EP0346619B1 - 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
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
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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
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German (de)
French (fr)
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EP0346619A2 (en
EP0346619A3 (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, 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.

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, 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 compared 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.This object is achieved by the invention through 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 gear wheels. According to a particular inventive concept, 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.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.

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.Exemplary embodiments of the invention are shown schematically in part on 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:
Figure 1
3 shows a section in an axial plane through an exemplary embodiment of a clamping coupling on a cylinder of a turning device,
Figure 2
2 shows a section as in FIG. 1, but in another exemplary embodiment,
Figure 3
2 shows an end view of the illustration in FIG. 1,
Figure 4
2 shows a top view of the components of an electrical fuse according to FIG. 2 in the operating position,
Figure 4a
3 shows a plan view in the direction of arrow 25 in FIG. 4,
Figure 5
a plan view corresponding to Figure 4, but in the state with released clamping coupling and
Figure 5a
a plan view in the direction of arrow 25 in Figure 5.

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 gears 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.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 inward with respect to the clamping plate 6 by a spring 21 relative 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.

BEZUGSZEICHENLISTEREFERENCE SIGN LIST

11
FestzahnradFixed gear
22nd
Wellewave
33rd
Schraubescrew
44th
ZapfenansatzPin approach
55
VerstellzahnradAdjusting gear
66
KlemmplatteClamping plate
77
KlemmschraubeClamping screw
88th
SchraubenkopfScrew head
99
DruckringPressure ring
1010th
ReibscheibeFriction disc
1111
ReibscheibeFriction disc
1212
Schraubescrew
1313
Schraubescrew
1414
ZwischenringIntermediate ring
1515
SchaltringSwitching ring
1616
SchaltplatteCircuit board
1717th
KontaktflächeContact area
1818th
Schaltercounter
19 )19)
19a)19a)
Nockencam
19b)19b)
9 Druckring9 pressure ring
2020th
KurveCurve
2121
Federfeather
2222
Schraubescrew
2323
AnschlagstiftStop pin
2424th
Anschlagattack
2525th
Pfeilarrow

Claims (17)

  1. Device for force-lockingly connecting a fixed gearwheel and a gearwheel, which is adjustable in its rotational position with respect to said fixed gearwheel, on a cylinder of a turning device in a sheet-fed rotary printing machine, in said device said fixed gearwheel and said adjustable gearwheel, arranged co-axially thereto, can be clamped with respect to each other by means of an actuatable clamping element and a clamping body braced against one of said gearwheels and held on the other gearwheel by means of said clamping element,
    characterized in
    that both gearwheels (1, 5) comprise friction elements (10, 11) overlappingly interengaging in the manner of a multi-disc clutch, and that said clamping body (6) is braced with an annular bearing (9) against an outer friction element (10) in an overlap region.
  2. Device according to Claim 1,
    characterized in
    that there are provided friction elements consisting of friction discs (10, 11) extending from outside to inside and from inside to outside, respectively, and being fastened alternatingly to one of said gearwheels (1, 5).
  3. Device according to Claims 1 and 2,
    characterized in
    that the clamping body consists of a clamping plate (6) which, on one side, is held at the fixed gearwheel (1) and, on the other side thereof, braced with its pressure ring (9) against a friction disc (10), also fastened to the fixed gearwheel (1), of a friction-disc packet consisting of a plurality of friction discs, said friction discs being spaced apart so as to receive therebetween at a respective edge thereof the friction discs (11) fastened to the adjustable gearwheel (5), the outer friction disc (10) which is disposed opposite the friction-disc packet abuts against an annular surface of said adjustable gearwheel (5).
  4. Device according to Claims 1 through 3,
    characterized in
    that the clamping element consists of a clamping screw (7) being actuatable from outside, with a pressure ring (9) formed at its edge said clamping screw extends through a central bore provided in a clamping plate (6) and is threadedly screwable into a female thread fixed in position with respect to the fixed gearwheel (1).
  5. Device according to Claims 1 through 4,
    characterized in
    that at the fixed gearwheel (1) and, if necessary, at the adjustable gearwheel (5) there is provided a plurality of friction discs (10, 11) and intermediate rings (14) disposed therebetween, the thickness of a respective intermediate ring corresponding to the thickness of a friction disc (10, 11) at the other gearwheel.
  6. Device according to Claims 1 through 5,
    characterized in
    that the friction discs (10, 11) are designed so as to be elastically deformable in axial direction of the gearwheels (1, 5), at least to some degree.
  7. Device according to Claims 1 through 6,
    characterized in
    that the friction discs (11) which are fastened to the adjustable gearwheel (5) and interengage from outside between the inner friction discs (10) provided at the fixed gearwheel (1) are of split construction and assemblable in segments.
  8. Device according to Claims 1 through 7,
    characterized in
    that in the overlap region friction discs (10, 11) are formed with incisions defining radially directed lugs.
  9. Device according to Claims 1 through 8,
    characterized in
    that the friction discs (10, 11) and the intermediate rings (14) are form-lockingly connected to the gearwheels (1, 5).
  10. Device according to Claims 1 through 8,
    characterized in
    that the friction discs (10, 11) are force-lockingly connected to the gearwheels (1, 5).
  11. Device according to Claims 1 through 10,
    characterized in
    that the friction discs (10, 11) and the intermediate rings (14) have intermediate layers and, in particular, are bonded together.
  12. Device according to one or several of Claims 1 through 11 including electrical means for safeguarding an effective connection of the fixed gearwheel (1) to the adjustable gearwheel (5),
    characterized in
    that a switching ring (15) is fastened onto the clamping screw (7) forming the clamping element, and that at the clamping plate (6) there is provided at least one radially movably guided switching plate (16) which is radially moved by said switching ring (15) when releasing said connection, an arcuate contact surface (17) acting on an electrical switch (18) provided in a power-supply circuit of the printing machine.
  13. Device according to Claim 12,
    characterized in
    that the switching ring (15) and the switching plate (16) have respective complementary cam dogs (19) and cam curves (20) for effecting cooperative engagement.
  14. Device according to Claims 12 and 13,
    characterized in
    that the switching plate (16) is formed by four segments, each of which is designed as a quarter-circle segment, and that said segments which are disposed opposite one another diametrically to the axis of the clamping screw (7) cooperate pairwise and are movable inwardly and outwardly, respectively, in the same direction.
  15. Device according to Claims 12 through 14,
    characterized in
    that the cam dog (19) effecting the radial movement is provided on the segments of the switching plate (16), that the complementary cam curves (20) are disposed in grooves formed in the switching ring (15), and that cam dogs (19a) and said cam curves (20) of the one pair are offset axially and radially by 90° with respect to cam dogs (19b) and said cam curves (20) of the other pair of segments of said switching plate (16).
  16. Device according to Claims 1 through 15,
    characterized in
    that the cam dogs (19a) of the one pair of segments of the switching plate (16) are designed so as to be on a front side thereof, whereas the cam dogs (19b) of the other pair of segments of said switching plate (16) are designed so as to be on a rear side thereof.
  17. Device according to the preceding Claims 12 through 16,
    characterized in
    that by means of a spring force (21) the segments of the switching plate (16) are spring-loaded against the radial movement for actuating the electrical switch (18) in the power-supply circuit of the printing machine.
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 EP0346619A2 (en) 1989-12-20
EP0346619A3 EP0346619A3 (en) 1990-05-30
EP0346619B1 true EP0346619B1 (en) 1992-11-04

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ID=6356410

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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

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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)

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

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