Extrusion press

Abstract

Operational safety during operation of an extrusion press (10) can be increased by virtue of the specialization of the electrical drives (50) that act upon the receiving container (13) in order to operate the extrusion press.

Description

[0001] Strangpresse

[0002]

[0001] The invention relates to an extrusion press for pressing a material to be pressed through a die with a receiver for receiving the material to be pressed and with a pressing die that can be displaced relative to the receiver.

[0002] Extrusion presses for pressing a material to be pressed through a die with a receiver for receiving the material to be pressed and with an assembly that can be displaced relative to the die and which can be subjected to a force required for pressing by an electric motor drive during pressing are already known from EP 3 470 146 B 1, from the as yet unpublished German patent application DE K1 2023 100 729 and from the as yet unpublished German patent application DE 10 2023 105 916.On the other hand, DE 102015 1 16 (X)2 B4 discloses an extrusion press for pressing a material to be pressed through a die with a receiver receiving the material to be pressed and with a pressing die that is displaceable relative to the receiver, in which the pressing forces are applied via a hydraulic drive and in which the receiver is driven by an electric motor and by a drive pinion-rack unit.

[0003]

[0003] It is an object of the present invention to provide an extrusion press which can be operated as reliably as possible while maintaining an electric drive for the extrusion press pickup.

[0004]

[0004] The object of the invention is achieved by extrusion with the features of the dependent claims. Further, possibly independent, advantageous embodiments can be found in the dependent claims and the following description.

[0005]

[0005] The invention is based on the general knowledge that by specializing the electrical drives acting on the transducer for operating the extrusion press, the operational reliability of the extrusion press can be increased accordingly.

[0006] In this context, the term "extrusion press" preferably encompasses a press that can be used for extrusion or molding processes. For example, an extrusion press can be used to produce, in particular, metallic wires, rods, tubes, and / or other prismatic profiles. Such extrusion presses can also, in particular, work with powder-like materials, for example, with metallic, ceramic, or hard-material powders, with Ciraphite powder, or mixtures thereof. Corresponding granules are also considered equivalent. For this purpose, the powders or granules can, if necessary, be sufficiently compacted and pressed beforehand, or suitably coated, so that they can then be loaded into the extrusion press's receiver. It is conceivable that plastic materials could also be processed, in which case the process is referred to as extrusion.The present extrusion presses are advantageously used for processing metallic materials. Preferably, the present extrusion press is used to form or re-form stainless steel or aluminum profiles. It should be understood that the application of the extrusion press of the present invention is not limited to this, but can also be used for other products.

[0006]

[0007] In this case, the material to be pressed is pressed against a die and through it by a press ram or a similar assembly with the force required for pressing. In this way, the forming or primary forming process takes place.

[0007]

[0008] To ensure that the material to be pressed through the die and does not escape sideways, the material is surrounded by a receiver during pressing. Depending on the specific implementation, the receiver usually remains stationary relative to the die or the die during pressing, although mixed forms are theoretically conceivable.

[0008]

[0009] In this context, the term “receiver” is preferably understood to mean any assembly that can receive the material to be pressed and prevent it from breaking out sideways during the pressing process.

[0009]

[0010] In practice, a distinction is made between direct and indirect presses. In the former, the press ram usually moves into the receiver, meaning the receiver remains stationary relative to the die, while in the latter, a relatively short press ram is generally provided, which merely closes the receiver at the end facing away from the die, while the die is carried in a die carrier, and the receiver and ram are moved over the die, which, carried by the die carrier, then moves into the receiver and extends into it.

[0010]

[0011] The extrusion press can have a die beam which supports the die, wherein at least two tie rods of the extrusion press, which counteract the force required for pressing by pulling, can act on the die beam in a pulling manner, so that the required pressing force for pressing the material to be pressed can be applied to the material to be pressed through the die.

[0011]

[0012] In particular, the pulling arms can also act on a die head in a pulling manner, so that the pressing force required for pressing the material to be pressed through the die can be applied to the die via this counter-bar.

[0012]

[0013] In this context, a die can be understood as the tool through which the material to be pressed is pressed, thereby effecting the final or primary shaping of the material. The die can therefore have a decisive influence on the shape of the material to be pressed after the pressing process, as it determines the essential parameters regarding the dimensions of the material pressed through the die.

[0013]

[0014] As is known, the pressing forces are applied by electromotive or hydraulic actuators acting between the counter-hollow and the press ram, whereby the press ram is moved against the die by the drive or drives for pressing.

[0014]

[0015] [nsofeni, the press ram can preferably serve to transfer the force required for pressing the material through the die to the material to be pressed or to apply it to it. [lö] So that the force transmission can be as even and reliable as possible, the press ram is preferably guided via a support beam or constructed in one piece with a travel beam, whereby the latter appears to be structurally simple, while the former has the advantage of being replaceable of the press ram in case of wear or damage and a specialization of the respective components for their respective task, for example a stabilization of the movement sequence by the support beam or a precise

[0015] The application of the pressing force to the material to be pressed, without it breaking out too much, can enable the pressing ram. By means of such a running beam, the pressing forces can then be transferred evenly into the pressing ram and then via the pressing ram to the material to be pressed.

[0017] - In the present context, a running beam can preferably be understood as a

[0016] This assembly is guided and mounted in such a way that it can be displaced in a controlled manner toward the die or toward the die spar and vice versa. In particular, the spar can also be designed so that sufficiently high pressing forces can be transmitted from the main drive generating the pressing force to the die spars.

[0017]

[0018] In order to press the material through the die in a reliable and controlled manner, the receiver can preferably be subjected to a radial expansion of the

[0018] Press material naturally expands radially when pressed with high force against an element, such as a die in this case. Particularly during a pressing process, very high forces act on the material. However, to ensure that the material can be pressed continuously and as completely as possible through the die, a suitably designed transducer can be advantageous. In particular, the transducer can be dimensioned depending on the forces acting on the material. The strength of the radial expansion of the material to be pressed then changes accordingly. The size or diameter of the die as well as the physical properties of the material to be pressed can also have an influence on the radial expansion of the material to be pressed, which the transducer is intended to counteract. In this respect, a transducer is understood in particular to be an assembly that is suitable and intended for this purpose.to counteract radial expansion of the material to be pressed during pressing.

[0019]

[0019] In this context, a pressed product describes in particular the

[0020] Pressing refers to the material to be formed or reshaped, or the raw material that is fed into the extrusion press for pressing. This can be steel, copper, brass, or aluminum.

[0021] Powdered materials, such as graphite, can also be used, if necessary after appropriate preparation. In particular, powder-like materials with metallic, ceramic, or hard material powders, with graphite powder, or with mixtures thereof, as well as corresponding granules, can serve as pressed material.

[0020] Preferably, the extrusion press is a metal extrusion press for pressing a metallic block through the die, so that metallic materials can be reliably pressed through the die by means of the extrusion press. Metal extrusion presses are designed for the particularly high forces that arise or must be applied when pressing a metallic block.

[0021] Accordingly, the transducer is preferably a kickback transducer, which represents a particularly stable transducer and is therefore specially designed for pressing metallic blocks through a die.In particular, it must be taken into account that when pressing metallic blocks, correspondingly high radial expansion forces act, which should be reliably absorbed by a block absorber.

[0022]

[0022] It is advantageous if the extrusion press operates discontinuously and the receiver can be filled with extruded material before pressing, emptied during pressing, and then refilled with extruded material for a new pressing process. During the pressing process, the extruded material can usually be pressed through the die and the receiver emptied. This then allows it to be refilled with extruded material. If any remnants of the extruded material remain in the receiver during the pressing process, these can also be removed if necessary before new extruded material is filled into the receiver. On the other hand, it is also conceivable that these extrusion residues are extruded during the next pressing process, whereby the areas pressed from the extrusion residues can be discarded as scrap if necessary.

[0023]

[0023] In order to be able to operate an extrusion press for pressing a material to be pressed through a die with a receiver that receives a material to be pressed and with a pressing spindle that is displaceable with respect to the receiver, if possible while maintaining an electric drive for the receiver of the extrusion press, the extrusion press can be distinguished as reliably as possible by an electromotive receiver spindle drive, independently of the other feature combinations described here as advantageous.

[0024]

[0024] In particular, for loading or setup purposes, the pickup should be capable of being moved, preferably independently of the main drive with which the pressing forces are applied. This is because, for setup or loading activities, the pickup should be able to be moved independently of the assemblies with which it remains stationary during pressing. One such assemblies could be, for example, the die beam if it is a direct press; on the other hand, it could be, for example, the travel beam if it is an indirect press. After each pressing cycle, it is advantageous to move the pickup independently of the travel beam, which is particularly advantageous or used in a direct press if the pickup is moved independently of the travel beam towards the die beam before the start of the pressing process and is moved around the die or the travel beam for the subsequent remaining process.is positioned accordingly. With an indirect press, it is advantageous if the receiver initially remains in its position after pressing and only the moving crosshead is removed from the die crosshead. If necessary, the receiver can even be brought even closer to the die crosshead in order to be able to carry out setup work on the die, which protrudes through the receiver and is carried by the die carrier. Then, after setup is complete, the receiver can be moved towards the moving crosshead so that the crosshead and receiver can then be moved together against the die crosshead again for the pressing process.

[0025] Therefore, any electric motor drive can be considered as a pickup drive, by means of which the pickup can be moved independently of the travel beam or independently of the main drive, with which the pressing forces are essentially applied. In this case, a pickup spindle drive is recognized as particularly advantageous as a pickup drive, since this appears to enable a reliable displacement of the pickup while maintaining an electric drive. This is especially true considering the fact that such

[0025] For reasons of stability, transducers are often solid and therefore very heavy, so the risk of jamming and uneven movements is relatively high. An electromotive transducer spindle drive includes any drive device driven by an electric motor and comprising a spindle gear. Such devices prove particularly advantageous when electromotive linear movements over long distances are to be carried out reliably.

[0026]

[0026] Cumulatively or alternatively to the combinations of features presented here as advantageous, an extrusion press for pressing a material to be pressed can be characterized by a die with a receiver receiving the material to be pressed and with a pressing punch that can be displaced with respect to the receiver by an electromotively opened and closed sealing device in order to be able to operate the extrusion press as reliably as possible while maintaining an electric drive for the receiver.

[0027]

[0027] As already explained above, relatively large forces occur during pressing, which lead to the pressed material tending to evade the movement between the press ram and the die and thus the forces applied to the pressed material, which happens particularly radially, and for which the receiver ultimately counteracts this. Since the receiver, as also explained above, is preferably displaced both in relation to the die and in relation to the crosshead. This displacement, depending on the specific design of the press, generally occurs during pressing with respect to one of these assemblies, and the displacement with respect to the other of these assemblies before or after seizing, arises in relation to the assemblies to which the receiver remains stationary during pressing.Seams into which the material to be pressed, after it has been pressed between the press ram and die and its radial expansion is limited by the receiver, tries to escape. The receiver seal serves precisely to seal these seams, so that a corresponding receiver seal, depending on the specific design of the press as a direct press or indirect press, should be effective towards the running hole or towards the die head.

[0028] Depending on the specific implementation, the transducer seal can be achieved by adjacent or mutually sealed surfaces of the transducer on the one hand and the respective assembly, i.e. the running beam or the die beam, on the other hand. On the other hand, it goes without saying that the transducer seal can optionally comprise additional assemblies which are arranged randomly between the transducer on the one hand and the other assembly, i.e. the running beam or the die, on the other hand, in order to influence the sealing properties of the transducer seal. For example, sealing materials or sealing bodies can be additionally provided between the transducer on the one hand and the other assembly, in particular the running beam or the die, on the other hand, in order to form the transducer seal. Likewise, additional die plates or other sealing elements can be used for the transducer seal.

[0028]

[0029] In particular, the receiver seal can comprise the receiver on the one hand and a sealing plate on the other, wherein the sealing plate is preferably then unattached to the die spar or the receiver or, as already described above, formed integrally with it. Any plate-shaped device can serve as the sealing plate, which can form a seal together with the receiver and is displaceable relative to the receiver, so that the receiver seal can be opened at certain times during operation of the extrusion press.

[0029]

[0030] Preferably, the sensor on the one hand and the sealing plate on the other hand can be subjected to a sealing force by an electric motor, whereby an openable and closable sensor seal can be realized in a structurally simple manner.

[0030]

[0031] Because of the relatively large compressed coal, it is particularly advantageous if the sealing force can be applied via a sealing spindle drive. As such spindle drives can generally transmit relatively large forces, a correspondingly large sealing force can be achieved, which can then be counteracted by the pressed material flowing through the receiver seal. 132] Since a linear movement is generally necessary or advantageous for applying the compression force, spindle drives are particularly suitable as sealing spindle drives, as they can transmit high forces reliably in a linear manner.

[0031] [33j Ultimately, any spindle drive that can sufficiently provide the required sealing force can be used as a sealing spindle drive. In particular, such spindle drives can be driven by an electric motor in a structurally simple manner, so that an electric motor-operated opening and closing of the sealing device can be advantageously provided.

[0032]

[0034] A structurally simple implementation of an electromotive openable and closable receiver seal can be achieved if the sealing force can be applied via a sealing spindle drive and this sealing spindle drive is implemented by the receiver spindle drive. In this way, the receiver seal can be provided directly by the receiver spindle drive, so that a supplementary electromotive drive for the openable and closable external receiver seal does not appear necessary. 135] On the other hand, additional gear construction measures may be required to relieve the external receiver spindle drive in such a design during pressing, so that it does not have to apply the sealing force for a longer period. For example, it is conceivable that the spindle drive... when the receiver has reached the position it is supposed to assume during pressing.rotates further to then bring a supplementary mechanical sealing clamp into a sealing position.

[0033]

[0036] In case of doubt, the sealing clamp can then take over the sealing forces, so that the spindle or the spindle drive is relieved accordingly.

[0034]

[0037] Instead of a sealing clamp, a locking device can also be used to relieve the spindle drive or the electric motor drive.

[0038] On the other hand, a separation of the drives for the pickup spindle drive, whose actual function is the axial displacement of the pickup, and the sealing drive, whose actual function is to seal the pickup to the sealing plate or either to the running line or to the die or to the die spar, can be advantageous, since although this requires several units, these can each be specially designed with regard to their task, so that this may result in cost savings that justify the somewhat higher construction effort.Under these conditions, it may even be possible to deviate from the basic design, which specifies an electric drive for the extrusion press's transducer as the target specification, and to equip the sealing element not with an electric motor but, for example, hydraulically.

[0039] Accordingly, it may be advantageous if the transducer seal can be opened and closed hydraulically. Deviating from the basic assumption that hydraulic units are generally relatively complex and that the hydraulic fluid may pose a fire hazard due to the high temperatures that occur in the transducer area, a sealing drive proves to be possible due to its generally short-distance and relatively limited structural demarcation, which such a transducer seal requires, in order to open and close a transducer seal in a structurally simple manner - and in particular to counteract the sealing forces.

[0035]

[0040] Preferably, the hydraulic opening and closing of the transducer seal is realized by a hydraulic cylinder-piston drive, which the transducer seal comprises. In particular, a short-stroke hydraulic cylinder can be advantageously used in this regard, which requires correspondingly low oil volumes, so that the risks of fire or oil contamination, as well as the effort for laying any lines, should be relatively low. Likewise, a cylinder-piston drive can be realized by an electro-hydrostatic actuator, which enables a particularly compact design and minimal use of hydraulic fluid, so that the actual disadvantages that lead to the use of an electric drive for the transducer do not occur to this extent. In particular, it is understood that this is the case with the transducer spindle.with which essentially the pickup is to be displaced axially with respect to the running beam or the die or the mold beam or with respect to the sealing plate, an electric motor drive does not have to be dispensed with.

[0036]

[0041] Preferably, the pickup spindle drive comprises an electric motor drive which can, for example, drive the spindle or an associated nut.

[0037]

[0042] In the present context, an electric motor drive can preferably be a drive by means of an electric motor or a servo motor, which can also be referred to as an electrical converter. This converts electrical power into mechanical power. For example, the electric motor drive could be a three-phase motor, a linear motor, or an alternating current motor. In the present context, all electromechanical converters by means of which electrical energy can be converted into mechanical energy are preferably referred to as electric motor drives.

[0038]

[0043] Any method by which a gear arrangement comprising a spindle can be driven by an electric motor is considered as an electric motor drive. For example, a torque motor can be used in this regard. In particular, however, a geared motor can also be used as an electric motor drive.

[0039] |44 | Depending on the specific design, two electric motors coupled via a gearbox can be used as an electric motor drive or as part of the pickup spindle drive.

[0040]

[0045] In particular, the receiver spindle drive can comprise a spindle-milling arrangement comprising at least one spindle and at least one nut, whereby a receiver spindle drive can be easily converted structurally. It is understood that, depending on the specific design, the spindle or the nut can be driven by an electric motor to implement an electric motor-driven receiver spindle drive.

[0041]

[0046] In the present context, a spindle can be understood as a threaded shaft for transmitting a rotary movement or for converting a rotary movement into a longitudinal movement or into pressure. For example, the spindle can be a threaded spindle, which, together with other elements in a helical gear, can serve, as already described above, to convert a rotary movement into a translatory movement. Threaded spindles preferably comprise a threaded rod, i.e., usually a cylindrical round rod, onto which, in simple applications, a trapezoidal or flat thread is applied.

[0042]

[0047] 'A nut in the present context preferably describes the counterpart to a spindle and represents a machine element with an internal thread whose diameter corresponds to the diameter of the thread of the spindle or is adapted to it, so that the nut can be screwed onto the spindle. By rotating the nut or the spindle relative to each other, these two elements can be translated relative to each other. A corresponding arrangement can be referred to in the present context as a spindle-nut arrangement.

[0048] Both a rotationally driven spindle and a non-rotating nut or a rotary-driven nut and a non-rotating spindle as well as the use of a rolling gear between spindle and nut result, in each case with a suitable design, in a reduction of the friction caused by the use of a spindle.A rolling-contact gear, although generally smaller surfaces are available for power transmission, can still reduce friction, especially since large forces can be transmitted by rolling. With a rotary-driven spindle, the bearings that support the rotating assembly of the spindle-nut arrangement can be mounted radially further inward, which, due to the smaller bearing radii, also reduces the resulting frictional moments. On the other hand, a rotating nut allows the use of relatively complex bearings and a drive with a relatively large ratio, which in turn can enable favorable frictional conditions.

[0043]

[0049] Preferably, the spindle-Muller arrangement has a rolling thread between the spindle and the Muller aut. so that a particularly uniform axial drive can be realized, which appears to be advantageous in particular with regard to the weight or mass of the sensor and the length of the path that the sensor is to travel.

[0044]

[0050] As already explained above, it can be advantageous if the spindle and / or the miller are driven by the electric motor drive. This allows an electromotive pickup spindle drive to be implemented in a correspondingly simple construction. Driving both the spindles and the nuts by an electric motor drive can, for example, be advantageous if different tasks, such as the axial displacement of the pickup on the one hand and the sealing of the pickup on the other hand, are to be achieved by the different drives as well as the two different drives, namely the spindle and the nut.

[0051] The spindles or the nut can be attached to the pickup or to a fixed component of the extrusion press, such as the die beam or the counter beam, via a damper in order to thereby dampen the effect of any shocks or impacts on the spindle-nut arrangement orto take on the pickup spindle drive.

[0045]

[0052] Preferably, the damping on the spindle or on the nut is random, so that damping of the entire arrangement can be achieved in a structurally simple manner, if this is deemed sufficient. In particular, it proves advantageous if the spindle is damped or the damping is arranged on the spindle if the spindle is not hydraulically driven, so that corresponding damping of the spindle can be implemented structurally simply.

[0046] (53 ] Depending on the specific implementation, the spindle or the nut can run with the transducer. Under certain circumstances, it may be structurally possible to have both the spindle and the nut run with the transducer if this part of the running

[0047] The arrangement serves a specific purpose, such as sealing the sensor. However, as a rule, only one of the two components—the spindles or the nut—runs with the sensor.

[0048]

[0054] The spindle may have a bearing area and a threaded area, wherein the bearing area primarily serves to support the spindle, while the thread of the spindle in its threaded area serves to interact with an assembly running along the spindle, in particular to interact with a nut.

[0049] [55 J Insofar as it can be assumed that the threaded area is subject to greater wear, it can be advantageous if the bearing area and the threaded area are designed to be separable from each other. This then makes it possible to replace the threaded area if excessive wear occurs. On the other hand, such separation also makes it possible to replace the longitudinal area if increased wear or damage is observed in this area.

[0050]

[0056] If the sealing force is actually applied via an electric motor drive, it may be advantageous to subject the motor torque to cyclic control in order to apply only the sealing force required for the process – and not the maximum possible power of the electric motor drive. Alternatively or in addition to this, the motor can, for example, be position-controlled, which can be particularly advantageous in conjunction with a sealing clamp or a wedge connection, in order to adapt the sealing force to the current conditions during pressing.

[0051]

[0057] It is understood that the features of the solutions described above or in the claims can also be combined if necessary in order to be able to implement the advantages cumulatively.

[0052]

[0058] Further advantages, aims, and features of the present invention will become apparent from the following description of exemplary embodiments, which are particularly illustrated in the accompanying drawings. In the drawings: Figure 1 shows a first extrusion press designed as a direct press in a schematic side view with the receiver open,

[0053] Figure 2 shows the extrusion press according to Figure 1 with the sensor closed and sealed:

[0054] Figure 3 shows a second extrusion press designed as an indirect press in a schematic side view with the receiver closed and sealed;

[0055] Figure 4 shows the extrusion press according to Figure 3 with the pickup open;

[0056] Figure 5 shows a third extrusion press designed as a direct press in a schematic side view with the receiver open:

[0057] Figure 6 shows a fourth extrusion press designed as a direct extrusion press in a schematic side view with the receiver open;

[0058] Figure 7 shows a fifth extrusion press designed as a direct press in a schematic rope view with the receiver open;

[0059] Figure 8 shows a sixth extrusion press designed as a rotary press in a schematic side view with the receiver open; Figure 9 shows an exemplary, partially exploded view of a ball screw;

[0060] Figure 10 shows an exemplary representation of a first roller thread;

[0061] Figure 11 shows a detailed view of the roller return of the roller thread according to Figure 10; Figure 12 shows an exemplary representation of a second roller thread; Figure 13 shows a front view of the roller thread according to Figure 12; Figure 14 shows a schematic representation of the damping used in the arrangement according to Figure 5 in an implementation by means of tell-springs; Figure 15 shows a schematic representation of the damping used in the arrangement according to Figure 5 in an implementation by means of an elastic body:

[0062] Figure 16 is a schematic representation of the damping used in the arrangement according to Figure 5 in an implementation by a hydraulic damper;

[0063] Figure 17 shows a seventh extrusion press similar to the extrusion press according to Figure I, with a separate sealing spindle drive for opening and closing the receiver seal; and

[0064] Figure 15 is an eighth extrusion press similar to the extrusion press according to Figure 1, with a hydraulically openable and closable receiver seal when the receiver is closed and sealed.

[0065]

[0059] The eight extrusion presses 10 shown in the drawing each serve to press material II through a die 12. For this purpose, the extrusion presses H1 each have a runner bar 15 and a counter bar 18, which are clamped via tension bars 16 in a manner known per se such that a press ram 14 can be moved toward the die 12 in order to press the material 11 through the die 12.

[0066]

[0060] The press punch bl is provided on a traveling beam 17, which is guided axially displaceably between the counter beam 18 and the die beam 15. The traveling beam 17 is driven in a manner well known per se by a main drive not numbered here.

[0067]

[0061] A receiver 13 is also provided which can be mounted in the axial direction and thus in the direction of movement 71 and which serves to counteract a radial expansion of the material to be pressed 11 when the pressing forces are applied by the main drive and the material to be pressed 11 is pressed through the die 12.

[0068]

[0062] The pickup 13 can be supported in the direction of movement 71 by a pickup spindle drive 40, which will be explained in more detail below, independently of a movement of the travel beam 17. The corresponding procedure will be explained in more detail below.

[0063] The eight extrusion presses 10 shown in the drawing are, with the exception of the second

[0069] Extrusion presses 10 according to Figures 3 and 4 each have direct presses, while the second extrusion press 10 shown in Figures 3 and 4 is designed as an indirect press. In direct presses, the press sleeve 14 is relatively long, so that for pressing, the receiver 13 is brought against the die bar 15, as shown by way of example in Figures 2, 17 and 18. The receiver 13 is held in this position during pressing, so that the press die 14, after the pressed material 11 is located in a receiving position of the receiver 13 in front of the die 12, can be displaced by the main drive against the die 12, whereby the pressing process e1 follows, by means of which the pressed material 11 is pressed through the die 12.

[0064] For loading the direct presses, the pickup 13 can be displaced by means of its pickup speitdclt line 40 in the direction of the counter-holin 18, as shown by way of example in Figures

[0070] I and 5 to 8. In this position, on the one hand, preparation work, for example cleaning work on the die 12, and on the other hand, loading the extrusion press 10 with pressed material

[0071] II is possible, as shown by way of example in Figure 1. If the material to be pressed is in the position shown in Figure 1, for example, the moving beam 17 can be displaced slightly towards the die 12, so that the press ram 14 presses the material 11 lightly against the die 12 and the material 11 thus remains in its position. The receiver 13 can then be moved against the die beam 15 and brought into the position shown in Figure 2 or also in Figures 17 and 18.

[0072]

[0065] In these embodiment examples, i.e. in the first extrusion press 10 and in the third to eighth extrusion presses 10, the die beam 15 is designed as a sealing plate 31, so that a receiving seal 30 can be provided between the receiver 13 and the sealing plate 31 or the die beam 15.

[0073]

[0066] Once the sealing has been completed, the pressing die 14 can be moved further against the die 12 in order to finally carry out the pressing process.

[0074]

[0067] Once the pressing process is completed, the press ram 14 is moved back toward the counter beam 18. The same also occurs with the receiver 13, so that setup activities can be carried out again and additional pressed material 11 can be fed into the extrusion press 10. The pressing cycle can then be carried out again.

[0075] [68J The processes are slightly different in an indirect press, as shown in Figures 3 and 4 as an example.

[0069] In an indirect press, the die 12 is preferably supported by a matrix carrier

[0076] 19, which extends from the die beam 15 toward the counter beam 18 and can project into the receiver oil opening (not numbered) of the receiver 13. On the other hand, in the indirect press, the press sleeve 14 is relatively short.

[0077]

[0070] In this context, it should be mentioned that the moving beam 17 and the pressing die 14 can, if appropriate, be formed as a single piece in both direct presses and indirect presses, if this appears advantageous. Particularly in an indirect press, it is conceivable that the die is relatively small and merely formed as a protrusion in the moving beam 17.

[0078]

[0071] For pressing, after the material to be pressed 1 1 is in the receiving opening of the receiver 13, the running beam 17 and the receiver 13 are moved against the Mairiz.enholin

[0079] 15, which in this embodiment serves as a sealing plate 31 and together with the sensor 13 forms a receiver seal 30.

[0080]

[72] For pressing, the arrangement of the running beam 17, receiver 13 and press die 14 can then be moved against the die beam 15 and the die 12 carried by the die carrier 19, whereby the pressing process takes place.

[0073] After pressing, the running beam 17 can be moved again in the direction of the counter beam 18, so that free space is created for setting-up activities and for loading the extrusion press 10 with pressed material 11, as is shown by way of example in Figure 4.

[0081]

[0074] In the direction shown in Figure 4, the running rod 17 and also the pressing rod 14 can now be moved in the direction of the die bar 15 until the material to be pressed 11 is slightly clamped between the pressing rod 11 and the die 12. The receiver 13 can also be moved in the direction of the counter bar 18 until the receiver seal 30 is closed and the position according to Figure 3 is reached. Then, the main drive can move the counter bar 17 again in the direction of the die bar 15 in order to carry out the next pressing process.

[0082]

[0075] In order that the pickup 13 can also be moved independently of the running line 17 in the direction of movement 71, the extrusion presses each have spindle-nut arrangements 20 as pickup spindle nuts 40.

[0083]

[0076] The respective spindle airlifter arrangements 20 comprise a spindle 21 and a nut 22, which is connected for example via a rolling gear 23, in particular for example via a

[0084] Ball screw 80 or a roller screw l W. can interact with each other.

[0085]

[0077] In particular, as shown in particular in Figure 9, a ball screw 80, which is to be used as a rolling screw 23, can comprise a spindle 21 and a nut 22 designed as a ball recirculating nut 82, which also has a ball return 83 and together with the spindle 21 forms grooves 84 for balls 81, which at a relative

[0086] Rotational movement between nut 22 and spindle 21 in the running grooves 84 and the ball groove 83.

[0087]

[0078] If the spindle 21 is now driven in rotation relative to the nut 22 or vice versa, the balls 81 move in the grooves 84 between the spindle 21 and the ball nut 82, which move axially when the spindle 21 rotates. The movement of the balls 81 occurs as a rolling action. The ball return guide 83 in the ball nut 82 transports the balls 81 back again, thus closing the circuit in which the balls 81 circulate.

[0088]

[0079] While in conventional dust gears with sliding surfaces 50 to 90% of the introduced power is converted into heat, the present ball screw 81 with its ball screw drive has less friction due to the rolling movement of the balls 81. In this way, a lower drive power can be sufficient, which appears to be particularly advantageous when using an electric motor drive. In addition, the overall wear and in particular the wear between spindle 21 and ball nut 82 is relatively low. Depending on the specific design, even relatively large forces can be applied reliably and smoothly by such an arrangement.

[0089]

[0080] In an alternative embodiment, a roller thread 90 can also be used as the rolling thread 23 for the spindle-nut arrangement 20.

[0090]

[0081] For example, a roller thread 97 can be used as the roller thread 90, as shown by way of example in Figures 10 and 11.

[0091]

[0082] Here, the roller screw drive 97 comprises a spindle 21 and a nut 22 designed as a roller-reducing nut 92. In this embodiment, rollers 91, each having circular grooves 99, rotate around the spindle 21. As the rollers 91 rotate with their grooves 99 around the spindle, a relative movement in the axial direction occurs. A correspondingly designed roller-reducing nut 92 also comprises a roller return 98, which serves to lift the rollers 91 off the spindle and return them again.

[0092]

[0083] Due to the radial and axial movement of the rollers 91, the roller nut

[0093] 92 is designed like a cage to hold the rollers 91 in position. Ultimately, the relative movements in the axial direction, which the rollers 91 perform with their circular grooves 99 in relation to the spindle 21, also drive an axial relative movement of the roller bearings 92 and the nut 22, respectively, which likewise enables relatively large power transmissions with smooth running and low friction losses.

[0094]

[0084] A roller thread 90 designed as a planetary roller screw drive 93 can also be used as the pickup spindle drive 40, as shown, for example, in Figures 12 and 13.

[0095]

[0085] The Pkmclcn roller screw drive 93 according to Figures 12 and 13 comprises rollers 91 with a thread 94, which rotate in an annular roller nut 92 as nut 22 around a spindle 21. This rotation results in an axial relative movement between the rollers 91 and the spindle 21 and thus also between the roller nut

[0096] 92 or the nut 22 and the spindle 21. [86J The diameters of the spindle 21, the rollers 91 and the roller nut 92 are selected so that the peripheral speeds of the spindle 21 and the rollers 91 match. The synchronization is carried out by a ring 95 with an internal toothing integrated into the roller nut 92, which engages in pinions 96 at the ends of the rollers 91.

[0087] In the planetary roller screw drive 93 according to Figures 12 and 13, the

[0097] Rollers dl or rolling elements - in contrast to the embodiments according to Figures 9 to 111

[0098] - in the longitudinal direction not relative to the roller bearing center 92, so that no feedback mechanism is necessary. This may allow higher speeds.

[0099] [881 Roller threads 90 also enable a corresponding reduction in friction or, with uniform axial propulsion, the transmission of relatively large forces.

[0100]

[0089] In the extrusion press shown in Figures 1 and 2, the pickup spindle drive 40 comprises an electric motor drive 50, which in this embodiment is implemented by two gear motors designed as electric motors 53, which can drive a spindle 21 in rotation via a gear wheel not numbered in more detail.

[0090] The spindle 21 comprises a threaded threaded area 24 and a bearing area 25, which essentially serves to support the spindle 21.

[0101]

[0091] For mounting the spindle 21, the support 25 of the spindle 21 carries a bearing body 27, on which bearings 28 engage, which in turn are supported on the counter-bearing IS, so that the electric motor drive 50 sets the spindle 21 in rotation and a double-shaped roller 22, which is held on the pickup 13 via a damper 60, can be axially displaced together with the pickup 13, whereby the desired axial movement along the direction of movement 71 can be realized independently of the running bolt 17 or the press ram 14.

[0102]

[0092] A separation point 26 is provided between the threaded portion 24 and the bearing portion 25 of the spindle 21, so that the threaded portion 24 can be replaced relatively easily if, for example, wear occurs.

[0103]

[0093] It is understood that in different guide forms, such a separation point 26 or even the strict separation between the threaded area 24 and the bearing area 25 can be dispensed with if this does not appear absolutely necessary.

[0094] If necessary, the electromotive drive 50 and / or the bearing body 27 on the one hand and the nuts 22 on the receiving spindle drive 40 can be exchanged in such a way that the electromotive drive 50 runs along with the sensor 13, while the nuts 22, possibly also via dampers 60, as shown by way of example in Figures 3 and 4, are held on the counter-hinge 18 in order to realize in this way a possibility of movement in the direction of movement 71 for the sensor 13.

[0104]

[0095] It is understood that the design of the pickup spindle drive 40 in the second extrusion press 10, as shown in Figures 3 and 4, can also be used in the remaining extrusion presses 10 if necessary. Conversely, the design of the pickup spindle drive 40 after the first extrusion press 10 or after the third to eighth extrusion presses 10 can also be used in the extrusion press II).

[0105]

[0096] While in the first and second extrusion presses 10 the spindle 21 rotates and the nuts 22 are mounted in a rotationally fixed manner, this can also be realized differently, as shown by way of example in Figures 5 and 6, in which the spindle 21 remains rotationally fixed, while the nuts 22 are rotationally driven,

[0106] [W] For this purpose, the nuts 22 are arranged on a multi-carrier 59, which in turn is mounted on the counter beam 15 (see Figure 5 l or on the pickup 13, Figure 5 f) via bearings 28, depending on whether the electric motor drive 50 is to run with the pickup 13 or not.

[0098] In the embodiment shown in Figure 5, the multi-carrier 59 is in turn connected via an intermediate piece 28 to electric motors 53 designed as drive motors 52, as is already known from the embodiments shown in Figures 1 to 4.

[0107]

[0099] Alternatively, as shown in Figure 6, a torque motor 51 or another direct drive can be used as the electric motor drive 50, which can drive the nut carrier 59 via the intermediate piece 58. Depending on the specific design, the intermediate piece 58 can also be omitted.

[0108]

[0100] It is understood that the drive types shown in Figures 1 to 5 can also be used in the exemplary embodiment according to Figure 6. It is also conceivable that a direct drive, such as the torque drive shown in Figure 6, is used correspondingly in the other extrusion presses 10 shown here. In order to realize the spindle 21 as non-rotating with respect to the rollers 22, the bearing body 27 can be mounted on the assembly, for example on the counter-element 15 (see Figure 6) or on the receiver 13 (see Figure 5), via an anti-rotation device 29, in order to provide a non-rotating spindle 21 in this way.

[0109]

[0102] A corresponding embodiment is shown by way of example in Figures 14 to 16, which comprises a locking means 29 in the form of a split pin, which is inserted into an associated groove of the receiver 13 and thus realizes an anti-twist device 24 for the embodiment shown in Figure 5.

[0110]

[0103] In addition, the bearing area 25 of the spindle 21 can be axially secured by means of a disc spring package 61, which is secured by means of lock nuts 69 on the bearing body 27 and on the sensor 13 in corresponding recesses of the sensor 13, so that a damping 60 can also be realized by means of the disc spring package 61, as shown by way of example in Figure 14.

[0111]

[0104] Alternatively, as Figure 15 shows by way of example, instead of the disc spring assemblies 61, a cylindrical body 62 can also be inserted into the corresponding recess of the transducer 13 and fixed by means of the locking nuts 69 in order to secure the spindle 21 with sufficient axial damping and in this way to realize the damping 60.

[0112]

[0105] Likewise, a hydraulic damper can optionally be used as damping 60, which is preferably also secured by a lock nut 69 in order to ensure an axial fixation of the spindle 21 in the receiver 13, as shown by way of example in Figure 16.

[0113] [ 1061 The dampers 60 shown in Figures 14 to 16 can, depending on the specific implementation, be provided in a slightly modified form, in differently aligned embodiments, or on the counter member 18, the main beam 15, and / or the running beam 17. Likewise, if necessary, a rotatable assembly or a bearing can be provided with a damper 60 adapted to the then prevailing geometric conditions. Depending on the specific conditions, dampers 60 can also be braced inwards against one another, as shown by way of example in the embodiments according to Figures 14 to 16, or outwards.

[0114]

[0107] It is understood that, in different embodiments, other dampers 60 may also be used accordingly. It is also understood that, if necessary, other securing systems than the anti-rotation device 29 may also be used in different embodiments to design the spindle 21 as a non-rotating spindle.

[0115]

[0108] Damping devices 60 and corresponding axial securing devices can also be used at other locations, in particular also in the embodiments shown in Figures 1 to 4 with a similar design, insofar as the spring packs 61, the elastic bodies 62 or the hydraulic dampers 63 then act accordingly on the nuts 22 and are sufficiently axially secured.

[0116] [ 109 J If necessary, damping means 60 can also be dispensed with, as shown by way of example in Figures 7 and 8. In this case, it must be assumed that, in case of doubt, the bearings 28 and the inherent elasticity of the spindle 21 should have a sufficient damping effect.

[0117]

[0110] Depending on the specific implementation, not only the counter beam 18, as shown by way of example in Figures 1 to 8 and 17 and 18, can be used as the stationary counterpart. If necessary, the pickup spindle drive 40 can also engage the die beam 15 or the die beam 17. The former allows, in particular, that the pickup spindle drive 40 can pull the pickup 13 against the die beam 15 in a direct press if the latter is to serve as a sealing plate 31 of the pickup seal 30, which may allow the application of higher forces. An arrangement of the stationary assembly, for example the nut 22 or the spindle 21 on the running beam 17 could lead to a simplification of the movement sequences, particularly in the case of an indirect press, in particular since the pickup spindle drive 40 is not operated synchronously with the movement of the running beam 17 during pressing.In this regard, the moving assembly can also be mounted on the traveling beam 17. On the other hand, it is conceivable that this problem can also be addressed by other solutions, for example, by separating the pickup spindle drive 40 and the pickup seal 30 during galling, so that the pickup spindle drive 40 can, for example, freely follow the movement of the traveling beam 17.

[0118]

[0111] In the embodiments shown in Figures 1 to 8, the pickup spindle drive 40 also serves as a pickup seal 30 or as an associated sealing spindle drive 32. Depending on the specific situation, this can have the disadvantage that the pickup spindle drive 40 has to apply the sealing forces over a long period of time and in particular during pressing under load, which ultimately places a relatively high load on the spindle-pin arrangement 20 and, in particular, also energetically leads to the questionable situation that the electric motor drives 15 remain under load.

[0119] [1 121 Finally, various measures can be provided to relieve the load on the pickup spindle drive 4(! in this regard. [ 1 13 J For example, it is conceivable that a pickup seal 30 is realized via a wedge connection 34, which presses the sealing plate 31 against the pickup 13 and in this way provides a separate pickup seal 30, as is shown by way of example in Figure 17. If necessary, such a wedge connection 34 can also be effectively designed between the running hole 17 and the pickup 13, in particular for indirect presses. [IM] Depending on the specific design of the wedge connection 34, the sealing force can be changed by adjusting the wedges. On the other hand, it is also conceivable to design the wedges in such a way that when the wedge connection 34 is closed, a certain sealing force is provided which is sufficient for all applications of the respective extrusion press 10.

[0120]

[0115] The wedge connection 34 can, as shown by way of example in Figure 17, be implemented by an electric motor drive 33, which in this embodiment is also realized by a nut-and-socket arrangement, although in this regard, other types of gears are also conceivable in different embodiments. In particular, the wedge connection can be realized, for example, by a type of bayonet lock, which is designed, for example, in a circle around the receiver 13.

[0116] Instead of an electric motor sealing drive 33, any other type of drive by means of which such a mechanical connection, such as the wedge connection 34, can be closed and opened can be used. In particular, for example, cylinder-piston drives or hydraulic drives, in particular hydrostatic drives or even electrohydrostatic drives can be used in this regard.The latter have the particular advantage that they are structurally simple to implement and do not have the disadvantages of hydraulic drives, namely large oil quantities and long and complex oil line paths.

[0121]

[0117] u For example, a breather seal 30 can also be realized by a cylinder-piston drive 35, which, when subjected to pressure, presses the spindle against the sensor 13 and thus against the sealing plate 31, thereby sealing the sensor 13. In a reverse mechanical configuration, the latter can also be achieved by tension, if necessary. A countermovement can also be realized by a cylinder-piston drive 35, as shown exemplarily in Figure 18.

[0122]

[0118] In order to relieve the electric motor drive 50, a locking device 36 can be provided, which in the embodiment shown in Figure 18 engages the bearing body 27. In this respect, it is to be feared that the locking device 36 leads to the contact pressure of the cylinder-piston drive 35 against the spindle housing 15 causing a rotational displacement of the spindle

[0123] 21 over the nuts 22, can be cumulative or alternatively also in the area of ​​the nuts

[0124] 22, a locking mechanism may also be provided. If necessary, the rolling threads 23, which are found in the nuts 22, can also be locked by preventing the rolling elements from rolling.

[0125]

[0119] Self-locking effects can also be used accordingly to enable locking. Furthermore, it is understood that instead of an axial displacement of the bearing body 27, an axial displacement of the rollers 2'2 or a nut carrier 59 can also be used to apply the sealing forces for the retaining seal 30, whereby cylinder-bulb drives can also be used here if necessary.

[0126] Reference symbols:

[0127] 10 Extrusion press 50 electric motor drive

[0128] 1 I Press material 51 Torque motor

[0129] 1 2 Die 52 Drive motor 13 Pickup 53 Electric motor

[0130] 14 Pross stamp 58 intermediate piece

[0131] 15 die bar 59 nut carrier

[0132] 16 tie rods

[0133] 17 Running bar 60 Dtopfiing 18 Counter bar 61 Disc spring package

[0134] 19 matrix carrier 62 elastic body

[0135] 63 hydraulic damper

[0136] 20 spindle-nut arrangement 69 lock nut,

[0137] 21 Spindle 22 Nut 71 Direction of movement

[0138] 23 rolling winds

[0139] 24 thread range 80 ball thread

[0140] 25 bearing area 81 ball

[0141] 26 Separation point 82 Ball nut 27 Bearing body 83 Ball nickel lug

[0142] 28 bearings 84 raceways

[0143] 29 Anti-twist device 90 Roller thread

[0144] 30 Recording 91 : Roller 31 Sealing plate 92 Roller circulation initiator

[0145] 32 Ahdichtspindehrieb 93 Pkmctcnrollcngewindetrieb

[0146] 33 electromotive sealing drive 94 thread

[0147] .34 wedge connection 95 ring

[0148] 35 Cylinder-piston drive 96 Pinion 36 Locking mechanism 97 Roller gear drive

[0149] 98 roller return

[0150] 40 Pickup spindle drive 99 Rdlen

Claims

Patent claims:

1. Extrusion press (10) for pressing a material (II) through a die (12) with a receiver (131) receiving the material (11) and with a press ram (14) displaceable relative to the receiver (13), characterized by an electromechanically rollable and closable receiver seal (130).

2. Extrusion press (10) according to claim 1, characterized in that the receiving seal (30) comprises, on the one hand, the receiver (13) and, on the other hand, a sealing plate (31), which can be acted upon by an electric motor with a sealing force against one another, wherein the sealing plate (31) is preferably arranged on a die beam (15) or on a die beam (117) or is formed in one piece with the latter.

3. Extrusion press (10) according to claim 1 or 2, characterized in that the sealing force can be applied via a sealing spindle drive (32). < Extrusion press ( 10) for pressing a material to be pressed ( 11 ) through a die ( 12 ) with a receiver ( 113 ) receiving a material to be pressed ( II ) and with a relative to the receiver ( 13 ) sci lageibaien f'ressstemp-d { II ), characterized by an electromotive Pickup spindle drive (40).

5. Extrusion press HO) according to claims 3 and 4, characterized in that the sealing spindle drive (32) is the receiver spindle drive (40).

6. Extrusion press 1 10) according to claim 4, characterized in that the receiver seal (30) can be opened and closed hydraulically.

7. Extrusion press (10) according to claim 6, characterized in that the receiver seal (30l) encloses a hydraulic cylinder-piston drive (35), for example with a short-stroke hydraulic cylinder or as an electro-hydrostatic actuator.

8. Extrusion press (10) according to one of claims 4 to 7, characterized in that the receiving spindle drive (40) comprises an electric motor drive (50), in particular a Torque motor (51) and / or a geared motor (52), in particular two electric motors (53) coupled via a gear.

9. Extrusion press (10) according to one of claims 4 to 8, characterized in that the pickup spindle (50) has a spindle-nut arrangement (20) which comprises at least one spindle (21) and at least one nut (22) and which preferably has a roller thread (23) between the spindle (21) and the nut (22).

10. Extrusion press (10) according to claims 8 and 9, characterized in that the spindle (21) and / or the nut (22) is / are rotationally driven by the electric motor drive (50).

11. Extrusion press (10) according to claim 9 or 10, characterized in that the spindle (21 1) and / or the nut (22) is connected via a damping (60) to the receiver (13) and / or to a fixed assembly of the extrusion press (10), such as to Jem Die beam ( 15 ) or on the die beam ( 18 ).

12. Extrusion press (10) according to claim 1 1, characterized in that the damping (60 i on the spindle (21), preferably when this is not rotationally driven, or on the nut (22) is disordered.

13. Extrusion press (10) according to one of claims 9 to 12, characterized in that the Spindle (21.) and / or the nut (122) runs along with the sensor (13).

14. Extrusion press (110) according to one of claims 9 to 13, characterized in that the spindle (21) has a bearing area (25) and a threaded area (24) and the bearing area (25) and the threaded area (24) are preferably designed to be separable from one another.

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