EP0704300B1 - Gear train separation - Google Patents

Gear train separation Download PDF

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Publication number
EP0704300B1
EP0704300B1 EP95114701A EP95114701A EP0704300B1 EP 0704300 B1 EP0704300 B1 EP 0704300B1 EP 95114701 A EP95114701 A EP 95114701A EP 95114701 A EP95114701 A EP 95114701A EP 0704300 B1 EP0704300 B1 EP 0704300B1
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EP
European Patent Office
Prior art keywords
clamping
shaft
spring
gear
clamping elements
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
EP95114701A
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German (de)
French (fr)
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EP0704300A2 (en
EP0704300A3 (en
Inventor
Josef Mathes
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Manroland AG
Original Assignee
MAN Roland Druckmaschinen AG
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Publication date
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Publication of EP0704300A2 publication Critical patent/EP0704300A2/en
Publication of EP0704300A3 publication Critical patent/EP0704300A3/en
Application granted granted Critical
Publication of EP0704300B1 publication Critical patent/EP0704300B1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/008—Mechanical features of drives, e.g. gears, clutches

Definitions

  • the invention relates to a device for gear train separation according to the preamble of claim 1.
  • a device for gear train separation is from the German Patent 4 141 817 known.
  • this facility there is one annular unlocking device in the form of a hydraulic clutch to release the jamming between a main gear and provided a gear ring.
  • the hydraulic clutch acts Clamping devices that create the clamping by means of springs.
  • the facility has a relatively large volume.
  • Devices of this type are used, for example, in sheet-fed rotary printing machines used to convert to operating modes in to enable so-called straight printing or perfecting, the change being an adjustment of printing units relative to each other.
  • the aim of the invention is a device for gear train separation to make it more compact, which can be used as a structural unit.
  • the object of the invention is a device for gear train separation in a compact design with improved holding forces and to describe increased functional reliability.
  • the object is achieved according to the characterizing part of patent claim 1.
  • the advantage of the newly designed gear train separation device is the increased holding force of the device at the same time extreme compact design.
  • the facility is also able to separated part of the drive train when turning the other Drive train part to hold so that an additional brake is saved. Above all, support forces are no longer required into one of the gears to release the clamp. Through this mode of action, the accuracy of the Changeover increased further. These measures also increase the Functional safety of the facility is not insignificant. Further Advantages result from the features of the subclaims.
  • FIG. 1 an output gear 3 which is rotatable relative to this shaft journal 1 is shown on a shaft journal 1 which is connected to a drive gear 2.
  • a hydraulic coupling 4 is arranged on the end of the shaft journal 1 and is connected to a clamping device 5 for fastening the driven gear 3 on the shaft journal 1.
  • the hydraulic clutch 4 consists of an annular housing 7 and an annular piston 8 slidably mounted therein. Pressure medium can be fed into the annular space between the piston 8 and the housing 7.
  • the piston 8 is connected to a cover 9 which is fixed to the frame and is rotatably mounted on the end of the shaft journal 1 by means of a thrust bearing 6.
  • a gripping ring 10 is arranged on the housing 7 of the hydraulic clutch 4.
  • the gripping ring 10 is arranged with a button 10A opposite the clamping device 5.
  • the clamping device 5 consists of a flat, ring-shaped spring 11, a pressure ring 12, and an actuating ring 13.
  • the unit is of ring-shaped design and is placed on the shaft journal 1 so that it cannot move in the axial direction and is preloaded by means of the pressure bearing 6.
  • a series of bendable clamping elements 14 is arranged on the driven gear 3 facing the clamping device 5.
  • the clamping elements 14 rest on a clamping surface K on the shaft journal 1.
  • Spring 11 lying between the pressure ring 12 and the bendable clamping elements 14 generates a radial movement on the clamping elements 14 by axial movement of a switching element 15. 1 shows two variants for such switching elements 15 in the clamping device 5.
  • a switching element can be designed in the form of a packet of plate spring-like ring elements 15.1.
  • the switching element can be designed in the form of a single spring element 15.2 consisting of an annular, inclined wall.
  • the switching elements 15.1, 15.2 lie with the inside of their ring surfaces against a stop 16 on the driven gear 3.
  • the outside of the ring surfaces lies against a stop of the actuating ring 13.
  • the actuating ring 13 is moved away from the driven gear 3 by means of the hydraulic clutch 4.
  • the piston 8 is supported with a button 8A on the pressure ring 12 and the housing 10 with the button 10A on the actuating ring 13.
  • the switching elements 15.1, 15.2 are moved further in their inclined position.
  • the associated change in diameter on the switching elements 15.1, 15.2 releases or reduces the pressure on the clamping elements 14 relative to the shaft journal 1.
  • the force of the hydraulic clutch 4 is released, as a result of which the clamping elements 14 reconnect to the shaft journal 1 under the force of the spring 11 via the actuating ring 13 and the switching elements 15.1, 15.2 straighten up in the process.
  • FIG. 1 A comparable device is shown in FIG.
  • the clamping is generated by means of a wedge surface.
  • This is a Actuating ring 17 in the form of a ring with an inner conical surface 18 provided with a corresponding cone shape Outside surface of clamping elements 19 on the output gear 3 cooperates. These rest on a clamping surface K on the shaft journal 1.
  • the pretensioning is carried out by means of a wave-shaped spring arrangement 20 generated.
  • the biasing force of the spring 20 can be by means of the annular Hydraulic clutch 4 are canceled, which is the Clamping the driven gear 3 on the shaft journal 1 releases.
  • the two operating states are shown by way of example in FIG. 2.
  • the output gear 3 is clamped in the upper half of the figure, solved in the lower half of the picture.
  • the hydraulic clutch 4 fixed in the idle state on the cover 9 arranged, but held contact-free to the clamping device 5 is.
  • the switching state ie. when the two gears 2, 3, the buttons 8A, 10A are on the clamping device 5, increase their preload and relieve the actuation ring 17 or the clamping elements 19.
  • the shaft journal 1 firmly with the cover 9 and thus is also connected to the machine frame.
  • the drive gear 2 is blocked together with the coupled gear.
  • FIG. 3 shows a variant of the invention according to FIG. 1, where the preload of a conical actuation ring 21 opposite clamping elements 22 on the output gear 3 generated by a plate spring-like, annular spring 23 becomes.
  • the clamping elements 22 lie on a clamping surface K on Shaft journal 1 on.
  • the Selection is determined by the required spring characteristics.
  • the clamping of the driven gear 3 is by means of load the annular hydraulic clutch 4 on the plate spring 23 via the Pressure ring 24 and the actuating ring 21 canceled.
  • FIG. 4 A further variant can be seen in FIG. 4, wherein the locking of the output gear 3 with the shaft journal 1 via an axial acting fine tooth coupling 25 is generated.
  • the fine tooth coupling 25 is arranged in a ring on an actuating ring 26 and engages in a counterpart on the output gear 3.
  • the unlocking takes place through the annular hydraulic clutch 4 on the outside of the Actuation ring 26 by axial movement.
  • the fine toothing lifts 25 off, so that the driven gear 3 is freely rotatable.
  • clamping elements 14, 19, 22, 25th must be slotted at least in the axial direction in order to to be able to perform the required radial movement.
  • the clamping surface lying on the shaft journal 1 can ensure operational reliability K profiled, e.g. with a narrow groove. So that is the safety when switching the clamp through the escape of air guaranteed.
  • the output gear 3 to the drive gear 2 towards Have a groove in which a pin engages from the drive gear 2. This acts with a stop in the output gear 3 together to limit the maximum twist angle.
  • the device according to the descriptions described have overall an improved clamping of the driven gear 3 to be released with the shaft journal 1.
  • the clamping is due to the Arrangement directly on the shaft journal very compact and still points the necessary holding forces for the transmission of a high drive power on. Due to the reduced size are on the annular hydraulic clutch 4 very favorable conditions at the Sealing and when pressure medium is supplied.
  • the device is advantageous in sheet-fed rotary printing presses Bow turning can be used. Then it is used in particular become, if for space requirements or technological reasons for shifting drives between different intermediate gear levels with a smaller diameter next to the large main drive wheels be used.
  • the device represents the invention in a limited aspect and can also be carried out differently by interpreting the patent claim.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Mechanical Operated Clutches (AREA)
  • Valve Device For Special Equipments (AREA)
  • Retarders (AREA)
  • Flexible Shafts (AREA)

Abstract

The device is for clamping or loosening a clamp connection of two gearwheels, which are arranged coaxial and parallel, whereby one gearwheel (3) is rotating located on a union or pin of a shaft (1) of the other gearwheel. A clamp device is provided for prodn. of a strong connection of the gearwheel pair and a ring-shaped unlocking device (4) releases the strong connection. The rotatable gearwheel has clamp components (14) for connection with the shaft, and a pre-tensioned spring device (12) acts on the clamp components. The unlocking device for removal of the clamping engages on the spring device, whereby the gearwheel (2) fixed to the shaft is clamped to the frame.

Description

Die Erfindung betrifft eine Einrichtung zur Getriebezugtrennung nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a device for gear train separation according to the preamble of claim 1.

Eine Einrichtung zur Getriebezugtrennung ist aus der deutschen Patentschrift 4 141 817 bekannt. In dieser Einrichtung ist eine ringförmige Entriegelungsvorrichtung in Form einer Hydraulikkupplung zur Aufhebung der Klemmung zwischen einem Hauptzahnrad und einem Zahnradring vorgesehen. Die Hydraulikkupplung wirkt auf Spanneinrichtungen, die die Klemung mittels Federn herstellen. Die Einrichtung ist relativ großvolumig gebaut.A device for gear train separation is from the German Patent 4 141 817 known. In this facility there is one annular unlocking device in the form of a hydraulic clutch to release the jamming between a main gear and provided a gear ring. The hydraulic clutch acts Clamping devices that create the clamping by means of springs. The The facility has a relatively large volume.

Einrichtungen dieser Art werden beispielsweise in Bogenrotationsdruckmaschinen eingesetzt, um eine Umstellung für Betriebsarten im sogenannten Schöndruck oder Schön- und Widerdruck zu ermöglichen, wobei die Umstellung eine Verstellung von Druckwerken relativ zueinander erfordert.Devices of this type are used, for example, in sheet-fed rotary printing machines used to convert to operating modes in to enable so-called straight printing or perfecting, the change being an adjustment of printing units relative to each other.

Ziel der Erfindung ist, eine Einrichtung zur Getriebezugtrennung kompakter zu gestalten, die als Baueinheit einsetzbar ist.The aim of the invention is a device for gear train separation to make it more compact, which can be used as a structural unit.

Aufgabe der Erfindung ist es, eine Einrichtung zur Getriebezugtrennung in kompakter Bauform bei verbesserten Haltekräften und erhöhter Funktionssicherheit zu beschreiben.The object of the invention is a device for gear train separation in a compact design with improved holding forces and to describe increased functional reliability.

Die Aufgabe wird nach dem Kennzeichen des Patentanspruchs 1 gelöst. Der Vorteil der neukonzipierten Einrichtung zur Getriebezugtrennung ist die erhöhte Haltekraft der Einrichtung bei gleichzeitig äußerst kompakter Konzeption. Außerdem ist die Einrichtung in der Lage den abgetrennten Teil des Antriebszuges bei der Verdrehung des anderen Antriebzugteiles festzuhalten, so daß eine zusätzliche Bremse eingespart wird. Vor allem ist es nicht mehr erforderlich Stützkräfte in eines der Zahnräder einzuleiten, um die Klemmung aufzuheben. Durch diese Wirkungsweise wird die Genauigkeit bei der Umstellung weiter erhöht. Außerdem erhöhen diese Maßnahmen die Funktionssicherheit der Einrichtung nicht unerheblich. Weitere Vorteile ergeben sich aus den Merkmalen der Unteransprüche.The object is achieved according to the characterizing part of patent claim 1. The advantage of the newly designed gear train separation device is the increased holding force of the device at the same time extreme compact design. The facility is also able to separated part of the drive train when turning the other Drive train part to hold so that an additional brake is saved. Above all, support forces are no longer required into one of the gears to release the clamp. Through this mode of action, the accuracy of the Changeover increased further. These measures also increase the Functional safety of the facility is not insignificant. Further Advantages result from the features of the subclaims.

Ein Ausführungsbeispiel wird im folgenden In der Beschreibung anhand von Zeichnungen näher dargestellt.An embodiment is described in the description below illustrated in more detail by means of drawings.

Darin zeigt:

Fig. 1
eine Gesamtdarstellung einer Klemmeinrichtung mit zwei Varianten zur Betätigung der Klemmung,
Fig. 2
eine Klemmeinrichtung mit konusförmiger Klemmung,
Fig. 3
eine Variante zu Figuren 1 und 2 und
Fig. 4
eine Klemmeinrichtung mit ringförmiger Feinverzahnung.
It shows:
Fig. 1
an overall view of a clamping device with two variants for actuating the clamping,
Fig. 2
a clamping device with conical clamping,
Fig. 3
a variant of Figures 1 and 2 and
Fig. 4
a clamping device with ring-shaped fine teeth.

In Figur 1 ist auf einem Wellenzapfen 1, der mit einem Antriebszahnrad 2 verbunden ist, ein gegenüber diesem Wellenzapfen 1 verdrehbares Abtriebszahnrad 3 dargestellt. Auf dem Ende des Wellenzapfens 1 ist eine Hydraulikkupplung 4 angeordnet, die mit einer Klemmeinrichtung 5 zur Befestigung des Abtriebszahnrades 3 auf dem Wellenzapfen 1 verbunden ist. Die Hydraulikkupplung 4 besteht aus einem ringförmigen Gehäuse 7 und einem darin verschiebbar gelagerten ringförmigen Kolben 8. In den Ringraum zwischen Kolben 8 und Gehäuse 7 ist Druckmittel zuführbar. Der Kolben 8 ist mit einem gestellfest angeordneten Deckel 9 verbunden, der mittels eines Drucklagers 6 drehbar auf dem Ende des Wellenzapfens 1 gelagert ist. An dem Gehäuse 7 der Hydraulikkupplung 4 ist ein Greifring 10 angeordnet. Der Greifring 10 ist mit einer Schaltfläche 10A gegenüber der Klemmeinrichtung 5 angeordnet. Die Klemmeinrichtung 5 besteht aus einer flachen, ringförmigen Feder 11, einem Druckring 12, und einem Betätigungsring 13. Die Einheit ist ringförmig ausgebildet ist und auf dem Wellenzapfen 1 in axialer Richtung unverschiebbar aufgesetzt und mittels des Drucklagers 6 vorgespannt. An dem Abtriebszahnrad 3 ist zur Klemmeinrichtung 5 gewandt eine Reihe von biegbaren Klemmelementen 14 angeordnet. Die Klemmelemente 14 liegen auf einer Klemmfläche K an dem Wellenzapfen 1 an. Zwischen dem Druckring 12 und den biegbaren Klemmelementen 14 liegende Feder 11 erzeugt durch Axialbewegung eines Schaltelementes 15 eine Radialbewegung an den Klemmelementen 14.
In Figur 1 sind zwei Varianten für derartige Schaltelemente 15 in der Klemmeinrichtung 5 dargestellt. Zum einen kann ein Schaltelement in Form eines Pakets von tellerfederartigen Ringelementen 15.1 ausgebildet sein. Zum anderen kann das Schaltelement in Form eines einzigen aus einer ringförmigen, schrägstehenden Wand bestehenden Federelementes 15.2 ausgebildet sein. Die Schaltelemente 15.1, 15.2 liegen mit der Innenseite ihrer Ringflächen an einem Anschlag 16 auf dem Abtriebszahnrad 3 an. Die Außenseite der Ringflächen liegt an einem Anschlag des Betätigungsrings 13 an. Durch Schalten der Hydraulikkupplung 4 wird die Schräglage der Schaltelemente 15.1, 15.2 gegenüber den Klemmelementen 14 verändert, wodurch diese gegenüber dem Wellenzapfen 1 gelöst bzw. freigegeben werden. Funktionell ist die Vorspannung der Klemmung durch Anpressen des Deckels 9 gegen das Drucklager 6 und den Betätigungsring 13 erzeugt. Beim Trennen des Getriebezuges wird der Betätigungsring 13 mittels der Hydraulikkupplung 4 vom Abtriebszahnrad 3 weg bewegt. Dabei stützt sich der Kolben 8 mit einer Schaltfläche 8A am Druckring 12 und das Gehäuse 10 mit der Schaltfläche 10A am Betätigungsring 13 ab. Dadurch werden die Schaltelemente 15.1, 15.2 in ihrer Schräglage weiterbewegt. Durch damit einhergehend Durchmesseränderung an den Schaltelementen 15.1, 15.2 wird die die Anpressung der Klemmelemente 14 zum Wellenzapfen 1 gelöst bzw. verringert. Zum erneuten Klemmen der Einrichtung wird die Kraft der Hydraulikkupplung 4 aufgehoben, wodurch sich die Klemmelemente 14 unter der Kraft der Feder 11 über den Betätigungsring 13 wieder mit dem Wellenzapfen 1 verbinden und die Schaltelemente 15.1, 15.2 sich dabei aufrichten.In FIG. 1, an output gear 3 which is rotatable relative to this shaft journal 1 is shown on a shaft journal 1 which is connected to a drive gear 2. A hydraulic coupling 4 is arranged on the end of the shaft journal 1 and is connected to a clamping device 5 for fastening the driven gear 3 on the shaft journal 1. The hydraulic clutch 4 consists of an annular housing 7 and an annular piston 8 slidably mounted therein. Pressure medium can be fed into the annular space between the piston 8 and the housing 7. The piston 8 is connected to a cover 9 which is fixed to the frame and is rotatably mounted on the end of the shaft journal 1 by means of a thrust bearing 6. A gripping ring 10 is arranged on the housing 7 of the hydraulic clutch 4. The gripping ring 10 is arranged with a button 10A opposite the clamping device 5. The clamping device 5 consists of a flat, ring-shaped spring 11, a pressure ring 12, and an actuating ring 13. The unit is of ring-shaped design and is placed on the shaft journal 1 so that it cannot move in the axial direction and is preloaded by means of the pressure bearing 6. A series of bendable clamping elements 14 is arranged on the driven gear 3 facing the clamping device 5. The clamping elements 14 rest on a clamping surface K on the shaft journal 1. Spring 11 lying between the pressure ring 12 and the bendable clamping elements 14 generates a radial movement on the clamping elements 14 by axial movement of a switching element 15.
1 shows two variants for such switching elements 15 in the clamping device 5. On the one hand, a switching element can be designed in the form of a packet of plate spring-like ring elements 15.1. On the other hand, the switching element can be designed in the form of a single spring element 15.2 consisting of an annular, inclined wall. The switching elements 15.1, 15.2 lie with the inside of their ring surfaces against a stop 16 on the driven gear 3. The outside of the ring surfaces lies against a stop of the actuating ring 13. By switching the hydraulic clutch 4, the inclined position of the switching elements 15.1, 15.2 with respect to the clamping elements 14 is changed, as a result of which they are released or released with respect to the shaft journal 1. Functionally, the pretension of the clamping is generated by pressing the cover 9 against the thrust bearing 6 and the actuating ring 13. When the gear train is separated, the actuating ring 13 is moved away from the driven gear 3 by means of the hydraulic clutch 4. The piston 8 is supported with a button 8A on the pressure ring 12 and the housing 10 with the button 10A on the actuating ring 13. As a result, the switching elements 15.1, 15.2 are moved further in their inclined position. The associated change in diameter on the switching elements 15.1, 15.2 releases or reduces the pressure on the clamping elements 14 relative to the shaft journal 1. To reclamp the device, the force of the hydraulic clutch 4 is released, as a result of which the clamping elements 14 reconnect to the shaft journal 1 under the force of the spring 11 via the actuating ring 13 and the switching elements 15.1, 15.2 straighten up in the process.

In Figur 2 ist eine vergleichbare Vorrichtung dargestellt. Hierbei ist die Klemmung mittels einer Keilfläche erzeugt. Dazu ist ein Betätigungsring 17 in Ringform mit einer inneren Konusfläche 18 versehen, die mit einer in entsprechendes Konusform versehenen Außenfläche von Klemmelemente 19 am Abtriebszahnrad 3 zusammenarbeitet. Diese liegen auf einer Klemmfläche K am Wellenzapfen 1 an. Die Vorspannung wird mittels einer wellenförmigen Federanordnung 20 erzeugt. Die Vorspannkraft der Feder 20 kann mittels der ringförmigen Hydraulikkupplung 4 aufgehoben werden, wodurch sich die Klemmung des Abtriebszahnrades 3 auf dem Wellenzapfen 1 löst.A comparable device is shown in FIG. Here the clamping is generated by means of a wedge surface. This is a Actuating ring 17 in the form of a ring with an inner conical surface 18 provided with a corresponding cone shape Outside surface of clamping elements 19 on the output gear 3 cooperates. These rest on a clamping surface K on the shaft journal 1. The pretensioning is carried out by means of a wave-shaped spring arrangement 20 generated. The biasing force of the spring 20 can be by means of the annular Hydraulic clutch 4 are canceled, which is the Clamping the driven gear 3 on the shaft journal 1 releases.

Die beiden Betriebszustände sind in Figur 2 beispielhaft dargestellt. In der oberen Bildhälfte ist das Abtriebszahnrad 3 geklemmt, in der unteren Bildhälfte gelöst. Dabei wird deutlich, daß die Hydraulikkupplung 4 im Ruhezustand am Deckel 9 gestelltfest angeordnet, aber berührungsfrei zur Klemmeinrichtung 5 gehaltert ist. Im Schaltzustand, dh. bei Trennung der beiden Zahnräder 2, 3, liegen die Schaltflächen 8A, 10A an der Klemmeinrichtung 5 an, erhöhen deren Vorspannung und entlasten dabei den Betätigungsring 17 bzw. die Klemmelemente 19. Hier ist auch gut erkennbar, daß in diesem Zustand der Wellenzapfen 1 fest mit dem Deckel 9 und damit auch mit dem Maschinengestell verbunden ist. Das Antriebszahnrad 2 ist damit samt dem angekoppelten Getriebe blockiert.The two operating states are shown by way of example in FIG. 2. The output gear 3 is clamped in the upper half of the figure, solved in the lower half of the picture. It becomes clear that the hydraulic clutch 4 fixed in the idle state on the cover 9 arranged, but held contact-free to the clamping device 5 is. In the switching state, ie. when the two gears 2, 3, the buttons 8A, 10A are on the clamping device 5, increase their preload and relieve the actuation ring 17 or the clamping elements 19. Here it is also clearly visible that in this state of the shaft journal 1 firmly with the cover 9 and thus is also connected to the machine frame. The drive gear 2 is blocked together with the coupled gear.

In Figur 3 ist eine Variante der Erfindung nach Figur 1 dargestellt, wobei hier die Vorspannung eies konusförmigen Betätigungsringes 21 gegen über von Klemmelementen 22 am Abtriebszahnrad 3 mittels einer tellerfederartigen, ringförmigen Feder 23 erzeugt wird. Die Klemmelemente 22 liegen auf einer Klemmfläche K am Wellenzapfen 1 an. In gleicher Weise kann für diese Ausführungsform auch ein Federpaket aus zwei oder mehr Tellerfedern 23, auch in unterschiedlicher Orientierung zueinander, eingesetzt werden. Die Auswahl wird von der erforderlichen Federcharakteristik bestimmt. Die Klemmung des Abtriebszahnrades 3 wird durch Belastung mittels der ringförmigen Hydraulikkupplung 4 an der Tellerfeder 23 über den Druckring 24 und den Betätigungsring 21 aufgehoben.FIG. 3 shows a variant of the invention according to FIG. 1, where the preload of a conical actuation ring 21 opposite clamping elements 22 on the output gear 3 generated by a plate spring-like, annular spring 23 becomes. The clamping elements 22 lie on a clamping surface K on Shaft journal 1 on. In the same way for this embodiment also a spring assembly from two or more disc springs 23, also in different orientation to each other. The Selection is determined by the required spring characteristics. The clamping of the driven gear 3 is by means of load the annular hydraulic clutch 4 on the plate spring 23 via the Pressure ring 24 and the actuating ring 21 canceled.

In Figur 4 ist eine weitere Variante zu sehen, wobei die Verriegelung des Abtriebszahnrades 3 mit dem Wellenzapfen 1 über eine axial wirkende Feinzahnkupplung 25 erzeugt wird. Die Feinzahnkupplung 25 ist ringförmig an einem Betätigungsring 26 angeordnet und greift in ein Gegenstück am Abtriebszahnrad 3 ein. Die Entriegelung erfolgt durch die ringförmige Hydraulikkupplung 4 an der Außenseite des Betätigungsringes 26 durch Axialbewegung. Dabei hebt die Feinverzahnung 25 aus, so daß das Abtriebszahnrad 3 frei drehbar ist.A further variant can be seen in FIG. 4, wherein the locking of the output gear 3 with the shaft journal 1 via an axial acting fine tooth coupling 25 is generated. The fine tooth coupling 25 is arranged in a ring on an actuating ring 26 and engages in a counterpart on the output gear 3. The unlocking takes place through the annular hydraulic clutch 4 on the outside of the Actuation ring 26 by axial movement. The fine toothing lifts 25 off, so that the driven gear 3 is freely rotatable.

Allgemein ist zu bemerken, daß die Klemmelemente 14, 19, 22, 25 wenigstens in axialer Richtung geschlitzt sein müssen, um die erforderliche Radialbewegung ausführen zu können. Zur Erhöhung der Betriebssicherheit kann die auf dem Wellenzapfen 1 liegende Klemmfläche K profiliert sein, z.B. mit einer schmalen Nut. Damit ist die Sicherheit beim Schalten der Klemmung durch entweichen der Luft gewährleistet.In general, it should be noted that the clamping elements 14, 19, 22, 25th must be slotted at least in the axial direction in order to to be able to perform the required radial movement. To increase the The clamping surface lying on the shaft journal 1 can ensure operational reliability K profiled, e.g. with a narrow groove. So that is the safety when switching the clamp through the escape of air guaranteed.

Weiterhin kann das Abtriebszahnrad 3 zum Antriebszahnrad 2 hin eine Nut aufweisen, In die vom Antriebszahnrad 2 aus ein Stift eingreift. Dieser wirkt mit einem Anschlag im Abtriebszahnrad 3 zusammen, um den maximalen Verdrehwinkel zu begrenzen.Furthermore, the output gear 3 to the drive gear 2 towards Have a groove in which a pin engages from the drive gear 2. This acts with a stop in the output gear 3 together to limit the maximum twist angle.

Die Vorrichtung nach den beschriebenen Darstellungen weisen insgesamt eine verbesserte Klemmung des zu lösenden Abtriebszahnrades 3 mit dem Wellenzapfen 1 auf. Insbesondere ist die Klemmung durch die Anordnung direkt am Wellenzapfenl sehr kompakt und weist trotzdem die erforderlichen Haltekräfte für die Obertragung einer hohen Antriebsleistung auf. Durch die verringerte Baugröße sind an der ringförmigen Hydraulikkupplung 4 sehr günstige Verhältnisse bei der Abdichtung und bei der Zuführung von Druckmitteln erreicht.The device according to the descriptions described have overall an improved clamping of the driven gear 3 to be released with the shaft journal 1. In particular, the clamping is due to the Arrangement directly on the shaft journal very compact and still points the necessary holding forces for the transmission of a high drive power on. Due to the reduced size are on the annular hydraulic clutch 4 very favorable conditions at the Sealing and when pressure medium is supplied.

Die Vorrichtung ist vorteilhaft in Bogenrotationsdruckmaschinen mit Bogenwendung einsetzbar. Insbesondere dann wird sie eingesetzt werden, wenn aus Raumerfordernissen bzw. technologischen Gründen zur Antriebsverlagerung zwischen verschiedenen Ebenen Zwischenzahnräder mit kleinerem Durchmesser neben den großen Hauptantriebsrädern eingesetzt werden.The device is advantageous in sheet-fed rotary printing presses Bow turning can be used. Then it is used in particular become, if for space requirements or technological reasons for shifting drives between different intermediate gear levels with a smaller diameter next to the large main drive wheels be used.

Die Vorrichtung stellt die Erfindung in einem begrenzten Aspekt dar und ist unter Auslegung des Patentanspruches auch anders ausführbar.The device represents the invention in a limited aspect and can also be carried out differently by interpreting the patent claim.

Claims (10)

  1. Device for clamping or releasing a clamping connection of two gears (2, 3) which are arranged coaxially and parallel, wherein a gear (3) is mounted rotatably on a collar or trunnion of a shaft (1) of the other gear (2), with a clamping device (5) for generating a force positive connection of the gear pair and with an annular unlocking device (4) for releasing the force positive connection, which has a part fixed with respect to the claim and one shiftable relative thereto, and which is held in the rest position contact-free from the clamping device, characterised in that the rotatable gear (3) has clamping elements (14, 19, 22, 25) for force positive connection with the shaft (1), that a pretensioned spring device (12, 20, 23, 26) acts on the clamping elements (14, 19, 22, 25) and that the unlocking device (4) for releasing the clamping engages on the spring device (12, 20, 23, 26), whereby the gear (2) fixed to the shaft is clamped fixed with respect to the frame.
  2. Device according to Claim 1, characterised in that the spring device (12, 20, 23, 26) is arranged on the shaft (1) of the gears (2, 3).
  3. Device according to Claim 1, characterised in that the clamping elements (14, 19, 22, 25) are radially bendable, like tongues, and formed axially extended on the gear (3) and that a clamping surface (K) is arranged on the shaft relative to the clamping elements (14, 19, 22, 25).
  4. Device according to Claim 1 to 3, characterised in that the clamping elements (19, 22) are constructed wedge or conically shaped in the axial direction and, connected with the spring device, a correspondingly shaped single or multi-part actuation element (17, 21) acting on the clamping elements (19, 22) is provided.
  5. Device according to Claim 1 to 3, characterised in that the clamping elements (14) are constructed shaped cylindrically and, connected with the spring device, a switching element (15.1, 15.2) is provided acting on the clamping elements (14) and radially changeable by axial movement.
  6. Device according to Claim 5, characterized in that as switching element (15.1, 15.2), an annular element with obliquely lying wall is provided, the inner or outer projecting walls in the axial direction of which lie, depending upon the orientation, against the free gear (3) and against the spring (11) or the actuation ring (13) and the interior diameter of which changes on axial loading.
  7. Device according to Claim 3, characterised in that the clamping surface (K) on the shaft (1) is profiled.
  8. Device according to Claim 1 to 7, characterised in that the spring device (11, 23, 26) is constructed in the fashion of a plate spring and the spring elements surround the shaft (1).
  9. Device according to Claim 1 to 7, characterised in that the spring device (20) is constructed in a wavy shape and the spring elements surround the shaft (1).
  10. Device according to Claim 1 and 2, characterised in that the clamping elements are constructed as axially acting fine toothing (25) and is arranged on the free gear (3) and against an actuation ring (26) which is connected rotationally fast with the shaft (1) and that the unlocking device engages on the actuation ring (26), wherein it moves axially to relieve the connection of the fine toothing (25).
EP95114701A 1994-10-01 1995-09-19 Gear train separation Expired - Lifetime EP0704300B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4435226A DE4435226C2 (en) 1994-10-01 1994-10-01 Device for gear train separation, i.e. for clamping or releasing a clamp connection of two gear wheels
DE4435226 1994-10-01

Publications (3)

Publication Number Publication Date
EP0704300A2 EP0704300A2 (en) 1996-04-03
EP0704300A3 EP0704300A3 (en) 1997-04-23
EP0704300B1 true EP0704300B1 (en) 1998-06-17

Family

ID=6529778

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95114701A Expired - Lifetime EP0704300B1 (en) 1994-10-01 1995-09-19 Gear train separation

Country Status (3)

Country Link
EP (1) EP0704300B1 (en)
AT (1) ATE167433T1 (en)
DE (4) DE4435226C2 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10152838B4 (en) 2000-11-30 2013-10-31 Heidelberger Druckmaschinen Ag A method of operating a sheet-fed rotary printing press and sheet-fed rotary printing press
DE10226230A1 (en) 2001-07-09 2003-01-23 Heidelberger Druckmasch Ag Gear train for rotary printing machine, includes rotary bodies divided into pairs and individually installed with gears having unequal tooth pitches
DE10329429B4 (en) * 2003-07-01 2006-10-12 Koenig & Bauer Ag Drives of a printing machine
US7484610B2 (en) 2004-03-10 2009-02-03 Heidelberger Druckmaschinen Apparatus for the actuation of clamping elements that can be controlled remotely
DE102008009631A1 (en) * 2008-02-18 2009-08-27 Heidelberger Druckmaschinen Ag Coupling device for coupling and decoupling plate cylinder of processing machine i.e. sheet fed rotary printing machine, with/from electric motor, has coupling half that is supported at toothed wheel in axially movable manner
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
DE102017210658A1 (en) * 2017-06-23 2018-12-27 Zf Friedrichshafen Ag Friction device for transmitting a torque from a flywheel to a drive device and corresponding method

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3534486A1 (en) * 1985-09-27 1987-04-16 Koenig & Bauer Ag CLUTCH IN AN ARC ROTATION PRINTING MACHINE
DE4005965C2 (en) * 1989-04-08 1998-09-17 Ringspann Gmbh clutch
DE4141817C2 (en) * 1991-12-18 1993-10-07 Roland Man Druckmasch Gear train separation device
DE4214228A1 (en) * 1992-04-30 1993-11-04 Kba Planeta Ag Drive system for printing cylinder - Incorporates hydraulic release system to allow phase adjustment of cylinder

Also Published As

Publication number Publication date
DE59502574D1 (en) 1998-07-23
DE4447862C2 (en) 2000-06-29
DE4435226A1 (en) 1996-04-04
EP0704300A2 (en) 1996-04-03
DE4435226C2 (en) 2000-06-29
DE4447863C2 (en) 2002-03-14
ATE167433T1 (en) 1998-07-15
EP0704300A3 (en) 1997-04-23

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