EP0346619A2 - Device for fixing the relative position between a toothed gear and a coaxially toothed ring in a rotary sheet printing machine - Google Patents

Device for fixing the relative position between a toothed gear and a coaxially toothed ring in a rotary sheet printing machine Download PDF

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Publication number
EP0346619A2
EP0346619A2 EP89108714A EP89108714A EP0346619A2 EP 0346619 A2 EP0346619 A2 EP 0346619A2 EP 89108714 A EP89108714 A EP 89108714A EP 89108714 A EP89108714 A EP 89108714A EP 0346619 A2 EP0346619 A2 EP 0346619A2
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EP
European Patent Office
Prior art keywords
friction
gear
segments
clamping
friction disks
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
EP89108714A
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German (de)
French (fr)
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EP0346619A3 (en
EP0346619B1 (en
Inventor
Willi Becker
Hans-Peter Hiltwein
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Heidelberger Druckmaschinen AG
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Heidelberger Druckmaschinen AG
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Application filed by Heidelberger Druckmaschinen AG filed Critical Heidelberger Druckmaschinen AG
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Publication of EP0346619A3 publication Critical patent/EP0346619A3/en
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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, which 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 in relation 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.
  • the invention solves this problem by the training features according to the characterizing part of patent claim 1.
  • 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 gears.
  • these electrical means are designed with the features according to the characterizing part of claim 12.
  • the training features are provided according to claim 14.
  • Embodiments of the invention are partly shown schematically in the drawing.
  • 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 gear wheels 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.
  • 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.
  • REFERENCE SIGN LIST 1 Fixed gear 14 Intermediate ring 2nd wave 15 Switching ring 3rd screw 16 Circuit board 4th Pin approach 17th Contact area 5 Adjusting gear 18th counter 6 Clamping plate 19) 7 Clamping screw 19a) cam 8th Screw head 19b) 9 pressure ring 9 Pressure ring 20th Curve 10th Friction disc 21st feather 11 Friction disc 22 screw 12 screw 23 Stop pin 13 screw 24th attack 25th arrow

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Gears, Cams (AREA)
  • Rotary Presses (AREA)

Abstract

In the device for the non-positive coupling of the turning apparatus in a rotary sheet printing machine, a fixed toothed gear (1) and an adjustable toothed gear (5), which can be adjusted in the rotational position relative to the fixed toothed gear, can be braced together by means of an actuatable tensioning element (7) and a clamping plate (6) which is supported against the one toothed gear (5) and is held by the tensioning element (7) on the other toothed gear (1). Both toothed gears (1, 5) have additional friction elements (10, 11) which engage in one another in an overlapping fashion in the manner of a multiple disc clutch, the clamping plate (6) being supported by a pressure ring (9) in the overlapping region against an outlying friction element. The friction elements consist advantageously of friction discs (10, 11). …<IMAGE>…

Description

Die Erfindung betrifft eine Vorrichtung zur kraftschlüssigen Kupplung eines Festzahnrades und eines demgegenüber in der Drehlage einstellbaren Verstellzahnrades an einem Zylinder einer Wendeeinrichtung in einer Bogenrotationsdruckmaschine mit Merkmalen nach dem Oberbegriff des Patentanspruches 1. Die Erfindung betrifft außerdem die Ausbildung einer elektrischen Absicherung einer solchen Vorrichtung zur Vermeidung der Inbetriebsetzung einer nicht betriebsbereiten Maschine.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.

Eine Vorrichtung zur kraftschlüssigen Kupplung des Festzahnrades und eines Verstellzahnrades zur Verstellung der Drehlage beider Zahnräder ist aus der DE-OS 36 11 325 bekannt. Bei dieser Anordnung wirkt eine Klemmscheibe mit ihrem Rand als Widerlager für auf dem Umfang verteilt angeordnete Druckhebel, die mit den einen Enden das Verstellzahnrad gegen eine Ringschulterausnehmung im Festzahnrad pressen, und deren andere nach innen gerichtete Enden mit der Federkraft eines zentral angeordneten Spannorgans belastet sind, wobei das Widerlager zur Erzielung einer optimalen Hebelwirkung weit nach außen verlegt ist, damit ein möglichst großes Drehmoment von der durch die Reibung der sich berührenden Flächen der beiden Zahnräder bewirkten kraftschlüssigen Kupplung aufgenommen werden kann. Große Drehmomente erfordern entsprechend sehr hohe Klemmkräfte.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. In this arrangement, 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.

Für die elektrische Absicherung der auf Klemmung beruhenden Kupplung ist bei der bekannten Anordnung das Verstellorgan mittels eines Gewindes auf einem Wege verstellbar, welcher einen ersten Abschnitt, in welchem die auf die Druckhebel wirkende Federkraft von einem geringen auf einen zur Beibehaltung der relativen Drehlage erforderlichen Wert ansteigt, und einen zweiten Abschnitt umfaßt, in welchem die zur Beibehaltung der relativen Drehlage erforderliche Federkraft beibehalten wird, so daß die Rotationsdruckmaschine nur dann in Betrieb genommen werden kann, wenn eine genügend feste Kupplung zwischen dem Festzahnrad und dem Verstellzahnrad besteht. Sobald das Verstellorgan zum Lösen des Verstellzahnrades aus seiner Endstellung bewegt wird, erfolgt zunächst eine Unterbrechung des Versorgungsstromkreises der Antriebseinrichtung und erst danach eine Verringerung der Kupplungskräfte.For the electrical protection of the clutch based on clamping, 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. As soon as the adjusting member is moved from its end position to release the adjusting gear, the supply circuit of the drive device is first interrupted and only then is the coupling forces reduced.

Aus der JP-A-58-78763 ist eine vergleichbare Kupplung bekannt, bei der das Verstellzahnrad zur Kupplung ebenfalls in eine Ringschulterausnehmung des Festzahnrades gepreßt wird. Dazu dienen auf dem Umfang verteilt vier Klemmsegmente, die je durch einen Zugbolzen mit einem Gewinde angezogen werden, und zur Verdrehung des Muttergewindes für diese Zugbolzen ist ein Getriebe vorgesehen, welches aus zwei koaxial angeordneten Schnecken und vier Schneckenrädern besteht, die mit ihren Verzahnungen paarweise von sich gegenüberliegenden Seiten in die Verzahnungen der beiden Schnecken eingreifen. Beide Schnecken sind über ein Kegelradgetriebe durch eine gemeinsame Kurbel verdrehbar. Eine solche Anordnung ist relativ teuer und in der Handhabung unpraktisch. Das Schneckengetriebe erfordert mehrere Kurbelumdrehungen, unter anderem auch für die Betätigung der Phasenverstellung des Verstellzahnrades gegenüber dem Festzahnrad. Eine elektrische Absicherung der Kupplung in der Betriebsstellung ist nicht vorgesehen.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. For this purpose, 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, which 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. Such an arrangement is relatively expensive and impractical to use. The worm gear requires several crank revolutions, including for the actuation of the phase adjustment of the adjusting gear in relation to the fixed gear. A electrical protection of the coupling in the operating position is not provided.

Aufgabe der Erfindung ist die Ausbildung einer in der Betriebsstellung gegebenenfalls elektrisch absicherbaren Vorrichtung mit den eingangs genannten Merkmalen in der Weise, daß in einer kostengünstigen Bauweise höhere Drehmomente bei geringeren Klemmkräften als bisher übertragen werden können, und dies vorzugsweise mit nur einer Klemmschraube ermöglicht wird.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.

Diese Aufgabe löst die Erfindung durch die Ausbildungsmerkmale nach dem Kennzeichen des Patentanspruches 1.The invention solves this problem by the training features according to the characterizing part of patent claim 1.

Wesentliches Merkmal dieser Ausbildung ist die Vergrößerung der Reibkraft durch Vermehrung der Anzahl der wirksamen Reibflächen. Dies wird vorzugsweise durch Reibelemente aus wechselseitig und lamellenartig ineinandergreifenden Reibscheiben am Festzahnrad und am Verstellzahnrad entsprechend Anspruch 2 erreicht, wodurch die Reibkraft insgesamt erheblich vergrößert wird. Unter der Voraussetzung eines gleichbleibenden Reibungsbeiwertes kann dadurch die Klemmkraft zur kraftschlüssigen Kupplung des Festzahnrades und des Verstellzahnrades reduziert werden. Umgekehrt ermöglicht diese Ausbildung bei gleichbleibender Klemmkraft eine wesentliche Vergrößerung des von der Kupplung übertragbaren Drehmoments, wodurch sich im Hinblick auf sichere Betriebszustände, vor allem bei schnellaufenden Druckmaschinen, beträchtliche Vorteile ergeben. Dadurch, daß sich der Klemmkörper im Überlappungsbereich der Reibscheiben mit einem ringförmigen Auflager gegen eine äußere Reibscheibe abstützt, kann die Spanneinrichtung aus einem einzigen, zentral angeordneten Spannorgan, insbesondere aus einem Gewindebolzen mit außenliegendem Schraubenkopf, bestehen, dessen Gewinde in ein Muttergewinde einschraubbar ist, welches sich zentral in der Achse des Zylinders der Wendeeinrichtung befindet.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. Because the clamping body is supported in the overlap area of the friction disks with an annular support against an outer friction disk, 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.

Durch diese eine Spannschraube werden vorteilhafte Voraussetzungen für die Anordnung elektrischer Mittel zur Absicherung der wirksamen Kupplung der Zahnräder geschaffen. Nach einem besonderen Erfindungsgedanken sind diese elektrischen Mittel mit den Merkmalen nach dem Kennzeichen des Anspruches 12 gestaltet.This one clamping screw creates advantageous conditions for the arrangement of electrical means for securing the effective coupling of the gears. According to a special inventive idea, these electrical means are designed with the features according to the characterizing part of claim 12.

Damit zum Lösen der kraftschlüssigen Kupplung der beiden Zahnräder ein möglichst großer Drehwinkel der Gewindeschraube, insbesondere ein Drehwinkel von nahezu 180 Grad, erreicht wird, sind die Ausbildungsmerkmale nach dem Anspruch 14 vorgesehen.In order that the greatest possible rotation angle of the threaded screw, in particular a rotation angle of almost 180 degrees, is achieved for releasing the frictional coupling of the two gear wheels, the training features are provided according to claim 14.

Weitere vorteilhafte Ausgestaltungen enthalten die Ansprüche 13 sowie 15 bis 17.Claims 13 and 15 to 17 contain further advantageous refinements.

Vorteilhafte Ausgestaltungen der Reibscheiben und ihre Anordnungen sind in den Merkmalen der Ansprüche 3 bis 11 enthalten.Advantageous configurations of the friction disks and their arrangements are contained in the features of claims 3 to 11.

Ausführungsbeispiele der Erfindung sind auf der Zeichnung teils schematisch dargestellt.Embodiments of the invention are partly shown schematically in the drawing.

Es zeigen:

  • Figur 1 einen Schnitt in einer Achsebene durch ein Ausführungsbeispiel einer Klemmkupplung an einem Zylinder einer Wendeeinrichtung,
  • Figur 2 einen Schnitt wie Figur 1, jedoch bei einem anderen Ausführungsbeispiel,
  • Figur 3 eine Stirnansicht der Darstellung in Figur 1,
  • Figur 4 eine Draufsicht auf die Bauelemente einer elektrischen Absicherung entsprechend Figur 2 in der Betriebsstellung,
  • Figur 4a eine Draufsicht in Richtung des Pfeiles 25 in Figur 4,
  • Figur 5 eine Draufsicht entsprechend Figur 4, jedoch in dem Zustand bei gelöster Klemmkupplung und
  • Figur 5a eine Draufsicht in Richtung des Pfeiles 25 in Figur 5.
Show it:
  • FIG. 1 shows a section in an axial plane through an exemplary embodiment of a clamping coupling on a cylinder of a turning device,
  • FIG. 2 shows a section as in FIG. 1, but in another exemplary embodiment,
  • FIG. 3 shows an end view of the illustration in FIG. 1,
  • FIG. 4 shows a top view of the components of an electrical fuse corresponding to FIG. 2 in the operating position,
  • FIG. 4a shows a plan view in the direction of arrow 25 in FIG. 4,
  • Figure 5 is a plan view corresponding to Figure 4, but in the state with the clamp coupling and
  • 5a shows a plan view in the direction of arrow 25 in FIG.

Beide Ausführungsbeispiele zeigen die Anordnung des Festzahnrades 1 an dem einen Ende der Welle 2 eines auf der Zeichnung aus Gründen der besseren Übersicht nicht dargestellten Zylinders der Wendeeinrichtung einer Bogenrotationsdruckmaschine für den wahlweisen Schöndruck oder Schön- und Widerdruck. Das Festzahnrad ist koaxial zur Welle 2 durch Schrauben 3 mit der Stirnfläche der Welle 2 verschraubt. Auf der Vorderseite des Festzahnrades 1 ist durch eine in der Schnittdarstellung winkelförmige Ausnehmung ein Zapfenansatz 4 gebildet, auf dem das kranzartig gestaltete und durch Klemmung mit dem Festzahnrad 1 kuppelbare Verstellzahnrad 5 im Drehwinkel einstellbar angeordnet ist. Diese kraftschlüssige Kupplung des Verstellzahnrades 5 mit dem Festzahnrad 1 erfolgt durch eine Klemmplatte 6, die den Klemmkörper bildet, und durch eine Klemmschraube 7, die eine zentrale Bohrung der Klemmplatte 6 durchgreift, sich mit dem Schraubenkopf 8 gegen die Klemmplatte 6 abstützt und mit ihrem Bolzengewinde in ein Muttergewinde in einer Bohrung der Welle 2 einschraubbar ist. An der Innenseite der Klemmplatte 6 ist ein angeformter Druckring 9 ausgebildet, durch den das Verstellzahnrad 5 beim Anziehen der Klemmschraube 7 gegen das Festzahnrad 1 gepreßt wird, so daß beide Zahnräder durch Reibungskräfte kraftschlüssig miteinander verbunden werden. Dabei sind die stirnseitigen Berührungsflächen beider Zahnräder wirksam.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. On the front of the fixed gear 1, 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. 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 gear wheels are frictionally connected to one another by frictional forces. The front contact surfaces of both gears are effective.

Zur Vermehrung der wirksamen Reibflächen zwischen dem Festzahnrad 1 und dem Verstellzahnrad 5 sind zusätzliche Reibelemente vorgesehen und abwechselnd mit einem der beiden Zahnräder verbunden, wobei diese Reibelemente nach Art einer Lamellenkupplung sich überlappend ineinandergreifen und im Überlappungsbereich durch die Klemmplatte 6 über den Druckring 9, der sich gegen ein außenliegendes Reibelement abstützt, ebenfalls fest zusammengepreßt werden. Die Ausführungsbeispiele zeigen Reibelemente aus Reibscheiben 10 und 11, die entweder an dem Festzahnrad 1 oder an dem Verstellzahnrad 5 mittels Schrauben 12 und 13 befestigt sind und lamellenartig ineinandergreifen, so daß hinter dem Druckring 9 ein Überlappungsbereich entsteht. Das in der Figur 1 dargestellte Ausführungsbeispiel zeigt zwei Reibscheiben 10, die mittels Schrauben 12 an der Stirnfläche des Zapfenansatzes 4 befestigt sind, und eine weitere Reibscheibe 11, die mittels Schrauben 13 an der Seitenfläche des Verstellzahnrades 5 befestigt ist. Die durch die Materialdicken in axialer Richtung der Welle 2 bedingten Höhenunterschiede sind durch Unterlegscheiben, Zwischenringe 14 oder andere Elemente ausgeglichen. Der innere Rand der Reibscheibe 11 greift lamellenartig zwischen die äußeren Ränder der Reibscheiben 10, so daß dadurch drei zusätzliche, ringförmige Reibflächen gebildet werden, durch die die übertragbaren Reibungskräfte erhöht werden können. Eine weitere Vermehrung der Reibungsflächen kann beispielsweise durch eine paketartige Anordnung der Reibscheiben erreicht werden, wie sie beispielsweise in der Figur 2 dargestellt ist. Hiernach sind an dem Verstellzahnrad 5 zwei Reibscheiben 11 mittels Schrauben 13 befestigt, die mit ihrem inneren Rand zwischen die äußeren Ränder von Reibscheiben 10 greifen, die an dem Zapfenansatz 4 des Festzahnrades 1 mittels Schrauben 12 befestigt sind. Der an der Klemmplatte 6 ausgebildete Druckring 9 drückt gegen die äußere Reibscheibe 10 des an dem Zapfenansatz 4 befestigten Reibscheibenpaketes, dessen innere Reibscheibe sich gegen eine ringförmige Auflagefläche an dem Verstellzahnrad 5 abstützt, so daß fünf zusätzliche Reibflächen gebildet sind.To increase the effective friction surfaces between the fixed gear 1 and the adjusting gear 5, 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. The exemplary embodiment shown in 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. Thereafter, two friction disks 11 are fastened to the adjusting gear 5 by means of screws 13, which engage with their inner edge between the outer edges of friction disks 10, which are fastened to the pin attachment 4 of the fixed gear 1 by means of screws 12. The pressure ring 9 formed on the clamping plate 6 presses against the outer friction disk 10 of the friction disk packet fastened to the pin attachment 4, the inner friction disk of which is supported against an annular bearing surface on the adjusting gear 5, so that five additional friction surfaces are formed.

Für die Gestaltung der Reibscheiben 10 und 11 ist eine in Richtung der Achse der Welle 2 elastisch verformbare Ausbildung vorgesehen, die den durch den Druckring 9 ausgeübten Klemmkräften möglichst keinen Widerstand entgegensetzt. Dies kann durch einen elastisch verformbaren Werkstoff erreicht und gegebenenfalls dadurch unterstützt werden, daß die Reibscheiben im Überlappungsbereich und gegebenenfalls darüber hinaus radiale Einschnitte bzw. Ausschnitte aufweisen, durch die Zungen gebildet werden, die sich leichter in Achsrichtung der Welle 2 verformen lassen, wie es sich beispielsweise aus der Darstellung in Figur 3 entnehmen läßt.For the design of the friction disks 10 and 11, 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.

Zum Zwecke der Montage ist vorgesehen, daß wenigstens die an dem Verstellzahnrad 5 oder an dem Festzahnrad 1 befestigten Reibscheiben geteilt ausgebildet sind, so daß getrennt montierbare Segmente entstehen. Vorteilhaft werden die an dem Verstellzahnrad 5 befestigten Reibscheiben 11 aus Segmenten zusammengesetzt, die von außen zwischen die Reibscheiben 10 geschoben werden, nachdem diese bereits fest montiert sind.For the purpose of assembly, it is provided that 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.

Anstelle der in den Ausführungsbeispielen dargestellten formschlüssigen Verbindung der Reibscheiben untereinander, die an dem gleichen Zahnrad befestigt sind, kann auch eine kraftschlüssige Verbindung vorgesehen sein. Die Montage und Demontage der Reibscheiben kann dadurch erleichtert werden, daß die Reibscheiben und Zwischenringe durch Zwischenlagen zu Paketen zusammengefügt, z.B. miteinander verklebt werden, so daß nur ein Teil zu montieren ist, entweder in der Ausbildung als Ring oder als Ringsegment, wie es weiter oben erläutert ist.Instead of the positive connection of the friction disks to one another, which are fastened to the same gearwheel, as shown in the exemplary embodiments, 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.

Die Mittel zur elektrischen Absicherung der wirksamen Kupplung zwischen dem Festzahnrad 1 und dem Verstellzahnrad 5 bestehen aus einem auf der Klemmschraube 7 drehfest angeordneten Schaltring 15 und aus an der Klemmplatte 6 radial beweglich geführten Schaltplatten 16, die der Schaltring 15 beim Lösen der Klemmung zwischen dem Festzahnrad 1 und dem Verstellzahnrad 5 radial bewegt und dadurch mit einer kreisbogenförmigen Kontaktfläche 17 auf einen elektrischen Schalter 18 einwirkt, der im Versorgungsstromkreis der Maschine angeordnet ist. Die Schaltplatte 16 ist aus vier Viertelkreissegmenten zusammengesetzt, von denen je zwei sich diametral zur Achse der Klemmschraube 7 gegenüberliegen und paarweise zusammenwirken, so daß sie sich gleichsinnig entweder gemeinsam nach außen oder gemeinsam nach innen zur Mitte der Klemmschraube 7 bewegen. Diese Elemente der elektrischen Absicherung sind auf der Zeichnung in den Figuren 4 und 5 dargestellt, wobei jedoch die Klemmschraube 7 durch den Schraubenkopf 8 verdeckt wird. Jedes Segment der Schaltplatte 16 weist an der inneren Ringfläche eine Nocke 19 auf, die mit einer komplementär geformten Kurve 20 am Schaltring 15 zusammenwirkt. Die Nocken und Kurven des einen Segmentpaares der Schaltplatte 16 sind zu den Nocken und Kurven des anderen Segmentpaares der Schaltplatte 16 sowohl axial versetzt als auch radial um 90 Grad zueinander versetzt angeordnet. Bei einer Verdrehung der Klemmschraube 7 erfolgt auch eine Relativbewegung des Schaltringes 15 gegenüber den Segmenten der Schaltplatte 16, so daß die Nocken 19 und Kurven 20 eine radiale Bewegung der Segmente der Schaltplatte bewirken, durch die der Schalter 18 betätigt wird. Damit diese Bewegung bei minimalem Drehwinkel einen ausreichenden Schaltweg ergibt, sind die wirksamen Kurvenflächen und Nockenflächen mit einer Steigung ausgebildet, die gerade oder als Rundung ausgelegt sein kann. Die Gegenbewegung der Segmente der Schaltplatte 16 erfolgt vorteilhaft durch Federkraft, so daß jedes Segment der Schaltplatte 16 mittels einer Feder 21 gegenüber der Klemmplatte 6 nach innen zur Achse der Klemmschraube 7 abgefedert ist. Die Führung der Segmente der Schaltplatte 16 erfolgt durch Schrauben 22, die radial gerichtete Schlitze der Segmente der Schaltplatte durchgreifen. Die Segmentaufteilung der Schaltplatte 16 und das paarweise Zusammenwirken der Segmente wird konstruktiv dadurch erreicht, daß die Nocken 19a des einen Segmentpaares auf der Vorderseite der Segmente und die Nocken 19b des anderen Paares auf der Rückseite der Segmente der Schaltplatte ausgebildet sind, wie es sich aus der Darstellung in den Figuren 4, 4a, 5 und 5a ergibt. Erreicht wird dadurch eine Klemmschraubendrehung über mehr als 90 Grad unter Öffnung des Schalters 18 im Antriebsstromkreis der Maschine. Begrenzt wird die Öffnungsbewegung durch einen mit dem Schaltring 15 verbundenen Anschlagstift 23, der mit Anschlägen 24 an Schrauben für die Führung und Halterung des einen Segmentpaares zusammenwirkt und den Öffnungswinkel der Klemmschraube 7 von einer Anschlaglage bis zur anderen Anschlaglage bis auf etwa 160 Grad begrenzt. BEZUGSZEICHENLISTE 1 Festzahnrad 14 Zwischenring 2 Welle 15 Schaltring 3 Schraube 16 Schaltplatte 4 Zapfenansatz 17 Kontaktfläche 5 Verstellzahnrad 18 Schalter 6 Klemmplatte 19 ) 7 Klemmschraube 19a) Nocken 8 Schraubenkopf 19b) 9 Druckring 9 Druckring 20 Kurve 10 Reibscheibe 21 Feder 11 Reibscheibe 22 Schraube 12 Schraube 23 Anschlagstift 13 Schraube 24 Anschlag 25 Pfeil 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. When the clamping screw 7 is rotated, there is also a relative movement of the switching ring 15 with respect to the segments of the switching plate 16, so that the cams 19 and curves 20 bring about a radial movement of the segments of the switching plate by which the switch 18 is actuated. So that this movement results in a sufficient switching path with a minimal angle of rotation, the effective cam surfaces and cam surfaces are designed with an incline that can be designed straight or as a curve. The counter movement of the segments of the switching plate 16 is advantageously carried out by spring force, so that each segment of the switching plate 16 is cushioned inwards by means of a spring 21 with respect to the clamping plate 6 to the axis of the clamping screw 7. 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. REFERENCE SIGN LIST 1 Fixed gear 14 Intermediate ring 2nd wave 15 Switching ring 3rd screw 16 Circuit board 4th Pin approach 17th Contact area 5 Adjusting gear 18th counter 6 Clamping plate 19) 7 Clamping screw 19a) cam 8th Screw head 19b) 9 pressure ring 9 Pressure ring 20th Curve 10th Friction disc 21st feather 11 Friction disc 22 screw 12 screw 23 Stop pin 13 screw 24th attack 25th arrow

Claims (17)

1. Vorrichtung zur kraftschlüssigen Kupplung eines Festzahnrades und eines demgegenüber in der Drehlage einstellbaren Verstellzahnrades an einem Zylinder einer Wendeeinrichtung in einer Bogenrotationsdruckmaschine, bei der das Festzahnrad und das dazu koaxial angeordnete Verstellzahnrad durch ein betätigbares Spannorgan und einen Klemmkörper miteinander verspannbar sind, der sich gegen das eine Zahnrad abstützt und mit dem Spannorgan an dem anderen Zahnrad gehalten ist,
dadurch gekennzeichnet,
daß die beiden Zahnräder (1,5) Reibelemente (10,11) aufweisen, die nach Art einer Lamellenkupplung sich überlappend ineinandergreifen, und daß sich der Klemmkörper (6) mit einem ringförmigen Auflager (9) im Überlappungsbereich gegen ein außenliegendes Reibelement (10) abstützt.1.Device for the frictional coupling of a fixed gear and an adjusting gear, which is adjustable in the rotational position, on a cylinder of a turning device in a sheet-fed rotary printing press, in which the fixed gear and the adjusting gear arranged coaxially therewith can be clamped together by an actuating tensioning element and a clamping body, which can be braced against one another supports a gear and is held on the other gear with the tensioning element,
characterized by
that the two gearwheels (1, 5) have friction elements (10, 11) which overlap one another in the manner of a multi-plate clutch, and that the clamping body (6) with an annular support (9) in the overlap area against an external friction element (10) supports. 2. Vorrichtung nach Anspruch 1,
dadurch gekennzeichnet,
daß Reibelemente aus Reibscheiben (10,11) vorgesehen sind, die sich einerseits von außen nach innen und andererseits von innen nach außen radial erstrecken und abwechselnd an einem der beiden Zahnräder (1,5) befestigt sind.2. Device according to claim 1,
characterized by
that friction elements made of friction disks (10, 11) are provided which extend radially on the one hand from outside to inside and on the other hand from inside to outside and are alternately fastened to one of the two gearwheels (1, 5). 3. Vorrichtung nach den Ansprüchen 1 und 2,
dadurch gekennzeichnet,
daß der Klemmkörper aus einer Klemmplatte (6) besteht, die einerseits am Festzahnrad (1) gehalten ist und sich andererseits mit seinem Druckring (9) gegen eine ebenfalls am Festzahnrad (1) befestigte Reibscheibe (10) eines Reibscheibenpakets aus mehreren Reibscheiben abstützt, die die an dem Verstellzahnrad (5) befestigten Reibscheiben (11) an ihrem Rand zwischen sich aufnehmen und von denen die außen auf der gegenüberliegenden Seite des Reibscheibenpakets angeordnete Reibscheibe (10) an einer Ringfläche des Verstellzahnrades (5) anliegt.3. Device according to claims 1 and 2,
characterized by
that the clamping body consists of a clamping plate (6), which is held on the one hand on the fixed gear (1) and, on the other hand, is supported with its pressure ring (9) against a friction disc (10), also attached to the fixed gear (1), of a friction disc package comprising a plurality of friction discs, which the friction disks (11) attached to the adjusting gear (5) receive between them at their edge and of which the friction disk (10) arranged on the outside on the opposite side of the friction disk package rests on an annular surface of the adjusting gear (5). 4. Vorrichtung nach den Ansprüchen 1 bis 3,
dadurch gekennzeichnet,
daß das Spannorgan aus einer außen betätigbaren Klemmschraube (7) besteht, die eine zentrale Bohrung einer Klemmplatte (6) mit einem an ihrem Rand angeformten Druckring (9) durchsetzt und mit ihrem Gewinde in ein gegenüber dem Festzahnrad (1) festgelegtes Muttergewinde einschraubbar ist.4. Device according to claims 1 to 3,
characterized by
that the clamping member consists of an externally actuable clamping screw (7) which passes through a central bore of a clamping plate (6) with a pressure ring (9) formed on its edge and can be screwed with its thread into a nut thread fixed relative to the fixed gear (1). 5. Vorrichtung nach den Ansprüchen 1 bis 4,
dadurch gekennzeichnet,
daß am Festzahnrad (1) und gegebenenfalls am Verstellzahnrad (5) mehrere Reibscheiben (10,11) und zwischen diesen angeordnete Zwischenringe (14) vorgesehen sind, deren Dicke der Stärke der Reibscheiben (10,11) an dem jeweils anderen Zahnrad entspricht.5. Device according to claims 1 to 4,
characterized by
that a plurality of friction disks (10, 11) and intermediate rings (14) arranged between them are provided on the fixed gear (1) and optionally on the adjusting gear (5), the thickness of which corresponds to the thickness of the friction disks (10, 11) on the other gear. 6. Vorrichtung nach den Ansprüchen 1 bis 5,
dadurch gekennzeichnet,
daß die Reibscheiben (10,11) in Achsrichtung der Zahnräder (1,5) wenigstens begrenzt elastisch verformbar ausgebildet sind.6. Device according to claims 1 to 5,
characterized by
that the friction disks (10, 11) are designed to be elastically deformable at least to a limited extent in the axial direction of the gear wheels (1,5). 7. Vorrichtung nach den Ansprüchen 1 bis 6,
dadurch gekennzeichnet,
daß die am Verstellzahnrad (5) befestigten, von außen zwischen die inneren Reibscheiben (10) am Festzahnrad (1) eingreifenden Reibscheiben (11) geteilt und aus Segmenten montierbar sind.7. Device according to claims 1 to 6,
characterized by
that the friction disks (11) attached to the adjusting gear (5), which engage from the outside between the inner friction disks (10) on the fixed gearwheel (1), can be divided and assembled from segments. 8. Vorrichtung nach den Ansprüchen 1 bis 7,
dadurch gekennzeichnet,
daß Reibscheiben (10,11) im Überlappungsbereich Einschnitte aufweisen, durch die radial gerichtete Zungen gebildet sind.8. Device according to claims 1 to 7,
characterized by
that friction disks (10, 11) have incisions in the overlap area, through which radially directed tongues are formed. 9. Vorrichtung nach den Ansprüchen 1 bis 8,
dadurch gekennzeichnet,
daß die Reibscheiben (10,11) und die Zwischenringe (14) formschlüssig mit den Zahnrädern (1,5) verbunden sind.9. Device according to claims 1 to 8,
characterized by
that the friction discs (10, 11) and the intermediate rings (14) are positively connected to the gears (1,5). 10. Vorrichtung nach den Ansprüchen 1 bis 8,
dadurch gekennzeichnet,
daß die Reibscheiben (10,11) kraftschlüssig mit den Zahnrädern (1,5) verbunden sind.10. Device according to claims 1 to 8,
characterized by
that the friction disks (10, 11) are non-positively connected to the gears (1,5). 11. Vorrichtung nach den Ansprüchen 1 bis 10,
dadurch gekennzeichnet,
daß die Reibscheiben (10,11) und die Zwischenringe (14) eine Zwischenlage aufweisen, insbesondere miteinander verklebt sind.11. The device according to claims 1 to 10,
characterized by
that the friction disks (10, 11) and the intermediate rings (14) have an intermediate layer, in particular are glued to one another. 12. Vorrichtung nach einem oder mehreren der Ansprüche 1 bis 11 mit elektrischen Mitteln zur Absicherung der wirksamen Kupplung des Festzahnrades (1) und des Verstellzahnrades (5),
dadurch gekennzeichnet,
daß auf der das Spannorgan bildenden Spannschraube (7) ein Schaltring (15) befestigt und an der Klemmplatte (6) wenigstens eine radial beweglich geführte Schaltplatte (16) vorgesehen ist, die der Schaltring (15) beim Lösen der Kupplung radial bewegt und dadurch mit einer kreisbogenförmigen Kontaktfläche (17) auf einen elektrischen Schalter (18) im Versorgungsstromkreis der Maschine einwirkt.12. The device according to one or more of claims 1 to 11 with electrical means for securing the effective coupling of the fixed gear (1) and the adjusting gear (5),
characterized by
that a switching ring (15) is attached to the clamping screw forming the tensioning member (7) and at least one radially movably guided switching plate (16) is provided on the clamping plate (6), which moves the switching ring (15) radially when the clutch is released and thereby with an arcuate contact surface (17) acts on an electrical switch (18) in the supply circuit of the machine. 13. Vorrichtung nach Anspruch 12,
dadurch gekennzeichnet,
daß der Schaltring (15) und die Schaltplatte (16) mit einer Nocke (19) des einen Teils und einer komplementär geformten Kurve (20) des anderen Teils zusammenwirken.13. The apparatus according to claim 12,
characterized by
that the switching ring (15) and the switching plate (16) interact with a cam (19) of one part and a complementarily shaped curve (20) of the other part. 14. Vorrichtung nach den Ansprüchen 12 und 13,
dadurch gekennzeichnet,
daß vier jeweils in der Form eines Viertelkreissegmentes ausgebildete Segmente die Schaltplatte (16) bilden, und daß je zwei Segmente sich diametral zur Achse der Spannschraube (7) gegenüberliegende Segmente paarweise zusammenwirken und gleichsinnig nach innen bzw. außen beweglich sind.14. Device according to claims 12 and 13,
characterized by
that four segments each formed in the shape of a quarter-circle segment form the circuit board (16), and that two segments, diametrically opposite to the axis of the clamping screw (7), interact in pairs and are movable in the same direction inwards or outwards. 15. Vorrichtung nach den Ansprüchen 12 bis 14,
dadurch gekennzeichnet,
daß die die radiale Bewegung bewirkende Nocke (19) an den Segmenten der Schaltplatte (16) und die komplementär geformten Kurven (20) in Nuten des Schaltringes (15) ausgebildet sind, und daß die Nocken (19a) und Kurven (20) des einen Paares zu den Nocken (19b) und Kurven (20) des anderen Paares der Segmente der Schaltplatte (16) axial und radial um 90 Grad zueinander versetzt angeordnet sind.15. The device according to claims 12 to 14,
characterized by
that the radial movement causing cam (19) on the segments of the switching plate (16) and the complementarily shaped curves (20) are formed in grooves of the switching ring (15), and that the cams (19a) and Curves (20) of one pair to the cams (19b) and curves (20) of the other pair of the segments of the circuit board (16) are axially and radially offset by 90 degrees to each other. 16. Vorrichtung nach den Ansprüchen 1 bis 15,
dadurch gekennzeichnet,
daß die Nocken (19a) des einen Paares der Segmente der Schaltplatte (16) auf der Vorderseite und die Nocken (19b) des anderen Paares der Segmente der Schaltplatte (16) auf deren Rückseite ausgebildet sind.16. The device according to claims 1 to 15,
characterized by
that the cams (19a) of one pair of the segments of the circuit board (16) on the front and the cams (19b) of the other pair of segments of the circuit board (16) are formed on the rear. 17. Vorrichtung nach den vorhergehenden Ansprüchen 12 bis 16,
dadurch gekennzeichnet,
daß die Segmente der Schaltplatte (16) gegen die radiale Bewegung zur Betätigung des elektrischen Schalters (18) im Versorgungsstromkreis der Maschine mit einer Federkraft (21) belastet sind.17. Device according to the preceding claims 12 to 16,
characterized by
that the segments of the circuit board (16) against the radial movement for actuating the electrical switch (18) in the supply circuit of the machine are loaded with a spring force (21).
EP89108714A 1988-06-13 1989-05-16 Device for fixing the relative position between a toothed gear and a coaxially toothed ring in a rotary sheet printing machine Expired - Lifetime EP0346619B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3820026A DE3820026A1 (en) 1988-06-13 1988-06-13 DEVICE FOR THE POWERFUL CLUTCHING OF A FIXED GEAR WHEEL AND AN ADJUSTING GEAR WHEEL ON A CYLINDER OF A TURNING DEVICE IN AN ARC ROTATION PRINTING MACHINE AND ELECTRICAL PROTECTION OF SUCH A DEVICE
DE3820026 1988-06-13

Publications (3)

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

Family

ID=6356410

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89108714A Expired - Lifetime EP0346619B1 (en) 1988-06-13 1989-05-16 Device for fixing the relative position between a toothed gear and a coaxially toothed ring in a rotary sheet printing machine

Country Status (6)

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

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0875375A1 (en) * 1997-04-30 1998-11-04 MAN Roland Druckmaschinen AG Device for detachably coupling a double toothed wheel
US6695114B2 (en) 2001-02-19 2004-02-24 Heidelberger Druckmaschinen Ag Multi-disk clutch
EP1393901A2 (en) * 2001-03-20 2004-03-03 Koenig &amp; Bauer Aktiengesellschaft Device for adjusting the contact pressure of an adjustably mounted cylinder

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DE4101823C2 (en) * 1990-01-31 1997-12-04 Kba Planeta Ag Drive gear train
DE4110035C2 (en) * 1991-03-27 1995-04-13 Roland Man Druckmasch Device for adjusting elements in folding cylinders of rotary printing machines
DE4131273C1 (en) * 1991-09-20 1992-12-10 Heidelberger Druckmaschinen Ag, 6900 Heidelberg, De
DE4141818C2 (en) * 1991-12-18 1995-05-04 Roland Man Druckmasch Clamping and tensioning devices
US5802920A (en) * 1995-11-15 1998-09-08 Heidelberger Druckmaschinen Aktiengesellschaft Double gear wheel of a turning device on printing presses
DE29518072U1 (en) * 1995-11-15 1996-01-04 Heidelberger Druckmaschinen Ag, 69115 Heidelberg Double gear wheel of a turning device on printing machines
JP2991138B2 (en) * 1996-12-09 1999-12-20 日本電気株式会社 Memory LSI failure analysis method
DE10113314C2 (en) 2001-03-20 2003-10-30 Koenig & Bauer Ag fixing
CN100509390C (en) 2001-12-06 2009-07-08 柯尼格及包尔公开股份有限公司 Device for regulating jointing force of printer roller and controlling clutch pressure of roller
DE10261984A1 (en) * 2002-09-21 2004-04-08 Koenig & Bauer Ag Method for adjusting the contact pressure of an adjustable roller
CN101737383B (en) * 2008-11-17 2014-02-26 海德堡印刷机械股份公司 Device for clamping or loosening driving wheel on shaft
CN108458010A (en) * 2018-05-30 2018-08-28 山东理工大学 A kind of noise reduction drum brake

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GB817354A (en) * 1955-11-11 1959-07-29 Reyrolle A & Co Ltd Improvements relating to printing press drives
GB1253525A (en) * 1968-11-28 1971-11-17 Norman Samuel Hardy Improvements in traversing means for machine tools
DE2901236A1 (en) * 1978-04-19 1979-10-31 Polygraph Leipzig Drive adjusting unit for rotary sheet printing machine - reduces adjusting time for selective first and back-up printing
DE3611325A1 (en) * 1986-04-04 1987-10-08 Heidelberger Druckmasch Ag DEVICE FOR ADJUSTING THE RELATIVE ROTATION BETWEEN A GEAR WHEEL AND A GEAR WHEEL BEARING WITH THIS SIMULTANEOUSLY

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JPS5871162A (en) * 1981-10-24 1983-04-27 Komori Printing Mach Co Ltd Phase adjusting device of rotary sheet-fed press with reversing mechanism
JPS5878763A (en) * 1981-11-05 1983-05-12 Komori Printing Mach Co Ltd Adjusting device for phase of rotary sheet-printing machine with inversion mechanism
US4554842A (en) * 1983-04-25 1985-11-26 Cincinnati Milacron Inc. Anti-backlash mechanism for machine drive
DE3534488A1 (en) * 1985-09-27 1987-04-16 Koenig & Bauer Ag CLUTCH IN AN ARC ROTATION PRINTING MACHINE
DE3611324A1 (en) * 1986-04-04 1987-10-08 Heidelberger Druckmasch Ag DEVICE FOR ADJUSTING THE RELATIVE ROTATION BETWEEN A GEAR WHEEL AND A GEAR WHEEL BEARING WITH THIS SIMULTANEOUSLY
DE3614734A1 (en) * 1986-04-30 1987-11-05 Heidelberger Druckmasch Ag DEVICE FOR SECURING A ROTARY PRINTING MACHINE
US4848531A (en) * 1987-07-30 1989-07-18 Dana Corporation Electronic system for monitoring clutch brake engagement and clutch slippage
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GB817354A (en) * 1955-11-11 1959-07-29 Reyrolle A & Co Ltd Improvements relating to printing press drives
GB1253525A (en) * 1968-11-28 1971-11-17 Norman Samuel Hardy Improvements in traversing means for machine tools
DE2901236A1 (en) * 1978-04-19 1979-10-31 Polygraph Leipzig Drive adjusting unit for rotary sheet printing machine - reduces adjusting time for selective first and back-up printing
DE3611325A1 (en) * 1986-04-04 1987-10-08 Heidelberger Druckmasch Ag DEVICE FOR ADJUSTING THE RELATIVE ROTATION BETWEEN A GEAR WHEEL AND A GEAR WHEEL BEARING WITH THIS SIMULTANEOUSLY

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0875375A1 (en) * 1997-04-30 1998-11-04 MAN Roland Druckmaschinen AG Device for detachably coupling a double toothed wheel
US6695114B2 (en) 2001-02-19 2004-02-24 Heidelberger Druckmaschinen Ag Multi-disk clutch
EP1393901A2 (en) * 2001-03-20 2004-03-03 Koenig &amp; Bauer Aktiengesellschaft Device for adjusting the contact pressure of an adjustably mounted cylinder
EP1400354A2 (en) * 2001-03-20 2004-03-24 Koenig &amp; Bauer Aktiengesellschaft Devices for adjusting the contact pressure of an adjustably mounted cylinder
EP1400355A2 (en) * 2001-03-20 2004-03-24 Koenig &amp; Bauer Aktiengesellschaft Devices for adjusting the contact pressure of an adjustably mounted cylinder
EP1437219A2 (en) * 2001-03-20 2004-07-14 Koenig &amp; Bauer Aktiengesellschaft Devices for adjusting the contact pressure of an adjustably mounted cylinder
EP1437220A2 (en) * 2001-03-20 2004-07-14 Koenig & Bauer Aktiengesellschaft Devices for adjusting the contact pressure of an adjustably mounted cylinder
EP1437221A2 (en) * 2001-03-20 2004-07-14 Koenig &amp; Bauer Aktiengesellschaft Device for adjusting the contact pressure of an adjustably mounted cylinder
EP1400354A3 (en) * 2001-03-20 2007-04-25 Koenig &amp; Bauer Aktiengesellschaft Devices for adjusting the contact pressure of an adjustably mounted cylinder
EP1437220A3 (en) * 2001-03-20 2007-05-02 Koenig & Bauer Aktiengesellschaft Devices for adjusting the contact pressure of an adjustably mounted cylinder
EP1437219A3 (en) * 2001-03-20 2007-05-02 Koenig &amp; Bauer Aktiengesellschaft Devices for adjusting the contact pressure of an adjustably mounted cylinder
EP1437221A3 (en) * 2001-03-20 2007-05-09 Koenig &amp; Bauer Aktiengesellschaft Device for adjusting the contact pressure of an adjustably mounted cylinder
EP1400355A3 (en) * 2001-03-20 2007-05-23 Koenig &amp; Bauer Aktiengesellschaft Devices for adjusting the contact pressure of an adjustably mounted cylinder

Also Published As

Publication number Publication date
DE58902599D1 (en) 1992-12-10
CN1011768B (en) 1991-02-27
DE3820026C2 (en) 1991-08-29
DE3820026A1 (en) 1989-12-14
AU3628389A (en) 1989-12-14
CN1038791A (en) 1990-01-17
JPH0230534A (en) 1990-01-31
EP0346619A3 (en) 1990-05-30
US5048362A (en) 1991-09-17
EP0346619B1 (en) 1992-11-04

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