EP2846942B1 - Hydraulische strangpresse sowie verfahren zum betrieb einer hydraulischen strangpresse - Google Patents

Hydraulische strangpresse sowie verfahren zum betrieb einer hydraulischen strangpresse Download PDF

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Publication number
EP2846942B1
EP2846942B1 EP13731660.0A EP13731660A EP2846942B1 EP 2846942 B1 EP2846942 B1 EP 2846942B1 EP 13731660 A EP13731660 A EP 13731660A EP 2846942 B1 EP2846942 B1 EP 2846942B1
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EP
European Patent Office
Prior art keywords
control pressure
control
pressure
hydraulic
main
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP13731660.0A
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German (de)
English (en)
French (fr)
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EP2846942A1 (de
Inventor
Klaus POGGENPOHL
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SMS Group GmbH
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SMS Group GmbH
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Classifications

    • 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 OR PROFILES, 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
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, 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 OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C31/00—Control devices, 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 extruders with a hydraulic main line driving at least one ram as the 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 are known from the prior art, for example from EP 0 027 743 A1 Well known, the extrusion as such is a forming process in which preferably preheated heavy or light metal blocks, also called bolts, with the aid of a hydraulic press ram by a tool or by a die to 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 switched on demand by strand valves different consumer groups, such as several cylinders, in which piston 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.
  • the tool or profile geometry and the pressing process result in different press forces and thus pressing pressures and different travel pressures for the main axes outside the pressing process for the respective machine size.
  • hydraulic extrusion presses usually have a separate control pressure system to ensure that, for example, for a valve control 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 acts on the main strand will, the non-productive time will be reduced.
  • control oil for example, in return strokes, where usually large volumes must be moved at lower pressures, even with cautious estimation or as already shown in the first experiments, lead to side-time reductions between 0.5 and 0.8 seconds or more . It is assumed that further reductions in the non-productive times can be achieved in other sequences of motion, so that significant reductions in overall secondary times can be achieved in this respect, especially without having to significantly increase the overall design of the extruder, in particular with regard to its performance characteristics a suitably equipped extruder is relatively low, since ultimately only relatively inexpensive additional components, such as a supplementary connecting line and any valves or buffer for oil must be used.
  • the non-productive times can be shortened in this way without increasing the drive power required or to be provided for the pressing process, which is correspondingly inexpensive.
  • the main line is volume-controlled, so that the volume flows required precisely for the operation of the extrusion press in the shortest possible time can be reliably made 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 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 auxiliary consumers who require relatively small volume flows, are operated without further notice.
  • auxiliary consumers can 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 loading of the main line with the control pressure can be effected in particular via a proportional volume flow control.
  • 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.
  • 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 acted upon 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 advantageously for back-offs or similar movements, which take place under low pressure, advantageously for the reduction of time.
  • hydraulic oil is stored only from a minimum control pressure of the control pressure in the memory, 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.
  • at least parts of the oil stored in the memory of the control pressure system are also made available to the main branch under corresponding operating conditions.
  • At least one memory is arranged in a connecting line between the main line and the control pressure system.
  • the memory between a pressure-adjusting valve in the direction of the control pressure system in the connecting line on the one hand and means for proportional flow control and / or a check valve in the direction of the main strand on the other hand can be arranged.
  • 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.
  • hydraulic extruder 100 comprises a pressing member 110 and a pump table 120 with five main pumps 2.
  • the pressing member 110 includes 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 controller 130.
  • the hydraulic control 130 can be realized in different ways, wherein FIGS. 2 to 6 corresponding embodiments, but exemplified 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 , where in the FIGS. 2 to 6 in each case 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 consumer controls 4.
  • these embodiments have a first consumer control 4.1, in which the two cylinders are summarized 1.1 and 1.2 for the ram, and 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 synchronously with hydraulic oil without further ado. 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 can be switched on via the string valves 3, in each case two consumer controllers 4, respectively.
  • the two main pumps 2 are identical pumps, which are each 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.
  • main strands 5 To the consumer controls 4 lead hydraulic main strands 5, it being understood that here, if necessary, more or more main strands 5 can be provided.
  • 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 11 is fed, which control pressure on control oil for valve control or, for example, for detachment processes, in particular by high start-up or tear-open, and for secondary consumers, such as block loaders or block loader, 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 concrete implementation - other services for the control pressure pump 11 or other control pressure pumps can be provided.
  • the control pressure system is connected via a not numbered 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 and a 2-way pressure compensator, 14th include.
  • a check valve is provided in the connecting line, which prevents a backlash in the direction of the control pressure system.
  • a hydraulic accumulator 12 is also provided, in which hydraulic oil of the control pressure system can be cached and retrieved as needed.
  • control pressure pump 11 to promote even during times 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 manual or proportional throttle
  • 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.
  • shuttle valves 15 may be provided to tap the relevant load pressure for the 2-way pressure compensator 14.
  • pressure compensators in particular 2-way print carriage 14, and connecting lines and check valves may be provided.
  • the arrangement after FIG. 4 corresponds to the arrangement according to their ability to control pressure to the main strands 5 available FIG. 2 , so that here too the control pressure can only be made available to the second main branch 5.2, but in both embodiments via the second strand valve 3.2 hydraulic oil from the second main pump 2.2 and the first main strand 5.1 can be provided so that accordingly both main pumps 2 for the first consumer control 4.1 can be used while the control pressure or the hydraulic oil originating from the control pressure system is simultaneously available to the second consumer control 4.2.
  • control pressure pumps 11 and 21 are provided, wherein the control pressure pump 11 is controlled at a high pressure (HD) and the control pressure pump 21 to a low pressure (ND).
  • HD high pressure
  • ND low pressure
  • the control pressure system with high pressure for example, the locking of valves and any start-up or breakaway pressures are used, while above the low control pressure driving pressures of ancillaries or valves can be provided with large adjustment paths.
  • 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, 24 and one each Check valve connected to 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 according to FIG. 3 , can be provided.
  • 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, 24 and one each Check valve connected to 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 according to FIG. 3 , can be provided.
  • the low pressure range of the control pressure system is passively switched on so that at high start-up or Losr ultimately only the high-pressure region is effective in the further course of motion, however, no switching operations are required.
  • the additional, provided by the control pressure pump 11 and by the control pressure flow can also be switched directly to a main consumer 1, as this example in the in FIG. 5 illustrated embodiment for the transducer cylinder 1.4 is done.
  • 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 pre-acceleration of the spar during return stroke, before a pickup for the ride in the "total differential" touches to take the strut for the rest of stroke, done accordingly.
  • the touchdown must then no longer be done with speed approaching "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.
  • the reservoir 32 is supplied with hydraulic oil from the control pressure pump 11 only when a minimum control pressure of the control pressure is reached and maintained.
  • 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 be combined, as immediately apparent.
  • These generally have a throttle 13, for example, implemented by a proportional valve, a proportional throttle or an electric proportional directional valve, and a 2-way pressure compensator 14.

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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)
EP13731660.0A 2012-05-10 2013-05-10 Hydraulische strangpresse sowie verfahren zum betrieb einer hydraulischen strangpresse Active EP2846942B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012009182A DE102012009182A1 (de) 2012-05-10 2012-05-10 Hydraulische Strangpresse sowie Verfahren zum Betrieb einer hydraulischen Strangpresse
PCT/DE2013/000257 WO2013167111A1 (de) 2012-05-10 2013-05-10 Hydraulische strangpresse sowie verfahren zum betrieb einer hydraulischen strangpresse

Publications (2)

Publication Number Publication Date
EP2846942A1 EP2846942A1 (de) 2015-03-18
EP2846942B1 true EP2846942B1 (de) 2016-06-08

Family

ID=48699473

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Application Number Title Priority Date Filing Date
EP13731660.0A Active EP2846942B1 (de) 2012-05-10 2013-05-10 Hydraulische strangpresse sowie verfahren zum betrieb einer hydraulischen strangpresse

Country Status (9)

Country Link
US (1) US11407192B2 (ja)
EP (1) EP2846942B1 (ja)
JP (1) JP6061161B2 (ja)
KR (1) KR101701016B1 (ja)
CN (1) CN104428077B (ja)
DE (2) DE102012009182A1 (ja)
ES (1) ES2587874T3 (ja)
PL (1) PL2846942T3 (ja)
WO (1) WO2013167111A1 (ja)

Families Citing this family (7)

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DE102016214767A1 (de) 2016-02-16 2017-08-17 Sms Group Gmbh Gleichgangzylinder für Strangpressanlagen
CN106180234A (zh) * 2016-07-20 2016-12-07 佛山市业精机械制造有限公司 一种低速铝型材挤压机
CN107701528B (zh) * 2017-10-31 2023-11-03 中国重型机械研究院股份公司 提高挤压机挤压筒动作速度的控制方法及系统
CN107605872B (zh) * 2017-10-31 2023-10-10 中国重型机械研究院股份公司 减少挤压机固定非挤压时间的控制方法及系统
US11193177B2 (en) * 2018-06-28 2021-12-07 Indian Oil Corporation Limited Process for recovering higher sugar from biomass
JP7234621B2 (ja) * 2018-12-21 2023-03-08 Ｕｂｅマシナリー株式会社 押出プレス装置のメインポンプユニット及びメインポンプユニットの制御方法
DE102020207274B3 (de) * 2020-06-10 2021-10-14 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulik-Aggregat für eine Strangpresse, Baureihe derartiger Aggregate und Strangpresse mit dem Hydraulik-Aggregat

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Also Published As

Publication number Publication date
US11407192B2 (en) 2022-08-09
US20150090132A1 (en) 2015-04-02
DE112013002395A5 (de) 2015-01-15
WO2013167111A1 (de) 2013-11-14
CN104428077B (zh) 2017-03-08
ES2587874T3 (es) 2016-10-27
CN104428077A (zh) 2015-03-18
KR20150008469A (ko) 2015-01-22
EP2846942A1 (de) 2015-03-18
PL2846942T3 (pl) 2016-12-30
DE102012009182A1 (de) 2013-11-14
JP2015520028A (ja) 2015-07-16
KR101701016B1 (ko) 2017-01-31
JP6061161B2 (ja) 2017-01-18

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