EP0272957B1 - Automatische Maschine zum Feststampfen von Kohlenkuchen zum Verkoken - Google Patents

Automatische Maschine zum Feststampfen von Kohlenkuchen zum Verkoken Download PDF

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Publication number
EP0272957B1
EP0272957B1 EP87402589A EP87402589A EP0272957B1 EP 0272957 B1 EP0272957 B1 EP 0272957B1 EP 87402589 A EP87402589 A EP 87402589A EP 87402589 A EP87402589 A EP 87402589A EP 0272957 B1 EP0272957 B1 EP 0272957B1
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EP
European Patent Office
Prior art keywords
stamping
stamper
machine
elementary
machine according
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Expired - Lifetime
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EP87402589A
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English (en)
French (fr)
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EP0272957A1 (de
Inventor
Robert Baro
Louis Crauser
André Mely
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Charbonnages de France CDF
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Charbonnages de France CDF
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Priority claimed from FR8616477A external-priority patent/FR2607064B1/fr
Priority claimed from FR8616478A external-priority patent/FR2607065B1/fr
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Publication of EP0272957A1 publication Critical patent/EP0272957A1/de
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    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10B—DESTRUCTIVE DISTILLATION OF CARBONACEOUS MATERIALS FOR PRODUCTION OF GAS, COKE, TAR, OR SIMILAR MATERIALS
    • C10B45/00—Other details
    • C10B45/02—Devices for producing compact unified coal charges outside the oven
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B21J7/36—Drives for hammers; Transmission means therefor for drop hammers

Definitions

  • the invention relates to a machine for automatically pounding coal mixtures (possibly with other constituents) to prepare pounded coal bars which are then placed in a coke oven to be transformed into coke.
  • Machines of this type are already known, the role of which is to pack a mixture of coals in a mold also called pounding box.
  • the mixture of fine charcoal is poured into the mold through the upper part of the latter and it is compacted by at least one pestle which has a pounding sole and which is constantly lifted and left in free fall on the coal to be compacted.
  • the box has a small width to which is substantially equal to that of the pounding sole of each pestle; the ramming box has a significant length.
  • Each movement corresponds to a ramming stroke which is approximately equal to the dimension of the soles of the drumsticks in the direction of movement.
  • Each pestle comprises a vertically disposed profile having a core which is covered on both sides with a lining with a high coefficient of friction; this core is contained on the one hand between two opposite eccentrics driven in rotation of a lifting device and on the other hand between two opposing elements of a braking and retaining device.
  • each pestle is rotated by a gear transmission made from the output shaft of a speed reducer itself coupled in rotation with an electric motor.
  • the main object of the invention is to provide a pounding machine of new design with which the duration of the pounding is significantly reduced; in addition, although the shelling is carried out in a shorter time, the invention has the secondary aim of improving the quality of the shelling, in particular the homogeneity and the density of the shelling.
  • a further object of the invention is to achieve a robust and simple design which reduces the costs of production and maintenance of the pounding machine and which allows complete automation of the pounding operation.
  • Another object of the invention is to equip the machine defined above with a braking and retaining device for the drumsticks which is simpler in its design and more economical in its operation than the known conventional means.
  • the braking device of each pestle has as opposing braking elements two jaws opposite one another which contain between them the core of the profile of said pestle.
  • the eccentrics Since the eccentrics generally rotate at the speed of one revolution per second, there is a difficulty in coordinating with their movements the closing and opening movements of the brake shoes. In addition, it is preferable that the jaws close on the soul of the pestle just when the speed of this upward pestle goes to zero before it begins to descend. For various reasons which depend, among other things, on friction and wear, the eccentrics do not always launch the pestle upwards at an always equal speed. For this reason, the time which elapses after the moment when the eccentrics have ceased to tighten the pestle between them and the moment when the speed ends up canceling out is a variable time.
  • the state of the art can be illustrated by the document FR-A-2 339 665 in which there is described a device for immobilizing the pestles of a coking plant rammer in the raised position.
  • This device is composed of two sectors with an angular extent of approximately 50 °, placed on either side of the core of the profile forming part of each pestle, with an eccentric non-tangential position; thus, these two sectors when they are applied together against the core are attracted by the latter in a direction tending to bring them together and to wedge between them this core, preventing it from descending further under the effect of gravity.
  • Each sector is associated with a toothed segment; these toothed segments mesh together and one of them is propped up on a maneuverable shaft in rotation using a jack, which requires good coordination, difficult to carry out and to keep over time, of the control of this cylinder and eccentrics of launching up the cylinders, as said above.
  • Another document FR-A-2 340 363 describes a flow device in which the pestles are distributed over three pestle-carrying carts coupled together to form a mobile assembly. This assembly is moved alternately in the direction of the length of the ramming box by a jack having a stroke, the importance of which is determined from the width of the sole of the drumsticks and the distance which separates the soles of two neighboring drumsticks d 'one cart. However, if the distance between successive drumsticks is constant on each carriage, the distance which separates the drumsticks closest to each other from two successive carriages has a greater value.
  • the two opposing rollers are carried by two levers at a first end thereof, and the second opposite end of the same levers is subjected to the effect of a tightening member which tends, during the use of the device , clamping said rollers against the core of the pestle.
  • said clamping member is joined at each second end of the two levers and it acts simultaneously on them in opposite directions.
  • the second end part of one of the levers is offset relative to the other lever by means of a bar terminated by an end part parallel to this other lever and the tightening member is an elastomer tensioner which tends bringing said end part and the other lever towards each other to apply the rollers against the core of the pestle.
  • a jack is coupled parallel to the tightening tensioner between the second end of the lever and the end part of the bar, the extension of this jack having the effect of rendering the rollers inoperative.
  • the profile of each pestle is provided with at least one detectable mark, preferably with several detectable marks spaced in the direction of its length, and there are corresponding detection sensors which are connected to a central monitoring device.
  • the main characteristic of the invention defined above is advantageously usable on a machine mounted movable in alternating directions along the longitudinal dimension (L) of the ramming box, with a displacement travel of value (C) considerably less than the length (L) of the box, this machine being additionally equipped with a displacement motor member capable of imposing on it in the direction of the length of the box, alternative movements over said displacement stroke (C), the distance (E1) and the second dimension (L2) of the soles being determined as a function of the value of said stroke (C) so that satisfactory recovery of the effect of the soles of the drumsticks occurs during said reciprocating movements;
  • a machine is characterized according to the invention in that it is composed of several elementary rammers each comprising a chassis mounted on wheels extending in transverse direction to the ramming box and bearing on at least one assembly line at least one pestle and its operating members, these rammers being coupled to each other to form a pounding train constituting a ramming machine, the assembly lines being spaced apart by a distance substantially
  • each elementary rammer is equipped with several pestles and the eccentrics of these pestles are mounted respectively on two common shafts each supported by the chassis by means of several bearings, these two shafts being connected one to the other by rotating transmission means and one of them being rotatably coupled to the output shaft of a speed reducer having an input shaft operatively connected to the output shaft of an engine mounted on the chassis.
  • each elementary rammer has a recess on a transverse side and the following elementary rammer has on a transverse side of its frame a projection of complementary profile engaging in said recess.
  • the output shaft of the speed reducer is a hollow shaft and the end part of the corresponding common shaft is engaged in said hollow shaft in relation to the transmission of the torque.
  • the displacement stroke (C) has a value which is substantially equal to half the distance (E1) while the second dimension (L2) of the sole of the drumsticks has a value which is substantially equal to half of the distance (E1).
  • the pounding is composed of four elementary rammers 1 which consequently have a length equal to a quarter of the length of the ramming box after deduction of a ramming stroke as will be explained below.
  • Each elementary rammer 1 has a robust chassis 2 mounted on wheels, preferably bogies 3, which make it possible to circulate it on rails supported above the upper level of the ramming box in the direction of the length of the latter.
  • the chassis 2 has, in a known and current manner, a width in the direction transverse to the ramming box which is greater than the width of this box, which makes it possible to install various equipment there.
  • a width in the direction transverse to the ramming box which is greater than the width of this box, which makes it possible to install various equipment there.
  • the chassis 2 supports a platform 4 which is partially broken away in FIG. 1 to reveal the bogies 3.
  • On this platform there are assembly lines 5A, 5B, 5C, 5D represented by dashed lines in the figures. These assembly lines 5A to 5D are parallel and arranged transversely to the length of the ramming box when the elementary rammer 1 is placed above the latter. These lines 5A to 5D are equidistant from each other and separated by a distance E1.
  • a pestle 6, of any suitable type known per se and which it is not necessary to describe.
  • each pestle 6 is of a type in which a vertical section 7 in I is provided at its lower end with a pounding sole (not visible in FIG. 1) which has a first dimension in transverse direction to the shelling box of substantially equal value, slightly lower as usual, to the interior width of the box.
  • the sole In the longitudinal direction of the latter the sole has a second dimension which is, in this particular case, substantially equal to half the distance E1 which separates two successive drumsticks 6.
  • Each vertical section 7 is maneuvered in the vertical direction by two opposite eccentrics 8, 9 which contain between them the core of this section 7.
  • the eccentrics of all the pestles 6 are mounted on a common shaft, respectively 10 for the eccentrics 8, and 11 for the eccentrics 9.
  • These two shafts 10, 11 extend in the longitudinal direction of the ramming box, in parallel with a side and other of the profiles 7. They are supported by several spaced bearings 12A, 12B ... and 13A, 13B ... which are themselves supported by the frame 2.
  • the shaft 10 is coupled in rotation with the output shaft 14 of a speed reducer 15.
  • this output shaft 14 is a hollow shaft into which the common shaft 10 penetrates through its end portion to produce a coupling in rotation.
  • the input shaft 16 of the reducer 15 carries a pulley 17 which is connected by a belt to the pulley 18 of the shaft of a motor 19.
  • the latter can also be installed on the platform 4, or below the latter in the chassis 2.
  • the common shaft 10 and the common shaft 11 are each provided with a toothed wheel 20, 21 respectively. These two wheels are equal and mesh together; thus a single motor 19 drives in synchronism the two common shafts 10, 11 and the set of eccentrics 8, 9 of all the pestles 7 of the elementary rammer 1.
  • this elementary rammer 1 has a length which is approximately a quarter of the length of the ramming box and it is equipped with four pestles 7 spaced apart. There therefore exists, so that the entire length of the box can be covered by the ramming machine, four successive rammers which are coupled to each other so that they can be moved together in the lengthwise direction of the ramming box.
  • Figure 1 shows a first elementary rammer 1 and only part of the second elementary rammer 1 ⁇ ; on this one we find the same organs as on the elementary rammer 1 designated by the same reference numbers with the index ⁇ .
  • a recess 22 with a trapezoidal profile in top view, in a transverse side of the frame 2 of an rammer and a corresponding complementary projection 23 of the same profile on the transverse side of the chassis 2 ⁇ of the elementary rammer 1 ⁇ which follows.
  • the projection 23 engages in the recess 22 and ensures good centering and better securing of the rammers.
  • the latter are securely attached together by known suitable coupling means not shown.
  • the elementary rammers 1, 1 ⁇ coupled to each other, constitute a rammer train which is the machine of the invention.
  • the latter is easily displaceable in its entirety thanks to the bogies 3.
  • a drive member such as a jack, not visible in FIG. 1, is articulated on the one hand on a fixed point external to the ramming machine, on the other hand on one of the elementary rammers, for example on the rammer 1.
  • This member is constructed and controlled, in a known manner, in order to impose on the pounding machine alternative movements of displacement in the longitudinal direction of the ramming box. These back and forth movements take place over a race (distance between the opposite extreme points) which is determined as a function of the distance E1 and of the second dimension of the sole of each pestle.
  • FIG. 2 schematically shows a pounding machine composed of four elementary rammers 1, 1 ⁇ , 1 ⁇ , 1 ′′′ coupled together on each of which there are four pestles located on four assembly lines 5A, 5B, 5C, 5D. These lines are separated by a distance E1 with a value of 785 mm; the distance E2 between the two successive assembly lines 5D and 5A ⁇ of two elementary rammers which follow one another has a value of 790 mm. A difference of 5 mm is quite tolerable. There is shown in phantom on the elementary rammer 1 ⁇ the sole of two pestles whose second dimension l2 is equal to about half of the distance E1.
  • the total length of the ramming machine is less than the length of the ramming box designated by the letter L (12.630 mm).
  • the difference is due to a clearance ⁇ which is necessary at the two ends and to a distance C which represents the alternative stroke which the drive member can give to the machine, during the operation of the drumsticks, inside the box of shelling.
  • the stroke C is 400 mm, that is to say a little more than half of the distance E1. Consequently, the coal is pounded over the entire length of the pounding box (12,630 mm), with the exception of the end parts which correspond to the clearance ⁇ , following a simple reciprocating movement over a distance C of 400 mm.
  • Automatic control includes for each movement on race C an acceleration phase, a constant speed phase and a deceleration phase.
  • the soles of the drumsticks can have a second dimension which is almost equal, apart from the clearance which must remain between two neighboring soles, at the distance E1.
  • the shelling machine is made with a chassis in one piece of the specified total length
  • the one where it is composed of several rammers coupled elementary it could be motorized to move by itself along the ramming stroke without external displacement cylinder.
  • FIGS. 3 and 4 describe the braking and retaining device for each of the drumsticks.
  • This device is not visible in Figure 1. It is mounted above the robust chassis 2, preferably it is installed above a small platform 24 which allows easy access to the parts of this device .
  • This platform 24 is itself supported by vertical uprights (not shown) which bear on the frame 2.
  • each pestle 6 is arranged vertically between two pairs of guide rollers 25,26 spaced vertically.
  • the core 27 of the vertical profile 7 passes between a pair 28 of two rollers mounted in opposition 28A, 28B which form part of the braking device.
  • the latter is designated by the general reference 29.
  • Each roller 28A, 28B is of the type with free wheel in one direction of rotation and with locking means in opposite direction, well known per se. The free rotation takes place during the rise of the pestle.
  • Each roller 28A, 28B is mounted free on a respective shaft 30A, 30B so as to be contained between the wings of the profile 7 and to be able to be pressed against a friction lining 31 which covers each of the faces of the core 27.
  • a set roller 28A-shaft 30A is mounted at a first end which is here the lower end of a lever 32; the latter is pivotally mounted about a horizontal axis 33 supported from the platform 24 and it extends vertically to end in a second end or upper end.
  • the other roller assembly 28B-shaft 30B is similarly mounted at a first end or lower end of a lever 34 also mounted pivoting about a horizontal axis 35 also supported from the platform 24.
  • This lever 34 extends vertically up to 'at a second end or upper end to which a horizontal bar 36 is firmly fixed.
  • the latter is offset relative to the pestle 6 so as not to hinder the latter.
  • the horizontal bar 36 ends in an extreme vertical part 37 which is parallel to the lever 32 opposite the second end of the latter.
  • the distance between the lever 32 and the vertical end portion 37 of the bar 36 is fixed at the value which is suitable for attaching to these two parts a clamping member which is preferably an elastomer return tensioner or a return spring, shown by a dashed line 38.
  • the arrangement which has just been described is equivalent to displacing the second end part of the lever 34 relative to the lever 32 so that the direction of approach of the ends of these levers is the same as the direction of approach rollers 28A, 28B. More precisely, when the elastic return tensioner 38 tends to bring the lever 32 and the vertical end portion 37 closer to the bar 36, it also tends to constantly apply the rollers 28A and 28 B against the friction lining 31 of the core 27 profile 7.
  • a compressed air cylinder 39 is coupled between the lever 32 and the vertical end portion 37 of the bar 36, parallel to the elastic tensioner 38.
  • this jack 39 When this jack 39 is put in extension it separates the lever 32 and the end portion 38 and, thus , it moves the rollers 28A, 28B away from the core 27 by a distance sufficient for these rollers to become inoperative.
  • Stops 40A, 40B are arranged to respectively limit the movement of the lever 32 and of the lever 34 in order to distribute the spacing of the rollers 28A, 28B equally on either side of the core 27.
  • the jack 39 is put into service in the direction of the extension so that the pestle 6 is completely free to move in the vertical direction under the effect of the eccentric cylinders 8,9. At each rotation, during a fraction of a turn, the latter tighten the core 27 of the pestle 6 and propel the latter upwards then let it fall during the rest of the turn to start again immediately.
  • the jack 39 When the shelling is finished and the pestle 6 must be raised to its highest position or rest position, the jack 39 is put to rest; it leaves free the elastic return tensioner 38 which then constantly clamps the rollers 28A, 28B against the core 27. These two rollers 28A, 28B are mounted so as to be free to rotate in the direction of the rise of the pestle 6 as indicated by arrows F in Figure 4 while the cylinders offset 8.9 cause this pestle to go up.
  • the rollers 28A, 28B simply roll against the friction lining 31 and remain constantly in rolling contact with it. The risk of deterioration is eliminated and wear is minimized.
  • the braking action due to the rollers 28A, 28B is automatic and completely independent of the movement of the eccentric cylinders 8,9; no coordination of movements is necessary.
  • the clamping action of the rollers 28A, 28B against the lining 31 of the core 27, under the effect of the elastic tensioner 38 produces controlled braking which makes it possible to stop the pestle during its fall without brutality.
  • the entire device is simple in its design and construction.
  • the described embodiment is preferred because of its simplicity and its operational safety. It will not depart from the scope of the invention by adopting other equivalent means for controlling the movements of the two rollers 28A, 28Bet the tightening of these rollers against the core 27 of the pestle in order to activate the braking device and of restraint during the rise of the pestle.
  • each of the pestles 6 there are on each of the pestles 6 at least one and preferably several detectable marks 41 to which correspond, on respective supports mounted on the platform 4, detection sensors 42. These sensors 42 are connected to a central monitoring device. In this way it is possible to remotely monitor the proper functioning of each of the pestles and to detect any pestle becoming defective as a result, most often, of the wear of the linings 31 which cover the core 27 of the profile 7.
  • the marks detectable may be plates 41 of stainless steel fixed for example on the outer face of a wing of the section 7 of each pestle 6. These plates 41 are shown only on the two pestles 6 furthest to the left when looking at FIG. 1. It is advantageous to put several plates 41 spaced by a constant pitch in the longitudinal direction of each pestle 6.
  • the sensors 42 for detecting the stainless steel plates 41 are of the non-magnetic type and are known in the trade. this, and need not be described; the same is true for the central surveillance apparatus.

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Claims (11)

  1. Maschine zum Stampfen von zu verkokenden Kohlegemischen in einem Stampfbehälter mit einer Länge (L), umfassend mehrere in Längsrichtung des Behälters mit im wesentlichen konstanten Abständen (E1) angeordnete Stempel, wobei jeder Stempel einen vertikalen Profilstab (7) mit einem Steg hat, ferner umfasend einerseits eine Hebeeinrichtung mit zwei Exzenterhebeeinrichtungen, die den genannten Steg zwischen sich aufnehmen, und andererseits eine Brems- und Halteeinrichtung mit zwei einander entgegenwirkenden Elementen, welche ebenfalls den genannten Steg zwischen sich aufnehmen, wobei jeder vertikale Profilstab (7) auch einen Stampffuß hat, der in Längsrichtung des Stampfbehälters eine zweite Abmessung (L2) hat, dadurch gekennzeichnet, daß die Brems- und Halteeinrichtung jedes Stempels zwei einander gegenüberliegende Rollen (28A, 28B) umfaßt, die nur in einer Drehrichtung drehbar sind, welche der Aufwärtsbewegung des Stempels entspricht und in der Gegenrichtung als Blockiereinrichtung dient, wobei diese Rollen während des Anhebens des Stempels bis zur oberen Totlage vorzugsweise mit gleichgroßen Kräften gegen den Belag (31) der einander abgewandten Seiten des Steges (27) des Stempels (6) angedrückt werden.
  2. Maschine nach Anspruch 1, dadurch gekennzeichnet, daß die beiden einander entgegenwirkenden Rollen (28A, 28B) von zwei Hebeln (32, 34) an einem ersten Ende derselben gehalten werden, während das zweite, diesem abgewandte Ende der jeweiligen Hebel der Wirkung eines Klemmorgans (38) ausgesetzt ist, welches während des Einsatzes der Einrichtung versucht, die genannten Rollen (28A, 28B) gegen den Steg (27) des Stempels (6) anzudrücken.
  3. Maschine nach Anspruch 2, dadurch gekennzeichnet, daß das Klemmorgan (38) jeweils mit dem zweiten Ende der beiden Hebel (32, 34) verbunden ist und auf diese gleichzeitig im entgegengesetzten Sinne einwirkt.
  4. Maschine nach Anspruch 2, dadurch gekennzeichnet, daß der zweite Endbereich eines der Hebel (34) gegenüber dem anderen Hebel (32) mittels einer Stange (36) versetzt ist, welche in einem zu diesem anderen Hebel (32) parallelen Endabschnitt (37) endet, und daß das Klemmorgan (38) ein Spannelement aus einem Elastomer ist, welches versucht, den genannten Endabschnitt (37) und den anderen Hebel (32) einander zu nähern und die Rollen (28A, 28B) gegen den Steg (27) des Stempels (6) anzudrükken.
  5. Maschine nach Anspruch 4, dadurch gekennzeichnet, daß ein Stellzylinder (39) parallel zum Klemm-Spannelement (38) zwischen dem zweiten Ende des Hebels (32) und dem Endabschnitt (37) der Stange (36) angeordnet ist, wobei das Ausfahren des Stellzylinders (39) die Wirkung hat, daß die Rollen (28A, 28B) außer Betrieb gesetzt werden.
  6. Maschine nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß der Profilstab (7) jedes Stempels (6) mit wenigstens einer detektierbaren Markierung (41), vorzugsweise aber mit mehreren in dessen Längsrichtung beabstandeten detektierbaren Markierungen versehen ist, und daß zugeordnete Detektoraufnehmer (42) vorgesehen sind, die mit einer zentralen Überwachungseinrichtung verbunden sind.
  7. Maschine nach einem der Ansprüche 1 bis 6, die in entgegengesetzten Richtungen entlang der Längsausdehnung (L) des Stampfbehälters versetzbar angeordnet ist, mit einem Wert (C) für den Versatzweg, welcher deutlich kleiner als die Länge (L) des Behälters ist, wobei diese Maschine außerdem mit einem Verstellantrieb zum Versetzen ausgestattet ist, welcher dazu dient, diese in Längsrichtung des Behälters auf dem genannten Versatzweg (C) hin- und herzubewegen, wobei ferner der Abstand (E1) und die zweite Abmessung (L2) der Stampffüße in Abhängigkeit vom Wert dieses Weges (C) so festgelegt sind, daß während dieser Hin- und Herbewegungen eine ausreichende Überdeckung der Wirkung der Stampffüße dieser Stempel gegeben ist, dadurch gekennzeichnet, daß sie aus mehreren Grund-Stampfeinheiten (1, 1',1",1"',...) zusammengesetzt ist, die jweils ein auf Rädern stehendes Chassis (2, 2'...) umfassen, das sich quer zum Stampfbehälter erstreckt und auf wenigstens einer Montagelinie (5A, 5B, 5C, 5A'..) wenigstens einen Stempel (6, 6'...) und dessen Betätigungsorgane trägt, wobei die Stampfeinheiten miteinander verbunden und zu einer Stampfreihe zusammengesetzt sind, die die Stampfmaschine bildet, und wobei die Montagelinien (5A, 5B, 5C, 5D, 5A'...) einen Abstand voneinander haben, welcher im wesentlichen zugleich dem Abstand (E1) bei den jeweiligen Grund-Stampfeinheiten sowie dem Abstand zwischen den hintereinanderfolgenden Stampfeinheiten gleich ist.
  8. Maschine nach Anspruch 7, dadurch gekennzeichnet, daß jede Grund-Stampfeinheit (1, 1', 1", 1''') mit mehreren Stempeln (6) ausgestattet ist und daß die Exzentereinrichtungen (8, 9) dieser Stempel auf zwei allen gemeinsamen Wellen (10, 11) angeordnet sind, die jeweils vom Chassis (2) durch mehrere Lager (12A, 12B, 12C) gehalten werden, wobei die beiden Wellen (10, 11) miteinander durch Drehübertragungsmittel (20, 21) verbunden sind und eine von ihnen mit der Ausgangswelle (14) eines Untersetzungsgetriebes (15) gekuppelt ist, dessen Eingangswelle (16) mit der Ausgangswelle eines auf dem Chassis (2) montierten Motors (19) antriebsverbunden ist.
  9. Maschine nach Anspruch 7, dadurch gekennzeichnet, daß das Chassis (2) jeder Grund-Stampfeinheit (1, 1',1', 1''') an einer Querseite eine Ausnehmung (22) hat und daß die daran anschließende Grund-Stampfeinheit an einer Querseite seines Chassis (2') einen Vorsprung (23) mit einem Profil aufweist, welches in die genannte Ausnehmung (22) eingreift.
  10. Maschine nach Anspruch 8, dadurch gekennzeichnet, daß die Ausgangswelle (14) des Untersetzungsgetriebes (15) eine Hohlwelle ist und daß der Endabschnitt der zugeordneten gemeinsamen Welle (10) in die Hohlwelle zur Übertragung des Drehmomentes eingreift.
  11. Maschine nach Anspruch 7, dadurch gekennzeichnet, daß der Versatzweg (C) einen Wert hat, welcher im wesentlichen gleich der Hälfte des Abstandes (E1) ist, und daß die zweite Abmessung (L2) des Stampffußes des Stempels einen Wert hat, welcher im wesentlichen gleich der Hälfte des Abstandes (E1) ist.
EP87402589A 1986-11-26 1987-11-17 Automatische Maschine zum Feststampfen von Kohlenkuchen zum Verkoken Expired - Lifetime EP0272957B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR8616477A FR2607064B1 (fr) 1986-11-26 1986-11-26 Machine automatique a pilonner les pains de charbon a cokefier
FR8616478A FR2607065B1 (fr) 1986-11-26 1986-11-26 Dispositif de freinage et de retenue des pilons dans une pilonneuse de cokerie
FR8616477 1986-11-26
FR8616478 1986-11-26

Publications (2)

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EP0272957A1 EP0272957A1 (de) 1988-06-29
EP0272957B1 true EP0272957B1 (de) 1992-05-13

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EP87402589A Expired - Lifetime EP0272957B1 (de) 1986-11-26 1987-11-17 Automatische Maschine zum Feststampfen von Kohlenkuchen zum Verkoken

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EP (1) EP0272957B1 (de)
CN (2) CN1033917C (de)
DE (1) DE3779076D1 (de)
IN (1) IN170405B (de)
PL (1) PL148488B1 (de)
RU (1) RU1831493C (de)
UA (1) UA12329A (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3910214C1 (en) * 1989-03-30 1990-05-31 Saarbergwerke Ag Automatic stroke monitoring during a ramming operation
CN103820136B (zh) * 2014-03-20 2016-02-03 武汉科技大学 用于实验焦炉料样的捣固设备
CN108285796A (zh) * 2018-03-30 2018-07-17 太原市凯特嘉机械有限公司 一种压浮煤机
CN116694342B (zh) * 2023-08-07 2023-10-03 太原市凯特嘉机械有限公司 一种煤粉捣固机以及煤粉捣固方法

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE284991C (de) *
FR354553A (fr) * 1905-05-23 1905-10-07 Nicolas Et Triquet Soc Pilonneuse
FR518411A (fr) * 1919-03-03 1921-05-26 Julius Urbanek Dispositif de levage de marteaux-pilons
FR2228557A1 (en) * 1973-05-08 1974-12-06 Muller Alfred Forge power hammer for ironworks - uses externally selected programme and has descent governing safety feature
DE2332867A1 (de) * 1973-06-28 1975-01-09 Saarbergwerke Ag Vorrichtung zum verdichten der einsatzmischung eines koksofens
DE2603677C2 (de) * 1976-01-31 1985-09-12 Saarbergwerke AG, 6600 Saarbrücken Einrichtung zum Festhalten von in die Stampfvorrichtung einer Stampfkokerei eingegliederten, angehobenen Stampfern
DE2603954C2 (de) * 1976-02-03 1983-01-13 Saarbergwerke AG, 6600 Saarbrücken Verfahren zum Verdichten von Kokskohle
FR2428667A1 (fr) * 1978-06-16 1980-01-11 Pohlig Heckel Bleichert Dispositif d'agglomeration d'un gateau de charbon destine a l'alimentation d'un four a coke
CN86202094U (zh) * 1986-04-04 1986-11-19 黄荣华 蜂窝煤机用冲针冲头组件

Also Published As

Publication number Publication date
PL148488B1 (en) 1989-10-31
UA12329A (uk) 1996-12-25
DE3779076D1 (de) 1992-06-17
CN1033917C (zh) 1997-01-29
RU1831493C (ru) 1993-07-30
IN170405B (de) 1992-03-21
CN87108045A (zh) 1988-06-08
PL269049A1 (en) 1988-08-18
EP0272957A1 (de) 1988-06-29
CN1074472A (zh) 1993-07-21

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