EP0346619B1 - Verstellvorrichtung der relativen Drehlage zwischen Zahnrad und gleichachsig gelagertem Zahnkranz in einer Bogenrotationsmaschine - Google Patents

Verstellvorrichtung der relativen Drehlage zwischen Zahnrad und gleichachsig gelagertem Zahnkranz in einer Bogenrotationsmaschine Download PDF

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Publication number
EP0346619B1
EP0346619B1 EP89108714A EP89108714A EP0346619B1 EP 0346619 B1 EP0346619 B1 EP 0346619B1 EP 89108714 A EP89108714 A EP 89108714A EP 89108714 A EP89108714 A EP 89108714A EP 0346619 B1 EP0346619 B1 EP 0346619B1
Authority
EP
European Patent Office
Prior art keywords
gearwheel
friction
clamping
segments
friction discs
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
EP89108714A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0346619A2 (de
EP0346619A3 (en
Inventor
Willi Becker
Hans-Peter Hiltwein
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
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Filing date
Publication date
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6356410&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0346619(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 EP0346619A2 publication Critical patent/EP0346619A2/de
Publication of EP0346619A3 publication Critical patent/EP0346619A3/de
Application granted granted Critical
Publication of EP0346619B1 publication Critical patent/EP0346619B1/de
Anticipated expiration legal-status Critical
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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
    • B41F13/0008—Driving devices
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/1987—Rotary bodies
    • Y10T74/19893—Sectional
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/1987—Rotary bodies
    • Y10T74/19893—Sectional
    • Y10T74/19912—Differential disks

Definitions

  • the invention relates to a device for the frictional coupling of a fixed gear and, in contrast, in the rotational position adjustable gear on a cylinder of a turning device in a sheet-fed rotary printing press with features according to the preamble of claim 1.
  • the invention also relates to the formation of an electrical fuse of such a device to avoid the Commissioning of a machine that is not ready for operation.
  • a device for the frictional coupling of the fixed gear and an adjusting gear for adjusting the rotational position of both gears is known from DE-OS 36 11 325.
  • a clamping disk with its edge acts as an abutment for pressure levers distributed over the circumference, which at one end press the adjusting gear against an annular shoulder recess in the fixed gear, and whose other inward ends are loaded with the spring force of a centrally arranged tensioning element, wherein the abutment is moved far outwards to achieve an optimal leverage so that the greatest possible torque can be absorbed by the frictional coupling caused by the friction of the contacting surfaces of the two gear wheels. Large torques require very high clamping forces.
  • the adjusting member can be adjusted by means of a thread in a way which has a first section in which the spring force acting on the pressure levers increases from a low to a value required to maintain the relative rotational position in the known arrangement , and comprises a second section in which the spring force required to maintain the relative rotational position is maintained, so that the rotary printing press can only be put into operation if there is a sufficiently tight coupling between the fixed gear and the adjusting gear.
  • the supply circuit of the drive device is first interrupted and only then is the coupling forces reduced.
  • a comparable coupling is known from JP-A-58-78763, in which the adjusting gear for coupling is also pressed into an annular shoulder recess of the fixed gear.
  • four clamping segments are distributed around the circumference, each of which is tightened by a draw bolt with a thread, and a gear is provided for rotating the nut thread for these draw bolts, which consists of two coaxially arranged worms and four worm wheels, with their teeth in pairs of engage on opposite sides in the toothing of the two screws. Both screws can be rotated by a common crank via a bevel gear.
  • the worm gear requires several crank revolutions, including for the actuation of the phase adjustment of the adjusting gear compared to the fixed gear. A electrical protection of the coupling in the operating position is not provided.
  • the object of the invention is to provide a device that can be electrically secured in the operating position with the features mentioned at the outset in such a way that higher torques can be transmitted at lower clamping forces than previously in an inexpensive construction, and this is preferably made possible with only one clamping screw.
  • An essential feature of this training is the increase in the frictional force by increasing the number of effective friction surfaces. This is preferably achieved by friction elements from mutually and lamellar interlocking friction disks on the fixed gear and on the adjusting gear according to claim 2, whereby the overall friction force is considerably increased. Assuming a constant coefficient of friction, the clamping force for the frictional coupling of the fixed gear and the adjusting gear can be reduced. Conversely, this design enables a substantial increase in the torque that can be transmitted by the clutch, while the clamping force remains the same, which results in considerable advantages with regard to safe operating conditions, especially in the case of high-speed printing presses.
  • the clamping device can be made from a single, centrally arranged clamping element, in particular from a threaded bolt with an external screw head, exist, the thread of which can be screwed into a nut thread, which is located centrally in the axis of the cylinder of the turning device.
  • This one clamping screw creates advantageous conditions for the arrangement of electrical means for securing the effective coupling of the gear wheels.
  • these electrical means are designed with the features according to the characterizing part of claim 12.
  • the training features according to claim 14 are provided so that the greatest possible angle of rotation of the threaded screw, in particular a rotation angle of almost 180 degrees, is achieved for releasing the force-locking coupling of the two gear wheels.
  • Both exemplary embodiments show the arrangement of the fixed gear 1 at one end of the shaft 2 of a cylinder of the turning device of a sheet-fed rotary printing press, which is not shown in the drawing for the sake of a better overview, for the optional face printing or perfecting.
  • the fixed gear is screwed coaxially to the shaft 2 by screws 3 with the end face of the shaft 2.
  • a pin extension 4 is formed by an angular recess in the sectional view, on which the ring-shaped adjusting gear 5, which can be coupled by clamping to the fixed gear 1, is arranged so as to be adjustable in the angle of rotation.
  • This frictional coupling of the adjusting gear 5 with the fixed gear 1 is carried out by a clamping plate 6, which forms the clamping body, and by a clamping screw 7, which passes through a central bore of the clamping plate 6, is supported with the screw head 8 against the clamping plate 6 and with its bolt thread can be screwed into a nut thread in a bore in shaft 2.
  • a clamping plate 6 which forms the clamping body, and by a clamping screw 7, which passes through a central bore of the clamping plate 6, is supported with the screw head 8 against the clamping plate 6 and with its bolt thread can be screwed into a nut thread in a bore in shaft 2.
  • Is on the inside of the clamping plate 6 an integrally formed pressure ring 9 is formed, by which the adjusting gear 5 is pressed against the fixed gear 1 when the clamping screw 7 is tightened, so that both gears are frictionally connected to one another by frictional forces.
  • the front contact surfaces of both gears are effective.
  • additional friction elements are provided and connected alternately to one of the two gears, these friction elements interlocking in the manner of a multi-plate clutch and in the overlap area by the clamping plate 6 via the pressure ring 9, which is supported against an external friction element, also be firmly pressed together.
  • the exemplary embodiments show friction elements made of friction disks 10 and 11, which are fastened either to the fixed gear 1 or to the adjusting gear 5 by means of screws 12 and 13 and mesh with one another in the manner of lamellas, so that an overlap area is created behind the pressure ring 9.
  • FIG. 1 shows two friction disks 10, which are fastened by means of screws 12 to the end face of the pin extension 4, and a further friction disk 11, which is fastened by means of screws 13 to the side face of the adjusting gear 5.
  • the height differences caused by the material thicknesses in the axial direction of the shaft 2 are compensated for by washers, intermediate rings 14 or other elements.
  • the inner edge of the friction plate 11 engages like a lamella between the outer edges of the friction plates 10, so that three additional annular friction surfaces are thereby formed, by means of which the transferable friction forces can be increased.
  • a further increase in the friction surfaces can be achieved, for example, by a packet-like arrangement of the friction disks, such as that shown in FIG Figure 2 is shown.
  • an elastically deformable design is provided in the direction of the axis of the shaft 2, which provides as little resistance as possible to the clamping forces exerted by the pressure ring 9.
  • This can be achieved by an elastically deformable material and, if necessary, supported by the fact that the friction disks in the overlap region and possibly also have radial incisions or cutouts through which tongues are formed, which can be deformed more easily in the axial direction of the shaft 2, as can be done can be seen, for example, from the illustration in FIG.
  • At least the friction disks fastened to the adjusting gear 5 or to the fixed gear 1 are of split design, so that separately mountable segments are created.
  • the friction disks 11 fastened to the adjusting gear wheel 5 are advantageously composed of segments which are pushed from the outside between the friction disks 10 after they have already been firmly mounted.
  • a non-positive connection can also be provided.
  • the assembly and disassembly of the friction disks can be facilitated by assembling the friction disks and intermediate rings into packages by means of intermediate layers, e.g. are glued together so that only a part is to be assembled, either in the form of a ring or as a ring segment, as explained above.
  • the means for electrically securing the effective coupling between the fixed gear 1 and the adjusting gear 5 consist of a switching ring 15 which is arranged on the clamping screw 7 in a rotationally fixed manner and of switching plates 16 which are guided on the clamping plate 6 in a radially movable manner and which the switching ring 15 releases when the clamping between the fixed gear is released 1 and the adjusting gear 5 moves radially and thereby acts with an arc-shaped contact surface 17 on an electrical switch 18 which is arranged in the supply circuit of the machine.
  • the circuit board 16 is composed of four quarter-circle segments, two of which are diametrically opposite to the axis of the clamping screw 7 and interact in pairs, so that they move in the same direction either together outwards or together inwards to the center of the clamping screw 7. These elements of the electrical protection are shown in the drawing in FIGS. 4 and 5, but the clamping screw 7 is covered by the screw head 8.
  • Each segment of the switching plate 16 has a cam 19 on the inner ring surface, which cooperates with a complementarily shaped curve 20 on the switching ring 15.
  • the cams and curves of the one pair of segments of the circuit board 16 are to the cams and curves of the other pair of segments of the circuit board 16 both axially offset and radially offset by 90 degrees to each other.
  • the segments of the circuit board 16 are guided by screws 22 which pass through radially directed slots in the segments of the circuit board.
  • the segmentation of the circuit board 16 and the paired interaction of the segments is achieved constructively in that the cams 19a of one pair of segments are formed on the front of the segments and the cams 19b of the other pair on the back of the segments of the circuit board, as is apparent from the Representation in Figures 4, 4a, 5 and 5a results.
  • a clamping screw rotation of more than 90 degrees is thereby achieved by opening the switch 18 in the drive circuit of the machine.
  • the opening movement is limited by a stop pin 23 connected to the switching ring 15, which interacts with stops 24 on screws for guiding and holding the one pair of segments and limits the opening angle of the clamping screw 7 from one stop position to the other stop position to approximately 160 degrees.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)
  • Rotary Presses (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
EP89108714A 1988-06-13 1989-05-16 Verstellvorrichtung der relativen Drehlage zwischen Zahnrad und gleichachsig gelagertem Zahnkranz in einer Bogenrotationsmaschine Expired - Lifetime EP0346619B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3820026A DE3820026A1 (de) 1988-06-13 1988-06-13 Vorrichtung zur kraftschluessigen kupplung eines festzahnrades und eines verstellzahnrades an einem zylinder einer wendeeinrichtung in einer bogenrotationsdruckmaschine und elektrische absicherung einer solchen vorrichtung
DE3820026 1988-06-13

Publications (3)

Publication Number Publication Date
EP0346619A2 EP0346619A2 (de) 1989-12-20
EP0346619A3 EP0346619A3 (en) 1990-05-30
EP0346619B1 true EP0346619B1 (de) 1992-11-04

Family

ID=6356410

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89108714A Expired - Lifetime EP0346619B1 (de) 1988-06-13 1989-05-16 Verstellvorrichtung der relativen Drehlage zwischen Zahnrad und gleichachsig gelagertem Zahnkranz in einer Bogenrotationsmaschine

Country Status (6)

Country Link
US (1) US5048362A (en(2012))
EP (1) EP0346619B1 (en(2012))
JP (1) JPH0230534A (en(2012))
CN (1) CN1011768B (en(2012))
AU (1) AU3628389A (en(2012))
DE (2) DE3820026A1 (en(2012))

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4101823C2 (de) * 1990-01-31 1997-12-04 Kba Planeta Ag Antriebsraederzug
DE4110035C2 (de) * 1991-03-27 1995-04-13 Roland Man Druckmasch Vorrichtung zum Verstellen von Elementen in Falzwerkzylindern von Rotationsdruckmaschinen
DE4131273C1 (en(2012)) * 1991-09-20 1992-12-10 Heidelberger Druckmaschinen Ag, 6900 Heidelberg, De
DE4141818C2 (de) * 1991-12-18 1995-05-04 Roland Man Druckmasch Vorrichtungen zum Klemmen und Spannen
JP4220581B2 (ja) * 1995-11-15 2009-02-04 ハイデルベルガー ドルツクマシーネン アクチエンゲゼルシヤフト 印刷機における反転装置の二重歯車
DE29518072U1 (de) * 1995-11-15 1996-01-04 Heidelberger Druckmaschinen Ag, 69115 Heidelberg Doppelzahnrad einer Wendeeinrichtung an Druckmaschinen
JP2991138B2 (ja) * 1996-12-09 1999-12-20 日本電気株式会社 メモリｌｓｉの不良解析方法
DE19718140C1 (de) * 1997-04-30 1998-10-01 Roland Man Druckmasch Vorrichtung zum lösbaren Verbinden eines Zahnradringes mit dem Hauptzahnrad
DE10202386A1 (de) 2001-02-19 2002-08-22 Heidelberger Druckmasch Ag Lamellenkupplung
DE10113314C2 (de) * 2001-03-20 2003-10-30 Koenig & Bauer Ag Fixiereinrichtung
DE10152021C2 (de) 2001-03-20 2003-05-08 Koenig & Bauer Ag Vorrichtung zum Einstellen des Anpressdrucks einer verstellbar gelagerten Walze
WO2003049946A2 (de) 2001-12-06 2003-06-19 Koenig & Bauer Aktiengesellschaft Verfahren zum betrieb eines farbwerkes oder feuchtwerkes in einer druckmaschine
DE10261984A1 (de) * 2002-09-21 2004-04-08 Koenig & Bauer Ag Verfahren zum Einstellen des Anpressdrucks einer verstellbar gelagerten Walze
CN101737383B (zh) * 2008-11-17 2014-02-26 海德堡印刷机械股份公司 用于在轴上夹紧或松脱驱动轮的装置
CN108458010A (zh) * 2018-05-30 2018-08-28 山东理工大学 一种降噪鼓式制动器

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB817354A (en) * 1955-11-11 1959-07-29 Reyrolle A & Co Ltd Improvements relating to printing press drives
FR814318A (fr) * 1935-12-06 1937-06-21 Bosch Robert Démarreur pour moteurs à combustion interne
US2185714A (en) * 1938-06-02 1940-01-02 Borg Warner Clutch
US3331482A (en) * 1965-09-20 1967-07-18 James G Keramas Friction clutch operable on rotating shaft
GB1253525A (en) * 1968-11-28 1971-11-17 Norman Samuel Hardy Improvements in traversing means for machine tools
GB1370011A (en) * 1972-04-07 1974-10-09 Gib Precision Ltd Torque limitting devices
DD135812A1 (de) * 1978-04-19 1979-05-30 Hans Zimmermann Vorrichtung zum verstellen des antriebes an bogenrotations-druckmaschinen
DE2921032C2 (de) * 1979-05-23 1981-09-17 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Vorrichtung zum Überwachen des Schaltzustandes einer schaltbaren Kupplung
JPS5871162A (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
JPS5878763A (ja) * 1981-11-05 1983-05-12 Komori Printing Mach Co Ltd 反転機構付枚葉輪転印刷機の位相調整装置
US4554842A (en) * 1983-04-25 1985-11-26 Cincinnati Milacron Inc. Anti-backlash mechanism for machine drive
DE3534488A1 (de) * 1985-09-27 1987-04-16 Koenig & Bauer Ag Kupplung in einer bogenrotationsdruckmaschine
DE3611325A1 (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
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
DE3614734A1 (de) * 1986-04-30 1987-11-05 Heidelberger Druckmasch Ag Vorrichtung zum absichern einer rotationsdruckmaschine
US4848531A (en) * 1987-07-30 1989-07-18 Dana Corporation Electronic system for monitoring clutch brake engagement and clutch slippage
US4836112A (en) * 1988-02-19 1989-06-06 Rockwell International Corporation Hydraulic inching drive system

Also Published As

Publication number Publication date
JPH0230534A (ja) 1990-01-31
EP0346619A2 (de) 1989-12-20
DE3820026A1 (de) 1989-12-14
CN1011768B (zh) 1991-02-27
DE58902599D1 (de) 1992-12-10
CN1038791A (zh) 1990-01-17
DE3820026C2 (en(2012)) 1991-08-29
EP0346619A3 (en) 1990-05-30
AU3628389A (en) 1989-12-14
US5048362A (en) 1991-09-17

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