EP0370206B1 - Auslegeeinrichtung für Bogen - Google Patents

Auslegeeinrichtung für Bogen Download PDF

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Publication number
EP0370206B1
EP0370206B1 EP89117985A EP89117985A EP0370206B1 EP 0370206 B1 EP0370206 B1 EP 0370206B1 EP 89117985 A EP89117985 A EP 89117985A EP 89117985 A EP89117985 A EP 89117985A EP 0370206 B1 EP0370206 B1 EP 0370206B1
Authority
EP
European Patent Office
Prior art keywords
catching
stop
lever
stops
spring
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
EP89117985A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0370206A1 (de
Inventor
Reinhold Max
Karl-Heinz Filsinger
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.)
Heidelberger Druckmaschinen AG
Original Assignee
Heidelberger Druckmaschinen 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6366008&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0370206(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Heidelberger Druckmaschinen AG filed Critical Heidelberger Druckmaschinen AG
Publication of EP0370206A1 publication Critical patent/EP0370206A1/de
Application granted granted Critical
Publication of EP0370206B1 publication Critical patent/EP0370206B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • B65H31/00—Pile receivers
    • B65H31/32—Auxiliary devices for receiving articles during removal of a completed pile
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2801/00—Application field
    • B65H2801/03—Image reproduction devices
    • B65H2801/21—Industrial-size printers, e.g. rotary printing press

Definitions

  • the invention relates to a delivery device for sheets which are output by means of transport in a conveying direction from a sheet-processing machine and are optionally placed on a stack or on catch arms of a catch device, the catch arms of which can be temporarily shifted from a basic position into a catch position above the stack, with on Stacked stops, which can be folded away from the stack in the conveying direction, for the respective leading edges of the sheets and with a gear arrangement for moving the catch arms from the basic position into the catch position and vice versa and for folding the stops against the action of a stop spring in the conveying direction into a release position and in an opposite direction in a stop position on the stack by means of a common actuator, the gear arrangement being designed such that the folding of the stops into the release position following the shifting of the tentacles in d The catching position is done.
  • Such a device is known from DE-PS 23 01 840.
  • at least the stops are to be held in their release position against the action of a stop spring by means of a manual force, while in one exemplary embodiment according to FIGS. 4 and 5, a bow catcher device is automatically held in the basic position and in the catching position.
  • pneumatic actuating and switching means in the form of pneumatic cylinders and corresponding control means in the form of a cam disk are provided.
  • both the stops are in their release position against the To hold the action of the stop spring and the bow catcher in its catch position against the action of another spring by hand.
  • An operator therefore has only one hand free for removing a test sheet from the stack and, depending on the required restoring forces of the springs mentioned, may have to apply a not inconsiderable actuating force simultaneously with the other hand to remove a sample sheet.
  • the object of the invention is therefore such an embodiment of a generic delivery device that it is characterized by simple structure and easy handling.
  • a dead center spring which is pivotable with respect to a pivot axis is articulated to the gear arrangement and which, in a first end position of the gear arrangement, holds the catch arms in the basic position against the action of at least one tension spring and in a second end position of the gear arrangement holds the stops against the action of the stop spring in the release position.
  • the gear arrangement is automatically held in both end positions. This makes it much easier to remove a sample sheet from the stack.
  • the full effective spring force of one of the springs provided need not be overcome by means of a corresponding manual force on the actuator, since the dead center spring counteracts either the tension springs or the stop spring.
  • the easy handling achieved with the invention is therefore also characterized in that only small forces for adjusting the actuator Gear arrangement in their end positions are required. This also enables a sample sheet to be removed conveniently within a very short time.
  • the gear arrangement can be designed as a simple lever gear which is suitable on the one hand for displacing the catch arms and on the other hand for folding the stops.
  • pneumatic actuating and switching means in particular are therefore unnecessary in order to ensure that at least individual gear parts remain in an end position on their own.
  • the actuator can also be adjusted by means of an actuator. With manual adjustment of the actuating part, any connection of the same with control lines and lines for energy supply is unnecessary in a delivery device according to the invention, so that overall a very simply constructed device is obtained, which is then also extremely less prone to failure.
  • An advantageous embodiment of the subject matter of the invention is characterized by an articulation of the dead center spring on a crank arm that can be pivoted by means of the actuating element, a first articulated connection of the crank arm provided with a first limited dead gear with a rocker arm, by means of which the tentacles can be displaced into the catching position and into the basic position are and a second articulated connection of the crank arm provided with a second limited dead gear with a stop lever, by means of which the stops can be folded into the release position and into the stop position.
  • the articulated connections are characterized according to an advantageous embodiment of the subject matter of the invention in that the first articulated connection is established by means of a first link which is articulated on the one hand on the rocker arm and on the other hand a first extending in the longitudinal direction of the first link Has an elongated hole in which a crank pin of the crank arm engages, and that the second articulated connection is established by means of a second link which is articulated on the crank pin of the crank arm and on the other hand has a second elongated hole running in the longitudinal direction of the second link, into which a engages driver pin connected to the stop lever.
  • a particularly compact design, in particular of the safety gear, is obtained in accordance with a further embodiment of the subject matter of the invention in that the rocker arm is fixedly connected to a rocker shaft, the rocker shaft is in turn connected to safety levers, one safety arm is articulated to one safety lever and is otherwise slidably supported, and that the tension springs are designed as leg springs and are each arranged between a catch lever and a catch arm articulated thereon and strive to rotate the tilting shaft in the sense of a displacement of the catch arms into the catch position.
  • the tension springs press the rocker arm in the catch position of the catch arms against a first stopper and that the stop spring presses the stop lever in the stop position of the stops against a second stopper.
  • additional means for slidably supporting the catch levers can be dispensed with in that the catch arms are slidably supported on a stop shaft which is in each case rotatably connected to the stop lever and the stops.
  • the extension device according to the invention can also be used in conjunction with means by means of which the Stops a pivoting movement for pushing a side of the stack assigned to the stops is communicated.
  • the drawing does not show the means of transport by means of which sheets are output in a conveying direction from a sheet-processing machine.
  • Such means of transport are known for example from the already mentioned DE-PS 23 01 840.
  • An embodiment of a gear arrangement of a delivery device is drawn in a first end position, in which the sheets are deposited on the stack 1 indicated by dash-dotted lines. From Catch arms arranged transversely to the conveying direction over the width of the stack 1, for the sake of simplicity, only one catch arm 2 is drawn. A respective catch arm 2 assumes a basic position in the drawn first end position of the gear arrangement and can be temporarily shifted out of this into a catch position above the stack 1 by means of the gear arrangement. This catch position of the catch arms 2 is assumed in a second end position of the gear arrangement.
  • stop 3 From stops arranged transversely to the conveying direction over the width of the stack 1 for respective leading edges of the sheets, only one stop 3 is also drawn.
  • a respective stop 3 assumes a stop position on the stack 1 in the drawn first end position of the gear arrangement and can be folded out of it by means of the gear arrangement against the action of a stop spring 4 in the conveying direction into a release position.
  • the release position of a respective stop 3 is also assumed in the second end position of the gear arrangement.
  • a respective catch arm 2 is moved and a respective stop 3 is folded by means of a common actuating element 5.
  • the gear arrangement is designed in such a way that each stop 3 is folded into the release position following the displacement of each catch arm 2 into the catch position.
  • the drawing shows the assignment of such a gear arrangement to a first side wall 8 of the delivery device, which faces a first side of the stack 1.
  • a similar assignment can also be made with regard to a second side wall (not shown) be met, which faces the second side of the stack 1.
  • a dead center spring 6 is articulated to the gear arrangement and can be pivoted with respect to a pivot axis 7.
  • the pivot axis 7 is mounted in the side wall 8 of the delivery device.
  • the pivot axis 7 carries a first support part 9, which is penetrated by one end of a guide shaft 10 of the dead center spring 6 designed as a helical spring, transversely to the longitudinal axis of the pivot axis 7.
  • the other end of the guide shaft 10 is fastened to a second support part 11, which in turn is connected in an articulated manner to the gear arrangement by means of a joint pin 12 parallel to the pivot axis 7.
  • the dead center spring 6 is clamped between the first support part 9 and the second support part 11.
  • the installation length of the dead center spring 6 is adjustable by means of a nut 13 which is screwed onto a thread of the end of the guide shaft 10 penetrating the first support part 9, so that the dead center spring 6 can be installed with an adjustable preload.
  • the articulated connection of the dead center spring 6 is provided on a crank arm 14 of the gear arrangement.
  • the crank arm 14 is fixedly connected to the actuating member 5 and can be pivoted with respect to a horizontal crank axis 15 arranged transversely to the conveying direction.
  • the crank axis 15 is mounted on at least one side wall 8.
  • only a part of the first side wall 8 is shown in the drawing and, in particular, that part which is penetrated by the crank axis 15 is broken off.
  • a tilt shaft 16 is rotatably mounted in each side wall 8.
  • the tilting shaft 16 is, seen in the conveying direction, arranged behind the stack 1 and in each case non-rotatably connected to a respective catch lever 17 assigned to a catch arm 2, to which a catch arm 2 is articulated.
  • the catch arms 2 are in the first end position of the gear arrangement shown in the drawing, seen in the conveying direction, also behind the stack and in the exemplary embodiment shown are slidably supported on their end facing the stack 1 on a stop shaft 27, which will be discussed in more detail below .
  • a tension spring 18 designed as a leg spring is arranged, of which a first leg 19 is supported against the catch lever 17 and a second leg 20 against the catch arm 2 such that forces exerted by the respective tension springs 18 Strive to rotate the tilting shaft 16 in the sense of a displacement of the catch arms 2 into the catch position, in which the catch arms 2 are pushed over the stack 1 against the conveying direction.
  • the catch arms 2 are now held in the basic position by means of the dead center spring 6 against the action of the tension springs 18.
  • the rocker shaft 16 is rotatably connected to a rocker arm 21 and a first articulated connection of the rocker arm 14 with the rocker arm 21 is provided, so that the rocker arm 21 can be pivoted in a first and an opposite second direction by means of the crank arm 14, whereby the rocker shaft 16 and the catch levers 17 connected to this in a rotationally fixed manner each result in a displacement of the catch arms 2 into the catch position or into the basic position.
  • the dead center spring 6 now exerts on the rocker arm 14 and on its first articulated connection with the rocker arm 21 in the first end position of the gear arrangement shown in the drawing on the rocking shaft 16 a torque rotating clockwise in the drawing, while by the efforts of the tension springs 18, to rotate the tilt shaft 16 in the sense of a displacement of the catch arms 2 into the catch position, on the tilt shaft 16 a torque directed counterclockwise is exerted.
  • This counterclockwise moment is caused by the support of the catch arms 2 on the stop shaft 27, by the efforts of the tension springs 18 to enlarge the angle enclosed between the first leg 19 and the second leg 20 of the respective tension spring 18 and by the resultant effort of the respective catch lever 17 to pivot counterclockwise with respect to the longitudinal axis of the rocker shaft 16.
  • the aforementioned first articulated connection of the rocker arm 14 to the rocker arm 21 is produced by means of a first link 22, which is articulated on the rocker arm 21 by means of a further articulation pin 23 and on the other hand has an elongated hole 24 in the longitudinal direction of the first link 22, in which a crank pin 25 of the crank arm 14 engages.
  • the clockwise rotating torque acting on the tilt shaft 16 is thus caused by the fact that the dead center spring 6 causes the crank pin 25 to rest on the upper end in the drawing of the first elongated hole 24 and thus the first link 22 acts as a push crank rod on the hinge pin 23.
  • This stop lever 26 is non-rotatably connected to a stop shaft 27, which is also parallel to the crank axis 15 and is rotatably mounted in the side walls 8 of the delivery device.
  • the stops 3 are rotatably connected to the stop shaft 27 and are in the first end position of the gear arrangement in the stop position in the drawing. In the exemplary embodiment shown, the stops 3 are folded into the release position by rotating the stop shaft 27 in a clockwise direction by means of the stop lever 26 connected in a rotationally fixed manner to the stop shaft 27. The stop lever 26 is rotated in this sense by means of the second articulated connection of the stop lever 26 Crank arm 14.
  • This second articulated connection is established by means of a second link 28, which is articulated on the one hand on the crank pin 25 of the crank arm 14 and on the other hand has a second elongated hole 29 running in the longitudinal direction of the second link 28, into which a driver pin connected to the stop lever 26 30 engages.
  • the actuating member 5 pivots the crank arm 14 clockwise with respect to the longitudinal axis of the crank axis 15. This pivoting movement enables the tension springs 18 to rotate the tilt shaft 16 counterclockwise and thus to shift the catch arms 2 into the catch position.
  • the gear arrangement is designed such that the stops 3 are folded into the release position following the shifting of the catch arms 2 into the catch position. This can be seen when tracking the above-mentioned pivoting movement of the crank arm 14 on its way from the first to the second end position of the gear arrangement.
  • a stop part 31 of the rocker arm 21 bears against a first stop 32, which in the exemplary embodiment is designed as a bolt fastened in the side wall 8.
  • a limited first dead gear in the form of the first elongated hole 24 in the first articulated connection existing between the rocker arm 14 and the rocker arm 21 allows following the first portion of the pivoting movement of the crank arm 14 to pivot it further into the second end position of the gear arrangement without having any effect on the Catch arms 2, since during this further pivoting the crank pin 25 can move against the lower end of the first elongated hole 24 in the drawing.
  • the first link 22 is pivoted only with respect to the pivot pin 23.
  • a limited second dead gear in the form of the second elongated hole 29 in the second articulated connection existing between the crank arm 14 and the stop lever 26, on the other hand, has the consequence that the second link 28 during the above-mentioned first part of the pivoting movement of the crank arm 14 in the direction of the second End position of the gear arrangement has no effect on the stop lever 26; rather, the second elongated hole 29 only migrates with respect to the driving pin 30 and the right end of this elongated hole 29 in the drawing reaches the driving pin 30 only when the pivoting continues Crank arm 14 beyond said first section of the pivoting movement.
  • this stop spring 4 is designed as a tension spring and is hooked in on the one hand to a bolt 33 fastened in the side wall 8 and on the other hand to a further bolt 34 fastened in the stop lever 26.
  • This further bolt 34 is arranged at a distance from the longitudinal axis of the stop shaft 27 that the stop spring 4 exerts on the stop lever 26 in the drawing rotating counterclockwise torque, which counteracts a clockwise rotating torque, which acts on the stop lever 26 when, during the mentioned further pivoting of the rocker arm 14 beyond the mentioned first section of the pivoting movement of the crank arm 14, the right end of the second elongated hole 29 in the drawing bears on the driving pin 30.
  • the dead center spring 6 passes through its dead center position when the hinge pin 12 is located on a connecting line between the center of the axis of the crank axis 15 and the pivot axis 7. With the pivot pin 12 in the drawing above this dead center position, that is to say in particular in the first end position of the gear arrangement, the dead center spring 6 now counteracts the tension springs 18 until the stop part 31 is placed against the first stopper 32.
  • the in the first end position of the Gear arrangement of the tension springs 18 on the one hand and forces exerted by the dead center spring 6 on the other hand are in particular matched to one another in such a way that the gear arrangement is held in the first end position by means of the dead center spring 6.
  • the tension springs 18 no longer exert any effect on the crank arm 14 when the pivoting continues.
  • the dead center spring 6 now acts against the crank pin 25 at the bottom of the first elongated hole 24 in the drawing, in particular in the second end position of the gear arrangement the effect of the stop spring 4.
  • the forces exerted in the second end position of the gear arrangement by the dead center spring 6 on the one hand and by the stop spring 4 on the other hand are in particular coordinated with one another in such a way that the gear arrangement is held in the second end position by means of the dead center spring 6.
  • a second stopper 35 is provided in the form of a bolt fastened in the side wall 8, against which the stop lever 26 is placed in the first end position of the gear arrangement.
  • the gear arrangement is formed by a special design of the second elongated hole 29 and a control surface 36 of the stop lever 26 for using the delivery device with a device for pushing the side of the stack 1 defined by the stops 3.
  • the control surface 36 cannot be used, for example Control cam shown work together, which causes periodic deflections on the stop lever 26 by small pivoting angle against the action of the stop spring 4.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sheets, Magazines, And Separation Thereof (AREA)
  • Pile Receivers (AREA)
  • Transmission Devices (AREA)
EP89117985A 1988-10-27 1989-09-28 Auslegeeinrichtung für Bogen Expired - Lifetime EP0370206B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3836571A DE3836571A1 (de) 1988-10-27 1988-10-27 Auslegeeinrichtung fuer bogen
DE3836571 1988-10-27

Publications (2)

Publication Number Publication Date
EP0370206A1 EP0370206A1 (de) 1990-05-30
EP0370206B1 true EP0370206B1 (de) 1992-12-02

Family

ID=6366008

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89117985A Expired - Lifetime EP0370206B1 (de) 1988-10-27 1989-09-28 Auslegeeinrichtung für Bogen

Country Status (6)

Country Link
US (1) US5005822A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
EP (1) EP0370206B1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
JP (1) JPH0633123B2 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
CN (1) CN1019905C (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
CA (1) CA1325023C (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
DE (2) DE3836571A1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4241787A1 (de) * 1992-12-11 1994-06-16 Heidelberger Druckmasch Ag Ausleger einer Bogendruckmaschine
DE4442385C1 (de) * 1994-11-29 1996-01-04 Heidelberger Druckmasch Ag Vorrichtung zur Bildung eines Stapels aus einem Bogenstrom
US5544583A (en) * 1995-06-08 1996-08-13 A.B. Dick Company Delivery interrupt mechanism for a printing machine
JP3500248B2 (ja) * 1996-05-13 2004-02-23 理想科学工業株式会社 排紙台装置

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE22249C (de) * CH. werner und K. berg in Friedberg, Grofsh. Hessen Ventilationskappe mit Windrädern
DE605130C (de) * 1933-02-17 1935-02-14 Faber & Schleicher Akt Ges Vorrichtung zum Aussondern einzelner Bogen in der Auslage von Druckmaschinen o. dgl.von Hand
FR896064A (fr) * 1942-04-07 1945-02-12 Roland Offsetmaschf Mécanisme permettant de séparer des feuilles individuelles dans le receveur de machines à imprimer et similaires
US2631038A (en) * 1948-06-15 1953-03-10 Harris Seybold Co Sheet delivery mechanism
DE913181C (de) * 1952-03-29 1954-06-10 Maschf Augsburg Nuernberg Ag Entnahmevorrichtung fuer Kontrollbogen aus schnellaufenden Druckmaschinen
US2785894A (en) * 1952-03-29 1957-03-19 Maschf Augsburg Nuernberg Ag Sheet delivering mechanism for printing presses
US2738973A (en) * 1953-01-27 1956-03-20 Roland Offsetmaschf Stacking device for machines working on sheets, particularly printing machines
US2836418A (en) * 1953-05-22 1958-05-27 Roland Offsetmaschf Stacking device for printing machines
GB861133A (en) * 1957-05-29 1961-02-15 William Frank Golding Improvements in or relating to sheet delivery apparatus for printing and like machines
DE2003553A1 (de) * 1970-01-27 1971-08-05 Windmoeller & Hoelscher Vorrichtung zum fortlaufenden Bilden von kantengleichen Werkstueckpaketen aus einer in Voranbewegung begriffenen Reihe von sich schuppenartig ueberdeckenden Werkstuecken,insbesondere Saecken und Beuteln
DE2301840C3 (de) * 1973-01-15 1981-03-26 MAN Roland Druckmaschinen AG, 63075 Offenbach Bogenauslegevorrichtung einer Bogendruckmaschine
DE3220813C2 (de) * 1982-06-03 1985-02-07 Bielomatik Leuze Gmbh + Co, 7442 Neuffen Vorrichtung zum Stapeln von Bogen
US4647265A (en) * 1985-07-08 1987-03-03 Tadao Uno Paper sheet manipulator

Also Published As

Publication number Publication date
JPH02182661A (ja) 1990-07-17
DE58902897D1 (de) 1993-01-14
DE3836571A1 (de) 1990-05-03
CA1325023C (en) 1993-12-07
EP0370206A1 (de) 1990-05-30
US5005822A (en) 1991-04-09
CN1019905C (zh) 1993-02-17
JPH0633123B2 (ja) 1994-05-02
DE3836571C2 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1991-01-03
CN1042128A (zh) 1990-05-16

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