Disc assembly and grinding unit for a mill, use of same for comminuting a grinding stock

Abstract

The invention relates to a disc assembly for a grinding unit, containing a plurality of discs (S) or consisting of a plurality of discs (S). Each of the discs (S) has a truncated conical or double conical or double truncated conical design, and for each discs (S), the angle between the surface line thereof and the cone axis > 30 to 82.5°. The discs (S) are stacked along a central axis (MA) of the assembly (A), and the assembly (A) has a plurality of radial grooves (RN) facing the central axis (MA) of the assembly (A) and radial webs (RS) facing away from the central axis (MA). Each of the radial grooves (RN) has a rounded groove base (NG), and each of the radial webs (RS) has a rounded edge (KT). The invention additionally also relates to a grinding unit which has at least two disc assemblies according to the invention and to the use of the assembly or the grinding unit according to the invention in order to comminute grinding stock.

Description

Technical field

[0001] The present invention relates to an arrangement containing a plurality of disks or consisting of a plurality of disks according to claim 1, a grinding mechanism for a mill according to claim 10 and a use of the arrangement or the grinding mechanism according to claim 14. Background of the invention

[0002] From the prior art, for example from publication EP 1 600 214 A1, grinding devices for bulk material particles are known which have rollers with a zigzag profile, wherein their radial ribs and radial grooves are arranged axially offset from one another in such a way that they form meshing pairs. A grinding gap is formed between the rollers, which has a zigzag shape when viewed from above of the grinding mechanism or the roller pair. Grinding mechanisms of this type are also known to those skilled in the art, for example, from EP2422881A2, EP0146515A1 and from the publication: Becher, T. et al.: "New mill type for a wide variety of raw materials", Brauwelt, No. 45, 2015, pages 1344 to 1349.

[0003] The inventors of the present application have observed, however, that with a sufficiently long service life of such grinding devices, local enlargements of the grinding gap occur in the area of ​​the radial web edges or radial groove bases, which adversely allow insufficiently ground material to pass through the grinding mechanism. This prevents the achievement of an optimal grist composition. Furthermore, the grinding mechanism must be replaced or serviced, which increases the grinding mechanism's downtime and maintenance costs. Object of the invention

[0004] It is therefore an object of the present invention to provide a disc arrangement and / or a grinding mechanism in which wear-related enlargement of the grinding gap in the region of the radial web edges or radial groove base is reduced or even avoided. Furthermore, it is an aspect of the present invention to provide a corresponding application. Summary of the invention

[0005] The aforementioned problem is solved by the arrangement according to claim 1. Advantageous embodiments are the subject of the dependent claims.

[0006] An arrangement A is claimed which contains or consists of a plurality of disks S. Each of the disks S has a frustoconical, double conical, or double frustoconical shape; wherein, in each of the disks S, the angle between a generatrix (= flank) of the disk S and a conical axis KA of the disk S is > 30 to 82.5°, preferably 40 to 75°; wherein the disks S are stacked along a central axis MA of the arrangement A; wherein the disks S are arranged such that the conical axis KA of each disk S is parallel or coaxial to the central axis MA of the arrangement A; wherein the arrangement A has a plurality of radial grooves RN pointing towards the central axis MA of the arrangement A; and wherein the arrangement A has a plurality of radial webs RS pointing away from the central axis MA of the arrangement A.

[0007] In the arrangement A according to the invention, the angle between a generatrix (= flank) of the disk S and a cone axis KA of the disk S is defined in each of the disks S in contrast to the usual angle measurement, which is always carried out counterclockwise, in such a way that it corresponds to the smaller of the two angles between the generatrix and the cone axis, wherein the two angles are determined once by measuring counterclockwise and once by measuring clockwise.

[0008] The arrangement according to the invention is characterized in that the radial grooves RN each have a rounded, preferably concave, groove base NG; and the radial webs RS each have a rounded, preferably convex, edge KT. The disc arrangement according to the invention can be a component of a roller for a grinding mechanism of a mill for grinding plant materials.

[0009] The inventors of the present invention have observed that wear of the discs in this area leads to an increase in the grinding gap in the region of the radial rib edges or radial groove bases. Furthermore, they have found that, surprisingly, the disc arrangement designed according to the invention, as described above, prevents or at least mitigates this increase in the grinding gap and thus a detrimental change in the grit sorting. Instead of the conventional design of the radial ribs with a pointed edge and a corresponding pointed V-groove in the radial grooves, the invention features both rounded edges on the radial ribs and a rounded groove base for the pointed V-shaped grooves in the radial grooves.In the case of the radial grooves RN according to the invention, a rounded groove base NG means a round groove with a predetermined radius (partial angle, depending on the opening angle OW of the radial groove RN) at the groove base.

[0010] By providing rounded edges on both the radial ribs and the radial grooves, it is ensured that the radial ribs have a greater material thickness compared to those with pointed edges. This prevents, or at least minimizes, the increase in the grinding gap in the radial grooves due to wear of the disc material during normal use of the assembly in a mill for grinding, for example, plant material. Furthermore, the rounding of the edges and groove bases according to the invention results in a longer service life for the disc assembly in a mill. In addition, the rounding of the edges according to the invention significantly reduces the risk of injury to the installer during installation or maintenance work compared to conventional radial ribs with pointed edges.Furthermore, the risk of damage to the disc at its radial web during transport and / or installation is also reduced, as the rounded edges of the radial webs are significantly less sensitive to impact or other mechanical stress.

[0011] For the purposes of the present invention, a "truncated cone or double cone or double truncated cone shape" comprises the corresponding ideal geometric forms of the truncated cone, the double cone, and the double truncated cone. However, the present invention is not limited to these, but may also include designs deviating from the ideal geometric form, such as non-linear, e.g., curved, stepped, or zigzag-shaped generatrix or flanks, which are common in the technical field of the application, namely in grinding mechanisms for mills suitable for grinding plant solids, or which are provided for according to the invention (e.g., rounded edges or rounded grooves).

[0012] The discs of the arrangement according to the invention are manufactured from materials commonly used in grinding mills, in particular stainless steel, hardened steel, or ceramic. The arrangement according to the invention is preferably rotationally symmetrical. It is preferred if the discs of the arrangement according to the invention are rotationally symmetrical at the edge or in the region of the edge. This particularly includes the case where the disc is rotationally symmetrical at the edge but has a regular or irregular profile on its outer surface. It is especially preferred if the discs of the arrangement according to the invention are rotationally symmetrical, i.e., each disc of the arrangement according to the invention is rotationally symmetrical as a whole.

[0013] Advantageous embodiments of the arrangement according to the invention are the subject of the dependent claims.

[0014] The radial grooves RN can point perpendicular to the central axis MA of the arrangement A. Alternatively or additionally, the radial webs RS can point perpendicularly away from the central axis MA of the arrangement A.

[0015] These arrangements represent structurally simple implementations of the arrangement according to the invention. Due to the symmetrical design of the radial webs, their mechanical strength is particularly high.

[0016] In an advantageous embodiment of the arrangement according to the invention, the radius Ri of the radial grooves RN at the rounded groove base NG can be larger than the radius Ra of the radial webs RS at the rounded edge.

[0017] This ensures that, when the arrangement according to the invention is used in a grinding mill with two parallel disc arrangements according to the invention, the radial ribs RS of one arrangement and the radial grooves RN of the other parallel arrangement (and vice versa) do not touch, thus preventing damage. Furthermore, if the radius Ri of the radial grooves RN at the rounded groove base NG is larger than the radius Ra of the radial ribs RS at the rounded edge, the grinding gap MS in the area of ​​the radial rib edges (i.e., at the turning points of the zigzag pattern of the grinding gap) is smaller than the grinding gap along the generatrix or flank of the respective disc S (linear area between the turning points). This effectively prevents excessively coarse particles or even whole grains from passing through the grinding gap in the area of ​​the rounded edges.

[0018] In the arrangement according to the invention, the disks S can have a diameter of 40 to 500 mm, preferably 100 to 400 mm. Furthermore, in the arrangement according to the invention, the disks S can have a thickness of 30 to 200 mm, preferably 50 to 80 mm. This results in high mechanical stability with comparatively little material.

[0019] Furthermore, the radius Ri of the radial grooves RN at the rounded groove base NG can be 0.5 to 25 mm, preferably 1 to 20 mm, and particularly 2 to 10 mm. Alternatively or additionally, the radius Ra of the radial webs RS at the rounded edge KT can be determined according to the following first equation (GL1) (* = multiplication operator): Ra = Ri − 2 * MS + RT

[0020] Where: Ra = radius Ra of the radial webs RS at the rounded edge KT in mm; Ri = radius Ri of the radial grooves RN at the rounded groove base NG in mm; MS = grinding gap in mm; and RT = runout tolerance in mm. The runout tolerance is a correction value and is determined, for example, by the shaft, bearing, and disc dimension tolerances.

[0021] According to the invention, the grinding gap MS can have a value of 0.10 to 1.40 mm, preferably 0.10 to 0.80 mm, preferably 0.10 to 0.50 mm, preferably 0.20 to 0.60 mm, and in particular 0.20 to 0.40 mm. Furthermore, the runout tolerance RT can have a value of 0.05 to 0.30 mm, preferably 0.10 to 0.20 mm, and in particular 0.12 to 0.18 mm. According to the invention, the runout tolerance includes bearing clearance resulting from wear and / or damage, deviations caused by thermal expansion, the bearing tolerance, and a predetermined safety margin.

[0022] The arrangement according to the invention can be limited to individual value ranges of the parameters Ri, Ra, MS and RT mentioned above or calculated above, or to any combination thereof. Preferably, all parameters Ri, Ra, MS and RT mentioned above are limited to the respective value ranges mentioned above or calculated above, in particular to the respective preferred or especially preferred value ranges.

[0023] In a variation of this embodiment, the radius Ra of the radial webs RS at the rounded edge KT can be determined according to the following second equation (GL2) (* = multiplication operator; / = division operator): Ra = Ri − 2 * RT * cos 180 ° − OW / 2 + RT

[0024] Where: Ra = radius Ra of the radial webs RS at the rounded edge in mm; Ri = radius Ri of the radial grooves RN at the rounded groove base NG in mm; OW = opening angle of the radial groove RN in °; and RT = runout tolerance in mm.

[0025] In this embodiment, the opening angle OW of the radial groove RN has a value of 15 to < 120°, preferably 30 to 100°, and particularly 40 to 80°. The opening angle OW of the radial groove RN is fundamentally related to the angle MWI between a generatrix of the disk S and the cone axis KA of the disk S according to the following third equation (GL3): OW = 180 ° − 2 * MWI

[0026] Furthermore, in this embodiment, the runout tolerance RT has a value of 0.05 to 0.30 mm, preferably 0.10 to 0.20 mm, and particularly 0.12 to 0.18 mm. The arrangement according to the invention can be limited to individual values ​​of the parameters Ri, Ra, OW, MWI, and RT mentioned above or calculated above, or to any combination thereof. Preferably, all parameters Ri, Ra, OW, and MWI mentioned above are limited to their respective value ranges mentioned above or calculated above, and in particular to their preferred or especially preferred value ranges.

[0027] According to the embodiments of the arrangement described above, the radius Ra of the radial webs RS is determined according to the first equation (GL1) or the second equation (GL2) above. This ensures that, when the arrangement according to the invention is used in a grinding mill with two parallel disc arrangements according to the invention, the radial webs RS of one arrangement and the radial grooves RN of the other parallel arrangement (and vice versa) do not touch, and that, on the other hand, the predetermined grinding gap does not increase, or does not increase as quickly as with conventional arrangements, due to material wear during intended use. This prevents deviations from the desired or preset degree of comminution or from the desired grist sorting, even over extended periods of use.Furthermore, in these embodiments, it is ensured that the grinding gap MS in the area of ​​the radial rib edges is smaller than the grinding gap along the generatrix or flank of the respective disc S. This effectively prevents the passage of excessively coarse particles or even whole grains through the grinding gap in the area of ​​the rounded edges. Only since the advent of modern machining techniques, particularly CNC milling, has it become possible to manufacture the disc assemblies according to the invention with rounded edges and groove bases precisely and affordably, although this still requires additional machining effort compared to the production of conventional disc assemblies with sharply defined edges and groove bases.

[0028] Furthermore, the arrangement A can have a first end section F1 at a first end E1. The first end section F1 has the shape of a cylinder or hollow cylinder. The first end section F1 is arranged such that its central axis MF1 is parallel or coaxial with the central axis MA of the arrangement A. The first end section F1 preferably has a length (= thickness) of 1 to 100 mm, preferably 1 to 50 mm, and particularly 2 to 20 mm, measured in the direction of the central axis MA of the arrangement A. The diameter of the first end section F1 preferably corresponds to the diameter of the disk SR1 of the arrangement A adjacent to the first end section F1 at the first end E1 of the arrangement A (= the diameter of the outer edge of the disk SR1 adjacent to the first end section F1). The disk SR1 is the outermost disk of the arrangement A located at the first end E1.It is preferred that the diameter of the first end section F1 is not larger than the diameter of the disk SR1 of the arrangement A adjacent to the first end section F1 at the first end E1 of the arrangement A. This ensures sufficient mechanical stability with the least possible material usage.

[0029] The inventors of the present invention have observed that the ends of disc assemblies in conventional mills represent design weaknesses where foreign matter in the material being ground can cause chipping. By reinforcing the arrangement according to the invention at at least one end, or preferably at both ends, with a cylindrical end section, these chippings at the respective end region of the arrangement are avoided when the arrangement according to the invention is used in a mill.

[0030] In this embodiment, it is particularly advantageous if the first end section F1 is connected to the disk SR1 of arrangement A, which is arranged adjacent to the first end section F1, by means of a force-fit, form-fit, or material-fit connection. Alternatively, the first end section F1 can be integral with the adjacent disk SR1.

[0031] Furthermore, the arrangement A can have a second end section F2 at a second end E2. The second end section F2 has the shape of a cylinder or hollow cylinder. The second end section F2 is arranged such that its central axis MF2 is parallel or coaxial with the central axis MA of the arrangement A. The second end section F2 preferably has a length (= thickness) of 1 to 100 mm, preferably 1 to 50 mm, and particularly 2 to 20 mm, measured in the direction of the central axis MA of the arrangement A. The diameter of the second end section F2 preferably corresponds to the diameter of the disk SR2 of the arrangement A adjacent to the second end section F2 at the second end E2 of the arrangement A (= the diameter of the outer edge of the disk SR2 adjacent to the second end section F2). The disk SR2 is the outermost disk of the arrangement A located at the second end E2.It is preferred if the diameter of the second end section F2 is not larger than the diameter of the disk SR2 of the arrangement A adjacent to the second end section F2 at the second end E2 of the arrangement A. The advantages listed above for the first end section F1 apply analogously.

[0032] In this embodiment as well, it is particularly advantageous if the second end section F2 is connected to the disk SR2 of arrangement A, which is arranged adjacent to the second end section F2, by means of a force-fit, form-fit, or material-fit connection. Alternatively, the second end section F2 can be integral with the adjacent disk SR2.

[0033] Preferably, the same material is used for the first end section F1 and / or the second end section F2 as for the disks of the arrangement. However, a material with greater hardness may also be used. A particularly high mechanical reinforcement effect is achieved if the first end section F1 and / or the second end section F2 consists of solid material.

[0034] The problem according to the invention is further solved by the subject matter of claim 10.

[0035] Thus, a grinding mechanism MW is required for a mill which has at least the following features: a first roller WA1 comprising a first shaft W1 and a first arrangement A1; and a second roller WA2 comprising a second shaft W2 and a second arrangement A2; wherein the first shaft W1 and the first arrangement A1 are connected to each other by force-fit, form-fit, or material-fit, or are integrally formed; wherein the second shaft W2 and the second arrangement A2 are connected to each other by force-fit, form-fit, or material-fit, or are integrally formed; wherein the first arrangement A1 is an arrangement A according to any one of claims 1 to 9; wherein the second arrangement A2 is an arrangement A according to any one of claims 1 to 9; wherein the central axis MA1 of the first arrangement A1 is arranged parallel to the central axis MA2 of the second arrangement A2; wherein the radial webs RS1 of the first arrangement A1 engage in the radial grooves RN2 of the second arrangement A2; and wherein the radial webs RS2 of the second arrangement A2 engage in the radial grooves RN1 of the first arrangement A1.

[0036] Since the grinding mill according to the invention provides at least two arrangements according to the invention, the advantages discussed above in connection with the arrangement according to the invention apply analogously to the grinding mill according to the invention. Preferably, in the grinding mill according to the invention, the first arrangement A1 and the second arrangement A2 each have the same values ​​for the parameters Ri, Ra, MWI, OW, RT, diameter of the disks S and thickness of the disks S defined above. Particularly preferably, in the grinding mill according to the invention, the first arrangement A1 and the second arrangement A2 are identical. Particularly preferably, in the grinding mill according to the invention, the first roller WA1 and the second roller WA2 are identical.

[0037] Particularly preferred in the grinding mill according to the invention are the first roller WA1 and the second roller WA2 or the first arrangement A1 and the second arrangement A2 arranged in opposite directions.

[0038] In the grinding mechanism according to the invention, a gap is formed between the first arrangement A1 and the second arrangement A2, which is referred to as the grinding gap MS.

[0039] In the grinding mechanism according to the invention, the distance between the central axis MA1 of the first arrangement A1 and the central axis MA2 of the second arrangement A2 (= axis distance of the grinding mechanism) is determined on the basis of the diameters of the disks of the first arrangement A1 and that of the second arrangement A2 and the desired grinding gap MS.

[0040] In the grinding mechanism according to the invention, the grinding gap MS in the area of ​​the radial web edges, i.e., in the area where the rounding is present, or a part thereof, is preferably smaller than the grinding gap MS along the generatrix or flank of the respective disk S, i.e., the linear area between the radial web edge and the groove base of the radial groove RN adjacent to this radial web RS. This effectively prevents the passage of excessively coarse particles or even whole grains through the grinding gap MS in the area of ​​the rounded edges.

[0041] Advantageous embodiments of the grinding mechanism according to the invention are the subject of the dependent claims.

[0042] In one embodiment, the central axis MA1 of the first arrangement A1 can be arranged coaxially with the central axis of the first shaft W1. The central axis MA2 of the second arrangement A2 is arranged coaxially with the central axis of the second shaft W2.

[0043] This arrangement facilitates the assembly and adjustment of the grinding mechanism according to the invention, such as the roller spacing and thus the grinding gap.

[0044] In a further embodiment, the first shaft W1 and the second shaft W2 can be arranged relative to each other such that the central axis of the first shaft W1 and the central axis of the second shaft W2 are parallel to each other. A gap, designated as the grinding gap MS, is formed between the first arrangement A1 and the second arrangement A2.

[0045] The grinding gap MS in the grinding mill according to the invention has a clear width of 0.10 to 1.40 mm, preferably 0.10 to 0.80 mm, preferably 0.10 to 0.50 mm, preferably 0.20 to 0.60 mm, and in particular 0.20 to 0.40 mm, over its entire length.

[0046] The problem according to the invention is finally solved by the use according to claim 14.

[0047] The use of at least one arrangement A according to any one of claims 1 to 9 or a grinding mill according to any one of claims 10 to 13 for grinding a material is claimed. The material to be ground is plant material, preferably protein-containing plant material, or contains such plant material. The material to be ground is preferably selected from the group consisting of: malt, unmalted grain, barley, rice, corn, millet, chickpeas, soybeans, potatoes, and any mixture thereof. Preferably, the material to be ground is a raw material suitable for food or beverage production, preferably for beer production, or any mixture of such raw materials.

[0048] By using the inventive arrangement or grinding mechanism for crushing plant material, in particular the aforementioned plant materials, the disadvantages discussed at the outset in connection with the prior art can be avoided and the desired degree of comminution can be achieved without resulting in unfavorable local enlargements of the grinding gap in the area of ​​the radial groove base. Further Revelation

[0049] The following table presents the parameters discussed above in connection with the invention and exemplary, non-limiting numerical values ​​for them: parameter Minimum value typical range / value according to the invention Maximum value Opening angle OW of the radial groove RN [°] 15 30 to 100, < 120 40 to 80, 50 to 70, 60 Grinding gap [mm] 0,10 0.10 to 0.80, 1,40 0.10 to 0.50, 0.20 to 0.60, 0.20 to 0.40, 0,30 Radius (Ri) of the radial grooves (RN) [mm] 0,5 1 to 20, 25 2 to 10, 5 Runout tolerance (RT) [mm] 0,05 0.10 to 0.20, 0,3 0.12 to 0.18, 0,15 Examples

[0050] Embodiments of the prior art and of the arrangement according to the invention are shown in the accompanying drawing. This drawing includes: Fig. 1 is a schematic, not to scale (top view) representation of a conventional grinding mechanism with two parallel, conventional disc arrangements, each having radial webs with a tapered edge and a corresponding tapered V-groove in the radial slots; Fig. 2 is an enlarged view of the engagement of the radial web RS of one conventional arrangement with the radial slot of the other conventional arrangement, which corresponds to the circular segment of the Fig. 1corresponds; Fig. 3 a schematic, not to scale (top view) representation of a grinding mechanism according to the invention with two parallel arrangements according to the invention with a plurality of discs, wherein the radial webs are rounded at their edges and the radial grooves have rounded groove bases; Fig. 4 an enlarged representation of the engagement of the radial web RS of one arrangement according to the invention in the radial groove of the other arrangement according to the invention, which corresponds to the circular segment of the Fig. 3 corresponds; Fig. 5 a further enlarged representation of the in Fig. 4Fig. 6 shows a schematic, not to scale, representation of an arrangement according to the invention with a plurality of disks, wherein the radial webs are rounded at their edges and the radial grooves have a rounded groove base shape; and Fig. 7 shows a schematic, not to scale, representation of an arrangement according to the invention with a plurality of disks, wherein the arrangement has a cylindrical end section at one end.

[0051] Fig. 1Figure 1 shows a conventional mill HMW equipped with two rollers HWA1, HWA2. Each roller HWA1, HWA2 consists of a rotatably mounted shaft HW1, HW2, on which an arrangement HA1, HA2 of disks HS1, HS2 is mounted. In this example, the conventional disks HS1, HS2 have a frustoconical or double frustoconical shape and are stacked along the central axis HMA1, HMA2 of the arrangement HA1, HA2. Both arrangements HA1, HA2 of conventional design each have a plurality of radial ribs HRS1, HRS2 and radial grooves HRN1, HRN2. The radial ribs HRS1 of the first arrangement (HA1) engage in the radial grooves HRN2 of the second arrangement HA2, and vice versa. In conventional arrangements, the radial webs HRS1, HRS2 have pointed edges HKT1, HKT2 and the radial grooves HRN1, HRN2 have tapered, V-shaped groove bases, as can be seen particularly in the enlarged engagement view of the Fig. 2This can be seen. The grinding gap HMS is formed between the two conventional arrangements HA1, HA2, or more precisely, between the radial ribs that are adjacent to each other when the two arrangements IIA1, IIA2 are engaged. The radial grooves HRN1, HRN2 each have an opening angle OW1, OW2, which is in Fig. 1 OW1 is given as an example. Each of the disks HS1, HS2 encloses an angle MWI1, MWI2 between a generatrix of disk HS1, HS2 and the respective cone axis KA1, KA2 of disks HS1, HS2, where in the Fig. 1 Only the angle MWI1 is specified. In the Fig. 1 The cone axes KA1 coincide with the central axis HMA1 of the arrangement HA1. Similarly, the cone axes KA2 coincide with the central axis HMA2 of the arrangement HA2.

[0052] In contrast, it shows Fig. 3A grinding mill MW according to the invention, comprising a first roller WA1 and a second roller WA2. The first roller WA1 has a first shaft W1 and a first arrangement A1 according to the invention. Correspondingly, the second roller WA2 has a second shaft W2 and a second arrangement A2 according to the invention. The first roller WA1 and the second roller WA2 are rotatably mounted and can rotate in opposite directions during operation of the grinding mill. The grinding gap MS of the grinding mill MW according to the invention is formed between the first arrangement A1 and the second arrangement A2 (only in Fig. 5 (shown). The first arrangement A1 consists of a plurality of first disks S1, each of the first disks S1 having either a frustoconical or double frustoconical shape. More precisely, only the one shown in the Figure 3The first disk S1, located at the left end of the first arrangement A1, has a conical step shape, while the other first disks S1 have a double frustoconical shape. The first disks S1 are stacked along a first central axis MA1 of the first arrangement A1. A first conical axis KA1 of each first disk S1 is arranged coaxially with the first central axis MA1 of the first arrangement A1. The first arrangement A1 has a plurality of first radial webs RS1 pointing away from the first central axis MA1 of the first arrangement A1. Between each pair of adjacent first radial webs RS1, a first radial groove RN1 is formed, pointing towards the first central axis MA1 of the first arrangement A1. In contrast to the prior art, according to the invention, the first radial grooves RN1 each have a rounded, concave groove base NG1, which is shown in the enlarged illustrations of the Figs. 4 and 5This is particularly easy to see. Furthermore, the first radial webs RS1 each have a rounded, convex first edge KT1. In the illustrated embodiment of the arrangement according to the invention, the angle MWI1 between a generatrix of the first disk S1 and a first conical axis KA1 of the first disk S1 is approximately 81° for each of the first disks S1. The opening angle OW1 of the first radial grooves RN1 is approximately 18° in each case.

[0053] The second arrangement A2 according to the invention is identical in structure to the first arrangement A1 described above, which is why a detailed description is omitted here. The second arrangement A2 according to the invention is arranged parallel to, but opposite to, the first arrangement A1 (cf. Fig. 3 ).

[0054] In the enlarged view of the Fig. 5The radius Ri of the radial groove RN1 at the rounded groove base NG1 and the radius Ra of the radial rib RS2 at the rounded edge KT2 are also specified, wherein the radius Ri of the radial groove RN1 is larger than the radius Ra of the radial rib RS2 at the rounded edge KT2. Furthermore, this figure shows that, in the embodiment according to the invention, the grinding gap MS in the area of ​​the radial rib edges KT2 is smaller than the grinding gap MS along the generatrix or flank of the disk S. This effectively prevents the passage of excessively coarse particles or even whole grains through the grinding gap in the area of ​​the rounded edges.

[0055] The arrangement A according to the invention, which is identical to the arrangement A1 according to the invention, is in Fig. 6 shown again separately.

[0056] Fig. 7 shows an arrangement according to the invention, which is essentially the same as the arrangement A described above. Fig. 6 and A1 according to Fig. 3 is identical. Therefore, only the differences in the embodiment of the Fig. 3 and 6 described. Thus, the arrangement A according to the invention has the Fig. 7 At a first end E1, a first end section F1 (shown hatched) is provided, which has the shape of a cylinder and is made of solid material. The central axis MF1 of the first end section F1 is arranged coaxially with the central axis MA of the arrangement A. In the illustrated example, the first end section F1 is materially bonded to the disk SR1 of the arrangement A, which is arranged adjacent to the first end section F1. However, the invention is not limited to this, but can alternatively or additionally have a second end section F2 at a second end E2 of the arrangement A (in Fig. 7(not shown). The length (= thickness) of the first end section F1, measured in the direction of the central axis MA of the arrangement A, is, for example, 5 mm. Providing the described first end section F1 and / or the second end section F2 advantageously increases the mechanical stability of the arrangement according to the invention at one or both ends of the arrangement A according to the invention.

Claims

1. An assembly (A) containing a plurality of disks (S) or consisting of a plurality of disks (S); wherein each of the disks (S) comprises a truncated conical, double conical, or double truncated conical shape; wherein in each of the disks (S), the angle (MWI) between a surface line of the disk (S) and a cone axis (KA) of the disk (S) is > 30 to 82.5 °, preferably 40 to 75 °; wherein the disks (S) are stacked along a central axis (MA) of the assembly (A); wherein the disks (S) are disposed such that the cone axis (KA) of each disk (S) is disposed parallel to or coaxially with the central axis (MA) of the assembly (A); wherein the assembly (A) comprises a plurality of radial grooves (RN) pointing to the central axis (MA) of the assembly (A); wherein the assembly (A) comprises a plurality of radial bars (RS) pointing away from the central axis (MA) of the assembly (A); characterized in that the radial grooves (RN) each comprise a rounded groove base (NG); and the radial bars (RS) each comprise a rounded edge (KT).

2. The assembly (A) according to claim 1, wherein the radial grooves (RN) point perpendicularly to the central axis (MA) of the assembly (A); and / or wherein the radial bars (RS) point perpendicularly away from the central axis (MA) of the assembly (A).

3. The assembly (A) according to claim 1 or 2, wherein the radius (Ri) of the radial grooves (RN) at the rounded groove base (NG) is in each case larger than the radius (Ra) of the radial bars (RS) at the rounded edge (KT).

4. The assembly (A) according to any one of claims 1 to 3, wherein the disks (S) have a diameter of 50 to 500 mm, preferably 100 to 400 mm; and / or wherein the disks (S) have a thickness of 40 to 200 mm, preferably 50 to 80 mm.

5. The assembly (A) according to any one of claims 1 to 4, wherein the radius (Ri) of the radial grooves (RN) at the rounded groove base (NG) is 0.5 to 25 mm, preferably 1 to 20 mm, in particular 2 to 10 mm; and / or wherein the radius (Ra) of the radial bars (RS) at the rounded edge (KT) is determined according to the following first equation (GL1): Ra = Ri − 2 * MS + RT wherein Ra = radius (Ra) of the radial bars (RS) at the rounded edge (KT) in mm; Ri = radius (Ri) of the radial grooves (RN) at the rounded groove base (NG) in mm; MS = grinding gap in mm; and RT = concentricity tolerance in mm; and wherein the grinding gap (MS) has a value of 0.10 to 1.40 mm, preferably 0.10 to 0.80 mm, preferably 0.10 to 0.50 mm, preferably 0.20 to 0.60 mm, in particular 0.20 to 0.40 mm; and wherein the concentricity tolerance (RT) has a value of 0.05 to 0.30 mm, preferably 0.10 to 0.20 mm, in particular 0.12 to 0.18 mm.

6. The assembly (A) according to any one of claims 1 to 5, wherein the assembly (A) comprises a first end section (F1) at a first end (E1); wherein the first end section (F1) has the shape of a cylinder or hollow cylinder; wherein the first end section (F1) is disposed such that its central axis (MF1) is disposed parallel to or coaxially with the central axis (MA) of the assembly (A); and wherein the first end section (F1) preferably has a length, measured in the direction of the central axis (MA) of the assembly (A), from 1 to 100 mm, preferably from 1 to 50 mm, in particular from 2 to 20 mm.

7. The assembly (A) according to claim 6, wherein the first end section (F1) is connected in a force-fit, form-fit or material-fit manner to a disk (SR1) of the assembly (A) disposed adjacent to the first end section (F1) or is integral therewith.

8. The assembly (A) according to claim 6 or 7, wherein the assembly (A) comprises a second end section (F2) at a second end (E2); wherein the second end section (F2) has the shape of a cylinder or hollow cylinder; wherein the second end section (F2) is disposed such that its central axis (MF2) is disposed parallel to or coaxially with the central axis (MA) of the assembly (A); and wherein the second end section (F2) preferably has a length, measured in the direction of the central axis (MA) of the assembly (A), from 1 to 100 mm, preferably from 1 to 50 mm, in particular from 2 to 20 mm.

9. The assembly (A) according to claim 8, wherein the second end section (F2) is connected in a force-fit, form-fit or material-fit manner to a disk (SR2) of the assembly (A) disposed adjacent to the second end section (F2) or is integral therewith.

10. A grinder (MW) for a mill, comprising at least: a first roller (WA1) comprising a first shaft (W1) and a first assembly (A1); and a second roller (WA2) comprising a second shaft (W2) and a second assembly (A2); wherein the first shaft (W1) and the first assembly (A1) are connected in a force-fit, form-fit or material-fit manner to each other or are integral; wherein the second shaft (W2) and the second assembly (A2) are connected in a force-fit, form-fit or material-fit manner to each other or are integral; wherein the first assembly (A1) is an assembly (A) according to any one of claims 1 to 9; wherein the second assembly (A2) is an assembly (A) according to any one of claims 1 to 9; wherein the central axis (MA1) of the first assembly (A1) is disposed parallel to the central axis (MA2) of the second assembly (A2); wherein the radial bars (RS1) of the first assembly (A1) engage in the radial grooves (RN2) of the second assembly (A2); and wherein the radial bars (RS2) of the second assembly (A2) engage in the radial grooves (RN1) of the first assembly (A1).

11. The grinder according to claim 10, wherein the central axis (MA1) of the first assembly (A1) is disposed coaxially with the central axis of the first shaft (W1); and wherein the central axis (MA2) of the second assembly (A2) is disposed coaxially with the central axis of the second shaft (W2).

12. The grinder according to claim 10 or 11, wherein the first shaft (W1) and the second shaft (W2) are disposed with respect to each other such that the central axis of the first shaft (W1) and the central axis of the second shaft (W2) are disposed parallel to each other; and wherein a gap referred to as a grinding gap (MS) is disposed between the first assembly (A1) and the second assembly (A2); and wherein the grinding gap (MS) has a clear width between 0.10 and 1.40 mm, preferably between 0.10 and 0.80 mm, preferably between 0.10 and 0.50 mm, preferably between 0.20 and 0.60 mm, in particular between 0.20 and 0.40 mm, over its entire length.

13. The grinder according to any one of claims 10 to 12, wherein the first roller (WA1) or the first shaft (W1) is rotatably mounted; and wherein the second roller (WA2) or the second shaft (W2) is rotatably mounted; and wherein the first roller (WA1) and the second roller (WA2) are rotatable in opposite directions.

14. Use of at least one assembly (A) according to any one of claims 1 to 9 or of a grinder according to any one of claims 10 to 13 for comminuting a material to be ground; wherein the material to be ground is or contains a plant material, preferably a protein-containing plant material; and wherein the material to be ground is preferably selected from a group consisting of: malt, unmalted grain, rice, corn, millet, chickpea, soybean, potato, and any mixture thereof.

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