EP0320747B1 - Presse à briquettes - Google Patents

Presse à briquettes Download PDF

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Publication number
EP0320747B1
EP0320747B1 EP88120319A EP88120319A EP0320747B1 EP 0320747 B1 EP0320747 B1 EP 0320747B1 EP 88120319 A EP88120319 A EP 88120319A EP 88120319 A EP88120319 A EP 88120319A EP 0320747 B1 EP0320747 B1 EP 0320747B1
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EP
European Patent Office
Prior art keywords
mould
carrier
mold
mould carrier
screwthread
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP88120319A
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German (de)
English (en)
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EP0320747A3 (en
EP0320747B2 (fr
EP0320747A2 (fr
Inventor
Werner Groebli
Hugo Hegelbach
Willi Wetzel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Buehler AG
Original Assignee
Buehler AG
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Application filed by Buehler AG filed Critical Buehler AG
Priority to AT88120319T priority Critical patent/ATE80340T1/de
Publication of EP0320747A2 publication Critical patent/EP0320747A2/fr
Publication of EP0320747A3 publication Critical patent/EP0320747A3/de
Publication of EP0320747B1 publication Critical patent/EP0320747B1/fr
Application granted granted Critical
Publication of EP0320747B2 publication Critical patent/EP0320747B2/fr
Anticipated expiration legal-status Critical
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    • 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
    • B30B11/20—Roller-and-ring machines, i.e. with roller disposed within a ring and co-operating with the inner surface of the ring
    • B30B11/201—Roller-and-ring machines, i.e. with roller disposed within a ring and co-operating with the inner surface of the ring for extruding material
    • B30B11/202—Ring constructions

Definitions

  • the invention relates to a pellet press, according to the preamble of claim 1, as used for example for animal feed and other materials to be pressed.
  • the invention has for its object to provide a pellet press in which the molds can be changed quickly, safely and with little effort. According to the invention, this is achieved by the characterizing features of claim 1.
  • a clamp fit with or without a form fit can be realized particularly easily, with sufficient force transmission between the mold carrier and the form being ensured even under the unfavorable conditions described above (temperature and dimension differences, flexing of the form and vibrations).
  • the shape is provided on at least one of its end faces with at least one undercut opening into which a rotatable locking element engages in such a way that it detects the undercut of the opening in a position rotated by a predetermined angular amount with a gripping surface, this also results in a simple manner flawless form fit between the mold and the mold carrier, whereby dimensional changes are easily compensated for.
  • the locking elements also serve as aids when mounting the mold on the mold carrier.
  • the mold can be fastened to the mold carrier by a simple rotary movement, for example by the drive motor for the mold, the thread simultaneously serving as a retraction device for the mold against the mold carrier and centering backs up.
  • the axially and / or radially fluid-actuated locking members are arranged so as to act in a distributed manner on the circumference of the mold, which results in the required centering.
  • At least one pressure accumulator can be provided in the fluid line for the locking members, whereby an advantageous pressurization is achieved even when there is no connection to the pressure generator, e.g. a hydraulic pump or a compressor, so that a fluid supply through the rotating mold carrier is not necessary during the operation of the pellet press.
  • the pressure generator e.g. a hydraulic pump or a compressor
  • the holding device is at least one fluidic actuating device with a piston Assigned cylinder unit, via which a separate stamp with piston, which is arranged in a hydraulic cylinder, can be actuated, and / or the locking element, which can be fluidly actuated in one actuation direction, is in the other direction by at least one, in particular mechanical spring device, for example by Disc springs, preferably in the direction of the stop position, acted upon.
  • Disc springs preferably in the direction of the stop position
  • the outer rotational surface of the mold is designed as a cone which can be inserted into a counter cone of the mold carrier which forms the inner rotational surface, possibly as a separate ring in this.
  • the respective radially actuatable locking element is expediently designed as a membrane that can be pressed against the external rotation surface of the mold.
  • the rotatable locking member can be used to easily center the mold on the mold carrier.
  • the thread With a relative rotation of the threaded parts from 15 “to 100", a particularly simple and quick assembly of the mold on the mold carrier is possible.
  • the thread If the thread is designed as a conical thread, the thread itself can already serve as an essentially conical fitting surface, with particularly high forces being able to be transmitted.
  • Such threads are used, for example, for prospecting and production lines in the petroleum industry.
  • the arrangement of the threaded segments arranged at a distance from one another makes it possible to measure their spacing in such a way that the threaded segments of the other part of the mold carrier or of the mold can be inserted axially and then rotated. With a connection of this type, particularly high forces can be transmitted between the mold and the mold carrier, a positive connection being able to be achieved by a small angular rotation.
  • the threaded ring is detachably connected to the mold or the mold carrier, the parts subject to wear can be exchanged in a simple manner. If the working direction of rotation of the mold carrier is selected in the sense of screwing in the thread, a particularly trouble-free connection between the mold and the mold carrier is possible, since loosening of the mold during its rotation is impossible.
  • a pellet press 1 In a pellet press 1 (FIG. 1), material to be processed is fed via a hopper 2 to a metering device 3, which feeds a predetermined amount of this material to a mixer 4, to which steam is simultaneously fed via a steam line 5 (FIG. 9).
  • the material mixed in this way then enters a kinked channel 6, which feeds it to a mold cover 7, from where it enters the interior of a press mold 9 via scraper blades 8 and there with the aid of a press roll 9a is pressed through the radial bores 9b of this die.
  • the mold 9 is held in a conventional embodiment with the aid of a ring 11 fastened to a rotatable mold carrier 10 and a clamping ring 13 which can be pulled by bolts 12 in a conical seat of the ring 11.
  • the mold carrier 10 is turned by hand to insert the levers into existing holes 14 to tighten the bolts 12, which holes are accessible via a side door 15a (FIG. 9).
  • V-belt drive shown here by way of example, any other type of drive could of course also be selected.
  • the invention is based on the object of simplifying and improving the arrangement in area A of FIG. 1.
  • clamping jaws 34 serve primarily to avoid the work involved in screwing and to secure the centering of the compression mold 9 on the mold carrier 10 by means of centering jaws 34 and to clamp it with clamping jaws 34 '(right edge indicated by dashed lines).
  • the jaws 34, 34 ' are alternately distributed over the circumference.
  • a plurality of cup-like centering parts 18 are provided on the press mold 9, or instead of several such cups, a U-shaped rail 18 (see FIG. 7), as can be seen in FIG. 2, is e.g. attached to form 9 by welding.
  • the mold carrier 10 has an annular recess 19 with an insert part 20 which has a similar recess 21, the rail 18 being insertable into the recess 21.
  • the rail 18 has elongated holes 22 aligned in the circumferential direction, some of which are distributed over the circumference of the rail 18.
  • the elongated holes 22 are designed such that an elongated head 23 of a bolt 24 can enter these elongated holes 22.
  • This bolt 24 is shown in section in FIG. 7. Its exact design can be seen in FIG. 6.
  • the bolt 24 has an approximately helical groove 25 with such a pitch that this "thread" is in any case not self-locking. At each end of the helical groove 25, which extends over about a quarter of the circumference of the bolt 24, there is an end part 26 which runs parallel to the axis.
  • the bolt 24 is or the like by disc springs. 27 (based on Fig. 2) against the right side.
  • a displacement of the bolt 24 in the axial direction must therefore inevitably involve a rotation of the bolt by 90.
  • a piston-cylinder unit 29, 30 is arranged behind the bolt 24, the piston 30 of which carries a stamp 31 at its left end. If pressure medium is now applied to the piston 30 via a line 32, this overcomes the force of the springs 27 and pushes the pin 24 to the left.
  • the bolt 24 is rotated by 90 due to the threaded groove 25 so that its elongated head 23 is aligned with the elongated hole 22 (FIG. 7). In this position, the mold 9 can be pulled off the bolts 24 or a new mold can be put on.
  • the piston 30 is relieved, whereupon the bolt 24 moves to the right under the load on the plate springs 27 (with reference to FIG. 2) and thereby reaches the locking position shown in FIG.
  • the screw bolts 35 can be omitted if a recess 121 with an inclined surface 133 lying on a somewhat smaller diameter is provided, which cooperates with a corresponding inclined surface 36 of the compression mold 9.
  • the springs 27 must be designed such that the mold 9 is frictionally clamped on the inclined surface 133, a positive connection being obtained via the bolts 24 and the U-rail 18.
  • FIG. 4 and 5 show an embodiment variant in which, instead of the bolts 35 in FIG. 2, there is a clamp fastening with the aid of a pressure medium, the compression mold 9 being drawn into the mold carrier 10 in the same manner as in FIG. 2 and 3.
  • At least one printing unit 37 is provided on the back of the mold carrier 10 or (in the case of several) distributed over its circumference.
  • Each of the pressure units 37 has a piston 38, the piston rod 39 of which protrudes outwards at the rear and can be actuated in an arbitrary manner, not shown, via an annular plate 40 connected to these piston rods 39.
  • the ring plate 40 could be screwed to the left (based on FIG. 4) or be moved to the right.
  • the piston rod 39 could also be replaced by a screw and actuated, for example, in the manner described later with reference to FIG. 16A.
  • A, preferably hydraulic, pressure medium is accommodated in a line system 41 on the left side of the piston 38.
  • This line system 41 opens out on the side of the mold 9 into a space 42 which is separated by a e.g. made of sheet metal, membrane 43 is completed. Therefore, if the piston 38 is moved to the left with reference to FIG. 4, the diaphragm 43 expands and presses against the U-shaped rail 18 on the one hand and against an annular shoulder 44 of the press mold 9 on the other hand.
  • the press mold expediently has a corresponding one Indentation (not shown) into which the membrane (or a piston) can penetrate.
  • FIG. 5 While a certain mechanical work for adjusting the ring plate 40 is still necessary in the embodiment according to FIG. 4, this work can be further simplified by the embodiment according to FIG. 5.
  • similar units 137 are provided, which, however, have the function of a pressure accumulator or buffer.
  • a line 45 can be supplied from a pressure medium supply 46 with the aid of a pump 47, which pumps the pump via a check valve 48 into the unit 137 and the line system 41. If, on the other hand, the membrane 43 is to be relieved, only one valve 49 in a branch line 50 needs to be opened, whereupon the pressure medium flows back into the reservoir 46.
  • the piston 138 of the unit 137 is expediently loaded by a spring 51 (it can also be a gas spring) which compensates for any pressure peaks that may occur.
  • a spring 51 it can also be a gas spring
  • pressure sensors can be connected which, for example, trigger an alarm when the value falls below a target value.
  • the bolt 24, which acts as a locking element which can be actuated in the axial direction can be modified in various ways.
  • he himself can carry the pin 28, while the groove 25, 26 is incorporated in the bearing sleeve 28 '(which carries the pin 28 in the illustration of FIGS. 2 and 3).
  • the bolt 24 is formed in two parts, the front part 23a of reduced diameter being the piston rod of a piston which can be displaced in a cylinder 24 and acted upon fluidically.
  • the piston rod 23a can carry a guide projection corresponding to the pin 28 and can be rotated by a groove 25, 26 formed in the cylinder 24, so that no further unit 29, 30 is then required.
  • connection for the line system 45 to 50 on the pressure unit 37 or 137 may have an additional valve (not shown) in order to be able to close off the respective unit after supplying it with pressure medium, but the valves 48, 49 can also be directly on the pressure unit unit 37 and 137, respectively, so that there is a coupling connection for lines 45 and 50.
  • the check valve 48 could be provided on the pressure unit 137 and this a coupling for the optional connection of, e.g. branched connection of e.g. have branched pressure line in which the valve 49 and (e.g. in a parallel branch) the pump 47 are provided.
  • the mold 9 similar to the embodiment according to FIG. 3, has an inclined surface 36.
  • this inclined surface 36 on the side of the mold carrier 10 is opposite an inclined surface 133 on an insert part 120.
  • the mold carrier 10 itself could have the inclined surface 133 instead of an insert part 120, but the use of an insert part 120 is preferable because it is easier to replace in the event of wear and tear.
  • the insert 120 is screwed onto the mold carrier 10 with the aid of screw bolts 135. It should be noted here that these bolts 135 do not normally need to be loosened when the shape is changed.
  • the insert part 120 is also characterized in that it is equipped with a, preferably multi-start, thread 52.
  • the mold 9 carries a threaded ring 54 which is screwed onto it with the aid of screws 53.
  • the mold 9 is equipped with corresponding screw holes 55 on both end faces.
  • the press mold When changing the shape, the press mold only needs to be screwed into the thread 52 with its threaded ring 54, the inclined surfaces 36, 133 ensuring a tight fit.
  • the threaded ring 54 could possibly itself be part of the compression mold 9.
  • the two threads 52, 54 are designed to be self-locking. It should also be mentioned that the screw holes 55 are arranged approximately in the middle of the thickness of the die 9, since the stresses are lowest there during operation.
  • the symmetrical design with screw holes 55 on both ends of the mold 9 also has the advantage that the mold carrier 10 is removed turned threaded holes, a reinforcement ring, which is usually attached to the front, can be screwed into the same screw holes 55.
  • the thread is expediently designed such that it is rotated in the normal direction of rotation of the mold carrier 10 in the sense of being screwed in, it may tighten too much during operation, so that the loosening of this threaded connection can be difficult.
  • Various designs for facilitating rotary fastening via threads or for loosening them with the aid of servo-actuating devices will now be discussed with reference to FIGS. 9 to 16A, i.e. So devices that allow twisting of the threaded parts to be achieved with minimal effort, even if they are seized.
  • the V-belt wheel 17 already mentioned has two conical coupling recesses 56, 57 in its interior, each of which has a coupling cone 58 or 59 opposite it. While the cone 58 is axially displaceable and rotatably connected to the motor shaft 60 of the drive motor 16, the cone 59 sits on an output shaft 61 of a reduction gear 62, which receives its drive from an auxiliary motor 63. The cone 59 is also connected to the output shaft 61 in a rotationally locking but axially displaceable manner.
  • Both cones 58, 59 are adjustable by a common actuating device 64, so that only one of the two cones 58, 59 can be coupled to the V-belt wheel 17.
  • two moving coil magnets 65, 66 can serve as the adjustment drive.
  • the reduction gear 62 With the help of the reduction gear 62, a strong reduction of at least one order of magnitude, preferably at least two, can be achieved, the speed ratio being approximately 1: 200, for example. It would be conceivable to achieve such a speed difference with purely electrical means, for example by using additional windings, by a DC motor with appropriate control for at least two speeds or the like.
  • the interposition of a reduction gear 62 is the structurally simpler way. It would be possible per se to design the reduction gear 62 in such a way that it can optionally be driven by the drive motor motor 16, so that the auxiliary motor 63 is saved. However, this would require greater gear expenditure than could be saved, which is why the auxiliary motor 63 is preferred.
  • the thread 52, 54 (FIG. 8) is now preferably designed such that a rotation between 15 "and 100" is sufficient to tighten the mold 9 on its mold carrier 10. Therefore, if the auxiliary motor 63 is switched on in order to rotate the mold carrier 10 at reduced speed, it is advantageous if an automatic shutdown takes place as soon as the mold 9 is fastened to the mold carrier 10. In the circuit according to FIG. 9, this is solved in different ways.
  • One possibility is to provide a light source 67 for illuminating the outer circumference of the mold carrier 10.
  • the arrangement is such that the light beam strikes the area in which the holes 14 are provided, which then simultaneously serve as markings. It goes without saying that any other marking can of course also be provided. If the light beam now falls on the outer circumference of the mold carrier 10, it is reflected against a photocell 68. On the other hand, if there is a hole 14, there will be no reflection. This means that the output signal of the photocell 68 is interrupted at each hole 14.
  • a pulley 69 is pivotally mounted about an axis 70 and, for mounting the press mold 9, supports the same on a hook 71 at the correct height.
  • the mold carrier 10 is now set such that the light beam from the light source 67 is directed straight toward a hole 14, the auxiliary motor 63 cannot be excited even when a selector switch 72 is moved from the position shown in broken lines to the position shown in full lines is set.
  • This selector switch 72 is in the circuit of a pulse shaper stage 73 to which a feed stage 74 is connected.
  • the auxiliary motor 63 is not only supplied with current via the feed stage 74, but the direction of rotation can also be selected with the aid of a switch 75.
  • the line coming from the pulse shaping stage 73 forms the Control line for the feed stage 74.
  • the reversing device 74 can also be designed purely mechanically, ie as a reversing gear.
  • a switch S1 As a result of which the photocell 68 is bridged until it again receives reflected light from the outer surface of the mold carrier 10.
  • the time constant of the pulse shaper 73 is dimensioned accordingly.
  • the moving coil magnets 65, 66 are excited to such an extent that the coupling cone 59 enters the coupling recesses 57, whereas the coupling cone 58 disengages.
  • An interrupter 76 may be provided so that the magnet 65 cannot be energized by mistake. This interrupter 76 is parallel to a control line for controlling a stage 174 similar to the feed stage 74 for the drive motor 16.
  • the selector switch 72 can also be connected to a terminal 77, which is located at the output of a counter Z.
  • the control is time-dependent, i.e. as soon as the counter Z has received a predetermined number of pulses from a pulse generator 78, a switch-off signal occurs via the pulse shaping stage 73.
  • the operation of the auxiliary motor 63 is either interrupted if a positioning error occurs, or if the mold 9 is screwed tightly to the mold carrier 10, in which case the mold 9 is also located gives a torque.
  • the selector switch 72 must be set to the terminal 82, which is decoupled from the terminal 81 via a valve circuit (diode D), so that the photocell at the terminal 81 is ineffective. Since the terminal 82 is controlled via a gate circuit 83, the auxiliary motor 63 can only run if the photocell 68 emits a signal and the strain gauge 79 remains fault-free.
  • a simplified circuit could also be designed such that the auxiliary motor 63 is only switched on and off manually by means of the pushbutton switch S1. In this case, the further parts 67 to 73 of the circuit shown in FIG. 9 are unnecessary.
  • the circuit is designed, it is preferable to provide a corresponding device Z, 68 or 79 by which the end of the screwing process is indicated. It goes without saying that the direction of rotation of the auxiliary motor 63 is reversed by switching the lever 75, so that in this way the mold 9 can also be released from the mold carrier 10 with the aid of the motor force.
  • FIGS. 10 to 12 come into question.
  • an insert ring 220 which supports the inclined surface 133, but a threaded ring 152 separate from this insert ring 220 is arranged.
  • the threaded ring 152 has on its outside a toothed ring, into which a pinion 84 engages and can be driven by means of a socket wrench to release the threaded connection on the back of the mold carrier 10.
  • the solution according to FIG. 11 is similar, but the threaded ring 252 has on its outside a worm toothing in which a worm 85 engages approximately tangentially and has a connection for a socket wrench 10 on the outside of the mold carrier 10.
  • FIG. 12 is even simpler, in which an external threaded ring 352 has a notch recess 86 on its radially outer side.
  • a screw bolt 87 which is inserted approximately tangentially on the outer circumference of the mold carrier 10 and protrudes into this notch recess, the threaded ring 352 being rotated counterclockwise when it rotates within a recess 88. In this way, an excessively tight thread can be easily loosened.
  • FIG. 13 shows a pellet press in a view from the front, wherein the mold carrier 10 has threaded segments 89 located at an angular distance from one another.
  • the mold 9 preferably has an uninterrupted Ge windering, although the reverse arrangement (mold with thread segments and mold carrier with full thread) or an arrangement in which the mold also has 9 thread segments would also be conceivable, so that the mold does not have to be screwed into the mold carrier, but rather only inserted with offset thread segments and then rotated approximately by the radian measure of the thread segments.
  • Such closures are known, for example, from artillery and have proven themselves there in view of their particularly high robustness and durability. In any case, temperature and vibration loads also occur with artillery breeches.
  • the compression mold 9 has a threaded ring 54 which is expediently connected to the same via screws 53, although it could also be designed in one piece.
  • the mold carrier 10 has, for example, a ring 90 which is provided with the threaded segments 89 inserted in the recesses. If necessary, however, the ring 90 can also be formed in several parts, both in the circumferential direction - with non-threaded sections 90b being provided between the threaded segments 89 - and in the axial direction, with an outer part 90a having a conical mating surface which matches the conical mating surface of the press mold 9 cooperates. Therefore, the sections 90b can be fastened with separate screws 98 (FIG. 14), the thread segments 89 (FIG. 15) with screws 91, as will be explained below.
  • FIG. 15 shows the section through a section of the multi-part threaded ring 90 with a threaded segment 89, the threaded segment 89 being held in place by means of screw bolts 91, a sleeve 91 a and plate springs 93.
  • the plate springs permit an elastic displacement of the threaded segment 89 parallel to the axis of the mold carrier 10 if they are either fluidically loaded by means of a cylinder-piston unit 95 (FIG. 16) with the aid of a pusher 94 or by means of a rotary spindle 96 which will be described in detail later (Fig. 16A).
  • the plate springs 93 do not necessarily have to be arranged on the outside of the mold carrier 10, as shown in FIG. 15, but can also be arranged in the mold carrier 10 according to FIG. 15a and provide a direct cushioning of the threaded segment 89, but act in the case 15 shows the springs 93 in the sense of positioning against the cylinder-piston unit 95, in the case of FIG. 15A in the sense of loosening.
  • the cylinder-piston unit 95 shown in FIG. 16 and arranged between two plate spring assemblies 93 according to FIG. 13 is expediently of a similar design, as illustrated in FIG. 5. Above all, it will expediently not be constantly connected to a pressure source, but will only be connected to such a pressure source when the mold carrier 10 is at a standstill to release the mold 9.
  • the threaded segment 89 is moved via pushers 94 in a manner similar to that according to FIG. 16.
  • a single rotary spindle 56 shown or a cylinder-piston unit 95 can suffice.
  • a plurality of rotating spindles 96 are distributed over the circumference of the mold carrier 10, these can be actuated jointly by a chain 97 and chain wheels 99.
  • a plurality of cylinder-piston units 95 can also be connected to one another via fluid lines.
  • the axially elastic fastening of the thread or the thread segments 89 to the mold carrier 10 can also be realized without the devices 95 or 96, in which case the pusher 94 can be made by hand, for example by means of a corresponding one Tool to be operated (see FIG. 15A).
  • the pusher 94 can be made by hand, for example by means of a corresponding one Tool to be operated (see FIG. 15A).
  • an analogous effect could of course be achieved by an elastic fastening of the threaded ring 54 to the compression mold 9, but the elastic displacement in the axial direction will usually be more difficult to achieve there, which is why the elastic fastening of the thread on the support side is preferred on its own.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Moulds For Moulding Plastics Or The Like (AREA)
  • Mechanical Treatment Of Semiconductor (AREA)
  • Saccharide Compounds (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
  • Processing And Handling Of Plastics And Other Materials For Molding In General (AREA)
  • Massaging Devices (AREA)
  • Earth Drilling (AREA)
  • Formation And Processing Of Food Products (AREA)
  • Meat, Egg Or Seafood Products (AREA)
  • General Preparation And Processing Of Foods (AREA)

Claims (10)

1. Presse à granuler avec une matrice de compression (9) cylindrique creuse présentant des alésages (9b) essentiellement radiaux, sur la surface périphérique interne de laquelle est disposé de manière à pouvoir rouler par rapport à elle au moins un cylindre de compression (9a) excentrique et qui présente ou porte sur une région terminale axiale une surface de rotation externe (36, 44) qui peut être insérée dans une surface de rotation interne correspondante (33, 34) d'un support de matrice logé de manière à pouvoir exercer une rotation et fixé par adhérence à un entraînement et est fixée par un dispositif de retenue de manière amovible caractérisée en ce que le dispositif de retenue (18-26; 43, 44; 52, 54) est composé de deux parties: l'une d'elles (18-22, 44, 54) est prévue sur la matrice (9) et l'autre (23-26; 43,52) sur le support de matrice (10), cette dernière pouvant être amenée d'une position de repos dans laquelle l'insertion de la matrice (9) en direction axiale dans la surface de rotation interne (21, 33) du support de matrice (10) est possible en une position de travail dans laquelle les deux parties sont en prise de transmission de force l'une avec l'autre et la matrice peut être amenée par un dispositif produisant cette force (27; 29-32; 52) dans une position de serrage dans laquelle la matrice (9) est centrée au moyen d'un dispositif de centrage (33,34; 133,30;44,121) dans le support de matrice (10), les deux parties pouvant judicieusement être détachées l'une de l'autre d'un engagement à crabot au moyen d'un dispositif de détachement (29-32; 84,152; 85,252; 86-88; 94-96) et en ce que le dispositif de retenue présente de préférence au moins un des groupes de caractéristiques suivants:
a) au moins un organe de blocage hydrauliquement actionnable en direction essentiellement radiale, p. ex. une membrane (43), qui peut être appliqué contre la surface de rotation externe (44) de la matrice (9) est prévu directement ou indirectement dans le support de matrice (10) sur la surface de rotation interne;
b) la matrice (9) est pourvue d'au moins un orifice en contre-dépouille (22) sur au moins une de ses faces frontales et un organe de blocage (23a) entrant en prise dans cet orifice (22) peut subir une rotation avec une surface de prise (23) formant un angle par rapport à son axe longitudinal au moyen d'un dispositif de commande (25-32), en particulier hydraulique, d'un angle prédéterminé, dans lequel la surface de prise (23) saisit la contre-dépouille de l'orifice (22);
(c) des filets (52) concentriques entrant en prise l'un dans l'autre, en particulier auto- bloquants, sont prévus directement ou indirectement sur le support de matrice (10) et la matrice (9).
2. Presse à granuler selon la revendication 1 caractérisée en ce que les organes de blocage (23a, 24, 43) actionnables hydrauliquement en direction axiale et/ou radiale sont conçus en s'appliquant partiellement à la périphérie de la matrice.
3. Presse à granuler selon la revendication 1 ou 2 caractérisée en ce qu'au moins un accumulateur de pression (137) est prévu dans la conduite hydraulique pour les organes de blocage.
4. Presse à granuler selon la revendication 1, 2 ou 3 caractérisée en ce qu'au moins un dispositif de commande hydraulique avec un ensemble piston-cylindre (29, 30) est affecté au dispositif de retenue, par lequel peut être commandé un poinçon séparé (23a; 31) avec piston (30) qui est disposé dans un cylindre hydraulique (29) et/ou
en ce que l'organe de blocage (23a, 24; 43) actionnable hydrauliquement dans une direction de commande est poussé dans l'autre direction par au moins un dispositif à ressort, en particulier mécanique, par exemple, par des ressorts à disques (27), de préférence en direction de la position de retenue.
5. Presse à granuler selon une des revendications 1 à 4 caractérisée en ce que la surface de rotation externe (36) de la matrice (9) est conçue en forme de cône qui peut être introduit dans un contre-cône (33) du support de la matrice (10) formant la surface de rotation interne (33; 133), éventuellement logé dans le support comme bague séparée.
6. Presse à granuler selon une des revendications 1 à 5 caractérisée en ce que l'organe de blocage respectivement actionnable radialement est conçu comme une membrane (43) à presser contre la surface de rotation externe (44) de la matrice (9).
7. Presse à granuler selon une des revendications 1 à 6 caractérisée en ce qu'au moins un organe de blocage (23, 24) pouvant exercer une rotation d'un angle prédéterminé, en particulier tous ces organes, présente au moins une des caractéristiques suivantes:
(a) une tête (23) essentiellement rectangulaire s'étendant de part et d'autre de l'axe,
(b) un dispositif de commande pour le mouvement axial lui est affecté, son mouvement rotatif étant assuré par l'intermédiaire d'un entraînement rotatif (25, 28);
l'entraînement rotatif présentant de préférence une saillie, en particulier une goupille (28), p. ex. sur le piston (23a) qui peut être guidée dans une rainure filetée (25), p. ex. dans un cylindre de guidage (24) et la rainure (25) présente judicieusement à ses deux extrémités des encoches, en particulier des pièces d'extrémité (26) s'étendant parallèlement par rapport à la direction de l'axe.
8. Presse à granuler selon une des revendications 1 à 7 caractérisée en ce qu'une majorité d'orifices en contre-dépouille (22) sont répartis sur la face frontale de la matrice (9), en particulier sont conçus sur un rail (18) circonférentiel fixé à la matrice qui peut être inséré dans une cavité (21) correspondante du support.
9. Presse à granuler selon une des revendications 1 à 8 caractérisée en ce que les caractéristiques suivantes sont prévues pour le filet sur le support de matrice (10) et la matrice (9):
a) la position de blocage peut être atteinte lors d'une rotation relative des pièces filetées de 15 à 100 ° ,
b) le filet est conique,
c) le filet est multiple,
d) des segments filetés (89) espacés l'un de l'autre par rapport à la circonférence sont prévus sur la matrice (9) et/ou le support de matrice (10), de préférence sur ce dernier, le nombre de segments filetés (89) étant de préférence égal au nombre de tours du filet multiple,
e) le filet de la matrice (9) et/ou du support de matrice (10), de préférence de ce dernier, est fixé de façon élastique en direction axiale, en particulier par l'intermédiaire de ressorts à disques (93),
f) il est prévu au moins une bague filetée (54) qui est fixée avec la matrice (9) ou le support de matrice (10), de préférence avec la première, de manière amovible, en particulier par des vis (53, 135),
g) le sens de rotation de travail du support de matrice (10) est choisi dans le sens de vissage du filet,
h) la matrice (9) peut être fixée avec un dispositif de levage, p. ex. un palan, qui présente un dispositif de mesure de la pression, p. ex. une jauge extensométrique, par lequel un servomoteur de filetage (63) peut être commandé pour une rotation relative des éléments filetés,
i) le filet intérieur du support de matrice (10) prévu sur une bague filetée (152; 252) est pourvu à l'extérieur au moins d'une denture partielle par laquelle la bague filetée (152) logée dans le support de matrice (10) de manière à pouvoir exercer une rotation, au moins partielle, peut être entraînée en rotation (fig. 10, 11), un pignon (84) ou une vis sans fin (85) entrant judicieusement en prise dans les dents de la bague filetée (152),
k) le filet intérieur du support de matrice (10) prévu sur une bague filetée (352) logée de manière à pouvoir exercer une rotation, au moins partielle, présente au moins une cavité périphérique (88) qui s'étend parallèlement par rapport à une tangente sur la bague filetée contre laquelle peut s'appuyer un poussoir, en particulier un boulon fileté (87) (fig. 12),
I) le filet intérieur du support de matrice (10) conçu sur une bague filetée (90) est logé avec du jeu axial dans le support de matrice (10) éventuellement de manière à pouvoir exercer une rotation partielle, la bague filetée (90) étant judicieusement maintenue par des boulons filetés (91, 92), de préférence de façon élastique, en particulier par des ressorts à disques (93) sur le support de matrice (10) et/ou la bague filetée (90) pouvant être poussée par au moins un poussoir (94) en direction axiale qui peut être actionné p.ex. par au moins un ensemble cylindre-piston (95) ou par au moins une broche de rotation (96), plusieurs poussoirs (94) pouvant en particulier être répartis sur la circonférence et pouvant éventuellement être actionnés ensemble, p. ex. par une chaîne (97).
10. Presse à granuler selon une des revendications 1 à 9 caractérisée en ce qu'un dispositif de servocommande (62, 63; 84; 85; 87) est prévu pour le desserrage et/ou le dévissage du filet (52, 54; 152; 252; 89) et en ce que l'entraînement de la presse (16, 63) sert de préférence lui-même de dispositif de servocommande (62, 63; 84; 85; 87) et peut être commuté sur au moins deux vitesses différentes d'au moins une dimension, de préférence d'au moins ses deux dimensions pour le mouvement de vissage du filet de la matrice (9) ou du support de matrice (10) à l'aide d'un dispositif de commutation (56-66) et/ou
possède un dispositif d'inversion du sens de rotation (74),
au moins une des caractéristiques suivantes étant judicieusement prévue:
a) un moteur d'entraînement (16) pour l'entraînement direct de son arbre à partir ou par l'intermédiaire d'un engrenage démultiplicateur (62) peut être fixé avec le support de matrice (10) par l'intermédiaire d'un couplage (56, 57) au choix, un moteur auxiliaire (63) étant en particulier affecté à l'engrenage démultiplicateur (62),
b) à l'entraînement (63) est fixé un capteur de position (14, 67, 68) par lequel l'entraînement (63) peut être commuté pour le vissage de la matrice (9) au support de matrice (10) pour un rotation angulaire prédéterminée,
une source de rayonnement, en particulier une source lumineuse, qui est orientée contre une partie circonférentielle du support de matrice (10), p. ex. dans la région des trous (14) ou d'un repère étant de préférence prévue et un détecteur (68), p. ex. une cellule photoélectrique, étant alimenté par le rayon réfléchi, détecteur qui commande le ou les moteurs et, éventuellement, le mouvement d'un élément de couplage (56, 57) et peut éventuellement être ponté par un commutateur S1.
EP88120319A 1987-12-18 1988-12-06 Presse à briquettes Expired - Lifetime EP0320747B2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88120319T ATE80340T1 (de) 1987-12-18 1988-12-06 Pelletpresse.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873743037 DE3743037A1 (de) 1987-12-18 1987-12-18 Pelletpresse
DE3743037 1987-12-18

Publications (4)

Publication Number Publication Date
EP0320747A2 EP0320747A2 (fr) 1989-06-21
EP0320747A3 EP0320747A3 (en) 1990-09-19
EP0320747B1 true EP0320747B1 (fr) 1992-09-09
EP0320747B2 EP0320747B2 (fr) 1996-05-08

Family

ID=6342963

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88120319A Expired - Lifetime EP0320747B2 (fr) 1987-12-18 1988-12-06 Presse à briquettes

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US (1) US4979887A (fr)
EP (1) EP0320747B2 (fr)
AT (1) ATE80340T1 (fr)
DE (2) DE3743037A1 (fr)
ES (1) ES2035232T3 (fr)
GR (1) GR3005668T3 (fr)

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Also Published As

Publication number Publication date
ATE80340T1 (de) 1992-09-15
DE3743037A1 (de) 1989-06-29
ES2035232T3 (es) 1993-04-16
DE3874501D1 (de) 1992-10-15
EP0320747A3 (en) 1990-09-19
US4979887A (en) 1990-12-25
EP0320747B2 (fr) 1996-05-08
GR3005668T3 (en) 1993-06-07
EP0320747A2 (fr) 1989-06-21

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