WO2013167610A1 - Verfahren und vorrichtung zur adaptiven steuerung einer hydraulischen presse - Google Patents
Verfahren und vorrichtung zur adaptiven steuerung einer hydraulischen presse Download PDFInfo
- Publication number
- WO2013167610A1 WO2013167610A1 PCT/EP2013/059522 EP2013059522W WO2013167610A1 WO 2013167610 A1 WO2013167610 A1 WO 2013167610A1 EP 2013059522 W EP2013059522 W EP 2013059522W WO 2013167610 A1 WO2013167610 A1 WO 2013167610A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- storage bottles
- groups
- press
- hydraulic
- Prior art date
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/16—Control arrangements for fluid-driven presses
- B30B15/163—Control arrangements for fluid-driven presses for accumulator-driven presses
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/04—Accumulators
- F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
- F15B11/064—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam with devices for saving the compressible medium
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/14—Energy-recuperation means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/20—Accumulator cushioning means
- F15B2201/205—Accumulator cushioning means using gas
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/30—Accumulator separating means
- F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/40—Constructional details of accumulators not otherwise provided for
- F15B2201/415—Gas ports
- F15B2201/4155—Gas ports having valve means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
- F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
- F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting output member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
- F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
- F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/88—Control measures for saving energy
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
- Y02P70/10—Greenhouse gas [GHG] capture, material saving, heat recovery or other energy efficient measures, e.g. motor control, characterised by manufacturing processes, e.g. for rolling metal or metal working
Definitions
- the present invention relates to a method for operating a
- Hydraulic press for prototyping, forming, stamping or machining of materials or workpieces such as plastic molding compounds, thermoforming sheets, forgings or the like, with a hydraulic
- the press ram is connected to one or more piston-cylinder units.
- Main working cylinder which generates the pressing force on the large cylindrical piston surface and for lifting the plunger on the smaller annular surface of the piston of the piston-cylinder unit with pressure medium
- the pump and the drive motor must always be designed for the highest power requirements of the press.
- the high-pressure pump can be designed as a variable displacement pump or adjustable hydraulic pump to a continuous adjustment of the flow rate and thus the ram speed adjust. At low pressure, therefore, a large amount of liquid is conveyed, thereby giving the pressing tool a high speed, and vice versa. This is expedient for a fast stroke as rapid traverse and for a high load on the forming process.
- the disadvantage is that the drive energy of the pump constantly changes between zero and a maximum value. This gives considerable burdens to the
- Another drive variant for hydraulic presses is the storage drive.
- a constant-delivery pump driven by an electric motor first conveys into a high-pressure accumulator, from which the working cylinder is then fed with the accumulator pressure via a proportional valve. This high storage pressure is available throughout the working stroke.
- Proportional valve and check valve is connected to a hydraulic accumulator so that the volume of the piston chamber of the cylinder is transmitted in the downward travel of the press ram in the hydraulic accumulator and that stored in the hydraulic accumulator energy via a release valve for powering hydraulic consumers, the lower hydraulic pressure than the Drive unit is working, is used.
- the storage drive has the disadvantage that it must be designed for maximum force of the cylinder.
- variable forces act on the pressing cylinder, depending on the range of parts: namely, small forces in small parts and large forces in large parts. Are printed on a press e.g. If small parts have been driven, which require only small forces, the storage tank must nevertheless be charged to the pressure level required for the maximum force.
- the invention is based on the object, an improved over the prior art, in particular more economical, method for
- Claim 10 solved. Advantageous embodiments and developments, which can be used individually or in combination with each other, are the subject of the dependent claims.
- the device can be used independently but also in particular for carrying out the method.
- the present invention is based on the idea of splitting the downstream of an expansion volume stored by gas compression into groups on storage bottles having different filling pressures.
- one group of storage bottles is opposite to the other group
- gas from an active group of storage bottles may be pumped into a non-active group of storage bottles.
- the active group or groups of storage bottles can thus be filled advantageously by transferring gas quantities to the demand-based boost pressure and operate energy-efficiently.
- the second operating mode brings improved energy efficiency.
- the second mode is also good for a partial load operation.
- a third operating mode is preferred in which first the group of storage cylinders with the lowest filling pressure is connected to the piston chamber of the cylinder and with progressive working stroke, the group of storage cylinders with the next higher filling pressure and / or further group of storage bottles be sequentially operatively connected with gradually higher filling pressures.
- the third operating mode uses the entire available volume of the hydraulic accumulator in cascaded form. By means of a sufficiently high number of groups of pressure-graduated storage cylinders, the volume of the hydraulic accumulator can be ideally adapted to the working stroke characteristic. This has significant energy savings even in full load operation of the press and thus the best possible energy efficiency advantage.
- connection of the next higher pressure-filled group of storage cylinders can be made shortly before reaching the pressure equalization between the accumulator pressure and the working pressure in the piston chamber of the cylinder or falls below the required Häshub für the piston.
- Storage bottles preferred in which the previously used group of storage bottles is closed or via a releasable
- Non-return valve closes automatically; in particular as soon as the accumulator pressure of the connected group of storage bottles is greater than that
- the kinetic energy of a plunger rapid traverse closing movement be slowed down before reaching a working stroke starting position, via the locking cylinder, and the
- Operating mode is not too high intelligence in the controller. All memories are loaded the same and only individual groups of memory bottles are or deselected.
- the control of the second operating mode can preferably be carried out adaptively (self-learning) after the first cycle, if necessary stepwise.
- the third mode in which cascaded, ie multi-level, filled at different pressure levels groups of storage bottles according to the force / displacement / time characteristic of a
- Working stroke of the press can be switched on and off as needed, a high level of intelligence in the adaptive control of the individual pressure levels.
- the present invention also relates to a device
- a hydraulic accumulator preferably adaptable to three operating modes from at least two groups of storage bottles, it is possible that after the start of production a press control, preferably automatically, analyzes the utilization and then correspondingly individual
- mode 1 Groups or even partitions of storage bottles shuts off (mode 1) or when charging at the end of the cycle, the gas in the storage bottles transfuses (mode 2) or the individual groups of storage bottles, adapted to the working stroke, different pressure levels adapts (mode 3). In all three cases advantageously no waiting times or refilling times are required.
- Fig. 1 is a hydraulic circuit diagram according to the prior art
- Fig. 2 is a hydraulic circuit diagram of a first embodiment of
- Fig. 3 is a hydraulic circuit diagram of a second embodiment of the
- Fig. 1 shows the hydraulic circuit diagram of a known from the prior art press.
- the piston 2 is pushed into the piston chamber of the cylinder 3 and the volume in the piston chamber is thereby reduced. This volume must be via a pipe 6 and a
- Security block 5 are performed. From the safety block 5, the volume is passed via the pipe 6 to a port A of a proportional valve 7. During the downward movement of the press, the proportional valve 7 is actuated in the position shown, that is, the volume flow goes from A to T in the pipe 6. About a check valve 9, which is controlled by the load energy, the volume goes into a low pressure - hydraulic accumulator 10.
- the low-pressure hydraulic accumulator 10 is designed in its volume so that it the auxiliary or secondary movements of the press can operate. If this low-pressure hydraulic accumulator 10 is filled, which is signaled by a pressure transducer 11, a switching valve 12 is switched on and the excess volume is discharged into a tank 13.
- the thus stored energy in the low-pressure hydraulic accumulator 10 can be guided via the line with a release valve 16 to the secondary function and used there.
- a secondary function is particularly the hydraulic auxiliary circuit 20 for cylinder units that can work with a pressure level of 40 to 80 bar, as is the case for example in a hydraulic cushion shown as a press table.
- this energy can also be used for a control oil system via a control oil line 15 and a control oil valve 14 as a control oil power supply.
- the low-pressure hydraulic accumulator 10 must be filled for the first charging operation of the low-pressure hydraulic accumulator 10 by a hydraulic pump 19 via a check valve 18 when the recirculation valve 17 is closed until the pressure transducer 1 1 indicates the desired pressure level. This message is a prerequisite for starting the machine.
- Fig. 1 with a dash-dotted line is the representation of a differential circuit with volume utilization, in addition to the
- the advantage is further that thus the pumps do not have to spend the full volume as an energy supply unit that is required as breaking force in the piston chamber of the cylinder 3 and would have to be brought over the entire stroke. Even after the pumps lying valves only have to cope with the residual amount of volume. This brings a cost savings, because the aggregates do not have to be designed as large as usual.
- the piston chamber of the cylinder 3 of the drive unit is connected or connectable via hydraulic pipes 22, a proportional valve 23, a release valve 24 to a high-pressure hydraulic accumulator 25, which besides a hydraulic pump 26 (for charging) has a new,
- the high-pressure hydraulic accumulator 25 is subdivided or subdividable into storage tanks in a plurality of groups 25a, 25b, 25c, ... such that an expansion volume stored in the groups 25a, 25b, 25c ... is directly or indirectly transferred to storage bottles by gas compression a piston accumulator or comparable media separator which supplies the energy required for a working stroke of the press in the form of volume flow and pressure. All storage bottles can be filled to the maximum operating pressure (eg 305 bar).
- the filling pressure in one or more groups of bottles 25a, 25b, 25c is made possible by a suitable gas-side valve control in conjunction with a "compressor operation" of the piston accumulator. .. lower.
- groups 25a, 25b, 25c ... have proven to be suitable for storage bottles which are filled in a graduated manner to a lowest possible pressure, which is adapted to a respective production requirement, primarily by the working pressure profile and withdrawal volume, in particular with regard to energy efficiency.
- one group 25a, ... of storage bottles can be shut off from the other group 25b, ... on storage bottles. If smaller forces are required on the plunger, individual or a plurality of groups 25a, 25b, 25c, ... can be closed to storage bottles via shut-off valves. Thus, the pressure level in the memory 25 drops more upon removal. This is illustrated by means of an example: If one were to operate a memory 25 with only two instead of eighteen memory bottles, the pressure level would be at max.
- Nitrogen or similar gas with which the storage bottles are prefilled may be transferred from an active group 25a ... to storage bottles into a non-active group 25b. . be pumped to storage bottles.
- the pressure level is lowered, for example, in a group of bottles 25a ....
- the active piston accumulator is thus better adapted to the required pressure level. Pressure losses are lower.
- the "superfluous" nitrogen is located in, for example, two groups of bottles 25b and 25c, which are shut off, in which the nitrogen pressure is then at a higher level (eg 350 bar max.)
- a higher level eg 350 bar max.
- a third operating mode is preferred, in which first the group 25a ... is connected to storage cylinders with the lowest filling pressure with the piston chamber of the cylinder and with progressing working stroke, the group 25b ... to storage bottles with the next higher Filling pressure and / or further group 25c ... on
- a working cycle can be run at full load by the first Third of the working stroke from the first group 25a ... is taken (pressure drop from 105 bar to 90 bar), the second third of the second group 25b ... with a pressure drop from 205 bar to 180 bar and the third third from the third group 25c ... with a pressure drop from 305 bar to 275 bar.
- the subsequent storage charge then takes place in the first group 25a ... from 90 bar to 105 bar, in the second group 25b ... from 180 bar to 205 bar and in the third group 25c ... from 275 bar to 305 bar. This then corresponds to a mean pressure of 193 bar instead of the usual 290 bar in the
- Fig. 3 shows an alternative embodiment of the invention. in the
- Cylinder units that can work with a pressure level of 40 to 80 bar, as for example in hydraulic cushion for a
- Press table is the case, provided.
- this system also offers the possibility to recycle energy back into the groups 25a, 25b, 25c, ... to storage bottles. If, for example, the plunger 1 of the press is delayed during the pressing process, this nowadays takes place via the return cylinders in that the control valves narrow the oil flow and thus convert the energy into heat.
- the brake pressure is for example 140 bar in the return cylinders.
- FIG. 4 shows the pressure profile ABC with groups 25a, 25b, 25c according to the invention on storage bottles. It is shown as in the working process of a press at each cycle on the time axis from zero to the
- a third operating mode provides a cascaded connection and disconnection of individual groups 25a, 25b, 25c, ... to storage bottles.
- the memory 25 can be filled with a lower pressure of for example 70 bar.
- Example 2 with a new design Example 3 with a new design:
- Preload pressure 70 bar preload pressure 140 bar
- the accumulator When the memory is designed for a preload pressure of 70 bar, the accumulator will be seventeen times larger than in the previous design.
- FIG. 5 shows the lower operating pressure as a function of active groups 25a, 25b, 25c,... Of nitrogen bottles.
- the present invention is finally based on the following
- an adaptive (self-learning) system is offered.
- the press control in a press according to the invention preferably automatically, for example after a certain number of (x) cycles found that fewer storage bottles in the hydraulic accumulator (gas storage) would be sufficient, and reduces the Filling pressure in one or more (X) bottles or groups of storage bottles according to one of the operating modes described above.
- the following calculation example illustrates the energy balance technical advantage:
- Maximum charge to 290 bar with 40 bottles means 40 bottles to lift from 250 to 290 bar is more expensive than in a lower pressure range or fewer bottles.
- Hydraulic accumulator comprising at least two
- a, b, c are pressure curve curves of groups 25a, 25b, 25c according to the invention
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/399,856 US20150158262A1 (en) | 2012-05-10 | 2013-05-07 | Method and device for adaptively controlling a hydraulic press |
RU2014149769A RU2014149769A (ru) | 2012-05-10 | 2013-05-07 | Способ и устройство для адаптивного управления гидравлическим прессом |
EP13721344.3A EP2846993A1 (de) | 2012-05-10 | 2013-05-07 | Verfahren und vorrichtung zur adaptiven steuerung einer hydraulischen presse |
KR1020147034382A KR20150007342A (ko) | 2012-05-10 | 2013-05-07 | 유압 프레스를 적합하게 제어하기 위한 방법 및 디바이스 |
JP2015510799A JP2015521109A (ja) | 2012-05-10 | 2013-05-07 | 液圧式のプレスを適応制御する方法及び装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012104124A DE102012104124A1 (de) | 2012-05-10 | 2012-05-10 | Verfahren und Vorrichtung zur adaptiven Steuerung einer hydraulischen Presse |
DE102012104124.5 | 2012-05-10 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2013167610A1 true WO2013167610A1 (de) | 2013-11-14 |
Family
ID=48326310
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2013/059522 WO2013167610A1 (de) | 2012-05-10 | 2013-05-07 | Verfahren und vorrichtung zur adaptiven steuerung einer hydraulischen presse |
Country Status (7)
Country | Link |
---|---|
US (1) | US20150158262A1 (de) |
EP (1) | EP2846993A1 (de) |
JP (1) | JP2015521109A (de) |
KR (1) | KR20150007342A (de) |
DE (1) | DE102012104124A1 (de) |
RU (1) | RU2014149769A (de) |
WO (1) | WO2013167610A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107672222A (zh) * | 2017-11-02 | 2018-02-09 | 中科聚信洁能热锻装备研发股份有限公司 | 一种液压机的高效节能回程缸 |
WO2022157360A1 (de) | 2021-01-25 | 2022-07-28 | Langenstein & Schemann Gmbh | Hydraulische umformmaschine zum pressen von werkstücken, insbesondere schmiedehammer, und verfahren zum betreiben einer hydraulischen umformmaschine, insbesondere eines schmiedehammers |
EP4043197A1 (de) * | 2016-06-14 | 2022-08-17 | Voith Turbo S.r.l. | Verfahren und system zur steuerung eines aktuators eines stössels einer presse |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105114376A (zh) * | 2015-09-17 | 2015-12-02 | 天津市天锻压力机有限公司 | 一种作用于热成型液压机上顶出缸的液压控制系统 |
CN106015124A (zh) * | 2016-07-22 | 2016-10-12 | 中聚信海洋工程装备有限公司 | 一种液压泵与高压蓄能器叠加供压的液压快锻机组 |
IT201700068317A1 (it) * | 2017-06-20 | 2018-12-20 | Hydromec S R L | Impianto di regolazione automatica del caricamento di accumulatori di pressione, e relativo metodo di regolazione, per pressa oleodinamica |
DE102018107245A1 (de) * | 2018-03-27 | 2019-10-02 | Moog Gmbh | Pressenantrieb mit Energierückgewinnung |
BR112021003358A2 (pt) * | 2018-10-01 | 2021-05-11 | Salvagnini Italia S.P.A. | máquina para trabalhar folha metálica, e, método para acionar uma pluralidade de ferramentas de trabalho |
CN109175183B (zh) * | 2018-10-16 | 2024-02-06 | 南京迪威尔高端制造股份有限公司 | 大型模锻液压机混合动力液压传动系统及方法 |
US20230160403A1 (en) * | 2020-03-23 | 2023-05-25 | Advanced Energy Storage, Llc | Deployable energy supply and management system |
CN114439786A (zh) * | 2021-12-30 | 2022-05-06 | 江苏盛鑫气动液压设备有限公司 | 小型液压打镁系统 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE626344C (de) * | 1932-12-10 | 1936-02-24 | Vladimir Vltavsky | Hydraulische Presse |
DE4436666A1 (de) * | 1994-10-13 | 1996-04-18 | Rexroth Mannesmann Gmbh | Hydraulisches Antriebssystem für eine Presse |
DE19528558B4 (de) | 1995-08-03 | 2006-10-05 | Dieffenbacher Gmbh + Co. Kg | Verfahren zum Betreiben einer hydraulischen Presse und Vorrichtung zur Durchführung des Verfahrens |
EP1967349A1 (de) * | 2007-03-08 | 2008-09-10 | Robert Bosch GmbH | Schließeinheit |
WO2011135522A2 (en) * | 2010-04-28 | 2011-11-03 | Abraham Bauer | Hydraulic power converter |
WO2012031970A1 (de) * | 2010-09-06 | 2012-03-15 | Eisenmann Siegfried A | Hydrostatischer antrieb für ein kraftfahrzeug |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2478013A (en) * | 1942-02-09 | 1949-08-02 | Fred M Roddy | Process for preparing and fashioning thermoplastic and thermosetting materials |
US3176466A (en) * | 1961-12-01 | 1965-04-06 | American Brake Shoe Co | Hydraulic press |
DE3531526A1 (de) * | 1985-09-04 | 1987-03-12 | Graebener Theodor Pressensyst | Mechanische presse, insbesondere kniehebelpresse |
CA2539642A1 (en) * | 2003-10-09 | 2005-04-21 | The Coe Manufacturing Company | Platen press |
WO2012100324A1 (en) * | 2011-01-28 | 2012-08-02 | Husky Injection Molding Systems Ltd. | Molding machine having auxiliary ejection-assistance assembly configured to apply additional ejection force |
CN102364120A (zh) * | 2011-06-30 | 2012-02-29 | 天津市天锻压力机有限公司 | 活塞式蓄能器控制液压系统 |
-
2012
- 2012-05-10 DE DE102012104124A patent/DE102012104124A1/de not_active Withdrawn
-
2013
- 2013-05-07 JP JP2015510799A patent/JP2015521109A/ja active Pending
- 2013-05-07 US US14/399,856 patent/US20150158262A1/en not_active Abandoned
- 2013-05-07 WO PCT/EP2013/059522 patent/WO2013167610A1/de active Application Filing
- 2013-05-07 RU RU2014149769A patent/RU2014149769A/ru unknown
- 2013-05-07 EP EP13721344.3A patent/EP2846993A1/de not_active Withdrawn
- 2013-05-07 KR KR1020147034382A patent/KR20150007342A/ko not_active Application Discontinuation
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE626344C (de) * | 1932-12-10 | 1936-02-24 | Vladimir Vltavsky | Hydraulische Presse |
DE4436666A1 (de) * | 1994-10-13 | 1996-04-18 | Rexroth Mannesmann Gmbh | Hydraulisches Antriebssystem für eine Presse |
DE19528558B4 (de) | 1995-08-03 | 2006-10-05 | Dieffenbacher Gmbh + Co. Kg | Verfahren zum Betreiben einer hydraulischen Presse und Vorrichtung zur Durchführung des Verfahrens |
EP1967349A1 (de) * | 2007-03-08 | 2008-09-10 | Robert Bosch GmbH | Schließeinheit |
WO2011135522A2 (en) * | 2010-04-28 | 2011-11-03 | Abraham Bauer | Hydraulic power converter |
WO2012031970A1 (de) * | 2010-09-06 | 2012-03-15 | Eisenmann Siegfried A | Hydrostatischer antrieb für ein kraftfahrzeug |
Non-Patent Citations (1)
Title |
---|
See also references of EP2846993A1 |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP4043197A1 (de) * | 2016-06-14 | 2022-08-17 | Voith Turbo S.r.l. | Verfahren und system zur steuerung eines aktuators eines stössels einer presse |
CN107672222A (zh) * | 2017-11-02 | 2018-02-09 | 中科聚信洁能热锻装备研发股份有限公司 | 一种液压机的高效节能回程缸 |
US10926502B2 (en) * | 2017-11-02 | 2021-02-23 | Zhongkejuxin Clean Energy & Hot Forging Equipment Research And Development Co., Ltd. | Efficient energy-saving return cylinder of hydraulic press and working method thereof |
CN107672222B (zh) * | 2017-11-02 | 2023-07-25 | 中科聚信洁能热锻装备研发股份有限公司 | 一种液压机的高效节能回程缸 |
WO2022157360A1 (de) | 2021-01-25 | 2022-07-28 | Langenstein & Schemann Gmbh | Hydraulische umformmaschine zum pressen von werkstücken, insbesondere schmiedehammer, und verfahren zum betreiben einer hydraulischen umformmaschine, insbesondere eines schmiedehammers |
DE102021101539A1 (de) | 2021-01-25 | 2022-07-28 | Langenstein & Schemann Gmbh | Hydraulische Umformmaschine zum Pressen von Werkstücken, insbesondere Schmiedehammer, und Verfahren zum Betreiben einer hydraulischen Umformmaschine, insbesondere eines Schmiedehammers |
Also Published As
Publication number | Publication date |
---|---|
RU2014149769A (ru) | 2016-07-10 |
KR20150007342A (ko) | 2015-01-20 |
JP2015521109A (ja) | 2015-07-27 |
DE102012104124A1 (de) | 2013-11-14 |
EP2846993A1 (de) | 2015-03-18 |
US20150158262A1 (en) | 2015-06-11 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2846993A1 (de) | Verfahren und vorrichtung zur adaptiven steuerung einer hydraulischen presse | |
EP1318906B1 (de) | Steuervorrichtung für eine hydraulische presse sowie verfahren zu deren betrieb | |
EP0615837A1 (de) | Verfahren zur Regelung des Antriebs einer hydraulischen Presse und Vorrichtung zur Durchführung des Verfahrens | |
DE102006058630B4 (de) | Elektrohydraulische Pressenhaupt- oder Nebenantriebseinrichtung, insbesondere elektrohydraulischer Ziehkissenantrieb | |
EP2846994B1 (de) | Verfahren zum betreiben einer hydraulischen presse und eine hydraulische presse | |
EP0641644A1 (de) | Verfahren zur Regelung des Antriebs einer hydraulischen Presse und Vorrichtung zur Durchführung des Verfahrens | |
EP0972631B1 (de) | Hydraulischer Antrieb für eine Presse | |
EP2838719B1 (de) | Maschinenpresse | |
EP2104578B1 (de) | Ziehkissenvorrichtung mit modularem hybridantrieb | |
EP2846942B1 (de) | Hydraulische strangpresse sowie verfahren zum betrieb einer hydraulischen strangpresse | |
DE102008003106A1 (de) | Verfahren zum energiesparenden Betreiben einer hydraulischen Presse und eine energiesparende und wartungsarme hydraulische Presse | |
DE10393056B4 (de) | Hydraulische Steuerung in einem hydraulischen System, insbesondere für den Betrieb einer Schrottschere | |
WO2009026893A1 (de) | Antriebssystem für hydraulische pressen | |
EP0692327B1 (de) | Antrieb für hydraulische Pressen mit hoher Hubzahl | |
DE19528558B4 (de) | Verfahren zum Betreiben einer hydraulischen Presse und Vorrichtung zur Durchführung des Verfahrens | |
EP0629455B1 (de) | Stauchpressenhauptantrieb | |
DE202012101725U1 (de) | Vorrichtung zur adaptiven Steuerung einer hydraulischen Presse | |
EP2335840B1 (de) | Hydraulischer Pressenantrieb | |
EP3056291B1 (de) | Presse mit Schnittschlagdämpfung | |
DE102012019665A1 (de) | Hydraulische Steueranordnung und Presse mit einer derartigen Steueranordnung | |
DE102018105228A1 (de) | Vorrichtung und Verfahren zum Expandieren und gleichzeitigen Befüllen von Behältnissen | |
AT520171B1 (de) | Hydrauliksystem für eine Formgebungsmaschine | |
WO2015177285A1 (de) | Strangpresse mit hydraulikantrieb | |
DE102016118854A1 (de) | Elektrohydraulische Antriebseinheit | |
DE202012101726U1 (de) | Hydraulische Presse |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 13721344 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2015510799 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 14399856 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: 20147034382 Country of ref document: KR Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2013721344 Country of ref document: EP |
|
ENP | Entry into the national phase |
Ref document number: 2014149769 Country of ref document: RU Kind code of ref document: A |