EP3402678A2 - Unlocking a coupling of a double gearwheel - Google Patents

Abstract

The aim of the invention is to simplify a device for releasing the clamping of a double gearwheel in a sheet-fed rotary printing press for face printing or face printing and reverse printing. To this end, an annular piston (41) is arranged in an annular cylinder (40) coaxially with respect to an axial bearing (33) on the cylinder pin (10) of a printing unit cylinder of the sheet-fed rotary printing press.

Description

 The invention relates to a device for releasing a force-locking connection according to the preamble of patent claim 1.

In sheet-fed rotary printing presses, a so-called sheet turning device is arranged in the transport path of the printed sheets to accomplish the sheet turning. Normally, the sheet is transported with its leading edge through the entire machine, in which case only the top of the sheet is printed. If the sheet is to be printed from both sides, the sheet turning device is switched between two printing units, as a result of which there is the trailing edge of the sheet to the leading edge.

For bowing, so the relative position of the adjacent printing units is to change so that at this point instead of the leading edge of the sheet now the trailing edge can be passed. In order to change the relative position of the gear train is in such a printing press by means of a coupled double pelzahnrads (on a main gear a gear ring is rotatably arranged) equipped with clamping devices. The clamping devices may include a clamping ring and are stretched and unlocked via curves or spring sets. A device of this type describes the DE-PS 35 34 488. In this device for jamming two gears in a convertible from perfecting to perfecting sheet-fed rotary printing press, the clamping force is applied by a spring, which is to cancel the clamping of a pneumatic piston or Bellows can be charged. The clamping is done by means of one-armed cranked levers, which are connected via bolts with the clamps for clamping the gear ring. The one-armed, cranked levers are mounted on ball elements and generate at the point of articulation of the bolt in their Movement an axial displacement with respect to the clamping claws. As a result, a clamping force is applied to the clamping claws with the pivotal movement of the lever. The pivotal movement of the lever is generated by a guide body in which engage the ends of the lever. The guide body sits on a rod centric to the main gear. The rod is axially slidably connected to the drive pin of the gear and is loaded by a compression spring to the outside. The outer end of the guide rod around. In addition, the power transmission is very complicated

solved. Another problem can be seen that the bellows is supported against the force of the compression spring between the housing wall and the cylinder. Thus, when unlocking the clamp, an axial force is applied to the cylinder bearings which can lead to a displacement of the entire cylinder and thus the gears. In other known devices both all necessary for the locking and unlocking of the clamping elements and the existing drive elements are housed on the gear. The whole unit of this double gear can The device has some disadvantages. Above all, the elements for generating the clamping are relatively complex and cylinder-mounted. Thus, they run during the entire operation with relatively compact, but it is very complicated and difficult. For the most part, this is not intended for automation.

DE 41 41 817 A1 discloses a device for unlocking a double-wheel clutch in a sheet-fed rotary printing machine which is explained in more detail in the context of the exemplary embodiment. Here the unlocking mechanism is mounted without contact outside and without contact with the double gear. The arrangement is complicated and requires a variety of mechanical auxiliary elements for safe execution of the clamping and exemption of the double fur gear when adjusting a perfecting press. From DE 10 2005 041 696 A1 a coupling device for effecting a temporary decoupling of the sections of a gear train of a printing press is known. The coupling device for carrying out a change of the phase position of the respective gear sections to each other nenden setting process should be characterized by a robust construction and a reliable high torque transfer. The coupling device is coaxially provided with a first and second spur gear. A clamping device serves to generate one of the frictional transmission of a torque between the first and the second spur gear. A chamber device is used for applying a clamping force bringing the clamping device in a release state. In the clamping device, a clamping plate is arranged, which is resiliently biased in a basic position and generates the necessary clamping force for the clutch engagement. From DE 10 2005 039 918 A1 a coupling device for effecting a temporary decoupling of the sections of a gear train of a printing press is known. The coupling device is used for the temporary separation of a gear train of a printing machine for processing a change in the phase position of portions of the gear train. A first and a second spur gear are clamped by a clamping device for the frictional transmission of torque. To cancel the clamping force in a release state, a force is applied by a pressure medium via a chamber device, wherein the chamber device is formed by a first ring element and a second, with respect to the first ring element axially displaceable ring element: The first ring element has for this purpose a release-contact portion, which is employed to transfer the to the movement of the clamping device in a release state against a resiliently supported component. The second ring element has a support abutment portion which is seated in the release state on a coupled with the first spur support shoulder.

Further devices of a similar type are described in DE 36 1 1 324 A1, DE 197 18 140 C1, DE 35 34 488 A1 and DE 10 2005 045 098 A1. In all embodiments, a space-consuming design of the unlocking mechanisms found is to complain. Furthermore, no assignment to the storage areas of the respective printing press cylinder relevant for the sensitive area of the drive accuracy is listed. A powerful and simply designed, as well as compact unlocking device, which protects the gear and bearing assembly in the clamping and unlocking operations, is not known from the prior art. It is therefore the object to provide a device according to the preamble of claim 1, which makes a safe and gently executable and associated with little effort unlocking the clamping on the double gear possible with minimal change to the drive gear, so that the forces acting on no negative impact have the affected components.

This object is achieved according to the characterizing part of patent claim 1.

To be particularly advantageous is to see that the device aligns itself on the gear and has no contact with the double gear during normal operation. This is achieved in that the unlocking mechanism consists of a rectangular in cross-section and formed by two concentric rings circular Hubkanal in which a lifting ring is displaced by means of a fluidically generated drive energy against the rings of the Hubkanals. During the displacement, the rings are supported on elements of the double gear so that the clamping of the gear ring is canceled. The embodiment of different variants of this solution principle is explained in the subclaims.

The described variants use hydraulic or pneumatic energy. In all variants it is the same that the force applied to unlock the clamping of the gear ring on the main gear is diverted within the double gear and thereby a rigid axial bearing of the printing cylinder can act supported. This also results in no shifts z. B. could lead to a rotational displacement of the drive in a helical gearing. Furthermore, the unlocking system is not in the normal machine operation with the double gear in touch. At the double gear itself no additional elements are required, so that the mass of the double gear is not increased. The double gear itself is so completely maintenance-free and the clutch to cancel the clamping of the double gear is to be maintained without changes to this or built and removed. It is a device for releasing the frictionally generated connection of a arranged on a cylinder pin first spur gear and a first spur associated with this designed as a gear ring second spur existing double gear provided which is arranged in a convertible from perfecting perfecting sheet-fed rotary printing press. The second spur gear is clamped by loaded by spring tension tie rods on the first spur gear. The device is arranged symmetrically to the axis of the double gear and has for releasing at least one annular fluid-operated lifting arrangement. This is coupled to the machine frame and at least partially displaceable in the direction of an axis of the double gear. The lifting arrangement connects in the release position a part of the double gear to the machine frame.

According to the invention, the cylinder pin is received in a cylinder bearing, in which an axial bearing arranged separately from a radial bearing is provided. An annular fluid operated lift assembly is disposed directly adjacent and concentric with the axial support on the machine frame of the sheet-fed rotary printing machine. A pressure element of the lifting arrangement is assigned to a respective pressure element transmitting the spring force to a respective tie rod.

As a result, the spring forces acting on the tie rod (s) are reduced or eliminated under load from the pressure element. In a further development, it is provided that the annular lifting arrangement is formed from a ring cylinder and an annular piston arranged in this ring opening. The ring cylinder is arranged coaxially with the axis of the double gear and directly adjacent to an outer circumference of a guide ring of the axial bearing of the cylinder bearing on the machine frame. The annular piston is arranged to be movable parallel to the axis in the direction of and to the machine frame to the double gear.

In a further development it is provided that the annular piston is formed as insertable into a front side of the machine frame facing away open piston chamber insert with sealing inserts on the inner and the outer edge.

In a further development, it is provided that the annular piston is assigned a holding device arranged inside the piston chamber and not influencing the annular piston in its lifting movement, but retaining its circumferential position relative to the annular cylinder.

In a further development it is provided that the ring cylinder is arranged fixedly connected to the machine frame.

In a further development it is provided that a support ring is provided in mechanical connection with the annular cylinder and the directly adjacent region of the double gear as Kraftleitelement. The support ring is preferably coupled with the ring cylinder and engages behind a further arranged on the double gear retaining ring.

In a further development it is provided that each tie rod is assigned a respective pressure piece at a head end, which is opposite to a clamping screw at the other end of the tie rod. The pressure piece is used to apply force to a respectively associated with the tie rod spring assembly. The thrust pieces of all tie rods are arranged so that they touch the ring piston in its stroke position. In a further development it is provided that a spring plate between a clamping ring and a cylinder-fixed element of the double gear is arranged. The spring plate dissolves the clamping ring when canceling the clamping of the clamping ring against a cylinder-fixed part of the double gear and is designed as an annular spring element.

In a further development it is provided that on the annular piston attacking one or more return springs are arranged such that the annular piston is pushed in pressure relief of the annular cylinder under the force of the return springs in the piston chamber.

In a further development, it is provided that the annular lifting element is formed from a plurality of lifting cylinders and in each case one lifting piston arranged in these. The lifting cylinders are arranged concentrically with respect to the cylindrical pin annular.

From the embodiments of the various variants, there are further specific advantages which are mentioned below in the description of the exemplary embodiments.

In the following, some embodiments of the invention will be described in detail with reference to pictorial representations.

Show in detail

 FIG. 1 is a partial view of a sheet-fed rotary printing press;

 FIG. 2 shows a partial section of a device according to the prior art,

 FIG. 3 shows the device according to the invention,

 Figure 4 is another view of this device and

 Figure 5 shows a variant of this device and

 Figure 6 / 6A a further developed variant of this device.

FIG. 1 schematically shows a detail of a sheet-fed rotary printing machine. Two printing units 1A and 1B are supported by printing cylinders 2, 3 and Transport drums 4, 5 connected together. The drive of the printing units is carried out by gears which are coaxial with the printing cylinders 2, 3 and sheet transport drums 4, 5 are arranged. If a Bogenhinterkantenwendung to be performed between the two printing units 1 A, 1 B, the sheet transport drum 5 is designed as a so-called turning drum. For the turning operation, the relative position of the two printing units 1 A, 1 B to each other in the circumferential direction to the extent of the length of the sheets to be printed to change so that the end of the sheet can be transferred instead of the beginning of the sheet. At the transfer point between the impression cylinder 2 and the sheet transport drum 5 so takes place for this purpose, a relative displacement between two printing units 1 A, 1 B, which must be implemented in the drive wheel of the engine transmission, since of the sheet transport drum 5 no longer the beginning of the sheet but the bow end is taken over by the printing cylinder 2. At the journal of the printing cylinder 2, a double gear 6 is flanged to it. In this, a gear ring is clamped or released by means of a double-wheel clutch 7 operated by an unlocking device 7A on a main gear wheel.

The principle of such a dual-wheel clutch 7 according to the prior art is shown in Figure 2. The double gear 6 consists of a main gear 8 and a gear ring 9. The main gear 8 is connected to a cylinder pin 10. Between gear ring 9 and main gear 8, a clamping connection via a clamping ring 1 1 is produced. For this purpose, between the fixed to the main gear 8 clamping ring 1 1 and the gear ring 9 clamping elements 12 under the force of spring assemblies 13 from. If the spring assemblies 13 are unloaded from the outside, they clamp the clamping element 12 against the clamping ring 1 1 and connect the ring gear 9 frictionally connected to the main gear 8. The drive torque is transmitted from a gear 14 via the ring gear 9 to the main gear 8 and passed there on in the gear train downstream drive elements.

To set the operation with perfecting the sheet transport elements are adjusted relative to each other after loosening the clamping of the gear ring 9, wherein the clamping force of the clamping elements 12 between clamping ring 1 1 and Gear ring 9 is canceled. This is effected with the double-wheel clutch 7, which consists of an inner ring 15 and an outer ring 16. The rings 15, 16 form a hydraulic or pneumatic system with a pressure chamber 28 which is sealed with seals 25 and to which a fluid is supplied through a pressure medium connection 27. The unlocking system is loaded by springs 18 engaging in the ring 15 engaging retaining pin 17 axially displaceable against a fixed support 20 as a rest position. The outer ring 16 abuts with a stop surface 21 under load of compression springs 19 on the inner ring 15.

To unlock the clamp, the outer end face 22 of the inner ring 15 and a bent annular face 23 of the outer ring 16 are used as effective surfaces of the system. As a force attack for the end face 22 of the inner ring 15, the clamping elements 12 and serve as a force application for the annular surface 23 of the outer ring 16 is an unlocking element 24 which is connected to the gear ring 9. The dual-wheel clutch 7 is positioned on the carrier 20, which is rigidly connected to a part of the machine frame 26.

 In the unlocked state, the release system is free from fixed supports to small spring forces. Upon further supply of pressure medium, the clamping of the gear parts is canceled, without axial forces in the main gear 8 and its storage would be introduced. The main gear 8 can be rotated relative to the gear ring 9, while the gear ring 9 and coupled to him gear parts are held.

After Relativeinstellung the drive wheels, the unlocking system is depressurized and is by means of the springs 18, 19 back to its original position. The inventive device on a double gear 6 is formed as shown in FIG. The impression cylinder 2 is received with its cylindrical pin 10 via a radial bearing 32 guided in a bearing sleeve 33 and via a thrust bearing 34 guided in the machine side wall 26 on a guide ring 35. The guide ring 35 of the thrust bearing 34 is in this case attached from the outside to the machine side wall 26 and defines the entire bearing unit of the cylinder pin 10 immovably in this position. On the cylinder pin 10, a gear main body 39 is fixed by means of a mounting plate 36. On the gear main body 39, a first spur gear 8 is mounted rotationally. Furthermore, parallel to and coaxial with the first spur gear 8, a second spur gear 9 is placed on the gear main body 39 as a gear ring. To fix the annular spur gear 9 with respect to the first spur gear 8 on the gear main body 39, a clamping ring 37 is arranged on the side facing away from the machine side wall 26 side. The clamping ring 37 is pressed by a tie rod 29 or more distributed over the circumference of the double gear 6 tie rods 29 against the first spur gear 8. For this purpose, each of the tie rods 29 passes through the first spur gear 8, the gear main body 39 and the clamping ring 37 and is supported, each with its own head-mounted pressure piece 31 against a respective spring assembly 13 (such as disc springs). Each of the spring assemblies 13 is received in corresponding devices on the first spur gear 8. Each tie rod 29 is further supported against the force of the spring pact 13 by a clamping nut 30, which is supported on the clamping ring 39, adjustable.

 To improve the handling between the clamping ring 37 and the gear main body 39, an annular spring plate 38 is arranged, which is shaped plate-shaped in the manner of a washer and is therefore biased during clamping between the clamping ring 37 and the gear main body 39. Therefore, the spring plate 38 when reducing or canceling the bias of the tie rods 29, the clamping ring 37 lift by a bulge of the gear ring of the second spur gear 9, so that it is movable relative to the first spur gear 8.

To cancel the frictional connection, which is generated under the load by the spring assemblies 13 between the mutually braced elements clamping ring 37, second spur gear 9 and first spur gear 8, a fluidic lifting device is provided.

This device consists of an annular cylinder (ring cylinder 40) which is arranged coaxially with the cylinder pin 10 in the immediate vicinity of the thrust bearing 34 on the machine side wall 26. In the ring cylinder 40 is a Ring piston 41 under fluid supply or removal axially parallel to the cylinder pin 10 arranged displaceably. With fluid supply to the annular cylinder 40, the annular piston 41 is moved parallel to the axis of the cylinder pin 10 away from the machine side wall 26 and displaced against the plungers 31 of the tie rods 29. With appropriate pressure build-up, the annular piston 41 then presses together the spring assemblies 13 via the pressure pieces 31, so that the preload load that has been applied to the clamping ring 37 via the clamping nuts 30 is reduced or eliminated. Thereby, and by the return action of the spring plate 38, the second annular spur gear 9 is free and can be adjusted relative to the first spur gear 8.

Due to the large diameter of the double gear 6, a ring cylinder 40 with a suitably large diameter and a correspondingly large-sized annular piston 41 are also required here. A corresponding Dar position of the annular cylinder 40 in association with the cylinder pin 10 and its axial bearing 34 (dash-dot-line) is shown in Figure 4, wherein the annular piston 41 is shown hatched for better visibility.

Therefore, as an alternative, an arrangement of smaller lifting cylinders 42, which is evenly distributed around the cylinder pin 10, can be provided with a respective lifting piston 43, as shown in FIG.

The assignment of each of these lifting cylinders 42 with their reciprocating piston 43 is such that they are each a respective tie rod 29 and its pressure piece 31 are positioned opposite to the machine side wall 26. In this case, a device for exact positioning of the double gear 6 must be provided in its rotational position. For a perfectly uniform cancellation of the clamping within the double gear 6 is a precisely aligned action of each of the reciprocating piston 43 to the respective associated tie rod 29 and its respective pressure piece 31 is required.

Alternatively, the annular piston 43 arranged in accordance with FIG. 5 about the cylinder journal 10 and its bearing could also be actuated by an all piston 43 overlapping and the tie rods 29 and the pressure pieces 31 opposite arranged intermediate ring are synchronized in their effect to unlock the Zahnradklemmung. FIG. 6 shows a structurally simple embodiment of the device according to FIG. 3 in connection with a particularly preferred bearing arrangement with separate axial and radial guidance for the pressure cylinder 2 which can be driven by means of the double gear 6, in which the unlocking device 7 directly engages an axial bearing 34 on the cylindrical journal 10 assigned. The cylindrical pin 10 is received in the machine side wall 26 via the radial bearing 32 guided in the bearing sleeve 33 and the axial bearing 34 guided on the guide ring 35, whereby the guide ring 35 secures the axial bearing 34 on the outside of the machine side wall 26 and the cylinder pin 10 in this position in the axial direction fixed immovably.

On the cylinder pin 10, a gear base body 39 is fixed with a mounting plate 36. On gear main body 39, a first spur gear 8 is mounted rotationally. Parallel and coaxial with the first spur gear 8, the second spur gear 9 is mounted as a gear ring on the gear main body 39. The annular spur gear 9 is fixed to the first spur gear 8 by a clamping ring 37 is disposed on the gear base body 39 on the side facing away from the machine side wall 26, which is distributed by tie rods 29 on the circumference of the double gear 6 against the first spur gear 8 pressed. Each tie rod 29 passes through the first spur gear 8, the gear main body 39 and the clamping ring 37 and is supported with a stepped head 29A in each one of the support load distributing pressure piece 31 against a spring assembly 13, which is received in the first spur gear 8. Each tie rod 29 is biased on the head 29A opposite side of a clamping nut 30, which is supported on the clamping ring 39, adjustable against the force of the spring assembly 13 to the clamping ring 39 with the annular spur gear 9 and the annular spur gear 9 with the fixed To connect spur 8 frictionally. To improve the handling when releasing the frictional connections an annular spring plate 38 is arranged according to Figure 3 between the clamping ring 37 and the gear main body 39. In order to remove the frictional connection based on clamping by spring assemblies 13 between clamping ring 37, second spur gear 9 and first spur gear 8, an annular cylinder (ring cylinder 40) is arranged coaxially with the cylinder pin 10 in direct proximity to the thrust bearing 34 on the machine side wall 26. The ring cylinder 40 is fixedly connected to the machine side wall 26 and encloses the guide ring 35 of the thrust bearing 34 in the radial direction without spacing. In the annular cylinder 40, an annular piston 41 is arranged under fluid supply or - removal axially parallel to the cylinder pin 10 displaced. With fluid supply to the annular cylinder 40, the annular piston 41 is moved parallel to the axis 44 of the cylinder journal 10 away from the machine side wall 26 and displaced against the pressure pieces 31 of the tie rod 29.

The force build-up starting from the ring cylinder 40 or the annular piston 41 against the machine side wall 26 and against the double gear 6 takes place in the smallest possible distance for fixing the thrust bearing 34 of the cylinder bearing on the machine side wall 26 and the cylinder pin 10.

However, it should be noted that from the compressive force on ring cylinder 40 and ring piston 41 elasticity and play effects in the area of the double gear 6 and the cylinder bearing are issued, so that an unwanted displacement of the double gear 6 can be done.

Therefore, in addition to the compact introduction of force, a support of the introduction of force on the double gear 6 can be provided. For this purpose, a support ring 45 is attached to the ring cylinder 40, which preferably engages behind the ring cylinder 40 at its base and is bent on the side of the ring piston 41. Here, the support ring 45 protrudes into a recess on the spur gear 8, which is covered by a retaining ring 46. Thus, an axial displacement of the double gear 6 relative to the ring cylinder 40 or the machine side wall 26 is possible only in a very limited and adjustable to minimum values measure. Under appropriate pressure build-up by means of fluid supply into the annular cylinder 40 then presses the annular piston 41 via the plungers 31, the spring assemblies 13 together, wherein the support ring 45 is supported on the retaining ring 46 on the fixedly mounted on the cylinder pin 10 spur gear 8.

As a result, the biasing load generated by the spring assemblies 13, which acts on the clamping ring 37 via the clamping nuts 30, reduced or eliminated. In this case, by the action of the support ring 40, which is supported on the retaining ring 41 on the spur gear 8, no unintentional displacement of bearing elements or other parts of the double gear 6 take place. The introduction of force to the various pressure pieces 31 of the tie rod 29 is distributed uniformly over the circumference of the double gear 6, since the fluid pressure builds up uniformly over the circumference of the annular cylinder 40. By relieving the bias of the tie rods 29 and the restoring action of the spring plate 38, the second annular spur gear 9 is released with high positional accuracy in its clamping position and can then adjusted in its recording on the gear base 39 and relative to the first spur gear 8 with equally high accuracy become.

Particularly advantageous in the embodiment according to the invention is that the annular cylinder 40 is fixedly connected to the frame side wall 26. In contrast to the prior art, this prevents unintentional contact between the double gearwheel 6 and the unlocking mechanism during running operation of the machine. Furthermore, a safe and well-supported force is given by the integrative proximity between the thrust bearing 34 of the cylinder bearing and the ring cylinder 40 of the unlocking mechanism.

In the enlarged view of the extract of Figure 6A of the ring cylinder 40 in conjunction with the annular piston 41 is very simple and easy to install and also designed as an extremely compact arrangement. The annular piston 41 is an insert element with an overlapping edge as a stop and a sealing system 41 A in the axial direction to the cylinder pin 10 in an annular piston chamber 40A within the annular cylinder 40 inserted inserted. This ensures a very simple operation and easy maintenance of the machine. In operation, the annular piston 41 can be loaded at the abovementioned overlapping edge with a few return springs 46 in the direction of the machine frame 26, so that it safely returns to the basic position in the ring cylinder 40 when pressure is released. In Figure 6A, the basic position of the annular piston 41 is shown with minimum distance to the pressure piece 31 on the tie rod 29 under load by the return springs 46. The return springs 46 may be arranged in any free access position to the annular piston 41 and must be secured to the machine frame 26 connected.

The annular piston 41 can be guided to secure against unintentional displacement in the circumferential direction with a loosely engaging in a recess 41 C in the piston head locking pin 41 B (see Figure 6A).

In this case, the annular piston 41 is not hindered by the securing pin 41 B with respect to the function to be performed for unlocking in the form of a lifting movement. In the case of rotational movements on the double gearwheel 6, which are to be carried out for adjusting the sheet-fed rotary printing press to the perfecting and backward printing mode, movement of the annular piston 41 relative to the ring cylinder 40 in the circumferential direction of the double gearwheel 6 is prevented by the securing pin 41B. This can not be done unintentionally rotation of the double gear 6 during the function change.

Finally, it is advantageous that for unlocking not the tie rods 29 are charged themselves, but that the force for unlocking via a this at the remote head 29A associated pressure piece 31 is introduced to a respective associated spring assembly 13. The tie rods 29 are therefore not overstressed and can not be moved under a direct action of the annular piston 41, which could lead to unintentional displacements. LIST OF REFERENCE NUMBERS

1 printing unit (1A / 1 B)

 2 pressure cylinders

 3 pressure cylinders

 4 sheet transport tunnel

 5 sheet transport tunnel

 6 double gear

 7 clutch

 8 main gear

 9 gear ring

 10 cylinder pin

 1 1 clamping ring

 12 clamping element

 13 spring pack

 14 gear

 15 inner ring

 16 outer ring

 17 retaining bolts

 18 spring

 19 compression spring

 20 carriers

 21 stop surface

 22 face

 23 ring surface

 24 unlocking element

 25 seal

 26 Machine cranks / machine side wall

27 pressure medium connection

 28 pressure chamber

 29 tie rods

30 clamping nut 31 pressure piece

 32 radial bearings

 33 bearing sleeve

 34 thrust bearings

 35 guide ring

 36 mounting plate

 37 clamping ring

 38 spring plate

 39 gear base body

 40 ring cylinders

 41 ring piston

 42 individual cylinders / lifting cylinder

 43 single piston / reciprocating piston

 44 axis of the printing cylinder

 45 support ring

 46 retaining ring

 47 return spring

7A unlocking drive

29A Head of tie rod

 40A piston chamber in the ring cylinder

 41A seals for ring pistons

 41 B Anti-rotation lock for ring piston

 41 C recess in the piston head of the annular piston

Claims

claims Device for unlocking a friction-locked connection of a first spur gear (8) arranged on a cylinder journal (10) of a printing press cylinder (2) and a second spur gear (6) associated with this first spur gear (8) designed as a gear ring a sheet-fed rotary printing press convertible from perfecting printing, wherein the second spur gear (9) is clamped to the first spur gear (8) via tension rods (29) loaded by spring force and the device for unlocking is symmetrical to the axis (44) of the double gear wheel (6) ), the device comprising at least one annular fluid operated lift assembly (40, 41) having a connection to a machine frame (26) and slidably mounted at least partially in the direction of an axis (44) of the double gear (6; 8, 9) is, wherein the lifting arrangement (40, 41) in an unlocked position, a part of the double gear (6; 8, 9) m it rotatably connects to the machine frame (26), characterized in that the cylinder journal (10) is accommodated in a cylinder bearing in which an axial bearing (34) arranged separately from a radial bearing (32) is provided, wherein an annular fluid-operated lifting arrangement (40, 41) lies directly adjacent and concentric with the axial bearing (34) Machine frame (26) of the sheet-fed rotary printing machine is arranged, wherein a pressure element of the lifting arrangement (40, 41) is associated with one of the spring force on a respective tie rod (29) transmitting coaxial with the tie rod (29) arranged pressure piece (31) such that on the / the tie rods (29) acting spring forces be reduced or removed under load by the pressure element. Device according to claim 1, characterized in that in that the annular lifting arrangement is formed by an annular cylinder (40) and an annular piston (41) arranged in an annular opening of the annular cylinder (40), wherein the ring cylinder (40) coaxial with the axis (44) of the double gear (6) and directly adjacent parallel to an outer periphery of a guide ring (35) of the axial bearing (34) of the cylindrical bearing on the machine frame (26) is arranged and wherein the annular piston (41) parallel to the axis (44) in the direction of and to the machine frame (26) to the double gear (6) is arranged to be movable. Device according to Claim 1 or 2, characterized in that the annular piston (41) is designed as an insert insertable with seals (41 B) on the inner and outer flanks into an open annular piston chamber (40A) of the annular cylinder (40) facing away from the machine frame (26). Device according to one or more of claims 1 to 3, in that the annular piston (41) is assigned a retaining device (41 A) which is connected within the piston chamber (40A) to the annular cylinder (40) and which does not influence the annular piston (41) in its circumferential movement relative to the annular cylinder (40) , Device according to one or more of claims 1 to 4, characterized, in that the ring cylinder (40) is fixedly connected to the machine frame (26). Device according to one or more of claims 1 to 5, characterized, that in mechanical connection with the ring cylinder (40) and the directly adjacent region of the double gear (6) as Kraftleitelement a support ring (45) is provided, wherein the support ring (45) with the ring cylinder (40) is preferably coupled behind this engaging and wherein the support ring (40) further comprises a on the Double gear (6) arranged retaining ring (46) is arranged behind engages. 7. Device according to one or more of claims 1 to 6,  characterized,  that each tie rod (29) per a pressure piece (31) at a head end, which is arranged opposite a clamping screw (30) at the other end of the tie rod (29), for introducing force to a respectively the tie rod (29) associated spring assembly (13) is. 8. Device according to one or more of claims 1 to 7,  characterized,  that the thrust pieces (31) of all tie rods (29) are associated with the annular piston (41) in its stroke position in the function of unlocking the clamping of the spur gears (8, 9) by the Doppelradkupplung (7) touching and that the pressure pieces (31) all Tie rod (29) of the annular piston (41) in its rest position in the function for releasing the clamping of the spur gears (8, 9) by the Doppelradkupplung (7) are not associated touching. 9. Device according to one or more of claims 1 to 8,  characterized,  that a spring plate (38) between a clamping ring (37) and a cylinder-fixed element of the double gear (6) as the clamping ring (37) upon release of the clamping of the clamping ring (37) against a cylinder-fixed part of the double gear (6) releasing, arranged annular spring element is. 10. Device according to one or more of claims 1 to 9,  characterized, that on the annular piston (41) attacking one or more return springs are arranged such that the annular piston (41) is pushed in pressure relief of the annular cylinder (40) under the force of the return springs in the piston chamber (40A) against a stop. Device according to one or more of claims 1 to 10, characterized, the annular lifting element is formed from a plurality of lifting cylinders (42) and in each case one lifting piston (43) arranged in them, in that the lifting cylinders (42) are concentric with the cylinder journal (10) and the annular cylinder Axis (44) of the double gear (6) are arranged, wherein each lifting cylinder (42) fixed to the frame frame (26) and the respective annular piston (43) parallel to the axis (44) in the direction of the machine frame (26) to the double gear ( 6) is arranged movable.