the spacer sleeves and form the agitator to which the dynamic cutting device is attached.
  • the return channel runs axially through the openings in the grinding disks.
  • the spacer sleeves preferably have a polygonal cross section, in particular a square cross section.
  • the spacers can also have a different cross section. It should be noted, however, that the cross section of the spacer sleeve is not circular, otherwise the desired pumping effect in the radial direction will not be achieved.
  • the opening in the grinding disks are made close to the center in such a way that auxiliary grinding bodies flowing through the opening close to the center are grasped by the spacer sleeves, accelerated and transported radially outwards.
  • the spacer bushings are preferably designed in such a way that their edges at least partially, particularly preferably completely, sweep over the opening area when the agitator shaft rotates.
  • the grinding disks can advantageously have radial recesses. These serve primarily to activate the auxiliary grinding bodies, but can also enable an additional backflow of the auxiliary grinding bodies according to the invention.
  • auxiliary grinding bodies can escape from the area of the separating device through the return channels, thereby preventing local accumulation of the auxiliary grinding bodies.
  • the even distribution of the auxiliary grinding bodies desired for an effective grinding process can be achieved through the recesses extending axially into the grinding chamber.
  • it is possible to adapt the distribution of the auxiliary grinding bodies to the respective grinding task by means of the described structural adjustments to the agitator shaft and / or the grinding parameters such as speed and flow rate.
  • Another advantage results from the fact that the advantageous effect is essentially based on the special design of the agitator shaft.
  • an agitator ball mill can also be modified with appropriate structural requirements and / or suitable adapter components.
  • the agitator ball mill 2 has a grinding container 4, in which a stirring shaft 8 provided with grinding elements 6 is arranged, whereby a grinding chamber 10 is formed between the grinding container 4 and the stirring shaft 8, into which the grinding elements 6 extend and into which at least one inlet channel 12 for ground material opens and in which a dynamic separating device 14 is provided for auxiliary grinding bodies, wherein the separating device 14 is provided with recesses 16 for the return of auxiliary grinding bodies and the agitator shaft 8 is provided with groove-shaped recesses 18 which expand the separating direction 14 and which extend in the axial direction towards the product flow The inlet area of the grinding chamber 10 extend.
  • a static separating device designed as a sieve 22 is connected upstream of a product outlet channel 20.
  • the groove-shaped recesses 18 in the agitator shaft 8 run axially parallel to the axis of rotation of the agitator shaft 8 and form return channels 18 for the auxiliary grinding bodies.
  • the return channels 18 and the recesses 16 in the separating device 14 merge, so that when the mill 2 is in operation, the auxiliary grinding bodies can escape via the return channels 18 in the direction of the product inlet, get back into the grinding chamber and are thus distributed.
  • the agitator ball mill 2 is constructed in such a way that the material to be ground is continuously conveyed into the grinding container 4 via the inlet channel 12 by means of a pump, not shown here, and flows in the grinding chamber 10 together with the auxiliary grinding bodies axially in the direction of the outlet channel 20 and is ground in the process.
  • the ground material flows with the grinding bodies through the recesses 16 in the separating device 14.
  • the ground material leaves the grinding container 4 via the outlet channel 20 and the auxiliary grinding bodies are moved radially outward due to the centrifugal forces acting on the auxiliary grinding bodies by the rotating separating device 14.
  • the continuously conveyed mixture of grinding material and auxiliary grinding bodies flows from the outside from the grinding chamber 10 into the recesses 16 of the separating device 14, which is why the return flow of the auxiliary grinding bodies is hindered.
  • the auxiliary grinding bodies flow into the return channel 18 in the agitator shaft 8 and are then further accelerated by the agitator shaft 8, which is also rotating, and conveyed back into the grinding chamber 10.
  • FIG 1b shows cross sections of the agitator ball mill 2 from FIG 1a on the one hand in the area of the separating device 14 as section A - A and on the other hand in the area of the agitator shaft 8 as section B - B.
  • the separating device 14 forms a kind of cage, through whose recesses 16 the grinding material auxiliary body -Mixture can flow and is thereby accelerated during operation of the mill 2.
  • the cross-sectional shape of the recesses 16 corresponds to the cross-sectional shape of the return channels 18 in the agitator shaft 8, which have a V-shape.
  • FIG 2a an agitator ball mill 2 is shown, in which the recesses 16 in the separating device are connected to the return ducts 18 in the agitator ball mill 2 via an axially introduced bore 26.
  • one or more return channels 18 are designed as a bore in a first section of the agitator shaft 8. It can thereby be achieved that the auxiliary grinding bodies flowing in the channel 18 only emerge into an area near the product inlet and are conveyed into the grinding chamber 10.
  • any other type of Recess possible which is suitable for guiding the auxiliary grinding bodies to an area or section with an open recess 18.
  • FIG 2b shows cross sections of the agitator ball mill 2 from FIG 2a on the one hand in the area of the separating device 14 as section A - A and on the other hand in the area of the agitator shaft 8 as section B - B.
  • the bore 26 as a connection between the recess 16 of the separating device and the return channel 18 is obliquely seen in the axial direction.
  • This section of the separating device 14 thus additionally acts as a pump for the auxiliary grinding bodies, which are sucked out of the area of the separating device 14 due to this pumping action in order to convey the auxiliary grinding bodies into the grinding chamber in an area of the agitator shaft 8.
  • FIG 3a An agitator ball mill 2 with one as in FIG 2a separator 14 shown is in FIG 3a shown.
  • the agitator shaft 8 has return channels 18 formed by axially extending bores 28 in the agitator shaft 8, which are interrupted in sections and open to the grinding chamber 10 like a return channel 18 introduced as a groove.
  • the bores 28 in the agitator shaft, like the bores 26 of the separating device 14, are made at an angle, viewed in the axial direction, and act as a pump.
  • the auxiliary grinding bodies can escape into the grinding chamber in the open sections of the return channels 18.
  • FIG 3b shows cross sections of the agitator ball mill 2 from FIG 3a on the one hand in the area of the separating device 14 as section A - A and on the other hand in the area of the agitator shaft 8 as section B - B.
  • FIG 4a essentially shows the agitator ball mill 2 FIG 1a with a dynamic separating device 14, which is coupled to the agitator shaft 8 and which has return channels 18 introduced as a groove in the agitator shaft 8, which axially expand the recesses 16 of the separating device 14, and with an additional dynamic element 30, which has radially extending channels or blades is provided.
  • the outlet end section 32 of the mill 2 and the adjoining additional dynamic element 30 run conically to one another, as a result of which a gap 34 is formed, which generates a flow in the radial direction towards the dynamic separating device 14.
  • the return channel 18 is closed off by a wall 36 on the product inlet side, as shown in the agitator ball mill 2 shown.
  • a disadvantageous inflow of the material to be ground into the return channel 18 from the product inlet side can be counteracted by the wall 36.
  • FIG 4b shows cross sections of the agitator ball mill 2 from FIG 4a on the one hand in the area of the separating device 14 as section A - A and on the other hand in the area of the agitator shaft 8 as section B - B.
  • the recesses 16 in the separating device 14 are made obliquely seen in the radial direction, which creates an additional pumping effect radially outward .
  • a sufficiently strong countercurrent can thus be generated to convey the auxiliary grinding bodies radially outward so that they can get back into the grinding chamber 10 via the return channel 18.
  • FIG. 5 An agitator ball mill 2 with an agitator shaft 8 with return channels 18 extending helically in the axial direction, which are introduced as a groove in the agitator shaft 8, is shown in FIG FIG 5 shown.
  • a flow is additionally generated in the axial direction towards the product inlet.
  • the recesses 16 of the separating device 14, are made axially parallel to the axis of rotation of the agitator shaft 8.
  • FIG 6 is an agitator ball mill 2 as in FIG 5 shown shown.
  • the agitator shaft 8 has only one return channel 18 which is also only coupled to a recess 16 of the separating device 14.
  • the auxiliary grinding bodies could thus be conveyed from all recesses 16 in the separating device 14 via the connecting recess into the return channel 18.
  • the return channel 18 could, however, also be introduced in a helical manner up to the separating device 14. Such an embodiment is in FIG 7 shown.
  • the separating device 14 has only one recess 16 which merges into the return channel 18.
  • FIGS 8 show examples of various embodiments of the agitator shaft 8 in cross section.
  • FIG FIG 8d pointed out, in which the agitator shaft 8 has recesses 18, but these are not designed as a channel 18 as in the figures described above.
  • a type of return channel 18 is formed by the rotation of the agitator shaft 8 during operation of the mill 2. Due to the continuous displacement of the mixture of the grinding material and auxiliary grinding body, a similarly designed one is created Grinding chamber 10 as in the case of a stirrer shaft 8 with a return channel 18, with the auxiliary grinding bodies being able to flow back below the grinding chamber 10.
  • Grinding disks 38 as grinding elements with at least one opening 40 close to the center are shown in FIG Figure 9 shown.
  • Spacer sleeves 42 are arranged between the grinding disks 38.
  • the grinding disks 38 and the spacer bushings 42 are braced axially and together with a dynamic separating device according to the invention, not shown here, form an agitator shaft.
  • Each grinding disk 38 in the Figures 9a to 9d is provided with a total of four openings 40 through which auxiliary grinding bodies can flow back.
  • the shapes of the grinding disks are illustrated by the dashed line and the spacer sleeves 42 have a polygonal cross section.
  • the openings 40 are made in the grinding disk 38 in such a way that a lower opening wall 44 as in FIG Figures 9a, 9b, 9c shown is flush with a surface 46 of the spacer sleeve 42.
  • the spacer sleeves 42 are designed in such a way that their edges completely sweep over the openings 40 when the agitator shaft 8 rotates.
  • the spacer sleeve 42 protrudes into the opening 40, seen in the axial direction, so that the opening 40 is only partially swept over when the agitator shaft 8 rotates.
  • Figures 9a, 9c and 9d shows a grinding disk 38 with a spacer sleeve 42 with a square cross-section
  • the grinding disk 38 in FIG Figure 9c additionally has a total of 4 radial recesses 48
  • Figure 9b shows a grinding disk 38 with a triangular shape and flattened or rounded corners, in which the spacer sleeve 42 has a shape corresponding to the grinding disk 38 in cross section.
  • FIGS. 9e and 9f show examples of further embodiments and arrangements according to the invention of a grinding disk 38 with an opening 40 close to the center and a spacer bushing 42
  • Figures 9 The variants shown are not exclusive, in particular a combination of different grinding disks 38 and spacer bushings 42 is conceivable as long as a backflow of the auxiliary grinding bodies according to the invention is guaranteed.
  • the agitator ball mill 2 is specifically designed for an effective distribution of the auxiliary grinding bodies in the grinding chamber 10. Since the auxiliary grinding bodies are conveyed back into the grinding chamber 10 in the axial direction along the agitator shaft 8 by the separating device 14, an increased concentration of auxiliary grinding bodies in the region of the separating device 14 is prevented.
  • unmilled product that flows close to the center along the agitator shaft 8 from the inlet area of the agitator ball mill 2 in the axial direction to the separating device 14 is also conveyed back in the radial direction into the grinding chamber 10, into an outer, more effective grinding area.
  • this effect comes into play particularly in grinding disks 38 with a radial recess 48, since unmilled product can flow back in the axial direction close to the center, particularly through the recesses 48 in the grinding disk 38.
  • the risk of unmilled product reaching the outlet channel 20 is minimized by the pumping action of the spacer bushings 42.

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  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Grinding (AREA)
  • Mixers Of The Rotary Stirring Type (AREA)
EP14752251.0A 2013-07-08 2014-06-25 Rührwerkskugelmühle mit axialkanälen Active EP3019276B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL14752251T PL3019276T3 (pl) 2013-07-08 2014-06-25 Młyn kulowy z mieszadłem z kanałami osiowymi

Applications Claiming Priority (2)

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DE102013107190 2013-07-08
PCT/DE2014/000330 WO2015003676A1 (de) 2013-07-08 2014-06-25 Rührwerkskugelmühle mit axialkanälen

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EP3019276A1 EP3019276A1 (de) 2016-05-18
EP3019276B1 true EP3019276B1 (de) 2020-11-25

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US (2) US10610871B2 (enrdf_load_stackoverflow)
EP (1) EP3019276B1 (enrdf_load_stackoverflow)
JP (1) JP2016528032A (enrdf_load_stackoverflow)
KR (1) KR20160029825A (enrdf_load_stackoverflow)
CN (1) CN204170782U (enrdf_load_stackoverflow)
BR (1) BR112016000066B1 (enrdf_load_stackoverflow)
DE (1) DE102013111762A1 (enrdf_load_stackoverflow)
ES (1) ES2845601T3 (enrdf_load_stackoverflow)
PL (1) PL3019276T3 (enrdf_load_stackoverflow)
RU (1) RU2663485C2 (enrdf_load_stackoverflow)
WO (1) WO2015003676A1 (enrdf_load_stackoverflow)

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KR101708376B1 (ko) * 2016-03-29 2017-02-21 세우씨앤이(주) 비드 밀
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ES2698254T3 (es) * 2016-10-18 2019-02-01 Bachofen Willy A Ag Molino de bolas con mecanismo agitador
EP3311922B1 (de) 2016-10-18 2018-12-05 Willy A. Bachofen AG Rührwerkskugelmühle
DE102017201418B3 (de) * 2017-01-30 2018-06-28 Netzsch-Feinmahltechnik Gmbh Rührwerksmühle
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BR112016000066A2 (enrdf_load_stackoverflow) 2017-07-25
US10610871B2 (en) 2020-04-07
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RU2663485C2 (ru) 2018-08-06
KR20160029825A (ko) 2016-03-15
PL3019276T3 (pl) 2021-05-17
US20160107163A1 (en) 2016-04-21
BR112016000066B1 (pt) 2021-11-16
CN204170782U (zh) 2015-02-25
DE102013111762A1 (de) 2015-01-08
US11141737B2 (en) 2021-10-12
JP2016528032A (ja) 2016-09-15
US20190358639A1 (en) 2019-11-28
ES2845601T3 (es) 2021-07-27
EP3019276A1 (de) 2016-05-18

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