EP1318906B1 - Steuervorrichtung für eine hydraulische presse sowie verfahren zu deren betrieb - Google Patents

Steuervorrichtung für eine hydraulische presse sowie verfahren zu deren betrieb Download PDF

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Publication number
EP1318906B1
EP1318906B1 EP01956735A EP01956735A EP1318906B1 EP 1318906 B1 EP1318906 B1 EP 1318906B1 EP 01956735 A EP01956735 A EP 01956735A EP 01956735 A EP01956735 A EP 01956735A EP 1318906 B1 EP1318906 B1 EP 1318906B1
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EP
European Patent Office
Prior art keywords
pressure
valve
line
press
reservoir
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Expired - Lifetime
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EP01956735A
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German (de)
English (en)
French (fr)
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EP1318906A1 (de
Inventor
Matthias Hahn
Arno MÖHN
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Laeis GmbH
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Laeis GmbH
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    • 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
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure
    • 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
    • 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
    • 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
    • B30B15/22—Control arrangements for fluid-driven presses controlling the degree of pressure applied by the ram during the pressing stroke
    • 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
    • F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • F15B11/0325—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters the fluid-pressure converter increasing the working force after an approach stroke
    • 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
    • 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
    • F15B2211/21—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
    • F15B2211/20—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
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
    • 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
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members
    • 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
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Definitions

  • the invention relates to a hydraulic press referred to in the preamble of claim 1, to a method for their operation according to the preamble of claim 8 and to a use according to claim 11.
  • Such hydraulic presses are used when it comes to molding or forming workpieces. Also for cutting operations hydraulic presses are used. The required force of the hydraulic press depends on the workpiece. In the ceramic industry, presses are used whose pressing force is 20,000 kN or more. In view of an economical production while the cycle time for a pressing operation should be as short as possible. Clock rates of 20 strokes per minute are indicative. By pressing force and cycle time, the energy to be expended is determined in hydraulic presses so the performance of pumps and these pumps driving electric motors. In hydraulic presses according to the prior art and memory are applied, so accumulator or flywheels.
  • a hydraulic press of this kind is from the DE-A1-43 20 213 known.
  • a pressure medium reservoir is present, which is loaded during the return stroke of the press and is used in the advancement of the pressing tool for driving. Energy can thus be saved with the main drive.
  • Out JP-A-63 256 300 is known a press that is operated with a multi-stage pressure converter. After a first pressing operation with low pressure, the hydraulic oil is drained into the tank. Then a second pressing operation with high pressure takes place. An energy recovery is therefore not possible here.
  • the invention has for its object to provide a hydraulic press, the hydraulic control is constructed so that in the sum of the energy consumption is reduced, without causing an increased expenditure on equipment is needed.
  • the control should also be applicable to a press with Plungerzylindem.
  • Fig. 1 1 means a press cylinder, which is assigned a reservoir 2 for the hydraulic medium.
  • Reference numeral 3 denotes a valve group including a series of valves which will be mentioned later. Over a Cylinder line 4, the hydraulic medium between the press cylinder 1 and the valve group 3 is promoted.
  • a storage line 5 is connected to the valve group 3.
  • a hydraulic pump 6 which is driven by an electric motor, which is not shown here, promotes hydraulic medium.
  • a pressure fluid accumulator 7 With the extending within the valve group 3 storage line 5 is a pressure fluid accumulator 7 in conjunction. This also means that the hydraulic pump 6, the hydraulic medium in the accumulator 7 is able to promote.
  • a non-illustrated check valve may be arranged to relieve the hydraulic pump 6 from the pressure prevailing in the pressure accumulator 7 pressure when the hydraulic pump 6 is not running.
  • a pressure converter 9 is connected to the valve group 3, which can act according to the general inventive concept on the one hand as a pressure intensifier, on the other hand as a pressure reducer.
  • the pressure converter 9 has a piston 9K which is displaceable within a cylinder 9Z and which separates a low pressure chamber 9.1 with a large effective cross section from a high pressure chamber 9.2 with a small effective cross section.
  • a piston rod 9S connected to the piston 9K in the high-pressure space 9.2.
  • the effective ratio in terms of pressure and flow rate is determined by the cross sections of the two pressure chambers 9.1 and 9.2.
  • a 9.1 is the hydraulically effective cross section of the Nederdruckraums 9.1, A 9.2 that of the high-room space 9.2, d 9Z, the inner diameter of the cylinder 9Z and d 9S, the diameter of the piston rod 9S.
  • the pressure ratio of the pressure converter 9 and accordingly also the ratio of the volume flows is thus determined by A 9.1 : A 9.2 .
  • the ratio A 9.1 : A 9.2 is for example 2: 1.
  • the position of the piston 9K is detected by means of a displacement transducer 9W.
  • the low-pressure chamber 9.1 communicates with a pressure converter Neder founded Arthur 10.1 of the valve group 3 in conjunction.
  • Neder founded Arthur 10.1 are three switching valves, namely a Vorpreßventil 11, the second port is connected to the cylinder line 4, a Neder réellehunt outlet valve 12 whose second port is connected via the tank line 8 to the reservoir 2, and a low-pressure chamber inlet valve 13, whose second terminal is connected to the storage line 5 and thus also to the accumulator 7.
  • the high-pressure chamber 9.2 communicates with a pressure converter high-pressure line 10.2 of the valve group 3 in conjunction.
  • a pressure converter high-pressure line 10.2 are also valves, namely a Hauptpreß valve 14 whose second port is connected to the cylinder line 4, and a check valve 15 whose second port is connected to the storage line 5 and thus with the accumulator 7.
  • a pressure relief valve 16 is located between the cylinder line 4 and the tank line 8.
  • At the pressure converter high-pressure line 10.2 is also a third valve, namely a 3-way valve 17 connected to an upstream check valve 18, wherein the 3-way valve 17 on the other hand with the storage line 5 and thus also with the accumulator 7 and with its further connection to the tank line 8 and thus connected to the reservoir 2.
  • the line section between the check valve 18 and the 3-way valve 17 is referred to as Preß réelle and is provided with the reference numeral 19.
  • the check valve 18 is functionally a return check valve. About the operation of the various valves 11, 12, 13, 14, 15, 16 and 17 is then based on the FIGS. 2 to 6 reported in detail.
  • the valves are electrically controllable and are controlled by a control unit 20.
  • the naturally existing connection lines from the control unit 20 to the valves 11, 12, 13, 14, 15, 16 and 17 are not shown in the figures for reasons of clarity.
  • a first phase of the press operation is described below, namely the structure of the form.
  • the press cylinder 1 is filled in a conventional manner from the reservoir 2 with hydraulic medium, which is indicated by an arrow.
  • the upper die is lowered and thus closed the mold.
  • the piston 9K is in an upper position near its upper end position A.
  • the 3-way valve 17 is driven so that it releases the flow from the terminal of the storage line 5 to the connection of the Preßtechnisch 19.
  • the control of the 3-way valve 17 is in the Fig. 2 marked by the fact that its electrically driven drive is filled in black.
  • Through this opening of the 3-way valve 17 can now hydraulic medium from the accumulator 7 via said 3-way valve 17 through the Preß réelle 19, through which because of the pressure of the hydraulic medium forcibly opening check valve 18 and by the pressure converter high-pressure line 10.2 in the High-pressure chamber 9.2 of the pressure converter 9 flow, which in the Fig. 2 indicated by arrows.
  • the Vorpreßventil 11 is driven, which in turn is marked by the fact that its electrically driven drive is filled in black.
  • hydraulic medium can now flow from the low-pressure chamber 9.1 via the pressure converter low-pressure line 10.1, through the pilot-pressure valve 11 and the cylinder line 4 into the press cylinder 1. Because of the area ratio A 9.2 to A 9.1, the pressure converter 9 now acts as a pressure reducer, wherein the amount of hydraulic medium is increased according to the area ratio A 9.2 to A 9.1 . If the area ratio A 9.2 to A 9.1 is 1: 2, for example, then the pressure converter 9 of FIG Pressure reduced in the ratio 1: 2, but the amount of hydraulic medium increased in the ratio 1: 2. By the flow of the hydraulic medium, the piston 9K is moved in the direction B.
  • the 3-way valve 17 is a proportionally controllable valve, so that the drive of the 3-way valve 17, for example, a proportional solenoid, so that the pressure in the Preßtechnisch 9 and in the pressure converter high-pressure line 10.2 and thus also the pressure in the pressure converter low pressure line 10.1. in the cylinder line 4 and in the press cylinder 1 can be controlled or regulated.
  • the control unit 20 If the desired pre-pressure is reached, which is detected by the pressure transducer 22, transmitted by the latter to the control unit 20 and thus detected by the control unit 20, then the control unit 20 causes the 3-way valve 17 and the pre-pressure valve 11 to be closed.
  • the pressure relief valve 16 is now activated and thus opened. This results in a pressure reduction in the press cylinder 1 and in the cylinder line 4, which is detected by the pressure transducer 22. Hydraulic medium thus flows from the press cylinder 1 and the cylinder line 4 via the pressure relief valve 16 and through the tank line 8 to the reservoir 2. Determines the pressure transducer 22, that the press cylinder 1 and the cylinder line 4 are depressurized, the pressure relief valve 16 is closed again.
  • the piston 9K is located within the cylinder 9Z in a position near the lower limit position B, which is detected by the position transducer 9W. This position is required to subsequently produce the required Hauptpreß réelle can.
  • Fig. 3 is the first step of this phase shown.
  • the controlled valves are represented by black marking of the electric drives and the flow of the hydraulic medium is indicated by arrows next to the lines.
  • the check valve 15 and the Hauptpreß valve 14 are driven. Lock valve 15 and Hauptpreß valve 14 are then open.
  • These two valves 14, 15 are advantageously electrically controllable open-close valves.
  • Vorpreßventil 11, low-pressure chamber inlet valve 13, low-pressure chamber outlet valve 12 and pressure relief valve 16 are advantageously of this type.
  • this pressure in the press cylinder 1 is followed by the pressure transducer 22. Once the desired pressure is reached, the low pressure chamber inlet valve 13 and the Hauptpreß valve 14 are closed again. It is understood that this pressure build-up is connected to a flow of hydraulic medium from the accumulator 7 in the low-pressure chamber 9.1 and the high-pressure chamber 9.2 via the cylinder line 4 to the press cylinder 1, whereby the piston 9K is moved in the direction A. Because of the area ratio A 9.2 to A 9.1 is the amount of hydraulic medium flowing from the high-pressure chamber 9.2, under the given conditions of area ratio A 9.2 to A 9.1 of 1: 2 only half as large as the amount of hydraulic medium from the accumulator 7th her in the low pressure chamber 9.1 flows.
  • the press now reaches its maximum pressure and performs the pressing. Under the effect of this pressure, the stresses in the components of the press are at the maximum values. Since the components deform elastically, so energy is stored in these components.
  • Another energy potential represents the compressible hydraulic fluid volume in the press cylinder 1, the press line 4, the pressure converter high-pressure line 10.2 and in the high-pressure chamber 9.2 of the pressure converter 9.
  • a phase of discharge with voltage reduction and decompression takes place.
  • This phase takes place in three steps, of which the first two in the Fig. 5 and 6 are shown.
  • the first step is in the Fig. 5 shown.
  • the Hauptpreß valve 14 and the check valve 15 are open, which is analogous to the previous figures with black marking of the drives of the valves 14, 15 is shown.
  • the hydraulic fluid can flow from the press cylinder 1 to the accumulator 7, taking the path through the cylinder line 4, the Hauptpreß-valve 14, the check valve 15 and the storage line 5.
  • the flow is due to the fact that, as previously mentioned, the pressure in the press cylinder 1 is greater than in the pressure fluid reservoir 7.
  • the first step lasts until the pressures in the press cylinder 1 and in the pressure fluid reservoir 7 are the same. However, this also means that a very considerable part of the energy stored in the components of the press is recovered by increasing the pressure in the accumulator 7. This is a decisive advantage of the control device according to the invention and the method for its operation.
  • the second step of the discharge phase will be based on the Fig. 6 described, in turn, the drives of the controlled valves are shown filled in black and the flow of hydraulic medium is marked with arrows on the lines.
  • This second step is the preparation of the next press cycle.
  • the pressure converter 9 must assume a certain position in the direction of the end position B.
  • the remaining volume in the low-pressure chamber 9.1 of the pressure converter is then so large that the pre-pressures for the next power stroke can be realized with this volume. With the transducer 9W can be checked whether this is the case.
  • the residual pressure in the press cylinder 1 and in the cylinder line 4 is still completely degraded in the third step, which takes place in that now the pressure relief valve 16 is opened.
  • the pressure relief valve 16 flows under the action of the residual pressure hydraulic fluid from the press cylinder 1 through the cylinder line 4, the pressure relief valve 16 and the tank line 8 in the reservoir 2. The flow ceases as soon as the residual pressure in the press cylinder 1 is completely degraded. Then, the pressure relief valve 16 is closed again.
  • Fig. 7 a variant of the press control according to the invention is shown.
  • the pressure converter 9 ' essentially consists of a first pump 23 whose shaft 24 is rigidly coupled to a second pump 25, so that the shaft 24 is common to both pumps 23, 25.
  • the first pump 23 is connected on the one hand to the pressure converter low pressure line 10.1, this side of the pump 23 acts as a low pressure chamber 9.1, on the other hand with a tank 26.
  • the second pump 25 is connected on the one hand to the pressure converter high pressure line 10.2, this side of the pump
  • the two pumps 23, 25 are not driven by a motor, but act through the rigid connection each as a unit of pump and hydraulic motor.
  • this combination of the two pumps 23, 25 is effective in that the specific delivery volume, ie the volume per revolution, is different, which in the Fig. 7 symbolically represented by the different size of the pumps 23, 25.
  • this ratio is 2: 1.
  • the pressure converter 9 'behaves exactly as the pressure converter 9 during the in the Fig.
  • the pressure converter 9 acts as a pressure reducer, wherein the second pump 25 operates as a hydraulic motor and drives the first pump 23.
  • the first pump 23 acts as a hydraulic motor, which drives the second pump 25.
  • control device can be recovered with this energy of individual pressing steps.
  • the control device comes without expensive components such as adjustable pumps.
  • the invention can be used in principle in hydraulic presses of various types for different applications with great advantage.
  • the press can be equipped with differential cylinders, DC cylinders or plunger cylinders. It is particularly advantageous if the control device according to the invention is used in presses for the shaping of ceramic parts such as tiles.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Control Of Presses (AREA)
  • Press Drives And Press Lines (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Fluid-Pressure Circuits (AREA)
EP01956735A 2000-09-20 2001-08-24 Steuervorrichtung für eine hydraulische presse sowie verfahren zu deren betrieb Expired - Lifetime EP1318906B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH18262000 2000-09-20
CH182600 2000-09-20
PCT/IB2001/001527 WO2002024441A1 (de) 2000-09-20 2001-08-24 Steuervorrichtung für eine hydraulische presse sowie verfahren zu deren betrieb

Publications (2)

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EP1318906A1 EP1318906A1 (de) 2003-06-18
EP1318906B1 true EP1318906B1 (de) 2009-09-30

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US (1) US6973780B2 (zh)
EP (1) EP1318906B1 (zh)
JP (1) JP5058426B2 (zh)
KR (1) KR20030032042A (zh)
CN (1) CN1243637C (zh)
AT (1) ATE444157T1 (zh)
AU (1) AU2001278651A1 (zh)
BR (1) BR0113991B1 (zh)
CA (1) CA2422879A1 (zh)
DE (1) DE50115141D1 (zh)
ES (1) ES2329443T3 (zh)
WO (1) WO2002024441A1 (zh)

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RU2468919C1 (ru) * 2011-08-15 2012-12-10 Валерий Владимирович Бодров Гидравлический привод подвижной траверсы пресса
RU2515779C1 (ru) * 2013-02-13 2014-05-20 Валерий Владимирович Бодров Гидравлический привод подвижной траверсы пресса
RU2528282C1 (ru) * 2013-02-18 2014-09-10 Валерий Владимирович Бодров Гидропривод подвижной траверсы пресса
RU2530917C1 (ru) * 2013-04-29 2014-10-20 Валерий Владимирович Бодров Гидропривод траверсы пресса
RU2598410C1 (ru) * 2015-06-03 2016-09-27 Валерий Владимирович Бодров Гидропривод подвижной траверсы пресса
RU2602934C1 (ru) * 2015-08-19 2016-11-20 Валерий Владимирович Бодров Гидропривод подвижной траверсы пресса
RU178161U1 (ru) * 2016-11-21 2018-03-26 Валерий Владимирович Бодров Гидравлический привод подвижной траверсы вертикального пресса
RU2687122C1 (ru) * 2018-07-24 2019-05-07 Валерий Владимирович Бодров Гидропривод подвижной траверсы вертикального пресса
RU2764536C1 (ru) * 2021-04-16 2022-01-18 Валерий Владимирович Бодров Способ управления подвижной траверсой гидравлического пресса

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FI20145773A (fi) * 2014-09-05 2016-03-06 Kratos Oy Menetelmä ja järjestely paineen muuntamiseksi ja latausjakson järjestämiseksi
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DE102016118853B3 (de) 2016-10-05 2017-10-26 Hoerbiger Automatisierungstechnik Holding Gmbh Elektrohydraulische Antriebseinheit
CN106553370B (zh) * 2016-11-30 2018-01-19 合肥工业大学 一种双执行单元液压机
CN106762893A (zh) * 2016-12-12 2017-05-31 天津书芹科技有限公司 具有稳压功能的机电加工机构
CN106762927A (zh) * 2016-12-12 2017-05-31 天津商企生产力促进有限公司 具有回程泄压功能的机电加工机构
EP3437848B1 (de) 2017-08-03 2024-03-20 Nienstedt GmbH Werkzeugmaschine
IT201800007019A1 (it) * 2018-07-09 2020-01-09 Impianto fluidodinamico per l'azionamento controllato della slitta di una pressa
CN109531150B (zh) * 2018-11-13 2020-10-13 太原重工股份有限公司 大口径焊管机组液压缸同步控制方法
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RU2468919C1 (ru) * 2011-08-15 2012-12-10 Валерий Владимирович Бодров Гидравлический привод подвижной траверсы пресса
RU2515779C1 (ru) * 2013-02-13 2014-05-20 Валерий Владимирович Бодров Гидравлический привод подвижной траверсы пресса
RU2528282C1 (ru) * 2013-02-18 2014-09-10 Валерий Владимирович Бодров Гидропривод подвижной траверсы пресса
RU2530917C1 (ru) * 2013-04-29 2014-10-20 Валерий Владимирович Бодров Гидропривод траверсы пресса
RU2598410C1 (ru) * 2015-06-03 2016-09-27 Валерий Владимирович Бодров Гидропривод подвижной траверсы пресса
RU2602934C1 (ru) * 2015-08-19 2016-11-20 Валерий Владимирович Бодров Гидропривод подвижной траверсы пресса
RU178161U1 (ru) * 2016-11-21 2018-03-26 Валерий Владимирович Бодров Гидравлический привод подвижной траверсы вертикального пресса
RU2687122C1 (ru) * 2018-07-24 2019-05-07 Валерий Владимирович Бодров Гидропривод подвижной траверсы вертикального пресса
RU2764536C1 (ru) * 2021-04-16 2022-01-18 Валерий Владимирович Бодров Способ управления подвижной траверсой гидравлического пресса

Also Published As

Publication number Publication date
KR20030032042A (ko) 2003-04-23
ATE444157T1 (de) 2009-10-15
JP5058426B2 (ja) 2012-10-24
EP1318906A1 (de) 2003-06-18
CA2422879A1 (en) 2003-03-19
BR0113991B1 (pt) 2010-05-18
WO2002024441A1 (de) 2002-03-28
ES2329443T3 (es) 2009-11-26
JP2004522580A (ja) 2004-07-29
CN1243637C (zh) 2006-03-01
DE50115141D1 (de) 2009-11-12
BR0113991A (pt) 2003-08-12
CN1461255A (zh) 2003-12-10
AU2001278651A1 (en) 2002-04-02
US6973780B2 (en) 2005-12-13
US20030167936A1 (en) 2003-09-11

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