Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES, PROFILES OR LIKE SEMI-MANUFACTURED PRODUCTS OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
  • B21C23/00—Extruding metal; Impact extrusion
  • B21C23/21—Presses specially adapted for extruding metal
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B30—PRESSES
  • B30B—PRESSES IN GENERAL
  • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
  • B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES, PROFILES OR LIKE SEMI-MANUFACTURED PRODUCTS OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
  • B21C23/00—Extruding metal; Impact extrusion
  • B21C23/21—Presses specially adapted for extruding metal
  • B21C23/211—Press driving devices
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES, PROFILES OR LIKE SEMI-MANUFACTURED PRODUCTS OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
  • B21C31/00—Control devices for metal extruding, e.g. for regulating the pressing speed or temperature of metal; Measuring devices, e.g. for temperature of metal, combined with or specially adapted for use in connection with extrusion presses

Definitions

• the invention relates to hydraulic extrusion presses with a hydraulic main line driving at least one press die as main consumer and with a hydraulic control pressure system. Likewise, the invention relates to a method for operating a hydraulic extruder with at least one ram in which at least the ram is driven by means of hydraulic oil from a main strand and used to control the extruder, a hydraulic control pressure.
• Extruders of this type are well known in the prior art, with extrusion as such being a forming process in which preferably preheated heavy or light metal blocks, also called bolts, are fed by means of a hydraulic ram through a tool or through a die strand-like semi-finished products, usually called profiles, are pressed.
• the common hydraulic actuators for the ram of these presses consist of a machine-dependent number of main pumps, which can be connected as needed via string valves different consumer groups, such as several cylinders, in which pistons for the hydraulic ram run.
• From the consumer groups can be driven by respective pump circuit and consumer circuits each have an axis with individual axes of other consumer groups at the same time.
• Extruders are built for different press forces, at present in a range between about 10 MN and about 150 MN. From the tool or profile geometry and the pressing process result for the respective machine size different pressing forces and thus pressing pressures and different Verfahrdschreibe for the main axes outside of the pressing process.
• hydraulic extrusion presses usually have a separate control pressure system to ensure that, for example, for a valve control
• CONFIRMATION COPY or pump drives sufficiently reliable at any time a corresponding control pressure is available.
• a hydraulic control pressure is used and which is characterized in that the control pressure also the main line is applied, the non-productive times are reduced.
• the main line volume-controlled so that the precisely required for the operation of the extruder in the shortest possible time volume flows can be made reliable available.
• control pressure system is preferably pressure-controlled or the control pressure is preferably maintained above a minimum pressure, so that the necessary control pressure is reliably available at all times.
• the minimum pressure is preferably a minimum of 80%, preferably a minimum of 90%, of the necessary control pressure to reliably enable control in this manner. It is understood that the pressures in the overall system are limited in a manner known per se to maximum pressures in order to be able to reliably avoid damage to the hydraulic system.
• the main cylinders as already mentioned, side cylinders, pick-up cylinders or a table displacement can be provided as main consumers in the main line.
• hydraulic motors for example for spindle drives, or the like can accordingly be driven via the main line.
• the various main consumers are preferably coupled to one another via consumer groups or consumer controllers, so that correspondingly a group-wise response is also possible. It is understood that the consumer groups or controls can be supplied individually or jointly from the respective main pumps with hydraulic oil, which can be readily implemented by appropriately switched strand valves in a conventional manner.
• control pressure system can - as already known from the prior art per se - valve controls or hydraulic pumps but also secondary consumers that require relatively small volume flows, are operated without further notice.
• secondary consumers may be, for example, block or bolt loaders or block or bolt loader tongs and the like.
• release pressures or the like can be applied via the control pressure system or via the control pressure at appropriate locations.
• the pressurization of the main line with the control pressure can take place in particular via a proportional volume flow control. In this way, it can be ensured, in particular, that the control pressure does not abruptly drop when the main line is acted upon or the control pressure system remains manageable for every operating situation.
• means for proportional volume flow control in the direction of the main line such as suitable throttles or pressure compensators, are preferably provided between the main line and the control pressure system. An inadmissible feeding back of volume flow from the main line in the control pressure system is prevented by at least one check valve with a direction of the main strand opening direction.
• hydraulic oil can be stored in one or more memories and the main branch can be supplied from this memory, these memories or one of these memories.
• the oil volume, which can be provided via the control pressure can be increased considerably, especially with a suitable design of the overall hydraulic system, the memory can be emptied to below the control pressure in the main strand, so that this volume considerable oil volumes are made available to the main strand can be used to reduce the reduction of time, especially in return strokes or similar movement sequences, which take place under low pressure.
• hydraulic oil is stored only from a minimum control pressure of the control pressure in the reservoir, preferably in a separate memory, so that the maintenance of the required control pressure is primarily ensured.
• control pressure system is connected to a memory.
• the memory can be filled with oil, in particular at the times when the control pressure pump or control pressure pumps merely serve to compensate for leakage oil losses or are under little load.
• this oil can also be used as a supply for the control pressure system.
• the accumulator can be arranged between a pressure-adjusting valve in the direction of the control pressure system in the connecting line on the one hand, and proportional flow control means and / or one check valve in the direction of the main line on the other hand.
• the pressure switching valve can be ensured that such a memory is filled only from certain pressures with oil from the control pressure system, while on the means for proportional flow control, the oil from the memory then, as already described above, the main strand can be provided If necessary, both the accumulator and the control pressure system can be secured against volume flow from the main branch via the non-return valve.
• Figure 1 is a perspective view of a hydraulic extruder
• Figure 2 is a schematic representation of essential for explaining the invention
• FIG. 3 is a schematic representation of essential for explaining the invention
• Figure 4 is a schematic representation of essential for explaining the invention
• Figure 5 is a schematic representation of essential for explaining the invention
• Figure 6 is a schematic representation of essential for explaining the invention
• Cutouts of a fifth hydraulic system for an extrusion press are identical to Cutouts of a fifth hydraulic system for an extrusion press.
• the hydraulic extruder 100 shown in Figure 1 comprises a pressing part 1 10 and a pump table 120 with five main pumps 2.
• the pressing part 1 10 comprises a master cylinder 1.1 and a plurality of slave cylinder 1 .1, with which a not shown, but known compression ram can be moved.
• a block or bolt 140 is loaded by means of a block loader, not shown, but also known per se in a hydraulically operated block receiver 150 before the ram presses the block or bolt through a die and the workpiece, the hydraulic extruder 100 by a Opening 160 leaves.
• the hydraulic extruder 100 is a relatively large plant operated by a hydraulic control 130.
• the hydraulic control 130 can be realized in different ways, wherein in FIGS. 2 to 6 corresponding embodiments, but only by way of example for only two main pumps 2, are shown.
• the latter drive main consumers 1, which in these embodiments, the cylinders 1.1 and 1.2 for the ram, a hydraulic motor 1.3 for a spindle drive and a cylinder 1.4 for a pickup, but may include a table shift or other aggregates in other embodiments, via main pumps 2 on , wherein in the figures 2 to 6 respectively a first main pump 2.1 and a second main pump 2.2 are shown, which are via strand valves 3, namely a first strand valve 3.1 and a second strand valve 3.2 respectively hydraulically the main consumers 1, which can be operated by Robinson4.
• a first consumer control 4.1 in which the two cylinders are summarized 1.1 and 1.2 for the ram
• a second load control 4.2 in which the hydraulic motor 1.3 and the transducer cylinder 1.4 are summarized.
• the grouped main consumers can accordingly be supplied with hydraulic oil without any problems. It is understood that the respective main consumers 1 can be combined in any manner to form further consumer controllers 4.
• both main pumps 2, respectively can be selectively connected via the string valves 3 to both consumer controls 4.
• the two main pumps 2 are identical pumps, each of which is driven by a corresponding 200 kW motor and have a flow rate control Q (Quantity) to flow.
• Q Quality
• a number of identical pumps are connected in parallel, depending on the required overall power, whereby the number of main pumps 2 does not necessarily have to correspond to the number of consumer controls 4.
• the pumps and corresponding motors may have different dimensions, for example, up to 1,000 kW pumps or motors, or even larger, with an optimum usually being found depending on the required power and the associated costs. It is understood that the number of main pumps 2, the strand valves 3 and the consumer controls 4 can be adapted to the respective specific requirements.
• Hydraulic main strands 5 each lead to the consumer controls 4, it being understood that several or further main strands 5 may also be provided here.
• the consumer controls 4 empty in a conventional manner in a container, from which in turn the main pumps 2 are fed in a conventional manner, in which case may be provided filtering operations or the like.
• a control pressure system via the control pressure pump 1 1 is fed, which control pressure on control oil for valve control or, for example, for detachment processes, in particular by high start-up or breakaway pressures, and for secondary consumers, such as Block loaders or block loader tongs, which have a small volume consumption available provides.
• a 90 to 100 kW pump or a pump with a 90 to 100 kW motor is used in this embodiment, whose control oil control p (pressure) is carried out under pressure. In this way it can be ensured that at any time sufficient control pressure for safe operation of the valves is available. It is understood that - depending on the specific implementation - other services for the control pressure pump 1 1 or other control pressure pumps can be provided.
• control pressure system is connected via an unnumbered connecting line to the hydraulic main line 5.2, wherein means are provided for proportional flow control in this connection line, which a throttle 13, in this embodiment concretely a manual or proportional throttle a 2-way pressure compensator, 14 include.
• a check valve is provided in the connecting line, which prevents a backlash in the direction of the control pressure system.
• control pressure pump 1 1 conveyed during periods of low flow rate in the hydraulic accumulator 12 in order to provide the corresponding volume to the main consumers 1 available.
• five 200 kW motors for the main pumps 2 and a 100 kW motor for the control pressure pump this can be provided by about one-tenth more power to have more volume of hydraulic oil available, which in particular can be provided for volume-intensive movements.
• the throttle 13 is designed as a hand or proportional throttle
• the embodiment shown in Figure 3 as a throttle 13, an electric proportional directional control valve, so that both the first main strand 5.1 and the second main branch 5.2 accordingly with control pressure or hydraulic oil from the control pressure system can be acted upon.
• each of the corresponding connecting lines is connected to a check valve and a shuttle valve 15 is provided between the two connecting lines to the two main strands 5, which accordingly acts on the 2-way pressure compensator 14.
• a corresponding number of shuttle valves 15 can also be provided in order to tap off the relevant load pressure for the 2-way pressure compensator 14.
• pressure compensators especially 2-way print carriage 14, and connecting lines and check valves may be provided.
• two control pressure pumps 1 1 and 21 are provided, wherein the control pressure pump 1 1 at a high pressure (HD) and the control pressure pump 21 is regulated to a low pressure (ND).
• the high-pressure control pressure system can serve, for example, the locking of valves and any starting or Losr employed within the low control pressure driving pressures of ancillaries or valves can be provided with large displacement.
• Both control pressure strands each have hydraulic accumulators 12, 22 and are in each case via a proportional volume flow control, in this embodiment each consisting of a throttle 13, 23, in particular a manual or proportional throttle, and in each case a 2-way pressure compensator 14, 24th and in each case connected to a check valve with the second main branch 5.2, it being understood that, if necessary, a connection to the first main branch 5.1 or a connection to both main strands 5, for example via the arrangement of Figure 3, may be provided.
• the low-pressure region of the control pressure system is passively engaged, so that only the high-pressure region is effective at high start-up or tear-off loads, but no switching operations are required in the further course of motion.
• control pressure pump 1 1 or by the control pressure flow can also be switched directly to a main consumer 1, as this is done by way of example in the embodiment shown in Figure 5 for the transducer cylinder 1.4.
• the pick-up cylinder 1.4 can also be moved independently of the corresponding main branch 5.2 or of the corresponding second consumer control 4.2.
• two main consumers 1.3 and 1.4 of a main line 5 can be moved simultaneously without further notice.
• the touchdown must then no longer with speed approximately "zero” but can happen on the fly, so at higher speed. Since this minimizes braking and acceleration, the estimated time savings can be between 0.5 and 0.8 seconds, depending on the machine type.
• a pressure switching valve 31 and then a supplementary memory 32 may be provided before then the proportional volume flow control, which at This embodiment in turn consists of a throttle 13 and a 2-way pressure compensator 14 follows.
• the memory 32 is supplied only with hydraulic oil from the control pressure pump 1 1 when a minimum control pressure of the control pressure is reached and maintained. In this respect, the control pressure over a secondary acceleration has priority, so the control is not affected by this.
• the useful volume of the memory 32 relative to the useful volume of the memory 12 can be increased by extending the usable pressure range down, since the memory 32 can be emptied to pressures which are below the control pressure. This reduces the number or size of memory used.
• FIGS. 2 to 6 can also be combined, as is immediately apparent. This applies in particular, for example, to the exemplary embodiment illustrated in FIG. 4, which can be supplemented or alternatively configured in accordance with the embodiments illustrated in FIGS. 3 and / or 6 in the high and / or low pressure region.
• These generally have a throttle 13, for example, implemented by a proportional valve, a proportional throttle or an electric proportional directional control valve, and a 2-way pressure compensator 14.
• first consumer control 140 block or bolt

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Fluid-Pressure Circuits (AREA)
• Extrusion Of Metal (AREA)
• Control Of Presses (AREA)
• Press Drives And Press Lines (AREA)

Priority Applications (7)

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Family Applications (1)

Country Status (9)

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• 2012
  • 2012-05-10 DE DE102012009182A patent/DE102012009182A1/de not_active Withdrawn
• 2013
  • 2013-05-10 EP EP13731660.0A patent/EP2846942B1/de active Active
  • 2013-05-10 ES ES13731660.0T patent/ES2587874T3/es active Active
  • 2013-05-10 PL PL13731660.0T patent/PL2846942T3/pl unknown
  • 2013-05-10 JP JP2015510644A patent/JP6061161B2/ja not_active Expired - Fee Related
  • 2013-05-10 CN CN201380036695.2A patent/CN104428077B/zh not_active Expired - Fee Related
  • 2013-05-10 US US14/399,579 patent/US11407192B2/en active Active
  • 2013-05-10 WO PCT/DE2013/000257 patent/WO2013167111A1/de not_active Ceased
  • 2013-05-10 KR KR1020147034493A patent/KR101701016B1/ko active Active
  • 2013-05-10 DE DE112013002395.4T patent/DE112013002395A5/de not_active Withdrawn

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