EP0302489B1 - Dispositif à plier - Google Patents

Dispositif à plier Download PDF

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Publication number
EP0302489B1
EP0302489B1 EP88112683A EP88112683A EP0302489B1 EP 0302489 B1 EP0302489 B1 EP 0302489B1 EP 88112683 A EP88112683 A EP 88112683A EP 88112683 A EP88112683 A EP 88112683A EP 0302489 B1 EP0302489 B1 EP 0302489B1
Authority
EP
European Patent Office
Prior art keywords
drive
folding
cylinder
shaft
drive wheel
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
EP88112683A
Other languages
German (de)
English (en)
Other versions
EP0302489A3 (en
EP0302489A2 (fr
Inventor
Rudolf Stäb
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.)
Albert Frankenthal AG
Original Assignee
Albert Frankenthal AG
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 Albert Frankenthal AG filed Critical Albert Frankenthal AG
Publication of EP0302489A2 publication Critical patent/EP0302489A2/fr
Publication of EP0302489A3 publication Critical patent/EP0302489A3/de
Application granted granted Critical
Publication of EP0302489B1 publication Critical patent/EP0302489B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/54—Auxiliary folding, cutting, collecting or depositing of sheets or webs
    • B41F13/56—Folding or cutting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/54—Auxiliary folding, cutting, collecting or depositing of sheets or webs
    • B41F13/56—Folding or cutting
    • B41F13/60—Folding or cutting crosswise
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/54—Auxiliary folding, cutting, collecting or depositing of sheets or webs
    • B41F13/56—Folding or cutting
    • B41F13/62—Folding-cylinders or drums
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H45/00—Folding thin material
    • B65H45/12—Folding articles or webs with application of pressure to define or form crease lines
    • B65H45/16—Rotary folders
    • B65H45/162—Rotary folders with folding jaw cylinders
    • B65H45/168—Rotary folders with folding jaw cylinders having changeable mode of operation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H45/00—Folding thin material
    • B65H45/12—Folding articles or webs with application of pressure to define or form crease lines
    • B65H45/28—Folding in combination with cutting

Definitions

  • the invention relates to a folder for producing at least once cross-folded, trimmed products parallel to the transverse fold, with a cross-cutting device, at least one cross-folding device and at least one smooth-cutting device, which are provided on a folding cylinder provided with folding flaps, which interact with folding knives a collecting cylinder, in the area between the Folding flaps arranged scissor cut knives and at least one cooperating with it, on a knife cylinder placed on the peripheral region of the folding cylinder running from the collecting cylinder counter shear cutting knife.
  • a folder of this type is known from DE-A 3030705.
  • the scissor cut knives are arranged at a fixed distance from the folding jaws and can therefore not be adjusted.
  • the action of the scissor cut knives is therefore always the same distance from the jaws.
  • it is often desirable to change this distance for example in order to be able to make a regulation. So there is another requirement that production downtimes due to machine downtimes should be avoided as far as possible.
  • the folding cylinder consists of at least two coaxial, mutually rotatable, drivable at the same speed dashboards, which are equipped with folding jaws or scissors cutters and are provided with coaxial drive wheels which are coupled to one another by means of an adjustable lock-up gear, whereby the drive wheel of the instrument holder carrying the scissor-cut knife with a drive wheel of the knife cylinder and the drive wheel of the instrument holder carrying the jaws a drive wheel assigned to the folding knives, engaging the collecting cylinder.
  • the lock-up gear provided here ensures a positive drive coupling of the pair of drive wheels assigned to the dashboards for the jaws or scissor-cut blades, so that during normal operation there is practically a quasi-rigid connection and thus exact synchronization of the dashboard forming the folding cylinder. At the same time, it is ensured that a corresponding mutual adjustment of the respectively assigned dashboard can be achieved by appropriate adjustment of the elements of the lock-up gear. A corresponding actuation of the lock-up gear can take place while the folder is running, so that shutdowns and the associated disadvantages with regard to waste, etc. are avoided. In addition, a smooth cut regulation that can be carried out during operation also enables simple control. The advantages that can be achieved with the invention can thus be seen in particular in a high level of economy and excellent ease of use.
  • the lock-up gear can have two firmly connected, helically toothed pinions which are adjustable in the axial direction and mesh with the associated, also helically toothed drive wheels.
  • the two pinions can be connected to one another by means of a differential gear, which enables an adjustment in the circumferential direction, so that a large one Adjustment path is available. It is therefore advantageously possible not only to regulate the smooth cut, but also to passivate it, in that the scissor cut knives are set so far away from the folding jaws that the mutual engagement of the scissor cut knife and counter scissor cut knife takes place outside the rear end of the sheet of the folded products.
  • the lock-up gear can have an axis parallel to the shafts of the associated drive wheels, on which the pinions meshing with the assigned drive wheels are rotatably mounted, which are connected to one another by a harmonic drive gear, the two of which are connected with a pinion on the inside has toothed, rigid rings which are in engagement with a common, externally toothed, elastic ring into which an elliptical collar which is fastened on the axis receiving the pinion and which can be adjusted in the direction of rotation by means of an adjusting device engages.
  • one of the drive wheels can simply have two ring gears with different diameters, one of which with the assigned pinion and the other with the assigned drive wheel adjacent cylinder is engaged.
  • a further advantageous measure can consist in the fact that the adjusting device assigned to the axis of the lock-up gear has a servomotor. This measure advantageously enables remote control.
  • the actuating device can at the same time be provided with a display device, which further increases the ease of use.
  • the folding apparatus on which FIG. 1 is based consists of cylinders arranged between two side walls 1 in the form of a cutting cylinder 2, a collecting cylinder 3 attached to the latter, a folding cylinder 4 interacting with the latter and a knife cylinder 5 interacting with the latter.
  • the cutting cylinder 2 is provided with a cutter bar 6 .
  • the collecting cylinder 3 has cutting grooves 7 assigned to the cutter bar 6.
  • the cutter bar 6 and the cutting grooves 7 cooperate in the form of a cross-cutting device 8, by means of which a paper strand 10 drawn into the folder by pulling rollers 9 is divided into sheet-like products.
  • the cutting grooves 7 of the collecting cylinder 3 are assigned punctures 11 which detect the beginning of the path newly produced for each cross section.
  • the collecting cylinder 3 is equipped with folding knives 12.
  • the folding cylinder 4 has folding flaps 13 assigned to the folding knives 12, which cooperate with the folding knives 12 in the form of a transverse folding device 14.
  • the folding cylinder 4 is equipped with scissor cut knives 15.
  • the knife cylinder 5 has a counter-scissors cut knife 16 which cooperates with the scissor cut knives 15 of the folding cylinder 4 to form a smooth cutting device 17, by means of which the rear edge of the products accommodated in the folding jaws 13 can be separated off in the form of a smooth or scissor cut. This makes it possible to contain the punctures of the punctures 11 Sever the edge.
  • the paper strips separated by means of the smooth cutting device 17 are sucked off by means of a suction device 18 assigned to the knife cylinder 5.
  • the folding cylinder 4 In order to be able to regulate the distance of the smooth cut made by the smooth cutting device 17 from the respective leading folding flap 13, the folding cylinder 4, as can also be seen in FIG. 1, consists of two coaxial fitting brackets 21 and 22, of which the fitting bracket 21 is the one that rotates Folding jaws 13 and the armature support 22 which carries the scissors-cutting knife 15.
  • the armature supports 21, 22 can be driven uniformly, so that there is a uniform rotation of the entire folding cylinder 4. In the event of an adjustment of the instrument holder 22 carrying the scissor-cut knife 15, the knife cylinder 5 is adjusted in the same way.
  • the collecting cylinder 3 also consists of two coaxial fitting supports 23 and 24, of which the fitting support 23 has the cutting grooves 7 and punctures 11 and the fitting support 24 has the folding blades 12 wearing.
  • the dashboard 23, 24 By appropriate mutual adjustment of the dashboard 23, 24, it is possible to regulate the position of the transverse fold which can be produced by means of the transverse folding device 14. Accordingly, together with the armature carrier 24 of the collecting cylinder 3, which has the folding blades 12, the armature carrier 21 of the folding cylinder 4, which has the folding flaps 13, is adjusted accordingly and vice versa.
  • the cutting cylinder 2 is adjusted with the instrument holder 23 containing the cutting grooves 7.
  • the cylinders or the dashboard forming them are mounted on the side walls 1 with lateral bearing journals, as can best be seen from FIG.
  • the journals of the folding cylinder 4 consist of hollow shafts 25 fastened to end plates of the valve holder 21 receiving the folding jaws 13, into which the inner shafts 26 fastened to the valve holder 22 of the scissors-type cutters 15 engage.
  • the inner shafts 26 are mounted on the hollow shafts 25 and these on the side wall 1.
  • the dashboard 23 receiving the punctures 7 is correspondingly provided with lateral hollow shafts 27 into which the inside shafts 28 attached to the dashboard 24 of the folding blade 12 engage.
  • the bearing sockets 29 and 30 of the cutting cylinder 2 or knife cylinder 5 are designed as simple journals mounted in the side walls 1.
  • the cylinders are driven by a drive wheel train arranged in the area of a side wall. This is in a side wall on which the figure 2 is based 1 attached gear box 31, and consists of on the projecting into the gear box 21 ends of the bearing pin or the shafts forming these wedged or screwed drive wheels.
  • the by the two dashboards 23 u. 24 formed cylinder 3 are accordingly assigned two coaxially arranged drive wheels 32, 33, of which the inner, ie the drive wheel 32 adjacent to the side wall 1 onto the end of the hollow shaft 27 projecting into the gearbox 31 and the outer drive wheel 33 onto the one from the hollow shaft 27 protruding end of the inner shaft 28 are keyed.
  • the two-part folding cylinder 4 is assigned two drive wheels 34 and 35, which are arranged coaxially next to one another, of which the inner drive wheel 34 on the hollow shaft 25 of the fitting bracket 21 assigned to the folding jaws 13 and the drive wheel 35 on the end of the inner shaft 26 projecting from the hollow shaft 25 the scissor-cut knife 15 carrying instrument holder 22 are placed.
  • a drive wheel 36 or 37 is assigned to the cutting cylinder 2 and the knife cylinder 5.
  • the drive torque is introduced via a drive element indicated at 38 into the drive wheel 36 assigned to the cutting cylinder 2 and, as a result of the tooth engagement of the drive wheels assigned to the adjacent cylinders, is passed in the form of a gear train up to the drive wheel 37 of the knife cylinder 5.
  • the drive wheel 36 of the cutting cylinder 2 is in engagement with the drive wheel 32 assigned to the cutting grooves 7 and punctures 11. From this, the torque is transmitted to the adjacent drive wheel 33 assigned to the folding blades 12, which engages with the drive wheel 34 assigned to the folding jaws 13 is. From this one transmit the torque to the adjacent drive wheel 35, which is assigned to the scissor-cut knives 15 and is in engagement with the drive wheel 37 of the knife cylinder 5. This ensures that when the cutting or folding members of one cylinder are adjusted, the cutting or folding members of another cylinder interacting with them are automatically adjusted as well.
  • the coaxially arranged side by side drive wheels 32, 33 and 34, 35 of the dashboard of the collecting cylinder 3 and the folding cylinder 4 are coupled during normal operation by means of an associated lock-up gear 39 and 40 so that practically a quasi rigid Connection and thus a complete synchronization results.
  • the drive gears 32 and 33 of the collecting cylinder 3 drive-connected to each other, as shown in Figure 2 further includes two, two on an axis 41 parallel to the axis of the associated drive wheels 32, 33 mounted in the frame rotatably mounted, interconnected, here consisting of one piece Pinions 42 and 43, which mesh with a drive wheel 32 and 33, respectively, so that there is a transmission of the torque.
  • the pinion 42 results.
  • the pinions 42, 43 are helically toothed so that when the pinions 42, 43 are axially displaced, the drive wheels 32, 33 are rotated.
  • the pinions 42, 43 are accordingly wider by the axial travel than the drive wheels 32, 33, so that there is a sufficiently wide tooth engagement even in the end positions.
  • the sprockets 42 and 43 arranged side by side are in the illustrated embodiment as well as the associated drive wheels 32 and 33 toothed in opposite directions, so that the achievable angle of rotation is doubled.
  • the axis 41 is adjusted to accomplish the axial adjustment of the pinions 42, 43.
  • the axis 41 has for this purpose a bushing which accommodates the pinions 42, 43 and which is accommodated on a pin which is fixedly arranged on the housing and which is provided with a drive connector 44 passing through the gearbox, which in its rear region is designed as a threaded connector which engages in a threaded sleeve provided on the housing side and carries a handwheel 45 at its end.
  • a toggle screw 46 which interacts with the drive connection 44 and can be screwed into a radial bore of the threaded sleeve, is provided.
  • the lock-up gear 40 provided for driving coupling of the drive wheels 34, 35 of the folding cylinder 4 can be designed in the same way as the lock-up gear 39 described above.
  • the lock-up gear 40 as can also be seen in FIG. 2, also contains two pinions 42, 43 which are rotatably mounted on an axis 41 arranged parallel to the axis of the associated drive wheels 34, 35 and which here are by means of a differential gear in the form of an HD gear 47 are connected to one another in terms of drive.
  • This use of a differential gear enables a practically unlimited mutual rotation of the pinions 42, 43.
  • the differential gear 47 is designed as an HD gear, which can best be seen from FIG. 3.
  • the pinion 42, 43 receiving the axis 41 is provided in the area between the two pinions with an elliptical collar 48 on which an elastic, externally toothed ring 49 is mounted, which is arranged with two adjacent, internally toothed, is rigid rings 50 and 51 in engagement, which are attached to the mutually facing end faces of the sprockets 42 and 43 arranged side by side.
  • Rotation of the axis and thus of the elliptical collar 48 results in a mutual rotation of the rigid rings 50, 51 and thus the pinions 42, 43 firmly connected to them and the drive wheels 34, 35 meshing with them.
  • the axis 41 is used to accomplish such a rotary movement rotatably mounted in the side wall 1 or the box wall parallel thereto and provided with a drive connector 44 which leads out of the gear box 31 and which, as in FIG is indicated, can be provided with a handwheel 45, wherein a toggle screw 46 can also be provided to accomplish a fixation.
  • a servomotor 52 is provided to bring about a rotation of the axis 41.
  • a bevel gear is wedged onto the drive connector 44, which meshes with a bevel gear wedged onto the motor shaft.
  • the servomotor 52 can be operated remotely from a control panel.
  • a display device 53 is provided which displays the set distance of the scissor-cut knife 15 from the respective leading flap 13.
  • the display device 53 has a drive wheel meshing with a pinion arranged on the drive connector 44, by means of which either a pointer assigned to a scale or an electrical measuring sensor in the form of a variable capacitor etc. can be adjusted.
  • the externally toothed, elastic ring 49 and the internally toothed, rigid rings 50, 51 of the HD transmission have different numbers of teeth. This results in different angles of rotation of the pinions 42, 43 during the transmission of the torque from one pinion 42 to the adjacent pinion 43. This could be compensated for by different pinion diameters.
  • the pinion 42, 43 same diameter to simplify the construction. The compensation takes place accordingly by different effective diameters of the drive wheels 34, 35.
  • the drive wheel 34 is provided with two toothed rings 34a and 34b of different diameters arranged next to one another for this purpose.
  • the sprocket 34a adjacent to the drive wheel 35 which has the larger diameter and which engages in the region of the lock-up gear with play between the corresponding spaced pinions 42, 43, meshes with the drive wheel 33 of the folding blade fitting carrier of the collecting cylinder 3.
  • the diameter of the ring gear 34b corresponds accordingly to the diameter of the drive wheel 35 meshing with the other pinion 43.
  • the difference in the number of teeth between the ring gears 34a and 34b corresponds to double Difference between the number of teeth of the elastic ring 49 and the rigid rings 50, 51, which results in a full compensation, that is, with which a synchronous rotational movement of the fitting carriers 21 and 22 of the folding cylinder is ensured.
  • the drive wheel 33 assigned to the folding blade dashboard 24 of the collecting cylinder 3 is arranged outside the adjacent drive wheel 32.
  • the second ring gear 34b which, as has already been mentioned, can simply be designed as a laterally attached ring can.
  • the rigid rings 50, 51 of the HD transmission are screwed to the respectively assigned pinion 42 and 43 by axially parallel screws.
  • the pinions 42, 43 are formed in two parts, with a base element provided with a hub, firmly connected to the associated ring 50 or 51, and a base element attached to it on the side opposite the ring 50 or 51, from the Result in penetrated hub element.
  • the desired overall tooth widths can be achieved in a simple manner even when using prefabricated elements.
  • the drive of downstream elements for example a belt guide assigned to the folding cylinder 4, can be removed from this intermediate wheel 54 in a simple manner.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Folding Of Thin Sheet-Like Materials, Special Discharging Devices, And Others (AREA)

Claims (10)

1. Plieuse pour la fabrication de produits pliés transversalement au moins une fois et coupés parallèlement au pli transversal, comprenant un dispositif de coupe transversale (8), au moins un dispositif de pliage transversal (14) et au moins un dispositif de coupe nette (17) qui se compose de lames de cisailles de découpage (15) disposées sur un cylindre plieur (4) muni de mâchoires de pliage (13) qui coopèrent avec des plioirs (12) d'un cylindre collecteur (3), et situées dans la région comprise entre les mâchoires de pliage (13), et d'au moins une lame de cisaille de coupe conjuguée (16) coopérant avec celles-ci et reçue sur un cylindre de coupe (5) serré sur la partie périphérique du cylindre plieur (4) qui s'éloigne du cylindre collecteur (3), caractérisée par le fait que le cylindre plieur (4) se compose d'au moins deux porte-armatures coaxiaux (21, 22) que l'on peut faire tourner l'un par rapport à l'autre, qui peuvent être entraînés à la même vitesse, qui sont équipés des mâchoires de pliage (13) et des lames de cisailles de découpage (15), respectivement, et qui sont munis de roues d'entraînement coaxiales (34, 35) accouplées entre elles, quant à l'entraînement, au moyen d'une transmission de liaison déplaçable (40), la roue d'entraînement (35) du porte-armature (22) qui porte les lames de cisailles de découpage (15) étant en prise avec une roue d'entraînement (37) du cylindre de coupe (5), et la roue d'entraînement (34) du porte-armature (21) qui porte les mâchoires de pliage (13) l'étant avec une roue d'entraînement (33) associée aux plioirs (12) du cylindre collecteur (3).
2. Plieuse selon la revendication 1, caractérisée par le fait que les roues d'entraînement (34, 35) accouplées entre elles, quant à l'entraînement, par la transmission de liaison (40), laquelle comprend de préférence un engrenage différentiel (47), sont disposées l'une à côté de l'autre et sont reliées chacune à un arbre (25, 26) parmi lesquels l'un (25) des arbres est réalisé sous la forme d'un arbre creux traversé par l'autre arbre (26), et par le fait que la transmission de liaison (40) présente un axe déplaçable (41) qui est parallèle aux arbres (25, 26) des roues d'entraînement (34, 35) et sur lequel sont montés tournants deux pignons (42, 43) reliés l'un à l'autre quant à l'entraînement et engrenant avec les roues d'entraînement (34, 35).
3. Plieuse selon la revendication 2, caractérisée par le fait que les pignons (42, 43) sont montés séparément l'un de l'autre sur l'axe (41) et qu'ils sont reliés l'un à l'autre, quant à l'entraînement, par une transmission "harmonic drive" (à entraînement harmonique) (47) qui est réalisée sous la forme d'un engrenage différentiel et qui comporte deux bagues (50, 51) à denture intérieure qui sont à chaque fois reliées à un pignon (42 et 43, respectivement) et qui sont en prise avec une bague élastique commune (49) à denture extérieure dans laquelle est en prise un collet elliptique (48) fixé sur l'axe recevant les pignons (42, 43), lequel peut être déplacé dans la direction de la rotation au moyen d'un dispositif de réglage.
4. Plieuse selon la revendication 3, caractérisée par le fait que l'une des roues d'entraînement, de préférence la roue d'entraînement (34) qui entraîne le porte-armature (21) équipé de mâchoires de pliage (13), comporte deux couronnes dentées (34a, 34b) qui présentent des diamètres différents, dont l'une est en prise avec la roue d'entraînement associée (33) située du côté du cylindre collecteur, et dont l'autre l'est avec un pignon (42) de la transmission de liaison (40), la différence de vitesse produite par la différence des diamètres des couronnes dentées (41a, 41b) correspondant à la différence de vitesse entre les deux bagues (50, 51) à denture intérieure de la transmission à entraînement harmonique.
5. Plieuse selon la revendication 4, caractérisée par le fait que la couronne dentée (34b) qui présente le plus petit diamètre, lequel correspond au diamètre de l'autre roue d'entraînement (35), et qui est de préférence réalisée sous la forme d'un anneau posé latéralement, est en prise avec le pignon (42), et que la couronne dentée (34a) qui présente le plus grand diamètre est en prise avec la roue d'entraînement (33) située du côté du cylindre collecteur.
6. Plieuse selon l'une des revendications précédentes 2 à 5, caractérisée par le fait que l'axe (41) qui reçoit les pignons (42, 43) est monté tournant sur une paroi latérale (1) de la machine et sur une paroi de boîte parallèle à celle-ci d'une boîte d'engrenages rapportée (31), et qu'il est muni d'un embout d'entraînement (44) qui traverse la paroi de caisson et sur lequel est posée une roue de réglage (45 et 55, respectivement) du dispositif de réglage qui peut être entraînée de préférence au moyen d'un servomoteur (52) et qui est réalisée sous la forme d'un pignon conique, lequel coopère avec un pignon conique fixé sur l'arbre du servomoteur (52) qui est disposé perpendiculairement à l'axe (41).
7. Plieuse selon l'une des revendications précédentes, caractérisée par le fait qu'est associé à la transmission de liaison (40) un dispositif indicateur (53) qui peut être déplacé en synchronisme avec elle.
8. Plieuse selon l'une des revendications précédentes, caractérisée par le fait que le cylindre collecteur (3) se compose également d'au moins deux porte-armatures coaxiaux (23, 24) que l'on peut faire tourner l'un par rapport à l'autre, qui peuvent être entraînés à la même vitesse, qui sont garnis des plioirs (12) ou, respectivement, de picots (11) ou de pinces et de réglettes de coupe (7), et qui sont munis de roues d'entraînement coaxiales (32, 33) accouplées entre elles, quant à l'entraînement, au moyen d'une transmission de liaison déplaçable (39), la roue d'entraînement (33) du porte-armature (24) qui porte les plioirs (12) coopérant avec la couronne dentée (34a) du porte-armature (21) associé aux mâchoires de pliage (13) qui présente le plus grand diamètre, et l'autre roue d'entraînement (32) coopérant avec une roue d'entraînement entraînée (36) d'un cylindre de coupe (2) serré sur le cylindre collecteur (3).
9. Plieuse selon l'une des revendications précédentes 2 à 8, caractérisée par le fait que la transmission de liaison (39 et 40, respectivement) comporte deux pignons (42, 43) solidaires l'un de l'autre qui sont de préférence à dents obliques en sens opposés et qui, au moyen de l'axe (41) les recevant, peuvent être déplacés en direction axiale par rapport aux roues d'entraînement (32, 33) qui sont en prise avec eux par leurs dents et qui, de préférence, sont également à dents obliques en sens opposés.
10. Plieuse selon l'une des revendications précédentes 2 à 9, caractérisée par le fait que l'axe (41) qui reçoit les pignons (42, 43) est de préférence bloqué au moyen d'un dispositif de serrage (46).
EP88112683A 1987-08-07 1988-08-03 Dispositif à plier Expired - Lifetime EP0302489B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3726239 1987-08-07
DE19873726239 DE3726239A1 (de) 1987-08-07 1987-08-07 Falzapparat

Publications (3)

Publication Number Publication Date
EP0302489A2 EP0302489A2 (fr) 1989-02-08
EP0302489A3 EP0302489A3 (en) 1989-03-22
EP0302489B1 true EP0302489B1 (fr) 1991-07-31

Family

ID=6333241

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88112683A Expired - Lifetime EP0302489B1 (fr) 1987-08-07 1988-08-03 Dispositif à plier

Country Status (4)

Country Link
US (1) US4895356A (fr)
EP (1) EP0302489B1 (fr)
JP (1) JPS6481764A (fr)
DE (2) DE3726239A1 (fr)

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DE4225122A1 (de) * 1992-07-30 1994-02-03 Roland Man Druckmasch Vorrichtung zur Korrektur des Schnittregisters
DE4241810C2 (de) * 1992-12-11 2001-01-04 Heidelberger Druckmasch Ag Formatvariabler Kombinationsfalzapparat
DE4426987C2 (de) * 1994-07-29 1998-10-22 Roland Man Druckmasch Falzapparat mit Formatumstellung
DE19500929A1 (de) * 1995-01-16 1996-07-18 Zirkon Druckmaschinen Gmbh Einrichtung zur Steuerung von Falzvorgängen in Rollenrotationsdruckmaschinen
DE19516443A1 (de) * 1995-05-04 1996-11-07 Wifag Maschf Einzeln angetriebener Falzapparat für eine Rotationsdruckmaschine
DE19755428A1 (de) * 1997-12-13 1999-06-17 Roland Man Druckmasch Vorrichtung zum Verstellen der Falzmechanismen an einem Falzzylinder eines Falzapparates
DE10124977A1 (de) 2001-05-21 2002-11-28 Roland Man Druckmasch Antrieb für einen Zylinder einer Rotationsdruckmaschine
DE10148503C5 (de) * 2001-10-01 2008-01-31 Koenig & Bauer Aktiengesellschaft Falzapparat mit umfangsverstellbarem Zylinder
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CN105398091A (zh) * 2015-12-04 2016-03-16 王群 一种加工“n”边形纸管的设备
CN105398091B (zh) * 2015-12-04 2019-02-22 王群 一种加工“n”边形纸管的设备

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DE3863993D1 (de) 1991-09-05
US4895356A (en) 1990-01-23
EP0302489A3 (en) 1989-03-22
JPS6481764A (en) 1989-03-28
DE3726239C2 (fr) 1989-07-13
DE3726239A1 (de) 1989-02-16
EP0302489A2 (fr) 1989-02-08

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