EP0355595B1 - Appareil pour plier - Google Patents

Appareil pour plier Download PDF

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Publication number
EP0355595B1
EP0355595B1 EP89114780A EP89114780A EP0355595B1 EP 0355595 B1 EP0355595 B1 EP 0355595B1 EP 89114780 A EP89114780 A EP 89114780A EP 89114780 A EP89114780 A EP 89114780A EP 0355595 B1 EP0355595 B1 EP 0355595B1
Authority
EP
European Patent Office
Prior art keywords
cam
cams
cylinder
peripheral
cover
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
EP89114780A
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German (de)
English (en)
Other versions
EP0355595A2 (fr
EP0355595A3 (fr
Inventor
Sebastian Prüm
Trifon Panow
Emil Fischer
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Albert Frankenthal AG
Original Assignee
Albert Frankenthal AG
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Publication date
Application filed by Albert Frankenthal AG filed Critical Albert Frankenthal AG
Publication of EP0355595A2 publication Critical patent/EP0355595A2/fr
Publication of EP0355595A3 publication Critical patent/EP0355595A3/fr
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Publication of EP0355595B1 publication Critical patent/EP0355595B1/fr
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Classifications

    • 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

Definitions

  • the invention relates to a folding apparatus, in particular a variable folding apparatus for rotogravure printing presses, with a collecting cylinder which can be converted from collective production to non-collective production and is provided with holding elements and folding knives, preferably designed as a gripper, the holding elements and folding knives of which are connected to actuating elements, preferably designed as feeler rollers, which are connected by a each associated control cam can be controlled, the control area of which, preferably designed as a depression, can optionally be released or covered by means of a cover device provided with cover cams which are accommodated on a cam carrier which is coaxial with the cam cam and can be driven (EP-A-66 867 and 98 415).
  • the cover device contains a drivable cover plate with fixed cover cams.
  • the cover plate must run not only in the case of collective production, but also in the non-collective production which is more common in practice, which can lead to heavy loads and, accordingly, rapid wear.
  • the number of consecutive collecting operations is very limited in such an arrangement.
  • Experience has shown that a limit is reached in two consecutive collection processes. Three or more consecutive collection processes are practically impossible.
  • the printing press width increases and with it the forme cylinder diameter.
  • the common formats are becoming shorter and shorter, so that there are more etchings on the circumference than before, for example eight etchings on the circumference, which justifies a need for an increase in the collection processes.
  • variable cover plate can easily stand still in the case of non-collective production, all or at least the disruptive covering cams being simply retracted, which has an advantageous effect on avoiding unnecessary wear.
  • the covering cams can be adjustable by means of an adjusting disk which is coaxial with the cam carrier and which can be driven together with the cam carrier and is adjustable in relation to the latter in the circumferential direction.
  • These measures make it easy to adjust the cover cams by turning the adjusting disc, which enables automatic presetting.
  • the cam carrier and the associated, uniformly drivable adjusting disk can expediently be connected to one another in terms of drive by means of a differential gear which can be adjusted by means of an auxiliary drive device which can be passivated during production. After setting, the differential gear practically functions as a rigid transmission element.
  • a further advantageous measure can consist in that those assigned to the folding blades and the holding elements Cam carriers or adjusting disks are each connected to one another in a rotationally fixed manner, preferably releasably braced together. These measures enable the two cam carriers or the two adjusting disks to be driven together, which can simplify the construction very much and at the same time ensure high accuracy.
  • the control cams assigned to the folding knives or holding elements are advantageously axially offset from one another with such a distance that the two assigned covering devices can be placed between them.
  • control cam assigned to the holding elements can preferably be adjustable in the circumferential direction by means of an auxiliary drive device that can be passivated during production. This enables adaptation to the respective production in such a way that shorter formats are released earlier than longer ones.
  • a further advantageous measure to simplify the pressure cam arrangement and the adjusting disks can consist in the fact that the cover device can be driven at different speeds during collective production depending on the number of desired collecting processes.
  • the drive device assigned to the covering devices can have an intermediate shaft parallel to the cylinder, through which the cam carrier can directly and the adjusting disks can be driven with the interposition of the adjustable differential gear and which, in turn, can be coupled in register-precise manner by means of a coupling part which is displaceably arranged on it, each with an opposing, freely rotatable drive wheel of different diameter, which mesh with different limits of a double wheel which can be driven by a cylinder part.
  • the collecting cylinder 1 shown in FIG. 1 of a variable folding apparatus as it is usually arranged downstream of a rotogravure printing press, consists of two armatures with a star-shaped cross-section, which can be driven uniformly, in the form of a laterally mounted folding knife part 2 and a gripper part 3 mounted thereon provided with folding knives 5 which can be actuated by an actuating device 4.
  • the gripper part 3 is provided with gripper bars 8 which can be actuated by an actuating device 6 and which are provided with grippers 7.
  • drive wheels 11 of the same diameter are fastened next to each other, which can be coupled by a lock-up gear (not shown here) to achieve a uniform drive with simultaneous adjustment possibility.
  • control cams 12 and 13 which are provided coaxially to the cylinder axis and are scanned by the associated actuating devices 4 and 6, are provided in the region of the cylinder end face.
  • the actuating devices 4 and 6 each contain two feeler rollers 14, 15 arranged side by side on a common axis, of which one feeler roller 14 runs on the respectively assigned control cam 12 or 13 and the other feeler roller 15 on one of the control curve 12 or 13 neighboring covering device for lateral covering of the control cam-side control depression 16 runs, by means of which the folding knife 5 or gripper 7 is actuated.
  • control cams 12 and 13 have an arcuate circumferential contour.
  • the control sinks 16 are released with each revolution of the collecting cylinder 1 (non-collecting) or with every nth rotation of the collecting cylinder 1 (collecting) and are otherwise covered laterally.
  • the cover devices are provided with cover cams 17 arranged parallel to the respectively associated control cam 12 or 13.
  • the width of the feeler rollers 14 and 15 corresponds to the width of the control cams 12, 13 or the cover cam 17.
  • the control cams 12, 13 are at a standstill with respect to the driven collecting cylinder 1.
  • the control cam 12 provided for controlling the folding knives 5 is fixed to a bush 18, which comprises the outer bearing journal 9 and is fastened to the housing.
  • the control cam 13 assigned to the grippers 7 is fixed to a radially outer bush 19 which is rotatably mounted in the machine frame and to which an adjustment pocket 20 is fastened, by means of which the control cam 13 can be adjusted in the circumferential direction to adjust the opening time of the grippers 7.
  • the adjustment pocket 20 can be driven by means of an auxiliary drive device in the form of an auxiliary motor etc. provided for setting the format, or it can be easily operated by hand. During production, the adjustment tab 20 is secured against twisting.
  • the covering devices having the covering cams 17 and assigned to the control cams 12 and 13 are driven in relation to the standing control cams 12, 13 during production.
  • a drive sprocket 21 is flanged to the outer drive wheel 11, from which the drive of the two control cams 12 and 13, respectively, associated covering devices is derived.
  • the two cover devices each comprise, as shown schematically in FIG. 2 for the cover devices assigned to the control cam 12 associated with the folding knives, a cam carrier 22 arranged coaxially to the control cam in question, on which the cover cams 17 are accommodated so as to be adjustable in the radial direction.
  • the circumferential contour 23 of the covering cams 16 corresponds to a circular section with a radius corresponding to the radius of the control cam 12 which is circular outside the control depression 16 formed by a circumferential recess.
  • the circumferential contour 23 of the covering cams 17 can be brought by moving the covering cams 17 from a radially outer active position that overlaps with the circular arc-shaped contour of the associated control cam 12 into a passive position located radially inside the control depression.
  • the covering cams 17 cover them laterally as they pass the depression 16, so that the feeler roller 14 running on the control cam 12 or 13 in question passes over it on the control depression 16 by the adjoining sensing roller 15 running on a cover cam 17 is prevented from falling into the control depression 16 and triggering a folding process, as indicated at 15a.
  • the actuating device which is assigned to the folding knife 5 passing through the folding nip in FIG. 2, on the other hand, can fall into the control depression 16 and carry out a folding operation, as indicated at 14a.
  • an adjusting disk 24 is provided, which is arranged coaxially to the cam carrier 22 and is aligned in the axial direction with the cover cams 17 and is provided with fixed control cams 25 and circumferential recesses 26 located therebetween.
  • the cover cams 17 are each fastened to a swivel arm 27 which is pivotably mounted on the cam carrier 22 with an axially parallel swivel axis and are provided with a push button 28 which projects radially inwards is held in contact with the circumferential contour of the associated adjusting disk 24 by the action of a pressure spring 29.
  • the pressure spring 29 is received in a recess 30 of the associated cover cam 17 and is supported on the one hand at the inner end of the cam-side recess 30 and on the other hand on a pin 31 which projects into the recess 30 and is fastened to the cam carrier 22.
  • the adjusting disk 24 and the cam carrier 22 carrying the covering cams 17 are driven uniformly after adjustment of the adjusting disk 24 during operation, so that the covering cams 17 maintain their position caused by the adjusting disk 24 during operation.
  • the drive speed of the entire covering device formed by the cam carrier and adjusting disk is selected depending on the respective type of production so that the covering cams 17 that are issued pass the control depression 16 in such a way that only the desired number of folding operations is carried out.
  • the two cam carriers 22 and the two adjusting disks 24 of the respectively assigned covering devices can be firmly connected to one another in order to simplify the drive device required for the drive. Accordingly, as can also be seen from FIG. 1, the two control cams 12 and 13 are spaced further apart from one another in the axial direction in such a way that in between both cover devices, the are arranged with adjacent cam carriers 22, find space. The back-to-back cam carriers 22 are firmly clamped together by clamping devices.
  • the adjusting disks 24 which engage under the respective associated control cam 12 or 13 facing cover cams 17 are screwed together with the interposition of a spacer 32, the thickness of which corresponds to the total thickness of the cam carriers clamped together.
  • two bushes 33, 34 are provided in the area between the bushings 18, 19 carrying the control cams 12, 13, the radially inner bush 33 being the cam bearers 22 which lie directly against one another and the radially outer sleeve 34 carry the adjusting disks 24 connected to one another with the interposition of the spacer 32.
  • one of the adjusting disks 24 and one of the cam carriers 22 extends with its radially inner edge to the respectively assigned bushing 33 and 34 and is screwed to it.
  • the respective other adjusting disk 24 and the other cam carrier 22 can end further out.
  • the spacer 32 engages with its spacer jaws through this associated window of the cam carrier 22 fastened to the sleeve 34.
  • the other cam carrier 22 comprises the spacer 32.
  • the bushes 33, 34 carrying the adjusting disks 24 or the cam carriers 22 are rotatably mounted and are provided with flanged drive toothed rings 35, 36 of the same diameter at their ends remote from the cylinder are accommodated in a chamber 37 delimited by the housing parts receiving the control cam bushings 18, 19 and accessible from the gear box 38.
  • the drive sprockets 35, 36 mesh with associated intermediate wheels 39, 40 of the same diameter, which are mounted on the frame side.
  • the intermediate gear 40 located in the drive train assigned to the cam carriers 22 meshes with a pinion 42 wedged onto an intermediate shaft 41 arranged parallel to the cylinder axis outside the collecting cylinder diameter.
  • the intermediate gear 39 belonging to the drive train of the adjusting disks 24 meshes with a ring gear 43 of a double wheel mounted on the intermediate shaft 41 , whose two ring gears 43, 44 have the same diameter as the pinion 42.
  • This meshes with the input wheel 45 of a differential gear 46 arranged axially parallel to the intermediate shaft 41, the output gear 47 of which meshes with the second ring gear 44 of the double wheel rotatably mounted on the intermediate shaft 41.
  • the differential gear 46 allows the output wheel 47 to be adjusted with respect to the input wheel 45 having the same diameter by means of an auxiliary drive device 48.
  • the auxiliary drive device 48 is passivated, so that the differential gear 46 functions like a rigid double wheel.
  • the adjusting disks 24 can be brought into the desired rotational position by actuating the auxiliary drive device 48.
  • the intermediate shaft 41 mounted in the gearbox 38 is in turn at different speeds due to the drive sprocket 21 flanged to the outer drive wheel 11 drivable.
  • a double wheel with two sprockets 49, 50 of different diameters mounted on a pin fastened on the frame is provided, which in turn mesh with drive wheels 51, 52 of different diameters that are freely rotatable on the intermediate shaft 41.
  • These can alternatively be coupled to the intermediate shaft 41 by means of a coupling part 53 which is slidably wedged onto the intermediate shaft 41 and arranged between them.
  • the drive wheels 51, 52 are provided in the region of their mutually facing end faces with two axially projecting coupling claws 54, into which the coupling part 53 can be latched with corresponding recesses 55, so that there is a clear, register-accurate coupling.
  • the coupling part 53 can be shifted into a right engagement position by means of a shift lever 56 engaging in a circumferential groove from the left engagement position shown in FIG. 1 via a middle position in which there is no engagement. Appropriate actuation of the shift lever 56 can thus bring about two different speeds or standstill of the covering devices.
  • the cam carrier 22 is provided with eight adjustable cover cams 17, the circumferential contour 23 of which has a circumferential length corresponding to an arc dimension of approximately 15 °.
  • the eight cover cams 17 are distributed over two groups of four, each offset by 180 °, of four cover cams 17 distributed over 90 °, viewed in the clockwise direction the first and second circumferential cams are offset by 30 °, the second and third circumferential cams by 15 ° and the third and fourth circumferential cams by 45 °.
  • the adjusting disk 24 is provided with six fixed circumferential cams 25, which are distributed over two groups of three circumferential cams, which are offset by 180 ° relative to one another, being clockwise, that is in the direction of rotation, the first and second circumferential cams 25 viewed at 48, 25 ° and the second and third circumferential cams are offset from one another by 57, 25 °.
  • the circumferential cams 25 of the adjusting disk 24 have different circumferential lengths.
  • the first circumferential cam 25 measures 13.5 ° here.
  • the second circumferential cam 25 measures 1 °.
  • the third circumferential cam 25 measures 24.5 °.
  • the setting of the adjusting disk 24 on which FIG. 2 is based, and accordingly the cover cam 17, corresponds to the production method of collecting twice, resulting in a three-layer product.
  • This type of production often occurs when using a forme cylinder with six etchings on the circumference.
  • the adjusting disc 24 is set so that every second cover cam 17, here the second and fourth cover cams of each group, are issued.
  • the drive speed that is, the speed of the cam carrier 22 and the adjusting disks 24 is 6/7 of the cylinder speed. This has the effect that the seven folding knives on the circumference of the folding knife part 2 only find a released control depression 16 with every third rotation of the collecting cylinder 1 and carry out a folding process, as indicated in FIG. 2 at 14a.
  • the adjusting disk 24 is set such that the two inner covering cams 17 each group retracted and the two outer cover cams 17 are issued each group.
  • the four covering cams 17 are accordingly offset from one another by 90 °.
  • the drive speed for this type of production is 7/8 of the cylinder speed.
  • the adjusting disk 24 is set in such a way that all covering cams 17 except the second one Cover cams of each group are issued.
  • the drive speed for this type of production is also 7/8 of the cylinder speed. Accordingly, when changing from one-time collection or three-time collection to two-time collection, coupling part 53 be shifted from one engagement position to the other engagement position.
  • the structure and the mode of operation of the covering device assigned to the gripper control correspond to the covering device of the folding knife control on which the FIGS. 2 to 5 are based only with the difference that the grippers 7 holding the beginning of the sheet have already passed through the folding gap when the folding operation is carried out.
  • the activation of the folding knife 5 and the opening of the gripper 7 therefore takes place essentially simultaneously.
  • these processes extend over a certain period of time, with the grippers 7 opening somewhat earlier when processing short products should than when processing longer products, which can be accomplished by means of the adjusting bracket 20 due to the rotatability of the gripper-side control cam 13 already described above.
  • the gripper bars 8 and the folder 5 are divided over the cylinder length, with each cylinder side being assigned its own control device.
  • the construction of these two control devices can correspond to the design of the control device for the right cylinder half shown in FIG. 1, with the only difference that the intermediate shaft 41 cannot be coupled to the cylinder drive via an associated claw coupling, but by means of a bridging shaft 57 with the opposite intermediate shaft 41 is connected, as shown in Figure 1. This results in a common drive shaft that extends across the entire width of the cylinder.
  • the cover cams are adjusted by means of assigned adjusting disks 24, which enables automatic presetting by appropriate programming of the auxiliary drive device 48.
  • the cam carrier 22 would simply have to be provided with suitable tensioning devices for holding the cover cams 17.

Landscapes

  • Folding Of Thin Sheet-Like Materials, Special Discharging Devices, And Others (AREA)

Claims (10)

  1. Appareil de pliage, en particulier appareil de pliage variable pour une presse rotative pour l'héliogravure, comportant un cylindre collecteur (1) muni d'éléments de retenue et de plioirs (5) réalisés de préférence en forme de griffes (7), réversible entre une production par accumulation et une production par non-accumulation, dont les éléments de retenue et les plioirs sont reliés à des éléments d'entraînement réalisés de préférence en forme de rouleaux danseurs (14, 15) qui peuvent être commandés par une came de commande (12 ou 13) qui leur est respectivement attribuée, dont la zone de commande réalisée de préférence en forme d'encoche de commande (16) peut être sélectivement libérée ou recouverte au moyen d'un mécanisme de recouvrement coaxial à la came de commande (12 ou 13), muni de cames de recouvrement (17) logées sur un support de cames actionnable (22), caractérisé en ce que les cames de recouvrement (17) de chaque mécanisme de recouvrement sont logées sur le support de cames qui leur est respectivement attribué en étant mobiles en direction radiale.
  2. Appareil de pliage selon la revendication 1, caractérisé en ce que les cames de recouvrement (17), qui présentent de préférence un contour périphérique (23) en forme d'arc de cercle qui peut s'étaler jusqu'à atteindre un rayon correspondant au rayon de la came de commande (12 ou 13) de forme circulaire à l'extérieur de la zone de commande, peuvent être déplacés au moyen d'un disque de déplacement (24) coaxial au support de cames (22), qui peut être entraîné conjointement avec le support de cames (22) et qui peut se déplacer par rapport à ce dernier en direction périphérique, les cames de recouvrement (17) étant fixées de préférence à un bras pivotant (27) monté en pivotement sur le support de cames (22) et étant munies d'un palpeur (28) disposé à côté du support de cames (22) et qui peut être pressé contre le disque de déplacement (24) muni de cames périphériques fixes (25).
  3. Appareil de pliage selon la revendication 2, caractérisé en ce que les palpeurs (28) peuvent être pressés respectivement contre le disque de déplacement au moyen d'un ressort (29) et en ce que les ressorts (29) viennent se loger dans un évidement (30) de la came de recouvrement (17) qui leur est respectivement attribuée et viennent s'appuyer contre la broche (31) fixée au support de cames (22) et faisant saillie à l'intérieur de l'évidement.
  4. Appareil de pliage selon l'une quelconque des revendications précédentes 2 à 3, caractérisé en ce que le support de cames (22) et le disque de déplacement (24) qui lui est attribué et qui peut être entraîné de manière uniforme avec ce dernier sont reliés l'un à l'autre en entraînement au moyen d'un engrenage différentiel (46) qui peut être réglé au moyen d'un mécanisme d'entraînement auxiliaire (48) que l'on peut rendre passif lors d'une production en continu, et en ce que, de préférence, la came de commande (13) attribuée aux éléments de retenue est mobile en direction périphérique au moyen d'un mécanisme d'entraînement auxiliaire que l'on peut rendre passif lors d'une production en continu.
  5. Appareil de pliage selon l'une quelconque des revendications précédentes 2 à 4, caractérisé en ce que les supports de came (22) ou les disques de déplacement (24) attribués aux plioirs (5) et aux éléments de retenue réalisés de préférence à l'intervention de griffes (7) sont reliés respectivement l'un à l'autre en étant immobiles en rotation, de préférence sont mutuellement verrouillés de manière amovible, et en ce que, de préférence, les cames de commande (12, 13) attribuées aux plioirs ou aux éléments de retenue sont écartées l'une de l'autre en direction axiale, des mécanismes de recouvrement disposés entre deux supports de came (22) tournés l'un vers l'autre venant s'y loger.
  6. Appareil de pliage selon l'une quelconque des revendications précédentes, équipé d'un cylindre collecteur à 7 éléments, en particulier, pour une presse rotative pour l'héliogravure comportant jusqu'à huit gravures à la périphérie du cylindre porte-clichés, caractérisé en ce qu'on prévoit huit cames de recouvrement (17) à la périphérie de chaque support de cames (22), présentant une mesure d'arc périphérique de préférence d'environ 15°, deux groupes de cames de recouvrement mutuellement décalés de 180° et comportant chacun quatre cames de recouvrement (17) étant prévus de préférence, dans lequel on prévoit respectivement, entre le milieu du contour périphérique de la première et de la deuxième cames périphériques (17), une distance de 30°, de la deuxième et de la troisième cames périphériques (17), une distance de 15° et de la troisième et de la quatrième cames périphériques (17), une distance de 45°.
  7. Appareil de pliage selon la revendication 6, caractérisé en ce que chaque disque de déplacement (24) présente six cames périphériques (25) respectivement séparées l'une de l'autre par un évidement périphérique (26) et peut être amené dans quatre positions périphériques avec des positions différentes des cames de recouvrement (17) correspondant aux types de production par accumulation triple, par accumulation double, par accumulation simple ou par non-accumulation, dans lequel on prévoit de préférence, sur chaque disque de déplacement (24), deux groupes de cames respectivement décalés l'un de l'autre de 180° et comportant chacun trois cames périphériques (25) de longueur différente dont, de préférence, les premières cames périphériques (25) présentent une longueur périphérique d'environ 13,5°, les deuxièmes, une longueur d'environ 1° et les troisièmes, une longueur d'environ 24,5°; et dans lequel, de préférence, on prévoit respectivement entre la première et la deuxième cames périphériques (25), une distance moyenne d'environ 48,25° et entre la deuxième et la troisième, une distance d'environ 57,25°.
  8. Appareil de pliage selon l'une quelconque des revendications précédentes, caractérisé en ce que l'entraînement de chaque support de cames (22) et éventuellement de chaque disque de déplacement (24) peut être mis hors-circuit, et en ce que chaque support de cames (22) et éventuellement les disques de déplacement (24) qui peuvent être entraînés de manière uniforme avec ces derniers, peuvent être entraînés avec deux vitesses différentes en fonction du type de production désiré, dans lequel, de préférence, la vitesse d'entraînement des supports de cames (22) et éventuellement des disques de déplacement (24) correspondant, dans le cadre d'une production par accumulation avec un nombre pair de processus successifs de production par accumulation, à 7/6 de la vitesse de rotation du cylindre collecteur (1) et, avec un nombre impair de processus successifs de production par accumulation, à 7/8 de la vitesse de rotation du cylindre collecteur (1).
  9. Appareil de pliage selon la revendication 8, caractérisé en ce que, dans le train d'entraînement cinétique des supports de came (22) et éventuellement des disques de déplacement (24), on prévoit un embrayage (54, 55) comprenant deux positions d'engrènement définies et une position de non-engrènement, le train d'entraînement présentant de préférence un arbre intermédiaire (41) parallèle à l'axe du cylindre, par lequel les supports de came (22) et les disques de déplacement (24) peuvent être entraînés en intercalant un engrenage différentiel réglable (46), et qui peut être accouplé, à son tour, au moyen d'un élément d'accouplement (53) sur lequel il est disposé en coulissement, en correspondance précise avec, respectivement, une des roues d'entraînement (51 ou 52) mutuellement opposées et de diamètre différent, et sur lequel elles sont montées en rotation libre, qui viennent s'engrener avec des couronnes dentées différentes (49 ou 50) d'un pignon coulissant qui peut être entraîné par un élément cylindrique et dans lequel, de préférence, l'engrènement différentiel (46) est disposé radialement à l'extérieur de l'arbre intermédiaire (41) et présente des roues d'entrée et de sortie (45 ou 47) présentant le même diamètre, dont la roue d'entrée (45) vient s'engrener avec un pignon (42) fixé sur l'arbre intermédiaire (17), qui vient s'engrener simultanément avec une des roues intermédiaires (40) attribuées aux supports de came (22), qui est disposée à côté d'une roue intermédiaire (49) de même diamètre attribuée aux disques de déplacement (24), qui vient s'engrener avec une couronne dentée (43) d'un pignon coulissant monté en rotation libre sur l'arbre intermédiaire (41) à côté du pignon (42) et présentant deux couronnes dentées (43 ou 44) dont le diamètre est identique à celui du pignon (42), et dont l'autre couronne dentée (44) vient s'engrener avec la roue de sortie (47) de l'engrenage différentiel (46).
  10. Appareil de pliage selon la revendication 9, caractérisé en ce que, dans le cadre d'un cylindre collecteur (1) dont la largeur est doublée, comportant des lattes de griffes et des plioirs répartis sur la longueur du cylindre et un mécanisme de commande disposé dans la zone des deux faces frontales du cylindre, muni de cames de commande (12 ou 13) et de mécanismes de recouvrement attribués à ces dernières munis de supports de cames (22) actionnables et de disques de déplacement (24) qui peuvent être entraînés de préférence de manière uniforme avec ces derniers, les arbres intermédiaires (41) prévus respectivement dans le train d'entraînement, dont un peut être accouplé au mécanisme d'entraînement du cylindre à l'intervention d'un embrayage, sont disposés radialement à l'extérieur de la périphérie du cylindre et peuvent être accouplés à l'intervention d'un arbre intermédiaire (57) s'étendant sur la longueur du cylindre.
EP89114780A 1988-08-20 1989-08-10 Appareil pour plier Expired - Lifetime EP0355595B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3828372 1988-08-20
DE3828372A DE3828372C2 (de) 1988-08-20 1988-08-20 Falzapparat

Publications (3)

Publication Number Publication Date
EP0355595A2 EP0355595A2 (fr) 1990-02-28
EP0355595A3 EP0355595A3 (fr) 1991-01-09
EP0355595B1 true EP0355595B1 (fr) 1993-10-27

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EP89114780A Expired - Lifetime EP0355595B1 (fr) 1988-08-20 1989-08-10 Appareil pour plier

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US (1) US5000433A (fr)
EP (1) EP0355595B1 (fr)
JP (1) JPH0747433B2 (fr)
DE (2) DE3828372C2 (fr)

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DE4041613A1 (de) * 1990-02-19 1991-08-22 Frankenthal Ag Albert Falzapparat
DE4117205A1 (de) * 1991-05-27 1992-12-03 Frankenthal Ag Albert Falzapparat
FR2711576B1 (fr) * 1993-10-26 1996-01-19 Heidelberg Harris Sa Dispositif de commande de l'accumulation ou non accumulation d'un cylindre coupeur-accumulateur d'une plieuse.
DE4404752C2 (de) * 1994-02-15 1995-11-16 Roland Man Druckmasch Vorrichtung zum Verstellen der Falzklappen eines Falzklappenzylinders
DE4408201C2 (de) * 1994-03-11 2000-06-29 Roland Man Druckmasch Falzzylinder
DE4408200C2 (de) * 1994-03-11 1999-02-25 Roland Man Druckmasch Falzzylinder
DE4408202C2 (de) * 1994-03-11 1999-02-25 Roland Man Druckmasch Falzzylinder
FR2726259B1 (fr) * 1994-10-27 1997-01-17 Heidelberg Harris Sa Dispositif de changement de mode d'un cylindre d'accumulation d'une plieuse
DE29502957U1 (de) * 1995-02-22 1995-04-06 MAN Roland Druckmaschinen AG, 63075 Offenbach Zylinder in einem Falzwerk mit vertellbarem Durchmesser
DE29507222U1 (de) * 1995-04-29 1995-06-29 MAN Roland Druckmaschinen AG, 63075 Offenbach Vorrichtung zum Verstellen der Falzklappen eines Falzklappenzylinders
DE19616629A1 (de) * 1995-08-23 1997-11-06 Heidelberg Harris Sa Vorrichtung zur Umstellung eines produktführenden Zylinders am Falzapparat
DE19625083C1 (de) * 1996-06-22 1997-11-13 Koenig & Bauer Albert Ag Getriebe
US6250622B1 (en) 1999-05-20 2001-06-26 Heidelberger Druckmaschinen Aktiengesellschaft Cylinder assembly for a folding apparatus of a rotary printing press
US6550385B1 (en) 1999-07-12 2003-04-22 Heidelberger Druckmaschine Ag Cam-independent drive for folding components
FR2796371B1 (fr) * 1999-07-12 2002-10-18 Heidelberger Druckmasch Ag Cylindre de pliage ainsi que procede, plieuse et machine a imprimer rotative faisant application d'un tel cylindre
US6684746B2 (en) 1999-12-02 2004-02-03 Heidelberger Druckmaschinen Ag Variable-length cut-off folder and method
US7137554B2 (en) * 2000-02-23 2006-11-21 Dynetics Engineering Corporation, Inc. Card mailer system and method of preparing card packages for mailing
US6547232B2 (en) * 2000-12-01 2003-04-15 Heidelberger Druckmaschinen Ag Device and method for switching between collect and straight modes on a folder
DE10121559C1 (de) * 2001-05-03 2002-10-10 Koenig & Bauer Ag Zylinder eines Falzapparats
DE102004020302B3 (de) * 2004-04-26 2005-08-18 Koenig & Bauer Ag Temperaturüberwachung in einer Maschine
DE102004020305A1 (de) 2004-04-26 2005-11-17 Koenig & Bauer Ag Falzapparat für Sammelbetrieb
DE102004020304B4 (de) * 2004-04-26 2007-11-29 Koenig & Bauer Aktiengesellschaft Zylinder für die Bearbeitung von Flachmaterial
DE102005017232B4 (de) * 2005-04-14 2016-04-28 Manroland Web Systems Gmbh Sammelzylinder eines Falzapparats einer Druckmaschine
US7530209B2 (en) * 2006-09-22 2009-05-12 Philip Morris Usa Inc. Coupon positioning and rotation wheel
EP2030931B1 (fr) 2007-09-03 2013-06-12 Koenig & Bauer Aktiengesellschaft Appareil de pliage variable et imprimantes dotées d'un appareil de pliage
DE102007055866B4 (de) 2007-09-03 2014-12-24 Koenig & Bauer Aktiengesellschaft Variabler Falzapparat und Druckmaschinen mit einem Falzapparat

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Also Published As

Publication number Publication date
EP0355595A2 (fr) 1990-02-28
JPH02106561A (ja) 1990-04-18
DE58906008D1 (de) 1993-12-02
DE3828372A1 (de) 1990-02-22
EP0355595A3 (fr) 1991-01-09
DE3828372C2 (de) 1995-12-21
US5000433A (en) 1991-03-19
JPH0747433B2 (ja) 1995-05-24

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