Extrusion and pipe press

Abstract

The present application relates to an extrusion and tube press (1) comprising a press frame consisting of a cylinder beam and a counter-beam connected thereto, in which a movable carriage beam (4) actuated via a displacement main cylinder (2) and at least one displacement secondary cylinder (3), preferably at least two displacement secondary cylinders (3), and a movable block receiver (6) actuated via at least one displacement cylinder (5), preferably at least two displacement cylinders (5), are arranged, wherein the at least one displacement secondary cylinder (3), preferably the at least two displacement secondary cylinders (3), and / or the at least one displacement cylinder (5), preferably the at least two displacement cylinders (5), is / are designed as a multi-surface cylinder.

Description

[0001] The present invention relates to an extrusion and tube press, comprising a press frame consisting of a cylinder beam and a counter beam connected thereto, in which a movable running beam actuatable via a displacement master cylinder and at least one displacement slave cylinder and a movable block receiver actuatable via at least one displacement cylinder are arranged.

[0002] Such extrusion and tube presses, which produce a continuous profile by pressing a blank through a die, are well known and are currently driven by hydraulic double-action cylinders, differential cylinders, or plungers. These can be used in combination in an open hydraulic circuit with appropriate switching on a drive axis to implement different force levels, such as rapid traverse or power traverse. The disadvantage is that the large volume flows returned to the storage tank introduce a large amount of air into the hydraulic fluid, requiring a large tank volume to allow the fluid sufficient time to degas.Furthermore, such drive systems have unfavorable energy efficiency, as the hydraulic power required to move the hydraulic axes must first be generated centrally in a unit with a large fluid volume and then distributed via lines and controlled by appropriate valves. Furthermore, the power not converted into mechanical energy is extracted from the system by cooling devices. A further disadvantage arises from the fact that the use of a cylinder design with only one effective area per direction of movement does not allow for gradual force gradation through interconnection. If this is implemented via multiple cylinders on one axis, the number of components and line paths requiring maintenance increases, as does the required installation space.

[0003] Hybrid drive systems are also known from the prior art, in which electromechanical direct drives are used for rapid movement of the moving beam and the block pick-up, while high forces are generated via hydraulic cylinders. Due to the additional electromechanical drives, such drive systems also have an increased number of components, which leads to higher maintenance, commissioning, and investment costs.

[0004] Further hybrid drive systems are known from European patents EP 3 801 941 B1 and EP 3 880 975 B1, in which, however, the use of the drive concept means that the pendulum volume of the cylinders must be bypassed.

[0005] The use of multi-surface cylinders in hydraulic circuits is generally known. For example, German patent DE 10 2021 212 944 B3 discloses a hydraulic circuit with multiple cylinders in a closed hydraulic circuit, with each cylinder being assigned its own separate motor and pump unit. However, such systems require significant downtime, which negatively impacts the economic efficiency of such a system.

[0006] Against this background, the present invention is based on the object of providing an extrusion and pipe press which is improved compared to the prior art, in particular providing an extrusion and pipe press which enables several hydraulic power stages on the drive axles of an extrusion and pipe press in a compact design using as few pump units as possible. Description of the invention

[0007] According to the invention, the object is achieved by an extrusion and pipe press having the features of patent claim 1.

[0008] This has a press frame consisting of a cylinder beam and a counter beam connected thereto, in which a movable running beam which can be actuated via a displacement master cylinder and at least one displacement slave cylinder, preferably at least two displacement slave cylinders, and a movable block receiver which can be actuated via at least one displacement cylinder, preferably at least two displacement cylinders, are arranged.

[0009] According to the invention, it is provided that the at least one displacement slave cylinder, preferably the at least two displacement slave cylinders, and / or the at least one displacement cylinder, preferably the at least two displacement cylinders, is / are designed as a multi-surface cylinder.

[0010] The billet receiver is only in motion for a short portion of the overall process, so that its displacement by means of the displacement cylinder(s) requires hydraulic power that enables high speed with low force (so-called rapid traverse). During the actual pressing process, only a constant or, to a certain extent, controllable force is required. Hydraulic power is also required for the displacement of the moving beam via its slave displacement cylinders for the short phases of rapid traverse, which enables high speed with low force. During the pressing process, however, these cylinders are operated with high force in parallel to the master displacement cylinder (so-called power traverse). By using multi-surface cylinders, several hydraulic power stages (rapid traverse and power traverse) can be implemented on the respective drive axes of the extrusion and pipe press in a compact design using as few pump units as possible.

[0011] Further advantageous embodiments of the invention are specified in the dependent claims. The features listed individually in the dependent claims can be combined with one another in a technologically expedient manner and can define further embodiments of the invention. Furthermore, the features specified in the claims are further specified and explained in the description, where further preferred embodiments of the invention are presented.

[0012] In an advantageous embodiment, the extrusion and tube press can also comprise a plurality of displacement cylinders or secondary displacement cylinders, via which the moving beam and / or the billet receiver can be actuated. The plurality can advantageously comprise three, more preferably four, and even more preferably five displacement cylinders and / or secondary displacement cylinders, which are designed as multi-surface cylinders.

[0013] In a further advantageous embodiment, the extrusion and pipe press according to the invention further comprises a hydraulic circuit arrangement via which the at least one displacement slave cylinder and / or the at least one displacement cylinder and optionally the displacement master cylinder can be supplied with a hydraulic fluid by a single electric motor-driven hydraulic machine unit. The respective cylinders or axes are thus not hydraulically operated via separate pumps and drives, but are supplied by a central hydraulic circuit, which is preferably based on the pump unit of the displacement master cylinder. This significantly reduces the number of components and line routes requiring maintenance, as well as the required installation space, and also lowers the investment costs and the costs for maintenance and commissioning.

[0014] Preferably, the electric motor-driven hydraulic machine unit comprises at least one positive displacement machine, in particular a pump, driven by at least one electric motor. In a further advantageous embodiment, the electric motor-driven hydraulic machine unit can comprise at least two, more preferably at least three, even more preferably at least four positive displacement machines, in particular pumps, driven by one or more electric motors. The number of positive displacement machines and electric motors depends on the required power that the hydraulic machine unit must provide to the consumers of the extrusion and pipe press in order to ensure smooth operation.

[0015] In a further advantageous embodiment, each of the multi-surface cylinders comprises at least three chambers, each of which is fluidically connected to the hydraulic circuit arrangement via a single inlet and outlet opening. Such a multi-surface cylinder essentially comprises a first cylindrical container (working cylinder) in which a working piston, via which the process force is transmitted to the actuatable moving beam or block receiver, is movably arranged. The piston divides the working cylinder into a main chamber and a first secondary chamber, wherein the piston surface (A1) facing the main chamber corresponds to a multiple of that facing the first secondary chamber (A2). Furthermore, the multi-surface cylinder comprises a second cylindrical container (auxiliary cylinder) in which an auxiliary piston is movably arranged, said auxiliary piston being mechanically coupled to the working piston, for example via a connecting rod.The auxiliary piston divides the auxiliary cylinder in such a way that the multi-surface cylinder has at least one second secondary chamber, wherein the piston surface (A3) facing the second secondary chamber then corresponds to the difference between the two piston surfaces A1 and A2.

[0016] The hydraulic circuit arrangement can advantageously be designed as an open or (partially) closed hydraulic circuit. Particularly in the (partially) closed design, a constant oil volume can be achieved by appropriately dimensioning the multi-surface cylinders, which can significantly reduce air ingress into the hydraulic fluid and thus the tank volume. Compared to a prior art extrusion and pipe press, the tank for the hydraulic fluid can be reduced by at least a factor of 10, more preferably by a factor of 16, which has a particularly advantageous effect on the required installation space of the extrusion and pipe press.

[0017] In the case of a (partially) closed hydraulic circuit, the hydraulic circuit arrangement preferably comprises at least a first main line, at least a second main line and at least two secondary lines, wherein the first main line fluidically connects a main chamber of each multi-surface cylinder and, if applicable, the displacement master cylinder to the hydraulic machine unit, the second main line fluidically connects a first secondary chamber of each multi-surface cylinder to the hydraulic machine unit, and the secondary lines fluidically connect a second secondary chamber of each displacement slave cylinder and of each displacement cylinder to the first main line and the second main line.In this context, it is further preferably provided that the secondary lines each comprise a first branch line, via which the secondary lines are fluidically connected to the first main line, and a second branch line, via which the secondary lines are fluidically connected to the second main line. The respective branch lines can be designed as separate line sections or as integral line sections. In order to achieve advantageous switching options, it is preferably provided that the two branch lines of each secondary line are each provided with a switching valve, preferably a 2 / 2-way valve, via which the secondary lines can be fluidically switched to the first or the second main line.Such a configuration allows the displacement cylinders and the displacement slave cylinders to be controlled independently of each other via their own switching valve block in three different switching modes (forward rapid motion, reverse rapid motion, and forward power motion). In other words, the at least one, preferably the at least two, displacement slave cylinders and / or the at least one, preferably the at least two, displacement cylinders can be controlled synchronously via a single valve switching arrangement.

[0018] In a further advantageous embodiment, the first main line in the fluidic connecting path between the hydraulic machine unit and each first branch line, and the second main line in the fluidic connecting path between the hydraulic machine unit and each second branch line, can each comprise a switchable main valve, preferably a 2 / 2-way valve, via which, for example, the axes can be controlled separately via the hydraulic machine unit. In a further advantageous embodiment, the first and / or second main line can each comprise at least one switchable main valve upstream of the switching valve block.

[0019] In the case of an open hydraulic circuit, the hydraulic circuit arrangement preferably comprises at least a first main line, which is designed, for example, as a so-called pressure line, at least one second main line, which is designed, for example, as a so-called tank line, as well as at least two sub-lines and one secondary line per multi-surface cylinder. The first main line can, if necessary, fluidically connect the sliding master cylinder to the hydraulic machine unit. Preferably, a main chamber of each multi-surface cylinder can be fluidically connected to the hydraulic machine unit via the first sub-line, and a first secondary chamber of each multi-surface cylinder can be fluidically connected to the hydraulic machine unit via the second sub-line, by arranging a switchable main valve, for example a 3 / 3-way valve or a valve arrangement, between the two main lines and the two sub-lines.In this context, it can further preferably be provided that the secondary line comprises a first and a second branch line, wherein the secondary line is fluidically connected to the first partial line via the first branch line and to the second partial line via the second branch line. The respective branch lines can be designed as separate line sections or as integral line sections. Furthermore, it is preferably provided that the two branch lines of each secondary line are each provided with a switching valve, preferably a 2 / 2-way valve, via which the secondary lines can be fluidically connected to the first or second partial line.Such a configuration enables the displacement cylinders and the displacement slave cylinders to be controlled independently of each other in an open hydraulic circuit via their own switching valve block in three different switching modes (rapid forward, rapid reverse and power forward).

[0020] In an advantageous embodiment, the displacement master cylinder includes an expansion tank. This allows the hydraulic fluid to be supplied directly to the displacement master cylinder or displaced back into it, thus reducing the load on the hydraulic machine unit.

[0021] In a further advantageous embodiment, the hydraulic circuit arrangement can comprise a compensation tank that is fluidly connected to the hydraulic machine unit via the first main line. This allows the volume of hydraulic fluid displaced by the displacement master cylinder, for example, during rapid reverse travel, to be transferred directly into such a compensation tank. According to a further aspect, the present invention also relates to the use of the extrusion and tube press according to the invention for the production of metallic products, such as extruded aluminum profiles. Figure designation

[0022] The invention and the technical environment are explained in more detail below with reference to the figures. It should be noted that the invention is not intended to be limited by the exemplary embodiments shown. In particular, unless explicitly stated otherwise, it is also possible to extract partial aspects of the facts explained in the figures and combine them with other components and findings from the present description and / or figures. In particular, it should be noted that the figures and in particular the illustrated proportions are only schematic. The same reference numerals denote the same objects, so that explanations from other figures can be used as a supplement if necessary. They show: Fig. 1 shows an embodiment of the extrusion and tube press according to the invention with a closed hydraulic system; Fig. 2a - 2c three different switching modes using a multi-surface cylinder and a valve arrangement, and Fig. 3 a further embodiment of the extrusion and tube press according to the invention with an open hydraulic system.

[0023] In Fig. 1 shows an embodiment of the extrusion and tube press according to the invention with a hydraulic circuit arrangement.

[0024] The extrusion and pipe press 1 comprises, in the present embodiment, a press frame (not shown) consisting of a cylinder beam and a counter beam connected thereto, in which a movable beam 4 actuated by a displacement master cylinder 2 and two displacement slave cylinders 3 and a movable block receiver 6 actuated by two displacement cylinders 5 are arranged. The two displacement slave cylinders 3 and the two displacement cylinders 5 are designed as multi-surface cylinders and are fluidically connected via a closed hydraulic circuit arrangement 7 comprising several hydraulic lines to a single electric motor-driven hydraulic machine unit 8, which supplies the system with a hydraulic fluid. Depending on the power required for the overall system, the hydraulic machine unit 8 can comprise a plurality of pumps and / or electric motors. Thus, the Fig. 1 schematically illustrated electric motor driven hydraulic machine unit 8 may comprise, for example, four pumps (not shown) driven by a single electric motor, via which the respective multi-surface cylinders can be supplied with the hydraulic fluid.

[0025] Starting from the electric motor-driven hydraulic machine unit 8, the circuit arrangement 7 comprises a first main line 9, via which a main chamber 10 of each multi-surface cylinder and the displacement master cylinder 2 are fluidically connected to the hydraulic machine unit 8. Furthermore, the circuit arrangement 7 comprises a second main line 11, via which a first secondary chamber 12 of each multi-surface cylinder is fluidically connected to the hydraulic machine unit 8. Furthermore, two secondary lines 13, 14 are provided, each of which fluidically connects a second secondary chamber 15 of each displacement slave cylinder 3 and each displacement cylinder 5 to the first main line 9 and the second main line 11.

[0026] The secondary lines 13, 14 each have a first branch line 16, via which the secondary lines 13, 14 are fluidically connected to the first main line 9, and a second branch line 17, via which the secondary lines 13, 14 are fluidically connected to the second main line 11. As can be seen from the illustration in Fig. As shown in Figure 1, a switching valve 18, 19, preferably a 2 / 2-way valve, is arranged in each of the two branch lines 16, 17 of each secondary line 13, 14, via which switching valve the secondary lines 13, 14 can be fluidically connected to the first or second main line 9, 11. Such a configuration enables the two displacement cylinders 5 and the two displacement slave cylinders 3 to be controlled independently of one another in three different switching modes, each via a dedicated switching valve block 20, 21. In an alternative embodiment, each of the multi-surface cylinders can also be designed with a separate switching valve block 20, 21.

[0027] Again Fig. 1, the displacement master cylinder 2 can be extended by a compensating reservoir 22 and / or a tank 23, the latter being fluidically connected to the first main line 9 via a controllable check valve 24. For example, the fluid flow during the switching modification rapid reverse ( Fig. 2b) the volume of hydraulic fluid displaced from the displacement master cylinder 3 is directly collected. Furthermore, a main valve 25, for example a 2 / 2-way valve, can be arranged in a fluidic section of the first main line 9, via which the supply and discharge of hydraulic fluid to the displacement master cylinder 2 can be controlled.

[0028] Furthermore, according to an advantageous embodiment, it can be provided that the first main line 9 in the fluidic connection path between the hydraulic machine unit 8 and each first branch line 16 and the second main line 11 in the fluidic connection path between the hydraulic machine unit 8 and each second branch line 17 each comprise a further main valve 32, 33, which can be designed as a 2 / 2-way valve, via which the first or second main line 9, 11 can then be closed. In the case of the switching modification rapid reverse, as described below in Fig. As shown in Figure 2b, when the main valve 32 is closed, the entire volume flow displaced from the main chamber 10 is pumped via the first branch line 16 and the secondary lines 13, 14 into the second secondary chamber 15. Furthermore, the two main valves 32, 33 allow the respective displacement secondary cylinders 3 and 5, respectively, and thus the respective axes of the extrusion and pipe press 1, to be controlled specifically via the central hydraulic system.

[0029] The following refers to the Fig. 2, which describes three different switching modes using a multi-surface cylinder and the Fig. 1 represents the valve arrangement shown.

[0030] As can be seen from each illustration, each of the multi-surface cylinders has three chambers 10, 12, 15, each of which is fluidically connected to the hydraulic circuit arrangement 7 via a single inlet and outlet opening. The multi-surface cylinder comprises, in detail, a working cylinder 26, in which a working piston 27 is arranged for axial movement. The process force is transmitted to the actuatable moving beam 4 or block receiver 6 via the working piston 27, as can be seen from the illustration in Fig. 1. The working piston 27 divides the working cylinder 26 into the main chamber 10 and the first secondary chamber 12, wherein the piston area 27.1 facing the main chamber 10 is a multiple of that facing the first secondary chamber 12 (piston area 27.2). The multi-surface cylinder also comprises an auxiliary cylinder 28, which, in the embodiment shown here, is arranged axially opposite the working cylinder 26. An auxiliary piston 29 is also arranged in this cylinder so as to be axially movable. As can be seen from the figures, the auxiliary piston 29 is firmly connected to the working piston 27 via a connecting rod 30, so that the working piston 27 and the auxiliary piston 29 are mechanically coupled to one another.The auxiliary piston 29 also divides the auxiliary cylinder 28 into two chambers, whereby for the purpose of explaining the present invention, reference is made only to the second auxiliary chamber 15, which is arranged between the main chamber 10 of the working cylinder 26 and the auxiliary piston 29. In order to achieve constant volume in the multi-surface cylinders, the piston surface 29.1 facing the second auxiliary chamber 15 has an area that essentially corresponds to the difference between the two piston surfaces 27.1 and 27.2. This ensures that - in the case of the operating mode according to . Fig. 2a - the volume of hydraulic fluid supplied to the main chamber 10 corresponds to that which is simultaneously displaced from the two secondary chambers 12, 15.

[0031] In Fig. Figure 2a shows a switching modification in rapid traverse (forward). Here, the hydraulic fluid is pumped via the first main line 9 into the main chamber 10 by the electric motor-driven hydraulic machine unit 8, causing the working piston 27 to move to the left in the direction of the arrow. In this switching modification, the switching valve 18 is closed and the switching valve 19 is open, so that the volume displaced from the second auxiliary chamber 15 reaches the main chamber 10 via the auxiliary lines 13, 14 and the first branch line 16. The volume displaced from the first auxiliary chamber 12, however, is sucked in by the electric motor-driven hydraulic machine unit 8.

[0032] Fig. Figure 2b, on the other hand, shows the rapid traverse (reverse) switching modification. Here, the hydraulic fluid is pumped by the electric motor-driven hydraulic machine unit 8 via the second main line 11 into the first secondary chamber 12, causing the working piston 27 to move to the right in the direction of the arrow. In this switching modification, the switching valve 18 is also closed and the switching valve 19 is open, so that the partial volume flow displaced from the main chamber 10 reaches the second secondary chamber 15 via the first branch line 16 and the secondary lines 13, 14.

[0033] Fig. Figure 2c shows the power gear shift modification. Here, the hydraulic fluid is pumped into the main chamber 10 by the electric motor-driven hydraulic machine unit 8 via the first main line 9 – analogous to the forward rapid gear shift modification – causing the working piston 27 to also move to the left in the direction of the arrow. However, in this shift modification, the switching valve 19 is closed and the switching valve 18 is open, so that the volume displaced from the second auxiliary chamber 15 is combined with the volume displaced from the first auxiliary chamber 12 via the auxiliary lines 13, 14 and the second branch line 17 and is drawn in via the electric motor-driven hydraulic machine unit 8.

[0034] In Fig. 3 shows a further embodiment of the extrusion and tube press 1 according to the invention, which, however, in contrast to the one shown in Fig. 1 has an open hydraulic system. As can be seen from the illustration, a reservoir 34 is provided for the hydraulic fluid, from which the open hydraulic circuit arrangement 7 is supplied with hydraulic fluid via the single electric motor-driven hydraulic machine unit 8. In contrast to the closed hydraulic circuit arrangement 7, however, the hydraulic machine unit 8 has a single direction of rotation, whereby the first main line 9 then forms a pressure line and the second main line 11 forms a tank line. A further difference from the Fig. 1 is that upstream of the respective switching valve block 20, 21 a switchable main valve 35 is arranged, which is designed in such a way that a fluidic connection is established depending on the respective switching modes ( Fig. 2a to 2c) between the partial lines 9.1, 11.1 with the pressure or tank line 9, 11.

[0035] In case of switching modification rapid traverse forward ( Fig. 2a), the hydraulic fluid is pumped via the first main line 9 and the first sub-line 9.1 into the main chamber 10, causing the working piston 27 to move to the left in the direction of the arrow. The switching valve 18 is closed, whereas the switching valve 19 is open, so that the volume displaced from the second secondary chamber 15 reaches the main chamber 10 via the respective secondary lines 13, 14 and the first branch line 16. The volume displaced from the first secondary chamber 12 reaches the reservoir 35 via the second sub-line 11.1 and the second main line 11 (tank line). In this case, the pressure line 9 is fluidly connected to the first sub-line 9.1 via the main valve 35, and the second sub-line 11.1 is fluidly connected to the tank line 11.

[0036] During the switching modification rapid traverse backward ( Fig. 2b), the hydraulic fluid is pumped via the first main line 11 (pressure line) and the second sub-line 11.1 into the first secondary chamber 12, causing the working piston 27 to move to the right in the direction of the arrow. In this switching modification, the switching valve 18 is also closed and the switching valve 19 is open, so that the partial volume flow displaced from the main chamber 10 reaches the second secondary chamber 15 via the first branch line 16 and the respective secondary lines 13, 14. In this case, the pressure line 9 is fluidically connected to the second sub-line 11.1 via the main valve 35, whereby the first sub-line 9.1 can also be fluidically connected to the tank line 11, if necessary.

[0037] When changing gears, power gear according to Fig.2c, the hydraulic fluid is pumped via the first main line 9 (pressure line) and the first sub-line 9.1 - analogous to the switching modification for rapid forward movement - into the main chamber 10, whereby the working piston 27 is also moved to the left in the direction of the arrow. In this switching modification, however, the switching valve 19 is closed and the switching valve 18 is open, so that the volume displaced from the second secondary chamber 15 is combined with the volume displaced from the first secondary chamber 12 via the secondary lines 13, 14 and the second branch line 17 and reaches the reservoir 35 via the second sub-line 11.1 and the second main line 11 (tank line). In this case, the pressure line 9 is fluidly connected to the first sub-line 9.1 via the main valve 35, and the second sub-line 11.1 is fluidly connected to the tank line 11. Reference symbol 1 extrusion and tube press 2 sliding master cylinders 3 sliding slave cylinders 4 Running beam 5 sliding cylinders 6 block receivers 7 hydraulic circuit arrangement 8 Hydromachine unit 9 first main line / pressure line 9.1 first sub-line 10 Main Chamber 11 second main line / tank line 11.1 second sub-line 12 first side chamber 13 Secondary line 14 Secondary line 15 second side chamber 16 first branch line 17 second branch line 18 Switching valve 19 Switching valve 20 Switching valve block / valve circuit arrangement 21 Switching valve block / valve circuit arrangement 22 Expansion tank 23 (Compensation) Tank 24 controllable check valve 25 Main valve 26 working cylinders 27 working pistons 27.1 Piston area 27.2 Piston area 28 auxiliary cylinders 29 auxiliary pistons 29.1 Piston area 30 connecting rod 31 Arrow 32 Main valve 33 Main valve 34 Reservoir 35 Main valve QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] EP 3 801 941 B1

[0004] EP 3 880 975 B1

[0004] DE 10 2021 212 944 B3

[0005]

Claims

[1] Extrusion and tube press (1), comprising a press frame consisting of a cylinder beam and a counter beam connected thereto, in which a movable beam (4) actuatable by means of a displacement master cylinder (2) and at least one displacement slave cylinder (3), preferably at least two displacement slave cylinders (3), and a movable block receiver (6) actuatable by means of at least one displacement cylinder (5), preferably at least two displacement cylinders (5) are arranged, characterized by that the at least one displacement secondary cylinder (3), preferably the at least two displacement secondary cylinders (3), and / or the at least one displacement cylinder (5), preferably the at least two displacement cylinders (5), is / are designed as a multi-surface cylinder. [2] Extrusion and pipe press (1) according to claim 1, further comprising a hydraulic circuit arrangement (7) via which the at least one displacement slave cylinder (3) and / or the at least one displacement cylinder (5) and optionally the displacement master cylinder (2) can be supplied with a hydraulic fluid by a single electric motor-driven hydraulic machine unit (8). [3] Extrusion and tube press (1) according to claim 2, wherein each of the multi-surface cylinders comprises at least three chambers (10, 12, 15), each of which is fluidically connected to the hydraulic circuit arrangement (7) via a single inlet and outlet opening. [4] Extrusion and pipe press (1) according to claim 3, wherein the hydraulic circuit arrangement (7) comprises at least a first main line (9), at least a second main line (11) and at least two secondary lines (13, 14), wherein the first main line (9) fluidically connects a main chamber (10) of each multi-surface cylinder and optionally the displacement master cylinder (2) to the hydraulic machine unit (7), the second main line (11) fluidically connects a first secondary chamber (12) of each multi-surface cylinder to the hydraulic machine unit (8), and the secondary lines (13, 14) fluidically connect a second secondary chamber (15) of each displacement slave cylinder (3) and of each displacement cylinder (5) to the first main line (9) and the second main line (11). [5] Extrusion and pipe press (1) according to claim 4, wherein the secondary lines (13, 14) each comprise a first branch line (16), via which the secondary lines (13, 14) are fluidically connected to the first main line (9), and each comprise a second branch line (17), via which the secondary lines (13, 14) are fluidically connected to the second main line (11). [6] Extrusion and pipe press (1) according to claim 5, wherein the two branch lines (16, 17) of each secondary line (13, 14) are each provided with a switching valve (18, 19), preferably a 2 / 2-way valve, via which the secondary lines (13, 14) can be fluidically switched with the first or the second main line (9, 11). [7] Extrusion and pipe press (1) according to claim 6, wherein the two displacement secondary cylinders (3) and / or the two displacement cylinders (5) can be controlled synchronously via a single valve circuit arrangement (20, 21). [8] Extrusion and pipe press (1) according to claim 6 or 7, wherein the first main line (9) in the fluidic connecting section between the hydraulic machine unit (8) and each first branch line (16) and the second main line (11) in the fluidic connecting section between the hydraulic machine unit (8) and each second branch line (17) each comprise a switchable main valve (32, 33), preferably a 2 / 2-way valve. [9] Extrusion and pipe press (1) according to one of the preceding claims, wherein the electric motor-driven hydraulic machine unit (8) comprises at least one displacement machine driven by at least one electric motor. [10] Extrusion and pipe press (1) according to one of the preceding claims, wherein the displacement master cylinder (2) comprises a compensation tank (22). [11] Extrusion and tube press (1) according to one of the preceding claims 2 to 10, wherein the hydraulic circuit arrangement (7) comprises a compensation tank (23) which is fluidically connected to the hydraulic machine unit (8) via the first main line (9). [12] Use of an extrusion and tube press (1) according to one of the preceding claims for the production of metallic products.

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