EP3056291B1 - Presse dotée d'un amortisseur de choc de coupe - Google Patents

Presse dotée d'un amortisseur de choc de coupe Download PDF

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Publication number
EP3056291B1
EP3056291B1 EP15154818.7A EP15154818A EP3056291B1 EP 3056291 B1 EP3056291 B1 EP 3056291B1 EP 15154818 A EP15154818 A EP 15154818A EP 3056291 B1 EP3056291 B1 EP 3056291B1
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EP
European Patent Office
Prior art keywords
counter
hydraulic
pressure
cylinder
press
Prior art date
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EP15154818.7A
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German (de)
English (en)
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EP3056291A1 (fr
Inventor
Volker Treffler
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Moog Luxembourg SARL
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Moog Luxembourg SARL
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Publication of EP3056291A1 publication Critical patent/EP3056291A1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/02—Die-cushions
    • 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
    • B30B15/18—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram
    • B30B15/20—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram controlling the speed of the ram, e.g. the speed of the approach, pressing or return strokes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D28/00—Shaping by press-cutting; Perforating
    • B21D28/02—Punching blanks or articles with or without obtaining scrap; Notching
    • B21D28/20—Applications of drives for reducing noise or wear

Definitions

  • the invention relates to hydraulic presses with integrated cutting impact damping according to the preamble of claim 1 and a method for operating such a press.
  • Hydraulic presses have the advantage of good press force over mechanical presses and are used for deformation, cutting or punching processes on workpieces.
  • the working tool is brought into contact with the workpiece by means of hydraulic cylinders and the force exerted on the workpiece (forming force) is increased until the workpiece is deformed, cut or provided with punched holes in the desired manner.
  • the maximum force is achieved for example in punching or cutting processes shortly before the material breakdown in the workpiece.
  • the counter-holding force disappears abruptly through the workpiece, so that the working tool undergoes a sudden movement under maximum pressure in the direction of the exerted deformation force. This effect is referred to as a cutting stroke and represents a high mechanical load on the press.
  • DE102009048483A1 discloses a device for cutting impact damping in pressing and punching machines, which a machine frame, a fixed to the upper part of the machine frame working cylinder for moving the Working tool and also attached there pressurized support cylinder has. During the working process, the working cylinder exerts a force on the workpiece, which also elastically deforms the upper part of the machine frame.
  • cutting shock press the support cylinder after material breakthrough from the top of the material frame, so that the elastic deformation can degrade only slowly without cutting shock.
  • the deformation energy is converted into heat and is thus lost for the rest of the process. Therefore, this form of cut impact damping is not energy efficient.
  • document DE 196 43 396 B4 also discloses a generic hydraulic press with cutting impact damping, in which in addition to a working cylinder four counter-holding cylinders are connected in differential circuit with a plunger as a working tool. So that these counter-holding cylinders on the press table can dampen the material breakdown impact during the punching process, the piston top sides of the working cylinder and the piston side of the counter-holding cylinders are interconnected via a control valve. The fact that the sum of the piston surfaces of the counter-holding cylinder is greater than the piston surface of the working cylinder is ensured by a corresponding bias on the annulus side of the counter-holding cylinder that both directions of force are in equilibrium, that is, the plunger stands still.
  • the movement of the plunger is regulated.
  • the oil is exchanged between the piston sides of the working cylinder and the counter-holding cylinder, wherein the volume fraction from the unequal area ratios filled into a memory or removed.
  • a pump is additionally required for transferring and subsequent delivery of the hydraulic fluid.
  • the force available through the power cylinder is predetermined by the design of the cylinder geometry and no longer adaptable to any other applications.
  • the hydraulic fluid must be in the pipelines here for long periods to move the Working tool accelerated or delayed, which is not suitable for quick-lifting movements.
  • a hydraulic press with integrated impact damping comprising a machine frame with a press table, a work tool mounted in the machine frame for exerting a forming force on a workpiece to be arranged on a press table during a machining operation and at least one press cylinder and at least one counter-holding cylinder respectively attached to the machine frame, the press cylinder being mechanically connected to the work tool moving tool via a press cylinder rod and the counterhold cylinder via a counterhold cylinder rod, the press cylinder being connected to a first hydraulic assembly at a first pressure for moving the press cylinder via a first proportional valve, characterized in that the counter-holding cylinder with a second hydraulic arrangement designed to be separated from the first hydraulic arrangement, under a second pressure for loading movement of the counter-holding cylinder is connected via a second continuous valve, and the first and second proportional valves are connected to a control unit, wherein the control unit is adapted to control the continuous valves for pressurizing the pressing and counter-holding cylinders so simultaneously and adapted to one another
  • the inventive hydraulic press refers to a press that can be used for forming, cutting or stamping processes.
  • high-speed presses in particular presses are referred to, which can reach a stroke rate of, for example, more than 150 strokes per minute.
  • the integrated cutting impact damping designates a cutting impact damping generated by the operating conditions of the press. Such a cutting impact damping is particularly advantageous for high-speed presses with forming forces of, for example, 5000 kN.
  • the machine frame designates the mechanical construction or arrangement to which the interacting components such as press cylinder, press table and counter-holding cylinder are attached, so that these components can not mutually shift when the forming force is exerted on the workpiece.
  • the configuration of the machine frame can be suitably selected by the person skilled in the art within the scope of the present invention.
  • the press table represents a support of the workpiece for subsequent processing.
  • the press table may comprise suitably designed means for holding and fixing the workpiece during processing.
  • the working tool is adapted to the respective desired machining (forming process, cutting process, punching process).
  • the working tool can be suitably selected by the person skilled in the art within the scope of the present invention.
  • the forming force exerted by the working tool on the workpiece denotes the force with which the workpiece is deformed, cut or punched by the working tool.
  • the forming force is applied and defined by the interaction of pressing and counter-holding cylinder in conjunction with the controls of the continuous valves by the controller.
  • the workpiece can be any workpiece suitable for machining by pressing.
  • workpieces may be metal plates or three-dimensional metal bodies into which holes are punched.
  • the workpieces can also be made of other materials consist of or include in part.
  • As a process gear here the process of the press is referred to, in which the working tool moves in the direction of the workpiece and the machining of the workpiece is performed. After completion of the machining of the workpiece by the press, the working tool is removed in a retraction phase again from the press table or the workpiece so that the press can perform a new machining operation on the same workpiece or a new workpiece again.
  • the pressing cylinder and the counter-holding cylinder may be any suitable for this type of press cylinder, each comprising a cylinder rod (here the press cylinder rod and the counter holding cylinder rod) for transmitting the movement of the piston on the working tool.
  • Pressing and counter-holding cylinders are, for example, differential cylinders which have a piston rod only on one side of the piston surface.
  • differential cylinders have two different sized effective surfaces: on the one hand, the surface on the piston side, which acts completely, and on the other hand, the rod-side surface, in which only the annular surface acts.
  • Pressing and / or counter-holding cylinders can also be tandem cylinders for increasing the forces acting on the piston surfaces in other embodiments.
  • the cylinder rod of the press and counter-holding cylinders are not directly connected, but mechanically connected to each other via the working tool.
  • the two types of cylinders can perform only a common same movement, wherein an extension of the press cylinder rod from the press cylinder requires retraction of the counter-holding cylinder rod in the counter-holding cylinder and vice versa, to allow movement of the working tool.
  • a control device controls the synchronized simultaneous movement of the pressing and counter-holding cylinders via control of the first and second continuous valves.
  • the movement of the cylinder rods of the press and counter-holding cylinder is made possible and supported by the software by the control unit.
  • the press and counter-holding cylinders in the press according to the invention are coupled by software.
  • the first and second are Hydraulic arrangements for operating the press and counter-holding cylinder separately, ie without hydraulic effective connection to each other executed.
  • the term "disconnected" thus includes, for example, the possibility of discharging the hydraulic fluids from the first and second assemblies into the same catch tank, as this manner of combining the hydraulic fluids from the first and second assemblies will not affect the first or second Can unfold arrangements.
  • the spring mass system consisting of the moving masses and the hydraulic capacity is extremely small and thus designed low and allows very high stroke rates.
  • the first and second hydraulic assemblies designate a number of components connected to each other via hydraulic lines.
  • first and second pressures For generating first and second pressures, respectively, these arrangements comprise at least one or more suitable pressure accumulators which maintain the first and second pressures in the hydraulic lines via suitable connections.
  • first and / or second arrangements are connected to an additional pressure supply, so that any pressure losses or losses of hydraulic fluid can be compensated.
  • the first and second arrangements may include other components depending on the application.
  • the continuous valves which are each arranged between the pressing or counter-holding cylinders and the first and second hydraulic arrangements, can regulate the volume flow in accordance with the desired value of the control unit continuously.
  • the control unit can adjust the volume flow and its direction depending on the operating phase of the press and desired operating conditions via a corresponding control of the continuous valves.
  • the volume flow of the hydraulic fluid through the continuous valve through into the cylinder chamber of the corresponding cylinder or in the first or second hydraulic arrangement into arbitrarily limited time intervals can be set arbitrarily.
  • the continuous valves comprise at least one switching position which allows a variably adjustable throttling of the first and / or second pressures for the variable pressurization by the continuous valves by the control unit.
  • variable selectable pressurization of the pressing and counter-holding cylinder not achieved by the first and second pressures, but by their throttling on the controlled continuous valves.
  • the adjustable restriction includes that the desired pressure is adjusted by means of a throttled valve and then the valve is closed, as long as the applied pressure corresponds to the desired pressure.
  • the usual cutting impact is avoided, for example, when punching high-strength materials as far as possible and the energy released when material is broken due to the stamping in the second hydraulic arrangement returned damped.
  • the kinetic energy is stored by the connected accumulators. This avoids that the switching to a throttling and the thus effective cutting impact damping of a hydraulic threshold or a differential pressure-dependent throttle valve, which converts the deformation energy into heat during the return stroke of the working tool.
  • the control unit comprises, for example, a processor and a data memory, in which corresponding control specifications are stored and which can be accessed by the processor for executing the control.
  • suitable control algorithms for controlling the hydraulic press may be executed on the processor. If the press is to be used for another application, only a suitable control algorithm needs to be loaded into the control unit for optimal operation of the press, or a suitable control algorithm must be selected from a plurality of already loaded control algorithms in the control unit without making any hardware adjustments Press would have to be made. If the control unit is connected to a computer network, such a software adaptation of the press to other applications could also be carried out by means of remote adaptation without having to be done on site by service technicians.
  • the kinetic energy of the pressing cylinder is buffered via the second continuous valve in a pressure accumulator of the second arrangement via a pressure increase in the pressure accumulator during workpiece breakthrough, whereby the bias of the press increases and thus the cutting impact damping is effected.
  • the kinetic energy stored in this accumulator can later be fed back into the workflow of the thereby energy-efficient press.
  • the present invention provides a variably employable hydraulic press for high-speed forming, cutting or stamping processes with an energy-efficient integrated cutting impact damping without large throttling losses available.
  • the continuous valves are servo valves with switching times less than 20 ms.
  • the servo valves are designed as 3/3-way built-in servo valves with extremely short switching times less than 10ms, which have a high bandwidth, are equipped with digital integrated valve electronics and can be controlled by the control unit via a fast bus system. These servo valves allow precise control of the control edges to each other in the various operating phases of the press such as processing and retraction phase.
  • the minimum value of the prestressing is between 20% and 50% of the deformation force, preferably between 30% and 45% of the deformation force, particularly preferably between 38% and 42% of the deformation force.
  • the minimum value ensures that the bias has at least the minimum value.
  • Such a bias of the press provides a cutting shock damping, which sufficiently dampens the plant stress cutting strokes.
  • the bias is ideally about 40% of the forming force (nominal value) of the press and can be lowered as needed for a higher forming force (for example, high-strength materials).
  • a bypass line and a switching valve disposed therein, preferably a 2/2-way valve, connected to each other, wherein the switching valve is also connected to the control unit.
  • the control unit can, if necessary for a higher forming force as an alternative to an increase in the first pressure basically lower the bias on the bypass line in order to achieve a material breakdown of the workpiece or achievable only at high pressure material deformation, which might not be possible with original bias
  • the bypass line may also be connected to an additional catch tank for discharging the hydraulic fluid via, for example, a check valve. The check valve seals the bypass line to the outside.
  • the first hydraulic arrangement comprises a first pressure accumulator for storing the first pressure and the second hydraulic arrangement comprises a second pressure accumulator for storing the second pressure, wherein the first pressure is a higher pressure than the second pressure.
  • the second pressure accumulator is provided for storing kinetic energy of the pressing cylinder in the form of an increased pressure in the cutting impact damping and for releasing this energy to the return stroke (retraction phase) of the pressing cylinder by means of an increased bias of the counter-holding cylinder.
  • the first accumulator is a high-pressure accumulator with pressures in the range of 350 bar and the second accumulator is a medium-pressure accumulator with pressures in the range of 210 bar.
  • first and second hydraulic arrangements are each connected to a first or second pressure supply. This connection is preferably carried out via check valves. These check valves seal the first and second assemblies at least up to the first or second pressures to the outside. As a result, permanent constant positions of the pressure applied in the first and second hydraulic arrangements can be ensured.
  • the press comprises a plurality of counter-holding cylinders, which are each mechanically connected via their counter-holding cylinder rods with the working tool.
  • the counter-holding cylinders are preferably arranged symmetrically to one another. Thus, tilting of the working tool due to the cutting stroke are avoided, allowing a more effective material-gentle damping of the press.
  • the counter-holding cylinders are connected to one another via a corresponding hydraulic circuit and the hydraulic circuit is connected to the second hydraulic arrangement via the second proportional valve.
  • the press comprises a plurality of second proportional valves and a plurality of second hydraulic assemblies, each counterforce cylinder being connected to a single one of the hydraulic assemblies via a single one of the second proportional valves, and all second proportional valves being connected to the control unit for actuation.
  • the individual counter-holding cylinder can be acted upon very precisely and with very short response times to the desired pressure by controlling the individual proportional valves. This can if necessary Even imbalances of the press can be compensated by individually pressurizing the individual counter-holding cylinder with slightly different biases. However, this arrangement requires a higher apparatus and possibly tax technical effort.
  • the second pressure supply is designed as a central pressure supply for all second hydraulic arrangements. Since the second pressures are substantially the same for all counter-holding cylinders, the individual second pressures can be ensured in the long term even by a central pressure supply, which reduces the manufacturing costs of this arrangement.
  • the second hydraulic arrangement is flanged to the counter-holding cylinder.
  • the press comprises at least one path measuring system for detecting the movement of the pressing cylinders and / or counter-holding cylinders, which transmits position data and / or speed data of the pressing cylinders and / or counter-holding cylinders for controlling the continuous valves to the control unit.
  • the press may also include pressure measuring systems for detecting pressures applied to the pressing cylinder and / or the counter-holding cylinders, which transmits pressure data of the pressing cylinders and / or counter-holding cylinders for controlling the continuous valves to the control unit. This data transmission takes place, as well as the control of the continuous valves by the control unit, by means of suitable data lines.
  • the position measuring system and / or the pressure measuring system can increase the precision of the control of the continuous valves to the desired movement of the Working tools and effective cutting shock absorption support, since the measurement data are fed back to the calculated motion sequence.
  • this bias for damping the cutting stroke can be increased immediately by appropriate control of fast-switching continuous valves by the control unit, if the Wegemesssystem or the pressure measuring system a material breakthrough on the basis of a greatly accelerated movement of the working tool or a short-term strong Pressure increase detected.
  • passing through the pressurization phase comprises the step of reducing the preload, to which both cylinder chambers of the retainer cylinder are interconnected via a bypass line and a switching valve disposed therein, and the control unit opens the switching valve at least during pressure build-up phase to reduce the pressure of the retainer cylinder.
  • Fig.1 shows an embodiment of a press 1 according to the invention with a counter-holding cylinder 7.
  • the hydraulic press 1 comprises a machine frame 2, which is shown here only schematically as a gray U-shaped frame.
  • the skilled person can adjust the machine frame 2 in the context of the present invention to the requirements in size, shape and choice of material of the press 1 suitable.
  • the press table 3 is mechanically firmly connected to the machine frame 2.
  • a pressing cylinder 6 and a counter-holding cylinder 7 are also fixed mechanically fixed to the machine frame 2, wherein the press cylinder 6 via a press cylinder rod 61 and the counter-holding cylinder 7 via a counter holding cylinder rod 71 are mechanically connected to the working tool 4 for moving the working tool 4.
  • press table 3 press cylinder 6 and Retaining cylinders 7 with the machine frame are not shown in detail, so that those skilled in the art can choose a suitable means for producing this solid mechanical connection.
  • these components are connected by means of screw with the machine frame 2.
  • the working tool 4 is thus stored in the machine frame 2 for exercising a forming force on a to be arranged on a press table 3 workpiece 5 during a processing cycle B.
  • the workpiece 5 is shown here only schematically and may have different shapes and dimensions depending on the application. Accordingly, the working tool 4 deviates from the illustration in Fig.1 Depending on the application form of the forming process have other shapes and dimensions.
  • the pressing cylinder 6 is connected to a first hydraulic arrangement 81, which is under a first pressure D1, via a first proportional valve 91.
  • a throttling of the continuous valve 91 determined by the control unit 10 and thus a specific pressurization of the pressing cylinder 6 can be set.
  • the counter-holding cylinder 7 is correspondingly connected to a second hydraulic arrangement 82, which is under a second pressure D2, for moving the counter-holding cylinder 7 via a second proportional valve 92.
  • the second hydraulic arrangement 82 is designed separately from the first hydraulic arrangement 81.
  • the first hydraulic arrangement 81 comprises a first pressure accumulator 811 for storing the first pressure D1 and the second hydraulic arrangement 82 a second accumulator 821 for storing the second pressure D1, wherein the first pressure D1 is a higher pressure than the second pressure D2 is.
  • the first accumulator 811 is a high pressure accumulator and the second accumulator 821 is a medium pressure accumulator.
  • first and second hydraulic assemblies 81, 82 are respectively connected to first and second pressure supplies 812, 822, respectively Keeping constant the applied in the first and second hydraulic assemblies 81, 82 pressures D1, D2 via appropriately suitable check valves 813, 823 connected.
  • a throttling of the continuous valve 92 determined by the control unit 10 and thus a specific pressurization of the counter-holding cylinder 7 can be set.
  • the pressure applied to the counter-holding cylinder 7 between zero and the second pressure D2 can be variably adjusted.
  • the continuous valves 91, 92 can be servo valves with switching times of less than 20 ms, preferably less than 10 ms.
  • the applied pressure on the counter-holding cylinder 7 can cause a preloading of the press 1 in the direction of movement of the press cylinder 6 or an extension movement of the counter-holding cylinder bar 71 if the pressure applied to the counter-holding cylinder 7 is a force causes, which is greater than the opposite force which is exerted on the counter-holding cylinder 7 via the working tool 4. This is for example during the withdrawal phase RZ (see Figure 5 ) the press 1 of the case.
  • the first and second continuous valves 91, 92 are connected to the control with a control unit 10, wherein the control unit 10, the continuous valves 91, 92 for pressurizing the pressing and counter-holding cylinders 6, 7 so simultaneously and adapted to each other controls S that one of the counter-holding cylinder 7 via the working tool 4 exerted on the pressing cylinder 6 axial bias voltage V of the working tool 4 and the pressing cylinder 6 a predetermined by the control unit 10 minimum value MW to provide the cutting shock damping at least during the processing cycle B does not fall short while allowing a desired movement of the working tool 4.
  • V the cutting impact damping is integrated into the press 1 without further additional components.
  • both cylinder chambers 7a, 7b of the counter-holding cylinder 7 via a bypass line 11 and a switching valve 12 disposed therein, preferably a 2/2-way valve, connected to each other, wherein the switching valve 12 also with the control unit 10 for driving through the Control unit 10 is connected.
  • the bypass line 11 can in particular can be used to reduce the bias for a limited time interval by the switching valve 12 allows passage of the hydraulic fluid from one to the other cylinder chamber 7a, 7b. This is advantageous if the forming force for machining the workpiece must be increased.
  • a collecting tank 114 can be connected to the bypass line 11 via a non-illustrated check valve for additional discharge of hydraulic fluid.
  • the press 1 additionally comprises in each case a path measuring system 64, 74 with suitable sensors for detecting the movement of the pressing cylinder 6 and the counter-holding cylinder 7, the respective position data PD of the pressing cylinder 6 and the counter-holding cylinder 7 for controlling the continuous valves 91, 92 to the Control unit 10 transmitted. Suitable sensors for this purpose are, for example, ultrasonic path measuring systems.
  • the press 1 here comprises in each case a pressure measuring system 65, 75 for detecting the pressure applied to the pressing cylinder 6 and the counter-holding cylinder 7, wherein the respective pressure data DD of the pressing cylinder 6 and the counter-holding cylinder 7 for controlling the continuous valves 91, 92 to the control unit 10 are transmitted.
  • the data lines S, DD, PD are shown here as a dashed line.
  • the path measuring system 64, 74 or the pressure measuring system 65, 75 may be present.
  • the catch tanks 814, 824 serve to provide a catchment reservoir for quick lift motions for the hydraulic fluid displaced by the piston. This heat can also be removed from the press, since the pressure supplies 812, 822 nachumblen cool hydraulic fluid in the first and second hydraulic assemblies 81, 82.
  • the catch tanks 814, 824 may also be a single common catch tank. Even in such an arrangement, the first and second hydraulic assemblies 81, 82 remain separate arrangements within the meaning of the invention, as still acting separately on the cylinders 6, 7.
  • Fig.2 shows an alternative embodiment of a press 1 according to the invention with two counter-holding cylinders 7 arranged symmetrically to each other, each with separate second hydraulic assemblies 82.
  • first continuous valve 91, first hydraulic assembly 81 and the connections to the control unit 10 is on the Explanations according to Fig.1 directed.
  • the same applies to the here as in FIG. 1 shown components related to FIG. 2 will not be discussed in detail.
  • the embodiment in FIG. 1 differs from the embodiment according to FIG. 2 in that the press 1 comprises two counter-holding cylinders 7, which are both mechanically connected via their respective counter-holding cylinder rods 71 symmetrically to each other with the working tool 4, so that the working tool 4 is supported and prestressed on both sides of the press table 5.
  • Each of the two second hydraulic assemblies 82 each includes a second continuous valve 92 disposed between the respective counter-holding cylinder 7 and the second hydraulic assembly 82.
  • each counter-holding cylinder 7 is connected to a single one of the hydraulic assemblies 82 via a single one of the second proportional valves 92 all second proportional valves 92 are connected to the control unit 10 for activation.
  • the second pressure supply 822 is designed as a central pressure supply for all second hydraulic arrangements 82.
  • the counter-holding cylinders 7 are in contrast to FIG.
  • these two (and possibly all other) counter-holding cylinder 7 may each be provided with a bypass line 11 for connecting the two cylinder chambers 7a, 7b of the counter-holding cylinder 7, in each of which a switching valve 12 is arranged, wherein the switching valve 12 also with the Control unit 10 is connected in order to reduce the short-term and significant, if necessary, the bias.
  • the two second hydraulic arrangements 82 here each include its own separate pressure measuring system 75.
  • Figure 3 shows an alternative embodiment of a press 1 according to the invention with two mutually symmetrically arranged counter-holding cylinders 7 with a common second hydraulic arrangement 82.
  • the embodiment shown here differs from the embodiment FIG. 2 merely by the fact that only a single second hydraulic arrangement 82 for moving the counter-holding cylinder 7 and for generating a bias is required by the two counter-holding cylinders shown 7 via a corresponding hydraulic circuit 76 with each other and this hydraulic circuit 76 via the second proportional valve 92 with the second hydraulic arrangement 82 are connected.
  • the operation of the counter-holding cylinder 7 significantly fewer components than in FIG. 2 required, whereby, however, an individual different pressurization of individual counter-holding cylinder 7 is no longer possible.
  • the description is to complement FIG. 1 for the components not described here in detail FIG. 3 to use.
  • FIG 4 shows an embodiment of the first and second continuous valves 91, 92 used in the previous figures, and the switching valve 12 in the bypass line 11 of the counter-holding cylinder 7.
  • the two proportional valves 91, 92 as 3/3-way valves each have three switching positions SD.
  • Switching position 91-1 of the first continuous valve 91 interrupts or closes the connection to the first hydraulic arrangement 81 and opens the connection to the collecting tank 814.
  • the switching position 91-2 interrupts or closes both connections to the first hydraulic arrangement 81 and to the collecting tank 814.
  • the third switching position 91 -3 opens the connection to the first hydraulic arrangement 81 and interrupts or closes the connection to the catch tank 814.
  • At least the switch position 91-3 comprises a restrictable connection to the first hydraulic arrangement 81, which is electronically controlled by controlling the continuous valve 91 by the control unit 10 (here dashed line) shown) can be variably adjusted to regulate the volume flow through the continuous valve 91 therethrough.
  • Switching position 92-1 of the second continuous valve interrupts or closes the connection to the second hydraulic arrangement 82 and opens the connection to the catch tank 824.
  • the switch position 92-2 interrupts or closes both connections to the second hydraulic assembly 82 and the catch tank 824.
  • the third shift position 92-3 opens the connection to the second hydraulic assembly 82 and interrupts or closes the connection to the catch tank 824.
  • At least the switching position 92-3 comprises a throttling connection to the second hydraulic arrangement 82, which can be adjusted electronically by controlling the continuous valve 92 by the control unit 10 (shown here in dashed lines) variably for regulating the volume flow through the continuous valve 92.
  • the switching valve 12 here as a 2/2-way valve has a switching position 12-1, which is permeable in both directions, while the switching position blocks 12-2 in both directions.
  • Figure 5 shows an embodiment of a method for operating the press 1 according to the invention on the basis of different characteristics of the press 1 over a complete cycle of movement of the working tool 4.
  • the movement cycle consists of a processing cycle B comprising the three following parts, passing through a Leerhubphase LH of the working tool 4 of a first Dead center T1 (top dead center) in the direction of the press table 3, passing through a pressure build-up phase DA for the working tool 4 after contact of the working tool 4 with the arranged on the press table 3 workpiece 5 for exerting a forming force on the workpiece 5 and passing through a Umformphase UF for the working tool 4 and the workpiece 5 until reaching a second dead center T2 (bottom dead center).
  • a processing cycle B comprising the three following parts, passing through a Leerhubphase LH of the working tool 4 of a first Dead center T1 (top dead center) in the direction of the press table 3, passing through a pressure build-up phase DA for the working tool 4 after contact of the working tool 4 with the
  • the processing cycle B is completed and it now closes the retraction phase RZ to prepare a new machining cycle B for the working tool 4 from the second dead center T2 to the first dead center T1.
  • the first diagram shows the position of the working tool 4 and thus the position of the cylinder rods 61, 71 of the pressing and counter-holding cylinders 6, 7,
  • the second upper diagram shows the bias voltage V applied to the counter-holding cylinder 7 via the machine frame 2 by corresponding activation of the second proportional valve 92 by the control unit 10.
  • the applied pressure is high enough that the resulting bias voltage V during the entire movement cycle over a Minimum value MW (dashed line) is.
  • the third diagram shows in the throttle position SD (here switching position 92-3) set by the control unit 10 throttling, larger values correspond to a larger throttle cross-section, which a larger volume flow could flow through the continuous valve 92, which a correspondingly lower pressurization of the counter-holding cylinder 7 corresponds to the second hydraulic arrangement 82 out.
  • a corresponding representation is shown in the lower diagram for the pressing cylinder 6 and the first continuous valve 91.
  • the negative values in the forming phase UF and in the retraction phase RZ correspond to a volume flow in the direction of the first hydraulic arrangement 81 or in the direction of the collecting tank 814.
  • the speed of the working tool 4 is controlled so that the displaced hydraulic fluid, such as oil, from the piston chamber 7b of the counter-holding cylinder 7 via the control edge of the second continuous valve 92 in the pressure accumulator 821 quasi throttle-free displaced and cached.
  • the function cutting impact damping is required only at very high forming forces, since the workpiece breakthrough only a slight relaxation of the machine frame 2 occurs and the kinetic energy is buffered in the pressure accumulator 821 and with a steep pressure rise curve.
  • acceleration sensors may be used as part of the path measurement system 64, 74 to detect tool breakthrough.
  • the pressure supply 822 In order to maintain the accumulator pressure of the pressure accumulator 821, which in principle corresponds to the counter-holding pressure (preload V), only the gap leakage on the proportional valve 92 needs to be compensated by the pressure supply 822. Usually, about 3-5 L / min volumetric flow are required under normal pressure conditions and thus also an exchange of the oil as a hydraulic fluid over several cycles guaranteed.
  • the catch tanks 814, 824 may be formed by a single central tank.
  • the energy buffered in the pressure accumulator 821 is used to position the working tool 4 energetically upwards, whereby upon reaching the first (top) dead center T1 of the pressing cylinder 6, the bias voltage V of the machine frame 2 reaches the original value again. Thus, there is a recovery of the energy that is released after the passage of material, instead.
  • the minimum value MW of the bias voltage (V) is between 20% and 50% of the forming force, preferably between 30% and 45% of the forming force, more preferably between 38% and 42% of the forming force.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Presses (AREA)

Claims (16)

  1. Presse hydraulique (1) avec amortissement de choc de coupe intégré comprenant un bâti de machine (2) doté d'une table de presse (3), un outil de travail (4) monté sur le bâti de machine (2) pour exercer une force de déformation sur une pièce à usiner (5) placée sur la table de presse (3) pendant une phase de travail (B) et au moins un cylindre de presse (6) et au moins un contre-cylindre (7), chacun fixé au bâti de machine (2), dans lequel le cylindre de presse (6) par l'intermédiaire d'une tige du cylindre de presse (61) et le contre-cylindre (7) par l'intermédiaire d'une tige de contre-cylindre (71) sont mécaniquement reliés à l'outil de travail (4) pour le déplacement de l'outil de travail (4), dans laquelle le cylindre de presse (6) est relié au premier dispositif hydraulique (81) par une première pression (D1) lors du mouvement du cylindre de presse (6) sous l'action d'une première valve de réglage continu (91), et caractérisé en ce que le contre-cylindre (7) est relié à un deuxième dispositif hydraulique (82) agissant séparément du premier dispositif hydraulique (81) sous l'action d'une deuxième pression (D2) lors du mouvement du contre-cylindre (7) sur une deuxième valve de réglage continu (92), et les premiers et deuxièmes valves de réglage continu sont reliées à l'unité de commande (10), laquelle est équipée de deux valves (91, 92) pour appliquer (S) une pressurisation du cylindre de presse et du contre-cylindre (6, 7) si bien adaptés l'un à l'autre et de façon si simultanée qu'une précharge axiale (V) exercée par le contre-cylindre (7) et le cylindre de presse (6) sur le bâti de machine (2) et l'outil de travail (4) ne passe pas sous la valeur minimale (MW) pouvant être prédéfinie par l'unité de commande (10) pour assurer l'amortissement du choc de coupe au moins pendant la phase de travail (B), tandis qu'est rendu possible le mouvement souhaité de l'outil de travail.
  2. Presse hydraulique (1) selon la revendication 1,
    caractérisée en ce que,
    les valves de réglage continu (91, 92) comprennent au moins une position de commutation (SD) permettant une régulation ajustable par l'unité de commande (10) des premières et/ou deuxièmes pressions (D1, D2) pour une pressurisation variable au moyen des valves de réglage continu (91, 92).
  3. Presse hydraulique (1) selon la revendication 1 ou 2,
    caractérisée en ce que,
    les valves de réglage continu (91, 92) sont des servo-valves avec une durée de commutation inférieure à 20 ms, de préférence inférieure à 10 ms.
  4. Presse hydraulique (1) selon l'une des revendications précédentes,
    caractérisée en ce que,
    la valeur minimale (MW) de la précharge (V) est comprise entre 20 % et 50 % de la force de déformation, de préférence entre 30 % et 45 % de la force de déformation, de préférence plus particulière entre 38 % et 42 %.
  5. Presse hydraulique (1) selon la revendication 4,
    caractérisée en ce que,
    les deux chambres de cylindre (7a, 7b) du contre-cylindre (7) sont reliées l'une à l'autre par une conduite de dérivation (11) et une soupape de commande (12) qui y est disposée, de préférence une soupape à 2/2 voies, dans laquelle la soupape de commande (12) est également reliée à l'unité de commande (10).
  6. Presse hydraulique (1) selon l'une des revendications précédentes,
    caractérisée en ce que,
    le premier dispositif hydraulique (81) comprend un accumulateur de pression (811) pour stocker la première pression (D1) et le deuxième dispositif hydraulique (82) comprend un accumulateur de pression (821) pour le stockage de la deuxième pression (D1), dans lequel la première pression (D1) est supérieure à la deuxième pression (D2), de préférence le premier accumulateur de pression (811) est un accumulateur de haute pression et le deuxième accumulateur (821) un accumulateur de moyenne pression.
  7. Presse hydraulique (1) selon la revendication 6,
    caractérisée en ce que,
    le deuxième accumulateur de pression (821) est prévu pour stocker l'énergie cinétique du cylindre de presse (6) sous forme de pression accrue par l'amortisseur de choc de coupe et pour libérer cette énergie lors de la course de retour du cylindre de presse (6) au moyen d'une tension accrue du contre-cylindre (7).
  8. Presse hydraulique (1) selon la revendication 6 ou 7,
    caractérisée en ce que,
    les premiers et deuxièmes dispositifs hydrauliques (81, 82) sont chacun connectés à une première et respectivement deuxième alimentation en pression (812, 822) pour maintenir constantes les pressions (D1, D2) appliquées dans les premier et deuxième dispositifs hydrauliques (81, 82), de préférence sur les clapets anti-retour (813, 823).
  9. Presse hydraulique (1) selon l'une des revendications précédentes,
    caractérisée en ce que,
    la presse (1) comprend une pluralité de contre-cylindres (7), qui sont chacun reliés mécaniquement par leurs tiges de contre-cylindre (71), de préférence de façon symétrique les uns par rapport aux autres, à l'outil de travail (4).
  10. Presse hydraulique (1) selon la revendication 9,
    caractérisée en ce que,
    les contre-cylindres (7) sont reliés les uns aux autres au deuxième dispositif hydraulique (82) par un circuit hydraulique correspondant (76) et le circuit hydraulique (76) par la deuxième valve de réglage continu (92).
  11. Presse hydraulique (1) selon la revendication 9,
    caractérisée en ce que,
    la presse (1) comprend une pluralité de deuxièmes valves de réglage continu (92) et une pluralité de deuxièmes dispositifs hydrauliques (82) dans laquelle chaque contre-cylindre (7) est à chaque fois relié à l'un des dispositifs hydrauliques (82) par l'une des deuxièmes vannes de réglage continu (92), et toutes les deuxièmes vannes de réglage continu (92) sont connectées à l'unité de commande (10) pour l'actionnement.
  12. Presse hydraulique (1) selon la revendication 11,
    caractérisée en ce que,
    la deuxième alimentation en pression (822) est équipée en tant qu'alimentation en pression centrale pour tous les deuxièmes dispositifs hydrauliques (82).
  13. Presse hydraulique (1) selon l'une des revendications précédentes,
    caractérisée en ce que,
    le deuxième dispositif hydraulique (82) est monté sur bride au contre-cylindre (7).
  14. Presse hydraulique (1) selon la revendication 1,
    caractérisée en ce que,
    la presse (1) comprend au moins un système de mesure de course (64, 74) pour enregistrer le mouvement du cylindre de presse (6) et/ou du contre-cylindre (7) qui transmet des données de positionnement (PD) et/ou des données de vitesse du cylindre de presse (6) et/ou du contre-cylindre (7) pour la commande des vannes de réglage continu (91, 92) sur l'unité de commande (10) et/ou en ce que la presse (1) comprend un système de mesure de pression (65, 75) pour enregistrer les pressions appliquées sur le cylindre de presse (6) et/ou le contre-cylindre (7) qui transmet des données de pression (DD) du cylindre de presse (6) et/ou du contre-cylindre (7) lors de la commande des vannes de régulation continue (91, 92) sur l'unité de commande (10).
  15. Procédé destiné à faire fonctionner une presse hydraulique (1) avec amortissement de choc de coupe intégré selon la revendication 1 comprenant un bâti de machine (2), une table de presse (3), un outil de travail (4) monté sur un bâti de machine (2) et au moins un cylindre de presse (6) fixé au bâti de machine (2) qui est relié de façon mécanique à un premier dispositif hydraulique (81) sous l'effet d'une première pression (D1) pour déplacer le cylindre de presse (6) par une première vanne de réglage continu (91) et par une tige de cylindre de presse (61) avec l'outil de travail (4), et au moins un contre-cylindre (7) fixé au bâti de machine (2) qui est relié de façon mécanique à un deuxième dispositif hydraulique (82) séparé du premier dispositif hydraulique (81) par le biais d'une deuxième pression (D2) pour déplacer le contre-cylindre (7) par une deuxième vanne de réglage continu (92) et par une tige de contre-cylindre (71) avec l'outil de travail (4), et avec une unité de commande (10) liée aux premières et deuxièmes vannes de réglage continu (91, 92), comprenant les étapes consistant à
    - passer d'une phase de course à vide (LH) de l'outil de travail (4) depuis un premier point mort (T1) en direction de la table de presse (3), comme première partie de la phase de travail (B) ;
    - passer d'une phase de de montée en pression (DA) pour l'outil de travail (4) après contact de l'outil de travail (4) avec la pièce à usiner (5) placée sur la table de presse (3) pour exercer une force de déformation sur la pièce à usiner (5), comme deuxième partie de la phase de travail (B) ;
    - passer d'une phase de déformation (UF) pour l'outil de travail (4) et la pièce à usiner (5) jusqu'à atteindre un deuxième point mort (T2), comme troisième partie de la phase de travail (B) ; et
    - passer d'une phase de course de retour (RZ) pour préparer une nouvelle phase de travail (B) pour l'outil de travail (4) depuis le deuxième point mort (T2) vers le premier point mort (T1),
    dans lequel l'unité de commande (10) contrôle les premières et deuxièmes vannes de réglage continu (91, 92) de manière à appliquer (S) une pressurisation simultanément adaptée des cylindres de presse et contre-cylindres (6, 7) les uns aux autres, de sorte que la précharge axiale (V) exercée par les contre-cylindres (7) et les cylindres de presse (6) sur le bâti de machine (2) et l'outil de travail (4) ne sera pas inférieure à la tension minimale (MW) prédéfinie par l'unité de commande (10) pour activer l'amortissement de choc de coupe au moins pendant la phase de travail (B) et en même temps permettre un mouvement souhaité de l'outil de travail (4).
  16. Procédé selon la revendication 15 dans lequel le passage de la phase de montée en pression (DA) comprend l'étape de réduction (RD) de la précharge (V) pour augmenter la force de déformation, les deux chambres de cylindre (7a, 7b) du contre-cylindre (7) étant reliées entre elles par une conduite de dérivation (11) et une soupape de commande qui y est disposée (12), et l'unité de commande (10) ouvrant la soupape de commande (12) au moins pendant la phase de montée en pression (DA) pour réduire la pression du contre-cylindre (7).
EP15154818.7A 2015-02-12 2015-02-12 Presse dotée d'un amortisseur de choc de coupe Not-in-force EP3056291B1 (fr)

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EP15154818.7A EP3056291B1 (fr) 2015-02-12 2015-02-12 Presse dotée d'un amortisseur de choc de coupe

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WO2019102410A1 (fr) * 2017-11-24 2019-05-31 Danieli & C. Officine Meccaniche S.P.A. Presse d'extrusion d'un matériau métallique
EP3666410A1 (fr) * 2018-12-13 2020-06-17 Lapmaster Wolters GmbH Presse de découpage fin et procédé de fonctionnement d'une presse de découpage fin
DE102019008242A1 (de) * 2019-11-27 2021-05-27 Siempelkamp Maschinen- Und Anlagenbau Gmbh Momentenkompensation für Schmiedepresse

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Publication number Priority date Publication date Assignee Title
DE2221290B2 (de) * 1972-04-29 1976-09-02 L. Schuler GmbH, 7320 Göppingen Schnittschlagdaempfungseinrichtung fuer mechanische pressen
DE2824176A1 (de) * 1978-06-02 1979-12-06 Thyssen Industrie Hydraulische presse mit servohydraulischer regelung der stoesselbewegung
DE19643396B4 (de) 1996-10-21 2008-09-11 Dieffenbacher Gmbh + Co. Kg Hydraulische Steuereinrichtung
DE102009048483B4 (de) 2009-09-29 2012-08-16 Voith Patent Gmbh Schnittschlagdämpfung

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