EP3280554B1 - Marteau pilon et procédé de commande du cycle de travail d'un marteau pilon - Google Patents

Marteau pilon et procédé de commande du cycle de travail d'un marteau pilon Download PDF

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Publication number
EP3280554B1
EP3280554B1 EP16712778.6A EP16712778A EP3280554B1 EP 3280554 B1 EP3280554 B1 EP 3280554B1 EP 16712778 A EP16712778 A EP 16712778A EP 3280554 B1 EP3280554 B1 EP 3280554B1
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EP
European Patent Office
Prior art keywords
hydraulic
speed
pump
hydro
piston
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EP16712778.6A
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German (de)
English (en)
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EP3280554A1 (fr
Inventor
Markus Otto
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Langenstein and Schemann GmbH
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Langenstein and Schemann GmbH
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Publication of EP3280554A1 publication Critical patent/EP3280554A1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B21J7/22—Drives for hammers; Transmission means therefor for power hammers
    • B21J7/28—Drives for hammers; Transmission means therefor for power hammers operated by hydraulic or liquid pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J11/00—Forging hammers combined with forging presses; Forging machines with provision for hammering and pressing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B21J7/46—Control devices specially adapted to forging hammers, not restricted to one of the preceding subgroups
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/10—Drives for forging presses
    • B21J9/12—Drives for forging presses operated by hydraulic or liquid pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/10—Drives for forging presses
    • B21J9/20—Control devices specially adapted to forging presses not restricted to one of the preceding subgroups
    • 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

Definitions

  • the underlying invention relates to a forming machine, in particular a forging hammer, and to a method for controlling a corresponding forming machine.
  • a forging hammer for the reshaping of workpieces comprising a striking tool and a hydraulic linear drive coupled to the striking tool and designed to drive the striking tool with a hydraulic circuit comprising a pressure accumulator, a hydraulic cylinder, in particular a differential cylinder, connected downstream of the pressure accumulator via a directional valve assembly, and comprising the Furthermore, a control unit designed at least for controlling the directional valve assembly.
  • the EP 0 116 024 B1 describes in connection with hydraulic machines the use of a pressure accumulator and hydraulic motor for the operation of hydraulic cylinders.
  • the EP 0 116 024 B1 also describes that elastic energy stored in the hydraulic system during operation of hydraulic machines can be converted into electrical energy by a hydraulic generator connected in parallel with the hydraulic pump in terms of fluid technology, the hydraulic generator being connected to the hydraulic circuit in order to generate the electrical energy.
  • an object of the present invention can be seen in particular in further developing and / or improving the known forming machines, in particular with regard to drive, energy efficiency and / or achievable working speeds.
  • the forming machine according to the embodiment according to claim 1 comprises an impact tool, for example an upper, lower die and / or bear, which e.g. can be designed as such as a forming tool, or can have a forming tool, and / or can have an interface for receiving, in particular fastening, a forming tool.
  • an impact tool for example an upper, lower die and / or bear, which e.g. can be designed as such as a forming tool, or can have a forming tool, and / or can have an interface for receiving, in particular fastening, a forming tool.
  • the forming machine further comprises a hydraulic linear drive designed to drive the striking tool and coupled to the striking tool for the purpose of driving the striking tool.
  • a hydraulic linear drive is to be understood to mean drives which are in particular designed to convert hydraulic energy into kinetic energy of a linear movement.
  • the hydraulic linear drive can comprise a hydraulic cylinder driven by a hydraulic fluid and acting as a linear motor.
  • a differential cylinder is proposed as the hydraulic cylinder, which has, for example, a piston guided in a cylinder tube with a one-sided of which can have a extending piston rod on which the striking tool, in particular the bear, can be fixed.
  • the invention can also be applied to any hydraulic cylinder.
  • a first fluid space which is formed on a side of the piston of the hydraulic cylinder facing away from the piston rod or is formed in operating states, is usually referred to as a piston space, and in particular in the sense of the underlying invention.
  • a second fluid space formed between the piston and the cylinder tube in an operating state of the hydraulic cylinder, in particular a differential cylinder, through which the piston rod extends or through which the piston rod can extend is referred to as an annular space.
  • the hydraulic linear drive comprises a hydraulic circuit with a servomotor hydraulic pump, i.e. a hydraulic pump coupled to its operation with a motor-driven servo motor.
  • the servo motor hydraulic pump is set up in such a way that the pump speed or pump power can be controlled by the servo motor.
  • the servo-motoric hydraulic pump is configured as a unidirectional servo-motoric hydraulic pump using the directional valve assembly proposed here and is integrated in the hydraulic circuit.
  • the term unidirectional should in particular be understood to mean that, when the forming machine is in operation, hydraulic fluid always flows through the pump in the same direction of flow, or that the hydraulic pump uses the same in one or more successive working cycles of the hydraulic cylinder, in particular differential cylinder Pump direction or direction of rotation is operated.
  • the unidirectional flow direction or pump direction can in particular be defined by a flow direction from one, in particular central, hydraulic tank to the hydraulic cylinder, in particular Differential cylinder, in particular to the piston space or to the annular space of the differential cylinder.
  • a hydraulic pump which is unidirectional in terms of fluid technology makes it possible, in particular, to achieve advantageous control times for the volume flows provided to the hydraulic system or the volume flows required by the hydraulic system.
  • the hydraulic pump can in particular be a constant pump, i.e. a hydraulic pump with a constant displacement.
  • the servomotor hydraulic pump proposed here enables the volume flow and / or pressure of the hydraulic fluid in the hydraulic circuit to be adapted comparatively precisely and quickly to the respective requirements and adjusted accordingly.
  • the latter is of particular advantage for the comparatively high piston speeds and piston accelerations that occur with forging hammers.
  • the pump speed or hydraulic power of the hydraulic pump can be optimally adapted to the movement phases that follow one another during a forging cycle and can be adjusted according to the respective requirements, while maintaining comparatively short control times.
  • the movement profile of the piston for example the speed, in particular the final speed reached immediately before the bear or tool hits a workpiece, can be set or controlled comparatively precisely by controlling the hydraulic circuit in a correspondingly precise and timely manner. Ultimately, this has an advantageous effect on the achievable forging or forming result, and an energy-efficient operation can advantageously be achieved.
  • the hydraulic pump of the hydraulic linear drive can be designed for comparatively high volume flows of, for example, 100 l / min to 500 l / min or more.
  • a plurality can be connected in parallel in terms of fluid technology Hydraulic pumps are used.
  • a pressure range in which the hydraulic pumps work i.e. a hydraulic pump pressure, can be in the range between 190-220 bar.
  • the hydraulic linear drive comprises a hydraulically operating or hydraulically operated hydraulic cylinder, in particular differential cylinder, in particular a double-acting hydraulic cylinder with a piston rod extending on one side of the piston.
  • the hydraulic cylinder, in particular differential cylinder, or generally formulated the hydraulic linear motor is fluid-technically with a directional valve assembly, i.e. a module comprising at least one, in particular directly controlled or piloted, directional valve, connected, and arranged downstream of the hydraulic pump via the directional valve assembly.
  • a directional valve assembly i.e. a module comprising at least one, in particular directly controlled or piloted, directional valve, connected, and arranged downstream of the hydraulic pump via the directional valve assembly.
  • the directional control valve assembly should in particular mean that the first fluid space, e.g. the piston chamber of the differential cylinder can be supplied or acted upon with hydraulic fluid in one switching position of a (directional) valve or a (directional) valve group, can be separated from the differential cylinder in another switching position, and / or in another switching position with a second one Fluid space, e.g. the annulus of the differential cylinder, can be fluidly connected.
  • the directional valve assembly two e.g. can have exactly two switching positions, the hydraulic pump being connected to the first fluid space, in particular piston space, in a first switching position, and to the second fluid space, in particular annular space of the differential cylinder, in a second switching position. Further or more detailed explanations for the connection also result from the explanations described below.
  • the hydraulic circuit further comprises a servo-motoric hydrogen generator, ie a hydraulic motor coupled to a servo motor that works as a generator.
  • the hydrogenerator can, for example, be designed for volume flows in the range of 300 l / min. For higher volume flows, several hydrogen generators or hydraulic motors connected in parallel in terms of fluid technology can be used.
  • the servomotor-driven hydrogenerator is in particular designed and connected to the hydraulic circuit in such a way that when hydraulic fluid is acted on and the shaping machine is operating properly, it works as a generator, i.e. Generate electrical energy from hydraulic energy.
  • the hydraulic motor can generate mechanical work from hydraulic energy for driving the regenerative servomotor, that is to say servo generator, wherein the servo generator can convert the mechanical energy into electrical energy.
  • the servo-motoric hydrogenerator is configured as a unidirectional servo-motoric hydrogenerator using the directional valve assembly proposed here and is integrated in the hydraulic circuit.
  • unidirectional reference is made to the above statements.
  • the hydrogenerator this is to be understood to mean that, when the forming machine is in operation, hydraulic fluid always flows in the same direction of flow through which the hydraulic motor or that the hydraulic motor in one or more successive working cycles of the hydraulic cylinder, in particular differential cylinder, with the same direction of rotation or The direction of flow of the hydraulic fluid is operated.
  • the unidirectional flow direction or direction of rotation can in particular be defined by a flow direction from the hydraulic cylinder, in particular differential cylinder, in particular piston space or to the annular space, to a, for example central, hydraulic tank of the hydraulic system.
  • the hydrogenerator is connected downstream of the hydraulic cylinder, in particular differential cylinder, in terms of fluid technology via the directional valve assembly.
  • fluid-technical interconnections of the hydraulic pump, hydraulic cylinder, in particular differential cylinder, and hydrogen generator can thus be carried out can be achieved in which hydraulic pump, differential cylinder and hydrogen generator are connected in series essentially always or in one or more predetermined time periods during a working cycle of the hydraulic cylinder, in particular differential cylinder, which should mean that hydraulic fluid flowing into a fluid space of the hydraulic cylinder, in particular differential cylinder is always provided by the hydraulic pump, and hydraulic fluid flowing away from the hydraulic cylinder, in particular differential cylinder, is always discharged via the hydrogenerator.
  • the hydrogen generator can be operated as a hydraulic brake for the piston of the hydraulic cylinder, in particular a differential cylinder, by means of a corresponding torque control of the regenerative servomotor.
  • the hydrogenerator can be used as an active hydraulic brake for the piston
  • the hydrogenerator can also be used for energy recovery, in that superfluous elastic Energy is extracted from the hydraulic system by appropriate control of the hydrogenerator.
  • the forming machine further comprises at least one control unit designed and designed to control at least the hydraulic pump, the hydrogen generator and the directional control valve assembly, in particular at least in sections or overlapping at the same time.
  • the hydraulic pump, hydrogenerator and directional valve assembly can be connected in series over an entire working cycle of the differential cylinder or at least over a substantial part of the working cycle, so that a defined and comparatively accurate movement control of the hydraulic cylinder, in particular Differential cylinder, can be achieved by hydraulic coupling of the hydraulic cylinder, in particular differential cylinder, to the hydraulic pump. Simultaneously or parallel to this, in particular over the entire working cycle, elastic or hydraulic energy stored or generated in the hydraulic system or hydraulic circuit can be converted into electrical energy by corresponding control of the hydrogenerator.
  • control unit can be set up in such a way that the directional valve assembly is controlled at least temporarily during a working movement or a working cycle of the hydraulic cylinder, in particular differential cylinder, or the switching position of the directional valve assembly is set such that the hydraulic pump with the first fluid chamber of the hydraulic cylinder, in particular the piston chamber, and the hydrogenerator are fluidically connected to a second fluid chamber of the hydraulic cylinder, in particular the annular chamber of the differential cylinder.
  • piston chamber and annulus reference is made to the above explanations, which apply accordingly.
  • the control unit can also be set up so that at least temporarily during a return movement, i.e. a movement opposite to the working movement, of the hydraulic cylinder, in particular differential cylinder, the directional valve assembly is controlled such that the hydraulic pump is fluidically connected to the second fluid chamber of the hydraulic cylinder, in particular the annular chamber, and the hydrogen generator is connected to the first fluid chamber of the hydraulic cylinder, in particular the piston chamber of the differential cylinder.
  • control unit can be set up in such a way that it controls the directional valve assembly in such a way that the hydraulic pump is connected or alternately connected to the first fluid space, in particular the piston space, and the second fluid space, in particular the annular space, in sequentially successive, in particular immediately successive, sections of a working cycle of the differential cylinder is.
  • the hydrogenerator can alternately be connected alternately to a second fluid space, in particular an annular space, and a first fluid space, in particular a piston space.
  • the hydraulic cylinder in particular differential cylinder, and in particular the striking tool, with continuous motion control between the reversal points of the hydraulic cylinder, in particular differential cylinder, and in particular also in the area of the reversal points, combined with energy recovery the hydraulic generator are operated.
  • the directional valve assembly can comprise a 4/2 way valve.
  • the directional control valve assembly can in particular comprise four individual hydraulic valves that are fluidly connected to one another in a bridge circuit.
  • a bridge circuit can be understood in particular as a ring circuit of, for example, four hydraulic valves with intermediate connection points.
  • such a bridge connection can be implemented by connecting two hydraulic valves connected in series.
  • the hydraulic circuit can comprise at least one suction valve, which is fluid-technically connected to a suction source, for example a hydraulic fluid reservoir or reservoir; or tank, on the one hand and with at least one fluid space, in particular the piston space and / or annular space, of the differential cylinder on the other hand.
  • a suction source for example a hydraulic fluid reservoir or reservoir; or tank, on the one hand and with at least one fluid space, in particular the piston space and / or annular space, of the differential cylinder on the other hand.
  • the fluidic connection of the suction valve can in particular be designed in such a way that a negative pressure which arises in the at least one fluid space during operation of the hydraulic cylinder, in particular a differential cylinder, can be compensated for by sucking in hydraulic fluid via the suction valve.
  • a negative pressure which arises in the at least one fluid space during operation of the hydraulic cylinder, in particular a differential cylinder, can be compensated for by sucking in hydraulic fluid via the suction valve.
  • Corresponding negative pressures can occur in a forging hammer, for example in the annular space when the impact tool rebounds, and / or when in an operating state the volume increase in the piston space is greater than the volume provided by the hydraulic pump of hydraulic fluid.
  • the latter can occur, for example, if the volume flow generated by the hydraulic pump remains or is smaller than or becomes the change in volume of the piston space caused by enlarging the piston space, which is the case, for example, after initially accelerating the piston towards the workpiece in order to regulate the required speed of the percussion tool Case may be.
  • the replenishment valve can be, for example, a hydraulic valve designed in the manner of a check valve, in particular a valve that automatically closes on one side.
  • the suction valve can, for example, be designed for volume flows in the range between 150 l / min to 10,000 l / min.
  • the respective design of the replenishment valve depends, among other things, on the respective stroke volume and the piston speeds that occur.
  • control unit can be set up to control the pump speed of the hydraulic pump such that the hydraulic pump is always operated at least at a non-zero minimum speed during operation, in particular during one or more successive working cycles.
  • control unit can be designed and set up in such a way that it controls the hydraulic pump or can control such that during operation, in particular a working section of one or more working cycles, the hydraulic cylinder, in particular the differential cylinder, has at least one different from zero Minimum speed is operated.
  • control unit can be set up in such a way that the hydraulic pump is always operated at least at the minimum speed during one or more immediately successive working cycles.
  • the minimum speed represents the lower limit for the speed of the hydraulic pump.
  • the hydraulic pump is therefore not stopped completely during appropriate operation, but is operated continuously, which can bring advantages in terms of energy efficiency and accuracy of setting the speed, in particular the final speed, of the forging tool.
  • control unit can be set up in such a way that the hydraulic pump is first activated or is activated at the minimum speed, and then the pump speed is initially increased from the minimum speed to a maximum speed in a working area of a working cycle of the hydraulic cylinder, in particular differential cylinder.
  • the pump speed can be reduced from the maximum speed to the minimum speed, in particular in such a way that the minimum speed is reached or is present at a reversal point of the hydraulic cylinder, in particular a differential cylinder.
  • the reversal point is preferably the reversal point of the piston of the hydraulic cylinder, in particular the differential cylinder, facing the area of action of the striking tool.
  • the increase in the pump speed of the hydraulic pump or the reduction in the pump speed of the hydraulic pump can take place in accordance with a linear function of time.
  • the control unit can be configured in such a way that the maximum speed is or is reached before reaching or at the time the impact tool strikes a workpiece positioned in the work area.
  • the pump speed of the hydraulic pump is reduced when the maximum speed is reached, so that under the action of the hydraulic forces prevailing in the hydraulic circuit and, if applicable, the force of gravity acting on the striking tool, the or a predetermined final speed has been reached in or shortly or immediately before the reversal point, or forming point, or in or short or immediately before the reversing point of the forming point.
  • the hydrogenerator can also be operated as a hydraulic brake in order to actively brake the piston.
  • the sequence of movements, in particular the final speed, of the hydraulic cylinder, in particular differential cylinder, and thus of the striking tool can be varied and adjusted comparatively flexibly within the limits given by the overall structure of the forming machine .
  • a suitable control of the pump speed of the hydraulic pump optionally with the additional use of suitable sensors for measuring the position and / or speed of the hydraulic cylinder, in particular differential cylinder, or the striking tool, and / or sensors for measuring one or more pressures prevailing in the hydraulic system comparatively accurate and reliable adjustment of the impact speed or final speed of the striking tool can be achieved.
  • the forming machine for example interacting with the control unit, can have sensors which are designed to determine the position of the hydraulic cylinder, in particular differential cylinder, and / or the impact tool.
  • sensors for measuring the pressure in the hydraulic circuit for example in a line opening into the first fluid space, in particular piston space, and or in a line opening into the second fluid space, especially annular space.
  • the sensors can be coupled to the control unit, so that values for pressures and / or position of the striking tool or hydraulic cylinder, in particular differential cylinder, transmitted from the sensors to the control unit for controlling the hydraulic pump and / or of the hydrogenerator can be used.
  • the pressures and / or positions are preferably processed by the control unit and used to control the hydraulic pump and / or the hydrogenerator in such a way that the striking tool has the required final speed in or shortly or immediately before the point of impact.
  • the hydraulic pump is operated at the minimum speed, i.e. that the pump speed of the hydraulic pump is set to the minimum speed in this movement section.
  • the operation at the minimum speed can be used to accelerate the bear and, in the case of an upper pressure forming machine, to drive the bear upwards.
  • control unit is connected to sensors for measuring the speed of the hydraulic cylinder, in particular differential cylinder, or percussion tool, that is to say that the peripheral machine can comprise corresponding speed sensors, and determined speed data from the control unit for control or regulation the hydraulic pump and / or the hydrogenerator can be used to regulate the final speed to a predetermined value.
  • a starting point for starting a forming or forging process in particular a starting point from which the piston or bear is accelerated in the direction of the forming area, depending on the respectively desired, required or predetermined final speed, corresponding to the respectively desired one , required or predetermined energy, in particular forming energy, depending on the height of the workpiece to be formed measured in the direction of movement of the piston, and / or depending on the respective forming path, for example for upsetting or reshaping the workpiece parallel to the direction of movement of the piston.
  • the starting point from which the acceleration of the bear takes place can be, in particular, a reversal point facing away from the forming area, in the case of an upper pressure forming machine, for example, an upper dead center of the piston or bear.
  • a variable setting of the starting point or output stroke from which the piston or striking tool, bear or die is accelerated, as described in particular in advance and possible in configurations, enables in particular an optimal setting of the movement sequence of the piston or bear, etc. It is also possible to variably adjust the stroke, for example the top dead center of the piston, so that, for example, improved forming or forging cycles, or forming or forging frequencies can be achieved.
  • control unit in such a way that the path or corresponding strokes covered by the striking tool during a forging cycle are / are minimal.
  • control unit can be designed and set up in such a way that different strokes, for example a minimally necessary stroke to achieve a desired or predetermined final speed or forming energy that follows in the forming operation, differ by targeted starting Reversal points, for example top dead centers of the piston, can be realized.
  • variable strokes of the piston it is possible to optimize forming times, and the movement sequence depending on the desired final speed, forming energy, depending on the height of the workpiece to be formed in the direction of movement of the piston, and / or depending on the respective forming path, e.g. for upsetting or forming the workpiece parallel to the direction of movement.
  • control unit can be set up and configured to use a starting point, in particular top dead center, of a preceding forming cycle, e.g. a starting point of the piston or bear or die at the beginning of a preceding forming cycle, in particular immediately preceding forming cycle, to determine a further starting point, in particular top dead center, of a subsequent, preferably immediately following, forming cycle.
  • a starting point in particular top dead center
  • control unit can be designed to use e.g. the piston, bear or die of a first forming process, second control data for movement control e.g. the piston, bear or die of a second forming process.
  • the second forming process can follow the first forming process directly in time. Optimized forming times can advantageously be achieved through such control of the forming processes, in particular successive forming processes.
  • the second control data can be determined from the first control data on the basis of the first control data and the boundary conditions specified for the subsequent temporal forming process.
  • an impact energy for example forming energy
  • the starting position of the piston is calculated on the basis of a subsequently required impact energy from the control unit or control, in particular is determined automatically.
  • the starting position can be set depending on the respective height of the workpiece to be formed.
  • the position, in particular the starting position, of the piston, or bear, or die is determined at the beginning or at a defined point in time during a forming or forging cycle and / or is used as a calculation basis for determining a starting position of the piston , Bears or dies and / or operating parameters for controlling the movement of pistons, bears and / or dies during or for a subsequent subsequent forming or forging process.
  • control unit can be set up and designed such that it controls or can control the hydraulic pump in such a way that a maximum feed speed of the hydraulic cylinder, in particular differential cylinder, or of the striking tool is in the range between 1.5 m / s to 6 m / s, in particular at about 1.5 m / s or 5 m / s, or between 4.8 m / s and 5.5 m / s, and that preferably a maximum return speed of the hydraulic cylinder, in particular differential cylinder, in the range between 1.5 m / s and 2 , 5m / s, preferably 2m / s, in particular between 1.8 m / s and 2.1m / s.
  • the volume flow during braking in one or the other direction of movement of the piston ie during the forward or backward movement of the piston, in the case of an overpressure forming machine when the piston moves up and down
  • the volume flow can vary depending on the piston diameter, rod diameter, piston speed and others, or can be set depending on these sizes.
  • the recovery of energy can take place in particular under roughly the same conditions of the reciprocating movement be optimized by means of the hydrogenerator, and overall an energy-saving operation can be achieved.
  • the forming machine can further comprise an energy store, which is connected to the hydrogenerator for the purpose of feeding in electrical energy generated by the hydrogenerator.
  • an energy store which is connected to the hydrogenerator for the purpose of feeding in electrical energy generated by the hydrogenerator.
  • the electrical energy generated by the hydrogenerator, or the electrical energy generated by the hydraulic energy of the hydraulic circuit by the hydrogenerator can be temporarily stored, and can be made available again as electrical energy in a subsequent work cycle or working section of the converter rail, for example for Operation of the hydraulic pump.
  • the electrical energy generated by the hydrogenerator can be fed into a power network or power-heat network connected to the forming machine.
  • a method for controlling a work cycle of a forming machine is provided.
  • the forming machine is a forging hammer.
  • a hydraulic cylinder in particular differential cylinder, coupled to an impact tool, is fluidly coupled via a hydraulic valve and a directional valve assembly connected upstream of the hydraulic cylinder.
  • Servomotor hydraulic pump of a hydraulic linear drive is driven by the supply of hydraulic fluid.
  • the hydraulic cylinder can be driven by acting on a fluid space, in particular the piston space or annular space of the differential cylinder.
  • hydraulic fluid e.g. the hydraulic fluid flowing from the second fluid space, in particular the annular space, or the first fluid space, in particular the piston space
  • hydraulic fluid is directed via the directional valve assembly to a servo motor-driven hydrogenerator that is fluid-connected downstream of the directional control valve assembly.
  • this should mean that the hydraulic pump is fluidly coupled to a fluid space, and, at least in one section of the working cycle, in particular at the same time, the hydrogen generator is coupled to the further fluid space.
  • the hydraulic cylinder in particular differential cylinder, can be controlled comparatively precisely and reliably, as a result of which, in particular, improved forging results can be obtained.
  • the directional valve assembly is controlled in such a way that the hydraulic pump with the first fluid chamber, in particular the piston chamber, and the hydrogen generator with the second fluid chamber , in particular the annular space of the differential cylinder, are fluidically connected.
  • the directional valve assembly is or is controlled such that the hydraulic pump with the second fluid space, in particular annulus, and the hydrogenerator with the first annulus, in particular Piston chamber, the differential cylinder are fluidly connected.
  • the hydraulic pump is controlled by the control unit such that the hydraulic pump is in operation is operated above or at least with a non-zero minimum speed.
  • the pump speed in a working section of a working cycle of the hydraulic cylinder, in particular differential cylinder can first be increased from the minimum speed to a maximum speed and then reduced from the maximum speed to the minimum speed, for example in such a way that in the working area of the impact tool, the reversal point of the hydraulic cylinder in particular differential cylinder or piston the minimum speed is reached or is present.
  • the pump speed can be controlled, for example, according to a predefined function of the time and / or the position of the hydraulic cylinder, in particular a differential cylinder, for example in accordance with a linear relationship with time.
  • control using at least partially non-linear relationships is also possible with the hydraulic system proposed here.
  • the pump speed can be set or regulated to the minimum speed during a return section of the working cycle of the hydraulic cylinder, in particular differential cylinder.
  • the pump speed of the Hydraulic pump from the minimum speed, in particular in a linear dependence on the time, to the maximum speed, in such a way that the maximum speed is or is reached before reaching a first reversal point of the hydraulic cylinder, in particular differential cylinder, assigned to the forming area.
  • control takes place in such a way that the pump speed of the hydraulic pump, i.e. the speed of the hydraulic pump of the hydraulic pump is reduced in such a way after reaching the maximum speed, in particular in a linear relationship with the time, that the minimum speed is reached or is set when the first reversal point is reached or is reached.
  • the directional valve assembly is controlled such that a pressure output of the hydraulic pump with the second fluid chamber of the hydraulic cylinder, in particular Annulus of the hydraulic cylinder, in particular differential cylinder, is or is fluidly connected, and that a pressure input of the hydrogenerator is or is fluidly connected to the first fluid chamber of the hydraulic cylinder, in particular piston chamber of the differential cylinder.
  • an elastic energy stored, generated and / or generated in the hydraulic system of the forming machine in particular potential energy stored in the hydraulic fluid, can be converted into electrical energy or another secondary energy form via the hydrogenerator, for example by decompression of the hydraulic fluid or the hydraulic system , and are fed to the metal forming machine, for example, in subsequent working cycles.
  • the hydrogenerator for example by decompression of the hydraulic fluid or the hydraulic system
  • the metal forming machine for example, in subsequent working cycles.
  • a negative pressure generated in the second fluid space, in particular the annular space, by rebound of the hydraulic cylinder, in particular differential cylinder, or percussion tool in the first reversal point is compensated for by at least one suction valve, which on the one hand is fluidly connected to the second fluid space and on the other hand a hydraulic tank.
  • an overpressure generated by the rebound in the first fluid chamber, in particular piston chamber, or an elastic energy generated in the hydraulic circuit is converted by decompression via or by the hydrogenerator into a secondary form of energy, for example electrical energy, and preferably in one Cache is saved.
  • the directional valve assembly is controlled in such a way that, when or when, or immediately before, a second reversal point of the hydraulic cylinder, in particular the differential cylinder, facing away from the forming area of the forming machine, is actuated such that a pressure output of the hydraulic pump with the first fluid chamber, in particular Piston space, is or is fluidly connected, and a pressure input of the hydrogenerator is or is fluidly connected to the second fluid space, in particular the annular space of the differential cylinder.
  • suction valves can be provided such that any pressure fluctuations in the hydraulic system can be compensated for, in particular to avoid pressure peaks.
  • the movement control of the piston, bear and / or die by the control unit in or in the region of the two reversal points of the piston, apart from the rebound occurring only in the deforming reversal point, is carried out approximately or essentially in the same way becomes.
  • FIG. 1 shows a schematic representation of the structure of an upper pressure forging hammer 1 designed according to an embodiment of the invention.
  • the forging hammer 1 comprises a frame (not shown) on which a differential cylinder 2 is fixed.
  • a lower die 3 is also fastened to the frame with a lower tool 4 detachably attached thereto.
  • a bear 8 i.e. Blacksmith bear, upper die attached, which can be moved back and forth along with the piston 6 in the longitudinal direction of the cylinder tube 5.
  • the degree of freedom of movement of the piston 6 or bear 8 is in FIG. 1 represented schematically by means of a double arrow.
  • the forging hammer 1 is designed as a vertical forging hammer, which is to mean that, in the correct operating state, the bear 8 or an upper tool 9 detachably fastened to it moves in the vertical direction from top to bottom and vice versa.
  • the forging hammer 1 is shown in a working state in which the upper tool 9 rests on the lower tool 4, corresponding to a first turning point U1 of the bear 8 or upper tool 9.
  • the forging hammer 1 has a hydraulic circuit comprising the differential cylinder 2, with one, or, as required, a plurality of servo-motoric hydraulic pumps 27, which comprises a hydraulic pump 11 controlled by a servo motor 10, the pressure side 12 of which with a 4/2 way valve 13 and the suction side 14 thereof are fluidly connected to a hydraulic tank 15.
  • the hydraulic circuit further comprises a hydrogen generator 16, the input side 17 of which is connected to the directional control valve 13, and the output side 18 of which is fluidly connected to the hydraulic tank 15.
  • the forming machine 1 further comprises a control unit 19, which is designed and is provided with corresponding control lines, so that the components of the forging hammer 1, in particular the directional control valve 13, hydraulic pump 27, and hydrogen generator 16, and, if appropriate, further components can be controlled.
  • a control unit 19 which is designed and is provided with corresponding control lines, so that the components of the forging hammer 1, in particular the directional control valve 13, hydraulic pump 27, and hydrogen generator 16, and, if appropriate, further components can be controlled.
  • the control unit 19 can be configured with various sensors for detecting operating parameters of the forging hammer 1.
  • the forging hammer 1 can have one or more pressure sensors 20 with which, for example, a pressure prevailing in a piston chamber 21 of the differential cylinder 2 and / or in an annular space 22 of the differential cylinder 2 during operation of the forging hammer 1 can be detected, which pressure can be detected, for example, by the control unit 19 can be used to control the forging hammer 1, in particular the differential cylinder 2 and / or the hydraulic pump 27 and / or the hydrogenerator 16.
  • the hydrogenerator 16 comprises one, or, if necessary, several, hydraulic motors 28 and a servo generator 29 coupled mechanically to the hydraulic motor 28, i.e. a servomotor operated as a generator.
  • the hydraulic pump 27 and the hydrogen generator 16 can be controlled using the servo motor 10 and the servo generator 29, and for this purpose are connected to the control unit 19 via corresponding control lines.
  • the hydraulic pump 27 and the hydrogenerator can be controlled in terms of speed and / or torque, for example in such a way that one for setting and / or reaching a predetermined or desired final speed of the bear 9 is achieved by.
  • the hydraulic pump 27 and the hydrogenerator 16 can be controlled such that the bear 9 or piston 6 follows a predetermined movement sequence, the hydraulic pump 27 and hydrogenerator 16 providing the hydraulic drive power or braking power required in each case.
  • the forging hammer 1 can further comprise a position and / or speed sensor 23, with which the control unit 19 can determine a position and / or speed of the bear 8 or the piston 6, with corresponding position and / or speed data for control purposes of the hydraulic circuit, in particular the hydraulic pump 27 and / or the hydrogenerator 16 and / or the directional control valve 13, can be used, for example for controlling or setting a desired final speed or impact speed of the differential cylinder 2.
  • the forging hammer 1 shown in connection with the figures further comprises an energy store 24 in which secondary energy generated by the hydraulic generator 16, for example by converting hydraulic energy, in particular elastic energy, from the hydraulic circuit, for example in the form of electrical energy, can be stored.
  • the energy store 24 can be connected to the control unit 19.
  • the energy store 24 and the associated one Control can be coordinated so that energy recovered from one or more preceding work cycles of the forging hammer 1 for operating the forging hammer 1, for example the hydraulic pump 27, is used or called up in subsequent work cycles.
  • the piston chamber 21 and the annular chamber 22 of the differential cylinder 2 are fluidically connected to the hydraulic tank 15 via suction valves 25 in order to compensate for any negative pressures that occur in the hydraulic system such that hydraulic fluid 30 is sucked in via the suction valves 25 from the hydraulic tank 15 in the event of a negative pressure and thus into the hydraulic system can be introduced.
  • the piston chamber 21 and the annular chamber 22 can each be fluidically connected to the hydraulic tank 15 or a hydraulic fluid source via a suction valve 25, so that in the event of a negative pressure hydraulic fluid is sucked into the piston chamber 21 or the annular chamber 22 by a suction effect caused by the negative pressure.
  • the suction valves 25 can, for example, be spring-loaded check valves or other similar valves which allow only unidirectional flow of hydraulic fluid in the direction from the hydraulic tank 15 to the piston chamber 21 or the annular chamber 22, but block in the opposite direction.
  • FIG. 2 to FIG. 5 show the forging hammer 1 in different operating states.
  • FIG. 2nd shows the forging hammer 1 in an operating state in which the hydraulic pump 27 and the directional control valve 13 are controlled by the control unit 19 such that the piston 6 of the differential cylinder 2 in the direction of the lower tool 4 is accelerated or moved for the purpose of machining a workpiece 26.
  • the directional valve 13 is designed in the present embodiment as a 4/2 way valve, and in the in FIG. 1 shown operating state switched so that a first connection A1, which is fluidly connected to the pressure side 12 of the hydraulic pump 11, is connected to a second connection A2, which is fluidly connected to the piston chamber 21.
  • hydraulic fluid 30 can be pumped from the hydraulic tank 15 into the piston chamber 21 by appropriate control of the servo motor 10 by the hydraulic pump 11, so as to increase the stroke of the piston 6 and to transmit a hydraulic acceleration force to the piston 6.
  • FIG. 1 shown operating state, in which the piston 6 is accelerated or moved in the direction of the lower tool 4, a third port A3 of the directional control valve 13 fluidly connected to the annular space 22, and switched through to a fourth port A4 of the directional control valve 13, which is fluidically connected to the hydrogenerator 16, more precisely connected to the input side 17 of the hydraulic motor 28.
  • the forging hammer 1 in the present example is designed as an upper pressure forging hammer 1 with an upper differential cylinder 2
  • the weight forces of the moving mass also contribute to the acceleration of the bear 8 in the direction of the lower tool 4 in addition to the hydraulic forces generated by the hydraulic pump 27 and the hydrogenerator 16 , in particular from bear 8, piston rod 7, piston 6, upper tool 9, etc., at.
  • the weight forces when the bear accelerates in the direction of the workpiece to be machined counteract the hydraulic force, which can also be recorded in terms of control technology by the hydraulic system proposed here.
  • a forging hammer can be used Both the upper pressure and the lower pressure forging hammer can be controlled with the method proposed here and have a corresponding structure.
  • control unit 19 can evaluate one or more position and / or speed sensors 23 and on the basis of the data obtained thereby, for example on the basis of the determined actual speed of the bear 8, or in accordance with the upper tool 9 or of the piston 6, control the hydraulic pump 28 and / or the hydrogenerator 16 such that the desired final speed is reached.
  • hydraulic fluid 30 flows into the piston space 21.
  • hydraulic fluid 30 located in the annular space 22 is displaced from the annular space 22, which is returned to the hydraulic tank 15 via the directional control valve 13 and the hydrogenerator 16.
  • elastic energy stored in the hydraulic system can, for example, be withdrawn from the hydraulic system and converted into electrical energy.
  • the electrical energy can in turn be temporarily stored in the energy store and the forging hammer 1 in subsequent work cycles, or also be provided immediately.
  • Elastic energy stored in the hydraulic system can be released, for example, by decompression of the hydraulic fluid 30.
  • hydraulic energy is withdrawn from the hydraulic circuit by, for example, increasing the torque of the servo generator 29 so that kinetic energy of the hydraulic fluid flowing through the hydraulic motor 28 is converted into electrical energy.
  • the latter leads to a braking effect overall, so that the moving mass, in particular piston 6, bear 8, etc., can be braked in a targeted manner.
  • the hydrogenerator 16 in the hydraulic system proposed here can be operated as a hydrofluidic brake to generate a braking effect for the moving mass, in particular the bear 8.
  • the hydrofluidic braking effect can be used for the purpose of setting a respectively required final speed when moving in the direction of the first turning point U1 and / or for braking the moving mass when moving in the direction of the second turning point U2, e.g. be used in the region of the upper second turning point with appropriate control of the hydrogenerator 16.
  • the hydraulic pump 27 and the hydrogenerator 16 can be operated essentially simultaneously at any time during the entire working cycle, the hydraulic pump 27 making it possible to generate a (positive) acceleration force and the hydrogenerator 16 making it possible to generate an opposite braking force.
  • this enables a comparatively exact and precise control of the movement sequence, for example of the bear 9, essentially, ie for example apart from periods in which the directional valve 13 is reversed, to be achieved during the entire working cycle of the forging hammer 1.
  • Negative pressures in the part of the hydraulic system on the piston chamber side can occur, for example, if, during the acceleration of the bear 8, the volume flow of hydraulic fluid 30 generated by the hydraulic pump 27 remains behind the volume change caused by enlarging the piston chamber 21. The latter can occur, for example, if the change in volume of the piston chamber 21 caused by the accelerating effect of gravity is greater than the volume flow of hydraulic fluid 30 provided by the hydraulic pump 27.
  • the volume flow of the hydraulic pump can be reduced so that the piston reaches the respectively predetermined final speed.
  • the time required to move the bear 8 from a second reversal point U2 of the piston 6 or the bear 8 to the first reversal point U1, which is distant from the lower tool 4 can be approximately 200 ms (milliseconds).
  • FIG. 3rd shows the forging hammer 1 in an operating state in which the bear 8 is in the first reversal point U1, ie in the present case the lower reversal point.
  • Impact and rebound can take place, for example, in a time range from 0.5 ms to 20 ms.
  • the directional control valve 13 is controlled accordingly by the control unit 19, in particular in such a way that the third connection A3 is fluidly connected to the first connection A1, and that the second Port A2 is connected to the fourth port A4 of the directional valve 13.
  • the piston chamber 21 is fluidly connected to the hydrogen generator 16, and the annular chamber 22 is fluidly connected to the pressure side 12 of the hydraulic pump 11.
  • a corresponding reversal of the directional control valve 23 can also take place before the first reversal point U1, for example at the time when the bear 9 has the desired final speed.
  • the directional control valve 23 can be switched over at a point in time at which the respectively desired final speed is reached, and any braking or braking operation of the piston 6 or bear 8 that may be required has been completed.
  • the braking process can take place, for example, in the end region of the movement of the bear 8 in the direction of the forming region or in the direction of the workpiece 26.
  • the end of the braking process can be before the point of impact of the bear 8 in the work area.
  • the directional control valve 23 can be switched over in time, in particular shortly before the point of impact, in particular in such a way that the required switching position of the directional control valve 23 is at least at the point of impact.
  • control of the directional control valve 23 can take place in such a way that control processes, in particular taking into account any system inertia or switching times, are initiated with a time delay such that the switching position of the directional control valve 23 required for a certain point in time is reliably reached at the respective point in time.
  • hydraulic fluid 30 displaced from the piston chamber 21 can be discharged via the hydrogenerator 16 into the hydraulic tank 15 by the displacement effect.
  • the one with the rebound in Hydraulic system generated and released by decompression of the hydraulic system elastic energy from the hydrogen generator 16 are converted into electrical energy, wherein the hydrogen generator 16 is controlled accordingly via the servo generator 29 so that it can be driven by the hydraulic motor 28 at least partially convert the elastic energy into electrical energy.
  • the electrical energy can be stored in the energy store 24 electrically connected to the servo generator 29 and e.g. for subsequent work cycles for electrically driving the hydraulic pump 27 and others be used.
  • hydraulic fluid 30 can be supplied to the annular space 22 through the fluidic connection of the hydraulic pump 27 and the annular space 22 in order to at least partially provide the hydraulic fluid required in the annular space 22 due to the movement of the piston in the direction of the second reversal point U2 or the annular space 22 in accordance with the movement of the To supply piston 6 at least partially with hydraulic fluid 30.
  • the suction valve or valves 25 can, as already mentioned, be designed as check valves and offer the possibility of vacuum peaks in the hydraulic system, without this requiring a full control of the hydraulic system by the control unit 19.
  • the hydraulic pump 27 is operated by the control unit 19, for example, at a minimum speed or minimum delivery rate which is required around the piston 6 after decay of the rebound to move to the second reversal point U2 at the desired speed. In this way, the control effort in particular can be reduced.
  • the movement of the piston 6 from the first U1 to the second reversal point U2 can e.g. in about 500 ms.
  • control unit 19 can control the hydraulic circuit, in particular the directional control valve 13 and the hydraulic pump 27 and the hydrogenerator 16, in such a way that the piston 6 together with the moving mass connected to it is braked.
  • the braking process can be performed in exemplary working cycles e.g. in a time span of approx. 100 ms.
  • control unit 19 can control the hydrogenerator 16 in such a way that hydraulic energy is withdrawn from the hydraulic fluid flowing back from the piston chamber 21 by the hydrogenerator 16, so that the hydrogenerator 16 acts as a hydrofluidic brake works.
  • the hydraulic pump 27 can be controlled in such a way that its delivery quantity is or is reduced, for example in such a way that the hydraulic pump 27 is operated at the minimum speed.
  • the hydraulic system is in any case controlled so that the bear 8 is completely braked in the second turning point U2, possibly using sensor-based position and / or speed data of the bear 8.
  • the completeness is noted that in the first turning point U1 the moving mass is braked as such by the forging process, but in the first turning point U1 effects such as rebound must be absorbed or managed by suitable control of the hydraulic system.
  • control unit 19 can control the hydraulic system in accordance with the previously described flowchart to carry out a further work cycle.
  • the control unit 19 can control the directional control valve 13 in such a way that the hydraulic pump 27, as in FIG. 2nd shown, is fluidly connected again to the piston chamber 21 and the hydrogenerator 16 is fluidly connected again to the annular space 22.
  • the hydraulic pump 27 and the hydrogen generator 16 can be controlled accordingly when the moving mass is accelerated and, if necessary, when the moving mass is decelerated to set the given impact speed.
  • FIG. 5 shows a working diagram relating to operating and control variables of the forging hammer 1, a total of five curves being shown, a first speed curve D1 describing the time dependence or the time course of the speed of the hydraulic pump 11.
  • a second speed curve D2 describes the time dependency or the time course of the speed of the hydrogenerator 16.
  • a first torque curve M1 describes the time dependence or the time profile of the torque of the hydraulic pump 11, and a second torque curve M2 shows the time dependency or the time profile of the torque of the hydrogenerator 16.
  • a movement curve B describes the time dependence or the time profile of the stroke of the piston 6 or bear 8. According to the movement curve B, the piston moves from the second reversal point U2 to the first reversal point U1, and then back to the first reversal point U1.
  • the bear 8 or piston 6 is accelerated from the second reversal point U2 in the direction of the first reversal point U1, the directional control valve 13 being controlled in such a way that the hydraulic pump 27 is fluidly connected to the piston chamber 21.
  • the hydrogenerator 16 is fluidically connected to the annular space 22.
  • the pump torque of the hydraulic pump 27 and thus the power which can be transmitted to the hydraulic system is increased in accordance with a comparatively steep flank, in the curve shown here as an example FIG. 5 down to about 1100Nm.
  • the torque required to accelerate the bear 9 decreases, not least because the gravity of the moving mass also contributes to the acceleration.
  • the bear 8 and the moving mass is accelerated to a first point in time t1, which is before a second point in time t2, in which the bear 8 reaches the first reversal point U1.
  • the respective final speed can optionally be set.
  • the directional control valve 13 can be reversed so that the hydraulic pump 27 is connected to the annular space 22 and the hydrogenerator 16 to the piston space 21.
  • the torque of the hydrogenerator 16 is increased in the period between t1 and t2, which means in particular that energy is withdrawn from the hydraulic fluid flowing into the piston chamber, which ultimately brakes the volume flow to the piston chamber 21, as a result of which the bear 9 has a braking effect can be generated.
  • the hydrogenerator 16 acts as a hydrofluidic brake in this period, in order to counteract any further acceleration of the bear 8 after the end speed has been reached.
  • the speed of the hydrogenerator 16 is approximately constant between t1 and t2 at the point in time mentioned (see curve D2). Before time t1, in the example the FIG. 5 in the time interval between t0 and t1, the speed of the hydrogen generator 16 can be set to the speed required for generator operation, in particular increased.
  • the torque of the hydrogenerator 16 increases until the second time t2, which e.g. can mean that the hydrogenerator 16 actually draws hydraulic energy from the hydraulic system.
  • curves of torque and speed of the hydraulic motor 28 and hydrogen generator 16 shown by way of example should be noted that the actual course of the curves may vary depending on the respective hydraulic system.
  • the course of the speed and / or torque can be offset in time from the times t0 to t4, which can be caused, for example, by different mass inertias and / or fluid inertias of the hydraulic fluid and / or components of the hydraulic system.
  • the increase in the speed of the hydrogen generator 16 before the time t1 to the speed required or suitable for generator operation can also be done otherwise than by the method shown in FIG FIG. 5 shown course can be achieved.
  • the speed and torque of the hydraulic motor and / or the hydrogenerator can vary depending on the respective forging hammer Design and dimensioning of the hydraulic system in particular FIG. 5 shown course deviate.
  • the hydraulic pump 27 is controlled in such a way that the speed drops to the minimum speed Dmin, the torque increasing when the final speed is reached.
  • the speed and torque of the hydraulic pump 27 are set such that, from the second point in time t2, the piston can be moved from the first reversal point U1 towards the second reversal point U2 at a predetermined return speed, for example 2 m / s.
  • the hydraulic pump 27 is corresponding to the in FIG. 5 shown example run according to the previously set minimum speed Mmin and the corresponding torque, and bear 8 or piston 6 are moved from the first reversal point U1 to the second reversal point U2. So that the hydrogenerator 16 does not act as a hydraulic brake for the return movement and acts as a brake on the hydraulic pump 27, the torque of the hydrogenerator 16 is reduced to zero after the second period.
  • the speed of the hydrogenerator 16, ie the hydraulic motor 28, results in this period in particular from the volume flow of the hydraulic fluid 30 displaced from the piston chamber 21.
  • the return movement of the piston 6 is slowed down from a third point in time t3 in such a way that the piston 6 together with the associated moving mass is braked in the second reversal point U2 and the working cycle can be repeated.
  • the torque of the hydrogenerator 16 is increased so that it acts as a hydraulic brake for braking the mass moving in the direction of the second reversal point U2.
  • the torque of the hydraulic pump 27 is reduced, which also leads to a slowdown the return movement leads.
  • the fourth point in time can be followed by a further working cycle which is carried out in accordance with the previously described working cycle, wherein after reversing the directional control valve 13, the hydraulic pump 27 is again connected to the piston chamber 21 and the hydrogenerator 16 is connected to the annular chamber 22 again.
  • Relief and simplification of the control of the arrangement proposed here consisting of hydraulic pump, hydrogenerator and directional valve can be achieved, for example, by the suction valves 25, which automatically, so to speak, any negative pressure conditions and pressure peaks, for example hydraulic impacts on the piston, hydraulic pump, hydrogenerator and / or directional valve assembly, in the hydraulic System can compensate.
  • the latter is not only beneficial on the control effort, but at the same time a comparatively low-wear operation can also be achieved.

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Claims (17)

  1. Marteau pilon (1) pour l'usinage par formage de pièces (26), comprenant un outil de percussion (8, 9) et un entraînement linéaire hydraulique (2, 13, 16, 19, 27) couplé à l'outil de percussion (8, 9) et réalisé de manière à entraîner l'outil de percussion (8, 9), pourvu d'un circuit hydraulique comprenant une pompe hydraulique (27) à servomoteur, un vérin hydraulique (2) monté fluidiquement en aval de la pompe hydraulique (27) au moyen d'un module distributeur (13), notamment un vérin différentiel (2), et un hydrogénérateur (16) à servomoteur, monté fluidiquement en aval du vérin hydraulique (2) au moyen du module distributeur (13), et comprenant par ailleurs une unité de commande (19) conçue au moins pour la commande (19) de la pompe hydraulique (27), de l'hydrogénérateur (16) et du module distributeur (13), dans lequel la pompe hydraulique (27) est conçue comme une pompe hydraulique (27) à servomoteur unidirectionnelle utilisant le module distributeur (13) et est intégrée dans le circuit hydraulique, et dans lequel l'hydrogénérateur (16) à servomoteur est conçu comme un hydrogénérateur (16) à servomoteur unidirectionnel utilisant le module distributeur (13) et est intégré dans le circuit hydraulique.
  2. Marteau pilon (1) selon la revendication 1, dans lequel l'unité de commande (19) est conçue de telle manière qu'au moins temporairement, pendant un mouvement de travail du vérin hydraulique (2), le module distributeur (13) est commandé de telle manière que la pompe hydraulique (27) est reliée fluidiquement à une première chambre de fluide (21), en particulier à la chambre de piston (21), et que l'hydrogénérateur (16) est relié fluidiquement à une seconde chambre de fluide, en particulier à une chambre annulaire (22), du vérin hydraulique (2), et qu'au moins temporairement, pendant un mouvement de rappel du vérin hydraulique (2), le module distributeur (13) est commandé de telle manière que la pompe hydraulique (27) est reliée fluidiquement à la seconde chambre de fluide (22) et que l'hydrogénérateur (16) est relié fluidiquement à la première chambre de fluide (21) du vérin hydraulique (2), et/ou dans lequel l'unité de commande (19) est conçue de telle manière que la pompe hydraulique (27) est reliée alternativement à une ou à la première chambre de fluide (21) et à la seconde chambre de fluide (22) du vérin hydraulique (2) dans des sections séquentiellement successives, en particulier directement successives, d'un cycle de travail du vérin hydraulique (2), dans lequel, éventuellement, l'hydrogénérateur (16) est relié alternativement de manière correspondante à la seconde chambre de fluide (22) et à la première chambre de fluide (21).
  3. Marteau pilon (1) selon la revendication 1 ou 2, dans lequel le module distributeur (13) comprend un distributeur 4/2 (13), ou dans lequel le module distributeur comprend au moins quatre soupapes hydrauliques individuelles qui sont reliées fluidiquement les unes aux autres dans un circuit en pont, dans lequel le circuit en pont est éventuellement réalisé sous la forme d'un circuit annulaire de quatre soupapes hydrauliques comportant des points de liaison intermédiaires, et est en outre éventuellement réalisé sous la forme d'un circuit parallèle de respectivement deux soupapes hydrauliques montées en série,
    et/ou
    dans lequel le circuit hydraulique comprend plusieurs pompes hydrauliques (27) montées fluidiquement en parallèle et/ou le circuit hydraulique comprend plusieurs hydrogénérateurs (16) montées fluidiquement en parallèle.
  4. Marteau pilon (1) selon la revendication 1 ou 2, ou 3 lorsqu'elle dépend de la revendication 2, dans lequel le circuit hydraulique comprend au moins une soupape de ré-aspiration (25) qui est reliée fluidiquement à une source de ré-aspiration (15) d'un côté et à au moins une chambre de fluide (21, 22) du vérin hydraulique (2), en particulier à la chambre de piston (21) et/ou à la chambre annulaire (22) de l'autre côté, dans lequel la liaison fluidique de la soupape de ré-aspiration (25) est éventuellement réalisée de telle manière qu'une dépression se produisant dans l'au moins une chambre de fluide (21, 22) lors du fonctionnement du vérin hydraulique (2), en particulier du vérin différentiel (2), puisse être compensée par la ré-aspiration du fluide hydraulique au moyen de la soupape de ré-aspiration (25).
  5. Marteau pilon (1) selon l'une des revendications 1 à 4, dans lequel l'unité de commande (19) est conçue pour commander la vitesse de la pompe hydraulique (27) de telle manière que, lors du fonctionnement, ladite pompe hydraulique fonctionne au moins à une vitesse minimale (Dmin) différente de zéro, dans lequel la vitesse de la pompe dans une plage de travail d'un cycle de travail du vérin hydraulique (2) augmente d'abord de préférence passant de la vitesse minimale (Dmin) à une vitesse maximale (Dmax) et ensuite diminue passant de la vitesse maximale (Dmax) à la vitesse minimale (Dmin), dans lequel l'unité de commande (19) est éventuellement conçue de telle manière que la pompe hydraulique (27) fonctionne toujours au moins à la vitesse minimale (Dmin) pendant plusieurs cycles de travail directement successifs, dans lequel en outre éventuellement
    l'unité de commande (19) est conçue de telle manière que la pompe hydraulique (27) est d'abord activée à la vitesse minimale (Dmin), puis la vitesse de la pompe dans une plage de travail d'un cycle de travail du vérin hydraulique (2) augmente d'abord passant de la vitesse minimale (Dmin) à une vitesse maximale (Dmax), et en outre, éventuellement, dans une section de travail suivante, la vitesse de la pompe diminue passant de la vitesse maximale (Dmax) à la vitesse minimale (Dmin), en particulier de telle manière que la vitesse minimale (Dmin) est atteinte à un point d'inversion du vérin hydraulique (2), dans lequel en outre, éventuellement, la vitesse de la pompe hydraulique (27) est augmentéet selon une fonction linéaire du temps, dans lequel, en outre éventuellement, l'unité de commande (19) est conçue de telle manière que, lorsqu'une vitesse finale prédéfinie de l'outil de percussion (8, 9) est atteinte, à partir du moment où la vitesse maximale (Dmax) est atteinte, la vitesse de la pompe hydraulique (27) diminue de telle manière que, sous l'action des forces hydrauliques régnant dans le circuit hydraulique, et le cas échéant, de la force de gravité agissant sur l'outil de percussion (8, 9), la vitesse finale prédéfinie est atteinte au point d'inversion ou peu ou immédiatement avant celui-ci, ou au point de formage ou peu ou immédiatement avant celui-ci, ou au point d'inversion du point de formage ou peu ou immédiatement avant celui-ci, dans lequel, éventuellement pour régler la vitesse finale, l'hydrogénérateur (16) fonctionne comme un frein hydraulique pour freiner activement le piston hydraulique (2).
  6. Marteau pilon (1) selon l'une des revendications 1 à 5, dans lequel l'unité de commande (19) est conçue et configurée pour commander la pompe hydraulique (27) de telle manière qu'une vitesse d'avancement maximale du vérin différentiel (2) soit comprise entre 1,0 et 6 m/s, et/ou dans lequel l'unité de commande (19) est conçue de telle manière qu'un point de départ pour le lancement d'un processus de formage ou de forgeage en fonction d'une vitesse finale respectivement nécessaire en fonction de la hauteur de la pièce (26) à former mesurée dans le sens de mouvement du piston hydraulique (2), et/ou dans lequel l'unité de commande est conçue de telle manière que la distance parcourue par l'outil de percussion (8, 9) pendant un cycle de forgeage soit minimale, et/ou dans lequel l'unité de commande (19) est configurée de telle manière que la position de départ du piston hydraulique (2) soit calculée à l'aide d'une énergie de percussion d'au moins une course parcourue sur la base d'une énergie de percussion nécessaire ultérieurement, dans lequel la position de départ est réglée éventuellement en fonction de la hauteur respective de la pièce (26) à former, et/ou dans lequel l'unité de commande (19) est conçue de telle manière qu'une position, en particulier la position initiale, du piston hydraulique (2) est déterminée au début ou à un instant défini pendant un cycle de formage ou de forgeage et sert de base de calcul pour la détermination d'une position initiale du piston hydraulique (2) et/ou des paramètres de fonctionnement pour la commande de mouvement du piston hydraulique (2) pour un processus de formage ou de forgeage suivant dans le temps.
  7. Marteau pilon (1) selon l'une des revendications 1 à 6, comprenant en outre un accumulateur d'énergie (24) relié à l'hydrogénérateur (16) aux fins de l'alimentation en énergie électrique générée par l'hydrogénérateur (16).
  8. Procédé de commande d'un cycle de travail d'un marteau pilon (1), dans lequel un vérin hydraulique (2) couplé à un outil de percussion (8, 9), en particulier un vérin différentiel (2), est entraîné par alimentation en fluide hydraulique (30) par une pompe hydraulique (27) à servomoteur d'un entraînement linéaire hydraulique (2, 13, 16, 19, 27) couplée fluidiquement au moyen d'un circuit hydraudlique et d'un module distributeur (13) monté fluidiquement en aval du vérin hydraulique (2), dans lequel le fluide hydraulique (30) s'écoulant ainsi du vérin différentiel (2) est conduit au moyen du module distributeur (13) vers un hydrogénérateur (16) à servomoteur monté fluidiquement en aval du module distributeur (13) dans le circuit hydraulique, dans lequel la pompe hydraulique (27) fonctionne comme une pompe hydraulique (27) à servomoteur unidirectionnelle en utilisant le module distributeur (13), et dans lequel l'hydrogénérateur (16) à servomoteur fonctionne comme un hydrogénérateur (16) à servomoteur unidirectionnel en utilisant le module distributeur (13).
  9. Procédé selon la revendication 8, dans lequel, au moins temporairement pendant un mouvement de travail du vérin hydraulique (2), le module distributeur (13) est commandé de telle manière que la pompe hydraulique (27) est reliée fluidiquement à une première chambre de fluide (21) du vérin hydraulique (2), en particulier à la chambre de piston (21), et que l'hydrogénérateur (16) est relié fluidiquement à une seconde chambre de fluide (22) du vérin hydraulique (2), en particulier à la chambre annulaire (22), et qu'au moins temporairement, pendant un mouvement de rappel suivant du vérin hydraulique (2), le module distributeur (13) est commandé de telle manière que la pompe hydraulique (27) est reliée fluidiquement à la seconde chambre de fluide (22), en particulier à la chambre annulaire (22), et que l'hydrogénérateur (16) est relié fluidiquement à la première chambre de fluide (21), en particulier à la chambre de piston (21), du vérin hydraulique (2), et/ou dans lequel la pompe hydraulique (27) est reliée alternativement à une ou à la première chambre de fluide (21) et à la seconde chambre de fluide (22) du vérin hydraulique (2) dans des sections séquentiellement successives, en particulier directement successives d'un cycle de travail du vérin hydraulique (2), dans lequel, éventuellement, l'hydrogénérateur (16) est relié alternativement de manière correspondante à la seconde chambre de fluide (22) et à la première chambre de fluide (21).
  10. Procédé selon l'une des revendications 8 ou 9, la pompe hydraulique (27) est commandée par l'unité de commande (19) de telle manière que la pompe hydraulique (27) fonctionne, pendant le fonctionnement, au moins à une vitesse minimale (Dmin) différente de zéro, dans lequel la vitesse de la pompe dans une section de travail d'un cycle de travail du vérin différentiel (2) augmente d'abord de préférence passant de la vitesse minimale (Dmin) à une vitesse maximale (Dmax) et ensuite diminue passant de la vitesse maximale (Dmax) à la vitesse minimale (Dmin), et dans lequel la vitesse de la pompe est de préférence réglée ou ajustée à la vitesse minimale (Dmin) pendant une section de rappel du cycle de travail.
  11. Procédé selon l'une des revendications 8 à 10, dans lequel, pour accélérer un piston (6) du vérin hydraulique (2) en direction d'un premier point d'inversion (U1) associé à une zone de formage (4) du marteau pilon (1), la vitesse de la pompe hydraulique (27) augmente, passant d'une ou de la vitesse minimale (Dmin), en particulier selon une fonction linéaire du temps, à une ou à la vitesse minimale (Dmin), en particulier en dépendance linéaire du temps, à une ou à la vitesse maximale (Dmax), de telle manière que la vitesse maximale (Dmax) soit atteinte avant qu'un premier point d'inversion (U1) du vérin hydraulique (2) associé à la zone de formage (4) soit atteint, dans lequel la vitesse de la pompe hydraulique (27) diminue de préférence après que la vitesse maximale (Dmax) a été atteinte , en particulier en relation linéaire avec le temps, de telle manière que la vitesse minimale (Dmin) soit atteinte lors ou par l'atteinte du premier point d'inversion (U1), dans lequel la pompe hydraulique (27) fonctionne toujours au moins à la vitesse minimale (Dmin) pendant plusieurs cycles de travail directement successifs, dans lequel en outre, éventuellement, la pompe hydraulique (27) est d'abord activée à la vitesse minimale (Dmin), et ensuite la vitesse de la pompe dans une plage de travail d'un cycle de travail du vérin hydraulique (2) augmente d'abord passant de la vitesse minimale (Dmin) à une vitesse maximale (Dmax), et en outre, éventuellement, dans une section de travail suivante, la vitesse de la pompe diminue passant de la vitesse maximale (Dmax) à la vitesse minimale (Dmin), en particulier de telle manière que la vitesse minimale (Dmin) est atteinte à un point d'inversion du vérin hydraulique (2), dans lequel en outre, éventuellement, lorsqu'une vitesse finale prédéfinie de l'outil de percussion (8, 9) est atteinte, la vitesse de la pompe hydraulique (27) diminue à partir de l'instant où la vitesse maximale (Dmax) est atteinte, de sorte que, sous l'action des forces hydrauliques régnant dans le circuit hydraulique, et éventuellement de la force de gravité agissant sur l'outil de percussion (8, 9), la vitesse finale prédéfinie est atteinte au point d'inversion ou peu ou immédiatement avant celui-ci, ou au point de formage ou peu ou immédiatement avant celui-ci, ou au point d'inversion du point de formage, ou peu ou immédiatement avant celui-ci, dans lequel, éventuellement pour régler la vitesse finale, l'hydrogénérateur (16) fonctionne comme un frein hydraulique pour freiner activement le piston hydraulique (2).
  12. Procédé selon l'une des revendications 8 à 11, dans lequel, lorsqu'un ou le premier point d'inversion (U1) associé à une ou l'une zone de formage (4) du marteau pilon (1) est atteint ou lorsqu'une vitesse prédéfinie du coulisseau (9) est atteinte, le module distributeur (13) est commandé de telle manière qu'une sortie de pression (12) dela pompe hydraulique (27) est reliée fluidiquement à une seconde chambre de fluide, lorsqu'elle dépend de la revendication 9, à la seconde chambre de fluide (22) du vérin hydraulique (2), en particulier la chambre annulaire (22) du vérin différentiel (2), et une entrée de pression (17) de l'hydrogénérateur (16) est reliée fluidiquement à une première chambre de fluide, lorsqu'elle dépend de la revendication 9, à la première chambre de fluide (21) du vérin hydraulique (2), en particulier à la chambre de piston (21) du vérin différentiel (2).
  13. Procédé selon la revendication 12, lorsqu'elle dépend de la revendication 9 ou d'une revendication rattachée à la revendication 9, dans lequel une dépression générée par le rebondissement au premier point d'inversion (U1) dans la seconde chambre de fluide (22), en particulier dans la chambre annulaire (22), est compensée au moyen d'une soupape de ré-aspiration (25) reliée fluidiquement d'un côté à la seconde chambre de fluide (22) et de l'autre côté à un réservoir hydraulique (15), et, de préférence, une énergie élastique générée par le rebondissement dans le circuit hydraulique est convertie en énergie électrique par décompression par l'hydrogénérateur (16) et est de préférence stockée dans un accumulateur intermédiaire (24).
  14. Procédé selon l'une des revendications 8 ou 13, dans lequel, lorsqu'un second point d'inversion (U2) du vérin hydraulique (2), opposé à la zone de formage (4) du marteau pilon (1) est atteint, le module distributeur (13) est commandé de telle manière qu'une sortie de pression (12) de la pompe hydraulique (2) est reliée fluidiquement à une première chambre de fluide, ou lorsqu'elle dépend de la revendication 9 ou d'une revendication rattachée à la revendication 9 à la première chambre de fluide (21) du vérin hydraulique (2), en particulier à la chambre de piston (21) du vérin différentiel (2), et une entrée de pression (17) de l'hydrogénérateur (16) est reliée fluidiquement à une chambre de fluide, ou lorsqu'elle dépend de la revendication 9 ou d'une revendication rattachée à la revendication 9, à la seconde chambre de fluide (22) du vérin hydraulique (2), en particulier à la chambre annulaire (22) du vérin différentiel (2).
  15. Procédé selon l'une des revendications 8 à 14, dans lequel un point de départ pour le lancement d'un processus de formage ou de forgeage en fonction d'une vitesse finale respectivement nécessaire en fonction de la hauteur de la pièce (26) à former mesurée dans le sens de mouvement du piston hydraulique (2), et/ou dans lequel la distance parcourue par l'outil de percussion (8, 9) pendant un cycle de forgeage est minimale.
  16. Procédé de commande d'un marteau pilon (1) selon l'une des revendications 1 à 7, dans lequel plusieurs cycles de travail successifs sont commandés selon un procédé selon l'une des revendications 8 à 15, dans lequel la pompe hydraulique (27) fonctionne au moins à une vitesse minimale différente de zéro pendant la pluralité de cycles de travail.
  17. Procédé selon la revendication 16, dans lequel de l'énergie secondaire générée dans un cycle de travail par l'hydrogénérateur (16) est fournie dans un cycle de travail suivant du marteau pilon (1), et/ou dans lequel une énergie de percussion d'au moins une course parcourue est utilisée pour calculer la position initiale du piston hydraulique (2) sur la base d'une énergie de percussion nécessaire ultérieurement, et/ou dans lequel une position, en particulier la position initiale, du piston hydraulique (2) est déterminée au début ou à un instant défini pendant un cycle de formage ou de forgeage et sert de base de calcul pour la détermination d'une position initiale du piston hydraulique (2) et/ou des paramètres de fonctionnement pour la commande de mouvement du piston hydraulique (2) pour un processus de formage ou de forgeage suivant dans le temps.
EP16712778.6A 2015-04-09 2016-03-18 Marteau pilon et procédé de commande du cycle de travail d'un marteau pilon Active EP3280554B1 (fr)

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PCT/EP2016/055950 WO2016162184A1 (fr) 2015-04-09 2016-03-18 Machine de formage, notamment marteau pilon et procédé de commande de la machine de formage

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Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
HUE069235T2 (hu) * 2016-10-18 2025-02-28 Automation Press And Tooling A P & T Ab Szervohidraulikus prés
DE102018120000A1 (de) * 2018-08-16 2020-02-20 Moog Gmbh Elektrohydrostatisches Aktuatorsystem mit Nachsaugbehälter
CN110259769B (zh) * 2019-05-27 2020-09-25 天津市天锻压力机有限公司 3000t液态模锻液压机的电液控制系统及成形工艺
DE102020213262A1 (de) * 2020-10-21 2022-04-21 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zum Betreiben eines hydraulischen Antriebs
DE102021101539B4 (de) 2021-01-25 2024-09-26 Langenstein & Schemann Gmbh Hydraulische Umformmaschine zum Pressen von Werkstücken, insbesondere Schmiedehammer, und Verfahren zum Betreiben einer hydraulischen Umformmaschine, insbesondere eines Schmiedehammers
CN114458663B (zh) * 2022-01-19 2024-02-02 上海海岳液压机电工程有限公司 基于液压打桩锤的能量控制方法
CN114505438B (zh) * 2022-04-02 2022-07-12 太原理工大学 一种大功率电液控制的压力机系统
DE102023105367B4 (de) 2023-03-03 2025-01-30 Langenstein & Schemann Gmbh Hydraulische Umformmaschine zur Werkstückumformung, Hydrauliksteuereinheit und Verfahren zur Steuerung eines Hydraulikzylinders einer hydraulischen Umformmaschine
DE102023113473B4 (de) 2023-05-23 2025-07-03 Langenstein & Schemann Gmbh Hydraulische Umformmaschine zur Werkstückumformung, Hydrauliksteuereinheit und Verfahren zur Steuerung eines Hydraulikzylinders einer hydraulischen Umformmaschine
US20260072458A1 (en) * 2024-08-19 2026-03-12 The Bradbury Co., Inc. Methods and apparatus to manage hydraulic systems

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3636265C1 (en) * 1986-10-24 1987-08-27 Langenstein & Schemann Gmbh Liquid-outlet-securing device in the region of the piston rod guide on the pull-back cylinder of a metal-forming machine tool

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3742820A (en) * 1971-09-22 1973-07-03 Sperry Rand Corp Power transmission
SE437861B (sv) * 1983-02-03 1985-03-18 Goran Palmers Anordning vid medelst hydraul-cylinder drivna maskiner med en av en drivkella via en energiackumulatordriven pump
DE3728418A1 (de) * 1987-08-26 1989-03-09 Horst Baltschun Dynamisch vorgespannte druckmittelbetaetigte presse
JPH07155999A (ja) * 1993-09-02 1995-06-20 Maschinenfabrik Mueller Weingarten Ag 液圧プレスの駆動を制御するための方法及び装置
DE102008003106A1 (de) 2008-01-01 2009-07-02 Dieffenbacher Gmbh + Co. Kg Verfahren zum energiesparenden Betreiben einer hydraulischen Presse und eine energiesparende und wartungsarme hydraulische Presse
DE102008053766A1 (de) 2008-10-21 2010-04-22 Voith Patent Gmbh Hydraulischer Pressenantrieb und Verfahren zum Betreiben eines hydraulischen Pressenantriebs
KR101267762B1 (ko) * 2009-07-27 2013-05-24 오일기어 토울러 에스.아.에스. 금속 성형 기계 같은 처리 기계를 유압으로 작동시키기 위한 기기 및 이와 같은 금속 성형 기계 작동 방법
DE102011000473B4 (de) * 2011-02-02 2017-07-13 Langenstein & Schemann Gmbh Pressmaschine und Verfahren zum Pressen von Werkstücken
DE102011011750A1 (de) * 2011-02-18 2012-08-23 MAE Maschinen- u. Apparatebau Götzen GmbH Druckspeicherlose hydraulische Antriebsanordnung für und mit einem Verbraucher, insbesondere für Pressen sowie Verfahren zum Betreiben einer solchen druckspeicherlosen hydraulischen Antriebsanordnung
DE102012000017A1 (de) 2012-01-02 2013-07-04 Schuler Smg Gmbh & Co. Kg Verfahren zur Steuerung einer hydraulischen Presse
DE202014104509U1 (de) 2014-09-22 2014-10-20 Schuler Pressen Gmbh Schmiedehammer

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3636265C1 (en) * 1986-10-24 1987-08-27 Langenstein & Schemann Gmbh Liquid-outlet-securing device in the region of the piston rod guide on the pull-back cylinder of a metal-forming machine tool

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WO2016162184A1 (fr) 2016-10-13
US20180185900A1 (en) 2018-07-05
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DE102015105400B4 (de) 2022-06-02
EP3280554A1 (fr) 2018-02-14

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