EP2363216A1 - Forming device - Google Patents

Abstract

The shaping device (1) has a machine frame (2), a driving device (6), a work piece round table (3) for retaining of hollow bodies (56) and a tool carrier (4) for retaining processing tools (58). A guiding device (40) is arranged at an external surface (36) of support tubes (33). The guiding device is formed for a linear-mobile bearing of the tool carrier or the work piece round table at the support tubes.

Description

The invention relates to a forming device for cup-shaped hollow body with a machine frame, a drive device, a workpiece turntable for receiving hollow bodies and a tool carrier for holding machining tools, wherein the workpiece rotary table and tool carrier are opposite and rotatable about an axis of rotation to each other and along the axis of rotation are mutually linearly adjustable and the drive device is designed for providing a rotary step movement and a cyclical linear movement between the workpiece rotary table and the tool carrier, in order to enable a deformation of the hollow body by means of the processing tools in several successive processing steps, as well as with a support frame fixedly assigned to the machine frame, the central axis of which extends along the axis of rotation and carries the tool carrier and / or the workpiece rotary table.

From the EP 0 275 369 A2 a forming machine is known, with the cup-shaped hollow body made of metal, in particular aluminum, from a substantially cylindrical sleeve-shaped initial state partially reshaped, in particular locally retracted, to be able to seal, for example, in the region of the opening a cap or a spray valve. The known forming machine has a machine frame, on which a support tube is formed. On an outer surface of the support tube, a workpiece rotary table is rotatably mounted. In a recess bounded by the support tube, a linearly displaceable guide tube is accommodated, at the end region of which the tool carrier is attached. In the machine frame, a drive device is received, which is designed to generate an intermittent rotary movement of the workpiece rotary table and to produce an oscillating linear movement of the guide tube and the associated tool carrier. As a result of the linear movement, the tools provided on the tool carrier, in particular forming tools, can be brought into engagement with the hollow bodies held on the workpiece rotary table in order to process them locally, in particular to plastically deform them. Due to the intermittent rotational movement of the workpiece rotary table, the hollow bodies can be brought into serial contact with the tools mounted on the tool carrier table, in order to achieve a stepwise deformation of the hollow bodies from an initial geometry to a target geometry.

The object of the invention is to provide a forming device, which allows for a simplified construction improved accuracy in the processing of the hollow body.

This object is achieved by a forming device of the type mentioned with the features of claim 1. It is provided that on a outer surface of the support tube, a guide device is arranged, which is designed for a linearly movable mounting of the tool carrier and / or the workpiece rotary table on the support tube. This is compared with the known linear bearing of the tool carrier table, which is provided on the inner surface of the support tube, a larger storage area available. This ensures a more reliable support of the forces to be transmitted during operation of the forming device from the tool carrier and / or from the workpiece rotary table to the carrier tube. In addition, the linear guide for the tool carrier and / or the workpiece rotary table can be designed such that the same storage conditions are always present over the entire length of the linear movement of the tool carrier and / or workpiece rotary table relative to the support tube. As a result, the machining tolerances for the hollow body machining can be kept within a narrow range. During the machining of the hollow body, the workpiece rotary table and / or the tool carrier move along the outside of the support tube mounted, at least one linear guide, relative to the support tube.

Advantageous developments of the invention are the subject of dependent claims.

It is useful if the support tube is fixedly mounted on the machine frame. As a result, a highly resilient and independent of the operating state or the operating position of the forming force transmission between the support tube and machine frame is guaranteed, whereby an advantageous support of the tool carrier and / or workpiece rotary table is ensured.

It is advantageous if the machine frame comprises a spaced pivoting from the support tube pivot bearing for the workpiece rotary table or tool carrier. Due to the spacing and the resulting at least partially mechanical decoupling of the pivot bearing from the linear bearing formed on the support tube is achieved that of Support tube on the machine frame to be transmitted forces and moments, in particular bending moments, and associated elastic deformation of the support tube not or at most to a small extent to undesirable deflections and / or lead to encumbrance for the pivot bearing. As a result, an advantageous mechanical decoupling of the rotary bearing is ensured by the linear guide, whereby the machining accuracy for the hollow body can be improved. Preferably, the rotary bearing is arranged in the radial direction outwardly spaced from the support tube. Particularly preferably, a longitudinal axis of the support tube and the rotational axis determined by the pivot bearing are arranged concentrically to one another.

In one embodiment of the invention it is provided that the pivot bearing and the support tube are arranged together on a support plate of the machine frame. The support plate is used to transfer forces between the support tube and the linearly movably mounted thereon tool carrier or workpiece turntable and rotatably received by means of the rotary bearing on the support plate workpiece rotary table or tool carrier. Preferably, the support plate is formed such that it is not or only slightly deformed elastically in the machining forces occurring during operation of the forming. As a result, the desired, at least almost complete mechanical decoupling between the support tube on the one hand and the pivot bearing on the other hand guaranteed. In a preferred embodiment of the invention, the carrying tube, in particular with a circular cross-section, and the rotary bearing are spaced apart in the radial direction relative to the axis of rotation, in particular concentrically with one another, attached to the support plate.

In this case, the pivot bearing surrounds the support tube, whereby it is possible to choose the diameter of the pivot bearing considerably larger than the diameter of the support tube. Preferably, the diameter of the pivot bearing is at least approximately as large as the diameter of the, preferably annular, executed tool carrier or workpiece rotary table. In this way, an advantageous support of the forces acting parallel to the axis of rotation on the tool carrier or workpiece rotary table forces can be ensured by support plate and arranged between the tool carrier or workpiece rotary table and support plate pivot bearing.

Preferably, it is provided that the support plate together with a support frame forms a first machine frame section and that the drive device is received on support cheeks, which form a second machine frame part, so that at least a substantial decoupling between the forces provided by the drive means and the workpiece rotary table and the tool carrier achieved becomes. The two machine frame parts in each case derive the forces acting on them preferably on a base plate. The base plate may be formed as a further part of the machine frame and / or as part of a foundation structure for the forming device and closes the power flow between the two machine frame parts. This base plate can be made particularly stable, so that it is not or only slightly deformed by the forces occurring during operation of the forming device. Preferably, the base plate is formed such that it at least largely, in particular practically complete, mechanical decoupling of the two machine frame parts from each other allows. This ensures that, for example, from the drive device outgoing forces and vibrations that are introduced to the second machine frame part, at least as far as possible can be kept away from the first machine frame part and thus no disturbing influence on the tool carrier and the workpiece rotary table, the relatively movable to each other on the first machine frame section are able to exercise.

In an advantageous development of the invention, it is provided that between the first machine frame section and the second machine frame section an articulated, preferably flexible, in particular as a solid-body joint, formed coupling region is provided. On the one hand, the coupling region serves to close the flow of force between the first and the second machine frame part, on the other hand, the coupling region is provided for as far as possible mechanical decoupling of the two machine frame parts. The coupling region is preferably designed as a flexible joint element, in particular as a solid-body joint. This ensures that the two machine frame parts are connected to each other without clearance. Preferably, the solid-body joint is integrated in the first machine frame part, for example in the region of a connection of the support plate to the bottom plate.

It is expedient if a joint axis of the articulated coupling region is aligned transversely to the axis of rotation. Depending on the design of the coupling region, the joint axis may be an actual physical axis or, in particular, a solid-state joint, about a geometric axis act. Due to the alignment of the joint axis according to the invention, the coupling region serves to decouple the linear vibrations generated by the drive device and, in particular, acting along the axis of rotation from the support plate. Preferably, the support plate for decoupling the linear vibrations of the drive means performs a tilting movement relative to the drive means about the hinge axis. This prevents that emanating from the drive device linear vibrations penetrate to the tool carrier and / or workpiece rotary table and influence the quality of processing there.

In a development of the invention, it is provided that a preferably preloaded, in particular backlash-free, rolling body bearing arrangement is formed between the support tube and the tool carrier or workpiece rotary table. A Wälzkörperlageranordnung allows high relative speeds for the oscillating linear movement between the tool carrier or workpiece rotary table and the support tube. Since moving in this linear movement of the tool carrier or workpiece rotary table always along the same portion of the support tube, the use of a Wälzkörperlageranordnung is advantageous because this produces less heat generation due to the rolling friction of the rolling elements as a corresponding slide bearing. Preferably, the Wälzkörperlageranordnung is biased designed to ensure a low-backlash, preferably backlash-free storage of the tool carrier or workpiece rotary table on the support tube. In particular, the bias of the rolling element bearing assembly is designed such that a rotational movement of the tool carrier or workpiece rotary table about the axis of rotation and to a tilt axis aligned transversely to the axis of rotation is at least partially, preferably completely, avoided.

It is advantageous if on an inner surface of the support tube, preferably designed as a slide bearing, bearing means for a coupling slide of the drive device is formed, which is provided for a force-transmitting connection between a connecting rod of the drive means and the tool carrier or the workpiece turntable. The coupling carriage is provided for transferring the oscillation movement provided by the drive device, preferably in the manner of a crank movement, as a superposition of a linear movement with a pivoting movement into a pure linear movement, which can then be forwarded to the tool carrier or workpiece rotary table. For this purpose, the coupling carriage is connected to the crank drive of the drive device mounted connecting rod and mounted linearly movable in the support tube. Since the mounting of the tool carrier or workpiece rotary table according to the invention is provided on the outer surface of the support tube, the inner surface of the support tube can be used for the storage of the coupling carriage. As a result, in addition to an advantageous guidance of the coupling slide and a compact design for the forming device is achieved. Particularly preferably, the coupling carriage rests against the inner surface of the support tube in the same way over the entire length of the linear oscillation movement.

In a further embodiment of the invention is arranged between the coupling carriage and the tool carrier or workpiece rotary table, preferably a ring-shaped, elastic coupling means for power transmission between coupling carriage and tool carrier or workpiece rotary table and is designed to decouple tilting movements of the coupling slide transversely to the axis of rotation. The elastic coupling means is first subjected to a compressive force during the machining process for the hollow body for the implementation of the linear oscillation movement in order to move the tool carrier or workpiece rotary table on the oppositely disposed workpiece rotary table or tool carrier and bring the processing tools into engagement with the hollow bodies. In a subsequent phase of the linear oscillation movement tensile forces are introduced to the elastic coupling means to increase the distance between the tool carrier and workpiece rotary table again and thus to remove the processing tools from the hollow bodies. Preferably, the elastic coupling means is sleeve-shaped, in particular made of a thin-walled metallic material. Particularly preferably, the elastic coupling means is aligned concentrically to the axis of rotation of the tool carrier or workpiece rotary table.

In a further development of the invention, it is provided that a guide length for the tool carrier or the workpiece rotary table along the support tube and / or for the coupling carriage along the support tube at least 1.5 times, preferably at least 2 times, in particular at least 2.5 -fold, the maximum stroke of the tool carrier or the workpiece turntable is. The guide length is the maximum distance of the respective outer rolling elements of the linear guides along the axis of rotation, which are assigned to the tool carrier or workpiece rotary table. By supporting the tool carrier or workpiece rotary table on such a guide length ist.auch also ensures maximum stroke of the drive device ensures that the tool carrier or the workpiece turntable is always performed reliably on the support tube.

It is expedient if the support tube and the tool carrier or workpiece rotary table are mounted cantilevered on the support plate. As a result, an advantageous accessibility of the tool carrier or workpiece rotary table is ensured, for example, for a rapid interchangeability of the tool carrier or workpiece rotary table.

Figur 1

eine ebene, schematische Schnittdarstellung durch eine Umformeinrichtung,

Figur 2

eine schematische Darstellung der Antriebseinrichtung mit den ersten und zweiten Antriebsmitteln.

An advantageous embodiment of the invention is shown in the drawing. Hereby shows:

FIG. 1

a planar, schematic sectional view through a forming device,

FIG. 2

a schematic representation of the drive device with the first and second drive means.

One in the FIG. 1 illustrated forming device 1, which is used in particular for forming cup-shaped hollow bodies, comprises a machine frame 2, on which a workpiece rotary table 3 and a tool carrier 4 are arranged. In the illustrated embodiment of the forming device 1 of the workpiece rotary table 3 is rotatably mounted on the machine frame 2, while the tool carrier 4 is exemplarily linearly movably received on the machine frame 2. The workpiece rotary table 3 is thus mounted so as to be rotatable relative to the machine frame 2 and the tool carrier 4 about an axis of rotation 5. The tool carrier 4 can be moved linearly along the axis of rotation 5 relative to the machine frame 2 and the workpiece rotary table 3.

The forming device 1 further comprises a drive device 6, which is designed to provide an intermittent rotational movement or rotational step movement and to provide a cyclically oscillating linear movement. In the present case, the drive device 6 is designed to provide the rotary step movement to the workpiece rotary table 3 and to provide the cyclically oscillating linear movement to the tool carrier 4.

Among other things, the drive mechanism 6 comprises a double eccentric arrangement 8. The double eccentric arrangement 8, which also includes an eccentric shaft 9 and an eccentric cam 10, serves as an eccentric crankshaft that can be adjusted with respect to the crank stroke to provide a circular circulation movement for a closer one designated connecting rod eye of a connecting rod. 7

The forces necessary for driving the connecting rod 7 are provided, for example, by a drive motor 11 designed as an electric motor, which is coupled to a flywheel 13 via a belt drive 12, which is designed as an exemplary V-ribbed belt. The flywheel 13 can be brought into force-transmitting connection with a drive pinion 15 via a flywheel clutch 14 that can be coupled during operation of the forming device 1. The drive pinion 15 is in engagement with a main gear 16, which is received rotatably mounted on two support webs 17, of which due to the sectional view of FIG. 1 only one is visible. On the main gear 16, two, preferably each integrally formed, exemplarily cylindrical bearing pin 18 are mounted in a mirror image arrangement, concentric with the main gear 16th are arranged and engage in a manner not shown in one of the support cheek 17 respectively associated storage and serve the pivot bearing of the main gear 16. In addition, the inner eccentric 9 is fixedly mounted on the main gear 16, while the outer eccentric 10 is adjustably mounted on the main gear 16 to adjust the crank stroke of the double eccentric 8 for the connecting rod 7 can.

For adjusting the maximum stroke, the outer eccentric 10 can be decoupled from the inner eccentric 9 by means of a coupling, not shown, and rotated about a normal to the plane of representation pivot axis, preferably continuously, relative to the inner eccentric 8 for stroke adjustment , Subsequently, the clutch is closed again, so that the two eccentrics 9 and 10 are again coupled to transmit power.

On the main gear 16 is also a driven gear 19 in permanent engagement, which can be brought via a switchable during operation of the forming device 1 step transmission clutch 21 with a step transmission 20 in force-transmitting connection. The indexing gear 20 converts the continuous rotational movement of the output gear 19 into a discontinuous, intermittent rotational step movement, which is transmitted to the workpiece rotary table 3 via a stepping shaft 22 and a stepping gear 23. By way of example, an internal toothing 24 is formed on the workpiece turning table 3, into which the stepping switching pinion 23 engages, in order to transmit the rotary stepping movement of the stepping gear 20 to the workpiece turning table 3 then completes the rotary step movement about the axis of rotation 5. Alternatively, instead of the stepping gear 20, a servo drive can be used, which allows an electrically controlled rotary step movement.

By way of example, the workpiece rotary table 3 is rotatably mounted on a support plate 26 by means of a rotary bearing 25. The support plate 26 is part of a first machine frame part, which also comprises a support frame 31. In particular, the support frame 31 has the task of deriving the torques, which act on the support plate 26 by the weight forces of the components mounted on the support plate 26, described in more detail below, into a base plate 32.

The rotary bearing 25 comprises, for example, a support ring 26 mounted on the preferably annular bearing ring 28 having a bearing surface on a circumferential outer surface for a plurality of rolling elements 29 shown schematically. The rolling elements 29 are arranged between the bearing ring 28 and a bearing ring 28 opposite, formed on the workpiece rotary table 3 by way of example as a circumferential collar 63 bearing surface 30 and are held by a cage, not shown in position. Together with the bearing ring 28 and the peripheral collar 63, they form a radial bearing which ensures a low-friction rotary movement of the workpiece rotary table 3 with high precision, in particular with respect to the axis of rotation 5 and the tool carrier 4. A support of machining forces acting in the direction of the axis of rotation 5 on the workpiece rotary table 3, for example, by an annular sliding bearing ring 62 which rests flat against the surface of the workpiece rotary table 3. Preferably, the slide bearing ring 62 and the opposite arranged surface of the workpiece rotary table 3 supplied by a lubrication circuit not shown with an intermittent or continuous lubricant supply with lubricant.

At a drive device 6 opposite surface of the support plate 26 and spaced from the pivot bearing 25, a support tube 33 is attached, which serves as an example for supporting and linear mounting of the tool carrier 4. The support tube 33 has an exemplary annular cross-section in a cross-sectional plane oriented normal to the axis of rotation 5, not shown. A cylindrical inner surface 35 of the support tube 33 serves as a sliding bearing surface for a coupling slide 34 which is coupled to the connecting rod 7 and serves to implement the combined rotational and linear movement of the connecting rod 7 in a linear movement.

The coupling carriage 35 includes by way of example a tubular body 37, on which a bearing pin 38 is mounted for the pivotable mounting of the connecting rod 7. On the base body 37 are radially outwardly a plurality of, preferably annular, sliders 39, for example of plain bearing bronze, arranged, which are designed for a sliding movement on the inner surface 35 of the exemplary, made of metal, support tube 33.

On an outer surface 36 of the support tube 33 a plurality of parallel to the rotation axis 5 extending bearing rails 40 are mounted, which serve as linear guide elements for the tool carrier 4. Preferably, the bearing rails 40 are arranged in the same angular pitch about the axis of rotation 5, for example in a 120-degree division or a 90-degree division.

For the linear guide of the tool carrier 40 also on a radially inner inner surface 41 of the tool carrier 4 corresponding to the bearing rails 40 also referred to as ball rolling shoes linear guides 42 are mounted, which engage around the bearing rails 40 each U-shaped. The linear guides 42 may be formed, for example, as recirculating ball bearings, in which a plurality of cylindrical or spherical rolling elements are received in a guideway and allow a linear relative movement relative to the respective bearing rail 40. Preferably, the linear guides 42 are braced against each other by not shown clamping means in the radial direction and / or in the circumferential direction of the support tube 33, whereby a backlash, in particular backlash-free, linear bearing of the tool carrier 4 relative to the support tube 33 is achieved. Due to the linear guides 42 of the tool carrier 4 is rotatably received on the support tube 33.

On the base body 37 of the coupling slide 34, a closing plate 43 is attached to the connecting rod 7 facing away from the end face, which carries a threaded spindle 44. The threaded spindle 44 extends, for example, in parallel, in particular concentrically, to the axis of rotation 5. Two spindle nuts 45, 46 spaced apart from each other along the axis of rotation 5 engage in the external thread of the threaded spindle 44 (not shown). The two spindle nuts 45, 46 are rotatably and linearly connected to each other. The second spindle nut 46 is assigned a, preferably hydraulically controllable, linear adjusting device 48 and a servomotor 49.

The object of the servomotor 49, which is preferably designed as a torque motor and coupled to the second spindle nut 46, rotatably mounted rotor 50 and a stator 51 includes, which is rotatably received in a driver 52, therein, the two spindle nuts 45, 46 by To move rotation along the threaded spindle 44 and thereby allow an adjustment of a starting position of the tool carrier 4 along the threaded spindle 44.

The task of the linear adjusting device 48, which can exert a force in the direction of the axis of rotation 5 on the second spindle nut 46, is to brace the second spindle nut 46 relative to the first spindle nut 45 and thus a backlash-free power transmission between the threaded spindle 44 and the driver 52 permit, in which the spindle nuts 45 and 46 are received stationary and rotationally movable.

The driver 52 is exemplarily designed as a substantially rotationally symmetrical body and has a circumferential flange 53, to which a tubular coupling means 54 is attached, which is designed for a force-transmitting connection with the tool carrier 4. The flange 53 and the coupling means 54 are dimensioned such that they are slightly elastically deformed due to the transmitted from the tool carrier 4 on the workpiece rotary table 3 forces while possibly occurring tilting of the coupling carriage 34 and the driver 47 take about tilt axes transversely to the axis of rotation 5 at least partially so that they are not or at best proportionally transferred to the tool carrier 4. In combination with the at least substantially play-free mounting of the tool carrier 4 on the support tube 33 is thereby a particularly achieved high precision for the processing of recorded on the workpiece rotary table hollow body 55.

Hereinafter, some aspects of the function of the forming device 1 will be outlined. It is assumed that on the workpiece rotary table 3 a plurality of the same angular distribution to the axis of rotation 5 arranged, also referred to as a chuck workpiece holder 55 are mounted, in each of which cup-shaped hollow body 56 are added. At the surface of the tool carrier 4 opposite the workpiece rotary table 3 corresponding tool holders 57 corresponding to the workpiece holders 55 are arranged, which are equipped with machining tools 58, for example with forming tools.

For commissioning in the FIG. 1 1, the clutches, in particular the flywheel clutch 14 and the stepping gear clutch 21, are first brought into an engaged, force-transmitting position. In addition, can be adjusted by the relative movement and locking of the outer eccentric 10 relative to the inner eccentric 9 before commissioning the eccentric or crank for the connecting rod 7 and the coupled therewith coupling carriage 34. In addition, the starting position of the tool carrier 4 along the axis of rotation 5 by driving the servo motor 49 and the coupled thereto spindle nuts 45, 46 can be adjusted. Subsequently, the spindle nuts 45, 46 are locked by means of the linear adjusting device 48 on the threaded spindle 44.

To start up the forming device 1, the drive motor 11 is acted upon by electrical voltage and generates a rotational movement, via the belt drive 12 is passed to the flywheel 13. The power transmission with the flywheel 13 connected drive pinion 15 sets the main gear 16 in motion. As a result, on the one hand, a crank movement is introduced onto the connecting rod 7 by means of the double eccentric arrangement 8. In addition, the stepping gear 20 is set in motion via the driven gear 19. When the clutches 14, 21 are closed, there is a kinematic forced coupling between the movement of the connecting rod 7 and thus of the tool carrier 4 and the movement of the stepping gear 20 and thus of the workpiece rotary table 3.

By the crank movement of the Doppelexzenteranordnung 8 and the coupling via the connecting rod 7 of the coupling slide 34 is placed in an oscillating linear motion, which is transmitted via the threaded spindle 44, the spindle nuts 45, 46, the driver 47 and the coupling means 54 on the tool carrier 4, the this linear movement in the same manner as the coupling carriage 34 completes.

The workpiece rotary table 3 is offset by the stepping gear 20 and the associated stepping shaft 22 and the stepping gear 23 and the internal teeth 24 in a rotary step movement about the rotation axis 5. In this case, the rotary step movement of the workpiece rotary table 3 and the oscillating linear movement of the tool carrier 4 are coordinated such that the workpiece rotary table 3 rests in the time interval in which the attached to the tool carrier 4 processing tools 58 are in engagement with the hollow bodies 56. The workpiece rotary table 3 completes the rotary step movement when the processing tools 58 are not in engagement with the hollow bodies 56. As a result, the processing tools 58 in the course of the combined linear and Rotation step movement of the tool carrier 4 and workpiece rotary table 3 are sequentially brought into engagement with the hollow bodies 56 in order to achieve a stepwise deformation of the hollow body 56.

Due to the crank movement of the double eccentric arrangement 8 and the connecting rod 7 coupled thereto, substantial mass forces and vibrations occur during operation of the forming device 1. In order to at least largely keep these disturbing influences away from the hollow bodies 56 and the machining tools 58, the support webs 17, which essentially form the second machine frame section 59, have a dimensionally stable design and are firmly anchored to the base plate 32, which in turn has a large mass and thus the interference influences can not be moved or only to a small extent in motion. The support plate 26, which carries both the support tube 33 for guiding the tool carrier 4 and the bearing ring 28 for pivotal mounting of the workpiece rotary table 3, is also dimensionally stable and is not or only slightly deformed by the forces occurring during operation of the forming device 1.

On the one hand to achieve the greatest possible decoupling of the support plate 26 of the drive means 6 and on the other hand a reliable power flow between the support plate 26 and drive means 6, the support plate 26 is connected via an articulated coupling region 60 to the base plate 32. In addition, since the support frame 31 has a significantly higher elasticity than the support plate 26, a machining unit 61 formed from the support plate 26, workpiece turntable 3, tool carrier 4 and support tube 33 as rigid and thus in terms of the machining process precise assembly be considered. The processing unit 61 is elastically connected to the base plate 32 via the coupling region 60 and the support frame 31. The movement provided by the connecting rod 7 is introduced into the processing unit 61 by means of the coupling carriage 34, which is received slidingly in the support tube 33. The coupling means 54 arranged between the coupling slide 34 and the tool carrier 4 decouples any tilting movements of the coupling slide 34, so that the tool carrier 4 is subjected to a pure linear movement. Since the tool carrier 4 is also accommodated by means of the prestressed, in particular play-free linear guides 42 on the bearing rails 40, an accurate positioning of the processing tools 58 with respect to the hollow bodies 56 is ensured.

For the implementation of the relative rotation of the inner eccentric 9 relative to the outer eccentric 10 and thereby to be effected, in particular stepless adjustment of the power stroke, a locking device 70 is provided which has a pivotally mounted on the machine frame 2 locking lever 71, a trained example as a hydraulically controllable cylinder Adjusting means 72 and a protruding on the outer eccentric 10 in the axial direction locking bolt 73 includes.

With the help of the locking device 70, the outer eccentric 10 can be determined by the adjusting means 72 is driven by the control device, not shown, and the locking lever 71 pivoted so that it can come into engagement with the locking bolt 73. Subsequently, the drive motor 11 is controlled by the control device such that the main gear 16 is a slow, in the representation of FIG. 1 preferably in Clockwise taking place rotational movement, performs. During this rotational movement, both the inner eccentric 9 and the outer eccentric 10 are initially moved, until the locking pin 73 comes into engagement with the fork-shaped locking lever 71. From this point, a further rotation of the outer eccentric 10 is prevented by the pivoted-locking lever 71, while the inner eccentric 9 can rotate relative to the outer eccentric 10 upon further rotation of the main gear 16.

By this relative rotation between inner eccentric 9 and outer eccentric 10, the desired adjustment of the working stroke is effected. Due to the reduction of the rotational movement between the drive motor 11 and the main gear 16, a very fine angular resolution for the relative movement between the inner eccentric 9 and the outer eccentric 10 can be achieved, so that a virtually stepless adjustment of the working stroke is made possible.

Once the desired stroke between inner eccentric 9 and outer eccentric 10 is set, can be brought out of engagement with the locking lever 71 by a reversing movement of the drive motor 16 of the locking pin 74. Subsequently, the locking lever 71 is brought by means of the adjusting means 72 in a neutral position, not shown, and the forming device 1 can now be put into operation with the newly set stroke.

When setting the working stroke, the phase position between cyclic linear movement and rotary step movement may change. This is due to, in that the upper and the lower dead center of the double eccentric arrangement 8, which result from the position of the two eccentrics 9, 10 relative to one another, move in the adjustment relative to the connecting rod 7. Without compensation for the adjusted phase position, a predefinable time sequence of cyclic linear movement and rotary step movement would no longer be guaranteed after stroke adjustment. By adjusting the phase position of the above timing can be specified and adapted exactly to the needs of the machining process for the hollow body.

The preferably continuously adjusted adjustment of the phase position between rotary step movement and cyclic linear movement is described below in the schematic representation of FIG. 2 explained. In the FIG. 2 For the sake of clarity, only the components of the forming device 1 which are essential for these setting processes are shown in FIG FIG. 1 shown. Some of the in the FIG. 2 For the sake of clarity, the components shown are themselves not in the FIG. 1 shown, but form integral parts of the forming device according to the FIG. 1 ,

The drive motor 11 is connected via the belt drive 12 in conjunction with the flywheel 13 and can initiate a rotational movement to the flywheel 13 with a corresponding control by a control device 80. The flywheel 13 is associated with the flywheel 14, which can be switched by an internal, not shown adjusting means between a disengaged and a force-transmitting position. The actuating means in the flywheel clutch 14 is connected to the control device 80 for receiving a corresponding switching signal.

At the unspecified driven side clutch disc of the flywheel clutch 14, the output gear 15 mounted rotatably, which meshes with the main gear 16 and thus allows initiation of the rotational movement of the flywheel 13 to the main gear 16, if the flywheel clutch 14 is engaged. On the main gear 16, the first eccentric 9 is integrally formed, further integrally formed bearing pin 18 are also attached to the main gear 16, which is for a pivotal mounting of the main gear 16 to the in FIG. 2 not shown support cheeks 17 are provided.

The output gear 19 meshes with the main gear 16 and thus enables the transmission of the rotational movement to the stepping gear clutch 21. In the stepping gear clutch 21, a not-shown adjusting means is integrated, that the stepping gear clutch 21 can switch between a disengaged and a power transmitting position. This actuating means is also connected to the controller 80 for receiving a corresponding switching signal.

When coupled and thus force transmitting step transmission clutch 21, the rotational movement of the output gear 19 can be transmitted to the indexer 20, which generates from the continuous rotational movement of the main gear 16, a rotary step movement with a predetermined angular increment. This rotary step movement is transmitted via the stepping shaft 22 and the stepping gear 23 on the workpiece rotary table 3.

On the inner eccentric 9 of the outer eccentric 10 is mounted rotatably. For a non-rotatable fixing of the outer eccentric 10 on the inner eccentric 9, the outer eccentric 10 a thin-walled sleeve portion 81 on which a designed as a switchable coupling clamping set 82 is arranged. The clamping set 82 comprises a double conical ring 83 bearing against the circumference of the sleeve section 81 and two clamping rings 84 resting on the respective conical outer surfaces of the double conical ring 83, which are each conical on an inner circumference.

The clamping set 82 is associated with a clamping means 85, which is adapted to initiate axial forces on the two clamping rings 84 in order to approach them in the axial direction or to remove each other and thus initiation of radial clamping forces on the double cone ring 83 and thus on the sleeve portion 81 of outer eccentric 10 to allow. Thus, the outer eccentric 10 can optionally be rotatably or rotatably mounted on the inner eccentric 9 in response to a control signal of the control device 80 which acts on the clamping means 85.

As already to the FIG. 1 has been executed, the outer eccentric 10 can be fixed by means of the locking device 70, to subsequently make the relative adjustment of the inner eccentric 9 relative to the outer eccentric 10 and thus the adjustment of the power stroke for the connecting rod 7. In order to detect the relative rotation of the two eccentrics 9, 10, the main gear 16 and the inner eccentric 9 connected therewith in a rotationally fixed manner are assigned a rotational angle sensor 86 whose sensor signal is transmitted to the control device 80.

The relative rotation of the two eccentrics 9, 10 can preferably be determined when the outer eccentric 10 is fixed by means of the locking device 70, as this also its rotational position is known. The rotational position of the inner eccentric 9 is detected by the rotation angle sensor 86. Once the desired relative rotation between inner eccentric 9 and outer eccentric 10 is reached, the outer eccentric 10 by driving the clamping means 85 rotatably fixed to the inner eccentric 9.

When setting the working stroke by means of the relative rotation of the two eccentrics 9, 10, the position of the upper and the lower dead center of the double eccentric arrangement 8 with respect to the connecting rod 7 can change. This is accompanied by a change in the phase position of the cyclic linear movement relative to the stepping gear 20. However, this is not desirable depending on the processing process for the hollow body 56. Therefore, the phase position between rotary stepping and cyclic linear motion can be corrected after the adjustment of the working stroke has been performed.

For the, preferably stepless, correction of the phase position of the outer eccentric 10 is first fixed by means of the clamping set 82 rotatably on the inner eccentric 9. The flywheel clutch 14 is closed, but the stepper clutch 20 is opened. The locking device 70 is in the neutral position, so that the rotational movement of the outer eccentric 10 is not hindered. In the presence of these conditions, the control device 80 can drive the drive motor 11 to bring the connecting rod 7 by rotation of the main gear 16 in the desired position. This may be due the reduction of the rotational movement between the drive motor 11 and the main gear 16 and with a suitable design of the control device 80 with an angular resolution done, which allows virtually infinite adjustment of the phase angle between cyclic linear motion and rotational step movement. For correct adjustment of the phase position, a value table or an algorithm is stored in the control device 80, with the aid of which the phase shift of the cyclic linear movement relative to the rotary step movement can be determined on the basis of the previously made adjustment of the working stroke. The phase angle can additionally be checked via the interrogation of the rotary position of the workpiece rotary table 3 by means of the workpiece rotary table sensor 88, which is, for example, an incremental rotary angle sensor or an inductively operating proximity sensor.

For monitoring the position of the connecting rod 7, a linear sensor 87 may additionally be provided, the signal of which is provided to the control device 80 and can be compared there with the signals of the rotational angle sensor 86.

Once the double eccentric assembly 8 and the connecting rod 7 coupled therewith have reached the position in which the desired phase relationship between the first drive means substantially formed by the stepper gearing 20 and the second drive means, substantially through the main sprocket 16 with the double eccentric assembly 8 and the connecting rod 7 are formed, the stepping gear clutch 21 can be closed again. This will cause the forced coupling restored between the cyclic linear movement and the rotary step movement.

Not shown in the FIG. 1 a conveyor belt and a conveyor belt associated Ladesters for a provision of hollow bodies in the tangential direction to a loading position of the workpiece rotary table 3 and another conveyor belt with an associated unloading for removal of hollow bodies in the tangential direction of a discharge position of the workpiece rotary table 3 and other peripheral devices such they are known in the art.

Claims (12)

Forming device for cup-shaped hollow body (56) with a machine frame (2), a drive device (6), a workpiece rotary table (3) for receiving hollow bodies (56) and a tool carrier (4) for receiving machining tools (58), wherein the workpiece rotary table ( 3) and tool carrier (4) are opposite one another and about an axis of rotation (5) rotatable relative to each other and linearly adjustable along the axis of rotation (5) and wherein the drive means (6) for providing a rotary step movement and a cyclic linear movement between the workpiece rotary table (3) and tool carrier ( 4) is formed in order to allow a deformation of the hollow body (56) by means of the processing tools (58) in several successive processing steps, and with a support tube (33) fixedly assigned to the machine frame (2), the central axis of which is along the axis of rotation (5). extends and that the tool carrier (4) and / or the workpiece rotary table (3) tr gt, characterized in that a guide device (40) is disposed on an outer surface (36) of the supporting tube (33) that for a linearly movable mounting of the tool carrier (4) and / or the workpiece rotary table (3) on the supporting tube (33) formed Forming device according to claim 1, characterized in that the support tube (33) is fixedly mounted on the machine frame (2). Forming device according to claim 1 or 2, characterized in that the machine frame (2) comprises a spaced from the support tube (33) formed pivot bearing (25) for the workpiece rotary table (3) or tool carrier (4). Forming device according to claim 3, characterized in that the pivot bearing (25) and the support tube (33) are arranged together on a support plate (26) of the machine frame (2). Forming device according to claim 4, characterized in that the support plate (26) together with a support frame (31) forms a first machine frame section (27) and that the drive device (6) on support cheeks (17) is received, the second machine frame part (59) form, so that an at least substantial decoupling between the forces provided by the drive device (6) and the workpiece rotary table (3) and the tool carrier (4) is achieved. Forming device according to claim 5, characterized in that between the first machine frame part (27) and the second machine frame part (59) an articulated, preferably flexible, in particular as a solid-body joint, formed coupling region (60) is provided. Forming device according to claim 6, characterized in that a hinge axis of the articulated coupling region (60) is aligned transversely to the axis of rotation (5). Forming device according to one of the preceding claims, characterized in that between the support tube (33) and the tool carrier (4) or workpiece rotary table (3) is formed, preferably prestressed, in particular backlash-free, rolling element bearing assembly (42). Forming device according to claim 8, characterized in that on an inner surface () of the support tube (33), preferably designed as a sliding bearing, bearing means (39) for a coupling slide (34) of the drive means (6) is formed, for a force-transmitting connection between a connecting rod (7) of the drive device (6) and the tool carrier (4) or the workpiece rotary table (3) is provided. Forming device according to claim 9, characterized in that between the coupling carriage (34) and the tool carrier (4) or workpiece rotary table (3), a preferably annular design, elastic coupling means (53, 54) is arranged, which is for power transmission between coupling slide (34). and tool carrier (4) or workpiece rotary table (3) and for decoupling of tilting movements of the coupling carriage (34) is formed transversely to the axis of rotation (5). Forming device according to one of the preceding claims, characterized in that a guide length for the tool carrier (4) or workpiece rotary table (3) along the support tube (33) and / or for the coupling slide (34) along the support tube (33) at least 1.5 -fold, preferably at least 2 times, in particular at least 2.5 times, the maximum stroke of the tool carrier (4) or workpiece rotary table (3). Forming device according to one of the preceding claims, characterized in that the support tube (33) and the tool carrier (4) or workpiece rotary table (3) are mounted cantilevered on the support plate (26).

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