EP4178738B1 - Dispositif de cintrage avec compensation de flexion - Google Patents

Dispositif de cintrage avec compensation de flexion Download PDF

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Publication number
EP4178738B1
EP4178738B1 EP21754891.6A EP21754891A EP4178738B1 EP 4178738 B1 EP4178738 B1 EP 4178738B1 EP 21754891 A EP21754891 A EP 21754891A EP 4178738 B1 EP4178738 B1 EP 4178738B1
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EP
European Patent Office
Prior art keywords
actuators
press table
recess
press
bearing
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.)
Active
Application number
EP21754891.6A
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German (de)
English (en)
Other versions
EP4178738C0 (fr
EP4178738A1 (fr
Inventor
Harald Fenzl
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.)
Trumpf Maschinen Austria GmbH and Co KG
Original Assignee
Trumpf Maschinen Austria GmbH and Co KG
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
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Publication of EP4178738A1 publication Critical patent/EP4178738A1/fr
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Publication of EP4178738C0 publication Critical patent/EP4178738C0/fr
Publication of EP4178738B1 publication Critical patent/EP4178738B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
    • B21D5/0272—Deflection compensating means

Definitions

  • the invention relates to a bending device for producing a component by forming a workpiece made of sheet metal according to the preamble of claim 1.
  • a bending device for producing a component by forming a workpiece made of sheet metal according to the preamble of claim 1.
  • Such a bending device is described in the JP-H-0331013U revealed.
  • An important criterion for the quality of workpieces that are produced by forming sheet metal parts intended for this purpose on a bending press is a bending angle that is as uniform as possible along the bending edge. To do this, it is necessary that the edge of the bending punch penetrates the same distance into the recess in the die over the bending edge that is being formed. The main prerequisite for this is that the contact surfaces or the edges of the bending tools that act on the sheet metal remain as parallel to one another as possible during the bending process. Depending on the arrangement of the bending tools on the tool holders of the press table and the press beam that is movable relative to it, as well as the size of the forming forces to be applied, the tool contact surfaces deform or bend in response to the forming forces.
  • the patent states EP 1 452 302 B1 A corresponding method for correcting a bending process in a bending press has already been described, in which the deformation forces occurring are measured with the aid of sensors and additional compensation forces are generated with the aid of hydraulic cylinders provided in the press table, by means of which the plate of the press table is kept essentially straight.
  • the document deals in particular with calculation methods that can be used when calibrating the correction method for the bending process.
  • the press table of the bending press described here is essentially constructed in a sandwich-like manner.
  • a central plate, on the top of which a tool holder for the dies is arranged, is supported on both sides, i.e. on the front and on the back, by another plate.
  • the lateral ends of all three plates are each attached together to the frame of the bending press.
  • tunnels extending through the fuselage are formed in the fuselage perpendicular to a front wall and a rear wall of the recess of the fuselage, and wherein an actuator is fastened to a bottom of each of the tunnels.
  • the design of the bending device according to which the tunnels with the actuators are arranged equidistantly distributed over the longitudinal extent of the press table, has the advantage that the control of the compensation of the deflection can be carried out more easily in this way.
  • the actuators can achieve a space-saving design of the press table.
  • Another advantageous development of the bending device is one in which threaded holes are formed in the pistons of the actuators, with which the pistons are screwed to the underside of the compensation beam. This can increase the rigidity or internal stability of the press table.
  • the bending device in which the recess for the compensating beam in the fuselage has an approximately trough-shaped course in the longitudinal direction of the press table, allows the formation of bearing points in the longitudinal end areas, between the front wall and the rear wall of the fuselage, which also have a high degree of rigidity.
  • the spatial position and orientation of the tool holder can be controlled well and reliably during bending.
  • downwardly open bearing shells for the bearing points in the longitudinal end regions of the press table are formed on an underside of the compensating beam.
  • the device for fastening the actuators to the floor of the tunnels comprises a mounting plate, wherein the mounting plate is fastened to the floor with several screws positioned approximately in the middle of the recess, and wherein the actuators are each fastened to the floor by a first row of screw connections in the area of the front wall and a second row of screw connections in the area of the rear wall. mounting plate.
  • a central bearing pin is arranged at the central bearing point, which extends perpendicular to the front wall or the rear wall through the fuselage in the area of its bottom surface, with a central bearing shell with an approximately semicircular cross-section being formed on the underside of the compensating beam for contact with the central bearing pin.
  • Another advantage is the development of the device in which a value of a width of the actuators is smaller than or at most equal to a value of a thickness of the hull. This enables an overall compact and space-saving construction of the press table, with the actuators being accommodated in the outer casing of the essentially plate-shaped hull.
  • the design of the bending device has the advantage that - even if both variants of bearing points (pivot bearings in the ends and central bearing point) are provided - the bending device can be optionally converted. This also makes it possible for tensile forces and compressive forces to be applied alternately to the balancing beam within the series of several actuators.
  • the design of the bending device in which at least four tunnels with actuators are arranged in the press table, has proven to be particularly practical for controlling the compensation of the deflection of the press beam.
  • the design of the device wherein the hydraulic cylinders of the actuators each have at least three pistons, has the advantage that the actuators can be arranged in a space-saving manner.
  • the Fig.1 shows a bending device 1 during the processing of a workpiece 2 in front view.
  • the bending device 1 comprises a press table 3 and a press beam 4 opposite it, aligned parallel to it. Bending tools facing each other are attached to the press table 3 and the press beam 4 with the help of corresponding tool holders. These bending tools are on the one hand a die or a bending die 5 on the press table 3 and on the other hand a bending punch 6 on the vertically adjustable press beam 4.
  • a first side part 7 and a second side part 8 together with the press table 3 form a fixed machine frame of the bending device 1. With the help of one or more drive devices 9, the press beam 4 is moved against the press table 3 and in this way the necessary forming forces for bending the workpiece 2 are generated.
  • the forces occurring during bending in the components of the bending device 1 or the deformations occurring in response to the forces are shown in the Fig.1 by arrows or dashed bending lines. These are, on the one hand, bending forces 10 generated by the drive devices 9 and, on the other hand, a deformation resistance 11 of the workpiece 2 in response to this.
  • the bending device 1 is designed as in the Fig.1 As shown, during the bending of the workpiece 2, a concave deflection of the press table 3 and the press beam 4 will generally occur. This deflection is in the Fig.1 by a bending line 12 on the tool holder side of the press table 3 and, on the other hand, by a second bending line 13 on the press beam 4.
  • the Fig. 2 shows a bending device 1 with a device for compensating the deformation of the press table 3 or the press beam 4 in perspective.
  • the drive devices 9 as well as the press beam 4 and the bending tools 5, 6 are not shown ( Fig.1 ).
  • the illustration essentially shows only the fixed machine housing consisting of the press table 3 and the two side parts 7, 8.
  • the press table 3 comprises a body 15 and a compensating beam 16 accommodated in a recess in the body 15.
  • a plurality of actuators 17 are also arranged distributed in the direction of the longitudinal extension of the press table 3.
  • the actuators 17 are preferably designed in the form of hydraulic cylinders.
  • the actuators 17 are arranged between the body 15 and the compensating beam 16. With the help of the actuators 17 in the press table 3, compressive or tensile forces can be applied between the body 15 and the compensating beam 16 in such a way that the deflection of the compensating beam 16 or its tool holder can be specifically adjusted.
  • the Fig.3 shows a longitudinal section through the press table 3 according to Fig. 2 .
  • the press table 3 is shown in perspective and partially in an exploded view.
  • a recess 18 for receiving the compensation beam 16 is formed in the body 15 of the press table 3.
  • the recess 18 for the compensation beam 16 is formed approximately in the shape of a slot in the body 15 and has an approximately trough-shaped profile in the longitudinal direction of the press table 3.
  • the body 15 is preferably made in one piece, with its external shape corresponding approximately to that of a rectangular plate.
  • the recess 18 is open at the top (towards the press beam 4).
  • a side of the compensation beam 16 which protrudes upwards from the recess 18 is T-shaped and functions as a tool holder for the bending die 5 to be attached to it.
  • a pivot bearing is formed in the press table 3 between the body 15 and the compensation beam 16.
  • a bearing bolt 21 is provided which extends through corresponding holes in the front wall 19 and the rear wall 20 of the body 15 of the press table 3.
  • bearing shells 22 which are open towards the bottom are formed on an underside of the compensation beam 16.
  • the two pivot bearings on the bearing bolts 21 enable the compensation beam 16 and the body 15 to pivot at least locally relative to one another with respect to an axis 23.
  • the two axes 23 of the bearing bolts 21 run horizontally and are directed vertically with respect to the longitudinal extent of the press table 3.
  • the pivoting of the compensating beam 16 and the fuselage 15 locally in the area of the bearing pin 21 is the result of a deformation of the compensating beam 16 or the fuselage 15 due to the bending forces 10 or the deformation resistance 11 during a bending deformation.
  • a deformation of the compensation beam 16 relative to the body 15 is brought about in a targeted manner by appropriate control of the actuators 17.
  • a first screw 24 and a second screw 25 are also provided, with the aid of which the respective longitudinal end regions of the compensation beam 16 are held fixed against the body 15 without play.
  • the first screw 24 and the second screw 25 are screwed into the body 15 perpendicularly and crossing the axis 23 of the bearing bolts 21, running through the compensation beam 16 and the bearing bolts 21.
  • the deflection of the compensation beam 16 and accordingly the course of the bending line 12 of the tool holder of the press table 3 can be influenced with the aid of the actuators 17.
  • the actuators 17 are formed by hydraulic cylinders, with the aid of which compressive forces can be generated.
  • tunnels 26 extending through the front wall 19 and the rear wall 20 are formed in the fuselage 15 for the arrangement of the actuators 17.
  • the actuators 17 are each fastened to a base 27 of the tunnel 26.
  • a mounting plate 28 can advantageously be provided on which the actuator 17 rests.
  • pressure pistons of the actuators 17 are positioned adjacent to an underside 29 of the compensation beam 16.
  • the Fig.5 shows a detail of the press table 3 of the longitudinal section according to Fig.3 shown in perspective.
  • the hydraulic cylinders used as actuator 17 are those in which three cylinders or pistons 30 are provided.
  • the three pistons 30 of this hydraulic cylinder are moved by the hydraulic fluid of a common or connected pressure chamber.
  • the fastening of the mounting plate 28 to the floor 27 of the tunnel 26 by means of screws can also be seen.
  • a hydraulic cylinder or an actuator 17 is fastened to the mounting plate 28 by screws.
  • Fig.6 is a cross section of the press table 3 according to Fig.3 shown in perspective.
  • the balancing beam 16 is not shown. In the assembled state, this is located in the recess 18, between the front wall 19 and the rear wall 20 of the fuselage 15 ( Fig.4 ). In this illustration, the upper end faces of the pistons 30 are visible.
  • the mounting plate 28 is attached to the floor 27 of the tunnel 26 by a row of screws that is positioned approximately in the middle of the recess 18.
  • the actuators 17 are each attached to the mounting plate 28 by a first row of screw connections in the area of the front wall 19 and a second row of screw connections in the area of the rear wall 20 (not shown).
  • the described use of the hydraulic cylinders with active elements divided into three pistons 30 as actuators 17 has the particular advantage that the actuators 17 are arranged entirely integrated in the body 15 or the press table 3. This means that the value of a width 32 of the actuator 17 is smaller or at most the same as the value of a thickness 31 of the body 15.
  • each actuator 17 is provided in the press table 3 of the bending device 1, distributed equidistantly over the length of the press table.
  • the pressure forces exerted by the actuators 17 on the underside 29 of the compensating beam 16 can push the compensating beam 16 out of the recess 18 of the body 15 and thus change and adjust its deflection.
  • This deformation of the compensating beam 16 takes place against the restraining effect of the bearing bolts 21 in the two end areas of the press table 3.
  • the vertical position is determined by screwing with the screws 24, 25 in the area of the bearing bolts 21.
  • the compensation beam 16 in the area of these bearing bolts 21 is always held in a clearly defined position. This means that due to the screw connection, the bearing on the bearing bolts 21 is in a permanently preloaded and thus play-free state.
  • the body 15 of the press table 3 of this bending device 1 is preferably formed in one piece.
  • the body 15 is made, for example, from a corresponding metal plate by material-removing machining to form the recess 18 and the tunnel 26.
  • the stability of the connection of a compensating beam 16 on or in the body 15 can also be increased by firmly connecting the pistons 30 of the actuators 17 to the underside 29 of the compensating beam 16.
  • threaded holes 33 are formed in the pistons 30 so that a screw connection can be made between these and the compensating beam 16.
  • the fuselage 15 is firmly connected to the two side parts 7, 8, preferably by welding.
  • the Fig.7 shows a detail of the longitudinal section of the press table 3 as shown in Fig.3 .
  • no pivot bearing is formed in the longitudinal end areas of the press table 3. This means that the bearing bolts 21 and the two screws 24, 25 are not present or have been removed in this bending device 1 ( Fig.3 , 4 ).
  • the compensating beam 16 is fastened in the middle of the longitudinal extension of the press beam in the recess 18 of the body 15.
  • the compensating beam 16 is fastened to a bottom surface 34 of the recess 18 of the body 15.
  • the compensating beam 16 is provided with a bottom side 35 ( Fig.4 ) against the bottom surface 34 of the recess 18.
  • a third and a fourth screw 36, 37 are preferably provided for this screw connection.
  • the screw connection can also be secured by a central bearing bolt 38.
  • the bearing bolt 38 extends perpendicular to the front wall 19 or the rear wall 20 through the fuselage 15 in the area of its bottom surface 34.
  • a central bearing shell 39 with an approximately semicircular cross-section is formed on the underside 35 ( Fig.4 ).
  • the fastening of the compensation beam 16 to the middle floor surface 34 of the fuselage 15 corresponds to the situation of a beam clamped in its middle with free ends on both sides.
  • a distance 40 is provided between the bottom of the recess 18 of the fuselage 15 and the underside of the compensation beam 16.
  • the gap or the value of the distance 40 is at least as large as is required to compensate for the compensation beam 16 during bending.
  • the actuators 17 are not only attached to the floor 27 of the tunnels 26 but also connected to the compensating beam 16, in which screw connections are provided between the threaded holes 33 of the pistons 30 of the actuators 17 and the compensating beam 16.
  • the hydraulic cylinders used as actuators 17 in this embodiment of the bending device 1 are suitable both for generating compressive forces acting on the compensating beam 16 and for generating tensile forces.
  • the pistons 30 can be subjected to pressure in both directions, whereby forces can be actively exerted both during the extension movement of the pistons 30 and during the retraction movement.
  • the actuators 17 it is thus possible to use the actuators 17 to apply tensile forces to the compensating beam 16, by means of which the distance 40 between the underside of the compensating beam 16 and the body 15 can be continuously reduced. It is thus possible to deform the compensating beam 16 and thus the bending line 12 of the tool holder into a convex shape.
  • the description of the bending device 1 according to the invention has been described in the exemplary embodiments using press tables 3 in which four actuators 17 are arranged. Alternatively, however, a different number of actuators 17 can also be provided. In practice, however, it has proven advantageous to provide four actuators 17, distributed symmetrically and equidistantly over the longitudinal extent of the press table 3.
  • the choice of hydraulic cylinders with three pistons each should not be understood as restrictive. Hydraulic cylinders with a different number of equally acting pistons 30 could also be provided.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)

Claims (12)

  1. Dispositif de pliage (1) pour la fabrication d'un composant par formage d'une pièce (2) en tôle avec une table de presse (3) et avec une barre de presse (4) orientée de manière opposée et parallèle à celle-ci, qui peut être déplacée par rapport à la table de presse (3) au moyen d'un dispositif d'entraînement (9) dans une direction orientée perpendiculairement à une extension longitudinale de la table (3), dans lequel la table de presse (3) comprend une coque (15), une barre d'équilibrage (16) avec un logement d'outil et des actionneurs (17) disposés entre la coque (15) et la barre d'équilibrage (16), pour la déformation élastique de la barre d'équilibrage (16) par rapport à la coque (15), dans lequel, dans la coque (15), est réalisé un évidement (18) s'étendant parallèlement à une extension longitudinale de la table de presse (3) et ouvert en direction de la barre de presse (4) et dans lequel la barre d'équilibrage (16) est logée dans l'évidement (18) de la coque (15) et les actionneurs (17) sont disposés entre un côté inférieur (29) de la barre d'équilibrage (16) et un fond de l'évidement (18) de la coque (15), caractérisé en ce que, dans des zones d'extrémité du côté longitudinal de la table de presse (3), est réalisé un point d'appui pour un palier rotatif avec une tige de palier (21) entre la coque (15) et la barre d'équilibrage (16), dans lequel, sur le côté inférieur de la barre d'équilibrage (16), dans les zones d'extrémité du côté longitudinal, sont réalisées des coques de palier (22) ouvertes vers le bas pour les points d'appui et dans lequel, à chacun des points d'appui, est prévue une vis (24, 25) avec laquelle les zones d'extrémité du côté longitudinal de la barre d'équilibrage (16) sont vissées contre la coque (15), dans lequel les vis (24, 25) s'étendent respectivement à travers la tige de palier (21) et croisent un axe (23) de a tige de palier (21).
  2. Dispositif selon la revendication 1, caractérisé en ce que, dans la coque (15), sont réalisés des tunnels (26) s'étendant perpendiculairement à une paroi avant (19) et à une paroi arrière (20) de l'évidement (18) de la coque (15), à travers la coque (15), dans lequel un actionneur (17) est fixé respectivement à un fond (27) des tunnels (26) et dans lequel les tunnels (26) sont conçus de sorte que les fonds (27) des tunnels (26) forment respectivement des parties du fond de l'évidement (18).
  3. Dispositif selon la revendication 2, caractérisé en ce que les tunnels (26) avec les actionneurs (17) sont répartis de manière équidistante sur l'extension longitudinale de la table de presse (3).
  4. Dispositif selon l'une des revendications précédentes, caractérisé en ce que les actionneurs (17) comprennent des vérins hydrauliques, dans lequel les vérins hydrauliques comprennent chacun plusieurs pistons (30).
  5. Dispositif selon la revendication 4, caractérisé en ce que, dans les pistons (30) des actionneurs (17), sont réalisés des trous filetés (33) avec lesquels les pistons (30) sont vissés au côté inférieur (29) de la barre d'équilibrage (16).
  6. Dispositif selon l'une des revendications précédentes, caractérisé en ce que la coque (15) de la table de presse (3) est réalisée d'une seule pièce avec une forme externe correspondant approximativement à une plaque rectangulaire.
  7. Dispositif selon l'une des revendications précédentes, caractérisé en ce que l'évidement (18) pour la barre d'équilibrage (16) présente, dans la coque (15), dans la direction longitudinale de la table de presse (3), une extension globalement en forme de cuvette.
  8. Dispositif selon l'une des revendications 2 à 7, caractérisé en ce que, pour la fixation des actionneurs (17) au fond (27) des tunnels (26), une plaque de montage (28) est prévue, dans lequel la plaque de montage (28) est fixée au fond (27) avec plusieurs vis positionnées approximativement au centre de l'évidement (18) et dans lequel les actionneurs (17) sont fixés sur la plaque de montage (28) respectivement à l'aide d'une première série de vissages au niveau de la paroi avant (19) et d'une deuxième série de vissages au niveau de la paroi arrière (20).
  9. Dispositif selon l'une des revendications précédentes, caractérisé en ce qu'une valeur d'une largeur (32) des actionneurs (17) est inférieure ou au maximum égale à une valeur de l'épaisseur (31) de la coque (15).
  10. Dispositif selon l'une des revendications précédentes, caractérisé en ce que les actionneurs (17) comprennent des vérins hydrauliques double effet qui permettent d'appliquer des forces de traction et des forces de compression sur les barres d'équilibrage (16).
  11. Dispositif selon l'une des revendications 2 à 10, caractérisé en ce qu'au moins quatre tunnels (26) avec actionneurs (17) sont prévus.
  12. Dispositif selon l'une des revendications 4 à 11, caractérisé en ce que les vérins hydrauliques des actionneurs (17) comprennent chacun au moins trois pistons (30).
EP21754891.6A 2020-07-09 2021-07-09 Dispositif de cintrage avec compensation de flexion Active EP4178738B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA50596/2020A AT523965B1 (de) 2020-07-09 2020-07-09 Biegevorrichtung mit Durchbiegungsausgleich
PCT/AT2021/060247 WO2022006613A1 (fr) 2020-07-09 2021-07-09 Dispositif de cintrage avec compensation de flexion

Publications (3)

Publication Number Publication Date
EP4178738A1 EP4178738A1 (fr) 2023-05-17
EP4178738C0 EP4178738C0 (fr) 2024-09-25
EP4178738B1 true EP4178738B1 (fr) 2024-09-25

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP21754891.6A Active EP4178738B1 (fr) 2020-07-09 2021-07-09 Dispositif de cintrage avec compensation de flexion

Country Status (4)

Country Link
EP (1) EP4178738B1 (fr)
CN (1) CN115835922B (fr)
AT (1) AT523965B1 (fr)
WO (1) WO2022006613A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2163473C3 (de) * 1970-12-25 1978-03-02 Amada Co. Ltd., Isehara, Kanagawa (Japan) Hydraulische Abkantpresse
IT968136B (it) * 1972-09-14 1974-03-20 Piccini G Dispositivo idraulico di autocenti natura per presse di stampaggio come presse piegatrici e simili
US4898015A (en) * 1988-07-18 1990-02-06 Houston David L Press brake deflection compensating device
NL8901560A (nl) * 1989-06-21 1991-01-16 Wila Maschf Bv Kantpers en een automatische bombeerinrichting daarvoor.
JPH087932Y2 (ja) * 1989-07-31 1996-03-06 株式会社小松製作所 曲げ機械の工具位置制御装置
JP2764350B2 (ja) * 1990-12-11 1998-06-11 丸機械工業株式会社 折曲げ機のたわみ補正装置
DE4138286A1 (de) * 1991-11-21 1993-05-27 M & S Brugg Ag Presse
IT1295498B1 (it) * 1997-10-17 1999-05-12 Luciano Gasparini Dispositivo per rilevare la flessione delle traverse, inferiore e superiore, finalizzato all'interazione con almeno un sistema di
EP1452302B1 (fr) 2003-02-26 2009-04-08 Bystronic Laser AG Procédé de correction d'une opération de pliage et presse-plieuse
ITTO20050676A1 (it) * 2005-09-29 2007-03-30 Crea Srl Pressa piegatrice con tavola portautensili a deformazione ridotta
PT106004B (pt) * 2011-11-15 2020-12-16 Adira Metal Forming Solutions S A Avental para compensação de deformação para quinadoras
TR201112647A2 (tr) * 2011-12-20 2012-05-21 Durmazlar Maki̇na Sanayi̇ Ve Ti̇caret Anoni̇m Şi̇rketi̇ Abkant preslerde sac sehimini engelleyen dinamik bombeleme mekanizması.
JP6457805B2 (ja) * 2014-02-27 2019-01-23 株式会社アマダホールディングス 曲げ加工装置
CN106890871B (zh) * 2017-04-28 2019-01-11 山东嘉意机械有限公司 机架变形补偿装置及折弯机

Also Published As

Publication number Publication date
CN115835922B (zh) 2025-09-09
WO2022006613A1 (fr) 2022-01-13
EP4178738C0 (fr) 2024-09-25
AT523965A1 (de) 2022-01-15
EP4178738A1 (fr) 2023-05-17
AT523965B1 (de) 2023-08-15
CN115835922A (zh) 2023-03-21

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