EP3402678A2 - Déverrouillage de l'accouplement d'une roue dentée double - Google Patents

Déverrouillage de l'accouplement d'une roue dentée double

Info

Publication number
EP3402678A2
EP3402678A2 EP17702301.7A EP17702301A EP3402678A2 EP 3402678 A2 EP3402678 A2 EP 3402678A2 EP 17702301 A EP17702301 A EP 17702301A EP 3402678 A2 EP3402678 A2 EP 3402678A2
Authority
EP
European Patent Office
Prior art keywords
cylinder
annular
ring
gear
clamping
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.)
Granted
Application number
EP17702301.7A
Other languages
German (de)
English (en)
Other versions
EP3402678B1 (fr
Inventor
Reinhold Achenbach
Harald Bayer
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.)
Manroland Sheetfed GmbH
Original Assignee
Manroland Sheetfed GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Manroland Sheetfed GmbH filed Critical Manroland Sheetfed GmbH
Publication of EP3402678A2 publication Critical patent/EP3402678A2/fr
Application granted granted Critical
Publication of EP3402678B1 publication Critical patent/EP3402678B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • B41F13/008—Mechanical features of drives, e.g. gears, clutches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
    • B41P2213/00—Arrangements for actuating or driving printing presses; Auxiliary devices or processes
    • B41P2213/10—Constitutive elements of driving devices
    • B41P2213/25—Couplings; Clutches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
    • B41P2213/00—Arrangements for actuating or driving printing presses; Auxiliary devices or processes
    • B41P2213/10—Constitutive elements of driving devices
    • B41P2213/25—Couplings; Clutches
    • B41P2213/254—Devices allowing two gears to engage with each other

Definitions

  • the invention relates to a device for releasing a force-locking connection according to the preamble of patent claim 1.
  • a so-called sheet turning device is arranged in the transport path of the printed sheets to accomplish the sheet turning. Normally, the sheet is transported with its leading edge through the entire machine, in which case only the top of the sheet is printed. If the sheet is to be printed from both sides, the sheet turning device is switched between two printing units, as a result of which there is the trailing edge of the sheet to the leading edge.
  • the relative position of the adjacent printing units is to change so that at this point instead of the leading edge of the sheet now the trailing edge can be passed.
  • the clamping devices may include a clamping ring and are stretched and unlocked via curves or spring sets.
  • a device of this type describes the DE-PS 35 34 488.
  • the clamping force is applied by a spring, which is to cancel the clamping of a pneumatic piston or Bellows can be charged.
  • the clamping is done by means of one-armed cranked levers, which are connected via bolts with the clamps for clamping the gear ring.
  • the one-armed, cranked levers are mounted on ball elements and generate at the point of articulation of the bolt in their Movement an axial displacement with respect to the clamping claws.
  • a clamping force is applied to the clamping claws with the pivotal movement of the lever.
  • the pivotal movement of the lever is generated by a guide body in which engage the ends of the lever.
  • the guide body sits on a rod centric to the main gear.
  • the rod is axially slidably connected to the drive pin of the gear and is loaded by a compression spring to the outside.
  • the outer end of the guide rod around.
  • the power transmission is very complicated
  • DE 41 41 817 A1 discloses a device for unlocking a double-wheel clutch in a sheet-fed rotary printing machine which is explained in more detail in the context of the exemplary embodiment.
  • the unlocking mechanism is mounted without contact outside and without contact with the double gear.
  • the arrangement is complicated and requires a variety of mechanical auxiliary elements for safe execution of the clamping and exemption of the double fur gear when adjusting a perfecting press.
  • From DE 10 2005 041 696 A1 a coupling device for effecting a temporary decoupling of the sections of a gear train of a printing press is known.
  • the coupling device for carrying out a change of the phase position of the respective gear sections to each other nenden setting process should be characterized by a robust construction and a reliable high torque transfer.
  • the coupling device is coaxially provided with a first and second spur gear.
  • a clamping device serves to generate one of the frictional transmission of a torque between the first and the second spur gear.
  • a chamber device is used for applying a clamping force bringing the clamping device in a release state.
  • a clamping plate is arranged, which is resiliently biased in a basic position and generates the necessary clamping force for the clutch engagement.
  • a first and a second spur gear are clamped by a clamping device for the frictional transmission of torque.
  • a force is applied by a pressure medium via a chamber device, wherein the chamber device is formed by a first ring element and a second, with respect to the first ring element axially displaceable ring element:
  • the first ring element has for this purpose a release-contact portion, which is employed to transfer the to the movement of the clamping device in a release state against a resiliently supported component.
  • the second ring element has a support abutment portion which is seated in the release state on a coupled with the first spur support shoulder.
  • the device aligns itself on the gear and has no contact with the double gear during normal operation.
  • the unlocking mechanism consists of a rectangular in cross-section and formed by two concentric rings circular Hubkanal in which a lifting ring is displaced by means of a fluidically generated drive energy against the rings of the Hubkanals. During the displacement, the rings are supported on elements of the double gear so that the clamping of the gear ring is canceled.
  • the described variants use hydraulic or pneumatic energy.
  • the force applied to unlock the clamping of the gear ring on the main gear is diverted within the double gear and thereby a rigid axial bearing of the printing cylinder can act supported. This also results in no shifts z. B. could lead to a rotational displacement of the drive in a helical gearing.
  • the unlocking system is not in the normal machine operation with the double gear in touch. At the double gear itself no additional elements are required, so that the mass of the double gear is not increased. The double gear itself is so completely maintenance-free and the clutch to cancel the clamping of the double gear is to be maintained without changes to this or built and removed.
  • the second spur gear is clamped by loaded by spring tension tie rods on the first spur gear.
  • the device is arranged symmetrically to the axis of the double gear and has for releasing at least one annular fluid-operated lifting arrangement. This is coupled to the machine frame and at least partially displaceable in the direction of an axis of the double gear.
  • the lifting arrangement connects in the release position a part of the double gear to the machine frame.
  • the cylinder pin is received in a cylinder bearing, in which an axial bearing arranged separately from a radial bearing is provided.
  • An annular fluid operated lift assembly is disposed directly adjacent and concentric with the axial support on the machine frame of the sheet-fed rotary printing machine.
  • a pressure element of the lifting arrangement is assigned to a respective pressure element transmitting the spring force to a respective tie rod.
  • the annular lifting arrangement is formed from a ring cylinder and an annular piston arranged in this ring opening.
  • the ring cylinder is arranged coaxially with the axis of the double gear and directly adjacent to an outer circumference of a guide ring of the axial bearing of the cylinder bearing on the machine frame.
  • the annular piston is arranged to be movable parallel to the axis in the direction of and to the machine frame to the double gear.
  • annular piston is formed as insertable into a front side of the machine frame facing away open piston chamber insert with sealing inserts on the inner and the outer edge.
  • the annular piston is assigned a holding device arranged inside the piston chamber and not influencing the annular piston in its lifting movement, but retaining its circumferential position relative to the annular cylinder.
  • the ring cylinder is arranged fixedly connected to the machine frame.
  • a support ring is provided in mechanical connection with the annular cylinder and the directly adjacent region of the double gear as Kraftleitelement.
  • the support ring is preferably coupled with the ring cylinder and engages behind a further arranged on the double gear retaining ring.
  • each tie rod is assigned a respective pressure piece at a head end, which is opposite to a clamping screw at the other end of the tie rod.
  • the pressure piece is used to apply force to a respectively associated with the tie rod spring assembly.
  • the thrust pieces of all tie rods are arranged so that they touch the ring piston in its stroke position.
  • a spring plate between a clamping ring and a cylinder-fixed element of the double gear is arranged. The spring plate dissolves the clamping ring when canceling the clamping of the clamping ring against a cylinder-fixed part of the double gear and is designed as an annular spring element.
  • the annular lifting element is formed from a plurality of lifting cylinders and in each case one lifting piston arranged in these.
  • the lifting cylinders are arranged concentrically with respect to the cylindrical pin annular.
  • FIG. 1 is a partial view of a sheet-fed rotary printing press
  • FIG. 2 shows a partial section of a device according to the prior art
  • FIG. 3 shows the device according to the invention
  • Figure 4 is another view of this device.
  • Figure 5 shows a variant of this device
  • Figure 6 / 6A a further developed variant of this device.
  • FIG. 1 schematically shows a detail of a sheet-fed rotary printing machine.
  • Two printing units 1A and 1B are supported by printing cylinders 2, 3 and Transport drums 4, 5 connected together.
  • the drive of the printing units is carried out by gears which are coaxial with the printing cylinders 2, 3 and sheet transport drums 4, 5 are arranged.
  • the sheet transport drum 5 is designed as a so-called turning drum. For the turning operation, the relative position of the two printing units 1 A, 1 B to each other in the circumferential direction to the extent of the length of the sheets to be printed to change so that the end of the sheet can be transferred instead of the beginning of the sheet.
  • the double gear 6 consists of a main gear 8 and a gear ring 9.
  • the main gear 8 is connected to a cylinder pin 10.
  • a clamping connection via a clamping ring 1 1 is produced.
  • clamping elements 12 under the force of spring assemblies 13 from. If the spring assemblies 13 are unloaded from the outside, they clamp the clamping element 12 against the clamping ring 1 1 and connect the ring gear 9 frictionally connected to the main gear 8.
  • the drive torque is transmitted from a gear 14 via the ring gear 9 to the main gear 8 and passed there on in the gear train downstream drive elements.
  • the double-wheel clutch 7 which consists of an inner ring 15 and an outer ring 16.
  • the rings 15, 16 form a hydraulic or pneumatic system with a pressure chamber 28 which is sealed with seals 25 and to which a fluid is supplied through a pressure medium connection 27.
  • the unlocking system is loaded by springs 18 engaging in the ring 15 engaging retaining pin 17 axially displaceable against a fixed support 20 as a rest position.
  • the outer ring 16 abuts with a stop surface 21 under load of compression springs 19 on the inner ring 15.
  • the outer end face 22 of the inner ring 15 and a bent annular face 23 of the outer ring 16 are used as effective surfaces of the system.
  • an unlocking element 24 which is connected to the gear ring 9.
  • the dual-wheel clutch 7 is positioned on the carrier 20, which is rigidly connected to a part of the machine frame 26.
  • the release system In the unlocked state, the release system is free from fixed supports to small spring forces. Upon further supply of pressure medium, the clamping of the gear parts is canceled, without axial forces in the main gear 8 and its storage would be introduced.
  • the main gear 8 can be rotated relative to the gear ring 9, while the gear ring 9 and coupled to him gear parts are held.
  • the inventive device on a double gear 6 is formed as shown in FIG.
  • the impression cylinder 2 is received with its cylindrical pin 10 via a radial bearing 32 guided in a bearing sleeve 33 and via a thrust bearing 34 guided in the machine side wall 26 on a guide ring 35.
  • the guide ring 35 of the thrust bearing 34 is in this case attached from the outside to the machine side wall 26 and defines the entire bearing unit of the cylinder pin 10 immovably in this position.
  • a gear main body 39 is fixed by means of a mounting plate 36.
  • a first spur gear 8 is mounted rotationally.
  • a second spur gear 9 is placed on the gear main body 39 as a gear ring.
  • a clamping ring 37 is arranged on the side facing away from the machine side wall 26 side.
  • the clamping ring 37 is pressed by a tie rod 29 or more distributed over the circumference of the double gear 6 tie rods 29 against the first spur gear 8.
  • each of the tie rods 29 passes through the first spur gear 8, the gear main body 39 and the clamping ring 37 and is supported, each with its own head-mounted pressure piece 31 against a respective spring assembly 13 (such as disc springs).
  • Each of the spring assemblies 13 is received in corresponding devices on the first spur gear 8.
  • Each tie rod 29 is further supported against the force of the spring pact 13 by a clamping nut 30, which is supported on the clamping ring 39, adjustable.
  • annular spring plate 38 is arranged, which is shaped plate-shaped in the manner of a washer and is therefore biased during clamping between the clamping ring 37 and the gear main body 39. Therefore, the spring plate 38 when reducing or canceling the bias of the tie rods 29, the clamping ring 37 lift by a bulge of the gear ring of the second spur gear 9, so that it is movable relative to the first spur gear 8.
  • This device consists of an annular cylinder (ring cylinder 40) which is arranged coaxially with the cylinder pin 10 in the immediate vicinity of the thrust bearing 34 on the machine side wall 26.
  • ring cylinder 40 In the ring cylinder 40 is a Ring piston 41 under fluid supply or removal axially parallel to the cylinder pin 10 arranged displaceably.
  • the annular piston 41 With fluid supply to the annular cylinder 40, the annular piston 41 is moved parallel to the axis of the cylinder pin 10 away from the machine side wall 26 and displaced against the plungers 31 of the tie rods 29. With appropriate pressure build-up, the annular piston 41 then presses together the spring assemblies 13 via the pressure pieces 31, so that the preload load that has been applied to the clamping ring 37 via the clamping nuts 30 is reduced or eliminated. Thereby, and by the return action of the spring plate 38, the second annular spur gear 9 is free and can be adjusted relative to the first spur gear 8.
  • a ring cylinder 40 with a suitably large diameter and a correspondingly large-sized annular piston 41 are also required here.
  • a corresponding Dar position of the annular cylinder 40 in association with the cylinder pin 10 and its axial bearing 34 (dash-dot-line) is shown in Figure 4, wherein the annular piston 41 is shown hatched for better visibility.
  • an arrangement of smaller lifting cylinders 42 which is evenly distributed around the cylinder pin 10, can be provided with a respective lifting piston 43, as shown in FIG.
  • each of these lifting cylinders 42 with their reciprocating piston 43 is such that they are each a respective tie rod 29 and its pressure piece 31 are positioned opposite to the machine side wall 26.
  • a device for exact positioning of the double gear 6 must be provided in its rotational position.
  • a precisely aligned action of each of the reciprocating piston 43 to the respective associated tie rod 29 and its respective pressure piece 31 is required.
  • FIG. 6 shows a structurally simple embodiment of the device according to FIG. 3 in connection with a particularly preferred bearing arrangement with separate axial and radial guidance for the pressure cylinder 2 which can be driven by means of the double gear 6, in which the unlocking device 7 directly engages an axial bearing 34 on the cylindrical journal 10 assigned.
  • the cylindrical pin 10 is received in the machine side wall 26 via the radial bearing 32 guided in the bearing sleeve 33 and the axial bearing 34 guided on the guide ring 35, whereby the guide ring 35 secures the axial bearing 34 on the outside of the machine side wall 26 and the cylinder pin 10 in this position in the axial direction fixed immovably.
  • a gear base body 39 is fixed with a mounting plate 36.
  • gear main body 39 On gear main body 39, a first spur gear 8 is mounted rotationally. Parallel and coaxial with the first spur gear 8, the second spur gear 9 is mounted as a gear ring on the gear main body 39.
  • the annular spur gear 9 is fixed to the first spur gear 8 by a clamping ring 37 is disposed on the gear base body 39 on the side facing away from the machine side wall 26, which is distributed by tie rods 29 on the circumference of the double gear 6 against the first spur gear 8 pressed.
  • Each tie rod 29 passes through the first spur gear 8, the gear main body 39 and the clamping ring 37 and is supported with a stepped head 29A in each one of the support load distributing pressure piece 31 against a spring assembly 13, which is received in the first spur gear 8.
  • Each tie rod 29 is biased on the head 29A opposite side of a clamping nut 30, which is supported on the clamping ring 39, adjustable against the force of the spring assembly 13 to the clamping ring 39 with the annular spur gear 9 and the annular spur gear 9 with the fixed To connect spur 8 frictionally.
  • an annular spring plate 38 is arranged according to Figure 3 between the clamping ring 37 and the gear main body 39.
  • annular cylinder (ring cylinder 40) is arranged coaxially with the cylinder pin 10 in direct proximity to the thrust bearing 34 on the machine side wall 26.
  • the ring cylinder 40 is fixedly connected to the machine side wall 26 and encloses the guide ring 35 of the thrust bearing 34 in the radial direction without spacing.
  • annular piston 41 is arranged under fluid supply or - removal axially parallel to the cylinder pin 10 displaced. With fluid supply to the annular cylinder 40, the annular piston 41 is moved parallel to the axis 44 of the cylinder journal 10 away from the machine side wall 26 and displaced against the pressure pieces 31 of the tie rod 29.
  • a support of the introduction of force on the double gear 6 can be provided.
  • a support ring 45 is attached to the ring cylinder 40, which preferably engages behind the ring cylinder 40 at its base and is bent on the side of the ring piston 41.
  • the support ring 45 protrudes into a recess on the spur gear 8, which is covered by a retaining ring 46.
  • the second annular spur gear 9 is released with high positional accuracy in its clamping position and can then adjusted in its recording on the gear base 39 and relative to the first spur gear 8 with equally high accuracy become.
  • annular cylinder 40 is fixedly connected to the frame side wall 26. In contrast to the prior art, this prevents unintentional contact between the double gearwheel 6 and the unlocking mechanism during running operation of the machine. Furthermore, a safe and well-supported force is given by the integrative proximity between the thrust bearing 34 of the cylinder bearing and the ring cylinder 40 of the unlocking mechanism.
  • annular piston 41 is an insert element with an overlapping edge as a stop and a sealing system 41 A in the axial direction to the cylinder pin 10 in an annular piston chamber 40A within the annular cylinder 40 inserted inserted. This ensures a very simple operation and easy maintenance of the machine.
  • the annular piston 41 can be loaded at the abovementioned overlapping edge with a few return springs 46 in the direction of the machine frame 26, so that it safely returns to the basic position in the ring cylinder 40 when pressure is released.
  • FIG 6A the basic position of the annular piston 41 is shown with minimum distance to the pressure piece 31 on the tie rod 29 under load by the return springs 46.
  • the return springs 46 may be arranged in any free access position to the annular piston 41 and must be secured to the machine frame 26 connected.
  • the annular piston 41 can be guided to secure against unintentional displacement in the circumferential direction with a loosely engaging in a recess 41 C in the piston head locking pin 41 B (see Figure 6A).
  • the annular piston 41 is not hindered by the securing pin 41 B with respect to the function to be performed for unlocking in the form of a lifting movement.
  • rotational movements on the double gearwheel 6, which are to be carried out for adjusting the sheet-fed rotary printing press to the perfecting and backward printing mode movement of the annular piston 41 relative to the ring cylinder 40 in the circumferential direction of the double gearwheel 6 is prevented by the securing pin 41B. This can not be done unintentionally rotation of the double gear 6 during the function change.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rotary Presses (AREA)
  • Gear Transmission (AREA)
  • Supply, Installation And Extraction Of Printed Sheets Or Plates (AREA)

Abstract

L'invention vise à simplifier un dispositif pour libérer le blocage d'une roue dentée double dans une presse rotative à feuilles pour l'impression en blanc ou l'impression recto-verso. A cet effet, un piston annulaire (41) est disposé dans un cylindre annulaire (40) coaxialement par rapport à un logement axial (33) sur l'axe de cylindre (10) d'un cylindre de groupe d'impression de la presse rotative à feuilles.
EP17702301.7A 2016-01-14 2017-01-14 Déverrouillage de l'accouplement d'une roue dentée double Active EP3402678B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102016100532 2016-01-14
DE102017100661.3A DE102017100661A1 (de) 2016-01-14 2017-01-13 Entriegelung einer Koppelung eines Doppelzahnrades
PCT/EP2017/050737 WO2017121889A2 (fr) 2016-01-14 2017-01-14 Déverrouillage de l'accouplement d'une roue dentée double

Publications (2)

Publication Number Publication Date
EP3402678A2 true EP3402678A2 (fr) 2018-11-21
EP3402678B1 EP3402678B1 (fr) 2019-10-30

Family

ID=59256348

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17702301.7A Active EP3402678B1 (fr) 2016-01-14 2017-01-14 Déverrouillage de l'accouplement d'une roue dentée double

Country Status (4)

Country Link
EP (1) EP3402678B1 (fr)
CN (1) CN108472945A (fr)
DE (1) DE102017100661A1 (fr)
WO (1) WO2017121889A2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020234004A1 (fr) * 2019-05-23 2020-11-26 Bobst Bielefeld Gmbh Arbre de serrage, unité de cylindre d'impression et procédé d'actionnement d'un arbre de serrage

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5871163A (ja) * 1981-10-24 1983-04-27 Komori Printing Mach Co Ltd 反転機構付枚葉輪転印刷機の位相調整装置
DE3534488A1 (de) 1985-09-27 1987-04-16 Koenig & Bauer Ag Kupplung in einer bogenrotationsdruckmaschine
DE3611324A1 (de) 1986-04-04 1987-10-08 Heidelberger Druckmasch Ag Vorrichtung zur verstellung der relativen drehlage zwischen einem zahnrad und einem mit diesem gleichachsig gelagerten zahnkranz
JPS63173644A (ja) * 1987-01-13 1988-07-18 Sumitomo Heavy Ind Ltd 片面・両面刷兼用枚葉印刷機の反転胴の位相切換装置
DE4141817C2 (de) 1991-12-18 1993-10-07 Roland Man Druckmasch Einrichtung zur Getriebezugtrennung
DE19718140C1 (de) 1997-04-30 1998-10-01 Roland Man Druckmasch Vorrichtung zum lösbaren Verbinden eines Zahnradringes mit dem Hauptzahnrad
US7484610B2 (en) * 2004-03-10 2009-02-03 Heidelberger Druckmaschinen Apparatus for the actuation of clamping elements that can be controlled remotely
DE102005039918A1 (de) 2005-08-24 2007-03-08 Man Roland Druckmaschinen Ag Kupplungseinrichtung zur Bewerkstelligung einer zeitweisen Entkoppelung der Abschnitte eines Getriebezugs einer Druckmaschine
DE102005041696A1 (de) 2005-09-02 2007-03-15 Man Roland Druckmaschinen Ag Kupplungseinrichtung zur Bewerkstelligung einer zeitweisen Entkoppelung der Abschnitte eines Getriebezugs einer Druckmaschine
DE102005045098B4 (de) 2005-09-21 2008-02-28 Pierburg Gmbh Kühlvorrichtung für eine Verbrennungskraftmaschine

Also Published As

Publication number Publication date
DE102017100661A1 (de) 2017-07-20
CN108472945A (zh) 2018-08-31
EP3402678B1 (fr) 2019-10-30
WO2017121889A2 (fr) 2017-07-20
WO2017121889A3 (fr) 2017-09-08

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