Stirring grinder with special driver

Abstract

The invention relates to a stirring mill (1), in particular in the form of a full-volume disc mill, comprising a grinding container (2), a stirring shaft (3) rotating therein about a horizontal axis (6), the stirring shaft carrying a plurality of grinding discs (4), which are connected to the stirring shaft in a rotationally fixed manner and are spaced apart from one another in the direction of the horizontal axis (6), wherein the grinding discs (4) each have an elongated opening or hole, characterized in that the stirred mill (1) has a driver in the region between the two grinding discs (4), which driver rotates synchronously with the grinding discs (4) during the grinding process and provides a movement component in a radially outward direction for at least a portion of the grinding body in contact therewith, the driving member directly moves the grinding body when the grinding body rotates (preferably in the radial direction).

Description

Technical Field

[0001] The invention relates to a mixer mill with a driver according to the preamble of claim 1 . Background Art

[0002] First, the basic principle of a stirrer mill will be explained based on FIG. 1 .

[0003] 1 schematically shows a stirred mill 1 with a horizontal stirring shaft 3. The illustration of the grinding bodies located in the grinding container 2 and usually in the form of steel balls or ceramic balls has been omitted.

[0004] During operation of the agitator mill 1, the material to be ground is pumped into or through the grinding space 14 surrounded by the grinding container 2 through the inlet 101 of the agitator mill 1. In the case of wet grinding, the material to be ground is a suspension or dispersion of liquid (usually in the form of water) and solids. In other cases, such an agitator mill 1 can also be used for dry grinding. It can be designed, for example, as an agitator mill with a vertical shaft, through which the grinding material is carried by a gaseous fluid (usually in the form of a descending flow).

[0005] According to its broadest aspect, the invention relates to two types of agitator mills. It is particularly preferably used for agitator mills with a horizontal agitator shaft 3.

[0006] Due to the rotational movement of the stirring shaft 3 around the stirring shaft axis 6, a grinding member connected to the stirring shaft 3 in a torsionally fixed manner and usually also implemented as and referred to as a grinding disc 4 is arranged to be rotatable. Likewise, in the context of the present invention, a grinding member in the form of a separate pin can also be formed, which will be described below. However, in the context of the present invention, it is preferred to use a grinding disc, which is why only "grinding disc" will be mentioned below and only this type of grinding disc will be shown as a grinding member. In order to generate the rotational movement, the stirring shaft 3 can be driven by an electric motor, for example by a belt drive. The driver of the stirring grinder 1 is thus usually located in a housing adjacent to the grinding container 2. For clarity, FIG. 1 does not show the driver and the housing.

[0007] Due to the rotation of the grinding disc 4, the grinding bodies located in the grinding space 14 (which are located near the grinding disc 4) are carried along in the circumferential direction of the grinding container 2. Once the apex region is reached, the displaced grinding bodies flow back again in the central region between the two grinding discs 4 in the direction of the agitator shaft 3. Thus, a circulating movement of the grinding bodies is generated between the two grinding elements or grinding discs 4, respectively. FIG. 1 schematically shows this circulating movement in the free space between the first and second grinding discs 4 (only in the upper region of the cross-sectional view of the agitator grinder 1, as seen from the inlet 101) by means of two dashed arrows (a line with a short line segment and two dots) in an exemplary manner.

[0008] The movement of the grinding bodies causes collision and rolling between the solids of the grinding material suspension pumped through the grinding container 2 and the grinding bodies ( These collision and rolling movements cause the fine particles of the solids in the grinding material suspension to break up, so that the solids reaching the outlet 102 of the agitator mill 1 are ultimately significantly smaller than the solids supplied at the inlet 101.

[0009] In order to ensure that the grinding bodies do not escape from the grinding space 14, a screen 103 is usually also attached in front of the outlet 102 and / or carried by the outlet 102. A basket 104 is attached around the screen 103 and engages around the screen. The function of the basket is to prevent the grinding bodies, which tend to be pushed in the direction of the screen due to the pressure of the feed pump, from exerting a harmful grinding body pressure on the screen.

[0010] As shown in FIG. 1 , such agitator mill, in particular a full-volume disc mill, is characterized in that a large number of free spaces are formed between directly adjacent grinding discs 4, which free spaces (as described above) are substantially filled with grinding bodies. This type of full-volume disc mill is particularly suitable for use with grinding discs as grinding elements and with an inner diameter D of the grinding container 2. B Equal to or greater than the diameter D of the stirring shaft 3 W The outer diameter of the stirring shaft 3 in the region between two adjacent grinding wheels 4 is understood here as the diameter D W .

[0011] Due to the corresponding packing density, the grinding bodies are essentially held in the area between the two grinding wheels 4 , even if gaps or holes are encountered, and depending on their properties, the grinding bodies can pass from the area between the two grinding wheels 4 to the adjacent area between the two grinding wheels 4 .

[0012] The fluid is pumped from the inlet 101 of the agitator mill 1 through the interspaces between the grinding bodies to its outlet 102. For this purpose, a feed pump is used. The feed pump flow of the fluid conveys the material to be ground through the agitator mill 1.

[0013] When the agitator shaft 1 and the grinding disk 4 connected thereto rotate, the grinding bodies are also driven, in particular by friction on the grinding disk 4. As described above, these grinding bodies thus rotate in the circumferential direction. As a result, the grinding bodies roll on the grinding container 2 and the grinding disk 4 in a manner that causes friction between them. In particular, due to the pulse effect of the grinding bodies that move toward each other and then abut against each other, and due to the grinding action, the grinding material is comminuted (i.e. ground).

[0014] Technical issues

[0015] The following problems therefore repeatedly occur: the grinding bodies do not move dynamically enough in the free space between two adjacent grinding discs 4, or do not move vigorously enough in the radial vicinity of the agitator shaft 3 (in which the feed pump attempts to establish a transverse flow), and / or the circulating movement of the grinding bodies cannot get close enough to the radial vicinity of the agitator shaft 3.

[0016] As a result, the fluid from the feed pump and carrying the grinding material passes through the free space between two adjacent grinding discs 4 in sequence along the shortest route, instead of gradually swirling for a period of time in each free space between two grinding discs 4 in each case. This leads to the so-called penetration (Durchschuss). In the case of penetration, the grinding material does not have a sufficiently close contact with the grinding body. Therefore, it is only ground insufficiently. FIG. 1 again schematically shows the schematic movement of the grinding material when this type of "penetration" occurs by means of curved arrows in an exemplary manner, which schematic movement is a movement starting from the inlet 101 and passing through the free space between the first and second grinding discs 4 (only in the upper area of ​​the cross-sectional view of the agitator grinder 1, as seen from the inlet 101).

[0017] The penetration problem is particularly problematic in the case of full-volume disc mills, since in such agitator mills the high free space between two adjacent grinding discs 4 has a significant tendency to prevent sufficient grinding body movement.

[0018] Basic Purpose

[0019] In view of the above circumstances, an object of the present invention is to produce a stirring mill with a further improved grinding effect.

[0020] Solution according to the invention

[0021] This problem is solved according to the invention by the features of the first independent claim.

[0022] For this purpose, a stirring mill, in particular in the form of a full-volume disc mill, is proposed, which has a grinding container and a stirring shaft which rotates therein about a horizontal axis. The stirring shaft thus carries a plurality of grinding discs which are connected thereto in a torsionally fixed manner and are spaced apart from one another in the direction of the horizontal axis, wherein each grinding disc has an elongated opening or hole. As described above, a full-volume disc mill of this type is suitable at least for use with grinding discs as grinding elements and for an inner diameter D of the grinding container. B Equal to or greater than the diameter D of the stirring shaft W The outer diameter of the agitator shaft in the region between two adjacent grinding discs is understood here to be the diameter D W .

[0023] The agitator grinding machine according to the invention is characterized in that it has a driver in the region between two directly adjacent grinding discs, which driver rotates synchronously with the grinding discs during the grinding process. In addition, these drivers also provide at least a portion of the grinding bodies in contact with them with a movement component that is mainly or essentially in the radially outward direction, because they directly move these grinding bodies during their rotation, preferably mainly or essentially in the radial direction. After a collision with the driver, the movement vector of the grinding body caused locally in each case therefore has a movement component in the radially outward direction, which movement component accounts for at least 60%, preferably at least 75% of the total movement vector. However, it is important to point out here again that this does not apply to every grinding body after a collision with the driver, but in fact only to at least a portion. How many grinding bodies actually collide with the driver depends on many factors, such as the design of the driver, the conveying speed, the size of the grinding body, the grinding material, etc.

[0024] Preferably, the pulse is thus transmitted to the respective grinding body, as a result of which the respective grinding body in turn transmits the pulse to at least one grinding body in contact with the respective grinding body. This grinding body then in turn transmits the pulse to the grinding body that collides with it. This thus creates a pulse chain, the origin of which lies in the transmission of the pulse from the entrainment member to the grinding body in contact with the entrainment member.

[0025] The result of the resulting movement component of at least a portion of the grinding bodies, especially in the radially outward direction, is an improved circulation of the grinding bodies. In particular, the grinding bodies in the vicinity of the agitator shaft are further activated, whereby the circulating movement of the grinding bodies comes closer to the rotating surface of the agitator shaft.

[0026] As a result, the grinding space available for the grinding effect is generally increased and / or the grinding effect on the material to be ground is enhanced. Since an increased movement of the grinding bodies in the entire grinding space radially outside the agitator shaft is ensured, the number of penetrations is also reduced, thereby ensuring an improved entrainment of the material to be ground.

[0027] Preferred improvement plan

[0028] The design of the present invention has a variety of options to further improve its effectiveness or usability.

[0029] A particularly preferred embodiment is that the driver has at least one portion with a non-circular surface profile (relative to the horizontal axis of the agitator shaft), which forms a pulse generator, through which the grinding body is displaced when the driver rotates. This "non-circular surface profile" is preferably achieved by arranging a plurality of flat portions on the driver. These flat portions are preferably formed so that they at least partially flatten the originally circular cross section in the circumferential region. It is important here that the driver can also be designed in such a way that a plurality of flat portions are at least partially arranged on the circumference of the driver so that the corresponding cross section no longer has any circular area. These flat portions are preferably formed as flat surfaces and can additionally be formed so that they are parallel to the longitudinal axis of the driver and therefore parallel to the axis of the agitator shaft, or also have a certain angle of attack (Anstellwinkel) relative to the longitudinal axis of the driver. Therefore, the flat surface of the bushing effectively acts as a pulse generator, thereby itself only being subject to reduced wear. In addition, it is important to generally mention that not every portion with a "non-circular surface profile" must also act as a pulse generator at the same time.

[0030] It is also particularly preferred that the driver is a bushing, which is engaged on the agitator shaft in the free area between the grinding discs, or it is formed integrally in this area by the agitator shaft, or it is an integral part of at least one grinding disc protruding on the end face, wherein, according to one of the above-mentioned alternatives, a single bushing is preferably located between two directly adjacent grinding discs in each case. Therefore, it can be ensured that the driver can be attached to the predetermined position between the grinding discs in a simple manner (easy to assemble and without a lot of manufacturing work). The preferred embodiment of the driver is preferably represented as an external bushing here, which surrounds the agitator shaft at least in the area between two adjacent grinding discs. Since this embodiment is an obviously preferred embodiment, the following will still only refer to the driver in the form of a bushing, which is why only the term "bushing" is used. However, it is important to emphasize here that the driver in other embodiments can also have this type of design features, which will be explained below. However, since the bushing shape is an obviously preferred embodiment, in order to simplify the "driver, preferably a driver in the form of a bushing", it is preferably described as a "bushing" below.

[0031] Another preferred embodiment is that the bushing in each case has an initial shape of a body with a polygonal cross section, preferably with a square cross section, which body has at least partially a waist between its end faces, the circumference of whose cross section is smaller than the circumference of the polygonal cross section of the initial shape.

[0032] On the one hand, this has manufacturing advantages, since it is preferred that the bushing is a partially twisted polygonal body. In addition, the above-mentioned "non-circular surface profile" or flat portion can be easily provided on the bushing. For example, it is thus possible to retain the area from the corresponding end face of the bushing up to the expected circumferential reduction without processing the bushing, which area then integrally forms various pulse generating parts due to its "angular" polygonal basic shape. In addition, the above-mentioned waist is provided on the bushing so that the grinding body can be closer to the original stirring shaft. As a result, the grinding space is increased again, and as described above, the desired cyclic movement of the grinding body up to the area near the surface of the stirring shaft can be formed over a larger area.

[0033] In addition, such a waist, in particular in combination with the above-mentioned flattened portion, has various advantages, since in particular those flat surfaces which extend close to the waist to the edge region with a larger diameter have a special blade effect.

[0034] Furthermore, if the cross section of the waist is at least approximately round, it is particularly preferred that its diameter preferably remains constant over the length of the waist. On the one hand, this can be achieved more easily from a manufacturing point of view, and since the agitator shaft preferably also has a circular cross section, on the other hand, it can be ensured that the grinding bodies can be guided close to the agitator shaft surface over the entire circumference of the bushing. In addition, the design of the waist has a significant influence on the flow behavior of the grinding bodies. For example, in the case of a circular embodiment, the waist hardly produces any pulse effect radially outward. Therefore, no movement significantly opposite to the desired grinding body movement in the axial direction occurs, and the circumferential movement of the grinding body in the center between the two grinding discs towards the bushing is not slowed down. As a result, the grinding body can also flow unimpeded into the area close to the shaft, and no space without grinding bodies is generated near the shaft. Therefore, penetration is generally less.

[0035] Furthermore, it is particularly preferred if the transition between the respective end face and / or end face section and the waist is inclined, preferably conical or spherical, so that the grinding bodies circulating in the region between the grinding wheels are urged to flow towards the axis, i.e. more strongly back into the central region between the two grinding wheels, for example as part of their downward movement, which intensifies the whirling of the grinding bodies in the free region between the two grinding wheels.

[0036] As mentioned above, an “end face portion” exists when the initial cross section of the end face is in each case still partially maintained until there is a certain circumferential reduction towards the center of the bushing.

[0037] Another preferred embodiment is that the waist of the bushing is delimited relative to the pulse generator by a surface which is curved in such a way that no pulse generator is formed even when the bushing is rotated. The "blade effect" of the bushing, i.e. the strength of the pulse generator formed with the bushing or the strength with which the pulse generator displaces the grinding body, can thus be set by the ratio of the surface area of ​​the waist to the surface area of ​​the pulse generator.

[0038] Furthermore, it is particularly preferred that in the region of the waist of the bushing, preferably in the transition region between the waist and the end face and / or between the waist and the end face section, the bushing has an inclined surface which is designed such that, by means of the inclined surface, in particular by means of a rotation of the bushing, the grinding bodies are forced to perform a movement predominantly or substantially in the circumferential direction of the agitator shaft. Thus, the grinding bodies coming from the center between the two grinding discs are deflected in the direction of the grinding discs close to the shaft and then move radially outwards from the inclined surface in the direction of the grinding disc walls in order to support the "friction support" of the grinding disc walls and accelerate the grinding bodies there. As a result, the grinding bodies increasingly whirl around and / or rotate about themselves in the free space region between two directly adjacent grinding discs, which in each case increases the grinding effect.

[0039] Furthermore, it is particularly preferred if the waist of the bushing is free of (i.e. completely or substantially free of) pulse generating sections. Thus, a controlled influencing of the "leaf effect" of the bushing can be achieved. Even if the corresponding waist is cut by a flat section, the pulse generating effect of the section in the waist region is negligibly small compared to the pulse generating section.

[0040] Another preferred embodiment is that the pulse generator is arranged substantially or even completely (i.e. absolutely completely or substantially completely) in a region near the end face of the grinding disc, said region being preferably less than or equal to 1 / 4 of the distance between two directly adjacent grinding discs, measured in the direction of the horizontal axis of the agitator shaft. This achieves a preferred cyclic movement of the grinding bodies.

[0041] It is particularly preferred if the grinding discs have at least one, preferably a plurality of, holes through which the grinding bodies can pass from the intermediate space between the two grinding discs to the adjacent intermediate space between the two grinding discs. The "holes" can be windows with frames on all four sides or elongated openings extending inwards from the largest outer radius. These holes allow the material to be ground to pass from the inlet of the agitator grinder to the outlet.

[0042] Another preferred embodiment is to set a cut-off piece between the grinding discs. The cut-outs protrude from the inner surface of the grinding container into the free area between the two grinding discs, preferably just above the waist of the bushing, ideally in its central area. These cut-outs are usually pins, and ideally (viewed in the circumferential direction) the cut-outs are arranged aligned one behind the other so that they do not slow down or do not significantly slow down the rotation of the grinding body in the circumferential direction.

[0043] Furthermore, the shut-off piece can be arranged asymmetrically (preferably viewed in the circumferential direction), i.e. in the intermediate space between two directly adjacent grinding discs, closer to one grinding disc than to the other. Apart from this, the above statements apply. Depending on the shape of the bushing, the shut-off piece and its described arrangement in turn lead to a favorable flow of the grinding bodies in the area between two adjacent grinding discs. The shut-off piece thus leads to a "loosening" of the ball bag formed by the grinding bodies. Due to the centrifugal force of the rotating agitator shaft, this "ball bag" tends to be distributed more densely at the container wall. Ball bags of this density move only slowly and therefore only provide a small amount of collision energy for grinding. The ball bag can be loosened accordingly by the shut-off piece, and the circumferential movement of the grinding bodies is also accelerated by this loosening. BRIEF DESCRIPTION OF THE DRAWINGS

[0044] 1 shows a stirred mill according to the prior art in a sectional side view, thereby schematically illustrating the grinding body flow (arrows with a line with a dashed line and two dots) and the flow of the grinding material (curved arrows with a solid line).

[0045] Similar to Figure 1, Figure 2 A first exemplary embodiment of an agitator grinding machine according to the invention with a bushing and the resulting grinding body flow (arrows with a line with a short line segment and two dots) is shown in a sectional side view.

[0046] Similar to Figure 2 , Figure 3 A second exemplary embodiment of an agitator grinding machine according to the invention with a bushing and the resulting grinding body flow (arrows with a line with a short line segment and two dots) is shown in a sectional side view.

[0047] Figure 4 Shown in three-dimensional view Figure 3 A second exemplary embodiment of a bushing according to the invention is shown in FIG.

[0048] Figure 5a A third exemplary embodiment of a bushing according to the invention is shown in a side view, and Figure 5b A three-dimensional view of this exemplary embodiment is shown.

[0049] Figure 6a A fourth exemplary embodiment of a bushing according to the invention is shown in a three-dimensional view, Figure 6bThe exemplary embodiment is shown in a front view, and Figure 6c This exemplary embodiment is shown in side view.

[0050] Figure 7a A fifth exemplary embodiment of a bushing according to the invention is shown in a three-dimensional view, Figure 7b The exemplary embodiment is shown in a front view, and Figure 7c This exemplary embodiment is shown in side view.

[0051] Figure 8a A sixth exemplary embodiment of a bushing according to the invention is shown in a three-dimensional view, Figure 8b The exemplary embodiment is shown in a front view, and Figure 8c This exemplary embodiment is shown in side view.

[0052] Preferred exemplary embodiments

[0053] FIG. 1 first shows the prior art, which has already been described in more detail in the “Technical Background” paragraph above. Therefore, FIG. 1 will not be explained in more detail here. However, it is important to point out again that for a stirred mill 1 implemented in this way, the desired mixing of the grinding bodies in the area between two adjacent grinding discs 4 does not occur. Even if the grinding bodies perform the desired cyclic movement (see the arrows of the line with short segments and two dots), this cyclic movement is not dynamic enough and does not always reach the vicinity of the stirring shaft 3, which is why "penetration" occurs in particular in this area. This means that the ground material does not stay in the area between two adjacent grinding discs 4 for a long enough time before it "penetrates" directly into the adjacent area between the two grinding discs 4 through the holes in the grinding discs 4 and does not or only partially perform a cyclic movement and therefore does not experience the desired grinding effect. For the sake of simplicity, the corresponding space between two adjacent grinding discs 4 is only referred to as a "grinding chamber", so these "grinding chambers" are part of the entire grinding space 14.

[0054] Similar to Figure 1, Figure 2 Now, a stirring mill 1 with a driver designed according to the invention is shown. For a more intuitive view, the grinding bodies and the grinding material as well as the driving components of the stirring mill 1 are also omitted here.

[0055] Here and in the other figures, the driver is implemented as a bushing 8, which surrounds the agitator shaft 3 at least between two adjacent grinding discs 4 and which is preferably pushed onto the flange of the agitator shaft. The agitator shaft 3 is therefore preferably completely surrounded by the bushing 8 in these areas. In this figure and all other figures, the driver is shown in the form of a bushing 8, which, for the sake of simplicity, will be referred to only as a "bushing" below. The specific design of these bushings 8 will be discussed in more detail below.

[0056] Therefore, in Figure 2 1 and 2. The attachment of the bushing 8 between the grinding discs 4 and the formation of the grinding chamber radially outside the bushing 8 can be seen in FIG. 1. Furthermore, the cyclic movement of the grinding bodies in the grinding chamber is schematically shown in an exemplary manner (arrows of the line with a short line segment and two dots). On the one hand, the cyclic movement is significantly more dynamic than the cyclic movement in FIG. 1 (not shown), but in particular it is closer to the surface of the bushing 8 than the equivalent stirring shaft surface in FIG. 1.

[0057] Therefore, in particular when used together with the cut-out piece 12, the desired dynamic cyclic movement of the grinding body can be achieved, wherein the cut-out piece 12 is designed as a protrusion extending radially inward and is preferably formed in the form of pins, which are attached to the inner wall of the grinding container 2 at fixed intervals in the circumferential direction.

[0058] Since the grinding material stays longer in the respective grinding chamber and is entrained by this circulation movement, less penetration occurs. As a result, an additional grinding effect on the grinding material can be achieved. This is schematically represented by the grinding material flow (three curved solid arrows, leading from the inlet 101 to the respective grinding chamber).

[0059] This desired cyclic movement is produced in particular by providing the grinding bodies with a movement component in the radially outward direction, which collide with the pulse generators 7 of the bushing 8, since these pulse generators 7 directly move the grinding bodies as they rotate, preferably in the radial direction. The pulse generators 7 and the individual parts of the bushing 8 will be discussed in more detail later.

[0060] Similar to Figure 2 , Figure 3 The same view of the agitator grinder 1 is shown, but with a second embodiment of the bushing 8. Everything here is the same as Figure 2 The cyclic movement of the grinding bodies is shown here by arrows with a short line segment and two dots. It can also be seen here that the grinding bodies are pushed through the waist 9 or the transition section 13 adjacent to the waist 9 towards the pulse generating section 7. In addition, Figure 3Also shown are flow arrows for the grinding material, which has a tendency to "penetrate" close to the axis, i.e. to jump over the grinding space in the unground state or in a state where the grinding intensity is not as expected. It is obvious here that even if some parts of the grinding material are mixed into the circular motion of the grinding body, various penetrations can occur, which need to be prevented.

[0061] Figure 4 Again, three-dimensionally shown Figure 3 An embodiment of a bushing 8 in FIG. Here the arrangement of such a bushing can be seen. Preferably, the initial body or base of the bushing 8 initially has a polygonal cross section. Figure 4 In the example of , this can be seen as an octagon, or more precisely a square with oblique corners (abgekantet). This type of bushing 8 also has a central through hole for mounting the bushing 8 on the agitator shaft 3. The bushing 8 has two end faces 10 in each case. Starting from the respective end face 10 towards the center of the bushing 8, the initial basic shape initially remains for a few millimeters, so that the end face section 11 is formed. From the respective end face section 11 towards the center, a transition region 13 is formed, which is designed to be spherical here. In the central area of ​​the bushing 8, the transition region 13 transitions into a waist 9, which has a circular cross section at least in part.

[0062] The circumference of the corresponding cross section thus decreases continuously from the end face section 11 towards the waist 9 .

[0063] Figure 4 This second embodiment of the bushing 8 in each case additionally has a connecting web 16 on each of the four sides, which connects the end faces 10 to one another and bridges the waist 9 .

[0064] To be more intuitive, Figure 4 The pulse generator 7 formed in this way is shown in hatching. As mentioned above, the pulse generator 7 is responsible for generating radially outward pulses on the grinding bodies, which are preferably guided from the waist 9 via the transition area 13 to the pulse generator 7 and / or the grinding disk 4.

[0065] It is generally preferred that, after the collision with the pulse generator 7, the corresponding locally induced motion vector of the grinding body has a motion component in the radially outward direction which accounts for at least 60%, preferably at least 75% of the entire motion vector.

[0066] And after the collision with the waist 9, the correspondingly induced movement vector of the grinding body has a movement component in the axial direction, which accounts for at least 60%, preferably at least 75% of the entire movement vector.

[0067] Figure 5a and Figure 5b The further embodiment of the bushing 8 shown shows that the waist 9 preferably does not need to be bridged by the connecting web 16 at all. In turn, the bushing 8 here also has a polygonal base body, which is a hexagon in this case. This basic shape is also maintained at a distance of a few millimeters from the corresponding end face until the transition to the waist 9 via the transition area 13. The waist 9 thus has a circular cross section. The pulse generator 7 of the bushing 8 is shown in hatching. Figure 5a Also depicted is a bushing axis 15 which, when manufactured and assembled as intended, preferably corresponds substantially to the axis of rotation of the stirring shaft 3 .

[0068] In order to simplify the assembly of the bushing 8 on the agitator shaft 3 and to achieve a rotational protection relative to the agitator shaft, the bushing 8 also preferably has a plurality of grooves 17 at the base of the central through hole, which are implemented over the entire length of the bushing 8. It goes without saying that for this purpose, the agitator shaft 3 must have a thickening, which is implemented in a complementary manner and can engage with these grooves 17.

[0069] Figures 6a to 6c Another almost identically implemented embodiment of a bushing 8 is shown. However, in contrast to the previous embodiment, this embodiment has an initial body with a purely square initial shape.

[0070] The fact that the pulse generating portion 7 cannot be formed by simply continuing the initial shape is based on Figures 7a to 7c It becomes clear from the illustrated embodiment of another bushing 8. The pulse generating portion 7 (here hatched) represents a flat portion parallel to a plane of the bushing axis 15. The original initial shape of the bushing 8 is a quadrilateral bushing which is distorted by a curved waist 9.

[0071] The waist 9 itself may also be only a few millimeters wide or may even represent only a connection between transition areas 13 that touch one another in the center of the bushing 8 . Figures 8a to 8c An embodiment designed in this manner is shown.

[0072] Reference numerals list

[0073] 1 Mixer grinder

[0074] 2 Grinding container

[0075] 3. Stirring shaft

[0076] 4 Grinding disc

[0077] 5 Unspecified

[0078] 6 Horizontal axis or stirring shaft axis

[0079] 7 Pulse generator

[0080] 8 Bushing

[0081] 9 Waist

[0082] 10 End face of bushing

[0083] 11 End face of bushing

[0084] 12 Cut-off piece

[0085] 13 Transitional section or transitional area

[0086] 14 Grinding Room

[0087] 15 Bushing axis

[0088] 16 Connecting web

[0089] 17 Grooves

[0090] 101 Entrance

[0091] 102 Exit

[0092] 103 Screen

[0093] 104 Basket

[0094] D B Grinding vessel inner diameter

[0095] D W Stirring shaft diameter

Claims

1. A stirring mill (1), in particular in the form of a full-volume disc mill, comprising a grinding container (2), a stirring shaft (3) which rotates in the grinding container (2) about a horizontal axis (6), the stirring shaft (3) carrying a plurality of grinding discs (4) which are connected to the stirring shaft (3) in a rotationally fixed manner and are spaced apart from one another in the direction of the horizontal axis (6), wherein: The grinding discs (4) each have an elongated opening or hole, characterized in that the agitator grinder (1) has a driving member in the area between the two grinding discs (4), which rotates synchronously with the grinding discs (4) during the grinding process and provides a movement component in the radial outward direction to at least a part of the grinding body in contact with it, because the driving member directly moves the grinding body when the grinding body rotates, preferably moves the grinding body in the radial direction.

2. The stirring grinder (1) according to claim 1, characterized in that The driver has at least one portion with a non-circular surface contour relative to the horizontal axis (6) of the stirring shaft (3), which portion forms a pulse generator (7) by which the grinding body is displaced when the driver rotates.

3. The stirring grinder (1) according to claim 1 or 2, characterized in that The drive element is a bushing (8) which engages on the agitator shaft (3) in the free area between the grinding wheels (4), or the bushing (8) is formed integrally with the agitator shaft (3) in said area, or the bushing (8) is an integral part of at least one grinding wheel (4) which protrudes at the end face, wherein a single bushing (8) is preferably located in each case between two directly adjacent grinding wheels (4).

4. A stirring mill (1) according to any one of the preceding claims, characterised in that The bushings (8) in each case have an initial shape of a body with a polygonal cross section, which body has at least partially between its end faces (10) a waist (9), the cross section of which has a smaller circumference than the circumference of the polygonal cross section of the initial shape.

5. The stirring grinder (1) according to claim 4, characterized in that The waist (9) is at least substantially circular in cross section, preferably with a diameter that remains constant over the length of the waist (9).

6. A stirring mill (1) according to any one of the preceding claims, characterised in that The transition portion (13) between the respective end face (10) and / or end face portion (11) and the waist (9) is inclined, preferably conical or spherical.

7. A stirring mill (1) according to any one of the preceding claims, characterised in that The waist (9) of the bushing (8) is delimited relative to the pulse generator (7) by a surface which is curved in such a way that the pulse generator (7) is not formed even when the bushing (8) is rotated.

8. A stirring mill (1) according to any one of the preceding claims, characterised in that In the region of the waist (9), preferably in the transition region (13) between the waist (9) and the end face (10) and / or between the waist (9) and the end face portion (11), the bushing (8) has an inclined surface, which is designed so that the grinding body is forced to move in the circumferential direction of the stirring shaft (3) by means of the inclined surface, in particular by means of the rotation of the bushing (8), and is thereby preferably also pushed into the central region between the two directly adjacent grinding discs (4).

9. A stirring mill (1) according to any one of the preceding claims, characterised in that The bushing (8) is conical in such a way that the length of its waist (9) is at least 45% of the distance between two directly adjacent grinding discs (4), measured in each case in a direction parallel to the horizontal axis (6) of the stirring shaft (3).

10. A stirring mill (1) according to any one of the preceding claims, characterised in that At least 45% of the sleeve surface facing the grinding space (14) is free of pulse generating portions (7).

11. A stirring mill (1) according to any one of the preceding claims, characterised in that The waist of the bushing (8) does not have a pulse generating portion (7).

12. A stirring mill (1) according to any one of the preceding claims, characterised in that The pulse generating portion (7) is arranged substantially or even completely in a region near the end face of the grinding disk, the region being preferably less than or equal to 1 / 4 of the distance between two directly adjacent grinding disks (4), measured in the direction of the horizontal axis (6) of the stirring shaft (3).

13. Agitator grinder (1) according to any one of the preceding claims, characterised in that The grinding disc (4) has at least one hole, preferably a plurality of holes, through which the grinding body can pass from the intermediate space between the two grinding discs (4) to the adjacent intermediate space between the two grinding discs (4).

14. Agitator grinder (1) according to any one of the preceding claims, characterised in that A cut-out (12) is provided between the grinding discs (4), which protrudes from the inner surface of the grinding container into the free area between the two grinding discs (4), preferably just above the waist of the bushing (8), ideally in its central area.

15. A stirring mill (1) according to any one of the preceding claims, characterised in that Preferably, the shut-off element (12) is arranged asymmetrically, viewed in the circumferential direction, ie, in the intermediate space between two directly adjacent grinding wheels (4), closer to one grinding wheel (4) than to the other grinding wheel (4).

16. A driver, preferably in the form of a bushing (8), arranged in the region between two adjacent grinding wheels (4), characterized in that The driving member rotates synchronously with the grinding disc (4) during the grinding process and provides a movement component in the radial outward direction to at least a part of the grinding body in contact with it, because the driving member directly moves the grinding body when the grinding body rotates, preferably moves the grinding body in the radial direction.

17. The driver according to claim 16, preferably in the form of a bushing (8), characterized in that The driver is designed according to at least one of the features of claims 2 to 15 in relation to the driver and / or the bushing (8).

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