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EP0173831B1 - Moulin à percussion - Google Patents

Moulin à percussion Download PDF

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Publication number
EP0173831B1
EP0173831B1 EP85108782A EP85108782A EP0173831B1 EP 0173831 B1 EP0173831 B1 EP 0173831B1 EP 85108782 A EP85108782 A EP 85108782A EP 85108782 A EP85108782 A EP 85108782A EP 0173831 B1 EP0173831 B1 EP 0173831B1
Authority
EP
European Patent Office
Prior art keywords
mill
casing
opening
hammer mill
openings
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.)
Expired
Application number
EP85108782A
Other languages
German (de)
English (en)
Other versions
EP0173831A2 (fr
EP0173831A3 (en
Inventor
Jörg A. Ammann
René Treier
Pierre-Alain Froidevaux
Beat Thoma
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
Priority to AT85108782T priority Critical patent/ATE39065T1/de
Publication of EP0173831A2 publication Critical patent/EP0173831A2/fr
Publication of EP0173831A3 publication Critical patent/EP0173831A3/de
Application granted granted Critical
Publication of EP0173831B1 publication Critical patent/EP0173831B1/fr
Expired 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
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/14—Disintegrating by mills having rotary beater elements ; Hammer mills with vertical rotor shaft, e.g. combined with sifting devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/26—Details
    • B02C13/286—Feeding or discharge
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/26—Details
    • B02C13/30—Driving mechanisms

Definitions

  • the invention relates to a hammer mill according to the preamble of claim 1.
  • Such an impact mill has become known, for example, from DE-PS 1016048, the different groups of impact tools being assigned to different rotor diameters.
  • the housing of this known impact mill is step-shaped
  • US Pat. No. 2,838,346 shows a conical impact mill housing, a group of impact tools being assigned to a single diameter.
  • the invention is by no means limited to striking tools with different rotor diameters; rather, the division into groups can also be carried out by appropriate spacing or by arrangement at uniform or different axial distances.
  • the conventional impact machines are relatively difficult to adapt to different circumstances, such as different types of ground material or different quantities to be processed.
  • sieves of different hole sizes are generally provided, by means of which the dwell time within the grinding chamber is practically determined, because any grain which does not correspond to the sieve hole size is beaten until it can pass through the sieve holes.
  • This also applies to an embodiment according to DE-A 2547008, in which several grinding rooms, each with an outlet closed by a sieve, were connected in series. Exchanging the sieves when changing the regrind or the required fineness is in any case associated with a certain amount of work, even if this could be reduced by various measures, for example in accordance with CH-PS 622188.
  • the invention has for its object to provide a simplification in the adaptation of a single mill to different circumstances, and this is achieved according to the invention by the characterizing features of claim 1. Because the millbase is fed to the mill at different locations and / or at different locations (in particular in the axial direction of the rotor), depending on the arrangement, various advantages can be achieved. An equalization of the supply of the regrind (and thereby an energy saving) will also be achievable - especially with training according to claim 10 - as well as a different number of striking tools will be used, especially in a development of the invention according to claim 12.
  • a sieve is no longer absolutely necessary in the embodiment according to the invention.
  • a sieve can be used, but its replacement is no longer necessary in every case, since the fineness of the grinding is no longer determined exclusively by the sieve. It may therefore only serve to separate the fine fraction of the ground material and thus to increase the capacity of the mill or to relieve it of the continuation of this fine fraction.
  • a further development according to claim 3 is of particular advantage.
  • Such a viewing device can consist, for example, of a rotary screen or a rotary screen driven by the rotor for an oscillating movement, but the connection can also be designed differently.
  • the classifying device preferably consists of a classifying wheel, in the middle of which a suction device for the finer regrind fraction is arranged, whereas the larger part is thrown out by the classifying wheel.
  • a beater mill 1 has a grinding chamber 3 surrounded by a housing 2.
  • a rotor shaft 4 is rotatably mounted on the housing 2 and can be driven by means of a drive wheel 5.
  • the rotor shaft 4 could be “floating” with the help of a single bearing 6, but it is advisable to arrange at least one second bearing 7 at the foot end or between two groups of striking tools.
  • Such striking tools 8 are mounted in a known manner on a pivot shaft 9, one of which is held by arms 10 each projecting from the rotor shaft 4 in a star shape.
  • Each star of arms 10 thus forms a group of striking tools 8, wherein a plurality of star arrangements of arms 10 held axially apart from one another by bushes 11 or 12 can be combined into a single group, as is the case with the top four arm stars 10 based on one group 110 in FIG. 1.
  • the material to be ground is fed to this group 110 of impact tools 8 via at least one feed opening 13.
  • This feed opening 13 is located slightly above the group 110 and is only intended to serve as an example of the arrangement of such an opening 13.
  • the feed opening then extends in a slot-like manner in the circumferential direction corresponding to the opening 13a.
  • the feed opening 13 is assigned a closing device in the form of a flap 15 which can be pivoted about a fulcrum 14 from the position shown in solid lines into the dashed position.
  • Training as a flap is particularly recommended where simple pipe cross-sections have to be closed, i.e. if there are circular or polygonal tube cross sections, so that the flap 15 is arranged at a location where the feed channel 16 has such a cross section, whereas the channel 16 in the region of the orifice opening 13 can easily be slit-shaped in the manner of the opening 13a .
  • a slide valve with a slide plate as the closure element can itself be provided in the region of the mouth openings.
  • the slide can be common to all openings 13 to 13c and itself have only a single passage opening. It is of course then expedient if the slide plate is adapted to the radius of curvature of the housing 2 and has a corresponding curvature. In the case of the arrangement of a plurality of feed openings over the circumference of the housing 2, it is of course also possible to arrange a single slide for at least several or all of the openings provided on this circumference in order to open or close them together.
  • feed openings 13d or 13e on the top of the housing 2 and, if appropriate, to arrange them distributed over the circumference of the housing 2.
  • feed openings 13d, 13e can of course also be assigned a closing device in such a way that the content of the ground material connected to them is fed to the central line 17 shown on the right in FIG after the flap position of the flap 15 or the flaps 15b, 15c assigned to the orifices 13b, 13c, to be fed to one of the orifice openings 13 or 13a-c.
  • flaps 15-15c are expediently actuated by solenoids, it being sufficient if one of the flaps lies in the inclined position shown by means of the flaps 15b, 15c in order to feed the regrind fed via the central line 17 to one of the orifices 13, 13b or 13c, whereas the mouth opening 13a is loaded when the flaps 15, 15b, 15c are aligned vertically. Accordingly, the circuit for the aforementioned solenoids, not shown, may be such that when the assigned switch is actuated, only one of the flaps 15, 15b, 15c moves into the inclined position.
  • the switch associated with the flap 15b must be connected to the solenoid for the flap 15c via a valve be, e.g. via a diode blocking in the opposite direction, in order to ensure that the flap 15c is moved together with the flap 15b, but not vice versa that the flap 15b is also moved when the switch for the flap 15c is actuated.
  • a valve be, e.g. via a diode blocking in the opposite direction, in order to ensure that the flap 15c is moved together with the flap 15b, but not vice versa that the flap 15b is also moved when the switch for the flap 15c is actuated. This also applies analogously to the flap 15.
  • the feed openings are above the associated group of striking tools is arranged, as shown by the openings 13 and 13b.
  • the feed opening 13b is assigned to a group 210 of striking tools 8 formed by a single arm star of the arms 10
  • the opening 13c is in turn assigned to a larger group 310.
  • the regrind is fed directly to the group 310 of striking tools 8 through the feed opening 13c, so that an intermediate distance between the groups 210 and 310 is avoided.
  • the upper row of striking tools 8 in the group 310 which lie opposite the mouth opening 13c, can hurl regrind particles against the incoming regrind, which may hamper the supply.
  • the mouth opening 13c practically extends in height over the first two rows of striking tools of group 310, so that part of the inflowing material is not processed at all by the top row of this group 310. This may cause an unevenness in the processing of the regrind. It is therefore preferred if the mouth opening corresponding to the mouth 13a is slit-shaped, because not only can this improve the feed, but also the feed between two rows of striking tools 8 is possible. Therefore, the height of the slot of the mouth opening 13a in the axial direction is preferably less than the distance between two adjacent rows of striking tools 8.
  • housing 2 is sieve-free, i.e. imperforate, trained.
  • such a design can be provided for the entire beating mill 1, the fineness of the end product being essentially dependent on the number of rows of beating tools passed through. As can be seen, this number can be predetermined by opening at least one feed opening 13, 13a, 13b or 13c for the regrind fed via the central channel 17.
  • the sieve 18 (as shown) only extends over part of the axial height of the impact machine 1, it is expedient to arrange the sieve against the end region (viewed in the transport direction of the ground material). Of course, it is also possible to keep more than two supply openings unlocked.
  • the sieve 18 is designed such that a regrind fraction of the desired fineness can be removed via the discharge channel 19 (by suctioning off via the channel 19), the still too coarse material collects accordingly in a funnel 20 at the lower end of the housing 2 , where it can be discharged, for example, with the aid of a screw 21 and can be fed again to the impact mill 1 via the respective feed opening.
  • the sieve 18 is designed in such a way that only the very finest fraction is removed via the discharge channel 19, whereas ground material with the respectively permitted grinding fineness also reaches the funnel 20, then a sifting, e.g. with the help of sieves.
  • the grain size distribution may be of less importance, so that there is no need for a screening process.
  • the simultaneous arrangement of a plurality of feed openings and a plurality of discharge openings or of at least one opening arranged in different positions relative to the rotor 22 seated on the shaft 4 can be of particular interest if the different striking tools are different Groups are designed differently and therefore have different effects.
  • the group 110 of striking tools 8 can thus be designed especially for the preliminary comminution, whereas the lower striking tools 8 are adapted accordingly to a finer grinding.
  • Different training of tools Gen is described below with reference to stator tools, which can be seen from Fig.1. Analogously, the striking tools 8 can have different designs.
  • stator tools are known per se, but is of particular interest in connection with the proposed design because the grinding fineness achieved depends very much on the number of rows of striking tools passed through and a “short circuit” between the respective feed opening 13 to 13c and the funnel 20 is to be prevented by material flowing along the housing wall.
  • relatively narrow rows of pin-shaped stator tools 23 can be provided, which, however, can optionally also be provided with tools 24 extending parallel to the axis of the rotor 22.
  • stator tools 25 with a triangular cross section are particularly expedient, which rest with one side 26 on the housing wall and have an oblique side 27 extending in the transport direction.
  • stator tool 25 extends in a ring around the circumference of the housing 2. At least this should be the case below or (viewed in the transport direction of the regrind) behind the respective feed openings.
  • stator tools 25 which extend over a predetermined angular range, are arranged one behind the other in the axial direction and possibly offset in the circumferential direction, the extent of the offset being less than that of their extension, so that - seen in the axial direction - overlapping regions of two adjacent ones Stator tools 25 result.
  • stator tools 25 it is also possible to make the stator tools 25 only approximately triangular in cross section, e.g. trapezoidal or the like.
  • the impact mill 1a according to FIG. 1 is constructed similarly to the impact mill 1, but has an intermediate bearing 7a and a hollow shaft 4a between two groups 410, 510 of impact tools 8, which is connected to a vacuum source (not shown), in particular a suction fan, through the air from the Grinding chamber 3a is drawn in the direction of arrow 29.
  • a vacuum source not shown
  • suction fan through the air from the Grinding chamber 3a is drawn in the direction of arrow 29.
  • the housing 2a which here consists of solid, unperforated walls, is provided at the level of the bearing 7a with a reinforcing ring 30 which transmits any radial forces which arise from the shaft 4a to an outer ring 31 and supports 32.
  • Spokes 33 extend from the reinforcement ring 30 and support the bearing housing of the bearing 7a, which is constructed in a conventional manner.
  • the bearing 7a has a cone 34 on its upper side, which ensures that any regrind particles falling thereon are discharged downwards.
  • This cone 34 of the bearing 7a can preferably also be used to cover suction openings 35 of the hollow shaft 4a.
  • a cell wheel 36 with a number voh of radial cell wheel walls 37 arranged between each suction opening 35 can be provided in the area of the suction openings 35 (the middle one in FIG. 1 is indicated by dash-dotted lines).
  • the diameter of this cellular wheel 36 is expediently dimensioned such that it can be accommodated within the cone 34 or within the diameter of the intermediate bearing 7a. This configuration is only preferred, but it may also be desirable to provide a cell wheel 36 projecting beyond the cone 34 or the bearing 7a.
  • an all-round roofing 38 can be provided below the bearing 7a.
  • a classifying wheel 39 is arranged below the cell wheel 36, which is fastened together with the cell wheel 36 on the hollow shaft 4a.
  • the regrind particles coming from the group 410 of impact tools 8 are on the one hand under the influence of gravity, and on the other hand under the influence of the suction effect exerted via the suction openings 35.
  • larger regrind particles M1 are therefore deflected less strongly from their essentially vertical path by the suction effect and at most possibly fall onto the classifying wheel 39, from where they are thrown radially outwards and are thus fed to the next group 510 of striking tools 8.
  • Fine regrind particles M2 are sucked into the area of the cell wheel 36. Should a larger regrind particle accidentally get into the area of the cellular wheel 36, it will be thrown radially outward by it.
  • the smaller regrind particles M2 have such a small mass that the centrifugal force given to them is in any case less than the suction effect acting on them, which is why the fine fraction M2 is sucked through the suction holes 35 into the interior of the hollow shaft 4a, from where it, e.g. is discharged via a rotary inlet (not shown).
  • the striking tools located below the group 410 of striking tools 8 are freed from or relieved of already finished particles.
  • a vibrating or rotating circular screen can also be arranged, the overflow of which group 510 from percussion tools gene 8 is supplied, whereas the fine material portion is discharged laterally from the housing 2a of the mill 1a, for example.
  • a screening is usually carried out after processing by a hammer mill, it can also be advantageous to provide such or a similar viewing device on the underside of the hammer mill, that is to say approximately below the bearing 7 in FIG. 1. Since the separating action of the viewing device shown can essentially be derived from the force ratio of suction action and centrifugal action, it may be expedient if the size of the suction power can be adjusted. This can be done by means known per se.
  • the magnitude of the centrifugal force depends on the speed of the wheels 36, 39, which cannot be easily changed in view of the grinding result to be achieved. It can therefore be advantageous if at least one of the wheels 36 and 39 can be driven independently of the shaft 4a, for example in that the classifying wheel 39 has a ring gear projecting through the wall of the housing 2a, via which it can be driven from the outside, whereby it is rotatably mounted on the shaft 4a. It would also be possible to interrupt the shaft 4a above the cellular wheel 36 and to provide a coaxial hollow shaft for driving the cellular wheel 36. In this case, however, the group 510 of bats would either have to be driven separately or be connected to the group 410 on its outer circumference bypassing the classifying wheel 39.
  • FIG. 1b Another embodiment of a beater mill 1b with a horizontal shaft 4b is shown on the basis of the figure.
  • special precautions are required to secure the regrind in the axial direction of the shaft 4b, especially since gravity is eliminated here for this purpose. Namely, while the regrind is introduced from above via a feed opening 13f, it is conveyed pneumatically by connecting a vacuum source sucking in the direction of the arrow 40 to a discharge opening 41 over the axial distance between the feed and discharge openings 13f and 41, respectively.
  • air supply openings 42 are provided in the housing 2b, through which openings parallel to the axis of the shaft 4b and transversely to the feed direction of the ground material from the supply opening 13f directed airflow can be generated.
  • the size of these air supply openings 42 is expediently adjustable by means of a rotary slide 43. The setting can be done by hand, but the rotary valve 43 may have a ring gear 44 on its outer circumference, into which a pinion 45 of a servomotor 46 engages.
  • the servomotor 46 is controlled by a control circuit 47, which are connected on the one hand to setpoint transmitters 48 and on the other hand to flow meters 49, which are only indicated schematically, and by means of which the ratio of the quantities of fractions of different fineness can be determined.
  • flow meters can be designed as weighing devices or as flow rate meters.
  • the strength of the air flow transporting the regrind particles can thus be adjusted and thus influence the dwell time for the regrind within the impact mill 1b. If the desired fineness of grinding is not achieved or if the coarse fraction of the grinding stock reaches an excess weight, the cross section of the openings 42 may be reduced with the aid of the slide 43 in order to reduce the transport speed for the grinding stock within the grinding chamber 3b. Since the impact mill 1b is sieve-free, a longer dwell time of the ground material within the grinding chamber 3b means a higher impact frequency per supplied ground material.
  • the selection of the number of groups of striking tools 8 that come into effect also forms a group here.
  • Each ring of striking tools arranged in one plane on striking arms 10 forms a group, the only one
  • the discharge opening 41 can be displaced parallel to the axis 4b and can thus be assigned to different impact tool groups.
  • the housing 2b has an elongated opening 50 on its underside, which is largely covered by a slide 51.
  • the slide 51 has only one opening receiving a hose 52, the mouth of the hose 52 simultaneously forming the discharge opening 41.
  • the discharge opening 41 is also preferably slit-shaped.
  • the slot 50 can be offset by individual discharge openings, which correspond to the cross section of the opening 41 and to which the hose 52 is to be aligned.
  • detents may be provided for certain positions of the hose 52 or the slide 51.
  • the slide 51 is provided with a drive which can only be brought digitally into predetermined discrete positions.
  • a follow-up control can be provided, for example, to which certain selector switches are assigned for each individual position.
  • FIGS. 1 to 4 can be interchanged or combined with one another.
  • several discharge openings 41 can be provided analogously to the different supply openings 13 to 13c in FIG. 1.
  • the various feed openings of FIG. 1 can be replaced by a single, displaceable feed opening analogous to the displaceable discharge opening 41 of FIG.
  • several of the feed openings 13-13e can also be opened or in operation at the same time. It has also already been mentioned that several feed openings can be distributed over the circumference of the housing, which of course also applies analogously to the discharge opening.
  • the slide 51 can be displaceable in the circumferential direction instead of in the axial direction of the housing 2, in particular if supply and discharge openings are provided in the circumferential direction.
  • flaps 15, 15b, 15c of FIG. 1 can be replaced by a slide, which may then be designed analogously to the slide 51, the only opening of which can be aligned with one of the feed openings 13 to 13c, whereby these feed openings are expediently to be of equal size to one another.
  • a viewing device for example by means of a rotary screen, drum screen or the like, can be provided between individual groups of clubs.
  • the striking tools may have different designs and, if desired, may also have axially extending extensions analogous to the pins 24 (FIG. 1). It has also already been mentioned that a combination of inlets (13-13c in FIG. 1) that can be released at different points can be provided with such outlets (41 in FIG. 3).
  • the closing device can also be provided with a hole, e.g. sieve-like, plates or the like. Be formed, which may be advantageous for air transportation.
  • a further variant can consist in that the slide 51, for example on its underside, is connected to a toothed rack, by means of which it can be adjusted by means of the pinion 45 of the servomotor 46 together with the connected circuit 47, 48, 49.
  • control via position sensors can be provided, as is known, for example, from elevators in buildings.
  • the precise positioning for the discharge opening 41 is less important than for a corresponding feed opening, because the risk of clogging by regrind particles ejected by the striking tools 8 is lower.
  • groups 410 and 510 of striking tools 8 can also be assigned an inlet or outlet opening or can be released in their area. Furthermore, the impact mill 1 can also be equipped with stator tools.
  • the discharge opening 41 which exposes a housing opening at various points, is of course preferably to be arranged in each case behind that group of striking tools 8 (seen in the transport direction of the ground material) which are just supposed to act on the ground material. If the grinding stock is also at least partially under the influence of gravity when the shaft 4 is arranged vertically according to FIG. 1, a slight aspiration or suction effect is usually applied to the opening 19 in the usual way, and possibly also to the lower part 20 of the Housing 2 are created, although for some applications, gravity alone may be sufficient. Furthermore, instead of the hose 52, any other flexible connection, e.g. a pipe joint to connect rigid pipes.
  • the mill 1 c is provided with a rotor 22, which is only indicated by dashed lines, the rotor shaft 4 of which can be driven by means of an AC motor 53 which can be switched over to two different speeds.
  • the material to be ground can be fed individually or together - depending on the circumstances - to the flow meters 49.
  • the individual components are weighed separately or mixed by at least one, possibly also several scales 49 and reach the feed apparatus of the mill 1 c.
  • the AC motor 53 which is designed as a three-phase motor, has a first group 55 of connections, which, for example, result in higher speed, and a second group of connections 56, which cause a slower speed of rotation of the motor 53. Accordingly, a switch package S1 and S2 are to be switched in opposite directions, ie when the switch package S1 is open, the switch package S2 is closed and vice versa. These switch packages S1, S2 are actuated with the help of magnets 57, 58 bar. An interrupter switch 59 is provided for switching off.
  • a program control device P which, for example, has an astable multivibrator 60, at the two outputs of which signals opposite to each other are connected to the two magnets 57, 58.
  • the time constants of this multivibrator 60 can be adjusted with the aid of an adjusting device 61 to adapt to different products or different grinding finenesses. In principle, this involves adjusting the resistances that determine the respective time constants, which can be changed, for example, with the aid of setting buttons 62.
  • resistors in the narrower sense of this word, rather they can be formed by any component that results in an adjustable resistance, for example field-effect transistors.
  • This latter design will be particularly advantageous if automatic control is to be achieved, with a control signal being supplied via a line 63 and 64, respectively.
  • a control signal being supplied via a line 63 and 64, respectively.
  • the corresponding output signals e.g. can be fed via a data bus 65 to a signal processing stage 66.
  • the two lines 63, 64 can be interrupted with the aid of switches S3, S4 and can thus be switched from automatic control to manual control.
  • program control device P can be designed in various ways, for example with the aid of time relays, which can optionally directly actuate the switch packs S1, S2.
  • time relays which can optionally directly actuate the switch packs S1, S2.
  • digital circuits with a counter as a timer digital circuits with a counter as a timer, mechanical program control devices with cams or contact disks, etc. are conceivable.
  • the motor 53 In operation of the mill 1c, the motor 53 is switched back and forth between its two speeds. It has already been mentioned that it is favorable for impact mills of the usual size to keep the number of switching operations as small as possible. It is particularly expedient if only a single switching operation needs to take place within a batch, so that switching frequencies of one switching operation occur per at least one minute, generally three minutes.
  • next batch is first processed at the lower speed for a period of time t2 ', whereupon the system then switches to the higher speed.
  • the corresponding fineness can be achieved in any of the ways shown in FIGS. 1 to 4, but possibly also by a combination of several of these measures.
  • the slide 51 can also have a plurality of such openings — distributed in the axial and / or circumferential direction — instead of a single opening 41.
  • the combinations of the described features are also possible, such as the combination of a plurality of supply or discharge openings with at least one displaceable.

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  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Pulverization Processes (AREA)
  • Electrophonic Musical Instruments (AREA)
  • Electronic Switches (AREA)
  • Saccharide Compounds (AREA)

Claims (15)

1. Moulin à battoirs comportant un bâti, qui constitue au minimum un compartiment de mouture, bâti dans lequel est logé un rotor muni de battoirs saillants, mobile autour de son axe, les battoirs étant subdivisés en différents groupes dans la direction axiale de l'arbre, cependant que le bâti comporte, respectivement, au minimum une ouverture pour l'amenée et l'enlèvement de la matière à moudre ou moulue, caractérisé par le fait que pour déterminer le degré de mouture, on prévoit des dispositifs de réglage (15, 15b, 15c; 41) pour le nombre de battoirs traitant chaque portion du produit et qu'à cet effet, on peut libérer à volonté l'orifice d'une au moins des ouvertures (13, 13e, 13f; 41) dans la zone de l'un ou l'autre des groupes (110-310) de battoirs (8) et/ou que plusieurs ouvertures d'amenée ou d'enlèvement (13-13e) sont prévues à différents emplacements du bâti (2) et/ou qu'un dispositif de commande à programme est prévu pour commuter un moteur à courant alternatif comportant au moins deux vitesses, cependant que l'on règle la durée de fonctionnement de l'une ou l'autre des vitesses à l'aide d'un dispositif de réglage.
2. Moulin à battoirs selon la revendication 1, caractérisé par le fait que l'on prévoit pour la libération à volonté d'un orifice d'ouverture (13-13c) au moins un dispositif d'obturation (15, 15b), 15c), par exemple une coulisse commune en particulier à plusieurs ouvertures, ou des volets.
3. Moulin à battoirs selon la revendication 1 ou 2, caractérisé par le fait que l'on relie au rotor (22) au minimum un dispositif de tamisage (35-39) comportant en particulier une roue de tamisage (38) et qu'on le place de préférence entre deux groupes (410,510) de battoirs (8).
4. Moulin à battoirs selon la revendication 1, 2 ou 3, caractérisé par le fait que plusieurs ouvertures (13, 13a-13e) sont réparties axialement sur le bâti (2) et que de préférence l'axe du rotor (4) est placé verticalement et qu'une ouverture d'amenée (13-13c) est adjointe à chaque groupe (110,210,310) de battoirs (8), tandis que le transport de la matière à moudre de l'un des groupes (110,210,310) de battoirs (8) à d'autres s'effectue partiellement au moins par gravité.
5. Moulin à battoirs selon l'une des revendications 1 à 4, caractérisé par le fait que l'ouverture d'amenée (13-13c) - vue dans la direction du transport de la matière à moudre - est placée chaque fois devant le groupe correspondant (110, 210, 310) de battoirs (8) et/ou l'ouverture d'enlèvement (41) est placée derrière.
6. Moulin à battoirs selon l'une des revendications 1 à 5, caractérisé par le fait que l'on place l'arbre du rotor (4b) horizontalement et que l'on adapte à l'ouverture d'enlèvement un dispositif d'aspiration pour le transport de la matière à moudre.
7. Moulin à battoirs selon l'une des revendications 1 à 6, caractérisé par le fait que l'on peut ad- joindre au bâti dans diverses positions, axiales par exemple, par rapport à celui-ci un dispositif de préférence flexible, à volonté d'amenée et/ou d'enlèvement (52), et qu'en particulier, le dispositif (52) d'amenée ou d'enlèvement est relié à une coulisse (51) pour le dégagement de la ou des ouvertures fermées du bâti.
8. Moulin à battoirs selon l'une des revendications 1 à 7, caractérisé par le fait que le bâti (2) porte, entre les battoirs (8) du rotor (22), des stators (23-25) qui, de forme sensiblement annulaire de préférence, du moins derrière l'ouverture d'amenée correspondante (13), s'avancent autour du périmètre intérieur du bâti (2) et qui, vus en coupe, sont en particulier, approximativement du moins, de forme triangulaire avec un côté (26) adjacent à la cloison du bâti et un côté oblique (27) l'intérieur dans la direction du transport de la matière à moudre.
9. Moulin à battoirs selon l'une des revendications 1 à 8, caractérisé par le fait que l'orifice d'une ouverture (13a) au moins est en forme de fente dans la direction du périmtètre du bâti (2), cependant que la hauteur de la fente est de préférence plus petite que la distance axiale entre deux rangées voisines de battoirs (8).
10. Moulin à battoirs selon l'une des revendications 1 à 9, caractérisé par le fait que plusieurs ouvertures (13, 13a-13e) sont réparties sur le périmètre du bâti (2).
11. Moulin à battoirs selon l'une des revendications 1 à 10, caractérisé par le fait que la matière moulue peut être enlevée directement du compartiment de mouture (3) par une ouverture d'envlèvement (20, 41) au moins, sans intercala- ge d'un tamis, que la majeure partie un tamis (18) uniquement dans la zone d'au moins une ouverture d'enlèvement (19).
12. Moulin à battoirs selon l'une des revendications 1 à 11, caractérisé par le fait que l'on a prévu plusieurs ouvertures non seulement d'amenée (13-13e), mais encore d'enlèvement (41).
13. Moulin à battoirs selon l'une des revendications 1 à 12, caractérisé par le fait qu'au moins une ouverture d'enlèvement (20) est reliée à au moins une ouverture d'amenée (13, 13a-e) pour le retour de la matière moulue, en particulier des éléments grossiers de celle-ci, dans le compartiment de mouture (3), tandis que l'on intercale de préférence un dispositif de tamisage (35-39).
14. Moulin à battoirs selon l'une des revendications 1 à 13, caractérisé par le fait qu'à l'entrée du moulin (1 b, 1 c), on prévoit un dispositif de mesure de quantité (49) d'apport de la matière à moudre dont le signal de sortie peut être transmis à un dispositif de réglage (42-47) au moins, par exemple à un dispositif de réglage d'intensité du courant d'air de transport et/ou un dispositif de réglage pour la vitesse (v) du moteur à courant alternatif (53).
15. Moulin à battoirs selon l'une des revendications 1 à 14, caractérisé par le fait que la durée de fonctionnement pour chaque vitesse s'élevé au minimum à 1 minute, à 3 minutes par exemple au moins, et que la sortie du moulin à battoirs (1 c) est raccordée à un mélangeur (67).
EP85108782A 1984-08-09 1985-07-13 Moulin à percussion Expired EP0173831B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85108782T ATE39065T1 (de) 1984-08-09 1985-07-13 Schlagmuehle.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3822/84 1984-08-09
CH382284 1984-08-09

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EP0173831A2 EP0173831A2 (fr) 1986-03-12
EP0173831A3 EP0173831A3 (en) 1986-10-01
EP0173831B1 true EP0173831B1 (fr) 1988-12-07

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EP85108782A Expired EP0173831B1 (fr) 1984-08-09 1985-07-13 Moulin à percussion

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JP (1) JPS6146265A (fr)
AT (1) ATE39065T1 (fr)
DE (1) DE3566618D1 (fr)
ES (1) ES9300009A1 (fr)

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Publication number Priority date Publication date Assignee Title
US5577675A (en) * 1995-01-25 1996-11-26 Mitsui Mining Co., Ltd. Agitating pulverizer
ITRE20040077A1 (it) * 2004-07-01 2004-10-01 Bonfiglioli Ing Spa "frantoio a martelli per la frantumazione di drupe, in particolare olive"
JP5058585B2 (ja) * 2006-12-25 2012-10-24 新日本海重工業株式会社 鎖打撃式破砕乾燥機
WO2021145010A1 (fr) * 2020-01-15 2021-07-22 日本国土開発株式会社 Dispositif de broyage rotatif
CN113275088A (zh) * 2020-10-16 2021-08-20 连云港如意情食用菌生物科技有限公司 金针菇种植原材料粉碎机
CN113713927B (zh) * 2021-09-11 2022-09-30 青岛大学附属医院 一种心血管内科用药物粉碎装置
CN116454258A (zh) * 2023-05-24 2023-07-18 福建省鑫森炭业股份有限公司 硅碳负极材料制备方法和应用

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DE1003546B (de) * 1954-12-17 1957-02-28 Erich Netzsch Schlaegermuehle fuer Fein- und Feinstvermahlung
GB1261709A (en) * 1968-07-17 1972-01-26 Nicholas Pora Two stage hammer mill
GB1518940A (en) * 1974-10-25 1978-07-26 Balfour & Co Ltd H Process and apparatus for the grinding of materials
DE2537880C3 (de) * 1974-12-06 1978-05-11 Vereinigte Oesterreichische Eisen- Und Stahlwerke - Alpine Montan Ag, Wien Vorrichtung zum Zerkleinern von Mahlgut

Also Published As

Publication number Publication date
EP0173831A2 (fr) 1986-03-12
ATE39065T1 (de) 1988-12-15
DE3566618D1 (en) 1989-01-12
JPS6146265A (ja) 1986-03-06
ES9300009A1 (es) 1993-04-16
EP0173831A3 (en) 1986-10-01

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