EP3056291A1 - Press with cutting shock damping - Google Patents
Press with cutting shock damping Download PDFInfo
- Publication number
- EP3056291A1 EP3056291A1 EP15154818.7A EP15154818A EP3056291A1 EP 3056291 A1 EP3056291 A1 EP 3056291A1 EP 15154818 A EP15154818 A EP 15154818A EP 3056291 A1 EP3056291 A1 EP 3056291A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- counter
- press
- cylinder
- hydraulic
- pressure
- 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
Links
Images
Classifications
-
- 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 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.
- the working cylinder exerts a force on the workpiece, which also elastically deforms the upper part of the machine frame. So that after the material breakthrough can not occur due to the corresponding rebounding of the machine frame, in particular the upper part, 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 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, wherein the pressing cylinder via a pressure cylinder rod and the counter-holding cylinder via a counter-holding cylinder rod are mechanically connected to the working tool for moving the working tool, wherein the pressing cylinder with a first hydraulic arrangement under a first pressure for moving the pressing cylinder via a first proportional valve and the counter-holding cylinder with one of the the first hydraulic arrangement separately acting executed second hydraulic arrangement under a second pressure for moving the counter-holding cylinder via a second continuous valve is connected, and the first and second continuous 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 each other that one
- 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 pressing and counter-holding cylinder software is enabled and supported 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 20ms.
- 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 forming force, preferably between 30% and 45% of the forming force, particularly preferably between 38% and 42% of the forming 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).
- Embodiment are both cylinder chambers of the counter-holding cylinder via 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 accumulator is provided for storing kinetic energy of the pressing cylinder in the form of an increased pressure in the cutting impact damping and releasing this energy for 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, each of which is in each case mechanically connected via its counter-holding cylinder rods to 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 retainer 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.
- performing the pressure build-up phase comprises the step of reducing the bias voltage to which both cylinder chambers of the counter-holding cylinder are connected 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 counter-holding cylinder.
- the press according to the invention can be designed according to the subject matter of the main claim or according to one of the preceding embodiments or, where appropriate, by realizing a combination of several of the preceding embodiments. The same applies to the method according to the invention.
- 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 proportional 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 nach telephonen 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.
- 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.
- the working tool 4 can not tilt with respect to the axial direction of movement B, RZ even if the preload is present.
- 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. 1 not provided with a connecting the two cylinder piston bypass line.
- 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 uppermost diagram of the voltage applied to the counter-holding cylinder 7 via the machine frame 2 bias V by appropriate control of the second Steady 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.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Presses (AREA)
Abstract
Die Erfindung betrifft eine hydraulische Presse (1) mit integrierter Schnittschlagdämpfung umfassend einen Maschinenrahmen (2) mit einem Presstisch (3), ein im Maschinenrahmen (2) gelagertes Arbeitswerkzeug (4) zur Ausübung einer Umformkraft auf ein auf einem Presstisch (3) anzuordnendes Werkstück (5) während eines Bearbeitungsgangs (B) und mindestens einen Presszylinder (6) und mindestens einen Gegenhaltezylinder (7) jeweils befestigt am Maschinenrahmen (2), wobei der Presszylinder (6) über eine Presszylinderstange (61) und der Gegenhaltezylinder (7) über eine Gegenhaltezylinderstange (71) mechanisch mit dem Arbeitswerkzeug (4) zur Bewegung des Arbeitswerkzeugs (4) verbunden sind, wobei der Presszylinder (6) mit einer ersten hydraulischen Anordnung (81) unter einem ersten Druck (D1) zur Bewegung des Presszylinders (6) über ein erstes Stetigventil (91) und der Gegenhaltezylinder (7) mit einer von der ersten hydraulischen Anordnung (81) getrennt wirkend ausgeführten zweiten hydraulischen Anordnung (82) unter einem zweiten Druck (D2) zur Bewegung des Gegenhaltezylinders (7) über ein zweites Stetigventil (92) verbunden ist, und die ersten und zweiten Stetigventile (91, 92) mit einer Steuereinheit (10) verbunden sind, wobei die Steuereinheit (10) dazu ausgestaltet ist, die Stetigventile (91, 92) zur Druckbeaufschlagung der Press- und Gegenhaltezylinder (6, 7) so simultan und aufeinander angepasst anzusteuern (S), dass eine von Gegenhaltezylinder (7) und Presszylinder (6) über den Maschinenrahmen (2) und das Arbeitswerkzeug (4) ausgeübte axiale Vorspannung (V) einen durch die Steuereinheit (10) vorgebbaren Minimalwert (MW) zur Bereitstellung der Schnittschlagdämpfung zumindest während des Bearbeitungsgangs (B) nicht unterschritten und gleichzeitig eine gewünschte Bewegung des Arbeitswerkzeugs (4) ermöglicht wird. Ein Verfahren zum Betreiben einer solchen hydraulischen Presse ist ebenfalls beschrieben.The invention relates to a hydraulic press (1) with integrated cutting impact damping comprising a machine frame (2) with a press table (3), a working tool (4) mounted in the machine frame (2) for exerting a forming force on a workpiece to be arranged on a press table (3) (5) during a processing run (B) and at least one press cylinder (6) and at least one counter-holding cylinder (7) respectively 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) is mechanically connected to the working tool (4) for moving the working tool (4), the pressing cylinder (6) being connected to a first hydraulic arrangement (81) under a first pressure (D1) for moving the pressing cylinder (6). via a first continuous valve (91) and the counter-holding cylinder (7) with one of the first hydraulic arrangement (81) separated acting executed second hydr the second assembly (82) is connected at a second pressure (D2) for moving the counter-holding cylinder (7) via a second proportional valve (92), and the first and second proportional valves (91, 92) are connected to a control unit (10) the control unit (10) is designed to actuate the continuous valves (91, 92) for the pressurization of the pressing and counter-holding cylinders (6, 7) simultaneously and adapted to each other (S) such that one of counter-holding cylinders (7) and pressing cylinders (6) axial preload (V) exerted on the machine frame (2) and the working tool (4) does not fall below a minimum value (MW) predeterminable by the control unit (10) for providing the cutting impact damping at least during the machining operation (B) and at the same time a desired movement of the working tool (4) is enabled. A method of operating such a hydraulic press is also described.
Description
Die Erfindung bezieht sich auf hydraulische Pressen mit integrierter Schnittschlagdämpfung und ein Verfahren zum Betreiben einer solchen Presse.The invention relates to hydraulic presses with integrated cutting impact damping and a method for operating such a press.
Hydraulische Pressen haben gegenüber mechanischen Pressen den Vorteil der gut dosierbaren Pressenkraft und werden für Verformungs-, Schneid oder Stanzprozesse an Werkstücken verwendet. Hierbei wird das Arbeitswerkzeug mittels hydraulischer Zylinder in Kontakt mit dem Werkstück gebracht und die so auf das Werkstück ausgeübte Kraft (Umformkraft) so lange erhöht, bis das Werkstück in gewünschter Weise umgeformt, geschnitten oder mit Stanzlöchern versehen ist. Hierbei wird die maximale Kraft beispielsweise bei Stanz- oder Schneideprozessen kurz vor dem Materialdurchbruch im Werkstück erreicht. Im Moment des Materialdurchbruchs verschwindet die Gegenhaltekraft durch das Werkstück schlagartig, so dass das Arbeitswerkzeug unter Maximaldruck stehend eine sprunghafte Bewegung in Richtung der ausgeübten Umformkraft erfährt. Dieser Effekt wird als Schnittschlag bezeichnet und stellt eine hohe mechanische Belastung für die Presse dar. Ähnliche Effekte können bei Verformungsprozessen auftreten, bei denen sich das Werkstück entsprechend schnell oberhalb einer bestimmten Kraftaufwendung verformt. Gerade bei schnelllaufenden Umformprozessen mit Hubzahlen der Presse von beispielsweise mehr als 150 Hüben pro Minute und hohen angewendeten Umformkräften verschleißen Pressen ohne Schnittschlagdämpfung schnell, was einen hohen Wartungsaufwand für einen zuverlässigen Betrieb notwendig macht.Hydraulic presses have the advantage of good press force over mechanical presses and are used for deformation, cutting or punching processes on workpieces. In this case, 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. In this case, the maximum force is achieved for example in punching or cutting processes shortly before the material breakdown in the workpiece. At the moment of material breakdown, 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. Similar effects can occur in deformation processes in which the workpiece deforms correspondingly fast above a certain application of force. Especially in high-speed forming processes with stroke rates of the press of, for example, more than 150 strokes per minute and high forming forces applied presses without cutting impact damping wear quickly, which makes a high maintenance required for reliable operation.
Dokument
Es ist eine Aufgabe der vorliegenden Erfindung, eine variabel einsetzbare hydraulische Presse für schnelllaufende Umform-, Schneide- oder Stanzprozesse mit einer energieeffizienten integrierten Schnittschlagdämpfung ohne große Drosselverluste zur Verfügung zu stellen sowie ein entsprechendes Verfahren zum Betrieben einer solchen Presse.It is an object of the present invention to provide a variably usable hydraulic press for high-speed forming, cutting or stamping processes with an energy-efficient integrated cutting impact damping without large throttling losses and a corresponding method for operating such a press.
Diese Aufgabe wird gelöst durch eine hydraulische Presse mit integrierter Schnittschlagdämpfung umfassend einen Maschinenrahmen mit einem Presstisch, ein im Maschinenrahmen gelagertes Arbeitswerkzeug zur Ausübung einer Umformkraft auf ein auf einem Presstisch anzuordnendes Werkstück während eines Bearbeitungsgangs und mindestens einen Presszylinder und mindestens einen Gegenhaltezylinder jeweils befestigt am Maschinenrahmen, wobei der Presszylinder über eine Presszylinderstange und der Gegenhaltezylinder über eine Gegenhaltezylinderstange mechanisch mit dem Arbeitswerkzeug zur Bewegung des Arbeitswerkzeugs verbunden sind, wobei der Presszylinder mit einer ersten hydraulischen Anordnung unter einem ersten Druck zur Bewegung des Presszylinders über ein erstes Stetigventil und der Gegenhaltezylinder mit einer von der ersten hydraulischen Anordnung getrennt wirkend ausgeführten zweiten hydraulischen Anordnung unter einem zweiten Druck zur Bewegung des Gegenhaltezylinders über ein zweites Stetigventil verbunden ist, und die ersten und zweiten Stetigventile mit einer Steuereinheit verbunden sind, wobei die Steuereinheit dazu ausgestaltet ist, die Stetigventile zur Druckbeaufschlagung der Press- und Gegenhaltezylinder so simultan und aufeinander angepasst anzusteuern, dass eine von Gegenhaltezylinder und Presszylinder über den Maschinenrahmen und das Arbeitswerkzeug ausgeübte axiale Vorspannung einen durch die Steuereinheit vorgebbaren Minimalwert zur Bereitstellung der Schnittschlagdämpfung zumindest während des Bearbeitungsgangs nicht unterschritten und gleichzeitig eine gewünschte Bewegung des Arbeitswerkzeugs ermöglicht wird.This object is achieved by 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, wherein the pressing cylinder via a pressure cylinder rod and the counter-holding cylinder via a counter-holding cylinder rod are mechanically connected to the working tool for moving the working tool, wherein the pressing cylinder with a first hydraulic arrangement under a first pressure for moving the pressing cylinder via a first proportional valve and the counter-holding cylinder with one of the the first hydraulic arrangement separately acting executed second hydraulic arrangement under a second pressure for moving the counter-holding cylinder via a second continuous valve is connected, and the first and second continuous 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 each other that one of counter-holding cylinders and press cylinder on the machine frame and the working tool applied axial bias a predetermined by the control unit minimum value for providing the cutting impact damping, at least during the Machining ratio is not exceeded and at the same time a desired movement of the working tool is made possible.
Die erfindungsgemäße hydraulische Presse bezeichnet eine Presse, die für Umform-, Schneide- oder Stanzprozesse verwendet werden kann. Als schnelllaufende Pressen werden hier insbesondere Pressen bezeichnet, die eine Hubzahl von beispielsweise mehr als 150 Hüben pro Minute erreichen können. Die integrierte Schnittschlagdämpfung bezeichnet eine durch die Betriebsbedingungen der Presse erzeugte Schnittschlagdämpfung. Eine solche Schnittschlagdämpfung ist insbesondere für schnelllaufende Pressen mit Umformkräften von beispielsweise 5000kN sehr vorteilhaft.The inventive hydraulic press refers to a press that can be used for forming, cutting or stamping processes. As 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.
Der Maschinenrahmen bezeichnet die mechanische Konstruktion oder Anordnung, an der die aufeinander wirkenden Komponenten wie Presszylinder, Presstisch und Gegenhaltezylinder befestigt sind, so dass sich diese Komponenten bei Ausübung der Umformkraft auf das Werkstück nicht gegenseitig verschieben können. Die Ausgestaltung des Maschinenrahmens kann vom Fachmann im Rahmen der vorliegenden Erfindung geeignet gewählt werden. Hierbei stellt der Presstisch eine Auflage des Werkstücks für die nachfolgende Bearbeitung dar. Der Presstisch kann dabei geeignet ausgestaltete Mittel zur Halterung und Fixierung des Werkstücks während der Bearbeitung umfassen. Das Arbeitswerkzeug ist dabei auf die jeweilige gewünschte Bearbeitung (Umformprozess, Schneideprozess, Stanzprozess) angepasst. Das Arbeitswerkzeug kann vom Fachmann im Rahmen der vorliegenden Erfindung geeignet gewählt werden. Die Umformkraft, die von Arbeitswerkzeug auf das Werkstück ausgeübt wird, bezeichnet die Kraft, mit der das Werkstück durch das Arbeitswerkzeug verformt, geschnitten oder gestanzt wird. Die Umformkraft wird dabei durch das Zusammenspiel von Press- und Gegenhaltezylinder in Verbindung mit den Ansteuerungen der Stetigventile durch die Steuereinrichtung aufgebracht und definiert. Das Werkstück kann dabei jedes für eine Bearbeitung durch Pressen geeignetes Werkstück sein. Beispielsweise können Werkstücke Metallplatten oder dreidimensionale Metallkörper sein, in die Löcher gestanzt werden. Die Werkstücke können allerdings auch aus anderen Werkstoffen bestehen oder diese zum Teil umfassen. Als Bearbeitungsgang wird hierbei der Vorgang der Presse bezeichnet, in der das Arbeitswerkzeug in Richtung des Werkstücks bewegt und die Bearbeitung des Werkstücks durchgeführt wird. Nach Beendigung der Bearbeitung des Werkstücks durch die Presse wird das Arbeitswerkzeug in einer Rückzugsphase wieder vom Presstisch bzw. dem Werkstück entfernt, damit die Presse erneut einen neuen Bearbeitungsgang an demselben Werkstück oder einem neuen Werkstück durchführen kann.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. Here, 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. For example, workpieces may be metal plates or three-dimensional metal bodies into which holes are punched. However, 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.
Der Presszylinder und der Gegenhaltezylinder können jede für diese Art von Pressen geeignete Zylinder sein, die jeweils eine Zylinderstange (hier die Presszylinderstange bzw. die Gegenhaltezylinderstange) zur Übertragung der Bewegung des Kolbens auf das Arbeitswerkzeug umfassen. Press- und Gegenhaltezylinder sind beispielsweise Differentialzylinder, die nur auf einer Seite der Kolbenfläche eine Kolbenstange besitzen. Dadurch besitzen Differentialzylinder zwei verschieden große Wirkflächen: zum einen die Fläche auf der Kolbenseite, die komplett wirkt, und zum anderen die stangenseitige Fläche, bei der nur die Ringfläche wirkt. Press- und/oder Gegenhaltezylinder können in anderen Ausführungsformen auch Tandemzylinder zur Erhöhung der auf die Kolbenflächen wirkenden Kräfte sein. Die Zylinderstange der Press- und Gegenhaltezylinder sind hierbei nicht direkt, sondern über das Arbeitswerkzeug mechanisch miteinander verbunden. Somit können die beiden Zylindertypen nur eine gemeinsame gleiche Bewegung ausführen, wobei ein Ausfahren der Presszylinderstange aus dem Presszylinder ein Einfahren der Gegenhaltezylinderstange in den Gegenhaltezylinder bedingt und umgekehrt, um eine Bewegung des Arbeitswerkzeugs zu ermöglichen. Damit diese Bewegung energieeffizient und ohne große Drosselverluste ausgeführt werden kann, steuert eine Steuereinrichtung über Ansteuerung der ersten und zweiten Stetigventile diese aufeinander abgestimmte simultane Bewegung der Press- und Gegenhaltezylinder. Somit wird die Bewegung der Zylinderstangen von Press- und Gegenhaltezylinder softwaremäßig durch die Steuereinheit ermöglicht und unterstützt. Somit sind die Press- und Gegenhaltezylinder in der erfindungsgemäßen Presse softwaremäßig gekoppelt. Um eine reine softwaremäßige Kopplung erreichen zu können, sind die ersten und zweiten hydraulischen Anordnungen zum Betreiben der Press- und Gegenhaltezylinder separat, d.h. ohne hydraulische wirksame Verbindung zueinander, ausgeführt. Der Begriff "getrennt wirkend" schließt somit beispielsweise die Möglichkeit einer Abführung der hydraulischen Flüssigkeiten aus den ersten und zweiten Anordnungen in den gleichen Auffangtank mit ein, da diese Art der Zusammenführung der hydraulischen Flüssigkeiten aus den ersten und zweiten Anordnungen keine Rückwirkungen auf die ersten oder zweiten Anordnungen entfalten können. Dadurch ist das Federmasse-System bestehend aus den bewegten Massen und den hydraulischen Kapazitäten extrem klein und damit günstig gestaltet und lässt sehr hohe Hubzahlen zu. Die ersten und zweiten hydraulischen Anordnungen bezeichnen eine Anzahl an Komponenten, die miteinander über hydraulische Leitungen verbunden sind. Zur Erzeugung von ersten bzw. zweiten Drücken umfassen diese Anordnung zumindest einen oder mehrere geeignete Druckspeicher, die über geeignete Anschlüsse die ersten und zweiten Drücke in der hydraulischen Leitungen aufrecht erhalten. Zusätzlich sind die ersten und/oder zweiten Anordnungen an eine zusätzliche Druckversorgung angeschlossen, damit etwaige Druckverluste oder Verluste an hydraulischer Flüssigkeit ausgeglichen werden können. Die ersten und zweiten Anordnungen können je nach Anwendung weitere Komponenten umfassen.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. As a result, 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. Thus, 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. In order for this movement to be carried out in an energy-efficient manner and without great throttling losses, a control device controls the synchronized simultaneous movement of the pressing and counter-holding cylinders via control of the first and second continuous valves. Thus, the movement of the cylinder rods of pressing and counter-holding cylinder software is enabled and supported by the control unit. Thus, the press and counter-holding cylinders in the press according to the invention are coupled by software. In order to achieve a pure software coupling, 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. As a result, 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. 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. In addition, the 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.
Die Stetigventile, die jeweils zwischen den Press- bzw. Gegenhaltezylindern und den ersten bzw. zweiten hydraulischen Anordnungen angeordnet sind, können den Volumenstrom entsprechend dem Sollwert der Steuereinheit stufenlos regeln. Somit kann die Steuereinheit den Volumenstrom und dessen Richtung je nach Betriebsphase der Presse und gewünschten Betriebsbedingungen über eine entsprechende Ansteuerung der Stetigventile einstellen. Damit kann der Volumenstrom des hydraulischen Fluids durch das Stetigventil hindurch in die Zylinderkammer des entsprechenden Zylinders oder in die erste oder zweite hydraulische Anordnung hinein für beliebig begrenzte Zeitintervalle beliebig eingestellt werden. In einer Ausführungsform umfassen daher die Stetigventile zumindest eine Schaltstellung, die eine von der Steuereinheit variabel einstellbare Drosselung der ersten und/oder zweiten Drücke zur variablen Druckbeaufschlagung durch die Stetigventile ermöglicht. Somit wird die variabel wählbare Druckbeaufschlagung der Press- und Gegenhaltezylinder nicht durch die ersten und zweiten Drücke, sondern durch deren Drosselung über die angesteuerten Stetigventile erreicht. Damit kann die Vorspannung der Arbeitswerkzeugs bzw. des Presszylinders durch den Gegenhaltezylinder zeitlich und in ihrer Größe frei über die Stetigventile mittels geeigneter Ansteuerung softwaremäßig durch die Steuereinheit eingestellt werden. Die einstellbare Drosselung schließt dabei mit ein, dass der gewünschte Druck mittels gedrosseltem Ventil eingestellt und danach das Ventil geschlossen wird, solange der anliegende Druck dem gewünschten Druck entspricht. Damit wird der sonst übliche Schnittschlag beispielsweise beim Stanzen von hochfesten Werkstoffen weitestgehend vermieden und die freiwerdende Energie beim Materialabriss infolge des Stanzens in die zweite hydraulische Anordnung gedämpft zurückgeführt. Dabei wird die Bewegungs-Energie von den angeschlossenen Druckspeichern gespeichert. Dadurch wird vermieden, dass die Umschaltung auf eine Drosselung und die damit wirksame Schnittschlagdämpfung von einem hydraulischen Schwellwert oder einem differenzdruckabhängigen Drosselventil erfolgt, die beim Rückhub des Arbeitswerkzeugs die Verformungsenergie in Wärme umwandelt.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. Thus, 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. Thus, 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. In one embodiment, therefore, 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. Thus, the 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. Thus, the bias of the working tool or the pressing cylinder by the counter-holding cylinder in time and in size freely over the continuous valves by means of suitable control software can be adjusted by the control unit. 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. Thus, 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.
Für die Ansteuerung der Stetigventile umfasst die Steuereinheit beispielsweise einen Prozessor und einen Datenspeicher, in dem entsprechende Steuervorgaben abgelegt sind und auf den der Prozessor zur Ausführung der Steuerung zugreifen kann. Auf dem Prozessor können beispielsweise geeignete Steueralgorithmen zur Steuerung der hydraulischen Presse ausgeführt werden. Sollte die Presse für eine andere Anwendung verwendet werden, braucht für einen optimale Betrieb der Presse lediglich ein geeigneter Steueralgorithmus in die Steuereinheit geladen werden oder ein geeigneter Steueralgorithmus aus einer Vielzahl an bereits geladenen Steueralgorithmen in der Steuereinheit ausgewählt werden, ohne dass dabei hardwaremäßig Anpassungen an der Presse vorgenommen werden müssten. Sofern die Steuereinheit an ein Computernetz angeschlossen ist, könnte eine solche softwaremäßige Anpassung der Presse an andere Anwendungen auch mittels Fernanpassung durchgeführt werden, ohne dass diese vor Ort durch Servicetechniker vorgenommen werden müsste.For controlling the continuous valves, 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. For example, 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.
Mit der erfindungsgemäßen hydraulischen Presse wird beim Werkstückdurchbruch die kinetische Energie des Presszylinders über das zweite Stetigventil in einen Druckspeicher der zweiten Anordnung über einen Druckanstieg im Druckspeicher gepuffert, wodurch die Vorspannung der Presse erhöht und somit die Schnittschlagdämpfung bewirkt wird. Die in diesem Druckspeicher gespeicherte kinetische Energie kann später wieder in den Arbeitsablauf der dadurch energieeffizienten Presse eingespeist werde. Somit wird durch die vorliegende Erfindung eine variabel einsetzbare hydraulische Presse für schnelllaufende Umform-, Schneide- oder Stanzprozesse mit einer energieeffizienten integrierten Schnittschlagdämpfung ohne große Drosselverluste zur Verfügung gestellt.With the hydraulic press according to the invention, 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. Thus, 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.
In einer Ausführungsform sind die Stetigventile Servoventile mit Schaltzeiten kleiner 20ms. In einer bevorzugten Ausführungsform sind die Servoventile als 3/3-wege Einbauservoventile mit extrem kurzen Schaltzeiten kleiner 10ms ausgeführt, die eine hohe Bandbreite besitzen, mit digitaler integrierter Ventilelektronik ausgestattet sind und über schnelle Bussystem durch die Steuereinheit regelbar sind. Diese Servoventile ermöglichen eine präzise Regelung der Steuerkanten zueinander in den verschiedenen Betriebsphasen der Presse wie Bearbeitungsgang und Rückzugphase.In one embodiment, the continuous valves are servo valves with switching times less than 20ms. In a preferred embodiment, 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.
In einer Ausführungsform beträgt der Minimalwert der Vorspannung zwischen 20% und 50% der Umformkraft, vorzugsweise zwischen 30% und 45% der Umformkraft, besonders bevorzugt zwischen 38% und 42% der Umformkraft. Der Minimalwert stellt sicher, dass die Vorspannung zumindest den Minimalwert besitzt. Eine derartige Vorspannung der Presse stellt eine Schnittschlagdämpfung bereit, die die anlagenbelastenden Schnittschläge ausreichend dämpft. Hierbei beträgt die Vorspannung idealerweise ungefähr 40% der Umformkraft (Nennwert) der Presse und kann je nach Bedarf nach einer höheren Umformkraft (beispielsweise bei hochfesten Werkstoffen) abgesenkt werden. In einer weiteren Ausführungsform sind dazu beide Zylinderkammern des Gegenhaltezylinders über eine Bypassleitung und ein darin angeordnetes Schaltventil, vorzugsweise ein 2/2-Wegeventil, miteinander verbunden, wobei das Schaltventil ebenfalls mit der Steuereinheit verbunden ist. Somit kann die Steuereinheit bei Bedarf nach einer höheren Umformkraft alternativ zu einer Erhöhung des ersten Drucks die Vorspannung grundsätzlich über die Bypassleitung absenken, um einen Materialdurchbruch des Werkstücks oder eine nur unter hohem Druck erreichbare Materialverformung erreichen zu können, die eventuell bei ursprünglicher Vorspannung nicht möglich wäre. Die Bypassleitung kann dazu noch mit einem zusätzlichen Auffangtank zum Ablassen des hydraulischen Fluids über beispielsweise ein Rückschlagventil verbunden sein. Das Rückschlagventil dichtet die Bypassleitung nach außen ab.In one embodiment, the minimum value of the prestressing is between 20% and 50% of the forming force, preferably between 30% and 45% of the forming force, particularly preferably between 38% and 42% of the forming 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. In this case, 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). In another Embodiment are both cylinder chambers of the counter-holding cylinder via 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. Thus, 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.
In einer weiteren Ausführungsform umfasst die erste hydraulische Anordnung einen ersten Druckspeicher zur Speicherung des ersten Drucks und die zweite hydraulische Anordnung einen zweiten Druckspeicher zur Speicherung des zweiten Drucks, wobei der erste Druck ein höherer Druck als der zweite Druck ist. Dadurch wird gewährleistet, dass das Arbeitswerkzeug gegen jede Vorspannung des Gegenhaltezylinders in Richtung des Presstisches bewegt werden kann und somit auch bei einer höheren Vorspannung eine ausreichende Umformkraft zur Verfügung steht. In einer Ausführungsform ist der zweite Druckspeicher dabei zum Speichern von kinetischer Energie des Presszylinders in Form eines erhöhten Drucks bei der Schnittschlagdämpfung und zum Freisetzen diese Energie zum Rückhub (Rückzugsphase) des Presszylinders mittels einer erhöhte Vorspannung der Gegenhaltezylinder vorgesehen. In einer bevorzugten Ausführungsform ist der erste Druckspeicher ein Hochdruckspeicher mit Drücken im Bereich von 350bar und der zweite Druckspeicher ein Mitteldruckspeicher mit Drücken im Bereich von 210 bar.In a further embodiment, 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. This ensures that the working tool can be moved against any bias of the counter-holding cylinder in the direction of the press table and thus a sufficient forming force is available even at a higher bias. In one embodiment, the second accumulator is provided for storing kinetic energy of the pressing cylinder in the form of an increased pressure in the cutting impact damping and releasing this energy for return stroke (retraction phase) of the pressing cylinder by means of an increased bias of the counter-holding cylinder. In a preferred embodiment, 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.
In einer weiteren Ausführungsform sind die ersten und zweiten hydraulischen Anordnungen jeweils an eine erste beziehungsweise zweite Druckversorgung angeschlossen. Dieser Anschluss ist vorzugsweise über Rückschlagventile ausgeführt. Diese Rückschlagventile dichten die ersten und zweiten Anordnungen dabei zumindest bis zu den ersten bzw. zweiten Drücken nach außen ab. Dadurch können dauerhafte Konstanthaltungen der in den ersten und zweiten hydraulischen Anordnungen anliegenden Drücken gewährleistet werden.In a further embodiment, the 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.
In einer weiteren Ausführungsform umfasst die Presse mehrere Gegenhaltezylinder, die alle jeweils mechanisch über ihre Gegenhaltezylinderstangen mit dem Arbeitswerkzeug verbunden sind. Somit können leicht auch Pressen mit größeren ausgedehnten Arbeitswerkzeugen zuverlässig vorgespannt werden. In einer bevorzugten Ausführungsform sind die Gegenhaltezylinder vorzugsweise symmetrisch zueinander angeordnet. Somit werden Verkippungen des Arbeitswerkzeugs aufgrund des Schnittschlags vermieden, was eine effektivere materialschonende Dämpfung der Presse ermöglicht.In a further embodiment, the press comprises a plurality of counter-holding cylinders, each of which is in each case mechanically connected via its counter-holding cylinder rods to the working tool. Thus, even presses with larger extended work tools can be reliably biased. In a preferred embodiment, 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.
In einer weiteren Ausführungsform sind die Gegenhaltezylinder über einen entsprechenden Hydraulikkreis miteinander und der Hydraulikkreis über das zweite Stetigventil mit der zweiten hydraulischen Anordnung verbunden. Somit braucht auch bei mehreren Gegenhaltezylindern nur ein einzelnes Stetigventil von der Steuereinheit angesteuert werden, was eine kostengünstige Herstellung der Presse ermöglicht und den Betrieb der Presse vereinfacht. Allerdings werden dadurch auch die benötigten hydraulischen Rohrleitungen länger, was eine Verzögerung der Druckbeaufschlagung der Gegenhaltezylinder aufgrund der geringen aber dennoch vorhandenen Kompressibilität des hydraulischen Fluids nach sich zieht.In a further embodiment, 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. Thus, even with a plurality of counter-holding cylinders only a single continuous valve needs to be controlled by the control unit, which allows a cost-effective production of the press and simplifies the operation of the press. However, this also makes the required hydraulic pipelines longer, which entails a delay in the pressurization of the counter-holding cylinders due to the low but nevertheless existing compressibility of the hydraulic fluid.
In einer alternativen Ausführungsform umfasst die Presse mehrere zweite Stetigventile und mehrere zweite hydraulische Anordnungen, wobei jeder Gegenhaltezylinder über ein einzelnes der zweiten Stetigventile mit jeweils einer einzelnen der hydraulischen Anordnungen verbunden ist, und alle zweiten Stetigventile zur Ansteuerung mit der Steuereinheit verbunden sind. In einer solchen Anordnung können die einzelnen Gegenhaltezylinder sehr präzise und mit sehr kurzen Ansprechzeiten mit dem gewünschten Druck durch Ansteuerung der individuellen Stetigventile beaufschlagt werden. Hierbei können bei Bedarf auch Unwuchten der Presse durch individuelle Druckbeaufschlagung der einzelnen Gegenhaltezylinder mit leicht anderen Vorspannungen ausgeglichen werden. Allerdings benötigt diese Anordnung einen höheren apparativen und gegebenenfalls steuertechnischen Aufwand.In an alternative embodiment, the press comprises a plurality of second proportional valves and a plurality of second hydraulic assemblies, each retainer 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. In such an arrangement, 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.
In einer weiteren Ausführungsform ist die zweite Druckversorgung als zentrale Druckversorgung für alle zweiten hydraulischen Anordnungen ausgestaltet. Da die zweiten Drücke im Wesentlichen für alle Gegenhaltezylinder gleich sind, können die einzelnen zweiten Drücke auch durch eine zentrale Druckversorgung langfristig gewährleistet werden, was die Herstellungskosten dieser Anordnung mindert.In a further embodiment, 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.
In einer weiteren Ausführungsform ist die zweite hydraulische Anordnung an den Gegenhaltezylinder angeflanscht. Durch diese Maßnahme wird das Kompressionsvolumen der hydraulischen Flüssigkeit wegen der kurzen hydraulischen Leitungen in der zweiten hydraulischen Anordnung weiter reduziert und damit die hydraulische Steifigkeit erhöht. Daher ist die Eigenfrequenz für das gekoppelte Federmassesystem bestehend aus bewegten Massen und den hydraulischen Kapazitäten extrem günstig und lässt besonders hohe Hubzahlen zu.In a further embodiment, the second hydraulic arrangement is flanged to the counter-holding cylinder. By this measure, the compression volume of the hydraulic fluid is further reduced because of the short hydraulic lines in the second hydraulic arrangement and thus increases the hydraulic rigidity. Therefore, the natural frequency for the coupled spring mass system consisting of moving masses and the hydraulic capacities is extremely low and allows for particularly high stroke rates.
In einer weiteren Ausführungsform umfasst die Presse mindestens ein Wegemesssystem zur Erfassung der Bewegung der Presszylinder und/oder Gegenhaltezylinder, das Positionsdaten und/oder Geschwindigkeitsdaten der Presszylinder und/oder Gegenhaltezylinder zur Steuerung der Stetigventile an die Steuereinheit übermittelt. In Kombination oder als Alternative kann die Presse auch Druckmesssysteme zur Erfassung von an dem Presszylinder und/oder den Gegenhaltezylindern anliegenden Drücken umfassen, welches Druckdaten der Presszylinder und/oder Gegenhaltezylinder zur Steuerung der Stetigventile an die Steuereinheit übermittelt. Diese Datenübermittlung erfolgt, wie auch die Ansteuerung der Stetigventile durch die Steuereinheit, durch geeignete Datenleitungen. Das Wegemesssystem und/oder das Druckmesssystem können die Präzision der Steuerung der Stetigventile zur gewünschten Bewegung des Arbeitswerkzeugs und zur effektiven Schnittschlagdämpfung unterstützen, da die Messdaten zum berechneten Bewegungsablauf rückgekoppelt werden. Im Falle einer reduzierten Vorspannung bei einer gewollten Erhöhung der Umformkraft kann diese Vorspannung zur Dämpfung des Schnittschlages durch entsprechende Ansteuerung der schnellschaltenden Stetigventile durch die Steuereinheit sofort erhöht werden, wenn das Wegemesssystem oder das Druckmesssystem einen Materialdurchbruch anhand einer stark beschleunigten Bewegung des Arbeitswerkzeugs oder eines kurzfristigen starken Druckanstiegs detektiert.In a further embodiment, 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. In combination or as an alternative, 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. In the case of a reduced bias at a desired increase in the forming force, 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.
Die Erfindung betrifft des Weiteren ein Verfahren zum Betreiben einer erfindungsgemäßen hydraulischen Presse mit integrierter Schnittschlagdämpfung mit einem Maschinenrahmen mit einem Presstisch, einem im Maschinenrahmen gelagerten Arbeitswerkzeug und mindestens einem am Maschinenrahmen befestigten Presszylinder, der mit einer ersten hydraulischen Anordnung unter einem ersten Druck zur Bewegung des Presszylinders über ein erstes Stetigventil und über eine Presszylinderstange mechanisch mit dem Arbeitswerkzeug verbunden ist, und mit mindestens einem am Maschinenrahmen befestigten Gegenhaltezylinder, der mit einer von der ersten hydraulischen Anordnung getrennt wirkend ausgeführten zweiten hydraulischen Anordnung unter einem zweiten Druck zur Bewegung des Gegenhaltezylinder über ein zweites Stetigventil und über eine Gegenhaltezylinderstange mechanisch mit dem Arbeitswerkzeug verbunden ist, und mit eine mit den ersten und zweiten Stetigventilen verbundenen Steuereinheit, umfassend die Schritte
- Durchfahren einer Leerhubphase des Arbeitswerkzeugs von einem ersten Totpunkt in Richtung des Presstisches als erster Teil des Bearbeitungsgangs;
- Durchfahren einer Druckaufbauphase für das Arbeitswerkzeug nach Kontakt des Arbeitswerkzeugs mit dem auf dem Presstisch angeordneten Werkstück zur Ausübung einer Umformkraft auf das Werkstück, als zweiter Teil des Bearbeitungsgangs;
- Durchfahren einer Umformphase für das Arbeitswerkzeug und das Werkstück bis Erreichen eines zweiten Totpunkts als dritter Teil des Bearbeitungsgangs; und
- Durchfahren einer Rückzugphase zur Vorbereitung eines neuen Bearbeitungsganges für das Arbeitswerkzeugs vom zweiten Totpunkt zum ersten Totpunkt,
- Traversing a Leerhubphase the working tool from a first dead center in the direction of the press table as the first part of the processing cycle;
- Passing through a pressure buildup phase for the work tool after contact of the work tool with the arranged on the press table workpiece for exerting a forming force on the workpiece, as the second part of the processing cycle;
- Passing through a forming phase for the working tool and the workpiece until reaching a second dead center as the third part of the processing cycle; and
- Traversing a retraction phase to prepare a new machining gear for the working tool from the second dead center to the first dead center,
In einer Ausführungsform des Verfahrens umfasst das Durchfahren der Druckaufbauphase den Schritt des Reduzierens der Vorspannung, wozu beide Zylinderkammern des Gegenhaltezylinders über eine Bypassleitung und ein darin angeordnetes Schaltventil miteinander verbunden sind, und die Steuereinheit das Schaltventil zumindest während Druckaufbauphase zur Druckreduzierung des Gegenhaltezylinders öffnet. Durch die Reduzierung der Vorspannung kann die Umformkraft bei Bedarf erhöht werden, sofern die resultierende Umformkraft bei der ursprünglichen Vorspannung nicht zur Bearbeitung des Werkstücks ausreicht oder eine höhere Umformkraft gewünscht wird.In one embodiment of the method, performing the pressure build-up phase comprises the step of reducing the bias voltage to which both cylinder chambers of the counter-holding cylinder are connected 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 counter-holding cylinder. By reducing the preload, the forming force can be increased if necessary, provided that the resulting forming force at the original bias is not sufficient for machining the workpiece or a higher forming force is desired.
Die erfindungsgemäße Presse kann dabei gemäß dem Gegenstand des Hauptanspruchs oder gemäß einer der voranstehenden Ausführungsformen oder gegebenenfalls unter Verwirklichung einer Kombination mehrere der voranstehenden Ausführungsformen ausgestaltet sein. Gleiches gilt für das erfindungsgemäße Verfahren.The press according to the invention can be designed according to the subject matter of the main claim or according to one of the preceding embodiments or, where appropriate, by realizing a combination of several of the preceding embodiments. The same applies to the method according to the invention.
Diese und andere Aspekte der Erfindung werden im Detail in den Abbildungen wie folgt gezeigt:
- Fig.1:
- ein Ausführungsbeispiel einer erfindungsgemäßen Presse mit einem Gegenhaltezylinder;
- Fig.2:
- ein alternatives Ausführungsbeispiel einer erfindungsgemäßen Presse mit zwei symmetrisch zueinander angeordneten Gegenhaltezylindern mit jeweils separaten zweiten hydraulischen Anordnungen;
- Fig.3:
- ein alternatives Ausführungsbeispiel einer erfindungsgemäßen Presse mit zwei symmetrisch zueinander angeordneten Gegenhaltezylindern mit einer gemeinsamen zweiten hydraulischen Anordnung;
- Fig.4:
- ein Ausführungsbeispiel für die in den vorangegangenen Abbildungen verwendeten ersten und zweiten Stetigventile und dem Schaltventil in der Bypassleitung des Gegenhaltezylinders;
- Fig.5:
- ein Ausführungsbeispiel eines Verfahrens zum Betreiben der erfindungsgemäßen Presse anhand von verschiedenen Kenngrößen der Presse über einen kompletten Bewegungszyklus des Arbeitswerkzeugs.
- Fig.1:
- An embodiment of a press according to the invention with a counter-holding cylinder;
- Figure 2:
- an alternative embodiment of a press according to the invention with two counter-holding cylinders arranged symmetrically to each other, each with separate second hydraulic arrangements;
- Figure 3:
- an alternative embodiment of a press according to the invention with two counter-holding cylinders arranged symmetrically to each other with a common second hydraulic arrangement;
- Figure 4:
- an embodiment of the first and second proportional valves used in the previous figures and the switching valve in the bypass line of the counter-holding cylinder;
- Figure 5:
- An embodiment of a method for operating the press according to the invention based on different characteristics of the press over a complete cycle of movement of the working tool.
Aus energetischen Gründen wird in der Leerhubphase LH die Geschwindigkeit des Arbeitswerkzeugs 4 so geregelt, dass das verdrängte hydraulische Fluid, beispielsweise Öl, aus der Kolbenkammer 7b des Gegenhaltezylinders 7 über die Steuerkante des zweiten Stetigventils 92 in den Druckspeicher 821 quasi drosselfrei verdrängt und zwischengespeichert wird. Da der Maschinenrahmen 2 bereits vorgespannt ist, wird die Funktion Schnittschlagdämpfung nur bei sehr hohen Umformkräften benötigt, da beim Werkstückdurchbruch nur eine geringe Entspannung des Maschinenrahmens 2 auftritt und die kinetische Energie in den Druckspeicher 821 und mit einer steilen Druckanstiegs-Kennlinie gepuffert wird. Somit wird der üblicherweise entstehende Schnittschlag und die extreme Beschleunigung des Presszylinders 6 vermieden. Zusätzlich können Beschleunigungssensoren als Teil des Wegemesssystems 64, 74 zur Erfassung des Werkzeugdurchbruches verwendet werden. Zur Aufrechterhaltung des Speicherdruckes des Druckspeichers 821, der im Prinzip dem Gegenhaltedruck (Vorspannung V) entspricht, braucht nur die Spaltleckage am Stetigventil 92 durch die Druckversorgung 822 kompensiert werden. Üblicherweise sind bei üblichen Druckverhältnissen ca. 3-5 L/min Volumenstrom erforderlich und somit ist auch ein Austausch des Öls als hydraulisches Fluid über mehrere Zyklen gewährleistet. Die Auffangtanks 814, 824 können durch einen einzigen zentralen Tank gebildet werden. Bei der Rückzugsphase RZ wird die im Druckspeicher 821 gepufferte Energie genutzt, um das Arbeitswerkzeug 4 energetisch günstig nach oben zu positionieren, wobei beim Erreichen vom ersten (oberen) Totpunkt T1 des Presszylinders 6 die Vorspannung V des Maschinenrahmens 2 den Ursprungswert wieder erreicht. Es findet somit eine Rückgewinnung der Energie, die nach dem Materialdurchtritt freigesetzt wird, statt.For energetic reasons, in the Leerhubphase LH the speed of the working
Vorzugsweise liegt der Minimalwert MW der Vorspannung (V) zwischen 20% und 50% der Umformkraft, vorzugsweise zwischen 30% und 45% der Umformkraft, besonders bevorzugt zwischen 38% und 42% der Umformkraft, beträgt.Preferably, 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.
Die hier gezeigten Ausführungsbeispiele stellen nur Beispiele für die vorliegende Erfindung dar und dürfen daher nicht einschränkend verstanden werden. Alternativen durch den Fachmann in Erwägung gezogene Ausführungsformen sind gleichermaßen vom Schutzbereich der vorliegenden Erfindung umfasst.The embodiments shown here are only examples of the present invention and therefore should not be understood as limiting. Alternatives contemplated by one skilled in the art are equally within the scope of the present invention.
- 11
- erfindungsgemäße PressePress according to the invention
- 22
- Maschinenrahmenmachine frame
- 33
- Presstischpress table
- 44
- Arbeitswerkzeugwork tool
- 55
- durch die Presse zu bearbeitendes Werkstückthrough the press to be machined workpiece
- 66
- Presszylinderpress cylinder
- 6161
- PresszylinderstangePress cylinder rod
- 6262
- Ringfläche PresszylinderRing surface press cylinder
- 6363
- Kolbenfläche PresszylinderPiston surface pressing cylinder
- 6464
- Wegemesssystem zur Bewegungserfassung des PresszylindersPosition measuring system for detecting movement of the pressing cylinder
- 6565
- Druckmesssystem zur Ermittlung des am Presszylinder anliegenden DruckesPressure measuring system for determining the pressure applied to the pressing cylinder
- 77
- GegenhaltezylinderCounterforce cylinder
- 7a, 7b7a, 7b
- Zylinderkammern des GegenhaltezylindersCylinder chambers of the counter-holding cylinder
- 7171
- GegenhaltezylinderstangeCounterforce cylinder rod
- 7272
- Ringfläche GegenhaltezylinderRing surface counterhold cylinder
- 7373
- Kolbenfläche GegenhaltezylinderPiston surface retaining cylinder
- 7474
- Wegemesssystem zur Bewegungserfassung des GegenhaltezylindersPosition measuring system for detecting movement of the counter-holding cylinder
- 7575
- Druckmesssystem zur Ermittlung des am Gegenhaltezylinders anliegenden DruckesPressure measuring system for determining the pressure applied to the counter-holding cylinder
- 7676
- Hydraulikkreis zur Verbindung mehrerer GegenhaltezylinderHydraulic circuit for connecting several counter-holding cylinders
- 88th
- Hydraulikleitunghydraulic line
- 8181
- erste hydraulische Anordnungfirst hydraulic arrangement
- 811811
- erster Druckspeicherfirst accumulator
- 812812
- erste Druckversorgungfirst pressure supply
- 813813
- (erstes) Rückschlagventil(first) check valve
- 814814
- Auffangtankcollecting tank
- 8282
- zweite hydraulische Anordnungsecond hydraulic arrangement
- 821821
- zweiter Druckspeichersecond pressure accumulator
- 822822
- zweite Druckversorgungsecond pressure supply
- 823823
- (zweites) Rückschlagventil(second) check valve
- 824824
- Auffangtankcollecting tank
- 9191
- erstes Stetigventilfirst continuous valve
- 9292
- zweites Stetigventilsecond continuous valve
- 1010
- Steuereinheitcontrol unit
- 1111
- Bypassleitungbypass line
- 114114
- Auffangtank der BypassleitungCollecting tank of the bypass line
- 1212
- Schaltventilswitching valve
- BB
- Bearbeitungsgangmachining operation
- D1D1
- erster Druck (in der ersten hydraulischen Anordnung)first pressure (in the first hydraulic arrangement)
- D2D2
- zweiter Druck (in der zweiten hydraulischen Anordnung)second pressure (in the second hydraulic arrangement)
- DATHERE
- DruckaufbauphasePressure build-up phase
- DDDD
- Druckdaten des DruckmesssystemsPressure data of the pressure measuring system
- PDPD
- Positionsdaten des WegemesssystemsPosition data of the position measuring system
- LHLH
- LeerhubphaseLeerhubphase
- MWMW
- Minimalwert der VorspannungMinimum value of the preload
- RZRZ
- Rückzugsphaseretraction phase
- SS
- Ansteuern der Stetigventile durch die SteuereinheitActivation of the proportional valves by the control unit
- SDSD
- Schaltstellung, die eine Drosselung der ersten / zweiten Drücke ermöglichtSwitching position that allows throttling of the first / second pressures
- T1T1
- erster Totpunkt (im Bewegungsablauf des Arbeitswerkzeugs)first dead center (in the movement sequence of the working tool)
- T2T2
- zweiter Totpunkt (im Bewegungsablauf des Arbeitswerkzeugs)second dead center (in the movement sequence of the working tool)
- UFUF
- Umformphaseforming phase
- VV
- Vorspannungpreload
Claims (16)
dadurch gekennzeichnet,
dass die Stetigventile (91, 92) zumindest eine Schaltstellung (SD) umfassen, die eine von der Steuereinheit (10) variabel einstellbare Drosselung der ersten und/oder zweiten Drücke (D1, D2) zur variablen Druckbeaufschlagung durch die Stetigventile (91, 92) ermöglicht.The hydraulic press (1) according to claim 1,
characterized,
in that the continuous valves (91, 92) comprise at least one switching position (SD) which permits a variable adjustment of the first and / or second pressures (D1, D2) by the control unit (10) for the variable pressurization by the continuous valves (91, 92). allows.
dadurch gekennzeichnet,
dass die Stetigventile (91, 92) Servoventile mit Schaltzeiten kleiner 20ms, vorzugsweise kleiner 10ms, sind.The hydraulic press (1) according to claim 1 or 2,
characterized,
in that the continuous valves (91, 92) are servo valves with switching times of less than 20 ms, preferably less than 10 ms.
dadurch gekennzeichnet,
dass der Minimalwert (MW) der Vorspannung (V) zwischen 20% und 50% der Umformkraft, vorzugsweise zwischen 30% und 45% der Umformkraft, besonders bevorzugt zwischen 38% und 42% der Umformkraft, beträgt.The hydraulic press (1) according to one of the preceding claims,
characterized,
that the minimum value (MW) of the bias voltage (V) 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 deformation force, is.
dadurch gekennzeichnet,
dass beide Zylinderkammern (7a, 7b) des Gegenhaltezylinders (7) über eine Bypassleitung (11) und ein darin angeordnetes Schaltventil (12), vorzugsweise ein 2/2-Wegeventil, miteinander verbunden sind, wobei das Schaltventil (12) ebenfalls mit der Steuereinheit (10) verbunden ist.The hydraulic press (1) according to claim 4,
characterized,
in that both cylinder chambers (7a, 7b) of the counter-holding cylinder (7) are connected to one another via a bypass line (11) and a switching valve (12) arranged therein, preferably a 2/2-way valve, wherein the switching valve (12) also communicates with the control unit (10) is connected.
dadurch gekennzeichnet,
dass die erste hydraulische Anordnung (81) einen ersten Druckspeicher (811) zur Speicherung des ersten Drucks (D1) und die zweite hydraulische Anordnung (82) einen zweiten Druckspeicher (821) zur Speicherung des zweiten Drucks (D1) umfasst, wobei der erste Druck (D1) ein höherer Druck als der zweite Druck (D2) ist, vorzugsweise ist der erste Druckspeicher (811) ein Hochdruckspeicher und der zweite Druckspeicher (821) ein Mitteldruckspeicher.The hydraulic press (1) according to one of the preceding claims,
characterized,
in that the first hydraulic arrangement (81) comprises a first pressure accumulator (811) for storing the first pressure (D1) and the second hydraulic arrangement (82) comprises a second pressure accumulator (821) for storing the second pressure (D1), wherein the first pressure (D1) is a higher pressure than the second pressure (D2), preferably, the first pressure accumulator (811) is a high pressure accumulator and the second accumulator (821) is a medium pressure accumulator.
dadurch gekennzeichnet,
dass der zweite Druckspeichers (821) zum Speichern von kinetischer Energie des Presszylinders (6) in Form eines erhöhten Drucks bei der Schnittschlagdämpfung und zum Freisetzen diese Energie zum Rückhub des Presszylinders (6) mittels einer erhöhte Vorspannung der Gegenhaltezylinder (7) vorgesehen ist.The hydraulic press (1) according to claim 6,
characterized,
in that the second pressure accumulator (821) is provided for storing kinetic energy of the pressing cylinder (6) in the form of an increased pressure during the cutting impact damping and for releasing this energy for the return stroke of the pressing cylinder (6) by means of an increased prestressing of the retaining cylinders (7).
dadurch gekennzeichnet,
dass die ersten und zweiten hydraulischen Anordnungen (81, 82) jeweils an eine erste beziehungsweise zweite Druckversorgung (812, 822) zur Konstanthaltung der in den ersten und zweiten hydraulischen Anordnungen (81, 82) anliegenden Drücken (D1, D2) angeschlossen sind, vorzugsweise über Rückschlagventile (813, 823).The hydraulic press (1) according to claim 6 or 7,
characterized,
that the first and second hydraulic arrangements (81, 82) each connected to a respective first and second pressure supply (812, 822) for keeping constant the in the first and second hydraulic arrangements (81, 82) applied pressures (D1, D2) are connected, preferably via check valves (813, 823).
dadurch gekennzeichnet,
dass die Presse (1) mehrere Gegenhaltezylinder (7) umfasst, die alle jeweils mechanisch über ihre Gegenhaltezylinderstangen (71), vorzugsweise symmetrisch zueinander, mit dem Arbeitswerkzeug (4) verbunden sind.The hydraulic press (1) according to one of the preceding claims,
characterized,
in that the press (1) comprises a plurality of counter-holding cylinders (7), which are each in each case mechanically connected to the working tool (4) via their counter-holding cylinder rods (71), preferably symmetrically to one another.
dadurch gekennzeichnet,
dass die Gegenhaltezylinder (7) über einen entsprechenden Hydraulikkreis (76) miteinander und der Hydraulikkreis (76) über das zweite Stetigventil (92) mit der zweiten hydraulischen Anordnung (82) verbunden sind.The hydraulic press (1) according to claim 9,
characterized,
in that the counter-holding cylinders (7) are connected to one another via a corresponding hydraulic circuit (76) and the hydraulic circuit (76) is connected to the second hydraulic arrangement (82) via the second proportional valve (92).
dadurch gekennzeichnet,
dass die Presse (1) mehrere zweite Stetigventile (92) und mehrere zweite hydraulische Anordnungen (82) umfasst, wobei jeder Gegenhaltezylinder (7) über ein einzelnes der zweiten Stetigventile (92) mit jeweils einer einzelnen der hydraulischen Anordnungen (82) verbunden ist, und alle zweiten Stetigventile (92) zur Ansteuerung mit der Steuereinheit (10) verbunden sind.The hydraulic press (1) according to claim 9,
characterized,
in that the press (1) comprises a plurality of second continuous valves (92) and a plurality of second hydraulic arrangements (82), each counter-holding cylinder (7) being connected via a single one of the second proportional valves (92) each having a single one the hydraulic assemblies (82) is connected, and all second proportional valves (92) are connected to the control unit (10) for activation.
dadurch gekennzeichnet,
dass die zweite Druckversorgung (822) als zentrale Druckversorgung für alle zweiten hydraulischen Anordnungen (82) ausgestaltet ist.The hydraulic press (1) according to claim 11,
characterized,
that the second pressure supply (822) is designed as a central pressure supply for all of the second hydraulic arrangements (82).
dadurch gekennzeichnet,
dass die zweite hydraulische Anordnung (82) an den Gegenhaltezylinder (7) angeflanscht istThe hydraulic press (1) according to one of the preceding claims,
characterized,
that the second hydraulic arrangement (82) is flanged to the counter-holding cylinder (7)
dadurch gekennzeichnet,
dass die Presse (1) mindestens ein Wegemesssystem (64, 74) zur Erfassung der Bewegung der Presszylinder (6) und/oder Gegenhaltezylinder (7) umfasst, das Positionsdaten (PD) und/oder Geschwindigkeitsdaten der Presszylinder (6) und/oder Gegenhaltezylinder (7) zur Steuerung der Stetigventile (91, 92) an die Steuereinheit (10) übermittelt und/oder dass die Presse (1) ein Druckmesssystem (65, 75) zur Erfassung von an dem Presszylinder (6) und/oder Gegenhaltezylinder (7) anliegenden Drücken umfasst, das Druckdaten (DD) der Presszylinder (6) und/oder Gegenhaltezylinder (7) zur Steuerung der Stetigventile (91, 92) an die Steuereinheit (10) übermitteltThe hydraulic press (1) according to claim 1,
characterized,
in that the press (1) comprises at least one path measuring system (64, 74) for detecting the movement of the pressing cylinders (6) and / or counter-holding cylinders (7), the position data (PD) and / or speed data of the pressing cylinders (6) and / or counter-holding cylinders (7) for controlling the continuous valves (91, 92) to the control unit (10) and / or that the press (1) a pressure measuring system (65, 75) for detecting on the press cylinder (6) and / or counter-holding cylinder (7 ), which transmits pressure data (DD) of the pressing cylinders (6) and / or counter-holding cylinders (7) for controlling the continuous valves (91, 92) to the control unit (10)
wobei die Steuereinheit (10) die ersten und zweiten Stetigventile (91, 92) so zu einer simultanen aufeinander angepassten Druckbeaufschlagung der Press- und Gegenhaltezylinder (6, 7) ansteuert (S), dass die von Gegenhaltezylinder (7) und Presszylinder (6) über den Maschinenrahmen (2) und das Arbeitswerkzeug (4) ausgeübte axiale Vorspannung (V) einen durch die Steuereinheit (10) vorgebbaren Minimalwert (MW) zur Bereitstellung der Schnittschlagdämpfung zumindest während des Bearbeitungsgangs (B) nicht unterschritten und gleichzeitig eine gewünschte Bewegung des Arbeitswerkzeugs (4) ermöglicht wird.
wherein the control unit (10) activates the first and second continuous valves (91, 92) in such a way that simultaneous pressurization of the pressing and counter-holding cylinders (6, 7) takes place (S), that of counter-holding cylinders (7) and pressing cylinders (6). axial preload (V) exerted on the machine frame (2) and the working tool (4) does not fall below a minimum value (MW) predeterminable by the control unit (10) for providing the cutting impact damping at least during the machining operation (B) and at the same time a desired movement of the working tool (4) is enabled.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP15154818.7A EP3056291B1 (en) | 2015-02-12 | 2015-02-12 | Press with cutting shock damping |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP15154818.7A EP3056291B1 (en) | 2015-02-12 | 2015-02-12 | Press with cutting shock damping |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3056291A1 true EP3056291A1 (en) | 2016-08-17 |
EP3056291B1 EP3056291B1 (en) | 2017-04-19 |
Family
ID=52465285
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15154818.7A Not-in-force EP3056291B1 (en) | 2015-02-12 | 2015-02-12 | Press with cutting shock damping |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP3056291B1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN111318605A (en) * | 2018-12-13 | 2020-06-23 | 莱玛特·沃尔特斯有限公司 | Fine blanking press and method for operating a fine blanking press |
DE102019008242A1 (en) * | 2019-11-27 | 2021-05-27 | Siempelkamp Maschinen- Und Anlagenbau Gmbh | Torque compensation for forging press |
US11260441B2 (en) * | 2017-11-24 | 2022-03-01 | Danieli & C. Officine Meccaniche S.P.A. | Press for extruding metal material |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2221290A1 (en) * | 1972-04-29 | 1973-11-15 | Schuler Gmbh L | PRESS WITH CONTROLLED CUTTING |
DE2824176A1 (en) * | 1978-06-02 | 1979-12-06 | Thyssen Industrie | Hydraulic press with servo-hydraulic ram movement control - has individual cylinders with chambers for press working force, and opposite force |
DE19643396B4 (en) | 1996-10-21 | 2008-09-11 | Dieffenbacher Gmbh + Co. Kg | Hydraulic control device |
DE102009048483A1 (en) | 2009-09-29 | 2011-06-16 | Voith Patent Gmbh | Cutting shock damping |
-
2015
- 2015-02-12 EP EP15154818.7A patent/EP3056291B1/en not_active Not-in-force
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2221290A1 (en) * | 1972-04-29 | 1973-11-15 | Schuler Gmbh L | PRESS WITH CONTROLLED CUTTING |
DE2824176A1 (en) * | 1978-06-02 | 1979-12-06 | Thyssen Industrie | Hydraulic press with servo-hydraulic ram movement control - has individual cylinders with chambers for press working force, and opposite force |
DE19643396B4 (en) | 1996-10-21 | 2008-09-11 | Dieffenbacher Gmbh + Co. Kg | Hydraulic control device |
DE102009048483A1 (en) | 2009-09-29 | 2011-06-16 | Voith Patent Gmbh | Cutting shock damping |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11260441B2 (en) * | 2017-11-24 | 2022-03-01 | Danieli & C. Officine Meccaniche S.P.A. | Press for extruding metal material |
CN111318605A (en) * | 2018-12-13 | 2020-06-23 | 莱玛特·沃尔特斯有限公司 | Fine blanking press and method for operating a fine blanking press |
CN111318605B (en) * | 2018-12-13 | 2024-01-02 | 莱玛特·沃尔特斯有限公司 | Fine blanking press and method for operating a fine blanking press |
DE102019008242A1 (en) * | 2019-11-27 | 2021-05-27 | Siempelkamp Maschinen- Und Anlagenbau Gmbh | Torque compensation for forging press |
Also Published As
Publication number | Publication date |
---|---|
EP3056291B1 (en) | 2017-04-19 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE102006058630B4 (en) | Electro-hydraulic press main or auxiliary drive device, in particular electro-hydraulic die cushion drive | |
EP3174650B1 (en) | Punching device and method for punching a workpiece | |
DE4308344A1 (en) | Method for controlling the drive of a hydraulic press and device for carrying out the method | |
AT509239B1 (en) | DRIVE DEVICE FOR A BEND PRESS | |
EP1782897B1 (en) | Press with cutting shocks damping. | |
DE10393056B4 (en) | Hydraulic control in a hydraulic system, in particular for the operation of a scrap shear | |
EP2183096A1 (en) | Drive system for hydraulic presses | |
DE19831624A1 (en) | Hydraulic drive for a press | |
EP3056291B1 (en) | Press with cutting shock damping | |
EP1656224B1 (en) | Device for controlling the drawing process in a transfer press | |
EP1602419B1 (en) | Press for cutting high strength metal sheets | |
DE4104136A1 (en) | Press for deep drawing of sheet metal workpieces - has hydraulic devices to control movement of punch and ram | |
EP3115190B1 (en) | Device and method for controlling the principal drive of a precision cutting press | |
DE3935498C3 (en) | Switchable press device for machining workpieces | |
DE102014002888A1 (en) | Forging hammer and method for operating a forging hammer | |
DE10005023A1 (en) | Press | |
WO2005021253A2 (en) | Hydraulic press and deep-drawing press | |
EP2114587B1 (en) | Forming press with a drawing cushion function integrated into the sliding table | |
DE102014101616B4 (en) | Hydraulic drawing pad of a drawing press and method of operating the hydraulic drawing pad | |
DE4122128A1 (en) | Hydro-elastic deep drawing of sheet metal workpieces - uses system which automatically actuates punch mounted in baseplate, with metal blank being gripped between hold-down plates | |
EP0865843A1 (en) | Drawing device for a drawing press | |
DE2432774B2 (en) | Press, especially fine blanking press | |
DE2621726C2 (en) | Cutting shock absorption device on presses | |
WO2008022607A1 (en) | Method and device for dampening cutting shock | |
DE1145018B (en) | High-speed hydraulic press, especially forging press or drawing press |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
17P | Request for examination filed |
Effective date: 20161117 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: B21D 24/02 20060101AFI20161205BHEP Ipc: B30B 15/16 20060101ALI20161205BHEP |
|
INTG | Intention to grant announced |
Effective date: 20161220 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 885455 Country of ref document: AT Kind code of ref document: T Effective date: 20170515 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502015000877 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20170419 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170720 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170719 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170719 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170819 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502015000877 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 |
|
26N | No opposition filed |
Effective date: 20180122 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20180727 Year of fee payment: 4 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20180228 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180228 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180228 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180212 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20181031 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180212 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180228 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180228 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502015000877 Country of ref document: DE |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20190212 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190212 Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190903 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20150212 Ref country code: MK Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170419 Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170419 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180212 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 885455 Country of ref document: AT Kind code of ref document: T Effective date: 20200212 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200212 |