WO2002045927A1 - Dispositif de compactage pour compacter des corps de produits constitues d'une masse granulee - Google Patents

Dispositif de compactage pour compacter des corps de produits constitues d'une masse granulee Download PDF

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Publication number
WO2002045927A1
WO2002045927A1 PCT/DE2001/004612 DE0104612W WO0245927A1 WO 2002045927 A1 WO2002045927 A1 WO 2002045927A1 DE 0104612 W DE0104612 W DE 0104612W WO 0245927 A1 WO0245927 A1 WO 0245927A1
Authority
WO
WIPO (PCT)
Prior art keywords
frame
mass
spring
forces
springs
Prior art date
Application number
PCT/DE2001/004612
Other languages
German (de)
English (en)
Inventor
Hubert Bald
Original Assignee
GEDIB Ingenieurbüro und Innovationsberatung GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by GEDIB Ingenieurbüro und Innovationsberatung GmbH filed Critical GEDIB Ingenieurbüro und Innovationsberatung GmbH
Publication of WO2002045927A1 publication Critical patent/WO2002045927A1/fr

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Classifications

    • 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
    • B30B11/02—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses using a ram exerting pressure on the material in a moulding space
    • B30B11/022—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses using a ram exerting pressure on the material in a moulding space whereby the material is subjected to vibrations
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B28—WORKING CEMENT, CLAY, OR STONE
    • B28B—SHAPING CLAY OR OTHER CERAMIC COMPOSITIONS; SHAPING SLAG; SHAPING MIXTURES CONTAINING CEMENTITIOUS MATERIAL, e.g. PLASTER
    • B28B3/00—Producing shaped articles from the material by using presses; Presses specially adapted therefor
    • B28B3/02—Producing shaped articles from the material by using presses; Presses specially adapted therefor wherein a ram exerts pressure on the material in a moulding space; Ram heads of special form
    • B28B3/022—Producing shaped articles from the material by using presses; Presses specially adapted therefor wherein a ram exerts pressure on the material in a moulding space; Ram heads of special form combined with vibrating or jolting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0076—Noise or vibration isolation means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides
    • B30B15/041—Guides

Definitions

  • the invention relates to a compacting device for compacting product bodies consisting of granular mass (e.g. made of concrete).
  • the compression is accomplished by introducing essentially harmonic (sinusoidal) vibration forces into the product body to be compressed.
  • the compression device comprises an (upper) press plate and a (lower) vibrating table, between which a product body is accommodated in a mold, the press plate and vibrating table being pressed towards one another and being able to be vibrated relative to one another by periodic dynamic forces around the product body to condense.
  • the compression device further comprises a special frame against which the forces transmitted via the press plate and the vibrating table can be supported.
  • a compression device with such a special frame is described in the document EP 0620 090 B1.
  • the pressure plate is supported by force against a special upper support mass and the vibrating table against a special lower support mass, the upper and lower support masses being able to transmit their forces to the frame only via insulation springs assigned to the respective support mass.
  • the function of the support masses is indispensable insofar as their masses, which have to reach a certain minimum size, determine the dynamic pressure to be built up in the product to be compacted, and thus the compression result.
  • the two different support masses are decoupled from each other by the insulation springs.
  • the insulation springs are provided to withstand the action of the dynamic inertial forces of the supporting masses on the foundation or on other parts of the compacting device in the interest of protection against vibrational emissions into the foundation and against noise radiation from the components transmitting the dynamic forces keep reasonable limits.
  • Said compression device according to EP 0 620 090 B1 is, however, in need of improvement, since it is expensive to manufacture because of the special individual supporting masses required and its special attachment to the frame via the insulation springs, and because the special supporting masses together with their associated insulation springs also involve new natural vibrations can form natural frequencies deviating from the vibration frequency.
  • the object of the invention is to provide, in comparison to the prior art mentioned, more suitable transmission paths for the alternating forces occurring during the vibration and emanating from the press plate and the vibrating table, taking into account the frame required anyway, the vibration behavior of the entire compression device, in particular with regard to the Improve overall noise emissions and reduce manufacturing costs.
  • the invention solves these problems by applying the teaching of claim 1. Further possible configurations of the invention are defined by the subclaims.
  • the compression vibrator comprises an oscillatable mass-spring system which accelerates the oscillating movement of the system mass in both oscillation directions via the system springs ! n must transmit the frame.
  • the inventor The basic idea on which it is based is to provide the entire mass of the frame structure, which is necessary anyway, as a common supporting mass for both the pressure plate and the dynamic forces transmitted by the vibrating table. In order to avoid noise-generating natural vibrations of the frame, the frame structure is to be designed in such a way that bending stresses on the frame parts are largely avoided.
  • the invention is also dedicated to eliminating a particular source of noise.
  • This consists in that the auxiliary device required for manipulating the shape in the prior art is attached to the connecting structure connecting the upper frame parts and the lower frame parts.
  • these auxiliary devices are fastened in a different manner in such a way that they cannot vibrate with the frame, at least during the implementation of the vibratory vibrations, but are preferably supported against the ground or the foundation.
  • the compression device according to the invention is also provided for receiving compression vibrators, which are described in the documents of EP 0870585 and PCT / DE00 / 04632, in which the intended vibratable mass-spring systems can also vibrate in or near their natural frequencies and where - When extremely high dynamic forces are to be transferred from the vibrating table to the frame.
  • FIG. 1 shows a compression device with a mass-spring oscillator with a hydraulically operated exciter actuator. 2, an exciter actuator designed as an electric linear motor is used.
  • the frame is also connected to an additional mass and the insulation of the frame mass from the foundation takes place via springs which are arranged above the center of mass.
  • the frame 100 which absorbs the vibration forces of the vertically oriented vibration vibrations (indicated by the double arrows 106 and 108, respectively) of the press plate 102 and of the vibrating table 104, is built up on the base crossbar 110.
  • the one that can vibrate in the vertical direction with its total mass (indicated by the double arrow 116) frame 100 is in turn supported by softly matched springs 112 against the soil 114 or against the foundation, as a result of which the vibrations which can be transmitted into the soil are greatly weakened.
  • the frame base 120 and that Frame upper part 122 are fixedly and stiffly connected to one another by two (one behind the other) left frame columns 126 and two (one behind the other) right frame columns 128.
  • the total mass of the frame which is responsible for supporting all dynamic forces that occur, must have a considerable amount that is at least twice the dynamic mass (that is the mass of the vibrating table including the masses of all parts that vibrate during the compression process with the vibrating table) got to.
  • Such a dimensioning of the total mass of the frame optimally with an even higher mass amount than double the dynamic mass, is also a prerequisite for achieving the required high dynamic baling pressure, especially if the acceleration forces for the swing table movement in both directions through the system Springs are transferred to the frame mass.
  • the product body 130 is located within a mold 132 and is delimited at the top by the underside of the pressing plate 102 and at the bottom by the top of a base plate 134 which can be exchanged with the product body and which in turn rests on the oscillating table 104.
  • the mold 132, the base plate 134 and the vibrating table 104 can be firmly clamped to one another via clamping devices (symbolized by two lines 136), the clamping device also being able to be released again in order to remove the product body 130 together with the base plate 134 after lifting the mold 132 to be able to.
  • the vibrating piston 140 which generates and transmits the vibrating vibrations and which is fixedly connected to the vibrating table 104 and which can also be designed to act in two directions is movably arranged in a vibrating cylinder 142 and is driven by the variable pressure and by the variable volume of a hydraulic oil 144 Hydraulic volume of the vibration cylinder 142 is connected via a line 146 to a hydraulic servo device, not shown, through which the hydraulic pressure and the hydraulic volume are influenced in a manner known per se with the help of a superordinate (also not shown) electrical control system in such a way that the vibration piston 140 leads to the necessary vibration vibrations 108 can be forced.
  • the simple compression vibrator shown here for the sake of simplicity and described by the components of the vibrating piston 140, the vibrating cylinder 142, the hydraulic oil 144 and the connected hydraulic servo device can be replaced in the practical application of the invention by compression vibrators which are equipped with a vibratable mass-spring system work, as described for example in the already mentioned EP 0 870 585 A1 or PCT / DE00 / 04632 or in FIG. 2 of the present invention with 262.
  • the dynamic mass forces of the vibrating table 104 and the mass parts connected to it are introduced into the frame via the system spring of the mass-spring system.
  • the hydraulic oil 144 enclosed between the vibration piston 140 and the vibration cylinder 142 not only serves to drive the vibration piston 140, but also represents the system spring, which is realized by the elastic compressibility of the hydraulic oil.
  • the vibrating piston 140 in its capacity as an excitation actuator and part of the system spring, could also be double-acting (in both vertical directions).
  • the vibration cylinder 142 could also be generally referred to as a spring force support member 142.
  • the plunger 150 which is fixedly connected to the press plate 102 and generates a press force, is movably arranged in a press cylinder 152 and is driven by the variable pressure and by the variable volume of a hydraulic oil 154.
  • the hydraulic volume of the press cylinder 152 is connected to one via a line 156 Hydraulic servo device, not shown, is connected, by means of which the hydraulic pressure and the hydraulic volume are influenced with the assistance of a superordinate (also not shown) electrical control such that the plunger 150 can be forced to move up and down and to build up a variable pressing pressure.
  • a (also changeable) pressing pressure is built up on the pressing plate 102 resting on the top of the product body 130 during the compression process, as a result of which the vibrating vibrations 108 of the vibrating piston 140 (in a modified form) are also transmitted to the pressing piston 150 and thereby also due to the oil compressibility change the volume of hydraulic oil 154.
  • the forces transmitted from the vibrating piston 142 to the plunger 150 and vice versa, from the plunger 150 to the vibrating piston 142 are brought together again in a power flow circuit via the frame.
  • the shape and press ram can also be designed in such a way that several product bodies can be compressed at the same time.
  • the function of the plunger and press cylinder could also be replaced by another function, e.g.
  • this replacement function could be implemented in such a way that a component transmitting the pressing force would be similar to that of the press cylinder 152, so that, in general terms, the press cylinder 152 in its force-transmitting function can also be referred to as a pressing force supporting member 152, via which the pressing force of the Press plate is inserted into the frame.
  • the upper frame part and the lower frame part are constructed in a similar force transmission structure, which is based on the example of the upper frame part (for the special situation of the transmission of such tensile forces via the frame columns resulting from the compressive forces are to be explained in the product body 130):
  • the resulting force flow lines 160 In order to be able to transmit the forces into the frame columns in such a way that they are subjected to bending as little as possible, it is necessary that the resulting force flow lines 160,
  • the structure of the upper frame part is constructed in such a way that there are structural parts that predominantly only contain compressive forces and such,
  • Structural components which predominantly transmit only compressive forces are two left diagonal struts 170 (one behind the other) and two right diagonal struts 172 one behind the other, these diagonal struts transferring the forces emanating from the press cylinder 152 into the force line crossing points 166 and 168 transmitted.
  • the traverse 174 has in particular to transmit tensile forces which are derived from the compressive forces of the diagonal struts.
  • the structural structure of the lower frame part 120 is constructed in a very similar manner, only the press cylinder 152 being replaced by the vibrating cylinder 142.
  • lines 160, 162, 164 of the upper frame part and / or the lower frame part caused by the arrangement of the diagonal struts could, however, also be arranged in mirror symmetry.
  • lines 160, 162 would then lie above it.
  • the diagonal struts (170, 172) would then have tensile forces and the traverse 174 would then have to transmit a compressive force.
  • the frame columns 128 are also subjected to such tensile and compressive forces that are derived solely from the mass forces of the vibrating mass of the mass-spring system. Under the influence of the dynamic that occurs in this case when the upward oscillating movement of the system mass is reversed
  • 35 mass forces can also be reversed in the diagonal struts].
  • structural parts 170, 172 are provided in the structure of the frame upper part 122 and / or the pressing force supporting member 152 which is included in the force flow to the connecting structure 126, 128 in to which forces passed via the press plate are passed, at least some of these forces being guided through these structural parts on force flow paths 160, 162 which are not parallel to the horizontal main direction of extension of the upper frame part.
  • Two auxiliary devices 180, 182 are provided with which the mold 132 can be raised in order to be able to remove the product body 130 from the mold after the clamping devices 136 have been released.
  • arms 184, 186 can travel under lugs 188, 189 to raise the shape.
  • the arms sit on carriages 190, 192, which can be moved up and down on guide parts 194, 196.
  • the guide parts 194, 196 themselves are attached to the foundation 114. Since the demolding of the product body and thus the contact between the arms 194, 196 and lugs 188, 189 does not take place during the compression process, the parts of the auxiliary devices 180, 182 cannot be excited by the vibration vibrations 108 to produce natural vibrations associated with noise radiation.
  • the entire frame 100 defined at least by the rigidly and rigidly connected components, namely, frame columns (126, 128), frame upper part 122, pressing force supporting element 152, frame lower part 120, spring force supporting element 142 , with its total mass serves as a supporting mass for those dynamic forces which are either guided over the vibrating table 104 and over the pressure plate 102 when oscillating movements 108 are carried out, or which act as reaction forces of the oscillating forces of the masses of the mass-spring system via the system Springs are inserted into the lower part of the frame.
  • FIG. 2 shows another embodiment variant of a compaction device, with a vibrating table 204, to which the parts of the base plate and shape (with product body) not shown, as shown in FIG. 1, have to be attached, and above which the dividing line 201 same parts and functional devices are to be connected to the frame columns 226 and 228, as shown and described in FIG. 1 in connection with the frame columns 126 and 128.
  • the frame 200 also includes the frame lower part 220, which in this case is composed of the base crossbeam 210 and the concrete container 250 attached underneath.
  • the concrete container 250 has the task of being more cost-effective Way to create a large mass for the whole frame.
  • the concrete container is originally a structure with one or more cavities, which is preferably only filled with concrete when the compacting device is installed at its work station, the filled-in concrete being indicated by the rectangle 252.
  • This measure advantageously gives the entire frame a very low center of gravity, which is symbolically identified by "G”.
  • the concrete container could of course also be replaced by prefabricated concrete plates or steel plates attached to the base crossbar.
  • FIG. 2 shows a compression vibrator 260 which, viewed from the total outlay, can be produced and operated even more cost-effectively than the one shown in FIG. 1 because of its purely mechanical design, and which also allows the vibration forces to be introduced more favorably into the overall mass of the frame 200.
  • the compression vibrator consists of the oscillatable mass-spring system 262 and the exciter actuator 264.
  • the compression vibrator is also able to carry out harmonic vibrations, ie vibrations with an essentially sinusoidal course, during the compression of the product bodies.
  • the mass of the mass-spring system comprises the oscillating oscillation in the vertical direction (indicated by the double arrow 230).
  • the system spring 266 consists of two identical springs 268 of the same type, the actual spring elements 270 of which are made of an elastomer material and can be subjected to thrust in both vertical directions.
  • the spring force generated during the deformation is transmitted via the center piece 272 to the oscillating table and via two support members 274 each to the base cross-member 210 or to the frame lower part 220.
  • the function of a "spring force support member" can also be assigned to the base crossbeam 210 based on the function correspondingly described in FIG. 2.
  • the individual springs 268 could also consist of individual springs made of a metallic material or of a fiber composite material, which would then have to be deformable in both vertical directions.
  • the excitation actuator 264 consists of one or more electric nuclear motors, each with a two-part primary part 280, 280 ', which carries the electrical winding and which is fastened to the base cross-member 210, and each with a secondary part 282 with the permanent magnets 284 Double arrangement of electric linear motors can cause the horizontal magnetic forces, which have very considerable amounts, to cancel each other out. This is the only way to achieve a precise vertical linear guidance of the vibrating table in connection with the spring elements 270 made of an elastomer material. The arrangement of the movable secondary parts on the vibrating table is recommended because this motor part is best able to withstand the high accelerations of the vibrating table.
  • the individual springs 268 are deliberately not attached in the middle of the vibrating table 204, but outside the center, since two advantageous effects can thus be achieved.
  • the eccentric arrangement of the individual springs can improve the power flow for the high dynamic forces, in addition to the power flow in the vibrating table itself, in that the introduction of the dynamic forces into the base crossbar 210, to which the frame columns 226, 228 are also attached are in the vicinity of the force introduction points of the force flows guided through the frame columns.
  • the single springs 268, which can be designed with a high level of horizontal rigidity can, in a second function, replace an otherwise necessary central straight guide, as is formed in FIG. 1 by the interaction of the vibration piston 140 and the vibration cylinder 142.
  • the maintenance of the air gaps in the motors can be achieved solely through the horizontal stiffness of the individual springs 268.
  • the entire frame 200 is supported against the foundation 214 by (at least 4) insulation springs 244, 246, to which the weight and the mass force of the frame are communicated via cantilever arms 240, 242.
  • Lateral support springs 234, 236 (which in this case are to be designed as elastomer springs) can help to prevent the frame from evading in the horizontal direction.
  • a natural frequency must be formed by the supported masses and the resulting spring constant of all insulation springs 244, 246 and the side support springs 234, 236 involved, which is at least a factor of 2 smaller than the lowest Work excitation frequency is, which in any case must be below 25 Hz.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Chemical & Material Sciences (AREA)
  • Ceramic Engineering (AREA)
  • Press-Shaping Or Shaping Using Conveyers (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

Ce dispositif comprend au moins une plaque de compression et une table vibrante, entre lesquelles est introduit un corps de produit qui est compacté sous l'effet des forces de vibration et des forces de compression. La plaque de compression est reliée à un dispositif de compression et la table vibrante est reliée à un vibrateur avec un système masse-ressort pouvant vibrer, le dispositif de compression et le vibrateur reposant également dynamiquement contre un châssis commun. Ledit châssis est constitué d'une partie supérieure et d'une partie inférieure spéciales, ainsi que d'une structure de liaison reliant ces deux parties, et il est isolé de la terre, de façon élastique, par des ressorts. Avec sa masse totale, ce châssis constitue la seule masse d'appui disponible tant pour les forces dynamiques exercées par l'intermédiaire de la plaque de compression que pour celles exercées par l'intermédiaire de la table vibrante. Une structure spéciale de la partie supérieure et de la partie inférieure sert à empêcher la génération de forces de flexion dans la partie supérieure, dans la partie inférieure et dans la structure de liaison, et donc à empêcher des vibrations de flexion produisant du bruit. Un tel dispositif peut être utilisé, par exemple, dans des machines de production de pierres artificielles.
PCT/DE2001/004612 2000-12-10 2001-12-10 Dispositif de compactage pour compacter des corps de produits constitues d'une masse granulee WO2002045927A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10061449.3 2000-12-10
DE10061449A DE10061449A1 (de) 2000-12-10 2000-12-10 Verdichtungseinrichtung zur Verdichtung von aus körniger Masse bestehenden Produktkörpern

Publications (1)

Publication Number Publication Date
WO2002045927A1 true WO2002045927A1 (fr) 2002-06-13

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PCT/DE2001/004612 WO2002045927A1 (fr) 2000-12-10 2001-12-10 Dispositif de compactage pour compacter des corps de produits constitues d'une masse granulee

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DE (1) DE10061449A1 (fr)
WO (1) WO2002045927A1 (fr)
ZA (1) ZA200206268B (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007057088A1 (fr) 2005-11-18 2007-05-24 Kobra Formen Gmbh Dispositif pour produire des pieces moulees en beton
CN104385436A (zh) * 2014-10-20 2015-03-04 佛山高品环保技术有限公司 一种人造石材生产系统
CN104441200A (zh) * 2014-10-20 2015-03-25 佛山高品环保技术有限公司 一种制备人造石材的振动装置
EP3031601A1 (fr) * 2014-12-10 2016-06-15 Quadra 1 Procédé de démoulage d'un élément de construction d'une presse vibrante
EP3031589A1 (fr) * 2014-12-10 2016-06-15 Quadra 1 Système de compression d'une presse vibrante pour la réalisation d'un élément de construction, presse vibrante et procede de demoulage

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1267584B (de) * 1961-12-23 1968-05-02 Laeis Werke Ag Ruettelform-Maschine mit einstellbarer Auflast
GB1142615A (en) * 1965-07-03 1969-02-12 Birmingham Small Arms Co Ltd Improvements in or relating to production of articles from metallic and non-metallic powders
DE2855875A1 (de) * 1978-12-22 1980-06-26 Schlosser & Co Gmbh Verfahren und vorrichtung zum verdichten von formkoerpern aus beton o.dgl. plastischen massen
FR2496541A1 (fr) * 1980-12-19 1982-06-25 Passavant Werke Dispositif pour la fabrication d'elements moules compactes en beton ou similaires
EP0620090A1 (fr) * 1993-04-07 1994-10-19 Den Boer Staal B.V. Installation de compactage

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1267584B (de) * 1961-12-23 1968-05-02 Laeis Werke Ag Ruettelform-Maschine mit einstellbarer Auflast
GB1142615A (en) * 1965-07-03 1969-02-12 Birmingham Small Arms Co Ltd Improvements in or relating to production of articles from metallic and non-metallic powders
DE2855875A1 (de) * 1978-12-22 1980-06-26 Schlosser & Co Gmbh Verfahren und vorrichtung zum verdichten von formkoerpern aus beton o.dgl. plastischen massen
FR2496541A1 (fr) * 1980-12-19 1982-06-25 Passavant Werke Dispositif pour la fabrication d'elements moules compactes en beton ou similaires
EP0620090A1 (fr) * 1993-04-07 1994-10-19 Den Boer Staal B.V. Installation de compactage

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007057088A1 (fr) 2005-11-18 2007-05-24 Kobra Formen Gmbh Dispositif pour produire des pieces moulees en beton
CN104385436A (zh) * 2014-10-20 2015-03-04 佛山高品环保技术有限公司 一种人造石材生产系统
CN104441200A (zh) * 2014-10-20 2015-03-25 佛山高品环保技术有限公司 一种制备人造石材的振动装置
CN104385436B (zh) * 2014-10-20 2017-01-18 佛山高品环保技术有限公司 一种人造石材生产系统
EP3031601A1 (fr) * 2014-12-10 2016-06-15 Quadra 1 Procédé de démoulage d'un élément de construction d'une presse vibrante
EP3031589A1 (fr) * 2014-12-10 2016-06-15 Quadra 1 Système de compression d'une presse vibrante pour la réalisation d'un élément de construction, presse vibrante et procede de demoulage
FR3029823A1 (fr) * 2014-12-10 2016-06-17 Quadra 1 Procede de demoulage d’un element de construction d’un presse vibrante
FR3029822A1 (fr) * 2014-12-10 2016-06-17 Quadra 1 Systeme de compression d’une presse vibrante pour la realisation d’un element de construction

Also Published As

Publication number Publication date
ZA200206268B (en) 2003-11-06
DE10061449A1 (de) 2002-06-13

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