EP1318906A1 - Controller for a hydraulic press and method for the operation thereof - Google Patents

Controller for a hydraulic press and method for the operation thereof

Info

Publication number
EP1318906A1
EP1318906A1 EP01956735A EP01956735A EP1318906A1 EP 1318906 A1 EP1318906 A1 EP 1318906A1 EP 01956735 A EP01956735 A EP 01956735A EP 01956735 A EP01956735 A EP 01956735A EP 1318906 A1 EP1318906 A1 EP 1318906A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
press
line
cylinder
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.)
Granted
Application number
EP01956735A
Other languages
German (de)
French (fr)
Other versions
EP1318906B1 (en
Inventor
Matthias Hahn
Arno MÖHN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Laeis GmbH
Original Assignee
Laeis Bucher GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Laeis Bucher GmbH filed Critical Laeis Bucher GmbH
Publication of EP1318906A1 publication Critical patent/EP1318906A1/en
Application granted granted Critical
Publication of EP1318906B1 publication Critical patent/EP1318906B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • 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
    • 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 of the type mentioned in the preamble of claim 1, to a method for its operation according to the preamble of claim 8 and to a use according to claim 11.
  • Hydraulic presses are used when it is a matter of shaping or reshaping workpieces. Hydraulic presses are also used for cutting processes. The required force of the hydraulic press depends on the workpiece. Presses are used in the ceramic industry whose press force is 20,000 kN or more. With regard to economical production, the cycle time for a pressing process should be as short as possible. Cycle sequences of 20 strokes per minute are a guide. The energy to be expended is determined by the pressing force and cycle time, in hydraulic presses it is the power of pumps and electric motors that drive these pumps. Hydraulic presses according to the prior art also use accumulators, such as pressure medium accumulators or flywheels.
  • a hydraulic press of the type mentioned in the preamble of claim 1 is known from DE-Al-43 20 213.
  • a pressure medium reservoir in the feed circuit of the hydraulic press cylinder which is loaded when the press returns and is used to drive the press tool when it is fed. Energy can thus be saved with the main drive.
  • a hydraulic drive system for a press is known from US-A-5,852,933 and DE-Al-44 36 666. It contains a low pressure and a high pressure circuit. In this there are three hydrostatic machines, two of which are mechanically coupled. In order to enable satisfactory operation, these machines have to swallow or Funding volume can be adjusted, which is associated with considerable costs.
  • the system described here can only be used if the press has differential cylinders or synchronous cylinders. It is also known (DE-Al-43 08 344) to use the principle of secondary control when controlling the drive of a hydraulic press. The various movements of the press ram are combined with one another in such a way that the pressure network operates in a closed circuit, the maximum system pressure being determined by the pressure medium reservoir.
  • the invention has for its object to provide a hydraulic press, the hydraulic control is constructed so that the total energy requirement is reduced without an increased outlay on equipment is necessary.
  • the control should also be applicable to a press with plunger cylinders.
  • Fig. 7 is a diagram of an embodiment of the press control.
  • 1 means a press cylinder to which a reservoir 2 for the hydraulic medium is assigned.
  • Reference number 3 designates a valve group which contains a series of valves which are mentioned below. Over a Cylinder line 4, the hydraulic medium is conveyed between the press cylinder 1 and the valve group 3.
  • a storage line 5 is connected to the valve group 3.
  • a pressure medium accumulator 7 is connected to the accumulator line 5, which also runs within the valve group 3. This also means that the hydraulic pump 6 is able to convey the hydraulic medium into the pressure medium reservoir 7.
  • a check valve (not shown) can be arranged in the line section between the hydraulic pump 6 and the storage line 5 in order to relieve the hydraulic pump 6 of the pressure prevailing in the pressure medium store 7 when the hydraulic pump 6 is not running.
  • a tank line 8 leads from the valve group 3 to the storage container 2.
  • a pressure converter 9 is also connected to the valve group 3, which according to the general inventive concept can act on the one hand as a pressure intensifier and 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.
  • the effective ratio with regard to pressure and volume flow is determined by the cross sections of the two pressure chambers 9.1 and 9.2.
  • the cross-section is determined according to the inner diameter of the cylinder 9Z and for the high pressure chamber 9.2 by the difference between the inner diameter of the cylinder 9Z and the piston rod 9S according to
  • a 9.1 is the hydraulically effective cross section of the low pressure chamber 9.1, A 92 that of the high chamber 9.2, d 9 z the inner diameter of the cylinder 9Z and d 9 s 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 therefore determined by A 9 . 1 : A 9 . 2nd
  • the ratio A 9 : A 92 is, for example, 2: 1.
  • the position of the piston 9K is detected by means of a displacement sensor 9W.
  • the low pressure chamber 9.1 is connected to a pressure converter low pressure line 10.1 of the valve group 3.
  • a pressure converter low-pressure line 10.1 there are three switching valves, namely a pre-pressure valve 11, the second connection of which is connected to the cylinder line 4, a low-pressure chamber outlet valve 12, the second connection of which is connected to the reservoir 2 via the tank line 8, and a low-pressure chamber inlet valve 13, the second connection of which is connected to the storage line 5 and thus also to the pressure medium store 7.
  • the high pressure chamber 9.2 is connected to a pressure converter high pressure line 10.2 of the valve group 3.
  • a pressure converter high-pressure line 10.2 there are also valves, namely a main pressure valve 14, the second connection of which is connected to the cylinder line 4, and a shut-off valve 15, the second connection of which is connected to the storage line 5 and thus also to the pressure medium store 7.
  • a pressure relief valve 16 lies between the cylinder line 4 and the tank line 8.
  • a third valve, namely a 3-way valve 17 with an upstream check valve 18, is also connected to the pressure converter high-pressure line 10.2, the 3-way valve 17 on the other hand the storage line 5 and thus also with the
  • Pressure medium accumulator 7 and its further connection is connected to the tank line 8 and thus to the reservoir 2.
  • the line section between the check valve 18 and the 3-way valve 17 is referred to as a press line and is provided with the reference number 19.
  • the check valve 18 is functionally a non-return valve.
  • the functioning of the various valves 11, 12, 13, 14, 15, 16 and 17 is then reported in detail with reference to FIGS. 2 to 6.
  • the valves can be controlled electrically 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.
  • control unit 20 displacement sensor 9W
  • pressure sensor 22 press safety lowering and retraction control 21 and other safety-relevant elements on the press are also not shown.
  • a first phase of press operation is described below with reference to FIG. 2, namely the build-up of the form.
  • the press cylinder 1 is filled in the usual way from the reservoir 2 with hydraulic medium, which is indicated by an arrow. This lowers the upper press tool and closes the mold.
  • the piston 9K is in an upper position near its upper end position A.
  • the 3-way valve 17 is controlled so that it releases the flow from the connection of the storage line 5 to the connection of the press line 19.
  • the activation of the 3-way valve 17 is marked in FIG. 2 by the fact that its electrically operated drive is filled in black.
  • hydraulic medium can now flow from the pressure medium reservoir 7 via said 3-way valve 17 through the press line 19, through the check valve 18 which inevitably opens due to the pressure of the hydraulic medium, and through the pressure converter high-pressure line 10.2 into the High-pressure chamber 9.2 of the pressure converter 9 flow, which is indicated by arrows in FIG. 2.
  • the pre-press valve 11 is also activated, which in turn is marked by the fact that its electrically operated 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 pre-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, the amount of hydraulic medium being increased in accordance with the area ratio A 92 to A 9 1 . Is that
  • Area ratio A 9 . 2 to A 9 ⁇ for example 1: 2, so the pressure converter 9 Pressure reduced in a ratio of 1: 2, but the amount of hydraulic medium increased in a ratio of 1: 2.
  • the piston 9K is moved in direction B by the flow of the hydraulic medium.
  • the 3-way valve 17 is a proportionally controllable valve, so that the drive of the 3-way valve 17 is, for example, a proportional magnet, so that the pressure in the press line 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. is controllable or regulatable in the cylinder line 4 and in the press cylinder 1.
  • the control unit 20 If the desired admission pressure has been reached, which is detected by the pressure transducer 22, transmitted by the latter to the control unit 20 and thus determined by the control unit 20, the control unit 20 causes the 3-way valve 17 and the pre-compression valve 11 to be closed.
  • the pressure relief valve 16 is then actuated 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 detector 22. Hydraulic medium flows from it
  • the piston 9K is located within the cylinder 9Z in a position near the lower end position B, which is determined by the displacement sensor 9W. This position is necessary in order to subsequently be able to generate the required main pressure.
  • the next phase of the press operation follows, the build-up of the main pressure. This is described below with reference to FIGS. 3 and 4.
  • the first step of this phase is shown in FIG.
  • the actuated valves are again shown 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 main press valve 14 are now controlled.
  • Check valve 15 and main press valve 14 are then open.
  • These two valves 14, 15 are advantageously electrically controllable OPEN-CLOSE valves.
  • Prepressing valve 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 build-up is connected to a flow of hydraulic medium from the pressure medium reservoir 7 into the low pressure chamber 9.1 and from the high pressure chamber 9.2 via the cylinder line 4 to the press cylinder 1, whereby the piston 9K is also displaced in direction A. Because of the area ratio A 92 to A 9 1 , the amount of hydraulic medium that flows from the high-pressure chamber 9.2 is, under the given conditions of an area ratio A 92 to A 9 1 of 1: 2, only half as large as the amount of hydraulic medium that flows from Pressure medium reservoir 7 flows into the low-pressure chamber 9.1.
  • the press now reaches its maximum pressure and carries out the pressing. Under the effect of this pressure, the stresses in the components of the press are also at the maximum values. Since the components deform elastically, energy is stored in these components. The compressible represents a further energy potential
  • FIGS. 5 and 6 The first step is shown in FIG. 5.
  • the main press valve 14 and the shut-off valve 15 are open, which is shown analogously to the previous figures with black marking of the drives of the valves 14, 15.
  • the hydraulic medium can flow from the press cylinder 1 to the pressure medium reservoir 7, taking the path through the cylinder line 4, the main press valve 14, the shut-off valve 15 and the accumulator line 5.
  • the flow comes about from the fact that, as mentioned above, the pressure in the press cylinder 1 is greater than in the pressure medium reservoir 7.
  • the first step lasts until the pressures in the press cylinder 1 and in the pressure medium reservoir 7 are equal.
  • the residual pressure prevailing in the press cylinder 1, in the cylinder line 4 and in the pressure converter high pressure line 10.2 by opening the main pressure valve 14 and the low pressure chamber outlet valve 12 is used to push the piston 9K of the pressure converter 9 into the bring desired position.
  • This desired position is shown in FIG. 6.
  • the high-pressure chamber 9.2 is also filled again with hydraulic medium under pressure, so that no hydraulic medium has to be removed from the pressure accumulator 7 for the filling. That means further energy savings.
  • the hydraulic medium displaced from the low-pressure chamber 9.1 during the movement of the piston 9K passes via the low-pressure chamber outlet valve 12 through the tank line 8 into the reservoir 2. If the piston 9K has reached the desired position, which is determined by the displacement sensor 9W, as will be said Low pressure chamber outlet valve 12 and main pressure valve 14 closed again.
  • the residual pressure in the press cylinder 1 and in the cylinder line 4 is completely reduced, which is done by opening the pressure relief valve 16. Hydraulic medium flows from the press cylinder 1 through the cylinder line 4 under the effect of the residual pressure
  • FIG. 7 shows a variant of the press control system according to the invention. Compared to the example of FIG. 1, the only change is that the pressure converter 9 'has a different design than the pressure converter 9 according to FIGS. 1 to 6.
  • the pressure converter 9' essentially consists of a first pump 23, the shaft 24 of which 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 acting as low pressure chamber 9.1, on the other hand to 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 25 acts as a high-pressure chamber 9.2, and also on the other hand with the tank 26.
  • the two pumps 23, 25 are not driven by a motor, but rather act as a unit of pump and hydraulic motor due to the rigid connection.
  • This combination of the two pumps 23, 25 is effective as a pressure converter in that the specific delivery volume, that is to say the volume per revolution, is different, which is symbolically represented in FIG. 7 by the different sizes of the pumps 23, 25. For example, this ratio is 2: 1.
  • the pressure converter 9 'behaves exactly like the pressure converter 9 during the different phases of the press operation shown in FIGS. 2 to 6 and described with reference to these figures.
  • the pressure converter 9 During the aforementioned first phase of the press operation, for example, the pressure converter 9 'acts as a pressure reducer, the second pump 25 working as a hydraulic motor and driving the first pump 23.
  • the first pump 23 acts as a hydraulic motor which drives the second pump 25.
  • control device Despite the very simple construction of the control device according to the invention, individual pressing steps can be recovered with this energy. As described above, even those in the press, in the material to be pressed and in the compressible hydraulic oil become elastic recovered stored energy.
  • the control device manages without expensive components such as adjustable pumps.
  • control device according to the invention achieves considerable energy savings compared to the prior art.
  • the energy saving can well reach around 40%.
  • the invention can be used with great advantage in hydraulic presses of various types for various fields of application.
  • the press can be equipped with differential cylinders, synchronous cylinders or even plunger cylinders. It is particularly advantageous if the control device according to the invention is used in presses for shaping ceramic parts such as tiles.

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  • 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)

Abstract

The invention relates to a controller for a hydraulic press, comprising a pressing cylinder ( 1 ), a reservoir ( 2 ), a valve group ( 3 ), a pressure medium reservoir ( 7 ) and a hydraulic pump ( 6 ), connected together by means of a cylinder line ( 4 ), a reservoir line ( 5 ) and a tank line ( 8 ). According to the invention, a pressure converter ( 9 ) is arranged on the valve group ( 3 ), which may operate as a pressure amplifier or pressure reducer. The particular mode of action of said controller is achieved whereby the valve group ( 3 ) comprises a pre-press valve ( 11 ), a low-pressure chamber outlet valve ( 12 ), a low-pressure chamber inlet valve ( 13 ), a main press valve ( 14 ), a closing valve ( 15 ), a pressure release valve ( 16 ) and a 3-way valve ( 17 ), which may be operated by a particular control sequence. Said invention is applicable in hydraulic presses and of particular advantage in presses for the forming of ceramic pieces such as tiles.

Description

Steuervorrichtung für eine hydraulische Presse sowie Verfahren zu deren BetriebControl device for a hydraulic press and method for its operation
Die Erfindung bezieht sich auf eine hydraulische Presse der im Oberbegriff des Anspruchs 1 genannten Art, auf ein Verfahren zu deren Betrieb gemäß dem Oberbegriff des Anspruchs 8 und auf eine Verwendung gemäß dem Anspruch 11.The invention relates to a hydraulic press of the type mentioned in the preamble of claim 1, to a method for its operation according to the preamble of claim 8 and to a use according to claim 11.
Solche hydraulischen Pressen werden verwendet, wenn es gilt Werkstücke zu formen bzw. umzuformen. Auch für Schneidvorgänge werden hydraulische Pressen angewendet. Die erforderliche Kraft der hydraulischen Presse hängt vom Werkstück ab. In der keramischen Industrie werden Pressen eingesetzt, deren Preßkraft 20 '000 kN oder mehr beträgt. Im Hinblick auf eine wirtschaftliche Fertigung soll dabei die Taktzeit für einen Preßvorgang möglichst kurz sein. Taktfolgen von 20 Hüben pro Minute gelten als Richtwert. Durch Preßkraft und Taktzeit wird die aufzuwendende Energie bestimmt, bei hydraulischen Pressen also die Leistung von Pumpen und diese Pumpen antreibenden elektrischen Motoren. Bei hydraulischen Pressen nach dem Stand der Technik werden auch Speicher angewendet, so Druckmittelspeicher oder Schwungräder.Such hydraulic presses are used when it is a matter of shaping or reshaping workpieces. Hydraulic presses are also used for cutting processes. The required force of the hydraulic press depends on the workpiece. Presses are used in the ceramic industry whose press force is 20,000 kN or more. With regard to economical production, the cycle time for a pressing process should be as short as possible. Cycle sequences of 20 strokes per minute are a guide. The energy to be expended is determined by the pressing force and cycle time, in hydraulic presses it is the power of pumps and electric motors that drive these pumps. Hydraulic presses according to the prior art also use accumulators, such as pressure medium accumulators or flywheels.
Eine hydraulische Presse der im Oberbegriff des Anspruchs 1 genannten Art ist aus der DE-Al-43 20 213 bekannt. Hier ist im Vorschubkreis des hydraulischen Preßzylinders ein Druckmittelspeicher vorhanden, der beim Rückhub der Presse geladen wird und beim Vorschub des Preßwerkzeuges zum Antrieb mit herangezogen wird. Beim Hauptantrieb kann somit Energie eingespart werden.A hydraulic press of the type mentioned in the preamble of claim 1 is known from DE-Al-43 20 213. Here there is a pressure medium reservoir in the feed circuit of the hydraulic press cylinder, which is loaded when the press returns and is used to drive the press tool when it is fed. Energy can thus be saved with the main drive.
Aus JP-A-63 256 300 ist eine Presse bekannt, die mit einem mehrstufigen Druckumsetzer betrieben wird. Nach einem ersten Pressvorgang mit niedrigem Druck wird das Hydrauliköl in den Tank abgelassen. Dann erfolgt ein zweiter Pressvorgang mit hohem Druck. Eine Energierückgewinnung ist folglich hierbei nicht möglich.From JP-A-63 256 300 a press is known which is operated with a multi-stage pressure converter. After a first pressing process with low pressure, the hydraulic oil is drained into the tank. Then a second pressing process with high pressure takes place. Energy recovery is therefore not possible here.
Aus US-A-5,852,933 und DE-Al-44 36 666 ist ein hydraulisches Antriebssystem für eine Presse bekannt. Es enthält einen Niederdruck- und einen Hochdruck-Kreis. In diesem sind drei hydrostatische Maschinen vorhanden, von denen zwei mechanisch gekoppelt sind. Um einen befriedigenden Betrieb zu ermöglichen, müssen diese Maschinen in ihrem Schluckbzw. Fördervolumen verstellbar sein, was mit erheblichen Kosten verbunden ist. Das hier beschriebene System kann nur angewendet werden, wenn die Presse Differentialzylinder oder Gleichgangzylinder aufweist. Es ist auch bekannt (DE-Al-43 08 344), bei der Regelung des Antriebs einer hydraulischen Presse das Prinzip der Sekundärregelung anzuwenden. Die verschiedenen Bewegungen des Pressenstößels werden derart miteinander kombiniert, daß das Drucknetz in einem geschlossenen Kreislauf arbeitet, wobei der maximale Systemdruck durch den Druckmittelspeicher bestimmt wird.A hydraulic drive system for a press is known from US-A-5,852,933 and DE-Al-44 36 666. It contains a low pressure and a high pressure circuit. In this there are three hydrostatic machines, two of which are mechanically coupled. In order to enable satisfactory operation, these machines have to swallow or Funding volume can be adjusted, which is associated with considerable costs. The system described here can only be used if the press has differential cylinders or synchronous cylinders. It is also known (DE-Al-43 08 344) to use the principle of secondary control when controlling the drive of a hydraulic press. The various movements of the press ram are combined with one another in such a way that the pressure network operates in a closed circuit, the maximum system pressure being determined by the pressure medium reservoir.
Bei der Regelung einer hydraulischen Presse spielt gemäß DE-Al-43 08 344 auch die Tatsache eine Rolle, daß das Hydrauliköl durchaus kompressibel ist. Dies wirkt sich in einem Pressentakt sowohl bei der Kompression als auch bei der Dekompression aus und stellt eine Quelle für Verluste dar. Weitgehend unberücksichtigt bleibt beim Stand der Technik die Tatsache, daß auch die mechanischen Teile der Presse durch elastischeAccording to DE-Al-43 08 344, the fact that the hydraulic oil is completely compressible also plays a role in the regulation of a hydraulic press. This affects both the compression and the decompression in one press cycle and is a source of losses. The fact that the mechanical parts of the press are also largely neglected by the prior art remains largely unconsidered
Verformung ihrer Bauteile Energie aufnehmen. Beim Schließ Vorgang der Presse muß diese Energie aufgewendet werden. Beim Öffiiungsvorgang wird diese Energie nicht zurückgewonnen.Deformation of their components absorb energy. This energy must be used when the press closes. This energy is not recovered during the opening process.
Der Erfindung liegt die Aufgabe zugrunde, eine hydraulische Presse zu schaffen, deren hydraulische Steuerung so aufgebaut ist, daß in der Summe der Energiebedarf reduziert ist, ohne daß dabei ein erhöhter apparativer Aufwand nötig ist. Die Steuerung soll dabei auch bei einer Presse mit Plungerzylindern anwendbar sein.The invention has for its object to provide a hydraulic press, the hydraulic control is constructed so that the total energy requirement is reduced without an increased outlay on equipment is necessary. The control should also be applicable to a press with plunger cylinders.
Die genannte Aufgabe wird erfindungsgemäß durch die Merkmale der Ansprüche 1 und 7 gelöst. Vorteilhafte Weiterbildungen ergeben sich aus den abhängigen Ansprüchen.The stated object is achieved according to the invention by the features of claims 1 and 7. Advantageous further developments result from the dependent claims.
Nachfolgend wird ein Ausführungsbeispiel der Erfindung anhand der Zeichnung näher erläutert.An exemplary embodiment of the invention is explained in more detail below with reference to the drawing.
Es zeigen: Fig. 1 ein hydraulisches Schema einer Pressensteuerung,1 shows a hydraulic diagram of a press control,
Fig. 2 bis 6 dieses Schema mit der Darstellung einzelner Schritte innerhalb eines Taktzyklus und2 to 6 this diagram with the representation of individual steps within a clock cycle and
Fig. 7 ein Schema einer Ausführungsvariante der Pressensteuerung.Fig. 7 is a diagram of an embodiment of the press control.
In der Fig. 1 bedeutet 1 einen Pressenzylinder, dem ein Vorratsbehälter 2 für das Hydraulikmedium zugeordnet ist. Mit der Bezugszahl 3 ist eine Ventilgruppe bezeichnet, die eine Reihe von Ventilen enthält, die anschließend erwähnt werden. Über eine Zylinderleitung 4 wird das Hydraulikmedium zwischen dem Pressenzylinder 1 und der Ventilgruppe 3 gefördert.In FIG. 1, 1 means a press cylinder to which a reservoir 2 for the hydraulic medium is assigned. Reference number 3 designates a valve group which contains a series of valves which are mentioned below. Over a Cylinder line 4, the hydraulic medium is conveyed between the press cylinder 1 and the valve group 3.
An die Ventilgruppe 3 ist eine Speicherleitung 5 angeschlossen. In diese Speicherleitung 5 hinein fördert eine Hydraulikpumpe 6, die von einem Elektromotor angetrieben ist, der hier aber nicht dargestellt ist, Hydraulikmedium. Mit der auch innerhalb der Ventilgruppe 3 verlaufenden Speicherleitung 5 steht ein Druckmittelspeicher 7 in Verbindung. Das heißt auch, daß die Hydraulikpumpe 6 das Hydraulikmedium in den Druckmittelspeicher 7 zu fördern in der Lage ist. Im Leitungsabschnitt zwischen der Hydraulikpumpe 6 und der Speicherleitung 5 kann ein nicht dargestelltes Rückschlagventil angeordnet sein, um die Hydraulikpumpe 6 vom im Druckmittelspeicher 7 herrschenden Druck zu entlasten, wenn die Hydraulikpumpe 6 nicht läuft.A storage line 5 is connected to the valve group 3. A hydraulic pump 6, which is driven by an electric motor but which is not shown here, conveys hydraulic medium into this storage line 5. A pressure medium accumulator 7 is connected to the accumulator line 5, which also runs within the valve group 3. This also means that the hydraulic pump 6 is able to convey the hydraulic medium into the pressure medium reservoir 7. A check valve (not shown) can be arranged in the line section between the hydraulic pump 6 and the storage line 5 in order to relieve the hydraulic pump 6 of the pressure prevailing in the pressure medium store 7 when the hydraulic pump 6 is not running.
Von der Ventilgruppe 3 führt eine Tankleitung 8 zum Vorratsbehälter 2. Erfindungsgemäß ist an die Ventilgruppe 3 zudem ein Druckumsetzer 9 angeschlossen, der nach dem allgemeinen Erfindungsgedanken einerseits als Druckübersetzer, andererseits als Druckuntersetzer wirken kann. Dazu weist der Druckumsetzer 9 einen Kolben 9K auf, der innerhalb eines Zylinders 9Z verschiebbar ist und der einen Niederdruckraum 9.1 mit großem wirksamen Querschnitt von einem Hochdruckraum 9.2 mit kleinem wirksamen Querschnitt voneinander trennt. Um den kleineren wirksamen Querschnitt zu erreichen, befindet sich im Hochdruckraum 9.2 eine mit dem Kolben 9K verbundene Kolbenstange 9S. Das Wirkverhältnis hinsichtlich Druck und Volumenstrom wird bestimmt durch die Querschnitte der beiden Druckräume 9.1 und 9.2. Für den Niederdruckraum 9.1 wird der Querschnitt bestimmt vom Innendurchmesser des Zylinders 9Z gemäß und für den Hochdruckraum 9.2 durch die Differenz von Innendurchmesser des Zylinders 9Z und Kolbenstange 9S gemäß A tank line 8 leads from the valve group 3 to the storage container 2. According to the invention, a pressure converter 9 is also connected to the valve group 3, which according to the general inventive concept can act on the one hand as a pressure intensifier and on the other hand as a pressure reducer. For this purpose, 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. In order to achieve the smaller effective cross section, there is a piston rod 9S connected to the piston 9K in the high pressure chamber 9.2. The effective ratio with regard to pressure and volume flow is determined by the cross sections of the two pressure chambers 9.1 and 9.2. For the low-pressure chamber 9.1, the cross-section is determined according to the inner diameter of the cylinder 9Z and for the high pressure chamber 9.2 by the difference between the inner diameter of the cylinder 9Z and the piston rod 9S according to
A9.1 ist dabei der hydraulisch wirksame Querschnitt des Niederdruckraums 9.1, A92 jener des Hochraumraums 9.2, d9z der Innendurchmesser des Zylinders 9Z und d9s der Durchmesser der Kolbenstange 9S. Das Druckverhältnis des Druckumsetzers 9 und entsprechend auch das Verhältnis der Volumenströme ist also bestimmt durch A9.1:A9.2. Das Verhältnis A9.ι:A92 ist beispielsweise 2:1. Die Stellung des Kolbens 9K wird mittels eines Wegaufhehmers 9W erfaßt.A 9.1 is the hydraulically effective cross section of the low pressure chamber 9.1, A 92 that of the high chamber 9.2, d 9 z the inner diameter of the cylinder 9Z and d 9 s 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 therefore determined by A 9 . 1 : A 9 . 2nd The ratio A 9 : A 92 is, for example, 2: 1. The position of the piston 9K is detected by means of a displacement sensor 9W.
Der Niederdruckraum 9.1 steht mit einer Druckumsetzer-Niederdruckleitung 10.1 der Ventilgruppe 3 in Verbindung. An dieser Druckumsetzer-Niederdruckleitung 10.1 liegen drei Schaltventile, nämlich ein Vorpreßventil 11, dessen zweiter Anschluß mit der Zylinderleitung 4 verbunden ist, ein Niederdruckkammer- Auslaßventil 12, dessen zweiter Anschluß über die Tankleitung 8 mit dem Vorratsbehälter 2 verbunden ist, und ein Niederdruckkammer-Einlaßventil 13, dessen zweiter Anschluß mit der Speicherleitung 5 und damit auch mit dem Druckmittelspeicher 7 verbunden ist.The low pressure chamber 9.1 is connected to a pressure converter low pressure line 10.1 of the valve group 3. At this pressure converter low-pressure line 10.1 there are three switching valves, namely a pre-pressure valve 11, the second connection of which is connected to the cylinder line 4, a low-pressure chamber outlet valve 12, the second connection of which is connected to the reservoir 2 via the tank line 8, and a low-pressure chamber inlet valve 13, the second connection of which is connected to the storage line 5 and thus also to the pressure medium store 7.
Der Hochdruckraum 9.2 steht mit einer Druckumsetzer-Hochdruckleitung 10.2 der Ventilgruppe 3 in Verbindung. An dieser Druckumsetzer-Hochdruckleitung 10.2 liegen ebenfalls Ventile, nämlich ein Hauptpreß- Ventil 14, dessen zweiter Anschluß mit der Zylinderleitung 4 verbunden ist, und ein Sperrventil 15, dessen zweiter Anschluß mit der Speicherleitung 5 und damit auch mit dem Druckmittelspeicher 7 verbunden ist. Ein Druckentlastungsventil 16 liegt zwischen der Zylinderleitung 4 und der Tankleitung 8. An der Druckumsetzer-Hochdruckleitung 10.2 ist außerdem ein drittes Ventil, nämlich ein 3- Wege- Ventil 17 mit einem vorgeschalteten Rückschlagventil 18 angeschlossen, wobei das 3 -Wege- Ventil 17 andererseits mit der Speicherleitung 5 und damit auch mit demThe high pressure chamber 9.2 is connected to a pressure converter high pressure line 10.2 of the valve group 3. At this pressure converter high-pressure line 10.2 there are also valves, namely a main pressure valve 14, the second connection of which is connected to the cylinder line 4, and a shut-off valve 15, the second connection of which is connected to the storage line 5 and thus also to the pressure medium store 7. A pressure relief valve 16 lies between the cylinder line 4 and the tank line 8. A third valve, namely a 3-way valve 17 with an upstream check valve 18, is also connected to the pressure converter high-pressure line 10.2, the 3-way valve 17 on the other hand the storage line 5 and thus also with the
Druckmittelspeicher 7 und mit seinem weiteren Anschluß mit der Tankleitung 8 und somit mit dem Vorratsbehälter 2 verbunden ist. Der Leitungsabschnitt zwischen dem Rückschlagventil 18 und dem 3 -Wege- Ventil 17 wird als Preßleitung bezeichnet und ist mit der Bezugszahl 19 versehen. Das Rückschlagventil 18 ist fünktionell ein Rücklaufsperrventil. Über die Funktionsweise der verschiedenen Ventile 11, 12, 13, 14, 15, 16 und 17 wird anschließend anhand der Figuren 2 bis 6 im Detail berichtet. Die Ventile sind elektrisch ansteuerbar und werden von einem Steuergerät 20 beherrscht. Die selbstverständlich vorhandenen Verbindungsleitungen vom Steuergerät 20 zu den Ventilen 11, 12, 13, 14, 15, 16 und 17 sind aus Gründen der Übersichtlichkeit in den Figuren nicht eingezeichnet. Dargestellt sind im hydraulischen Schema nur die erfindungswesentlichen Elemente, daneben noch eine Pressensicherheits-Senk- und Rückzugssteuerung 21, die für den sicheren Betrieb des Pressenzylinders 1 notwendig, im Hinblick auf die Erfindung aber ohne Relevanz ist. Ebenso notwendig ist ein Druckaufhehmer 22, der den Druck in der Zylinderleitung 4 erfaßt.Pressure medium accumulator 7 and its further connection is connected to the tank line 8 and thus to the reservoir 2. The line section between the check valve 18 and the 3-way valve 17 is referred to as a press line and is provided with the reference number 19. The check valve 18 is functionally a non-return valve. The functioning of the various valves 11, 12, 13, 14, 15, 16 and 17 is then reported in detail with reference to FIGS. 2 to 6. The valves can be controlled electrically 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. Only the elements essential to the invention are shown in the hydraulic diagram, as well as a press safety lowering and retraction control 21, which is necessary for the safe operation of the press cylinder 1, but is irrelevant with regard to the invention. Also necessary is a pressure transducer 22 which detects the pressure in the cylinder line 4.
Nicht dargestellt sind aus Gründen der Übersichtlichkeit auch die elektrischen Verbindungen zwischen Steuergerät 20, Wegaufhehmer 9W, Druckaufhehmer 22, Pressensicherheits-Senk- und Rückzugssteuerung 21 und weitere sicherheitsrelevante Elemente an der Presse.For reasons of clarity, the electrical connections between control unit 20, displacement sensor 9W, pressure sensor 22, press safety lowering and retraction control 21 and other safety-relevant elements on the press are also not shown.
Anhand der Fig. 2 wird nachfolgend eine erste Phase des Pressenbetriebs beschrieben, nämlich der Aufbau des Vordrucks. Der Pressenzylinder 1 wird in üblicher Weise aus dem Vorratsbehälter 2 mit Hydraulikmedium befüllt, was mit einem Pfeil gekennzeichnet ist. Dadurch wird das obere Preßwerkzeug abgesenkt und damit die Form geschlossen. Gleichzeitig befindet sich der Kolben 9K in einer oberen Position in der Nähe seiner oberen Endlage A.A first phase of press operation is described below with reference to FIG. 2, namely the build-up of the form. The press cylinder 1 is filled in the usual way from the reservoir 2 with hydraulic medium, which is indicated by an arrow. This lowers the upper press tool and closes the mold. At the same time, the piston 9K is in an upper position near its upper end position A.
Nun wird das 3 -Wege- Ventil 17 so angesteuert, daß es den Durchfluß vom Anschluß der Speicherleitung 5 zum Anschluß der Preßleitung 19 freigibt. Die Ansteuerung des 3 -Wege- Ventils 17 ist in der Fig. 2 dadurch markiert, daß dessen elektrisch betriebener Antrieb schwarz ausgefüllt ist. Durch dieses Öffnen des 3 -Wege- Ventils 17 kann nun Hydraulikmedium vom Druckmittelspeicher 7 über besagtes 3 -Wege- Ventil 17 durch die Preßleitung 19, durch das sich wegen des Druckes des Hydraulikmediums zwangsweise öffnende Rückschlagventil 18 und durch die Druckumsetzer-Hochdruckleitung 10.2 in den Hochdruckraum 9.2 des Druckumsetzers 9 strömen, was in der Fig. 2 durch Pfeile angedeutet ist. Gleichzeitig wird auch das Vorpreßventil 11 angesteuert, was wiederum dadurch markiert ist, daß dessen elektrisch betriebener Antrieb schwarz ausgefüllt ist.Now the 3-way valve 17 is controlled so that it releases the flow from the connection of the storage line 5 to the connection of the press line 19. The activation of the 3-way valve 17 is marked in FIG. 2 by the fact that its electrically operated drive is filled in black. By opening the 3-way valve 17, hydraulic medium can now flow from the pressure medium reservoir 7 via said 3-way valve 17 through the press line 19, through the check valve 18 which inevitably opens due to the pressure of the hydraulic medium, and through the pressure converter high-pressure line 10.2 into the High-pressure chamber 9.2 of the pressure converter 9 flow, which is indicated by arrows in FIG. 2. At the same time, the pre-press valve 11 is also activated, which in turn is marked by the fact that its electrically operated drive is filled in black.
Damit kann nun Hydraulikmedium aus dem Niederdruckraum 9.1 über die Druckumsetzer- Niederdruckleitung 10.1, durch das Vorpreßventil 11 und die Zylinderleitung 4 in den Pressenzylinder 1 strömen. Wegen des Flächenverhältnisses A9.2 zu A9-1 wirkt der Druckumsetzer 9 jetzt als Druckuntersetzer, wobei die Menge des Hydraulikmediums entsprechend dem Flächenverhältnis A92 zu A9 1 erhöht wird. Beträgt dasHydraulic medium can now flow from the low-pressure chamber 9.1 via the pressure converter low-pressure line 10.1, through the pre-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, the amount of hydraulic medium being increased in accordance with the area ratio A 92 to A 9 1 . Is that
Flächenverhältnis A9.2 zu A9Λ zum Beispiel 1 :2, so wird durch den Druckumsetzer 9 der Druck im Verhältnis 1:2 untersetzt, die Menge des Hydraulikmediums aber im Verhältnis 1 :2 erhöht. Durch das Strömen des Hydraulikmediums wird der Kolben 9K in Richtung B bewegt.Area ratio A 9 . 2 to A 9Λ for example 1: 2, so the pressure converter 9 Pressure reduced in a ratio of 1: 2, but the amount of hydraulic medium increased in a ratio of 1: 2. The piston 9K is moved in direction B by the flow of the hydraulic medium.
Zu bemerken ist noch, daß das 3 -Wege- Ventil 17 ein proportional steuerbares Ventil ist, daß also der Antrieb des 3 -Wege- Ventils 17 beispielsweise ein Proportionalmagnet ist, so daß der Druck in der Preßleitung 9 und in der Druckumsetzer-Hochdruckleitung 10.2 und somit auch der Druck in der Druckumsetzer-Niederdruckleitung 10.1. in der Zylinderleitung 4 und im Pressenzylinder 1 steuerbar bzw. regelbar ist.It should also be noted that the 3-way valve 17 is a proportionally controllable valve, so that the drive of the 3-way valve 17 is, for example, a proportional magnet, so that the pressure in the press line 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. is controllable or regulatable in the cylinder line 4 and in the press cylinder 1.
Ist der gewünschte Vordruck erreicht, was durch den Druckaufhehmer 22 detektiert, von diesem dem Steuergerät 20 übermittelt und vom Steuergerät 20 also festgestellt wird, so veranlaßt das Steuergerät 20, daß das 3 -Wege- Ventil 17 und das Vorpreßventil 11 geschlossen werden.If the desired admission pressure has been reached, which is detected by the pressure transducer 22, transmitted by the latter to the control unit 20 and thus determined by the control unit 20, the control unit 20 causes the 3-way valve 17 and the pre-compression valve 11 to be closed.
Anschließend wird nun das Druckentlastungsventil 16 angesteuert und somit geöffnet. Dadurch erfolgt ein Druckabbau im Pressenzylinder 1 und in der Zylinderleitung 4, der vom Druckaufhehmer 22 detektiert wird. Hydraulikmedium fließt damit vomThe pressure relief valve 16 is then actuated 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 detector 22. Hydraulic medium flows from it
Pressenzylinder 1 und der Zylinderleitung 4 über das Druckentlastungsventil 16 und durch die Tankleitung 8 zum Vorratsbehälter 2. Ermittelt der Druckaufhehmer 22, daß der Pressenzylinder 1 und die Zylinderleitung 4 drucklos sind, so wird das Druckentlastungsventil 16 wieder geschlossen.Press cylinder 1 and the cylinder line 4 via the pressure relief valve 16 and through the tank line 8 to the reservoir 2. If the pressure transducer 22 determines that the press cylinder 1 and the cylinder line 4 are depressurized, the pressure relief valve 16 is closed again.
Es kann vorteilhaft sein, eine weitere Phase des Aufbaus eines Vordrucks anzuschließen. Dies geschieht in der zuvor beschriebenen Weise, nun aber mit einem höheren Vordruck, der durch entsprechend modifizierte Ansteuerung des 3 -Wege- Ventils 17 erreicht wird. Diese Phase kann ablaufen, während das nicht dargestellte obere Werkzeug auf dem ebenfalls nicht dargestellten Preßgut liegt. Es kann aber auch vorteilhaft sein, das obere Werkzeug geringfügig anzuheben.It can be advantageous to connect a further phase of building up a form. This is done in the manner described above, but now with a higher admission pressure, which is achieved by appropriately modified actuation of the 3-way valve 17. This phase can take place while the upper tool, not shown, lies on the material to be pressed, also not shown. However, it can also be advantageous to raise the upper tool slightly.
Nach der Phase zum Aufbau des Vordruckes bzw. der Vordrucke befindet sich der Kolben 9K innerhalb des Zylinders 9Z in einer Position nahe der unteren Endlage B, was durch den Wegaufhehmer 9W ermittelt wird. Diese Position ist erforderlich, um anschließend den erforderlichen Hauptpreßdruck erzeugen zu können. Nun folgt die nächste Phase des Pressenbetriebs, der Aufbau des Hauptpreßdrucks. Dies wird anhand der Fig. 3 und 4 nachfolgend beschrieben. In der Fig. 3 ist der erste Schritt dieser Phase gezeigt. In dieser Figur sind nun wiederum die angesteuerten Ventile durch schwarze Markierung der elektrischen Antriebe dargestellt und der Fluß des Hydraulikmediums ist mit Pfeilen neben den Leitungen angezeigt. Wie also aus der Fig. 3 zu ersehen ist, sind jetzt das Sperrventil 15 und das Hauptpreß-Ventil 14 angesteuert. Sperrventil 15 und Hauptpreß-Ventil 14 sind dann geöffnet. Diese beiden Ventile 14, 15 sind vorteilhaft elektrisch ansteuerbare AUF-ZU- Ventile. Auch Vorpreßventil 11, Niederdruckkammer-Einlaßventil 13, Niederdruckkammer- Auslaßventil 12 und Druckentlastungsventil 16 sind vorteilhafterweise von dieser Bauart.After the phase for building up the form or forms, the piston 9K is located within the cylinder 9Z in a position near the lower end position B, which is determined by the displacement sensor 9W. This position is necessary in order to subsequently be able to generate the required main pressure. Now the next phase of the press operation follows, the build-up of the main pressure. This is described below with reference to FIGS. 3 and 4. The first step of this phase is shown in FIG. In this figure, the actuated valves are again shown by black marking of the electric drives and the flow of the hydraulic medium is indicated by arrows next to the lines. As can be seen from Fig. 3, the check valve 15 and the main press valve 14 are now controlled. Check valve 15 and main press valve 14 are then open. These two valves 14, 15 are advantageously electrically controllable OPEN-CLOSE valves. Prepressing valve 11, low pressure chamber inlet valve 13, low pressure chamber outlet valve 12 and pressure relief valve 16 are advantageously of this type.
Durch das Ansteuern von Sperrventil 15 und Hauptpreß-Ventil 14 wird der Fluß des Hydraulikmediums vom Druckmittelspeicher 7 über die Speicherleitung 5, durch das Sperrventil 15, das Hauptpreß-Ventil 14 und durch die Zylinderleitung 4 zum Pressenzylinder 1 ermöglicht. Im Pressenzylinder 1 wird somit ein Druck aufgebaut, der vorwählbar ist, maximal aber dem Druck im Druckmittelspeicher 7 entspricht.By activating the shut-off valve 15 and the main press valve 14, the flow of the hydraulic medium from the pressure medium reservoir 7 via the storage line 5, through the shut-off valve 15, the main press valve 14 and through the cylinder line 4 to the press cylinder 1 is made possible. A pressure is thus built up in the press cylinder 1, which can be preselected, but at most corresponds to the pressure in the pressure medium reservoir 7.
In der Fig. 4 ist der zweite Schritt der Phase des Aufbaus des Hauptpreßdrucks gezeigt. Nun sind das Niederdruckkammer-Einlaßventil 13 und das Hauptpreß-Ventil 14 angesteuert, das heißt geöffnet, was wie bei den vorherigen Figuren dadurch markiert ist, daß die elektrischen Antriebe der Ventile 13, 14 schwarz dargestellt sind. Der sich dadurch einstellende Fluß des Hydraulikmediums ist wiederum mit Pfeilen neben den Leitungen gekennzeichnet. Nun strömt also Hydraulikmedium vom Druckmittelspeicher 7 durch die Speicherleitung 5, das geöffnete Niederdruckkammer-Einlaßventil 13 und durch die Druckumsetzer-Niederdruckleitung 10.1 in den Niederdruckraum 9.1 des Druckumsetzers 9. Der im Druckmittelspeicher 7 herrschende Druck entsteht dadurch auch im Niederdruckraum 9.1. Infolge des Flächenverhältnisses A92 zu A9 1 entsteht gleichzeitig im Hochdruckraum 9.2 ein höherer Druck, der also bei einem schon erwähnten Flächenverhältnis A9,2 zu A9 1 von 1 :2 doppelt so groß ist wie der Druck im Druckmittelspeicher 7. Weil nun aber auch das Hauptpreß-Ventil 14 geöffnet ist, baut sich im Pressenzylinder 1 ein ebenso hoher Druck auf. Beim Abschluß dieser Phase des Pressenbetriebs ist also der Druck im Pressenzylinder 1 unter den gegebenen Bedingungen doppelt so hoch wie der Druck im Druckmittelspeicher 7. Der Aufbau dieses Drucks im Pressenzylinder 1 wird vom Druckaufhehmer 22 verfolgt. Sobald der gewünschte Druck erreicht ist, werden das Niederdruckkammer- Einlaßventil 13 und das Hauptpreß-Ventil 14 wieder geschlossen. Es versteht sich, daß dieser Druckaufbau mit einem Fluß von Hydraulikmedium vom Druckmittelspeicher 7 in den Niederdruckraum 9.1 und vom Hochdruckraum 9.2 über die Zylinderleitung 4 zum Pressenzylinder 1 verbunden ist, wodurch auch der Kolben 9K in Richtung A verschoben wird. Wegen des Flächenverhältnisses A92 zu A9 1 ist dabei die Menge an Hydraulikmedium, die vom Hochdruckraum 9.2 abfließt, unter den gegebenen Bedingungen eines Flächenverhältnisses A92 zu A9 1 von 1 :2 nur halb so groß wie die Menge des Hydraulikmediums, das vom Druckmittelspeicher 7 her in den Niederdruckraum 9.1 einströmt.4, the second step of the phase of building the main pressure is shown. Now the low-pressure chamber inlet valve 13 and the main press valve 14 are activated, that is to say open, which is marked, as in the previous figures, by the fact that the electric drives of the valves 13, 14 are shown in black. The resulting flow of the hydraulic medium is in turn marked with arrows next to the lines. So now hydraulic medium flows from the pressure medium accumulator 7 through the accumulator line 5, the opened low pressure chamber inlet valve 13 and through the pressure converter low pressure line 10.1 into the low pressure chamber 9.1 of the pressure converter 9. The pressure prevailing in the pressure medium accumulator 7 thereby also arises in the low pressure chamber 9.1. As a result of the area ratio A 92 to A 9 1 , a higher pressure is simultaneously created in the high-pressure chamber 9.2, which is therefore at an area ratio A 9 , 2 to A 9 1 of 1: 2, which is twice as large as the pressure in the pressure medium reservoir 7. Because now but also the main press valve 14 is open, an equally high pressure builds up in the press cylinder 1. At the end of this phase of the press operation, the pressure in the press cylinder 1 is twice as high as the pressure in the pressure medium reservoir 7 under the given conditions. The build-up of this pressure in the press cylinder 1 is followed by the pressure receiver 22. As soon as the desired pressure is reached, the low-pressure chamber inlet valve 13 and the main press valve 14 are closed again. It is understood that this pressure build-up is connected to a flow of hydraulic medium from the pressure medium reservoir 7 into the low pressure chamber 9.1 and from the high pressure chamber 9.2 via the cylinder line 4 to the press cylinder 1, whereby the piston 9K is also displaced in direction A. Because of the area ratio A 92 to A 9 1 , the amount of hydraulic medium that flows from the high-pressure chamber 9.2 is, under the given conditions of an area ratio A 92 to A 9 1 of 1: 2, only half as large as the amount of hydraulic medium that flows from Pressure medium reservoir 7 flows into the low-pressure chamber 9.1.
Die Presse erreicht nun ihren maximalen Druck und führt die Pressung aus. Unter der Wirkung dieses Drucks sind auch die Spannungen in den Bauteilen der Presse auf den Maximalwerten. Da sich die Bauteile elastisch verformen, ist also in diesen Bauteilen Energie gespeichert. Ein weiteres Energiepotential stellt das kompressibleThe press now reaches its maximum pressure and carries out the pressing. Under the effect of this pressure, the stresses in the components of the press are also at the maximum values. Since the components deform elastically, energy is stored in these components. The compressible represents a further energy potential
Hydraulikmediumvolumen im Pressenzylinder 1, der Pressenleitung 4, der Druckumsetzer- Hochdruckleitung 10.2 und im Hochdruckraum 9.2 des Druckumsetzers 9 dar.Hydraulic medium 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.
Danach erfolgt nun eine Phase der Entlastung mit Spannungsabbau und Dekompression. Diese Phase erfolgt in drei Schritten, von denen die ersten beiden in den Fig. 5 und 6 dargestellt sind. Der erste Schritt ist in der Fig. 5 gezeigt. Jetzt sind das Hauptpreß- Ventil 14 und das Sperrventil 15 geöffnet, was analog zu den vorherigen Figuren mit schwarzer Markierung der Antriebe der Ventile 14, 15 dargestellt ist. Nun kann das Hydraulikmedium vom Pressenzylinder 1 zum Druckmittelspeicher 7 strömen, wobei es den Weg durch die Zylinderleitung 4, das Hauptpreß-Ventil 14, das Sperrventil 15 und die Speicherleitung 5 nimmt. Der Fluß kommt dadurch zustande, daß, wie zuvor erwähnt, der Druck im Pressenzylinder 1 größer ist als im Druckmittelspeicher 7. Der erste Schritt dauert so lange, bis die Drücke im Pressenzylinder 1 und im Druckmittelspeicher 7 gleich groß sind. Das heißt nun aber auch, daß ein ganz erheblicher Teil der in den Bauteilen der Presse gespeicherte Energie zurückgewonnen wird, indem der Druck im Druckmittelspeicher 7 erhöht wird. Dies ist ein entscheidender Vorteil der erfindungsgemäßen Steuervorrichtung und des Verfahrens zu deren Betrieb. Der zweite Schritt der Phase der Entlastung wird anhand der Fig. 6 beschrieben, wobei wiederum die Antriebe der angesteuerten Ventile schwarz ausgefüllt dargestellt sind und der Fluß von Hydraulikmedium mit Pfeilen an den Leitungen gekennzeichnet ist. Dieser zweite Schritt dient der Vorbereitung des nächsten Pressentaktes. Für diesen muß der Druckumsetzer 9 eine bestimmte Position Richtung der Endlage B einnehmen. Das noch verbleibende Volumen im Niederdruckraum 9.1 des Druckumsetzers ist dann so groß, daß die Vordrücke für den nächsten Arbeitstakt mit diesem Volumen realisiert werden können. Mit dem Wegaufhehmer 9W kann geprüft werden, ob dies der Fall ist. Ist dies nicht der Fall, so wird der im Pressenzylinder 1, in der Zylinderleitung 4 und in der Druckumsetzer- Hochdruckleitung 10.2 herrschende Restdruck durch Öffnen des Hauptpreß-Ventils 14 und des Niederdruckkammer- Auslaßventils 12 dazu benutzt, den Kolben 9K des Druckumsetzers 9 in die gewünschte Position zu bringen. Diese gewünschte Position ist in der Fig. 6 dargestellt. Dabei wird auch der Hochdruckraum 9.2 schon wieder mit unter Druck stehendem Hydraulikmedium befüllt, so daß für die Befüllung gar kein Hydraulikmedium aus dem Druckspeicher 7 entnommen werden muß. Das bedeutet eine weitere Energieeinsparung. Das bei der Bewegung des Kolbens 9K aus dem Niederdruckraum 9.1 verdrängte Hydraulikmedium gelangt über das Niederdruckkammer- Auslaßventil 12 durch die Tankleitung 8 in den Vorratsbehälter 2. Hat der Kolben 9K die gewünschte Position erreicht, was wie gesagt durch den Wegaufhehmer 9W ermittelt wird, so werden Niederdruckkammer- Auslaßventil 12 und Hauptpreß-Ventil 14 wieder geschlossen.Then there is a phase of relief with tension relief and decompression. This phase takes place in three steps, of which the first two are shown in FIGS. 5 and 6. The first step is shown in FIG. 5. Now the main press valve 14 and the shut-off valve 15 are open, which is shown analogously to the previous figures with black marking of the drives of the valves 14, 15. Now the hydraulic medium can flow from the press cylinder 1 to the pressure medium reservoir 7, taking the path through the cylinder line 4, the main press valve 14, the shut-off valve 15 and the accumulator line 5. The flow comes about from the fact that, as mentioned above, the pressure in the press cylinder 1 is greater than in the pressure medium reservoir 7. The first step lasts until the pressures in the press cylinder 1 and in the pressure medium reservoir 7 are equal. However, this now also means that a very substantial part of the energy stored in the components of the press is recovered by increasing the pressure in the pressure medium store 7. This is a decisive advantage of the control device according to the invention and the method for operating it. The second step of the relief phase is described with reference to FIG. 6, the drives of the actuated valves again being filled in black and the flow of hydraulic medium being indicated by arrows on the lines. This second step serves to prepare the next press cycle. For this, 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 admission pressures for the next work cycle can be realized with this volume. The 9W displacement sensor can be used to check whether this is the case. If this is not the case, the residual pressure prevailing in the press cylinder 1, in the cylinder line 4 and in the pressure converter high pressure line 10.2 by opening the main pressure valve 14 and the low pressure chamber outlet valve 12 is used to push the piston 9K of the pressure converter 9 into the bring desired position. This desired position is shown in FIG. 6. The high-pressure chamber 9.2 is also filled again with hydraulic medium under pressure, so that no hydraulic medium has to be removed from the pressure accumulator 7 for the filling. That means further energy savings. The hydraulic medium displaced from the low-pressure chamber 9.1 during the movement of the piston 9K passes via the low-pressure chamber outlet valve 12 through the tank line 8 into the reservoir 2. If the piston 9K has reached the desired position, which is determined by the displacement sensor 9W, as will be said Low pressure chamber outlet valve 12 and main pressure valve 14 closed again.
Anschließend wird im dritten Schritt der Restdruck im Pressenzylinder 1 und in der Zylinderleitung 4 noch völlig abgebaut, was dadurch erfolgt, daß nun das Druckentlastungsventil 16 geöffnet wird. Dabei fließt unter der Wirkung des Restdrucks Hydraulikmedium vom Pressenzylinder 1 durch die Zylinderleitung 4, dasSubsequently, in the third step, the residual pressure in the press cylinder 1 and in the cylinder line 4 is completely reduced, which is done by opening the pressure relief valve 16. Hydraulic medium flows from the press cylinder 1 through the cylinder line 4 under the effect of the residual pressure
Druckentlastungsventil 16 und die Tankleitung 8 in den Vorratsbehälter 2. Der Fluß hört auf, sobald der Restdruck im Pressenzylinder 1 völlig abgebaut ist. Dann wird das Druckentlastungsventil 16 wieder geschlossen.Pressure relief valve 16 and the tank line 8 into the reservoir 2. The flow stops as soon as the residual pressure in the press cylinder 1 is completely reduced. Then the pressure relief valve 16 is closed again.
Gleichzeitig bleibt aber der Druck im Hochdruckraum 9.2 und in der Druckumsetzer- Hochdruckleitung 10.2 erhalten. Dieser Druck kann beim nächsten Pressentakt genutzt werden, was wiederum eine Energieeinsparung ergibt, da der Druck nicht neu aufgebaut werden muß. In der Fig. 7 ist eine Variante der erfindungsgemäßen Pressensteuerung gezeigt. Gegenüber dem Beispiel der Fig. 1 besteht die einzige Änderung darin, daß der Druckumsetzer 9' eine andere Bauart aufweist als der Druckumsetzer 9 nach den Fig. 1 bis 6. Der Druckumsetzer 9' besteht im wesentlichen aus einer ersten Pumpe 23, deren Welle 24 starr mit einer zweiten Pumpe 25 gekoppelt ist, so daß die Welle 24 beiden Pumpen 23, 25 gemeinsam ist. Die erste Pumpe 23 ist einerseits mit der Druckumsetzer- Niederdruckleitung 10.1 verbunden, wobei diese Seite der Pumpe 23 als Niederdruckraum 9.1 wirkt, andererseits mit einem Tank 26. Die zweite Pumpe 25 ist einerseits mit der Druckumsetzer-Hochdruckleitung 10.2 verbunden, wobei diese Seite der Pumpe 25 als Hochdruckraum 9.2 wirkt, und ebenfalls andererseits mit dem Tank 26. Die beiden Pumpen 23, 25 werden nicht von einem Motor angetrieben, sondern wirken durch die starre Verbindung jeweils als Einheit von Pumpe und Hydromotor. Als Druckumsetzer ist diese Kombination der beiden Pumpen 23, 25 dadurch wirksam, daß das spezifische Fördervolumen, also das Volumen pro Umdrehung, unterschiedlich ist, was in der Fig. 7 symbolisch durch die unterschiedliche Größe der Pumpen 23, 25 dargestellt ist. So beträgt beispielsweise dieses Verhältnis 2:1. Das kommt auch dadurch zustande, daß die der Förderung des Hydraulikmediums durch die beiden Pumpen 23, 25 in diesen wirksamen Flächen den Flächen bzw. A9.2 gemäß dem ersten Ausführungsbeispiel entsprechen. Entsprechend verhält sich der Druckumsetzer 9' ganz genau so wie der Druckumsetzer 9 während der in den Fig. 2 bis 6 dargestellten und anhand dieser Figuren beschriebenen unterschiedlichen Phasen des Pressenbetriebs. Während der zuvor erwähnten ersten Phase des Pressenbetriebs wirkt beispielsweise der Druckumsetzer 9' als Druckuntersetzer, wobei die zweite Pumpe 25 als Hydromotor arbeitet und die erste Pumpe 23 antreibt. Bei der Wirkung als Druckübersetzer wirkt die erste Pumpe 23 als Hydromotor, der die zweite Pumpe 25 antreibt. Die einzelnen Phasen und deren Schritte eines Pressentaktes entsprechen dem zuvor Beschriebenen.At the same time, however, the pressure in the high-pressure chamber 9.2 and in the pressure converter high-pressure line 10.2 is maintained. This pressure can be used at the next press cycle, which in turn results in energy savings since the pressure does not have to be built up again. 7 shows a variant of the press control system according to the invention. Compared to the example of FIG. 1, the only change is that the pressure converter 9 'has a different design than the pressure converter 9 according to FIGS. 1 to 6. The pressure converter 9' essentially consists of a first pump 23, the shaft 24 of which 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 acting as low pressure chamber 9.1, on the other hand to 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 25 acts as a high-pressure chamber 9.2, and also on the other hand with the tank 26. The two pumps 23, 25 are not driven by a motor, but rather act as a unit of pump and hydraulic motor due to the rigid connection. This combination of the two pumps 23, 25 is effective as a pressure converter in that the specific delivery volume, that is to say the volume per revolution, is different, which is symbolically represented in FIG. 7 by the different sizes of the pumps 23, 25. For example, this ratio is 2: 1. This is also due to the fact that the promotion of the hydraulic medium by the two pumps 23, 25 in these effective areas the surfaces or A 9 . 2 according to the first embodiment. Correspondingly, the pressure converter 9 'behaves exactly like the pressure converter 9 during the different phases of the press operation shown in FIGS. 2 to 6 and described with reference to these figures. During the aforementioned first phase of the press operation, for example, the pressure converter 9 'acts as a pressure reducer, the second pump 25 working as a hydraulic motor and driving the first pump 23. When acting as a pressure intensifier, the first pump 23 acts as a hydraulic motor which drives the second pump 25. The individual phases and their steps of a press cycle correspond to those described above.
Vorteilhaft ist dabei auch, daß ein Wegaufhehmer 9W nicht erforderlich ist und der Druckumsetzer 9' zur Vorbereitung des nächsten Pressentaktes keine bestimmte Stellung einnehmen muß, was das Steuerverfahren vereinfacht.It is also advantageous that a Wegaufhehmer 9W is not required and the pressure converter 9 'does not have to assume a specific position in preparation for the next press cycle, which simplifies the control process.
Trotz des sehr einfachen Aufbaus der erfindungsgemäßen Steuervorrichtung läßt sich mit dieser Energie einzelner Pressschritte zurückgewinnen. So wird, wie zuvor beschrieben, sogar die in der Presse, im Pressgut und im kompressiblen Hydrauliköl elastisch gespeicherte Energie zurückgewonnen. Dabei kommt die Steuervorrichtung ohne teure Bauelemente wie verstellbare Pumpen aus.Despite the very simple construction of the control device according to the invention, individual pressing steps can be recovered with this energy. As described above, even those in the press, in the material to be pressed and in the compressible hydraulic oil become elastic recovered stored energy. The control device manages without expensive components such as adjustable pumps.
Durch Versuche wurde festgestellt, daß durch die erfindungsgemäße Steuervorrichtung eine beträchtliche Energieeinsparung gegenüber dem vorbekannten Stand der Technik erzielbar ist. Die Energieeinsparung kann durchaus gegen 40 % erreichen.Experiments have shown that the control device according to the invention achieves considerable energy savings compared to the prior art. The energy saving can well reach around 40%.
Die Erfindung kann grundsätzlich bei hydraulischen Pressen verschiedener Bauart für verschiedene Anwendungsgebiete mit großem Vorteil genutzt werden. Die Presse kann dabei mit Differentialzylindern, Gleichgangzylindern oder auch Plungerzylindern ausgestattet sein. Besonders vorteilhaft ist es, wenn die erfindungsgemäße Steuervorrichtung bei Pressen für die Formgebung keramischer Teile wie Fliesen benutzt wird.In principle, the invention can be used with great advantage in hydraulic presses of various types for various fields of application. The press can be equipped with differential cylinders, synchronous cylinders or even plunger cylinders. It is particularly advantageous if the control device according to the invention is used in presses for shaping ceramic parts such as tiles.
Anhand des zuvor beschriebenen Aufbaus und der gleichzeitig beschriebenen Wirkungsweise ergibt sich, daß sowohl der Aufbau der Vorrichtung als auch die Betriebsweise, also das Steuerungsverfahren, Gegenstand der Erfindung sind. Based on the structure described above and the mode of operation described at the same time, it follows that both the structure of the device and the mode of operation, that is to say the control method, are the subject of the invention.
BezugszeichenlisteLIST OF REFERENCE NUMBERS
1 Pressenzylinder1 press cylinder
2 Vorratsbehälter2 storage containers
3 Ventilgruppe3 valve group
4 Zylinderleitung4 cylinder line
5 Speicherleitung5 storage line
6 Hydraulikpumpe6 hydraulic pump
7 Druckmittelspeicher7 pressure medium accumulator
8 Tankleitung8 tank line
9 . Druckumsetzer (erste Ausführungsvariante)9. Pressure converter (first version)
9' Druckumsetzer (zweite Ausführungsvariante)9 'pressure converter (second variant)
9.1 Niederdruckraum9.1 Low pressure room
9.2 Hochdruckraum9.2 High pressure room
9Z Zylinder9T cylinder
9K Kolben9K pistons
9S Kolbenstange9S piston rod
9W Wegaufhehmer9W displacement sensor
10.1 Druckumsetzer-Niederdruckleitung10.1 Pressure converter low pressure line
10.2 Druckumsetzer-Hochdruckleitung10.2 Pressure converter high pressure line
11 Vorpreßventil11 Prepress valve
12 Niederdruckkammer-Auslaßventil12 low pressure chamber outlet valve
13 Niederdruckkammer-Einlaßventil13 low pressure chamber inlet valve
14 Hauptpreß-Ventil14 main press valve
15 Sperrventil15 shut-off valve
16 Druckentlastungsventil16 pressure relief valve
17 3 -Wege- Ventil17 3-way valve
18 Rückschlagventil18 check valve
19 Preßleitung 0 Steuergerät19 Press line 0 control unit
21 Pressensicherheits-Senk- und Rückzugssteuerung 2 Druckaufhehmer 3 erste Pumpe 4 Welle 5 zweite Pumpe 6 Tank 21 Press safety lowering and retraction control 2 pressure transducers 3 first pump 4 shaft 5 second pump 6 tank

Claims

Patentansprüche claims
1. Steuervorrichtung für eine hydraulische Presse mit einem Pressenzylinder (1), einem Vorratsbehälter (2), einer Ventilgruppe (3), einem Druckmittelspeicher (7) und einer Hydraulikpumpe (6), wobei Pressenzylinder (1), Vorratsbehälter (2), Ventilgruppe (3), Druckmittelspeicher (7) und Hydraulikpumpe (6) mittels einer Zylinderleitung (4), einer Speicherleitung (5) und einer Tankleitung (8) untereinander verbunden sind, dadurch gekennzeichnet, daß der Ventilgruppe (3) ein Druckumsetzer (9; 9') zugeordnet ist, der als Druckübersetzer und als Druckuntersetzer betreibbar ist.1. Control device for a hydraulic press with a press cylinder (1), a reservoir (2), a valve group (3), a pressure medium reservoir (7) and a hydraulic pump (6), with press cylinder (1), reservoir (2), valve group (3), pressure medium accumulator (7) and hydraulic pump (6) are interconnected by means of a cylinder line (4), a storage line (5) and a tank line (8), characterized in that the valve group (3) has a pressure converter (9; 9 ') is assigned, which can be operated as a pressure intensifier and as a pressure coaster.
2. Steuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Druckumsetzer (9) aus einem in einem Zylinder (9Z) verschiebbaren Kolben (9K) und einer mit dem Kolben (9K) starr verbundenen Kolbenstange (9S) besteht, wobei der Druckumsetzer (9) einen Niederdruckraum (9.1) und einen Hochdruckraum (9.2) aufweist, die voneinander durch den Kolben (9K) getrennt sind, und daß der Niederdruckraum (9.1) einen größeren Querschnitt A9 1 aufweist als der Hochdruckraum (9.2), der einen Querschnitt A9.2 besitzt.2. Control device according to claim 1, characterized in that the pressure converter (9) consists of a piston (9K) displaceable in a cylinder (9Z) and a piston rod (9S) rigidly connected to the piston (9K), the pressure converter (9 ) has a low pressure chamber (9.1) and a high pressure chamber (9.2), which are separated from each other by the piston (9K), and that the low pressure chamber (9.1) has a larger cross section A 9 1 than the high pressure chamber (9.2), which has a cross section A. 9 . 2 owns.
3. Steuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Druckumsetzer (9') aus einer ersten Pumpe (23) mit größerem spezifischen Fördervolumen und einer zweiten Pumpe (25) mit kleinerem spezifischen Fördervolumen besteht, die starr mittels einer Welle (24) verbunden sind, wobei die eine Seite der ersten Pumpe (23) als Niederdruckraum (9.1) wirkt und die eine Seite der zweiten Pumpe (25) als Hochdruckraum (9.2) wirkt.3. Control device according to claim 1, characterized in that the pressure converter (9 ') consists of a first pump (23) with a larger specific delivery volume and a second pump (25) with a smaller specific delivery volume, which is rigidly connected by means of a shaft (24) , one side of the first pump (23) acting as a low pressure chamber (9.1) and one side of the second pump (25) acting as a high pressure chamber (9.2).
4. Steuervorrichtung nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß der Niederdruckraum (9.1) über eine Druckumsetzer-Niederdruckleitung (10.1) an die Ventilgruppe (3) angeschlossen ist und daß diese Druckumsetzer- Niederdruckleitung (10.1) verbunden ist4. Control device according to claim 2 or 3, characterized in that the low pressure chamber (9.1) via a pressure converter low pressure line (10.1) is connected to the valve group (3) and that this pressure converter low pressure line (10.1) is connected
- mit einem Vorpreßventil (11), dessen zweiter Anschluß an der Zylinderleitung (4) liegt,- With a pre-press valve (11), the second connection of which is located on the cylinder line (4),
- mit einem Niederdruckkammer-Einlaßventil (13), dessen zweiter Anschluß an der Speicherleitung (5) liegt, und- With a low pressure chamber inlet valve (13), the second connection to the storage line (5), and
- mit einem Niederdruckkammer- Auslaßventil (12), dessen zweiter Anschluß an der Tankleitung (8) liegt, und daß der Hochdruckraum (9.2) über eine Druckumsetzer-Hochdruckleitung (10.2) an die Ventilgruppe (3) angeschlossen ist und daß diese Druckumsetzer- Hochdruckleitung (10.2) verbunden ist- With a low pressure chamber outlet valve (12), the second connection to the tank line (8), and that the high pressure chamber (9.2) is connected to the valve group (3) via a pressure converter high pressure line (10.2) and that this pressure converter high pressure line (10.2) is connected
- mit einem Hauptpreß-Ventil (14), dessen zweiter Anschluß an der Zylinderleitung (4) liegt,- With a main press valve (14), the second connection to the cylinder line (4),
- mit einem Sperrventil (15), dessen zweiter Anschluß an der Speicherleitung (5) liegt, und- With a check valve (15), the second connection to the storage line (5), and
- über ein Rückschlagventil (18) und eine Preßleitung (19) mit einem 3-Wege- Ventil (17), dessen zweiter Anschluß an der Speicherleitung (5) liegt, und dessen dritter Anschluß an der Tankleitung (8) liegt.- Via a check valve (18) and a press line (19) with a 3-way valve (17), the second connection to the storage line (5), and the third connection to the tank line (8).
5. Steuervorrichtung nach Anspruch 4, dadurch gekennzeichnet, daß das 3 -Wege- Ventil (17) proportional steuerbar ist.5. Control device according to claim 4, characterized in that the 3-way valve (17) is proportionally controllable.
6. Steuervorrichtung nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß zwischen der Zylinderleitung (4) und der Tankleitung (8) ein Druckentlastungsventil (16) angeordnet ist.6. Control device according to claim 4 or 5, characterized in that between the cylinder line (4) and the tank line (8) a pressure relief valve (16) is arranged.
7. Steuervorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß7. Control device according to claim 6, characterized in that
Vorpreßventil (11), Niederdruckkammer-Einlaßventil (13), Niederdruckkammer- Auslaßventil (12), Hauptpreß-Ventil (14), Sperrventil (15) und Druckentlastungsventil (16) elektrisch steuerbare AUF-ZU- Ventile sind.Prepress valve (11), low pressure chamber inlet valve (13), low pressure chamber outlet valve (12), main press valve (14), shut-off valve (15) and pressure relief valve (16) are electrically controllable on-off valves.
8. Verfahren zur Steuerung einer hydraulischen Presse mit einem Pressenzylinder (1), einem Vorratsbehälter (2), einer Ventilgruppe (3), einem Druckmittelspeicher (7) und einer Hydraulikpumpe (6), wobei Pressenzylinder (1), Vorratsbehälter (2), Ventilgruppe (3), Druckmittelspeicher (7) und Hydraulikpumpe (6) mittels einer Zylinderleitung (4), einer Speicherleitung (5) und einer Tankleitung (8) untereinander verbunden sind, dadurch gekennzeichnet, daß ein der Ventilgruppe (3) zugeordneter Druckumsetzer (9; 9') als Druckübersetzer und als Druckuntersetzer betreibbar ist.8. Method for controlling a hydraulic press with a press cylinder (1), a reservoir (2), a valve group (3), a pressure medium reservoir (7) and a hydraulic pump (6), with press cylinder (1), reservoir (2), Valve group (3), pressure medium accumulator (7) and hydraulic pump (6) are interconnected by means of a cylinder line (4), a storage line (5) and a tank line (8), characterized in that a pressure converter (9) assigned to the valve group (3) ; 9 ') can be operated as a pressure booster and as a pressure coaster.
9. Verfahren nach Anspruch 8, dadurch gekennzeichnet, daß in der Ventilgruppe (3) gemäß den Ansprüchen 3 und 5 angeordnete Ventile in der Weise betrieben werden,9. The method according to claim 8, characterized in that in the valve group (3) according to claims 3 and 5 arranged valves are operated in the manner
- daß in einem ersten Verfahrensschritt durch Ansteuerung des 3 -Wege- Ventils (17) und des Vorpreß ventils (11) der Druckumsetzer (9; 9') als Druckuntersetzer wirkt und im Pressenzylinder (1) ein Vordruck aufgebaut wird, - daß in einem weiteren Verfahrensschritt durch Ansteuerung des Sperrventils (15) und des Hauptpreß- Ventils (14) im Pressenzylinder (1) ein Druck aufgebaut wird, der vorwählbar ist und maximal dem Druck im Druckmittelspeicher (7) entspricht,- That in a first process step by controlling the 3-way valve (17) and the pre-press valve (11) the pressure converter (9; 9 ') acts as a pressure reducer and a pre-pressure is built up in the press cylinder (1), - That in a further process step by controlling the shut-off valve (15) and the main press valve (14) in the press cylinder (1), a pressure is built up which can be selected and which corresponds at most to the pressure in the pressure medium reservoir (7),
- daß in einem daran anschließenden weiteren Verfahrensschritt durch Ansteuerung des Hauptpreß- Ventils (14) und des Niederdruckkammer-Einlaßventils (13) der- That in a subsequent further process step by controlling the main pressure valve (14) and the low pressure chamber inlet valve (13)
Druckumsetzer (9; 9') als Druckübersetzer wirkt und im Pressenzylinder (1) ein Druck aufgebaut wird, der höher ist als der Druck im Druckmittelspeicher (7),Pressure converter (9; 9 ') acts as a pressure intensifier and a pressure is built up in the press cylinder (1) that is higher than the pressure in the pressure medium reservoir (7),
- daß in einem daran anschließenden weiteren Verfahrensschritt durch Ansteuerung des Hauptpreß- Ventils (14) und des Sperrventils (15) der im Pressenzylinder (1) herrschende Druck abgebaut wird, bis er so hoch ist wie der Druck im Druckmittelspeicher (7),- That in a subsequent further process step by controlling the main pressure valve (14) and the shut-off valve (15) the pressure prevailing in the press cylinder (1) is reduced until it is as high as the pressure in the pressure medium reservoir (7),
- daß gegebenenfalls in einem daran anschließenden weiteren Verfahrensschritt durch Ansteuerung des Hauptpreß- Ventils (14) und des Niederdruckkammer- Auslaßventils (12) der Kolben (9K) des Druckumsetzers (9) in eine für einen nächsten Pressentakt gewünschte Position gebrach wird, und - daß zuletzt durch Ansteuerung des Druckentlastungsventils (16) der Restdruck im Pressenzylinder (1) abgebaut wird.- That, if appropriate, in a subsequent further process step by actuating the main pressure valve (14) and the low-pressure chamber outlet valve (12), the piston (9K) of the pressure converter (9) is brought into a position desired for a next press cycle, and - that Finally, the residual pressure in the press cylinder (1) is reduced by activating the pressure relief valve (16).
10. Verfahren nach Anspruch 9, dadurch gekennzeichnet, daß im Abschluß an den ersten Verfahrensschritt dieser erste Verfahrensschritt wiederholt wird, wobei durch eine modifizierte Ansteuerung des 3 -Wege- Ventils ein höherer Vordruck aufgebaut wird.10. The method according to claim 9, characterized in that at the end of the first process step, this first process step is repeated, a higher admission pressure being built up by a modified actuation of the 3-way valve.
11. Verwendung einer Steuervorrichtung nach den Ansprüchen 1 bis 7 und gemäß dem Verfahren nach den Ansprüchen 8 bis 10 bei einer Presse für die Formgebung keramischer Teile wie Fliesen. 11. Use of a control device according to claims 1 to 7 and according to the method according to claims 8 to 10 in a press for the shaping of ceramic parts such as tiles.
EP01956735A 2000-09-20 2001-08-24 Controller for a hydraulic press and method for the operation thereof Expired - Lifetime EP1318906B1 (en)

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CH182600 2000-09-20
CH18262000 2000-09-20
PCT/IB2001/001527 WO2002024441A1 (en) 2000-09-20 2001-08-24 Controller for a hydraulic press and method for the operation thereof

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EP1318906B1 EP1318906B1 (en) 2009-09-30

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CA2422879A1 (en) 2003-03-19
BR0113991B1 (en) 2010-05-18
US20030167936A1 (en) 2003-09-11
WO2002024441A1 (en) 2002-03-28
CN1243637C (en) 2006-03-01
DE50115141D1 (en) 2009-11-12
EP1318906B1 (en) 2009-09-30
AU2001278651A1 (en) 2002-04-02
ATE444157T1 (en) 2009-10-15
BR0113991A (en) 2003-08-12
JP5058426B2 (en) 2012-10-24
US6973780B2 (en) 2005-12-13
KR20030032042A (en) 2003-04-23
ES2329443T3 (en) 2009-11-26
CN1461255A (en) 2003-12-10

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