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WO2009144249A1 - Dispositif de broyage - Google Patents

Dispositif de broyage Download PDF

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Publication number
WO2009144249A1
WO2009144249A1 PCT/EP2009/056460 EP2009056460W WO2009144249A1 WO 2009144249 A1 WO2009144249 A1 WO 2009144249A1 EP 2009056460 W EP2009056460 W EP 2009056460W WO 2009144249 A1 WO2009144249 A1 WO 2009144249A1
Authority
WO
WIPO (PCT)
Prior art keywords
grinding
grinding bodies
bodies
rotor
container
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2009/056460
Other languages
German (de)
English (en)
Inventor
Kurt Müntener
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Buehler AG
Original Assignee
Buehler AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Buehler AG filed Critical Buehler AG
Publication of WO2009144249A1 publication Critical patent/WO2009144249A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C15/00—Disintegrating by milling members in the form of rollers or balls co-operating with rings or discs
    • B02C15/12—Mills with at least two discs or rings and interposed balls or rollers mounted like ball or roller bearings
    • B02C15/123—Mills with at least two discs or rings and interposed balls or rollers mounted like ball or roller bearings with rings and interposed rollers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C15/00—Disintegrating by milling members in the form of rollers or balls co-operating with rings or discs
    • B02C15/004—Shape or construction of rollers or balls
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C15/00—Disintegrating by milling members in the form of rollers or balls co-operating with rings or discs
    • B02C15/12—Mills with at least two discs or rings and interposed balls or rollers mounted like ball or roller bearings
    • B02C2015/126—Mills with at least two discs or rings and interposed balls or rollers mounted like ball or roller bearings of the plural stage type

Definitions

  • the invention relates to a crushing device according to the preamble of claim 1.
  • Such crushing devices are generally designed as heavy, expensive and space-consuming rolling mills, which serve for the crushing of a variety of ground materials.
  • Particularly well known are u.a. so-called Reibwalzwerke in which several rollers each rotate at different speeds from each other to comminute a regrind, as well as a liquid millbase in the form of a dispersion, such as paints, coatings, coatings or cocoa masses, etc.
  • Reibwalzwerke for these purposes, which provide a fairly good product.
  • a Reibwalzwerke several rollers are pressed against each other and at the same time driven so that they have different peripheral speeds, with always the following roller runs faster than the previous one.
  • the investment and space required for such Reibwalzwerke is not inconsiderable, which is why even agitator ball mills have been proposed for carrying out the so-called wet milling, but which are less preferred in some respects against Reibwalzwerken.
  • agitator ball mills have been proposed for carrying out the so-called wet milling, but which are less preferred in some respects against Reibwalzwerken.
  • a considerable amount of space is required, which will not be given especially for smaller businesses.
  • the invention has for its object to make a crushing device of the type mentioned simpler, space-saving and cost-effective, and this is achieved according to the invention by the characterizing features of claim 1.
  • a cage ring holding together the rollers of at least one grinding ring could be provided which extends in a plane perpendicular to the axes of the grinding wheels and supports their axes (with free space) and which is driven for relative rotation with respect to the races. It is preferred, however, if the races relative to each other are rotatable and at least one of which is provided with a rotary drive, preferably at least the outer race.
  • the invention also provides a kind of refiner conche for the production of chocolate, of so-called compound and fillers of nuts, crocants and the like, which in principle is capable or can be formed so that even coarse-grained ingredients such as granulated sugar, Nuts, etc. may be milled, and it may generally be such that all components of the intended end product, or a large part thereof, are already filled into the device at the beginning of operation.
  • the races are housed in a container space for receiving regrind, although it would also be possible to form them as a separate aggregate, which is submersible in a container, as is known from some mixers.
  • FIG. 1 shows an axial longitudinal section through a first inventive embodiment of a crushing device.
  • Fig. 2 is a section along the line II-II of Fig. 1;
  • Fig. 3 is a section along the line III-III of Fig. 1;
  • Fig. 4 is an enlarged detail to Fig. 1, and
  • Fig. 5 is a partial section along the line V-V of Fig. 4;
  • FIG. 6 shows an inclined variant of FIG. 1
  • Fig. 7 is an enlarged section along the line VII-VII of Fig. 5;
  • Fig. 8a is a side view of a grinding body shown in Figs. 1-7, to which
  • Fig. 8b is a view in the direction of arrow b of Fig. 8a, whereas the
  • Fig. 8c illustrates the layout of such a grinding body and the Fig. 9 shows a variant of a hollow grinding body
  • Fig. 10 illustrates another embodiment with several rows of grinding media of the type previously shown, including the
  • Fig. 1 1 illustrates a section along the line XI-XI of Fig. 10, which in turn is a section along the line X-X of Fig. 11, whereas the
  • FIGS. 10 and 11a show similar to FIGS. 10 and 11 a variant with three Mahl stressesringen, wherein Fig. 10a is a section along the line Xa-Xa of Fig. 11 and Fig. 11 a is a section along the line XIa-XIa 10a, and
  • FIG. 12 illustrates the geometric relationships in the region of the grinding bodies of FIG. 10 on an enlarged scale along the line XII-XII of FIG. 11, but in a variant slightly modified with respect to FIG. 10, whereas FIG. 12
  • Fig. 12a is a section similar to Fig. 12, taken approximately along the line XIIa-XIIa of Fig. 11a;
  • Fig. 13 is another embodiment with conical grinding bodies, including the
  • Fig. 14 is a section along the line XIV-XIV of Fig. 13;
  • FIG. 15 illustrates a variant similar to FIG. 13, but with a plurality of superimposed grinding stages
  • Figs. 16 and 17 contrast two possible arrangements of conical grinding media, of which Fig. 16 is a section along the line XVI-XVI of Fig. 19a, and Fig. 17 is a section along the line XVII-XVII of Fig. 19 , and wherein the cutting guide is in each case designed such that the drawing-in gap 19a can be seen between two adjacent grinding bodies
  • FIG. 18 shows a practical example with conical grinding bodies with an arrangement of the grinding bodies corresponding to FIG. 17, to which the FIGS Fig. 19 shows a section along the line XIX-XIX of Fig. 18, which in turn is a section along the line XVIII-XVIII of Fig. 19;
  • Fig. 18a illustrates this an alternative arrangement to Fig. 18 in section along the line XVIIIa-XVIIIa of Fig. 19a, and the
  • Fig. 19a shows a section along the line XIXa-XIXa of Fig. 18a;
  • Fig. 20 shows an arrangement similar to that of Fig. 18, but with a plurality of superimposed grinding stages
  • Figs. 21-26 illustrate various other embodiments of grinding media, wherein Fig. 23b is a section on the line bb of Fig. 23a, Fig. 24b) is a plan view of Fig. 24a, Fig. 25b) is a section on the line bb Fig. 25a is and Fig. 26b is a section along the line bb of Fig. 26a;
  • Fig. 27 is a plan view of a guide and sliding block as shown in section in Fig. 4;
  • Fig. 27a is a section along the line XXVIIa-XXVIIa of Fig. 27;
  • Fig. 27b is a section along the line XXVIIb-XXVIIb of Fig. 27a;
  • Fig. 28 is a perspective view of a guide and sliding block of Fig. 27;
  • Fig. 29 shows a plan view of a plate-like end of a rotor with a view of radially arranged, the sliding blocks of Figure 27 respectively receiving grooves, in which the sliding blocks (and with them the outer grinding media) can move radially;
  • Fig. 30 is a section along the line XXX-XXX of Fig. 29.
  • a container 1 is provided, which is suitably designed for tempering double-walled with an annular tempering 2.
  • tempering the choice of means for tempering is not critical, so that many of the known types can be used here. If the term "tempering" is used here as a generic term, then it should include both (or Alternatively, a heating or warming device as well as a cooling device understood, because depending on the to be comminuted - in general liquid - Good one or the other, or in sequence both may be desirable.
  • the supply and removal of temperature control via an inlet connection 4 or via an outlet 5.
  • the flanged bottom 6 may have an approximately disc-shaped temperature control 2 ', which is connected to inlet and outlet ports 4' and 5 '.
  • the container 1 has a filling opening 3, which is realized here in the form of a hopper.
  • this inlet opening can be of any desired design, that is to say as here as mere pouring opening or as pipe connection for forcibly feeding a dispersion, such as a cocoa-containing mass or about a dye or lacquer dispersion or a plastics material, via a pump.
  • a level sensor 12 here indicated only schematically and which can be formed in any desired manner, may be provided which optionally regulates the supply (for example a feed pump) to a predetermined level.
  • the container 1 Inside the container 1 is at least one rotor, in the present case the two, namely an inner rotor 7 driven by a motor M1 and a shaft 11 'and an approximately bell-shaped outer rotor 8 driven by a motor M2, a belt pulley 10 and a hollow shaft 11 intended.
  • This bell rotor 8 has openings 9, passes through the mass to be massed from the outer container 1 into the interior of the bell rotor 8 and thus to the inner rotor 7. Since it is provided that the outer rotor 8 rotates, if appropriate, relatively slowly, the motor M1 is preferably connected to a self-locking gear, such as a worm gear. For some applications, however, it may be desirable to reverse drive the inner rotor 7 slowly (e.g., via a worm gear) and run the outer rotor fast.
  • a self-locking gear such as a worm gear
  • the tempering chambers 2, 2 ' In order to enable the introduction of high amounts of energy without damaging the temperature of the mass to be mashed, attention has already been drawn above to the tempering chambers 2, 2 '. However, it is expedient if at least one of the rotors 7 and / or 8 can be tempered.
  • a rotary input / output 13 for the supply of a coolant to a supply channel 14 of the hollow shaft 11 is provided on the hollow shaft 11, from where the coolant flows along (or helically guided) a tempering channel 15 of the outer rotor 8, to get to the bottom in an annulus 16 to a discharge channel 17, to flow upwards (see upward arrow on the hollow shaft 11 in a drain channel 14 ') and exit from the rotary input / execution 13 according to the exit arrow again.
  • This can be done in a, possibly regulated, cycle, much as it is known for agitator mills.
  • cooling system can be used; For example, the use of evaporable coolants has already been proposed for agitator mills as in a refrigerator.
  • the heat dissipated in this way is in the region of a lining of the lower part of the outer rotor 8, e.g. made of harder material, existing annular grinding surface 18 (distribution cylinder), roll on the grinding body 19 under friction.
  • the grinding bodies 19 are similar to a roller bearing in an outer Mahl Eisenring (dash-dotted) 20, wherein the annular grinding surface 18 to some extent forms the race of this "roller bearing.”
  • These grinding bodies 19 are so on Gap arranged in the circle 20 that they engage in the interstices of (here) smaller grinding media 21 and in turn each form Reibspalte, in which the liquid to be mowed Good drawn and ground by a difference in speed of the grinding media 19 against the grinding media 21 (not necessarily) smaller media 21 could in turn interact with an inner stator 22 ( Figure 4) as a refining surface, but a more preferred embodiment is shown in Figure 1. It is therefore also clear that the media 21 thus to some extent form an inner media ring. with the contact surfaces 23, 24
  • a loading device spring
  • any other loading device such as a hydraulic or pneumatic It is preferred if the pressure of the loading device 25 is adjustable, for example adjustable by means of an adjusting nut 31.
  • an outer holder 30 is advantageously provided as an anti-twist device for the inner stator 22.
  • this type of load results in an advantageous manner on the one hand for the grinding on the surfaces 23 and 24 acting grinding pressure
  • this pressure acts as a result of the slope of the surfaces 23, 24 against the voltage applied to the small grinding media 21 large grinding media 19, so that the grinding pressure necessary for the action of a friction rolling mill, both between the individual grinding bodies 19, 21, and between the grinding bodies 19 and the friction surface 18 of the rotor 7, is ensured.
  • the surfaces 23, 24 act as an inner race.
  • the filled through the opening 3 mass passes through the openings 9 into the interior of the bell rotor 8 and between the grinding media 19, 21 and grinding surfaces 18, 23, 24 of the rotors 7 and 8.
  • a conveyor for the, in particular ongoing or ongoing, supply of the ground material from bottom to top to the feed openings 9 are provided in the interior.
  • the outside of the bell rotor 8 is provided with an upwardly conveying screw conveyor 27, ie that its rotary Direction is chosen so that this screw 27 also really upwards against the openings 9 promotes.
  • the drive of the outer rotor 8 serves a dual purpose, namely on the one hand the generation of a differential speed of the grinding surfaces 18, 19 and on the other hand as a drive member for the screw 27th
  • a Mahlgutstrom from the inlet opening 3 results in an annular space 28 between the container 1 and bell rotor 8, from there into the openings 9, down to the grinding media 19, 21 and further down to the, preferably oblique, lower end faces 29 of the large grinding media 19.
  • the bevel of the end face 29 entails that this results in a wider grinding gap together with a reinforced bottom surface 2a, but which leads through the slope to an improved intake angle, for example for coarser particles of the ground material, such as sugar crystals or nut particles.
  • the surface 29 cooperates with the bottom surface 2a of the container 1, but it could also be combined with any, e.g. cooperate at any height through the container continuous wall, which may be slightly inclined as the bottom 2a, so as to cooperate to form a pull-in gap (19a in Fig. 7). It is clear that such an inclined surface could also be provided on the upper side of a grinding element and interact there with a corresponding wall passing through the container space, but an arrangement on the underside and especially in the region of the bottom wall 2a will be particularly recommended.
  • the thus treated regrind is then either through the conveying action of the screw 27 again via the outer space 28 (in which it can be intensively heated or cooled by the flow through a tempered from both sides passage or cooled) the openings 9 or fed (simultaneously or in individual batches are emptied through a discharge opening 32, wherein in the illustrated embodiment, the discharge opening is closed by a movable piston 33.
  • the arrangement described acts as a combined 2-stage rolling process by coarse grinding of oversized solid components, which would not be drawn into the grinding gap of the abutting cylindrical surfaces of grinding media 19, 21 and friction surfaces 18, simultaneously with the already sufficiently fine particles between the cylindrical surfaces , now be pre-ground between the surface 19 a and the bottom surface 2 a to the required fineness in order to subsequently pass through the feed nip between the cylindrical surfaces for fine grinding.
  • the formation of the outer rotor 8 can be seen there particularly clearly. He has, as already mentioned, a double wall, in which a to the channel 14 (Fig. 1) connected inlet pipe 33 opens for the temperature control, and from which a discharge channel 14 '(Fig. 1) leading outflow pipe 34 opens again.
  • the openings 9 are preferably so coordinated with the direction of rotation cw of the outer rotor 18 that they favor the passage of the ground material from the annular outer space 28 into the interior of the bell rotor 8 by oblique intake walls 35.
  • the intake wall which thus draws out the grinding stock, could also be extended radially outward, for example, to the inner wall of the container housing.
  • this cone In connection with the surfaces 23, the cone carrying them was referred to as a "compensating cone.” In fact, this cone preferably has a double function in that it forms not only the counter-bearing surface for the grinding-element cones 21 ', but also the support for the cone Loading device 25.
  • a load balancing arrangement which, for example, accommodates the compensating body 23 and supports it movably, for this purpose, a ball bearing with a spherical surface 38 can be provided in its center, around which the body 23 can become more or less inclined, depending on the wear Mahl Sciences 21 between the surfaces 23 'and 24 are held and on them, as on races of a roller bearing - but sliding because of the differential speed while shearing and rubbing - the cones 19 'are held in guide and sliding blocks 39 of the rotor 7 in their position relative to the central axis Z of the shaft 11' , wherein its conical surface on the angled surfaces 39 '(see.
  • Figs. 27 to 28, in particular Fig. 27b) of Guide and sliding blocks 39 is held.
  • the passage openings 40 in the inner rotor 7, and 40 'in the guide and sliding blocks 39 ensure the flow of the ground material to the grinding media or the entirety of the grinding arrangement.
  • the guidance of at least one of the outer grinding elements 19 in these guiding and sliding blocks 39 has two functions (the term "stone", of course, does not designate the material of which they are made, although this would also be possible, preferably a hard, abrasion-resistant one Material, such as metal, hard metal, ceramic or the like):
  • the inner rotor 7 keeps above the guide and sliding blocks 39, the back pressure to the vertical pressure generated by the grinding in the Mahlspalt 19a from the pre-grinding of the oversized solid particles in the dispersion to be mulched.
  • the guide and sliding blocks 39 embedded in the star-shaped grooves 7 '(see Fig. 29) allow a radial movement of the grinding bodies 19, primarily outwards, and thus the application of an indirect pressure of the loading device 25 the internal grinding bodies 21, which in turn act on the outer grinding bodies 19 by means of their cones 21 'and 21 "and are thus able to press them against the cylindrical friction surface 18 of the outer rotor 8 (FIG.
  • the continuous abrasion of the grinding media 21 and 19 and the friction surface 18 requires a continuous feeding of the grinding media 21 and 19 radially outward. This feeding is ensured by the guide and sliding blocks 39 in two respects: once by the sliding possibility of the cone tips 19 'within the angled surfaces 39' (see Fig. 27a, 28), as in Fig.
  • the second function of the leadership of at least one outer grinding body 19 in the guide and sliding blocks 39 is that the interaction of the outer grinding body 19th with the inner rotor 7 the whole Mahl Sciencesp, ie the Mahl Sciencesn 19 and 21, by the, eg predetermined, speed of the inner rotor 7 by means of the drive motor M1 a certain speed of planetary circulation of Mahl stresseses 19, 21 imposes and thus the desired differential speed between the grinding surfaces create among each other, and possibly also controls, leaves.
  • This also applies if only a single grinding body 19 is connected to the inner rotor 7 with respect to the central axis Z (of course not with respect to its own grinding body axis), which latter is at the same time also the rotor axis of the inner rotor 7.
  • any number of grinding bodies 19 and 21 may be provided.
  • the position of the inner rotor 7 and its grinding bodies 19, 21 is actually overdetermined with more than three outer grinding bodies 19 in the sense of an edition on more than three points.
  • the device - as shown in Fig. 6 - constantly or only in some stages of the process can be kept awry. In this case, of course, a (relatively) asleep level of the liquid ground material at the sensor 12 will result.
  • Fig. 7 shows the grinding zone on a larger scale. Since coarser particles, such as granulated sugar settle on the bottom 2a, it makes sense to form this bottom 2a as a harder friction plate 2a, which is connected to the oblique, lower end faces 29 of the large grinding bodies 19 (as the intake gap 19a for the premilling of the oversized grain fractions of the dispersion). interacts. At the same time, a fine grinding zone results between the distribution cylinder 18 and the grinding bodies 19 rubbing and rolling against it, in particular for that via the holes 40, 41, 41 'and the openings 9 repeatedly brought up, generally liquid, ground material.
  • Figs. 8a to 8c show the large grinding media 19 from the side (Fig. 8a); 8b in a view b of Fig. 8a, that is rotated by 90 °, so that the lower inclined end faces 29 are visible; and in plan view ( Figure 8c). It is shown with reference to FIG. 9 that it would also be possible to make these grinding bodies hollow as grinding bodies 119.
  • the cavity is used in liquid millbase (because in rarer cases can also be particulate, at least flowable, dry millbase comminuted) for cooling the grinding media 119 by the liquid millbase can flow through the hollow grinding body 119 and in turn acts as a cooling medium with the inventive shredder or Mahl stressestage absorbed.
  • 10 and 11 illustrate a variant embodiment, seen in the axial direction of the container 1, a plurality of layers A, B, C of rotating grinding bodies 19, 21.
  • the same reference numerals are used for parts identical function as in the previous figures, for Parts only similar function the same reference numerals, but provided with an addition. It should be noted that the possibility of coarse or pre-grinding, as given in FIG. 1 by the interaction of the surfaces 2 'and 29, is not shown or the apparatus described below is designed only for fine grinding.
  • Mahleniaringe A, B, C instead of the three Mahl Sciencesringe A, B, C, if desired, also odd, more, five or more Mahl Sciencesringe can be provided, which of course has effects on the one hand to be introduced on the respective drive grinding performance, on the other hand also on the dissipated heat.
  • the grinding bodies 19 of the layers A and C may optionally have different diameters from each other.
  • the inner grinding bodies 21 would then have different diameters at the upper side with respect to the lower side, or that the arrangement of the lower and upper grinding bodies 19 would not be so symmetrical with respect to the inner grinding bodies 21, as can be seen from FIG ,
  • the upper media of layer A could have a larger diameter than the lower media 19 of layer C, but their downwardly facing cones 19b would be longer so that they again frictionally contact the upper cones of the inner media 21 at a location where their diameter corresponds to the distance ratios between the inner grinding bodies 21 and the distribution cylinder 18.
  • the type of load that presses the grinding media not only against each other and against the outer friction surface 18 and the outer rotor 8, but also simultaneously against the inner (n) friction surface (s) 23 and 44 of the inner stator 35a.
  • the spring 25 of Fig. 1 the conical surfaces 24 and 23 loaded, which act on the inner grinding media 21, here act the surfaces 23, 24 on the cones of the outer grinding body 19.
  • the load is in this case from above, and preferably adjustable by a spring housing 45 via a sealed disc 31 a and the spring 25, adjustable by means of the screw bolt 31 b with respect to their compressive force, with its friction surfaces 23 'on the upper outer grinding body 19 and thus interacts with the inner grinding media 21, all Mahl Eisenringe A to C charged
  • the arrangement according to FIG. 10 preferably has a cooled stator 35a, with a coolant space 49 inside this inner stator 35a.
  • the coolant space 49 in turn is supplied with coolant (or temperature control medium) via an inflow pipe 4 ", which also supplies the bottom gap 2 'from there ..
  • FIG. 12 shows a section along the line XII-XII of Fig. 1 1, but with slightly varied Mahl stresses 19, 21.
  • the top of the cones 19 ' is here somewhat shallower and is below an expedient 90 °, angle ⁇ .
  • the friction surfaces 23 are extended to the cone tip of the grinding media 19, so that an enlarged grinding surface (or a enlarged friction gap) between these two parts 19 'and 23 results, but also increases the braking effect on the grinding media 19.
  • This braking effect leads, inter alia, to that speed difference which results in friction (and thus the effect of a friction rolling mill), which in turn prevents the grinding bodies 19 from merely rolling on the distribution cylinder 18.
  • This braking effect is particularly desirable when no driven inner rotor 7, as shown in Fig. 1, is used, which inner rotor with its own drive M1 otherwise for the braking effect or for generating a differential speed between the grinding bodies 19, 21 and the friction surfaces, as the friction surface 18, provides.
  • FIGS. 10a and 11a show a variant for which the above with respect to FIGS. 10 and 11 applies, but in which still a third Mahl Sciencesring 51 with slightly smaller, in this example cylindrical, Mahl Sciencesn 52 in addition to the previously described Mahl Sciencesringen 20th and 26 is used (see Figures 2 and 11).
  • Fig. 12a shows these cylindrical grinding media 52, which - since they are just cylindrical - in the axial direction Ax of the container 1 must not follow an axial movement caused by the loading device and therefore can be interconnected by a shaft 53. Since the distribution cylinder 18 but extends over the full height of the three Mahl Sciencesringe A, B, C, it would also be possible to form the cylindrical grinding media 52 - without the shaft 53 in between - reaching over the entire height.
  • a bell rotor is missing, and it is only one (possibly single) rotor 8a as an outer rotor with the grinding bodies 19c holding and in the star-shaped grooves 7 '(see Fig. 29) of the here annular end of the rotor 8a embedded and as described - provided in the grooves T radially slidable guide and sliding blocks 39.
  • a relatively thin inner rotor 7a is provided, which is pressed in the direction of the arrows 25 'by an arbitrary, per se loading device down.
  • a loading device could also act on the lower conical surfaces 24, which are rigidly secured to the bottom plate 2 in this embodiment.
  • a controllable differential speed between the grinding surfaces when a relatively thin, only the friction surfaces ("race of a roller bearing") carrying inner rotor 7a rotatably mounted, and preferably also via a motor (similar to the motor M2 of Fig. 1) driven
  • the arrows P1 and P2 show, as an example, the directions of rotation of the two rotors 7a, 8a, but they could also have the same direction of rotation arises.
  • the rotor 8a expediently has a cylinder wall 50 which is provided with openings 9a between webs 56, which openings 9a may in principle be made similar, as has been explained with reference to FIG.
  • the product to be mashed can not be pumped from above through the opening 3, but from below via a supply pipe 3a, wherein the ground material up into the room 1 a, possibly from below passes through the grinding zone, passes.
  • the space radially outside the friction surfaces 18a is used as a tempering and the pipes 5a and 32 serve as supply and discharge pipes for temperature control.
  • the inner and outer grinding bodies 21c and 19c have approximately the same size.
  • the position of the inner grinding bodies 21c are defined by their lower and upper cones 21 "and 21 'and the contact with the friction surfaces 23 and 24, which are inner races of a roller bearing
  • the outer grinding bodies 19c are in contact with the now conical friction surface 18a, on the other hand on the conical surfaces of the upper cones 21 'of the inner grinding body 21 and are held by the, now on the outer rotor 8a in guide and sliding blocks, analogous to Figs. 1, 5 and 27 to 29, which stones 57 in radial guides or again radially arranged grooves 40a (similar to the grooves T of Fig. 5) are radially displaceable and so to allow a radial position change to compensate for wear.
  • a spherical surface 38 has been shown on the grinding surfaces 23 to compensate for different wear, here are the grinding bodies 19c, which are provided with such a "gimbal" 38a, to a slight tilting movement of the respective grinding body relative to the friction surface 18a in the case allow different wear.
  • a temperature control or cooling of the shaft 1 1 'of the inner rotor 7a is possible, as can be seen in particular from FIG. 13.
  • a feed tube 59 is provided as a feed channel in the relatively thick shaft 11 ', whereas the annular space 60 surrounding this tube 59 serves as a drainage channel. It is clear that these channels 59, 60 are provided at the top in a similar manner with a rotary inlet, as the device of Fig. 1 with the rotary inlet 13th
  • this embodiment variant too is to a certain extent "multiply” by arranging several layers of grinding body rings A, B and C in the axial direction, such an embodiment being shown in FIG. 15.
  • the outer grinding bodies 119 are provided with intermediate rings 7 ', 7 " Rotor 7a connected, whereby the rotor 7a by means of its associated drive bes determines the speed of the Mahlmorringe about the central axis Z, whereas the rotation of the grinding bodies 119, 121 about its own axis by the drive of the central shaft 11 'via the wedges 58a at its wedged conical pieces 58 and is determined.
  • the rotational speeds of the rotor 7a and the central shaft 11 ' are chosen so that instead of a mere unwinding of the grinding bodies 119, 121 at the friction surfaces 18a, 23, a rubbing or shearing (speed difference) is formed.
  • the rotor 7a is again loaded by a spring 25a, which in turn may be loaded either by a construction (arrows 25 '), similar to that shown in Fig. 10, or by a fluidic loading device, in which case the spring 25a is more the function has to cushion the force of this fluidic load device elastic, or even completely eliminated.
  • the vertical pressure generated by the loading device 25a on the outer grinding bodies 119 is transmitted via the inner grinding bodies 121, to the annular friction surfaces 24, as well as to the cone pieces 58, respectively on the next lower Mahlèveringe.
  • the loading device 25a can also act on the cone pieces 58 or on both, the rotor 7a and / or the cone pieces 58 can be loaded to provide the necessary pressure on the friction surfaces on the one hand between the grinding body 119, 121 itself, on the other hand between the grinding bodies 119th , 121 and the friction surfaces 18a and 23 to produce.
  • the outer grinding bodies 119 are again connected by means of guiding and sliding blocks 57 to the intermediate rings 7 ', 7 ", while with their conical outer surfaces they are supported downwards against complementary conical friction surfaces 18a, on which the material to be ground passes
  • the outer surfaces of the downwardly converging outer surfaces of the grinding bodies 119 abut against the upward converging outer surfaces of the inner grinding bodies 121.
  • the internal grinding bodies 121 also have (depending on the type of installation) upwardly or downwardly swept conical surfaces 21 "which interact with friction surfaces 24. These friction surfaces 24 are fixedly mounted on the base 2a and on the grinding rings A and Br on the support rings 24 ' However, if necessary, the conical lateral surfaces of the inner, conical grinding bodies 121 rest against the inner conical friction surfaces 23 and exert the comminuting friction and shear there.
  • the container 1 'of individual, provided with mounting flanges 62 housing rings 63 may be constructed. This has the advantage that it is easily possible, instead of one, two, or three Mahl stressesringe A, B, C build a different number of modular.
  • each housing ring 62 may be provided with a temperature control inlet 4 and a drain pipe 5. Furthermore, the comminuted material to be ground, for example in the manner of FIG. 1, can also be supplied or removed from above, eg via the inlet trench 4 '', for example (best, especially in the case of supply from below) via a discharge pipe 32 located at the top.
  • FIG. 16 corresponds to the section XVI-XVI in an arrangement according to FIGS. 18a and 19a, but with the difference that between the embodiments according to FIGS. 13 to 15 and those according to FIGS. 18 to 19 a Stator surfaces or the friction surfaces are mounted differently.
  • Mahleniaringe 1 above is mounted radially and axially expediently by means of a spherical roller bearing.
  • Mahleniaringe form the lower abutment of the inner rotor 7b .
  • Mahleniaringe thus have a dual function, namely on the one hand a milling and on the other hand, a storage unit.
  • an inner rotor is not provided, and the rotation of the grinding bodies about their own axis as well as the rotation of the Mahl stressesringes around the central axis Z takes place solely by means of sliding frictional engagement over the outer rotor.
  • 16 corresponds to the section along the line XVI-XVI of FIG. 19a
  • the illustration of FIG. 17 corresponds to the section along the line XVII-XVII of FIG. 19.
  • FIGS. 7 and 12a show and FIGS. 16 and 17 show the section through the grinding bodies in their contact line according to the sectional details in the associated plan views.
  • Fig. 16 shows an embodiment with cylindrical friction surfaces 18a and 44 and designed as a plate rings friction surfaces 23 and 24, wherein the axes of the grinding media 19d and 21 d are skewed to the vertical.
  • FIGS. 18 and 19 An apparatus equipped with the configuration of FIG. 17 is shown in FIGS. 18 and 19.
  • the advantage of this solution lies in the fact that the arrangement of the inclined, purely conical grinding bodies without having a cylindrical part, as well as the solution according to FIGS. 16 and 18a is very space-saving with respect to the grinding media and thus allows a dense packing of grinding media in a container, but compared to the embodiment of FIGS. 16 and 18a no obliquely conical or friction surfaces on the outer rotor, inner stator or inner rotor required, which in particular a solution with several grinding rings at an axial distance, such as the Fig. 20 shows, is of great advantage.
  • the pressing of all friction or shear surfaces takes place, as shown in FIG. 10, by means of a loading device 25 within a housing 45.
  • FIG. 18 a shows an example of a similar configuration, but with grinding body axes running at least approximately parallel to the central axis Z.
  • the inner friction surface 44 ' is conical, and it may in turn be provided (in the form of a gap, but actually a Mahlspalt forming) friction surface 24 in the form of an inwardly facing cone ring. It then results in a horizontal section through the line of contact of the respective inner and outer grinding body according to the line XIXa-XIXa the image shown in FIG. 19a.
  • FIG. 20 with reference to a longitudinal section through a variant embodiment.
  • the loading spring 25a in the Mahlgutraum of the container 1 " presses on one, for example by means of keyways in the housing cylinder secured against rotation annular disc 31 d and thus loads the annular friction surface 23.
  • the container 1 is expediently made up of individual modular rings 63, but the bottom ring 63 'may possibly be made slightly less high.It is also understood that the containers V and 1" according to FIG. 6 are also skewed, pivotable or can be arranged horizontally.
  • a self-aligning bearing 65 is provided.
  • the grinding material flow is inversely to that of FIG. 1: The uncomminuted material passes from below - pumped by a pump, not shown - through a feed pipe 3b and flows upwards until it exits through the outlet pipe socket 32 again.
  • the arrangement corresponds approximately to that of a stirred mill. But also a flow from top to bottom or horizontal position vice versa from left to right and vice versa is possible.
  • the rotors which here in all embodiments with only one camp, so to speak "flying" should be stored, unless you want to call the arrangement of the grinding media as their second camp, even with a stub shaft through the opposite end of the storage of the container wall by means of corresponding dynamic seals can lead to the rotors 7, 8, 8a, outside the container a second time, so to speak, in a classical manner, to store, if you then but the grinding media anyway and continue As a bearing, even a triple bearing of the rotors results.
  • FIGS. 21 to 26b With reference to FIG. 9, a hollow, substantially cylindrical grinding body 119 has already been presented. A corresponding conical grinding element 219 is illustrated in FIG. 21. Due to its hollow, preferably cylindrical interior 68, ground material can flow and thus contribute to a certain cooling and mixing effect. For this purpose, it may be advantageous if mixing tools are provided or insertable inside, but this is not always desirable in terms of facilitated cleaning.
  • the hollow design contributes mainly to better cooling because the regrind itself is simultaneously coolant and so, with a pick execution of the grinding media, a heat accumulation can be avoided as a result of their grosserer mass.
  • An embodiment can be seen with reference to FIG.
  • slotted versions can also be transferred to hollow cylindrical grinding media 419, as illustrated in FIG. 24a with its section b) and FIG. 25a with section b).
  • the cylindrical grinding body 419 has a straight slot 69 extending along a generatrix; According to Fig. 25a, an obliquely to the generatrix, i. helical slot 69a.
  • the sections b) each show how - in the desired direction of rotation in the direction of the arrow ccw - the slot 69 or 69a should preferably be configured in cross-section, namely so that a flow of material from its interior in the opposite direction to the direction of rotation ccw and simultaneously retracted oversized grains can be fed and at the same time oversized grains of the ground material can be fed.
  • slots are advantageous for producing a material flow from the interior of the hollow grinding body
  • the slots do not necessarily have to extend over the entire length of a grinding body, as shown in FIGS. 26 a) and b).
  • a straight (it could also be lying obliquely to the generatrix) slot 69b extends over only a portion of the length of the grinding body 519.
  • a distance measuring device can be provided at the bottom of the container, or in horizontal containers on the front side of the end - seen in the printing direction of the loading device ago, the distance between the container bottom 2a and the respective lowermost or last To measure grinding media to indicate when the grinding media must be replaced because of excessive wear.
  • This may also be a position sensor or a rangefinder, for example, according to the Trianguilati- onslick, where - depending on the ground material - ultrasound or photoelectric, such as laser rangefinder, as well as measuring devices that work by means of inductive current, come into question.

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  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Grinding (AREA)

Abstract

L'invention concerne un dispositif de broyage pour une matière à moudre. Plusieurs corps de mouture (19, 21) de type cylindres ou rouleaux sont mis en rotation à l'aide d'un mécanisme d'entraînement (M1, M2) pour broyer entre eux la matière à moudre dans un interstice de mouture. A cet effet, les corps de mouture (19, 21) sont disposés en anneau autour de bagues de roulement (18, 23, 24) à la manière d'un palier à rouleaux. A l'extérieur d'une bague de corps de mouture intérieure (26), il est prévu de préférence au moins une bague de corps de mouture située davantage à l'extérieur (20), dont les corps de mouture (19), espacés les uns des autres, sont disposés à des intervalles respectifs entre deux corps de mouture (21) de la bague de corps de mouture intérieure (26), disposés à distance l'un de l'autre et forment dans chaque cas un interstice de mouture avec les corps de mouture (19) de la bague de corps de mouture intérieure (26). En variante ou en complément, les bagues de roulement (18, 23, 24) peuvent tourner l'une par rapport à l'autre et au moins une d'entre elles peut être munie d'un mécanisme d'entraînement rotatif (M1, M2). Les corps de mouture (19, 21) peuvent être au moins partiellement de forme conique, par exemple tronconique.
PCT/EP2009/056460 2008-05-27 2009-05-27 Dispositif de broyage Ceased WO2009144249A1 (fr)

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CH00803/08 2008-05-27
CH8032008 2008-05-27

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010030480A1 (de) * 2010-06-24 2011-12-29 Hitachi Power Europe Gmbh Wälzmühle und Verfahren zur Bestimmung des Verschleißes einer Wälzmühle
CN112087704A (zh) * 2020-09-29 2020-12-15 徐长金 一种防夹伤的麦克风外壳打磨设备

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1833560A (en) * 1930-02-10 1931-11-24 Hugh R Carr Pulverizer mill
DE651638C (de) * 1936-09-05 1937-10-16 Chemische Werke Brockhues Akt Quetschmuehle
US2464733A (en) * 1945-08-09 1949-03-15 Jr Samuel William Traylor Multiple stage roller pulverizer
US2574979A (en) * 1949-03-14 1951-11-13 Messinger William Vertical axis dispersion mill with drive motor supported from conical grinding head
DE1208605B (de) * 1959-04-21 1966-01-05 C U R A Patents Ltd Waelzkoerperquetschmuehle mit rotierender, als Drehkoerperinnenflaeche ausgebildeter Mahlbettflaeche
US3368763A (en) * 1964-05-01 1968-02-13 John Robert Berend Processing apparatus
DE2138025A1 (de) * 1970-07-29 1972-02-03 Bristol, Bertram W, Verona, N J (VStA) Mahlvorrichtung

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1833560A (en) * 1930-02-10 1931-11-24 Hugh R Carr Pulverizer mill
DE651638C (de) * 1936-09-05 1937-10-16 Chemische Werke Brockhues Akt Quetschmuehle
US2464733A (en) * 1945-08-09 1949-03-15 Jr Samuel William Traylor Multiple stage roller pulverizer
US2574979A (en) * 1949-03-14 1951-11-13 Messinger William Vertical axis dispersion mill with drive motor supported from conical grinding head
DE1208605B (de) * 1959-04-21 1966-01-05 C U R A Patents Ltd Waelzkoerperquetschmuehle mit rotierender, als Drehkoerperinnenflaeche ausgebildeter Mahlbettflaeche
US3368763A (en) * 1964-05-01 1968-02-13 John Robert Berend Processing apparatus
DE2138025A1 (de) * 1970-07-29 1972-02-03 Bristol, Bertram W, Verona, N J (VStA) Mahlvorrichtung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010030480A1 (de) * 2010-06-24 2011-12-29 Hitachi Power Europe Gmbh Wälzmühle und Verfahren zur Bestimmung des Verschleißes einer Wälzmühle
CN112087704A (zh) * 2020-09-29 2020-12-15 徐长金 一种防夹伤的麦克风外壳打磨设备

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