CH715325A2 - Agitator ball mill with a wear protection sleeve, wear protection sleeve and method for producing a wear protection sleeve for an agitator ball mill. - Google Patents

Abstract

The invention relates to an agitator ball mill with a grinding container (51) extending along a horizontal or vertical axis (L50), a grinding material inlet and a product outlet (72), a stirring shaft which can be rotated about the horizontal or vertical axis (L50) within the grinding container (51) with stirring elements, a wear protection sleeve (30) being associated with the stirring shaft in the area of the product outlet (72). The wear protection sleeve (30) is made in one piece, the wear sleeve (3) being a 3D-printed component which consists of a ceramic material, has elevations (34) on an outer surface and comprises at least one cooling device (37) or is as formed part of a cooling system. The invention further relates to a wear protection sleeve for an agitator ball mill and a method for producing a corresponding wear protection sleeve.

Description

The present invention relates to an agitator ball mill with a wear protection sleeve, a wear protection sleeve and a method for producing a wear protection sleeve for an agitator ball mill according to the features of the independent claims.

State of the art

The invention relates to an agitator ball mill, in particular an agitator for an agitator ball mill. The agitator ball mill is a device for coarse, fine and very fine comminution or homogenization of regrind. An agitator ball mill consists of a vertically or horizontally arranged, mostly approximately cylindrical grinding container, which is filled to 70% to 90% with auxiliary grinding media. In the case of agitator ball mills, the grinding container is usually stored stationary. Many conventionally known mills are filled through a central opening in one of the end walls. Alternatively, the filling can also be done directly via the grinding cylinder. The product to be ground flows continuously during the grinding process from a product inlet axially through the grinding chamber to a product outlet. The suspended solids are crushed or dispersed between the grinding media by impact and shear forces. The grinding auxiliary bodies are then separated from the product stream in an outlet area. The discharge depends on the design and is carried out, for example, through a sieve at the end of the mill.

The agitator is usually formed by an agitator shaft, which serves to rotate agitator elements in the form of disks or radially projecting pins, in particular to deagglomerate and comminute solids of the ground material distributed in liquid. The agitator shaft is usually driven by a motor. Disk stirrers with a plurality of grinding disks arranged on a stirrer shaft are used in particular as suitable stirring elements. The grinding disks are usually circular and can be provided with through openings. The product flow is ensured in particular via the passage opening.

Between the inside of the grinding cylinder and the agitator, an annular grinding gap is formed, in which the material to be ground is to be comminuted during operation of the agitator ball mill. The agitator is driven in rotation and thus loads the material to be ground within the grinding gap, as a result of which it is comminuted, which is supported on the one hand by the auxiliary grinding bodies and on the other hand by the stirring elements of the agitator. In particular, the material to be ground and the auxiliary grinding bodies are moved intensively by means of a stirring shaft. The solid particles of the ground material are crushed by impact, pressure, shear and friction.

Many processes, chemical, mechanical or other, run with the generation of process heat, which can negatively affect the process itself or the starting materials used, for example, because the substances involved in the process are temperature sensitive or the temperature change affects the process speed and thus orderly process management is difficult. For this reason, it is common to stabilize a process flow, for example by dissipating the process heat generated by means of suitable cooling devices or processes. Processes running in containers are usually tempered via the container wall, for example by cooling or hot water pipes running on the wall or by guiding another outer container, which is spaced radially from the first container, around the first container, so that there is a cavity between the two containers forms, through which a fluid flow, which can be a hot water flow or a coolant flow, can be conducted to transport the process heat.

Heat also arises in the grinding process. Depending on the product, this heat must be dissipated or heat generation must be prevented. The problem exists particularly with agitator ball mills with a large grinding volume or when a higher power input is desired. For cooling during the grinding process, it is provided, for example, to design the grinding cylinder to be coolable. For example, the published patent application DE 361 147 A1 describes the equipment of the grinding container with a cooling jacket as known prior art. This document also discloses that the agitator rotor can also be provided with at least one cooling channel on its circumference. A grinding container with a cooling jacket is also shown in the published patent application WO 2007/042 059 A1. Furthermore, the agitator mill described in this document has an inner stator, which can also be cooled. The agitator is cup-shaped and comprises an annular cylindrical rotor.

[0007] As already mentioned in connection with DE 3 614 721 A1, cooling can alternatively or additionally also be implemented via the agitator rotor. The published patent application DE 3 015 631 A1 describes an agitator consisting of an inner and an outer cylinder, between which an annular cooling space is formed, a cooling line supplying cooling medium being arranged axially parallel within the cooling chamber for cooling and being connected to a supply pipe for coolant.

From a certain size, agitator shafts or ceramic agitators must be constructed from several components. A lot of grinding work is necessary to produce the individual parts to each other, which means that the costs are very high due to the necessary working time. In addition, when the agitator shaft is assembled from a plurality of parts, so-called dead spaces arise, in which ground material and / or auxiliary grinding bodies can become lodged and thus contaminate the machine room. Such multi-part ceramic stirrer shafts are also very sensitive to breakage, especially during assembly, disassembly, cleaning and maintenance. In addition, it has so far not been possible to produce ceramic rotors with cooling.

description

The object of the invention is to produce a wear protection sleeve for an agitator ball mill easily and inexpensively, in particular a coolable wear protection sleeve for use in high-performance agitator ball mills.

The above object is achieved by a wear protection sleeve for an agitator ball mill, an agitator ball mill and a method for producing a wear protection sleeve for an agitator ball mill, which comprise the features in the independent claims. Further advantageous configurations are described by the subclaims.

The invention relates to an agitator ball mill, a wear protection sleeve for an agitator ball mill and a method for producing a wear protection sleeve for an agitator ball mill. The agitator ball mill described here is, in particular, an agitator ball mill with a grinding container extending along a horizontal or vertical axis. A regrind inlet is provided for adding the regrind. A product outlet is provided for the removal of the product in the form of ground material. The agitator ball mill comprises an agitator shaft with agitating elements which can be rotated about the horizontal or vertical axis within the grinding container. In the area of the product outlet, the agitator shaft is assigned a wear protection sleeve which is formed in one piece and is formed by a component which is produced by SD printing and which consists of a ceramic material. The wear protection sleeve is particularly preferably made from silicon carbide (SiC), in particular sintered silicon carbide (SSiC), from silicon carbide with free silicon (SiSiC), from silicon nitride, from zirconium oxide or from mixed ceramics. Silicon carbide ceramics have a high wear resistance, low thermal shock sensitivity, low thermal expansion, high thermal conductivity, good resistance to acids and alkalis and are also light and retain their positive properties up to temperatures above 1400 ° C. In addition, silicon carbide is toxicologically safe and can therefore also be used in the food sector. Silicon nitride has a reduced hardness in comparison to silicon carbide, but a sintering process can cause a recrystallization of the β-silicon nitride crystals, which leads to increased fracture toughness of the material. The high fracture toughness in combination with small defect sizes gives silicon nitride one of the highest strengths among the engineering ceramic materials. The combination of high strength, low coefficient of thermal expansion and a relatively small modulus of elasticity make silicon nitride ceramic particularly suitable for components subject to thermal shock. In contrast to other ceramic materials, zirconium oxide has a very high resistance to the spread of cracks. In addition, zirconium oxide ceramic has a very high thermal expansion and is therefore often chosen when realizing connections between ceramic and steel.

It is preferably provided that the wear protection sleeve has elevations at least in regions on its outer surface and comprises at least one cooling device and / or forms part of a cooling system.

[0013] The wear protection sleeve essentially has a hollow cylindrical shape and a longitudinal axis. The longitudinal axis of the wear protection sleeve is arranged within the agitator ball mill coaxially with the longitudinal axis of the grinding container and coaxially with the longitudinal axis of the agitator shaft. The elevations can be designed, for example, in the form of cams which extend radially outwards. The elevations or cams are preferably formed in a regular pattern on the outer surface of the wear protection sleeve. In particular, the elevations can, on the one hand, be arranged in an aligned arrangement in rows parallel to the longitudinal axis of the wear protection sleeve. Alternatively or additionally, the elevations can be arranged in parallel rows along circumferential lines of the wear protection sleeve.

The shape of the elevations can assume any geometrical shape, both in axial section and in radial view, for example trapezoidal, with rounded corners, with chamfered edges, etc. In particular, it is provided that a connecting surface of the elevations formed on the cylindrical base body of the wear protection sleeve is proportionate is large, in particular in relation to the radial height of the elevations.

It is preferably provided that the wear protection sleeve including elevations and optionally including the cooling device is made in one piece from a ceramic material, in particular using a 3D printing method. In this way it is possible to produce a component with internal cavities that can be manufactured using conventional methods such as injection molding or the like. would not be producible in one process step without further post-processing, for example without subsequent drilling of holes or the like. However, it is now possible to easily and inexpensively form at least one integrated cooling device within the wear protection sleeve.

Due to the shape of the elevations described above, the sensitivity of the elevations to break-off or break-out in ceramic material is significantly reduced. The one-piece design of the wear protection sleeve promotes both stability and heat conduction, as there are no potential break points and heat conduction barriers.

The agitator shaft of the agitator ball mill has, on the side facing the product outlet, an inner cavity at least in regions, in particular the end of the agitator shaft facing the product outlet is designed to be open to the inner cavity. In particular, it is provided that the wear protection sleeve projects partially into the hollow interior area of the agitator shaft, the wear protection sleeve extending from the free end of the agitator shaft from the product outlet in the direction of the regrind inlet. It is provided that the wear protection sleeve in the area of the cams has a maximum outer diameter that is less than an inner diameter of the inner cavity of the agitator shaft.

At an end region of the wear protection sleeve, a fastening area, for example a flange, can be provided in order to position and secure the wear protection sleeve in or on the agitator ball mill. The grinding container base preferably has a corresponding receptacle for the flange of the wear protection sleeve, wherein the wear protection sleeve can be fixed to the grinding container base by means of suitable fastening options, for example screwing, jamming or the like. The fixation is preferably detachable, so that the wear protection sleeve can be replaced if necessary, for example in the event of defects on the wear protection sleeve. The fastening area is preferably also part of the one-piece wear protection sleeve and, in particular, is not subsequently attached to the wear protection sleeve.

According to one embodiment, it is provided that the cooling device of the wear protection sleeve is designed as at least one cooling channel, which preferably extends at least in regions parallel to the longitudinal axis of the wear protection sleeve. In particular, the cooling device can provide at least two cooling duct sections, which are connected to one another in terms of flow in a deflection area, the coolant flowing through the two cooling duct sections in opposite directions of flow.

According to one embodiment it is provided that the cooling device comprises interconnected, meandering arranged cooling channel sections, for example at least two cooling channel sections each extend parallel to the longitudinal axis of the agitator shaft, with a deflection area being formed between the two parallel cooling channel sections . If one considers a wear protection sleeve in axial cross section, then in this embodiment the cooling duct sections are preferably each arranged at the same radial distance from the center point defined by the longitudinal axis of the wear protection sleeve. A coolant inlet and a coolant outlet with connection to the at least one cooling channel or the at least two cooling channel sections are preferably provided in the fastening area of the wear protection sleeve. Corresponding to this, the grinding container base has corresponding coolant connections, so that the coolant can be introduced into the wear protection sleeve and removed again via the grinding container base.

The coolant is introduced via the coolant inlet into a first cooling channel section and flows through it in a first flow direction parallel to the longitudinal axis of the wear protection sleeve. In the end region of the wear protection sleeve, which lies opposite the coolant inlet or fastening region, a deflection region is formed between the first cooling duct section and a second cooling duct section, which connects the two cooling duct sections to one another in terms of flow. The coolant is diverted and flows through the second cooling channel section in a second flow direction opposite to the first flow direction. A further deflection area is formed between the second cooling duct section and a third cooling duct section, which connects the two cooling duct sections to one another in terms of flow technology. The coolant is diverted and flows through the third cooling duct section in the first flow direction etc. After flowing through a last cooling duct section in the second flow direction, the coolant is discharged through the coolant outlet. The meandering arrangement of the cooling channel sections creates a large cooling surface and optimal cooling of the agitator ball mill is achieved in the area of the product outlet.

[0022] Alternatively, it can be provided that the at least one cooling channel is at least partially spiral-shaped around the longitudinal axis of the wear protection sleeve. The coolant flows through the cooling channel and is guided in a spiral around the longitudinal axis. The flow direction of the coolant in the spiral cooling channel section can have a movement component in the first flow direction or a movement component in the second flow direction.

According to a further embodiment it is provided that the cooling device is designed as a so-called countercurrent cooling. It is also provided here that the cooling device comprises a plurality of cooling channel sections which are each parallel, in particular extending parallel to the longitudinal axis of the wear protection sleeve. If one considers a wear protection sleeve in axial cross section, then in this embodiment two cooling channel sections are arranged on a radial which extends from a center point defined by the longitudinal axis of the wear protection sleeve to the outer circumference of the wear protection sleeve.

In countercurrent cooling, the coolant flows through the cooling channel sections arranged on a common radial one after the other, so that one of the two cooling channel sections arranged on the same radial is flowed through in a first flow direction, while the other of the two cooling channel sections from the coolant in flows in the opposite direction. To deflect the direction of flow of the coolant, a deflection region is provided in an end region of the wear protection sleeve, which connects the two cooling duct sections with one another in terms of flow. In this embodiment, too, the coolant is preferably fed in and out via the fastening area of the wear protection sleeve and the bottom of the grinding container and first flows through a first cooling channel section arranged closer to the center of the wear protection sleeve in the direction of the ground material inlet of the agitator ball mill and then through a second cooling channel section on the same radial , which, however, is arranged closer to the outer surface of the wear protection sleeve, in the direction of the product outlet.

In countercurrent cooling, it can be provided that a first annular gap is assigned to the coolant inlet, via which the coolant is simultaneously supplied to a plurality of first cooling channel sections. Furthermore, a second annular gap can be provided, into which the coolant flows from all second cooling channel sections and is discharged via the coolant outlet.

With the help of countercurrent cooling it is achieved that the freshest and thus coolest coolant is first led into an area of the agitator ball mill in which the ground material is the warmest. This is in particular the area near the product outlet after the millbase has flowed through the agitator ball mill in the conveying direction from the millbase inlet side. In particular, the coolant flows through the wear protection sleeve on the outer circumferential surface of the wear protection sleeve in the opposite direction to the conveying direction of the ground material within the terminal inner cavity of the agitator shaft. The cooling process can be further optimized with this countercurrent cooling.

In particular, it can be provided in the embodiments described here with meandering cooling, spiral cooling or with countercurrent cooling that the cooling channel sections extend parallel to rows of the elevations on the outside of the wear protection sleeve and thus preferential cooling of the wear protection sleeve in the region of the Surveys take place because in this area, due to the stresses on the material to be ground and / or the auxiliary grinding bodies, the surveys cause particularly strong heating within the agitator ball mill.

A further possibility for cooling the agitator ball mill in the area of the product outlet comprises a specially designed receiving part in operative connection with a corresponding wear protection sleeve. In particular, the product outlet is formed by a receiving part that is arranged in regions within the agitator shaft. In particular, the receiving part is partially arranged in the inner cavity of the agitator shaft, which extends from the free open end of the agitator shaft near the bottom of the grinding container in the direction of the grist inlet. Furthermore, the receiving part extends in some areas through the bottom of the grinding bowl of the agitator ball mill. The receiving part has an essentially hollow cylindrical basic shape with a longitudinal axis and a cylindrical inner space that is open on both sides and is arranged within the agitator ball mill in such a way that the longitudinal axis of the receiving part and the stirring shaft are arranged coaxially. The interior in particular forms an outlet channel with an open end area as a product outlet. The end region of the receiving part forming the product outlet is at least partially surrounded by a wear protection sleeve, while a separating device, in particular a separating sieve or the like, is located on the opposite end region arranged within the inner cavity of the agitator shaft. is arranged. Sufficiently shredded regrind - which is referred to below as the product - passes through the separating device into the cylindrical interior of the receiving part and is conveyed to the product outlet in the bottom of the grinding container by the product that is pressing. The separating device prevents auxiliary grinding bodies from getting into the interior of the receiving part. Instead, the auxiliary grinding bodies are conveyed back into the grinding gap via through openings in the stirring shaft.

The receiving part has at least one profile, which forms a cooling system in operative connection with the wear protection sleeve. In particular, a partial area of the outer circumferential surface of the receiving part is profiled near the product outlet and has a plurality of elevations and / or depressions. For example, the partial area is designed as an external thread with depressions, the depressions being spaced apart and separated from one another by elevations. A wear protection sleeve is placed on the receiving part in such a way that a sealing connection is established between the wear protection sleeve and the receiving part, cooling channels being formed in the area of the profiling between the receiving part and the wear protection sleeve. In particular, there is a sealing connection between the elevations of the external thread which extend in a spiral around the receiving part and the inner lateral surface of the wear protection sleeve. As a result, the depressions in the receiving part form a cooling channel, which extends spirally around the receiving part of the cooling system formed jointly by the receiving part and the wear protection sleeve.

Another component of the cooling system is formed by at least one inner cooling channel of the receiving part or the wear protection sleeve, coolant preferably being supplied via a coolant inlet first into the inner cooling channel and then to the cooling channel formed between the receiving part and the wear protection sleeve. The coolant flows through the outer cooling channel, preferably in a direction directed towards the product outlet, and is then discharged via a coolant outlet. The coolant outlet is preferably formed on the receiving part adjacent to the product outlet. Alternatively, it can be provided that the coolant is introduced from the cooling duct into a corresponding duct section of the wear protection sleeve and is drained off via the latter. The cooling system is used in particular to cool the product as it passes through the outlet channel of the receiving part and then exits through the product outlet. Alternatively, depending on the production conditions, it can also be provided that the coolant is first led via the outer cooling channel from the product outlet side in the direction of the regrind inlet side and after deflection flows through the inner cooling channel to the product outlet. Furthermore, embodiments of the receiving part are conceivable for the person skilled in the art, in which the profiling for forming a suitable cooling channel is formed on the end region of the receiving part opposite the product outlet side or largely over the entire length of the receiving part.

According to a further embodiment, it can be provided that a spiral cooling channel is formed within the wear protection sleeve, which runs at least partially in a spiral around the longitudinal axis of the wear protection sleeve. The coolant flows through the cooling channel and is guided in a spiral around the longitudinal axis of the wear protection sleeve. The direction of flow of the coolant in the spiral cooling channel section can be a movement component in the direction of the product outlet or a movement component in the opposite direction, i.e. away from the product outlet. The coolant is guided, for example, analogously to the spiral coolant guide, as has already been described above in connection with the receiving part, only that the cooling channel is completely formed within the wear protection sleeve and is not formed by the interaction of the wear protection sleeve and the receiving part. In addition, an outer coolant spiral and an inner coolant spiral can be formed, the outer coolant spiral being formed closer to the outer lateral surface of the wear protection sleeve and the inner coolant spiral closer to the inner lateral surface of the wear protection sleeve. Now, for example, the coolant can first flow through the inner coolant spiral in a flow direction with a movement component against the flow direction of the product within the product outlet and thereby cool it. The coolant is then removed again from the wear protection sleeve via the outer coolant spiral. Depending on the production conditions, the coolant can also be supplied via the outer coolant spiral and removed again via the inner coolant spiral.

At this point it should be expressly mentioned that all aspects and design variants which were explained in connection with the device according to the invention relate to or may be partial aspects of the method according to the invention. If, therefore, at one point in the description or also in the definition of claims for the device according to the invention, certain aspects and / or relationships and / or effects are mentioned, this applies equally to the method according to the invention. Conversely, the same applies, so that all aspects and design variants which have been explained in connection with the method according to the invention also relate to or can be partial aspects of the device according to the invention. Therefore, if there are certain aspects and / or relationships and / or effects at a point in the description or also in the definition of claims for the method according to the invention, then this applies equally to the device according to the invention.

Figure description

In the following, exemplary embodiments are intended to explain the invention and its advantages with reference to the attached figures. The size ratios of the individual elements to one another in the figures do not always correspond to the real size ratios, since some shapes are simplified and other shapes are shown enlarged in relation to other elements for better illustration. <tb> Fig. 1 <SEP> shows a side view of a wear protection sleeve. <tb> Fig. 2 <SEP> shows a perspective view of a wear protection sleeve. <tb> Fig. 3 <SEP> shows a perspective view of a wear protection sleeve cut along a section line C-C according to FIG. 1. <tb> Fig. 4 <SEP> shows a cross section of a wear protection sleeve cut along the section line C-C according to FIG. 1. <tb> Fig. 5 <SEP> shows a longitudinal section through an agitator ball mill with a wear protection sleeve according to FIGS. 1 to 4. <tb> Fig. 6 <SEP> shows a cross section through an agitator ball mill according to FIG. 5 along a section line BB. <tb> Fig. 7A to 7E <SEP> show different representations of a second embodiment of a wear protection sleeve. <tb> Fig. 8A to 8E <SEP> show different representations of a third embodiment of a wear protection sleeve. <tb> Fig. 9A to 9E <SEP> show different representations of a receiving part. <tb> Fig. 10 <SEP> shows a longitudinal section through an agitator ball mill with a receiving part according to FIGS. 9A to 9E. <tb> Fig. 11 <SEP> shows a partial section of the outside of a wear protection sleeve.

Identical reference numerals are used for identical or identically acting elements of the invention. Furthermore, for the sake of clarity, only reference numerals are shown in the individual figures which are necessary for the description of the respective figure. The illustrated embodiments merely represent examples of how the device according to the invention or the method according to the invention can be designed and do not constitute a final limitation.

1 to 4 show different views and sectional views of a wear protection sleeve 30 designed in one piece according to the invention. Such a wear protection sleeve 30 is preferably used in an agitator ball mill 50, as will be explained in more detail below with reference to FIGS. 5 and 6.

The wear protection sleeve 30 is preferably formed in one piece and in particular made of a ceramic material and can be produced, for example, from a ceramic material using the SD printing method. The ceramic material can be, for example, silicon carbide (SiC), in particular sintered silicon carbide (SSiC), silicon carbide with free silicon (SiSiC), silicon nitride, zirconium oxide or mixed ceramics. Silicon carbide ceramics have a high wear resistance, low thermal shock sensitivity, low thermal expansion, high thermal conductivity, good resistance to acids and alkalis and are also light and retain their positive properties up to temperatures above 1400 ° C. In addition, silicon carbide is toxicologically safe and can therefore also be used in the food sector. Silicon nitride has a reduced hardness compared to silicon carbide. However, a stalk recrystallization of the β-silicon nitride crystals can be brought about by a sintering process, which leads to an increased fracture toughness of the material. The high fracture toughness in combination with small defect sizes gives silicon nitride one of the highest strengths among the engineering ceramic materials. The combination of high strength, low coefficient of thermal expansion and a relatively small modulus of elasticity make silicon nitride ceramic particularly suitable for components subject to thermal shock. In contrast to other ceramic materials, zirconium oxide has a very high resistance to the spread of cracks. In addition, zirconium oxide ceramic has a very high thermal expansion and is therefore often chosen when realizing connections between ceramic and steel.

The wear protection sleeve 30 is at least partially cylindrical, in particular the wear protection sleeve 30 has as the base body 32 a hollow cylinder 33 with a longitudinal axis L30, on the outside of which elevations 34, in particular in the form of cams 35 described in more detail below, are formed. The outer surfaces of the cams 35 and the outer surfaces of the cylindrical base body 32 not covered by cams 35 together form the outer surface of the wear protection sleeve 30.

The hollow cylinder 33 has a maximum outer diameter d30, which is smaller than a smallest inner diameter of a third inner region III of a stirring shaft 1 described below (see FIGS. 5 and 6). A fastening area, for example a flange 36, can be provided at an end region of the wear protection sleeve 30 in order to position and fasten the wear protection sleeve 30 in or on the agitator ball mill 50, in particular around the wear protection sleeve 30 on the grinding container base 59, in particular in a suitable receptacle on the grinding container base 59 to be determined - see FIG. 5.

The elevations 34 or cams 35 are preferably arranged in a regular pattern. In particular, the cams 35 are arranged in rows 100 parallel to the longitudinal axis L30 of the wear protection sleeve 30, and the cams 35 are also arranged in parallel rows along circumferential lines 101 of the wear protection sleeve 30.

As can be seen in the sectional views of FIGS. 3 and 4, the wear protection sleeve 30 shows a largely circular cross section, the center of which runs through a longitudinal axis L30 of the wear protection sleeve 30.

The wear protection sleeve 30 comprises at least one cooling device 37. In the illustrated embodiment, the cooling device 37 is designed as a counterflow cooling. In particular, it is provided that the cooling device 37 comprises a plurality of cooling channel sections 38a, 38b, each in parallel, wherein two parallel cooling channel sections 38a, 38b are each arranged on a radial R, which extends from the longitudinal axis L30 to the outer circumferential surface of the base body 32 the wear protection sleeve 30 extends from. In particular, it can be provided that the cooling duct sections 38a, 38b parallel to rows 100 of the cams. 35 extend and thus a preferred cooling of the wear protection sleeve 30 takes place in the area of the cams 35, since in this area a particularly strong heating takes place within the agitator ball mill due to the stress on the ground material and / or the grinding auxiliary bodies by the cams 35.

In countercurrent cooling, it is provided in particular that a coolant is introduced into the cooling channel sections 38a, 38b that flows through the two cooling channel sections 38a, 38b, which are each on a common radial R, one after the other. It is preferably provided that the coolant flows through the inner cooling duct section 38a first. The coolant is then deflected in the end region of the wear protection sleeve 30, which lies opposite the fastening flange 36, and now flows in the opposite direction through the outer cooling duct section 38b.

In particular, it can be provided that a first annular gap or the like on the flange 36 or within the flange 36. is formed so that coolant can simultaneously enter all inner cooling duct sections 38a. Furthermore, a second annular gap can be provided on the flange 36 or within the flange 36, via which the coolant can be removed simultaneously from all outer cooling duct sections 38b.

5 and 6 show different representations of an agitator ball mill 50 with a wear protection sleeve 30, as has been described in connection with FIGS. 1 to 4, in particular FIG. 5 shows a longitudinal section through the agitator ball mill 50 and FIG. 6 5 shows a cross section along a section line BB according to FIG. 5.

The agitator ball mill 50 comprises a cylindrical grinding container 51 which extends along a horizontal axis L50 and has an inner circumferential surface 52. The grinding container 51 can be formed from a metal or, analogously to the stirring shaft 1, from a ceramic material. It can further be provided that the grinding container is designed to be coolable and comprises, for example, an outer cylinder 53 and an inner cylinder 54, between which a cooling space 55 is formed, into which coolant K is introduced via a suitable coolant inlet (not shown) and a coolant outlet (not shown) can be. The grinding container 51 further comprises a grinding container cover 58 and a grinding container base 59.

A stirring shaft 1 with a longitudinal axis L is arranged horizontally within the grinding container 51. The longitudinal axis L of the agitator shaft 1 also represents its axis of rotation and is also congruent with the horizontal axis L50 of the grinding container 51. The agitator shaft 1 has a cylindrical base body 2 with a longitudinal axis L, wherein 2 stirring elements, in particular stirring rods, cams or grinding disks, are arranged and / or formed on the outer surface of the cylindrical base body.

The agitator shaft 1 has three sections, in particular a first terminal section I, a second central section II and a third terminal section III. The agitator shaft 1 is connected with its first terminal section I to a drive shaft 70 of the agitator ball mill 50. For this purpose, a shaft holder 7 is formed in the first terminal section I, for example. The agitator shaft 1 is at least partially designed as a hollow shaft, in particular the second partial section II and the third partial section III and possibly the first partial section I each have interior areas. In particular, the second middle section II has a first hollow interior or interior area 12 and the third section III has a second hollow interior or interior area 13. These preferably also have a cylindrical shape, the longitudinal axis of which is congruent with the longitudinal axis L of the agitator shaft 1. Furthermore, it is provided that the third section III is designed to be open at the end and, in particular, to have a further enlarged hollow interior in this open area.

It can also be provided that through openings 15 are formed in the second middle section II between the hollow interior area 12 and the outer surface 5 of the agitator shaft 1, through which the auxiliary grinding bodies MH are returned to the grinding gap MS described below.

The drive shaft 70 for the agitator shaft 1 extends through the grinding container cover 58 and is connected to a drive (not shown). The drive can be, for example, an electric motor or the like. act. The drive shaft 70 is connected in a rotationally fixed manner to the agitator shaft 1, in particular the end of the drive shaft 70 protruding into the grinding container 51 engages in the shaft receptacle 7 in the first partial section i of the stirring shaft 1. Furthermore, on the grinding container cover 58 or on the grinding container 51 adjacent to the grinding container cover 58 a regrind inlet (not shown) is provided, through which the regrind is filled into the agitator ball mill 50. A product outlet 72 is provided in the grinding container bottom 59, through which the ground product P leaves the agitator ball mill 50.

An annular grinding gap MS is formed between the inner lateral surface 52 of the grinding container 51 and an outer lateral surface of the stirring shaft 1, in particular in the area of the stirring elements 3. During operation of the agitator ball mill 50, the grinding stock / grinding aid mixture G is located therein. By rotating the agitator shaft 1 in combination with the grinding aid bodies (not shown), the grinding stock is moved in the grinding gap MS from the grinding stock inlet side to the product outlet side and is thereby stressed so that it is comminuted , for example by impacting regrind particles against one another, by impacting regrind particles on auxiliary grinding bodies MH, by shear forces etc. To reinforce the grinding effect, it can be provided that projections such as cams, rods or the like are also arranged on the inner surface 52 of the grinding container 51 can be, which on the one hand bring about additional mixing of the regrind / auxiliary grinding mixture G and on the other hand, for example, increases the number of collision processes taking place in the grinding gap MS and thus increases the size reduction effect of the agitator ball mill 50 .

The product outlet 72 is formed by a so-called receiving part 75, which extends through a central opening in the grinding container bottom 59. Another embodiment of a receiving part 75 will be described in connection with FIGS. 9A to 9E. The receiving part 75 extends coaxially, at least in some areas, in the inner cavity of the agitator shaft 1 and is surrounded in some areas by the wear protection sleeve 30, in particular the receiving part 75 extends coaxially within the first interior area 12 of the second middle section II of the agitator shaft 1 and the second interior area 13 of the third terminal section II of the agitator shaft 1 and through the grinding container bottom 59. A separating device 40, in particular a separating sieve 41, is arranged on the end region of the receiving part 75 arranged within the first interior area 12, which is permeable for sufficiently ground material to be ground - which is referred to below as the product - but prevents the auxiliary grinding bodies MH from reaching the product outlet 72 reach. The separating device 40 or the separating sieve 41 has a passage size or gap width corresponding to the desired product fineness. The size of the auxiliary grinding bodies MH is chosen accordingly, since they must not pass through the separating device 40. Milling auxiliary bodies MH are preferably selected, the diameter of which preferably corresponds at least twice to the passage size or gap width of the separating device 40.

In Fig. 5, the path of the regrind / auxiliary grinding mixture G within the agitator ball mill 50 is also shown and described. Ground material is filled into the interior of the grinding container 51 via the ground material inlet (not shown). This is already partially filled with grinding aids MH, for example, the interior of the grinding container is already about 80% filled with grinding aids MH. Due to the rotation of the agitator shaft 1, the millbase and the auxiliary grinding media MH are mixed to form a millbase / auxiliary grinding media mixture G, which runs along the agitator shaft 1, in particular in the grinding gap MS formed between the inner lateral surface 52 of the grinding container 51 and the outer lateral surface 5 of the stirring shaft 1 first conveying direction FR1 is conveyed in the direction of the grinding container base 59. A distance is formed between the open end region of the third partial section III of the agitator shaft 1 and the grinding container base 59, in which the material to be ground / auxiliary grinding mixture G is deflected, so that this now the second hollow interior region 13 in a second conveying direction FR2 opposite to the first conveying direction FR1 of the third section III and the first hollow interior area 12 of the second middle section II of the agitator shaft 1. In particular, the material to be ground / grinding auxiliary mixture G flows through an annular space formed between the wear protection sleeve 30 and the inner lateral surface of the agitator shaft 1. Subsequently, the regrind that is sufficiently intermingled, which is referred to below as product P, enters through the separating device 40 into an annular space formed between the receiving part 75 and the separating device 40, while maintaining the second conveying direction FR2. The auxiliary grinding bodies MH, on the other hand, are held back by the separating device 40 and returned to the grinding gap MS via the passage openings 15 of the stirring shaft 1.

The receiving part 75 comprises an axial through hole 77 which extends in particular coaxially to the longitudinal axis L of the agitator shaft 1 and which in particular forms an outlet channel 78 for the product P. A separating device 40, for example a separating sieve 41 or another suitable device, is arranged on the receiving part 75 within the first hollow interior area 12 and in particular at least partially closes the terminal opening of the through-hole 77. The separating device 40 is necessary in order to prevent the grinding auxiliary bodies MH from escaping together with the product P. Instead, only sufficiently milled regrind as the finished product P should get into the through hole 77 of the receiving part 75 and thus to the product outlet 72 so that it can be removed from the agitator ball mill 50. A cover 79 on the receiving part 75 causes product P, which is located in the annular space between the separating device 40 and the receiving part 75, to be deflected into the through bore 77 of the receiving part 75 in the direction of the product outlet 72. The through the separating device 40, the separating screen 41 or the like. retained auxiliary grinding bodies MH and, if appropriate, not yet sufficiently ground grinding material pass through the openings 15 in the second middle section II of the stirring shaft 1 back into the grinding gap MS between the grinding container 51 and the stirring shaft 1 and are moved again in the conveying direction FR1.

A wear protection sleeve 30 is arranged within the second interior area 13 of the agitator shaft 1. In particular, the wear protection sleeve 30 encompasses the receiving part 75 near the product outlet 72. In this case, an annular gap is again formed between the inner surface area of the agitator shaft 50 in the third interior area III and the outer surface area of the wear protection sleeve 30, in which the ground material / grinding aid mixture G in the conveying direction FR2 in the direction of the first hollow interior region 12 of the second middle section II is guided. This annular gap between the cams 35 of the wear protection sleeve 30 and the inner circumferential surface of the agitator shaft 50 in the third interior area III is particularly small. The cams 35 of the wear protection sleeve 30 serve in particular as wipers in order to prevent ground material and / or auxiliary grinding bodies MH from adhering to the inner lateral surface of the agitator shaft 1. Instead, the cams 35 ensure that the material to be ground / auxiliary grinding mixture G is kept in flow, and is fed in the conveying direction FR2 to the passage openings 15 in the second partial section, where the auxiliary grinding bodies MH are returned in the direction of between the outer surface of the stirring shaft 1 and the Inner circumferential surface 52 of the grinding container 51 formed grinding chamber or grinding gap MS takes place.

The wear protection sleeve 30 has in particular a cooling device 37 in the form of parallel cooling duct sections 38a, 38b, as have been described in particular in connection with FIGS. 3 and 4. Coolant K flows in via the inner cooling duct sections 38a in a flow direction which corresponds to the second conveying direction FR 2 within the agitator ball mill 50 and in particular corresponds to a flow from the product outlet 72 in the direction of the regrind inlet (not shown). The coolant K is deflected in a deflection area 39 in an opposite direction of flow and into the cooling channel section 38 b. The coolant K thus flows through the wear protection sleeve 30 adjacent to the outer lateral surface in a flow direction which is opposite to the second conveying direction FR2 of the ground material / grinding aid mixture G. This ensures that the freshest and thus coolest coolant K is first led into the area of the agitator ball mill 50 which includes the wear protection sleeve 30, in which the material to be ground / grinding aid mixture G is the warmest. This is in particular the area near the separating device 40 after the ground material / grinding aid mixture G has flowed through the agitator ball mill 50 from the ground material inlet side, has been diverted and has been further stressed by the cams 35 of the wear protection sleeve 30. With the help of this counterflow cooling, an optimized cooling process within the agitator ball mill 50 is achieved.

The cross section of the agitator ball mill 50 shown in FIG. 6 shows in particular a cross section in the region of the third terminal section III of the agitator shaft 1. It can be seen here that the agitator shaft 1 on its outer surface 5 has agitator elements 3 in the form of cams 4 having. Furthermore, cooling channels 6 can also be provided within the agitator shaft 1 for cooling the agitator shaft 1 and the material to be ground / grinding auxiliary mixture G.

7A to 7E show different representations of a second embodiment of a wear protection sleeve 30 and FIGS. 8A to 8E show different representations of a third embodiment of a wear protection sleeve 30. In particular, FIGS. 7A and 8A each show a front view from the flange side, 7B and 8B each show a side view, FIGS. 7C and 8C each show a cross section along a section line AA according to FIG. 7B. 7D and 7E and 8D and 8E each show perspective representations with and without elevations 34.

In the flange 36 of the different embodiments of the wear protection sleeves 30, a coolant inlet 45 is formed in each case, via which the coolant 37 is supplied with coolant. Furthermore, a coolant outlet 46 is formed, via which the coolant is removed again from the cooling device 37 of the wear protection sleeve 30. The cooling device 37 provides in particular meandering cooling channel sections 48-1 to 48-8. The cooling duct sections 48-1 to 48-8 in particular each extend largely parallel to the longitudinal axis L30 of the wear protection sleeve 30, a deflection region 49 being provided in the end regions, which connects two adjacent cooling duct sections 48 to one another. The cooling duct sections 48-1 to 48-8 each have the same radial distance A48 from the center point defined by the longitudinal axis L30 of the wear protection sleeve 30.

The coolant is introduced via the coolant inlet 45 into the first cooling channel section 48-1 and flows through it in a first flow direction SR1. In the end region of the wear protection sleeve 30, which lies opposite the flange 36, a deflection region 49 is formed between the first cooling duct section 48-1 and the second cooling duct section 48-2, which deflects the two cooling duct sections 48-1, 48- 2 connects with each other. The coolant is diverted and flows through the second cooling channel section 48-2 in a second flow direction SR2 opposite to the first flow direction SR1. In the region of the flange 36, a further deflection region 49 is formed between the second cooling duct section 48-2 and the third cooling duct section 48-3, which connects the two cooling duct sections 48-2, 48-3 to one another. The coolant is diverted and flows through the third cooling channel section 48-3 in the first flow direction SR1 etc. After flowing through the last cooling channel section 48-8 in the second flow direction SR2, the coolant leaves the cooling device 37 through the coolant outlet 46 Arranging the cooling duct sections 48-1 to 48-8 forms a large cooling surface and optimal cooling of the agitator ball mill is achieved in the area of the product outlet. In particular, it is provided that openings are provided in the base of the grinding container (cf. FIG. 5), the arrangement of which corresponds to the arrangement of the coolant inlet 45 and the coolant outlet 46 of the wear protection sleeve 30, so that corresponding coolant supply and discharge lines are preferably arranged and / or fastened on the base of the grinding container.

9A to 9E show different representations of a receiving part 75 with product outlet 72. In particular, FIG. 9A shows a perspective representation and FIG. 9B shows a longitudinal section through a perspective representation, FIG. 9C shows a plan view, FIG. 9D shows a side view Representation and FIG. 9E a cross section through a lateral representation.

The receiving part 75 essentially has a cylindrical base body 76 and a longitudinal axis L75. A through bore 77 extends coaxially to the longitudinal axis L75 and in particular forms an outlet channel 78 for the product P. The embodiment of the receiving part 75 shown here is designed such that it forms a cooling system together with a suitable wear protection sleeve (not shown, compare FIG. 10). In particular, it is provided here that the receiving part 75 has a coolant inlet 80 and a coolant outlet 81, via which coolant can be supplied and removed accordingly. Furthermore, the receiving part 75 has an open external thread 82 in some areas, which is connected to the coolant inlet 80 via at least one suitable first connecting section 83. The external thread 82 has, in particular, depressions 86 which extend in a spiral around the receiving part 75 and are provided and / or suitable for forming outer cooling channels (cf. FIG. 10). Furthermore, the receiving part 75 has at least one inner cooling channel 85, into which coolant is introduced through the coolant inlet and a first connecting section 83 and is fed in the direction of the external thread 82. The external thread 82 is connected to the open coolant outlet 81 via at least one suitable second connecting section 84.

10 shows a longitudinal section through an agitator ball mill 50 with a receiving part 75 according to the embodiment described in FIGS. 9A to 9E. The essential components of the agitator ball mill 50 according to FIG. 10 correspond to the agitator ball mill 50 according to FIG. 5, which is why reference is made to the corresponding description. In addition, a coolant inlet 56 formed on the grinding container 51 is shown in FIG. 10, via which coolant K can be introduced into the cooling space 55 between the inner cylinder 54 and the outer cylinder 56 for cooling the grinding container 51. The coolant K flows through the cooling space 55 preferably in a flow direction which is formed opposite to the first conveying direction FR1 of the ground material / grinding aid mixture G within the agitator ball mill 50 and is discharged again via the coolant outlet 57.

It is further shown in FIG. 10 that stirring elements 3 in the form of cams 4, which extend radially outward, are formed on the outer surface 5 of the stirring shaft 1. The agitator shaft 1 can also be cooled as well. For this purpose, the agitator shaft 1 can have cooling channels 6, which, however, will not be dealt with in the present application.

The grinding material inlet 71 is formed on the grinding container lid 58, via which the grinding material M is filled into the agitator ball mill 50.

The agitator shaft 1, as already described in connection with FIG. 5, is partially hollow on the inside, in particular an inner cavity extends from the open end of the third partial section III through the third partial section III and the second partial section II.

The receiving part 75 is arranged coaxially to the longitudinal axis L of the agitator shaft 1 within the cavity. The end region of the receiving part 75 with the product outlet 72, the coolant inlet 80 described in connection with FIGS. 9A to 9E, the coolant outlet 81 and the open external thread 82 points in particular towards the grinding container base 59 or extends partially through the grinding container base 59, the The opposite end region of the receiving part 75 is arranged in the first interior region 12 within the second part section II of the agitator shaft 1. In particular, in this area the through hole 77 is at least partially covered by a separating device 40, which prevents the auxiliary grinding bodies MH from entering the outlet channel 78 and thus the product outlet 72. The product P flows through the outlet channel 78 in a flow direction corresponding to the first conveying direction FR1 and leaves the agitator ball mill 50 via the product outlet 72.

On the area of the receiving part 75, which has the external thread 82, a wear protection sleeve 30 sits sealingly. So-called outer cooling channels 87 are formed between the recesses 86 of the receiving part 75 and the inner lateral surface of the wear protection sleeve 30. The assembly consisting of a receiving part 75 and a wear protection sleeve 30 arranged thereon thus forms a cooling system in which inner cooling channels 85 are formed in the receiving part 75 and outer cooling channels 87 for cooling within the agitator ball mill 50 between the receiving part 75 and the wear protection sleeve 30. The coolant K is introduced into the receiving part 75 via the coolant inlet 80 and flows through it from the product outlet side in the direction of the regrind inlet side. In the area of the second partial section II of the agitator shaft 1, the coolant K is deflected within the receiving part 75 and now flows through it in the opposite direction. The coolant K is guided to the external thread 82 via the first connecting section 83 and flows through the outer cooling channels 87 formed by the depressions 86 and the wear protection sleeve 30, the coolant K being guided in a spiral around the receiving part 75 before it passes through the second connecting section 84 and the coolant outlet 81 exits the agitator ball mill 50. The cooling system is used in particular to cool the product P when it passes through the outlet channel 78 and exits the agitator ball mill 50 via the product outlet 72.

Alternatively (not shown), it can be provided that the at least one cooling channel within the wear protection sleeve is at least partially spiral-shaped around the longitudinal axis of the wear protection sleeve. The coolant flows through the cooling channel and is guided in a spiral around the longitudinal axis of the wear protection sleeve. The direction of flow of the coolant in the spiral cooling channel section can have a movement component in the first flow direction or a movement component in the second flow direction. The coolant is guided, for example, analogously to FIG. 10, except that the cooling channel is formed inside the wear protection sleeve and is not formed by the interaction of the wear protection sleeve and the receiving part.

11 shows a partial section of the outside of a wear protection sleeve 30. In this connection, the shape of the elevations 34 will be discussed in more detail. As already described, the wear protection sleeve 30 is produced in one piece, in particular the elevations 34 are formed directly with the manufacture of the wear protection sleeve 30 and are not subsequently attached. The elevations 34 are formed in particular as cams 35 projecting from the cylindrical base body 22 of the wear protection sleeve 30. The connecting surface 60 of the cams 35 which is formed on the base body 32 of the wear protection sleeve 30 is relatively large, in particular in relation to the radial height h of the cams 35. The shape of the cams 35 can assume any geometrical shape both in axial section and in radial consideration, for example trapezoidal, with rounded corners, with chamfered edges etc. The connecting surface 60 corresponds in particular to a base surface of each cam 35 and means the surface with which each cam 35 is in contact with the outer surface of the wear protection sleeve 30.

Due to the shape, the sensitivity of the cams 35 to break-off or break-out existing with ceramic material is significantly reduced. The one-piece design of the wear protection sleeve 30 promotes both stability and heat conduction, since potential fragments and heat conduction barriers are eliminated.

It is advantageous, for example, if each cam 35 has a connecting surface 60 to the wear protection sleeve 30 with a greatest width B and the ratio of the height h of each cam 4 to the wear protection sleeve 30 and the greatest width B is greater than 0.2. Furthermore, each cam 35 can have a connecting surface 60 to the wear protection sleeve 30 with a greatest length L35, the ratio of the height h of each cam 35 and the greatest length L35 preferably being less than 1. According to a further embodiment, it is advantageous if each cam 35 has a connecting surface 60 to the wear protection sleeve 30 with a greatest length L35 and a greatest width B, the ratio of the greatest width B and the greatest length L35 being less than 1.

Basically, it is advantageous to provide a plurality of cams 35 on the wear protection sleeve 30. The wear protection sleeve 30 can also have cam-free areas, or can have more cams 35 in some areas and fewer cams 35 in other areas. In addition, not all cams 35 need to be of the same design, but can be arranged in different shapes and sizes in different areas.

As can be seen in particular with reference to FIG. 2, it can be advantageous to arrange several cams 35 in a row 101 in a row 101 along a circumferential line of the base body 32 of the wear protection sleeve 30 in the circumferential direction of the base body 32 of the wear protection sleeve 30. For example, a distance between successive cams 35 of a row in the circumferential direction can be formed equal to or greater than the greatest length L35 of a cam 35 in the circumferential direction.

If a plurality of cams 35 are arranged in succession in a row 101 along a plurality of circumferentially spaced circumferential lines, then an axial distance between two axially adjacent rows of cams is advantageously greater than or equal to 1.1 times the greatest width B one Cam 35. If cams 35 are formed at a distance from one another in the axial direction on the base body 32 of the wear protection sleeve 30, then these cams 35 can be arranged axially either in rows 100 or offset from one another.

The embodiments, examples and variants of the preceding paragraphs, the claims or the following description and the figures, including their different views or respective individual features, can be used independently or in any combination. Features described in connection with an embodiment are applicable to all embodiments unless the features are inconsistent.

Although there is generally talk of “schematic” representations and views in the context of the figures, this does not mean in any way that the figure representations and their description should be of secondary importance with regard to the disclosure of the invention. The person skilled in the art is quite capable of extracting enough information from the schematically and abstractly drawn representations that facilitate his understanding of the invention, without having to draw from the drawn and possibly not to scale proportions of the piece goods and / or parts of the device or other drawn elements would be impaired in any way. The figures thus enable the person skilled in the art as a reader to derive a better understanding of the inventive concept formulated in the claims and in the general part of the description in more general terms and / or in more abstract terms on the basis of the specifically explained implementations of the method according to the invention and the specifically explained mode of operation of the device according to the invention.

The invention has been described with reference to a preferred embodiment. However, it is conceivable for a person skilled in the art that modifications or changes of the invention can be made without leaving the scope of the following claims.

Reference list

[0078] <tb> 1 <SEP> stir <tb> 2 <SEP> cylindrical body <tb> 3 <SEP> stirring element <tb> 4 <SEP> cam <tb> 5 <SEP> outer surface <tb> 6 <SEP> cooling channel <tb> 7 <SEP> wave recording <tb> 12 <SEP> first interior area <tb> 13 <SEP> second interior area <tb> 15 <SEP> passage opening <tb> 30 <SEP> wear protection sleeve <tb> 32 <SEP> cylindrical body <tb> 33 <SEP> hollow cylinders <tb> 34 <SEP> survey <tb> 35 <SEP> cam <tb> 36 <SEP> flange; Mounting flange <tb> 37 <SEP> cooling device <tb> 38a <SEP> (inner) cooling duct section <tb> 38b <SEP> (outer) cooling duct section <tb> 39 <SEP> deflection area <tb> 40 <SEP> separation device <tb> 41 <SEP> separating sieve <tb> 45 <SEP> coolant inlet <tb> 46 <SEP> coolant outlet <tb> 48, 48-1 to 48-8 <SEP> cooling duct section <tb> 49 <SEP> redirection area <tb> 50 <SEP> agitator ball mill <tb> 51 <SEP> grinding bowl <tb> 52 <SEP> inner surface <tb> 53 <SEP> outer cylinder <tb> 54 <SEP> inner cylinder <tb> 55 <SEP> cold room <tb> 56 <SEP> coolant inlet <tb> 57 <SEP> coolant outlet <tb> 58 <SEP> grinding container lid <tb> 59 <SEP> grinding container bottom <tb> 60 <SEP> interface <tb> 70 <SEP> drive shaft <tb> 71 <SEP> regrind inlet <tb> 72 <SEP> product outlet <tb> 75 <SEP> receiving part <tb> 76 <SEP> cylindrical body <tb> 77 <SEP> through hole <tb> 78 <SEP> exit channel <tb> 79 <SEP> cover <tb> 80 <SEP> coolant inlet <tb> 81 <SEP> coolant outlet <tb> 82 <SEP> open external thread <tb> 83 <SEP> first connection section <tb> 84 <SEP> second connection section <tb> 85 <SEP> inner cooling channel <tb> 86 <SEP> deepening <tb> 87 <SEP> outer cooling duct <tb> 100 <SEP> row <tb> 101 <SEP> perimeter <tb> <SEP> <tb> A48 <SEP> radial distance <tb> B <SEP> width <tb> d30 <SEP> outer diameter wear protection sleeve <tb> FR1 <SEP> first conveying direction <tb> FR2 <SEP> second conveying direction <tb> G <SEP> regrind / auxiliary grinding mixture <tb> h <SEP> radial height of the cams <tb> I <SEP> first terminal section <tb> II <SEP> second middle section <tb> III <SEP> third terminal section <tb> K <SEP> coolant <tb> L <SEP> longitudinal axis of the agitator shaft <tb> L3.0 <SEP> Longitudinal axis of the wear protection sleeve <tb> L35 <SEP> length cam <tb> L50 <SEP> Axis of the grinding bowl of the agitator ball mill <tb> L75 <SEP> longitudinal axis receiving part <tb> M <SEP> regrind <tb> MH <SEP> grinding aid <tb> MS <SEP> grinding gap <tb> P <SEP> product <tb> R <SEP> radial <tb> SR1 <SEP> first flow direction <tb> SR2 <SEP> second flow direction

Claims (15)

1. agitator ball mill (50) with a grinding container (51) extending along a horizontal or vertical axis (L50), a grinding material inlet (71) and a product outlet (72), one inside the grinding container (51) about the horizontal or vertical axis ( L50) rotatable stirrer shaft (1) with stirrer elements (3), the stirrer shaft (1) being assigned a wear protection sleeve (30) in the area of the product outlet (72), the wear protection sleeve (30) being formed in one piece, the wear protection sleeve (30) is a component produced in 3B printing, which consists of a ceramic material. 2. Agitator ball mill (50) according to claim 1, wherein the wear protection sleeve (30) has elevations (34) on an outer surface and wherein the wear protection sleeve (30) comprises at least one cooling device (37) or forms part of a cooling system. 3. agitator ball mill (50) according to claim 1 or 2, wherein the agitator shaft (1) on the side facing the product outlet (72) has at least in regions an inner cavity (13) and in particular wherein the agitator shaft (1) at the end that the Product outlet (72) facing, is designed to be open to the inner cavity (13), the wear protection sleeve (30) being at least partially arranged in the inner cavity (13) of the agitator shaft (1). 4. agitator ball mill (50) according to one of the preceding claims, wherein the wear protection sleeve (30) has a fastening device for fixing to and / or within the agitator ball mill (50), in particular a flange (36) for fastening the wear protection sleeve (30) to a grinding vessel bottom (59) of the agitator ball mill (50). 5. agitator ball mill (50) according to any one of the preceding claims, wherein the cooling device (37) of the wear protection sleeve (30) is designed as at least one cooling channel, which preferably extends at least in regions parallel to the longitudinal axis (L30) of the wear protection sleeve (30). 6. agitator ball mill (50) according to claim 5, wherein the at least one cooling channel extends in at least two areas in each case parallel to the longitudinal axis (L30) of the wear protection sleeve (30), wherein a deflection area is formed between the two parallel areas, in particular wherein a coolant flows through the at least two areas connected to one another via a deflection area in opposite flow directions. 7. agitator ball mill (50) according to claim 6, wherein the at least one cooling channel comprises meandering cooling channel sections (48) or wherein the at least one cooling channel is at least partially spiral around the longitudinal axis (L30) of the wear protection sleeve (30). 8. agitator ball mill (50) according to claim 6, wherein the two parallel regions on a radial (R) between the longitudinal axis (L30) and an outer circumference of the wear protection sleeve (30) are arranged. 9. agitator ball mill (50) according to one of the preceding claims, wherein the product outlet (72) is formed by a receiving part which is arranged in regions within the agitator shaft and extends through a grinding vessel bottom (59) of the agitator ball mill (50). 10. agitator ball mill (50) according to claim 9, wherein the receiving part is arranged at least in regions in the inner cavity of the stirring shaft (1), and or wherein a separating device (40) for retaining the auxiliary grinding bodies (MH) is arranged at an end region of the receiving part and the wear protection sleeve (30) being arranged at the opposite end region. 11. agitator ball mill (50) according to claim 10, wherein the receiving part has at least one profile, which forms a cooling system in operative connection with the wear protection sleeve (30). 12. Wear protection sleeve (30) for an agitator ball mill (50) which is formed in one piece, has elevations (34) on an outer surface and comprises at least one cooling device (34) or forms part of a cooling system. 13. Wear protection sleeve (30) according to claim 12 for an agitator ball mill (50) according to one of claims 1 to 11. 14. A method for producing a wear protection sleeve (30) for an agitator ball mill (50), the wear protection sleeve (30) having elevations (34) on an outer circumferential surface, comprising at least one cooling device (37) or forming part of a cooling system, and wherein the wear protection sleeve (30 ) is made in one piece from a ceramic material. 15. The method according to claim 14 for producing a wear protection sleeve (30) for an agitator ball mill (50) according to one of claims 1 to 11, in particular wherein the wear protection sleeve (30) is produced by means of 3D printing from a ceramic material.