WO1984001125A1 - Extrudeuse - Google Patents

Extrudeuse Download PDF

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Publication number
WO1984001125A1
WO1984001125A1 PCT/AT1983/000024 AT8300024W WO8401125A1 WO 1984001125 A1 WO1984001125 A1 WO 1984001125A1 AT 8300024 W AT8300024 W AT 8300024W WO 8401125 A1 WO8401125 A1 WO 8401125A1
Authority
WO
WIPO (PCT)
Prior art keywords
screw
press according
screw press
strand
roller
Prior art date
Application number
PCT/AT1983/000024
Other languages
German (de)
English (en)
Inventor
Raimund Falkner
Original Assignee
Pfeifer Oskar
Raimund Falkner
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
Priority claimed from AT346182A external-priority patent/AT381472B/de
Priority claimed from AT45583A external-priority patent/ATA45583A/de
Application filed by Pfeifer Oskar, Raimund Falkner filed Critical Pfeifer Oskar
Priority to DE8383902419T priority Critical patent/DE3376102D1/de
Priority to DE19838337835U priority patent/DE8337835U1/de
Priority to AU18241/83A priority patent/AU1824183A/en
Priority to DE19838390031U priority patent/DE8390031U1/de
Priority to IT67958/83A priority patent/IT1193148B/it
Publication of WO1984001125A1 publication Critical patent/WO1984001125A1/fr
Priority to DE8484890144T priority patent/DE3474416D1/de
Priority to EP84890144A priority patent/EP0140869B1/fr
Priority to AT84890144T priority patent/ATE37671T1/de

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B9/00—Presses specially adapted for particular purposes
    • B30B9/02—Presses specially adapted for particular purposes for squeezing-out liquid from liquid-containing material, e.g. juice from fruits, oil from oil-containing material
    • B30B9/12—Presses specially adapted for particular purposes for squeezing-out liquid from liquid-containing material, e.g. juice from fruits, oil from oil-containing material using pressing worms or screws co-operating with a permeable casing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B11/00—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses
    • B30B11/22—Extrusion presses; Dies therefor
    • B30B11/224—Extrusion chambers
    • B30B11/225—Extrusion chambers with adjustable outlet opening
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B11/00—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses
    • B30B11/22—Extrusion presses; Dies therefor
    • B30B11/227—Means for dividing the extruded material into briquets
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B9/00—Presses specially adapted for particular purposes
    • B30B9/02—Presses specially adapted for particular purposes for squeezing-out liquid from liquid-containing material, e.g. juice from fruits, oil from oil-containing material
    • B30B9/12—Presses specially adapted for particular purposes for squeezing-out liquid from liquid-containing material, e.g. juice from fruits, oil from oil-containing material using pressing worms or screws co-operating with a permeable casing
    • B30B9/122—Means preventing the material from turning with the screw or returning towards the feed hopper
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B9/00—Presses specially adapted for particular purposes
    • B30B9/02—Presses specially adapted for particular purposes for squeezing-out liquid from liquid-containing material, e.g. juice from fruits, oil from oil-containing material
    • B30B9/12—Presses specially adapted for particular purposes for squeezing-out liquid from liquid-containing material, e.g. juice from fruits, oil from oil-containing material using pressing worms or screws co-operating with a permeable casing
    • B30B9/18—Presses specially adapted for particular purposes for squeezing-out liquid from liquid-containing material, e.g. juice from fruits, oil from oil-containing material using pressing worms or screws co-operating with a permeable casing with means for adjusting the outlet for the solid

Definitions

  • the invention relates to a screw press according to the preamble of patent claim 1.
  • Such a screw press is described for example in DE-A-2736810.
  • the guide element is a longitudinal guide for the material to be pressed within the screw flights, that is, an effective in the circumferential direction is achieved that only allows axial movement of the material.
  • Separate sieve-like outlet openings are provided for cooling the pressed-out liquid, which cannot be kept free.
  • the screen openings inevitably become blocked, which means that the entire press has to be dismantled and cleaned.
  • this disadvantage occurs when processing combustible waste of any composition, such as industrial waste, domestic waste, sawdust, Rixid pieces, waste paper, etc., which have a different liquid content, different particle size and different pressing properties.
  • thermoplastic waste becomes viscous to thin, so that even in small proportions they quickly move the liquid outlet openings.
  • the trapped liquid causes differences in the strength of the resulting strand, so that the strand may disintegrate even after further compression.
  • a high moisture content naturally also reduces the calorific value or the burning properties of the product if it is to be used as a fuel.
  • the strength of the resulting strand is dependent on other factors, such as an adapting post-compression and a correspondingly metered feed, which are not dealt with in the known screw press.
  • the invention has now set itself the task of designing a screw press of the type mentioned in such a way that not only a constant leakage of liquid can take place and continuous strand formation with the same strength as possible is achieved, so that the best possible coordination between loading, pressing and post-compression given is.
  • the essential problem of liquid leakage is now solved in that each guide element is inserted to an extent for the pressed-out liquid, which represents the longitudinal slot in the wall of the screw tube, the teeth of the guide element moving in the longitudinal slot forming cleaning elements for keeping the outlet free.
  • the longitudinal slot Due to the arrangement of the longitudinal slot according to the invention, through which the guide element engages with the teeth in the screw and is therefore kept in motion when the screw rotates, the longitudinal slot is constantly cleaned, so that the squeezed-out liquid can escape through the longitudinal slot of the screw tube wall at any time can.
  • An additional outlet for the squeezed-out liquid can be created by connecting an extension part to the screw tube beyond the mouthpiece, which is formed by at least two radially expandable wall parts which are separated from one another by longitudinal slots.
  • the extension part also ensures the closing of each longitudinal groove formed by a guide element in the strand during the recompression, in particular if, in a preferred embodiment, it is provided that the guide element extends into the mouthpiece over the last screw flight.
  • extension part is spring-loaded counter to the pressing direction and to be displaceable along outer guide parts, the expandable wall parts being articulated in a radially movable manner on a slide which can be displaced on the mouthpiece.
  • Fixed rolling bearings are preferably provided as guide parts, on which flat guide surfaces of the displaceable extension part roll.
  • the screw press provides a device for canceling the counterpressure if the outlet length of the strand is equal to the length of the strand piece to be cut corresponds to a cutting device which can be used after the counterpressure has been lifted substantially perpendicularly to the strand, and has a return guide device for the printing surface in the starting position.
  • the pitch of the screw flights is increased, an edge of the hopper near the screw being designed to be shear or Sri Lina-oriented.
  • the shear or cutting element ensures that the screw is only fed well in a compressible size.
  • the filling funnel is designed as the housing of a comminution device, in which a pair rotates in opposite directions Rolls of several interlocking and equipped with fangs discs is arranged, a grid or the like below the crushing rollers. is provided, the total passage area can be adjusted by at least one movable cover dan absorption capacity of the screw. The cover allows the passage for the shredded material to the extent required, so that overdosing is avoided. The excess material remains in the hopper and is conveyed upwards again by the slowly rotating shredding rollers, where it is returned to the material to be shredded. It then gradually falls down through the grille openings.
  • the grid has in particular a longitudinally symmetrical curved shape adapted to the rolls.
  • two covers are arranged so as to be symmetrically displaceable parallel to the grid, the
  • Release of the total passage cross section is preferably controlled by the movement of the slide of the expandable wall parts of the extension part. The latter enables automatic metering of the material feed into the screw.
  • the term "lattice” is understood to mean all components which have passages which can be used for screening purposes.
  • the grille can be formed by a perforated plate, the covers also representing perforated plates.
  • each hole of the grille is covered by a material area of a cover in this embodiment. If the cover is moved, the holes in the cover increasingly slide over all holes in the grille at the same time until they are aligned with one another, thus achieving the largest passage area.
  • the displacement of the covers is only slightly above the hole diameter.
  • the grating consists of rods extending in one direction, and metal sheets are provided as covers which have teeth which extend along their contact edges over a plurality of rods interlock in the closed position.
  • the grid is formed by a bar grate. If the covers are pulled apart, the gaps between the middle bars open first, and then only between the edge bars, since the direction of displacement of the covers extends perpendicular to the bars of the grid. With a displacement direction in the longitudinal extension of the bars, which is also possible, there is a longer displacement path since the filling funnel preferably has a rectangular outlet opening. It will depend above all on the design of the coupling of the displacement movements of the covers and the extension part, which displacement length of the covers appears to be the most favorable in the respective embodiment.
  • the Kihrungselement for axial guidance of the strand is formed by a toothed disk driven by the worm, the teeth of which cause the cleaning of the most important liquid outlet as described, in a further embodiment it is provided in order to achieve the greatest possible axial engagement length that the toothed Disc with at least two successive teeth at the same time engages snugly in the worm, which tapers concavely in the area of engagement corresponding to the starting line of the disc.
  • the screw preferably ends at the level of the axis of the disk, so that it protrudes by half its diameter beyond the front screw end into the mouthpiece and also forms an axial guide in this area.
  • the guide element is formed by at least one bar equipped with teeth and loaded towards the screw axis, which is arranged to be radially movable in the plane of the longitudinal slot, preferably the length of each tooth being at most corresponds to half the distance between the assigned pair of worm threads.
  • the teeth of the guide element that is to say the disk
  • the evasive movement also has a large, sometimes even exclusively axial Has component
  • the radial component of the evasive movement is at least predominant in a strip as a guide element.
  • the worm threads approaching the teeth displace them radially to the outside when touching the worm axis, whereby of course also keeping the longitudinal slot free for the
  • Liquid leakage remains. After passing through each worm gear below the dodged tooth of the bar, it is pushed back towards the worm axis, whereby various options are available for this loading.
  • the application of pressure springs is conceivable.
  • these would have to be of relatively large dimensions in order to be able to penetrate the space between two screw flights, which has at least partially been filled in the meantime, positive guidance is advantageous.
  • this can be achieved by the worm itself, in that at least one pair of strips equipped with teeth are arranged in diametrically opposite longitudinal slots and are coupled in a radially movable manner in the same direction. Coupling the two strips of each pair results in their positive guidance. If one ledge is pushed outwards by the worm threads, the teeth of the other ledge inevitably penetrate between two worm threads on the opposite side, which are offset by exactly half the pitch.
  • the pair of strips can be connected on at least one side by a ring which surrounds the screw tube at a distance and is preferably guided in a displaceable manner.
  • a ring can of course the strips on both. Connect the sides with each other, the depth of the screw flight being the same across the entire length of the screw.
  • each bar can also be achieved by an eccentrically rotating driven element, the speeds of the eccentric element and the screw being the same.
  • the eccentric element can be formed on a support ring which is connected to the worm via a reinforced section of the worm thread forming a spoke.
  • the support ring protrudes on all sides from the screw tube, which is thus divided into two parts, the inner surface of the support ring being flush with the inner surface of the screw tube, so that the annular gap interrupted by the spoke does not cause any significant change in the conveying cross section.
  • the guide element extends into the mouthpiece over the last screw flight, so that the axially parallel guidance of the strand that is formed, which is effective as long as possible and above all also in the mouthpiece area, is achieved.
  • the end section of the screw with a constant pitch which tapered evenly towards the mouthpiece for the progressive compression of the material, also makes it possible to link each bar equipped with the teeth on one side to the screw tube and to move it radially on the other side, with the bar joint moving axially the tapered end portion of the screw is offset to the outside.
  • all teeth of the groin can penetrate equally deep between the worm threads, since in the immediate area of the groin joint, in which the swivel path would not be sufficient to allow passage of a worm gear, the radial distance from the worm is greater if the groin joint is provided on the funnel side or at an axial distance from the preferably tapered screw end if the inguinal joint is provided on the mouthpiece side.
  • the expandable wall parts of the connecting part can be formed, for example, by flat strips which complement one another to form the corresponding polygon if a prismatic strand is to be achieved. So the extension part between four and eight such Stripes included. However, it is also conceivable to use curved wall parts, for example quarter disks or, in particular, half disks for the extension part, so that there is a continuation of the cylindrical screw tube.
  • the guide surfaces along which the extension part can be displaced diverge in the pressing direction.
  • the convergence of the guide surfaces to the mouthpiece or their divergence in the pressing direction allows its radial expansion and thus a cancellation or at least reduction of the friction when the extension part is displaced, whereupon the compressed spring brings about a return movement of the displaceable extension part.
  • the guide surfaces converging towards the mouthpiece reduce the cross section of the extension part, as a result of which the frictional forces increase again and the
  • the compression spring in particular a helical spring, is preferably adjustable, so that the starting position, which defines the minimum cross section of the displaceable section, can then be adapted to the material to be processed, such as industrial waste, household waste, sawdust, pieces of bark, waste paper etc. or its necessary degree of compaction.
  • the extrusion pressure of the extrusion press can be kept smaller thanks to the reduction in extrusion friction when the spring pressure is exceeded, since it does not reach the maximum
  • the extrusion press can thus be lighter and therefore more economical.
  • the guide surfaces are advantageously formed in two spaced-apart rings on the displaceable section, the divergence of the guide surfaces on the outlet opening side being greater than that of the worm tube side.
  • Rolling bearings or rollers are preferably provided as fixed guide parts, on which the guide surfaces roll during the longitudinal displacement.
  • each guide surface can be delimited in the longitudinal direction by projections on both sides.
  • the screw tube side serve as end stops in the pressing direction if the spring travel of the compression spring is greater than the displacement length.
  • the projections on the outlet opening side represent a flange on which the compression spring, preferably a pressure plate and radial roller bearings, is supported.
  • a second embodiment for post-compression which uses the pressure face mentioned above, provides that it is formed on a piston which is acted upon by the pick-up device counter to the feed direction, the return device being designed, for example, as a compression spring which surrounds the piston rod and engages with one another adjustable abutment of the device frame supports.
  • the piston can also be acted upon by a compressible pressure medium, for example air.
  • the expandable wall parts are locked during the pressing feed of the emerging strand and opened during the ejection of the strand piece.
  • the aforementioned design of the wall parts as quarter shells is favorable, two of which are stationary in the extension of the mouthpiece and are separated by a longitudinal slot, and the two second quarter shells are each articulated to a first quarter shell.
  • the Er is in the longitudinal slot between the two quarter shells invention arranged an ejection plate to cause the ejection of the strand piece when the second quarter shells are open.
  • a cutting plate is provided as a cutting device on the mouthpiece side of the ejection plate, and the device for canceling the counter pressure is provided on the pressure surface side, which device can be displaced perpendicularly to the strand.
  • the actuating device for the device for canceling the counterpressure which is formed, for example, by a displacement slide for the pressure surface with an oblique ramp surface, also displaces the cutting plate and subsequently the ejection plate, so that the counterpressure is lifted, the strand piece is separated, and finally released of the strand piece from the fixed quarter shells.
  • a third way to achieve the post-compression provides that the pressure surface is formed on a connecting web which extends over about half the circumference of two disks combined to form a roller, which are fixed eccentrically on a drive shaft, and their distance from one another is greater than the cross section of the emerging strand is.
  • the eccentrically arranged roller rotates over 180 to continuously evade the pressure surface, but the back pressure remains essentially the same. As soon as the rotation through 180 ° has taken place, due to the missing connecting web, the pressure on the strand is increased and the further rotation of the roller is made possible, the strand entering between the disks of the roller.
  • the other end of the connecting step is preferably shaped into a cutting edge, so that the strand piece protruding into the roller is cut off before reaching the starting position, the counterpressure being built up again immediately thereafter.
  • the drive shaft which in particular can consist of two pins, each of which protrudes from the outside of a disk, on both sides in a carriage is rotatably mounted, each carriage rests in a sliding guide in the pressing direction on an adjustable pressure element in particular.
  • roller drive is switched on when the set pressure is exceeded, exact control of the back pressure can be achieved, since the rotation of the roller then only takes place until the set back pressure is fallen below due to the backing of the pressure surface. At this moment the roller is stopped until the counter pressure is exceeded again. There is therefore a rotation of the roller divided into a plurality of small steps.
  • the expandable wall parts are advantageously designed as half-shells which are articulated on the slide and whose movement is controlled by the roller.
  • the control of the movement of the half-shells is achieved, for example, by providing a recess which extends approximately over half the circumference and is offset by 180 ° to the connecting web on the periphery of the outside of each disc, the half-shells being assigned positive guide rollers which are associated with one another then roll the recessed peripheral area of each disc.
  • the two positive guide rollers are arranged on parallel guide elements extending parallel to the half-shells, which are articulated on the slide of the extension part, each guide element being articulated to the roller-side end of the opposite half-shell.
  • the articulated connections between the movable parts of the extension part and the slide can be designed in any suitable manner. They are preferably formed by bolts which connect the corresponding parts with radial play, with at least one contact surface being arched in each connection.
  • a half-shell, its guide element, the slide and the connection between the half-shell and the guide element, preferably a screw bolt, represent in a preferred embodiment an articulated parallelogram which is controlled by the rotating roller and the positive guide roller arranged on the guide element.
  • the alternate connection between a positive guide roller and a half-shell prevents their opening during the press feed, since in this phase the roller does not run in the recess of the roller disc.
  • the pressing pressure acting on the half-shells during the pressing feed takes the extension part in the pressing direction and thereby stops it on the roller lying. It is therefore preferably provided that a roller is arranged on the outside of each half-shell at the roller-side end, which rolls on the end face of a disk of the roller.
  • a control disk can be arranged on the drive shaft, which has a switching cam which extends over half the gear, which interacts with the drive of the roller, if, for example, a mechanical pressure lament (rubber buffer, compression spring, etc.) is used.
  • the control cam of the control disk can actuate at least one limit switch of the drive motor of the roller, the accuracy of the control depending on the response speed of the limit switches, the drive or the drive brake, etc.
  • the switching cam acts on a switching lever that mechanically engages the roller drive.
  • the roller drive has a worm wheel fixed on the roller drive shaft, a worm driving it, an axially displaceable intermediate shaft extending the worm drive shaft, and an output shaft rotated by the motor of the press worm, an axially displaceable between the worm drive shaft and the intermediate shaft , toothed clutch with a limit stop lying in the pressing direction and between the intermediate shaft and the output shaft of the press worm motor a friction clutch is provided when the intermediate shaft is moved in the pressing direction, and the cam-actuated shift lever axially displaces the intermediate shaft.
  • hydraulic pressure elements instead of mechanical pressure elements, which drive the roller by means of its own motor or from the screw press motor
  • FIG. 4 shows a longitudinal section through the exemplary embodiment according to FIG. 1
  • FIGS. 5 and 6 show a further embodiment in two different positions
  • FIG. 7 shows a section along the line VII-VII in FIG. 5
  • FIG. 8 shows a schematic side view of an exemplary embodiment similar to FIGS. 3 or 5 and 6
  • FIG. 9 shows a schematic view of a fifth embodiment
  • FIG. 10 shows a vertical section through the mouthpiece and the extension part
  • Fig. 11 shows a section along the line XI-XI in Fig. 11
  • Fig. 12 shows a schematic longitudinal section through a sixth embodiment in the starting position
  • FIG. 13 shows a longitudinal section in the end position 14 shows a section along the line XIV-XIV of FIG. 13
  • FIG. 15 shows a longitudinal section through a seventh exemplary embodiment in the ed 15
  • FIG. 17 shows a longitudinal section through the end position of the fifth exemplary embodiment
  • FIG. 18 shows a plan view of the illustration according to FIG. 17,
  • FIG. 19 shows a section along the line XIX -XIX of FIG. 14
  • FIG. 20 shows a schematic illustration of the drive of the post-compression device according to FIGS. 15-19 via the motor of the press screw
  • FIG. 21 shows a vertical section through an embodiment of the filling funnel according to line XXI-XXT of FIG. 1
  • FIG. 22 is an enlarged bottom view of an embodiment of the grille cover of the hopper.
  • Invention screw presses are particularly suitable for sealing all kinds of combustible waste and have a screw tube 1 with a screw 6, a hopper 2 above one end of the screw 6 and a mouthpiece 3 which is located at the other end of the screw 6 Screw tube 1 connects.
  • the screw 6 is provided with screw flights 7, which are in the area between the feed hopper 2 and the mouthpiece side End have a flat slope, while they rise much steeper in the area of the hopper 2.
  • the hopper 2, not shown in detail is, for example, of a truncated pyramid shape, with at least one of the hopper walls 22, for example, having conveyors moving in the direction of the screw 6, for example a conveyor belt or the like equipped with drivers. are provided. Other structural designs of the hopper are shown in FIGS.
  • One of the edges 19 of the hopper 2 close to the screw is arranged at a distance from the screw 6, which corresponds to the maximum size of the material to be pressed that can be grasped by the screw 6, and serves as a shear element for the material to be processed, the edge 19 in the direction of rotation of the Snail 6 points.
  • the materials fed through the hopper 2, for example plastic, cardboard or wooden packaging, waste paper, food waste from commercial operations, pieces of bark, sawdust and wood waste from sawmills, straw, brushwood and other waste from agriculture etc. are supported by the preferred funding the funnel wall 22, gripped by the worm threads 7 of the worm 6 running in this area with a large gradient, torn by the Scherelanent and conveyed into the worm tube 1.
  • an edge 19 of the hopper 2 pointing against the direction of rotation of the screw 6 can also be designed as a cutting edge.
  • the material to be pressed is then compressed in the screw tube 1 in which the screw flights 7 are continued with a smaller and, for example, constant pitch, the liquid contained, in particular water, which can be a relatively large proportion depending on the material, being released.
  • At least one longitudinal slot 4 in the wall 5 of the screw tube 1 is used to discharge the squeezed liquid, while that compresses to one strand
  • this strand 10 breaks into handy parts or, if appropriate, is also divided into parts which have a transportable strength and can be used as fuel with a medium to high calorific value. With material-related fluctuations, this lies approximately in the Height of lignite briquettes, the strand parts also having approximately similar combustion properties.
  • a progressive compaction of the material is necessary in order to achieve a higher degree of dewatering with strong, water-containing waste, for example with pieces of bark that previously had to be pre-dried during briquetting.
  • this could also be achieved by continuously reducing the pitch of the screw flights 7.
  • it is also more favorable in these exemplary embodiments, in the two other exemplary embodiments according to FIGS. 1/4 and 2, it is necessary to keep the slope constant. At least the end section 20 of the screw 6 is therefore tapered towards the mouthpiece 3.
  • each guide element 9 is equipped with teeth 8, 37 and is designed to be movable in a radial plane of the screw axis 12, so that it can avoid the migrating screw flights 7.
  • the radial plane runs through the longitudinal slot 4 in the wall 5 of the screw tube 1, so that the guide element 9 can be mounted on the outside of the screw tube 1.
  • the longitudinal slot 4 is also kept constantly free and its clogging by the material, which would prevent the liquid from escaping.
  • the worm 6 also ends on the mouthpiece side at a distance from the mouthpiece 3, and the guide element 9 projects beyond the worm 6, so that the guiding action of the guide element 9 is maintained approximately directly up to the mouthpiece 3.
  • the guide element 9 is formed by a toothed disc 11 which is arranged loosely rotatable on the axis 42.
  • the rotating screw 6 therefore drives the disk 11 provided with teeth 8, which on the one hand cleans the longitudinal slot 4 and on the other hand forms a longitudinal guide for the material.
  • the taper of the end portion 20 of the screw 6 is concave to the extent of Adjusted disk 11 so that several teeth 8 of the disk 11 engage snugly in the screw 6.
  • the longitudinal slot 4 can be made substantially longer than shown and, if necessary, a further disk 11 provided with teeth 8 can also be provided at a distance from the front disk 11 in order to increase the length of the guide element 9.
  • the worm 6 has a further concavely curved, tapering section.
  • the tapering of the screw 6 is constant over the entire length of the screw tube 1 and a circumferential chain 13 is provided as a guide element 9 in the longitudinal slot 4, the links of which are also equipped with teeth 8.
  • the chain 13 is guided over two deflection rollers 23, 24, the oil steering roller 24 near the mouthpiece being arranged directly at the mouthpiece 3 before the end of the screw 6.
  • the teeth 8 of the chain 13 now engage between two screw flights 7 and in turn bring about the axial or longitudinal guidance of the material to be pressed, as well as the keeping of the longitudinal slot 4.
  • the chain 13 is also loosely rotatably supported and is rotated by the rotating screw 6 driven.
  • the guide element 9 is formed by a bar 14 which is rigid in the longitudinal direction and on which teeth 8 are provided, which in turn engage between the screw flights 7. Since the teeth 8 of the bar 14 must also dodge, but an axial movement of the teeth 8 is not possible, the bar 14 is arranged to be movable essentially radially or perpendicularly to the surface of the screw, with a corresponding displacement of the teeth 8 in this case as well is achieved by the rotating screw 6. An additional device is, however, for the return of the bar 14 after the passage
  • the kick of the bar 14 towards the screw axis 12 can be achieved by an eccentrically rotating element 15, the speed of which is equal to the screw speed.
  • the eccentric element 15 can thereby a cam disk or camshaft can be formed, which bears against the bar 14 from the outside, the nooke causing the bar 14 to be returned.
  • a cam could be arranged at each end of the bar 14.
  • Element 15 the screw tube 1 on the hopper side and is driven at the same speed in a manner not shown.
  • a roller bearing 17 is arranged, which is enclosed by a ring 16, from which a tab 26 projects radially. This is loosely penetrated by a bolt 25 which is provided on the bar 14.
  • the protruding into the tab 26 bolt 25 prevents the entrainment of the ring 16 when the eccentric element 15 rotates, so that the ring 16 orbits the screw axis 12 eccentrically without self-rotation.
  • the tab 26 is preferably only pivotable to a limited extent ver arranged on the ring 16 which extends to the screw axis 12.
  • the movement of the eccentric element 15 therefore presses the bar 14 and thus its teeth 8 alternately radially outwards and inwards.
  • the area of the bar 14 close to the tooth, insofar as it engages in the longitudinal slot 14, with unevenness such as ribs, sharp-edged projections 38 or the like which supports the cleaning of the longitudinal slot 4. be provided.
  • Such a guide for the bar 14 can be provided at both ends.
  • the bar is articulated at the other end, in the exemplary embodiment on the mouthpiece side, so that its movement represents a pivoting movement about the joint axis 28.
  • the bolt 25 is therefore, as mentioned, arranged in the bracket 26 with some play and therefore movable and longitudinally displaceable so as not to hinder the swiveling movement.
  • the eccentric element 15 does not surround the screw tube 1 as a separately driven component, but is formed on a support ring 32 , which is connected to the screw 6.
  • the Screw tube 1 is interrupted in this area, ie divided into two parts, and the support ring 32 protrudes outward from the conveying space of the screw 6.
  • the inner surface of the support ring 32 is aligned with the inner wall of the worm tube 1 and the connection between the support ring 32 and the worm 6 takes place via the reinforced section 33 of the worm gear 7, which consequently forms a type of spoke (FIG. 7), so that the conveying cross section is only slightly reduced.
  • a further guide element 9 in the form of an angled lever 36 is provided in this embodiment, which is attached to a screw tube fixed and an outer bearing 34 for the support ring 32 the part of the screw press is articulated.
  • the lever 36 extends on the side of the support ring 32 facing the feed hopper 2 into a further longitudinal slot 4 of the wall of the screw tube 1 and is equipped with a tooth 37 which engages in the space 41 between the support ring 32 and the screw 6 at a slightly inclined angle to the screw axis 12 has a long length, since the slope of the screw flights 7 in the feed area, as mentioned, is high.
  • the other end of the lever 36 is provided with a longitudinal slot through which a guide pin provided on the bracket 26 extends, the bracket 26 being pivotable about the axle pin 27.
  • a roller bearing 35 is provided between the support ring 32 and the outer bearing 34.
  • an annular gap 40 is also provided on both sides, through which liquid which has also been squeezed out can escape.
  • the adjacent area of the eccentric element 15 or the support ring 32 is also provided with unevenness, such as sharp-edged ribs, or cutting edges 39, which can additionally be bent.
  • Fig. 5 shows in longitudinal section the pivoted-out position of the bar 14, in which the screw flights 7 are arranged below the teeth 8 and at the same time the lever 36 is pivoted in with the tooth 37.
  • FIG. 6 shows the pivoted-in position of the strip 14, in which the teeth 8 engage between the worm threads 7, and the pivoted-out position of the lever 36, in which the tooth 37, the worm thread 7 and let section 33 pass.
  • the teeth 8, 37 preferably have a length which corresponds to approximately half the pitch, so that there is sufficient play.
  • the hinge axis 28 is arranged closer to the mouthpiece 3 than the front end of the worm 6, so that the teeth 8 can all be formed with the same depth, since a sufficient distance from the worm 6 is already achieved with the first tooth 8 engaging between the two foremost worm threads 7 , which allows the passage of the worm gear 7.
  • the arrangement or guidance shown of the bar 14 could also be reversed, so that the hinge axis 28 on the side of the hopper 2 and the ring 16 and the eccentric element 15 is on the mouthpiece side. Even with such an embodiment, there are no obstacles to the pivoting movement if the hinge axis 28 is arranged closer to the filling funnel 2 with respect to the tapering section of the screw 6.
  • a plurality of guide elements 9 distributed over the circumference. 8
  • the formation of a further strip 14 on the side of the screw tube 1 diametrically opposite the first strip 14, in whose wall 5 a further longitudinal slot 4 is provided, is particularly favorable.
  • the two strips 14 can be coupled in a simple manner through the ring 16 and the two tabs 26 and attached to two parallel joint axes 28.
  • the formation of an eccentric element 15 is not absolutely necessary, since the two strips 14 force each other.
  • the ring 16 must surround the screw tube 1 with a sufficient distance.
  • the teeth 8 ′ of the two strips 14 are arranged exactly opposite one another, with one strip 14 (the upper one in FIG.
  • a coupling by a ring 16 and tabs 26 can also be provided on this side.
  • an extension part 18 composed of individual wall parts 21 arranged at a distance to form longitudinal slots 29.
  • the wall parts 21 are individually radially adjustable, for which purpose, for example, a ring 30 is provided which is penetrated by adjustable bolts 31 which bear against the wall parts 21.
  • a radial compression of the strand 10 emerging from the mouthpiece 3 is achieved, which is adjustable. Post compression can be used depending on the material. If, on the one hand, very dry waste, such as paper wool or wood wool, or, on the other hand, very wet waste, the drainage of which has not been completely carried out in the screw tube 1, is pressed, the strength of the strand 10 is usually too low, and this disintegrates into small parts when it emerges.
  • the expandable wall parts 21 are individually adjusted so that a further cross-sectional taper is achieved. This also compensates for the grooves in the strand formed by the guide elements 9 and sufficiently compresses the strand 10. Post-compression by tapering the cross-section can be unnecessary if the waste contains a large proportion of thermoplastic materials, which melt during the compression in the screw press and mix intimately with the remaining material due to the screw movement.
  • a Rafonen 60 is provided in this embodiment with a side plate 65 which adjoins the screw tube 1 and which carries the extension part 18.
  • the extension part 18 has a displaceable section 43 Mistake.
  • This has a slide 49 on the press side, which is slidably arranged on the end region of the screw tube 1, ie on the mouthpiece 3.
  • On the carriage 49 several, for example six strip-shaped flat wall parts 21 are articulated, for example by means of screws 51 which penetrate them with play, which complement each other to form a tube with a hexagonal cross section. Continuous longitudinal slots 29 remain over the entire length between the wall parts 21, which also allow the liquid squeezed out of the material to exit.
  • At least two wedges 55 are fastened at a distance from one another on each wall part 21, the outer surfaces of which form flat guide surfaces 44, 45 and each diverge on the outlet side.
  • the guide surfaces 44, 45 roll on stationary rolling bearings 52 or rollers.
  • the wedges 55 are arranged in rings 61 and the roller bearings 52 in cages 53, the angle of the guide surfaces 44, 45 to the pressing direction A being different.
  • the outlet-side guide surfaces 44 run, for example, at an angle of 5, the screw-tube-side 45 at an angle of 1 ° to the pressing direction A.
  • projections 54, 56 of the wedges 55 protrude outward on both sides in the longitudinal direction.
  • the projections 54 on the screw tube side form a sliding stop for the section 43 of the extension part 18 in the pressing direction A.
  • the projections 56 on the outlet opening side of the wedges 55 complement one another to form a flange on which a compression spring 59 is supported.
  • a pressure plate 58 and radially movable roller bearings 57 are provided between the compression spring 59 and the projections 56.
  • the compression spring 59 is supported on the outlet opening side against an abutment 63 arranged longitudinally adjustable on the frame 60, so that the spring travel of the compression spring 59 can be changed with the aid of the nuts 62.
  • the waste material to be pressed into the strand 10 is pressed by the screw 5 through the mouthpiece 3. Through to the wall share 21 resulting friction there is an increasing compression of the material strand 10, which exits at the outlet opening 66 and breaks off into handy pieces due to its own weight.
  • the length of the extension part 18 corresponds approximately to 10 to 20 times the strand diameter.
  • the section 43 of the extension part 18 moves under compression of the compression spring 59 in Pressing direction A with the material strand 10, with the slide 49 sliding on the end section of the screw tube 1 or mouthpiece 3.
  • the guide surfaces 44, 45 roll on the roller bearings 52 since they are pressed against them by the radial pressure of the material strand 10.
  • the divergence of the guide surfaces 44, 45 now causes an enlargement of the mouthpiece cross-section when the section 43 is displaced, so that the frictional forces and the compression become smaller and the feed of the material strand 10 is maintained or increased slightly.
  • the compressed compression spring 59 moves the displaceable section back again, the cross section of the extension part 18 being reduced by the divergence of the guide surfaces, the frictional forces being increased and the compression of the material strand 10 being increased.
  • the section 43 is pushed even further onto the mouthpiece 3 by the compression spring 59, so that the cross section of the section 43 at the outlet opening 66 is also smaller than the cross section of the Mouthpiece 3 can be, whereby the compression of the strand 10 is increased.
  • a constant forward and backward shift occurs with a simultaneous change in cross-section, which results in a strand of essentially the same strength.
  • the change in cross section decreases as the distance to the slide 49 decreases, since the wall parts 21 are hinged to this.
  • the crown 61 of wedges 55 on the side of the screw tube can therefore have contact surfaces 45 with a smaller angle than the guide surfaces 44 to the pressing direction A.
  • the auger tube-side rim 61 is used in particular for the longitudinal stiffening of the expandable wall parts 21, so that they can be made of a thinner material and bulges are kept out.
  • a central ring 61 with guide surfaces and a central cage 53 with roller bearings 52 could also be provided to support the wall parts 21.
  • the adjustment of the abutment 63 could also be automated, with different setting levels for certain compositions of the waste to be processed can be provided.
  • Auger 6 is shown in the area of the mouthpiece 3, the extension part 18 follows in the form of a cylindrical part which is composed of quarter shells 86, 87 over the length of the strand section 72 to be produced.
  • the first two quarter shells 86 preferably form the upper half of the cylindrical part with horizontal pressing direction A and are immovably arranged in the extension of the mouthpiece 3.
  • a longitudinal slot 88 extends between the two quarter shells 86.
  • the two second quarter shells 87 are each movably connected to the two first quarter shells 86 via a joint 89 and are held in contact with one another by a locking device (not shown) during the pressing advance of the strand 10 (FIG. 12 ).
  • the lock is released and the two second quarter shells 87 are opened (FIGS. 13 and 14), so that the strand piece 72 to be cut can exit laterally, preferably downwards.
  • An ejector plate 94 acts as an ejector, which is inserted into the longitudinal slot 88 and retracted so far that it does not protrude into the cylindrical space 92.
  • the cutting device 76 is arranged on the mouthpiece side of the longitudinally extending ejection plate 94 in the form of a cutting plate 95 perpendicular to the direction of the strand and is guided in corresponding transverse slots 96 (FIG. 12) of the first quarter shells 86.
  • the device 75 for canceling the counter pressure is designed in the form of a displacement slide 95, which projects beyond the lower edge of the ejection plate 94 and has an inclined run-up surface 97.
  • the counterpressure device 73 with the pressure surface 74 is accommodated in a tubular extension section 91 which adjoins the hollow cylindrical part consisting of the quarter shells 86, 87 and forms a fixed part of the frame 60.
  • the pressure surface 74 is provided on the end face of a piston 81 which is guided axially displaceably via a piston rod 82.
  • a compression spring 59 which also serves as a return device 77, presses the pressure surface 74 against the end face of the strand 10 and is supported on an abutment 63, preferably axially adjustable by means of screws 98, which are arranged rotatably in the frame 60.
  • the compression spring 59 is increasingly compressed by the strand 10 pressed out of the mouthpiece 3.
  • the quarter shells 86, 87 support the emerging strand 10 circumferentially against buckling.
  • the displacer disk 95 is set in motion, the contact surface 97 of the displacer slide 59 pressing so that it detaches from the end face of the strand.
  • the cutting plate 93 begins to separate the strand piece 72, the second quarter shells 87 opening, and subsequently the strand piece 72 is ejected by the advance of the ejection plate 94.
  • the displacement slide 95, the cutting plate 93 and the ejection plate 94 then pull back again, the second quarter shells 87 are closed and the released one
  • Pressure surface 74 is pressed forward under the action of the compression spring 59 against the end face of the strand 10.
  • the exemplary embodiment according to FIGS. 15-19 shows an embodiment of the device according to the invention in which the back pressure during the press feed of the strand 10 remains essentially unchanged.
  • the essential components namely the counter pressure device 73 with pressure surface 74, the device 75 for canceling the counter pressure, the cutting device 76, the return device 77 of the pressure surface 74 and the extension part 18 are provided.
  • the most important component of this variant is represented by a roller 100, which is composed of two side disks 101 and a connecting web 102 extending approximately over half the circumference of the disks 101, the outer surface of which forms the pressure surface 74.
  • the roller 100 is fixed eccentrically on a shaft running perpendicular to the pressing direction A, which is preferably formed from two pins 103, but can also be formed continuously .
  • a sliding guide 104 is provided on each side of the roller 100, each of which receives a slide 119, the two pins 103 each being rotatably mounted in a slide 119.
  • Each carriage 119 rests on a pressure element 105, for example a rubber buffer, a compression spring cdgl. on.
  • a control disk 106 is also fastened, which cooperates via a switching cam 117 extending over half the circumference with two limit switches 118, which control the drive 107 of the roller 100, which is coupled to the second pin 103.
  • the pressure element 105 is preferably adjustable, as is the position of the limit switches 118, in order to be able to adjust the counterpressure to be applied to the strand 10 approximately uniformly, depending on the type and moisture content of the material to be pressed.
  • expandable wall parts 21 are also provided in this embodiment, which consist of two half-shells 108.
  • the two half-shells 108 are articulated on the face of the carriage 49, which is displaceable on further guides 116, preferably arranged in the extension of the slide guides 104.
  • a roller 112 is rotatably arranged on each half-shell 108, on which the side plates 101 of the roller 100 roll.
  • a recess 113 in particular a groove, is made in the side window 101 over the ecden area over which the connecting web 102 forming the pressure surface 74 does not extend.
  • the positive guide roller 111 therefore runs over approximately 180 in the recess 113 and over the remaining active area on the outer surface of the side window 101 itself. This causes an alternating occupation of each guide element 109, from which the upper and lower connecting bolts 110 close of the respective opposite half-shell 108 of the extension part 18 for the strand 10.
  • the shells 108 are therefore held in contact with one another during a roller rotation, as long as the positive guide rollers 111 do not roll in the recesses 113 but on the side window 101 itself, and spread apart as soon as the positive guide rollers 111 have entered the recesses 113.
  • the ex Centricity of the roller 100 to its drive shaft is half the length of the strand piece 72 to be cut, a change in length being possible by radial adjustment of the pins 103 on the roller 100 and displacement of the associated pressure elements 105 in the pressing direction A.
  • the facilities required for this are
  • the distance between the pressure surface 74 and the mouthpiece 3 increases by a certain amount, so that the strand 10 can emerge by this partial length. Since the counterpressure is thereby briefly reduced, the pressure elements 105 move the roller 100 again against the pressing direction A, as a result of which the switching cam 117 of the control disk releases the switch 118 again. The drive 107 is interrupted and the roller 100 stops. The pressing pressure of the screw 6 then increases again, so that the roller 100 is moved again in the pressing direction A, the pressure elements 105 are compressed again more intensely and finally the drive 107 is switched on again in the manner described.
  • the strand 10 entering this slightly enlarged space 120 relative to the mouthpiece 3 is pressed radially by the counterpressure against the half-shells 108, which are each held in the closed position by the positive guide roller 111 running in the curved piece between the recess 113 and the side window 101 via the connecting bolts 110 become.
  • the radial pressure now creates a frictional connection to the half-shells 108, which are prevented from moving laterally by the positive guide rollers 111, so that the extension part 18 is carried along by the strand 10.
  • the rollers 112 of the extension part 18 therefore rarely remain attached to the forehead of the side windows 101 during the entire press feed, so that when the end position is reached according to FIGS. 17 and 18 of the extension part 18, a tubular extension to the extent of the length of the strand piece 72 to be cut off, i.e. the double eccentricity of the side windows 101 forms.
  • the onset kick rotation of the roller 100 in which the end faces of the side disks 101 approach the mouthpiece 3 again, pushes the one that has exited Strand detached extension part 18 back on the mouthpiece 3.
  • the extruded strand 10 penetrates between the side disks 101 into the roller 100 and is exposed there.
  • the end of the groove 113 is reached immediately before the starting position is reached, as a result of which the positive guide rollers 111 are lifted off and the half-shells 108 are pressed together again.
  • the severed free strand 10 is cut off by the cutting device 76, which is formed by a cutting edge 121, into which the front end of the connecting surface 102 forming the pressure surface 74 runs out.
  • the drive shaft or a drive pin 103 is located next to the control disk 106 another worm wheel 123 is fixed, in which a gear worm 124 engages.
  • the gear worm 124 which also moves with the slide 45, has a worm drive shaft 126 which, via an axially displaceable toothed coupling 133, has an axially displaceable intermediate shaft 125 is coupled.
  • the switching cam 117 of the control disk 106 moves a switching lever 122 articulated on the frame 60, the movement of which axially displaces the intermediate shaft 125, a compression spring 130 supported on the frame 60 acting on a pressure disk 132 fixedly connected to the intermediate shaft 125 via a thrust bearing 131.
  • This compression spring 130 is compressed by the switching cam 117 when the switching lever 122 is actuated.
  • a clutch disc 127 of a friction clutch 129 is arranged, which interacts with a second clutch disc 128.
  • This clutch disc 128 is preferably driven by a gear from the motor of the press screw 6.
  • the axially displaceable coupling 133 has a coupling sleeve 140 provided with an internal toothing 137 and a front limit stop 136 in the pressing direction.
  • a gear 139 fixed on the worm drive shaft 126 slides in the internal toothing 137.
  • the switching cam 117 of the control disk 106 is in the position shown in FIG. 20.
  • the switching cam 117 now actuates the switching lever 122 which can be rotated about the axis 134, the claw 138 of which comprises the intermediate shaft 125 and abuts the internally toothed sleeve 140. This also attracts the intermediate shaft 125 and engages the friction clutch 129, the gear wheel 139 being axially displaced in the toothing 137.
  • the preferably compressed combustible waste material is therefore, regardless of its moisture content, compressed to transportable press briquettes with sufficient strength and high calorific value.
  • the filling funnel 2 has two vertical side walls 156 and two side walls 146 widening after the filling opening 148.
  • two drive shafts 142, 143 of a shredding device 149 are mounted, each of which is equipped with a slowly rotating shredding roller 150, which is composed of shredding disks 144 provided with fangs 145.
  • the shredding disks 144 are axially grounded at a distance from one another which corresponds to the width of a shredding disk 144, the shredding disks 14 of one shredding roller 150 engaging those of the other shredding rollers 150.
  • the two shredding rollers 150 rotate in opposite directions, so that the waste filled in via the filling opening 148 is passed between the shredding disks 144 of the rollers 150 and thereby shredded.
  • a grid 147 for example a sieve, a perforated plate or a bar grate, which has openings 157 corresponding to the desired size of the comminuted material particles.
  • A, preferably two-part cover 151 on the underside of the grating 147 ensures the correct metering of the amount of shredded material passing through the grating 147.
  • the distance between the grating 147 and the shredding rollers 150 is approximately as large as the size of the shredded pieces of material and the distances between the comminution rollers 150 and the inclined side walls 146 are chosen to be larger than the size of the comminuted material pieces, and furthermore each comminution roller 150 is assigned a series of wipers 152 which each extend obliquely in the direction of the center web 153 extending below the comminution device 149 Drive shafts 142, 143 extend between the shredding disks 144. To achieve the mentioned distance of the grid 147 to the comminution rollers 150, this is therefore symmetrical
  • the overall passage area of the grille 147 is reduced by shifting the covers 151. This can be done manually, but is preferably coupled with the change in the outlet cross section of the extension part 18, in particular with the axial displacement given in the embodiments according to FIGS. 9-19.
  • both the grid 147 and the covers 151 are formed by perforated metal sheets, the latter being able to be displaced by the hole diameter in the direction of the arrows from the closed state shown. As a result, all of the openings 157 in the grille 147 widen at the same time, and the displacement path is short.
  • the grid 147 is formed by parallel bars 154 of a grate, so that it can be seen as Openings 157 provide slots extending lengthways.
  • the covers 151 are in turn formed by metal sheets which, in the closed state, also engage under the central web 153 carrying the wipers 152 and have a toothing along their contact edges, for example the teeth 155 shown, which, in the closed state, completely close the mesh 147 in the closed state. With increasing pull-out movement of the cover, the openings 157 are gradually opened from the center, FIG. 22 showing a central position. As shown, the covers 151 can be moved perpendicular to the bars 154, but also parallel to them.
  • the amount of material between the shredding device 149 and the grating 147 is greater than the amount that can be fed to the screw 6, the shredded material is taken along by the shredding rollers 150 again into the filling funnel 2, or is circulated until the total cross-sectional area of the grating 147 is enlarged. Any further comminution that may take place during this time is of no importance; however, a dosage which is essentially adapted to the absorption capacity of the screw 6 is achieved in a simple manner.
  • FIGS. 9-11 A variant of the embodiment shown in FIGS. 9-11 provides an immovable extension section 18, the expandable wall parts 21 having legs which are angled outwards on the mouthpiece side and which are articulated on the frame 60.
  • a radially acting compression spring can now be provided for each wall part 21, which, when the radial pressure of the strand 10 increases, allows the wall parts 21 to pivot slightly outwards and returns them inwards as the radial pressure decreases.
  • an axially acting compression spring can also be provided, which is supported on the angled legs which essentially complement one another to form a flange. In this way, a shorter overall length is achieved in any case, since the front abutment 63 is omitted.
  • FIGS. 9-22 are not limited to the use of a screw 6 for generating the press feed. They can also be designed as piston extrusion presses.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Transmission Devices (AREA)
  • Processing Of Solid Wastes (AREA)
  • Solid Fuels And Fuel-Associated Substances (AREA)

Abstract

Dans les extrudeuses à vis traitant en particulier des déchets combustibles, il est nécessaire d'avoir une alimentation de la matière par dosage, une pression élevée et une élimination de liquide la plus complète possible pour obtenir un rapport aussi bon que possible entre l'alimentation, la compression et la densification. A cet effet, au moins un organe de guidage qui est en contact avec l'extrémité antérieure de la vis et avec la sortie (3) voisine de la filière, permet le guidage axial de la matière extrudée pour éviter qu'elle ne se casse. La section et par conséquent la contre-pression dans un organe de rallonge (18) de la sortie de filière (3) est réglable et s'obtient de préférence par des éléments de paroi (21) extensibles et amovibles axialement grâce à l'action de ressorts. Un dispositif de dosage qui en dépend, comprend des éléments de couvertures commandés de préférence par le déplacement axial de l'organe de rallonge (18) en fonction de la pression. Ces éléments de couverture protègent une grille ou similaire disposée dans la trémie (2) entre un broyeur de la trémie (2) et l'extrémité amont de la vis. L'organe de guidage traverse la paroi (5) de la filière (1), est entraîné par la vis et nettoie constamment la sortie principale du liquide exprimé, matérialisée par la fente du support dans la paroi (5).
PCT/AT1983/000024 1982-09-16 1983-08-01 Extrudeuse WO1984001125A1 (fr)

Priority Applications (8)

Application Number Priority Date Filing Date Title
DE8383902419T DE3376102D1 (en) 1982-09-16 1983-08-01 Extruding machine
DE19838337835U DE8337835U1 (de) 1982-09-16 1983-08-01 Schneckenpresse
AU18241/83A AU1824183A (en) 1982-09-16 1983-08-01 Schneckenpresse
DE19838390031U DE8390031U1 (de) 1983-02-10 1983-08-01 Schneckenpresse
IT67958/83A IT1193148B (it) 1982-09-16 1983-09-15 Estrusore a vite
DE8484890144T DE3474416D1 (en) 1983-08-01 1984-07-31 Waste comminuting apparatus
EP84890144A EP0140869B1 (fr) 1983-08-01 1984-07-31 Dispositif pour le broyage de déchets
AT84890144T ATE37671T1 (de) 1983-08-01 1984-07-31 Vorrichtung zum zerkleinern von abfall.

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT346182A AT381472B (de) 1982-09-16 1982-09-16 Schneckenpresse
AT45583A ATA45583A (de) 1983-02-10 1983-02-10 Strangpresse
AT94283 1983-03-17

Publications (1)

Publication Number Publication Date
WO1984001125A1 true WO1984001125A1 (fr) 1984-03-29

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Application Number Title Priority Date Filing Date
PCT/AT1983/000024 WO1984001125A1 (fr) 1982-09-16 1983-08-01 Extrudeuse

Country Status (5)

Country Link
EP (1) EP0119208B1 (fr)
AU (1) AU1824183A (fr)
DE (1) DE3376102D1 (fr)
IT (1) IT1193148B (fr)
WO (1) WO1984001125A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1984003252A1 (fr) * 1983-02-23 1984-08-30 Spaenex Sander Gmbh & Co Kg Presse a briquettes; procede et installation pour regler la puissance de pression de la presse a briquettes
WO1984003661A1 (fr) * 1983-03-17 1984-09-27 Pfeifer Oskar Boudineuse
EP0359285A2 (fr) * 1988-09-16 1990-03-21 Franz Haimer Dispositif pour agglomérer du brin végétal, notamment de paille
US4947743A (en) * 1988-02-19 1990-08-14 Stake Technology Limited Apparatus for feeding a mass of particulate or fibrous material
WO1991004150A1 (fr) * 1989-09-15 1991-04-04 Franz Haimer Dispositif d'aglomeration de matiere vegetale, en particulier de paille et matieres analogues
FR2658751A1 (fr) * 1990-02-23 1991-08-30 Inst Francais Du Petrole Dispositif de pre-traitement de dechets plastiques avant recyclage.
EP0451348A1 (fr) * 1990-04-06 1991-10-16 Alois Pöttinger Maschinenfabrik GmbH Presse à vis
GR1002459B (el) * 1995-09-19 1996-11-01 Συνθετο πιεστηριο υψηλης συμπιεσης συνεχους λειτουργιας για τον διαχωρισμο μειγματος στερεων υγρων.

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GB190901034A (en) * 1908-01-16 1909-06-03 Jules Gustave Tirlicien Apparatus for the Treatment and Moulding of Peat and Plastic Matters.
FR542776A (fr) * 1921-10-27 1922-08-21 Marmonier Fils Appareil permettant de fouler, d'égoutter et d'égrapper les raisins
FR29577E (fr) * 1924-03-14 1925-08-27 Procedes Ind Candlot Soc D Exp Presse à agglomérés
DE735471C (de) * 1935-10-25 1943-05-15 Ernst Bisterfeld Verfahren und Presse zum Herstellen von Tabletten aus Kunststoffen
DE814098C (de) * 1948-10-02 1951-09-20 Wilhelm Neuscheler Schneckenpresse
FR1189251A (fr) * 1957-11-18 1959-10-01 Perfectionnement au pressurage des marcs de raisins ou toutes autres matières pouvant être pressurées par vis sans fin
GB904619A (en) * 1961-03-21 1962-08-29 Robert Desmond Parker Improvements in machines for consolidating granular or other material by extrusion
FR1401378A (fr) * 1964-04-22 1965-06-04 Pressoir à vendange et autres matières pulpeuses
US4343233A (en) * 1980-03-31 1982-08-10 Burgin Kermit H Apparatus for producing and collecting a liquid extract and a dry by-product from a mash

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB190901034A (en) * 1908-01-16 1909-06-03 Jules Gustave Tirlicien Apparatus for the Treatment and Moulding of Peat and Plastic Matters.
FR542776A (fr) * 1921-10-27 1922-08-21 Marmonier Fils Appareil permettant de fouler, d'égoutter et d'égrapper les raisins
FR29577E (fr) * 1924-03-14 1925-08-27 Procedes Ind Candlot Soc D Exp Presse à agglomérés
DE735471C (de) * 1935-10-25 1943-05-15 Ernst Bisterfeld Verfahren und Presse zum Herstellen von Tabletten aus Kunststoffen
DE814098C (de) * 1948-10-02 1951-09-20 Wilhelm Neuscheler Schneckenpresse
FR1189251A (fr) * 1957-11-18 1959-10-01 Perfectionnement au pressurage des marcs de raisins ou toutes autres matières pouvant être pressurées par vis sans fin
GB904619A (en) * 1961-03-21 1962-08-29 Robert Desmond Parker Improvements in machines for consolidating granular or other material by extrusion
FR1401378A (fr) * 1964-04-22 1965-06-04 Pressoir à vendange et autres matières pulpeuses
US4343233A (en) * 1980-03-31 1982-08-10 Burgin Kermit H Apparatus for producing and collecting a liquid extract and a dry by-product from a mash

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1984003252A1 (fr) * 1983-02-23 1984-08-30 Spaenex Sander Gmbh & Co Kg Presse a briquettes; procede et installation pour regler la puissance de pression de la presse a briquettes
WO1984003661A1 (fr) * 1983-03-17 1984-09-27 Pfeifer Oskar Boudineuse
US4947743A (en) * 1988-02-19 1990-08-14 Stake Technology Limited Apparatus for feeding a mass of particulate or fibrous material
EP0359285A2 (fr) * 1988-09-16 1990-03-21 Franz Haimer Dispositif pour agglomérer du brin végétal, notamment de paille
EP0359285A3 (en) * 1988-09-16 1990-11-22 Franz Haimer Apparatus for briquetting plant material, in particular stalks and the like
WO1991004150A1 (fr) * 1989-09-15 1991-04-04 Franz Haimer Dispositif d'aglomeration de matiere vegetale, en particulier de paille et matieres analogues
US5302102A (en) * 1989-09-15 1994-04-12 Franz Haimer Equipment for briqueting vegetal material in particular stalk-plant materials
FR2658751A1 (fr) * 1990-02-23 1991-08-30 Inst Francais Du Petrole Dispositif de pre-traitement de dechets plastiques avant recyclage.
US5211841A (en) * 1990-02-23 1993-05-18 Institut Francais Du Petrole Device for pretreating plastic waste before recycling
EP0451348A1 (fr) * 1990-04-06 1991-10-16 Alois Pöttinger Maschinenfabrik GmbH Presse à vis
GR1002459B (el) * 1995-09-19 1996-11-01 Συνθετο πιεστηριο υψηλης συμπιεσης συνεχους λειτουργιας για τον διαχωρισμο μειγματος στερεων υγρων.
WO1997010946A1 (fr) * 1995-09-19 1997-03-27 Nikolaos Nikolarakis Pressoir complexe continu haute pression pour la separation d'un melange solides - liquides

Also Published As

Publication number Publication date
IT8367958A0 (it) 1983-09-15
IT1193148B (it) 1988-06-02
DE3376102D1 (en) 1988-05-05
EP0119208A1 (fr) 1984-09-26
AU1824183A (en) 1984-04-04
EP0119208B1 (fr) 1988-03-30

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