EP0978317B1 - Air-swept crushing machine with rotary impact rotor - Google Patents

Description

The invention relates to a gas-flow crushing machine with a rotating impact wheel system according to claim 1 and claim 8.

Such machines are mainly used for the processing of waste wood used, the waste wood is crushed until it is used as a starting material z. B. can be used in the chipboard industry. By the increasing amount of waste wood, but also due to the steadily growing demand the trend goes according to the secondary raw materials created during recycling in the woodworking industry, increasingly effective machines with use higher throughputs. Such an increase in However, machine performance cannot be achieved by a proportional one alone Achieve enlargement of the dimensions of known machines. That would find uncontrollable shredding processes take place in the shredding room Inhomogeneity and thus reduced quality of the shredded material.

A generic shredder is for example from the German patent specification 19 05 286 and German design specification 19 09 022 known. A beater mill with a rotating beater wheel system is disclosed there, in which the feed material is axially in by the air flow generated by the beater wheel the shredding room is sucked. There the air and material flow is on the cone-shaped central area of the bat wheel into one of the Deflected deflector-shaped annular disk-shaped channel that the Feed material feeds an annular, corrugated grinding track. In the grinding gap between the corrugations of the grinding track and the striking edges of the beater wheel the feed is crushed to the desired fineness. there the air and material flow on the grinding path towards the screen surfaces redirected, through which the shredded material is viewed and removed.

The shredding principle is based on a swirling of the feed material With the help of vortices generated on the inner surface of the grinding track, the Feed material due to repeated impacts on striking plates and corrugations is unlocked. Another shredding machine is known from FR 2 270 004 A. The striking plates of the FR 2 270 004 A are not almost, but about an axis rotatably attached.

Against this background, the invention is based on the task Efficiency of a shredding machine of the type mentioned above to increase.

According to the invention, this object is achieved by a comminution machine the features of claim 1 or claim 8 solved. Advantageous further training result from the subclaims.

The basic idea of the invention is to unlock the Material necessary vortex zone, when a club plate is passed on the shredding path arises through appropriate measures shape that a more intense swirling and thus an extremely effective Dissolution of the feed takes place. The feed is always checked passed through the shredding room, whereby a shredded material of constant size and high quality. In addition, the measures according to the invention for no increase in energy consumption, but only convert the energy inherent in the racket wheel into more Shredding capacity around.

According to claim 1 this is achieved by a fixed arrangement of a variety of Punch plate pairs, consisting of two at a short distance opposite striking plates. This creates an alternating sequence the impact plates on the shredding path with a short distance as a result the short distance between a pair of striking plates and a larger distance due to the greater distance between the striking plate pairs.

In the space between two striking plates of a pair of striking plates an energetic vortex zone, in the air vortex at high speed and small diameter are generated. In this zone a large part of the Shredding work instead. In the area between two Punch plate pairs are due to the increased space relaxation of the vortex zone, in the air vortex of larger diameter and are observed at a lower speed. One finds in this zone Loosening of the previously shredded feed takes place, which is already sufficient fine particles with the air flow deflected on the shredding path be swept away by the principle of wind sifting.

According to an advantageous embodiment, at least that is in the direction of rotation broken rear longitudinal edge of a striking plate. This will form Whirling favors and the shredding performance further increased.

According to a particularly advantageous embodiment, the gap between the Striking plates of a pair of striking plates limited in depth. This can e.g. B. by appropriate mounting of the striking plates on the carrier plate, so that a U-shaped channel is formed by the support plate and impact plates. The the resulting spatially defined conditions largely determine uniform flow conditions with the consequence of a constantly high Efficiency.

Another way to take advantage of the flow conditions in the vortex zone to influence happens by keeping different distances between the striking plates of a pair of striking plates and the comminution path. So carries an increase in the distance between the in the direction of rotation rear impact plate and the effective area compared to the distance of the front Striking plate and the active surface for a faster exit from the spinal zone between the striking plates. In reverse order, the Residence time of the comminuted material in this zone can be increased.

The arrangement according to the invention of two striking plates proves to be Forming a pair of striking plates as extremely advantageous, since the position of the individual impact plates in the radial direction independently of each other only by Loosen the fastening screws and move them radially Can be adjusted. This is simple and, above all, quick and way given a possibility depending on the crushing process optimize the size of the material to be shredded by the geometric conditions be changed in a targeted manner in order to control the material flow and vortex formation.

By doubling the number of striking plates on the racket wheel, the Wear on each individual striking plate is less, as the wear and tear overall distributed over a larger number of striking plates. In this way higher machine running times and longer impact plate service lives are achieved.

Regardless of the arrangement of a large number of striking plate pairs on Beater wheel can the vortex zone according to claim 8 by the arrangement concentric washers on the beater wheel influenced in a suitable manner become. One or more of these washers can be removed from the carrier washer or carrier ring disc in the direction of the free ends of the striking plates on Racket wheel can be arranged, whereby between the discs or Washer chambers are formed, which are open in the radial direction. Under The air and material flow passes through these washers on its way through the comminution chamber, with air swirls in the individual chambers are generated. These vortices are from the behind the Striking plates generated vortices superimposed, their axis of rotation by 90 ° is offset. This creates extremely complex flow conditions of which the feed material is carried along and against the shredding path or Ring discs is thrown, so that the feed to an extreme effective way is unlocked.

By arranging several washers next to each other, this area becomes divided into a plurality of chambers, which are gradually fed by the feed material be hiked through. As a result of the shredding work in the individual chambers the feed material becomes ever finer towards the striking plate ends. On this ensures that the feed is always controlled by the Area of shredding and also with shredding machines very large dimensions, especially great depth, is prevented from large particles get into the comminuted material and its inhomogeneity and thus lead to a reduction in quality. This is mostly at Shredding machines with a wide shredding path without wire mesh from Significance in which the shredded material is removed without sighting.

According to an advantageous embodiment, the distance between each washer to the shredding path and the distance between the washers adjustable. As a result, the swirl chamber can be tailored to the type of feed, the requirements for maintaining a constant material flow and the desired degree of fineness can be adjusted.

The highest efficiency of a shredding machine according to the invention can be achieved by arranging a large number of striking plates at the same time according to claim 1 and coaxial washers on the beater wheel according to Claim 8, because thereby the racket wheel accomplished Shredding performance is greatest. Thus, the combination results of the different embodiments according to claims 1 to 7 and the claims 8 to 14 a variety of possible configurations of the Invention, all of which are the subject of the present invention.

The invention is illustrated below with reference to one in the drawing Embodiment explained in more detail.

Fig. 1

eine schematische Schnittdarstellung einer Doppelstrommühle,

Fig. 2

einen Schnitt durch den äußeren Bereich des Schlägerrades entlang der in Fig. 3 dargestellten Linie II-II,

Fig. 3

einen Vertikalschnitt durch die oberen Hälfte einer erfindungsgemäßen Doppelstrommühle und

Fig. 4

eine Draufsicht auf eine Schlagplattenhälfte in großem Maßstab mit Darstellung der Strömungsverhältnisse.

Show it

Fig. 1

2 shows a schematic sectional illustration of a double-stream mill,

Fig. 2

3 shows a section through the outer region of the beater wheel along the line II-II shown in FIG. 3,

Fig. 3

a vertical section through the upper half of a double stream mill according to the invention and

Fig. 4

a plan view of a striking plate half on a large scale with representation of the flow conditions.

1 shows a double-stream mill 1 according to the invention in a greatly simplified manner Presentation. The double current mill 1 has a housing 2, the one drum-shaped crushing room 3 encloses. The front of the Housing 2 has a central, circular opening, which by means of a pivotable housing cover 4 is closable. The housing cover 4 has a central inlet opening 5, which is used to feed the double stream mill 1 serves. For this purpose, a is on the housing cover 4 above the inlet opening 5 Feeding shaft 6 attached, in the manner of a heavy goods separator is trained. To control the air and material flow, the Loading chute 6 in its interior pivotable guide surfaces 7.

The beater wheel 8 is free in the interior of the drum-shaped comminution space 3 rotatably arranged. The beater wheel 8 is of a horizontal, the Inlet opening 5 opposite drive shaft 9, which at the rear of the Housing 2 is mounted in the bearings 10, driven. To connect the Double current mill 1 to an external engine carries the outside of the Housing 2 lying end of the drive shaft 9, a multi-pulley 11. Das other end of the drive shaft 9 carries the actual bat wheel 8. Das Bat wheel 8 consists of a cylindrical seat 12 which on the Drive shaft 9 is plugged in and non-positively connected to it. The cylindrical seat 12 is surrounded by a coaxial support plate 13, the opposite a likewise coaxial carrier washer 14 in a predetermined Distance is arranged so that between the support plate 13 and Ring carrier disk 14, an annular disk-shaped channel 26 is formed. The inner one The circumference of the carrier ring disk 14 closes with a small gap Housing cover 4, which for this purpose with the formation of a conical Widening 15 is guided into the interior of the crushing room 3. On the outside The circumference of the carrier disk 13 and the carrier ring disk 14 are a large number parallel carrier plates 16 attached in a ring shape, on the front and Back of the striking plates 17 are attached.

The central region of the carrier disk 13 has a deflection device 18 in Form of a hollow truncated cone, on the widening in the direction of entry Conical surface one for the division of the air and material flow parallel and coaxial arranged to the support plate 13 arranged washer 19.

The beater wheel 10 is at a radial distance from a cylindrical active surface 20 surround so that an annular gap 21 between beater wheel 10 and active surface 20 (Fig. 2) arises. The active surface 20 is in its central region as a grinding track 22 trained, for which the surface is covered with impact and corrugated elements. Which regions of the active surface 20 adjoining on both sides of the grinding track 22 consist of annular sieve tracks 23 and 24 with radial sieve passages, via which the regrind is finally arranged in the bottom of the housing Exhaust opening 25 arrives.

The air and material flow is shown symbolically in FIG. 1 by arrows. The Feed material first enters the feed chute 6 from above and is by the air flow generated by the beater wheel 8 through the inlet opening 5 in sucked the inside of the shredding room 3. The air and Material flow deflected by more than 90 ° with the aid of the guide surfaces 7, Impurities in the feed, such as B. nails, screws, etc., due to their high dead weight and its resulting inertia over the below open feed chute 6.

At the deflection device 18 and the distribution disk 19, the axial one experiences directed air and material flow a deflection in the radial direction, whereby he through that formed by the carrier disc 13 and carrier ring disc 14 annular disk-shaped channel 26 reaches the active surface 20 and there at Impact on the grinding track 22 and the striking plates 17 is unlocked. The Grinding track 22 also causes a further division of the air and material flow to the laterally adjoining screen tracks 23 and 24 through which the Airflow with the sufficiently fine material occurs and the double flow mill 1 leaves again via the outlet opening 25.

2 shows a radial section through the outer region of the Beater wheel 8 and the grinding track 22. The grinding track 22 encloses this Beater wheel 8 concentric. The inner surface of the grinding track 22 is of axial Corrugations 27 formed, in the present example by semicircular Wells 28 are separated, otherwise different, the desired Fineness can be designed accordingly. In the recesses 28 in the course of shredding, the feed material gradually arrives with an axial Direction of movement out of the area of the grinding track 22 and into the area the sieve tracks 23 and 24 into it.

In compliance with the annular gap 21, the bat wheel 8 strokes with his outer circumference of the support plate 13 evenly distributed in pairs Striking plates 17a, 17b along the inner surface of the grinding track 22. to Attachment of the striking plates 17a, 17b serve the carrier plates 16, which Rigidly connect the carrier ring disk 14 to the carrier disk 13 and to the latter A striking plate 17a, 17b is fixed on the front and back. Here are the longitudinal edges of the striking plates 17a, 17b opposite the grinding track 22 over the corresponding longitudinal edge of the carrier plate 16, so that a to Grinding track 22 open, U-shaped channel is formed. To attach the Striking plates 17a and 17b on the carrier plate 16 cannot, for example Serve screws shown, which are through radially aligned elongated holes in the Striking plates 17a and 17b are sufficient. This enables an adjustment of the Striking plates 17a and 17b in the radial direction.

If the beater wheel 8 rotates counterclockwise in the direction of the arrow, is generated by the striking plates 17a, 17b, an air flow that the entire Flushes through the crushing chamber 3 and thereby carries the feed material with it. in the Air layers are also observed near the surface of the grinding track 22 low speed at which, due to the rotating striking plates 17a, 17b air is passed at high speed. In the annular gap 21 compresses the air between the impact plates 17a, 17b and the grinding track 22, before it can expand again behind the striking plate 17a, 17b. Thereby there is a pronounced vortex zone behind the individual Striking plates 17a, 17b. The resulting vortices have a Drive shaft parallel axis of rotation and are in Fig. 2 with the ring arrows 29a, 29b marked.

Through the U-shaped space behind the first striking plate 17a the vortices 29a do not expand freely to dissipate energy, but point inevitably a small diameter and high circulation speeds on. In this first high-energy vortex zone, a large part of the Shredding work instead.

There is no spatial limitation behind the second striking plate 17b, so that here adjust vortex 27b with a larger diameter, which is particularly good for Loosen up the shredded feed material.

Fig. 3 shows a further possibility to vortex formation in the comminution room Taxes. Only the upper part of a double-stream mill 1 is shown, the same reference numerals for the same features as in FIG. 1 have been used.

Here, too, one can see freely within a housing 2 about an axis 30 rotatable beater wheel 8, consisting of a coaxial carrier disc 13 and Carrier washer 14 and carrier plates 16 and impact plates attached thereto 17. The beater wheel 8 is at a radial distance from an active surface 20 in shape a grinding track 22 with screen tracks 23 and 24 adjoining on both sides enclosed. Between the housing 2 and the active surface 20 is an annular Channel 31 formed, which is divided by two annular walls 32 and 33. In the channel 31 is the shredded and shredded material of the sieves 23 and 24 Outlet opening 25 in the bottom area of the double stream mill 1 is fed.

Concentric to the carrier disc 13 and ring carrier disc 14 are to the free Ends of the striking plates 17 and carrier plates 16 towards further annular disks 34, 35, 36 and 37 arranged in this way with the striking plates 17 in form open chambers in the radial direction. The distance between the washers 34 and 35 or 36 and 37 to one another and to the carrier disk 13 or Carrier washer 14 and towards the active surface 20 depends on the Properties of the feed material, the desired fineness of the shredded material and freely adjustable to control the material flow.

The operation of a double-stream mill 1 according to the invention setting flow conditions are shown in Fig. 4 on a large scale. The arrow 38 symbolizes how the air and material flow in that formed by the carrier disk 13 and carrier ring disk 14 (FIG. 3) annular disk-shaped channel 26 in the radial direction between the striking plates 17 passes through on the grinding track 22, where it in on both sides in Direction of the screen tracks 23 and 24 is deflected.

He first underlines the outer circumference of the carrier disk 13 and generates in the first chamber 39 a swirl zone indicated by arrows, the The axis of rotation extends tangentially to the direction of rotation of the beater wheel 8. The the same process is repeated in the chambers 40 and with the Chamber 41 formed chamber 41, where further vortex zones arise.

By superimposing these vortex zones with those described in Fig. 2 Vortex zones, whose axes of rotation are offset by 90 °, arise extremely complex flow conditions leading to an intense and powerful Swirl the feed material. The result is quick and effective shredding of the feed material in a narrow fluctuation range in terms of fineness.

Claims (15)

1. An air-swept size reduction machine, especially suitable for the processing of materials containing cellulose as e.g. wood flakes, comprising a rotating impeller system, particularly beater mills, having impact plates (17) arranged like a ring on the outer periphery of the impeller (8) and parallel to its axis, said impact plats (17) generating whirling zones in predetermined radial spacing when passing along a cylindrically shaped effective surface (20) encircling coaxially the impeller (8), wherein each impact plate (17a) is followed at a small tangential distance by a second impact plate (17b), both plates forming a pair.
2. An air-swept size reduction machine according to claim 1, characterized in such a manner that the spacing between both impact plates (17 a, 17b) ranges from 0.5 to 3.0 cm, preferably being 1.5 cm.
3. An air-swept size reduction machine according to claim 1 or 2, characterized in such a manner that the spacing between both impact plates (17a, 17b) corresponds to the thickness of the supporting plate (16) supporting the impact plates (17a, 17b).
4. An air-swept size reduction machine according to claim 3, characterized in such a manner that the supporting plate (16) and the impact plates (17a, 17b) form an open, u-shaped channel in front of the effective surface (20).
5. An air-swept size reduction machine according to one of the claims 1 to 4, characterized in such a manner that the spacing between the impact plates (17a, 17b) fixed on the supporting plate (16) and the effective surface (20) is different for both impact plates.
6. An air-swept size reduction machine according to claim 5, characterized in such a manner that the spacing of the impact plate (17a) being in front referring to the direction of rotation is smaller than the spacing of the following impact plate (17b).
7. An air-swept size reduction machine according to one of the claims 1 to 6, characterized in such a manner that the impact edges of the impact plates (17a, 17b) facing the effective surface (20), especially the rear edge in the direction of rotation, are broken.
8. An air-swept size reduction machine, especially suitable for the processing of materials containing cellulose as e.g. wood flakes, comprising a rotating impeller system, particularly in beater mills, the impeller (8) consisting of a shaft (9) carrying a coaxial supporting disc (13) fixed onto it and of an axially spaced facing coaxial supporting ring disc (14) connected together via the impact plates (17), the impeller (8) being concentrically encircled at a radial spacing by a cylindrically shaped effective surface (20) in which the zone of the outer periphery of the supporting disc (13) and supporting ring disc (14) further concentric ring discs (34, 35, 36, 37) are arranged with a predetermined axial spacing to the impeller (8).
9. An air-swept size reduction machine according to claim 8, characterized in such a manner that the spacing between the concentric ring discs (34, 35, 36, 37) ranges from 2,5 to 15,0 cm, being preferably 5,0 cm.
10. An air-swept size reduction machine according to claim 8 or 9, characterized in such a manner that the spacing of the concentric ring discs (34, 35, 36, 37) increases in direction of the free end of the impact plates (17).
11. An air-swept size reduction machine according to one of the claims 8 to 10, characterized in such a manner that the spacing between the ring discs (34, 35, 36, 37) and the effective surface (20) ranges from 1,5 to 8,0 cm, being preferably 4,0 cm.
12. An air-swept size reduction machine according to one of the claims 8 to 11, characterized in such a manner that the spacing between the individual ring discs (34, 35, 36, 37) and the effective surface (20) differs.
13. An air-swept size reduction machine according to claim 12, characterized in such a manner that the spacing between the outer ring discs (34, 37) and the effective surface (20) is larger than the spacing between the inner ring discs (35, 36) and the effective surface (20).
14. An air-swept size reduction machine according to one of the claims 8 to 13, characterized in such a manner that the ring width of the ring discs (34, 35, 36, 37) ranges from 5,0 to 12,5 cm, being preferably 10,0 cm.
15. An air-swept size reduction machine, especially suitable for the processing of material containing cellulose as e.g. wood flakes, comprising a rotating impeller system, particularly in beater mills, the impeller (8) consisting of a shaft (9) carrying a coaxial supporting disc (13) fixed onto it and of an axially spaced opposite supporting ring disc (14), the supporting disc (13) and the supporting ring disc (14) being connected tightly together by the impact plates (17) distributed on their outer periphery and oriented axially, said impact plates (17) passing at a radial spacing along a cylindrical effective surface (20) encircling the impeller (8) coaxially, characterized in such a manner that next to each impact plate (17a) a second impact plate (17b) is arranged at a small tangential distance thereof to form a pair, thus creating an alternating sequence of impact plates with small spacing between each other and a large spacing to the impact plates facing them and that in the zone of the outer periphery of the supporting disc (13) and supporting ring disc (14) further concentric ring discs (34, 35, 36, 37) are arranged with an axial spacing to the impeller (8).

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