EP4065360A1 - Système électrohydrostatique à capteur de pression - Google Patents

Système électrohydrostatique à capteur de pression

Info

Publication number
EP4065360A1
EP4065360A1 EP20811548.5A EP20811548A EP4065360A1 EP 4065360 A1 EP4065360 A1 EP 4065360A1 EP 20811548 A EP20811548 A EP 20811548A EP 4065360 A1 EP4065360 A1 EP 4065360A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
fluid
electrohydrostatic
cylinder
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
Application number
EP20811548.5A
Other languages
German (de)
English (en)
Other versions
EP4065360B1 (fr
Inventor
Sascha DANY
Sven Müller
Kohlhaas REINER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Moog GmbH
Original Assignee
Moog GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Moog GmbH filed Critical Moog GmbH
Publication of EP4065360A1 publication Critical patent/EP4065360A1/fr
Application granted granted Critical
Publication of EP4065360B1 publication Critical patent/EP4065360B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • 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
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/28—Arrangements for preventing distortion of, or damage to, presses or parts thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40592—Assemblies of multiple valves with multiple valves in parallel flow paths
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/613—Feeding circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/85—Control during special operating conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8757—Control measures for coping with failures using redundant components or assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input

Definitions

  • the present invention relates to an electrohydrostatic system for controlling the set-up speed of a hydraulic cylinder, for example in a powder press, forging press and / or a forming press.
  • FIGS. 2 and 3 show two systems known in the prior art for safeguarding the set-up speed.
  • the constant pressure system includes a constant pressure source 15 for supplying hydraulic pressure. Furthermore, the constant pressure system in FIG. 3 includes directional control valve 18 for controlling the function of the hydraulic cylinder 10, for example the retraction and extension.
  • the safe set-up speed is secured via one or more fixed orifices 13, with or without set-up valves 14, 17.
  • the fixed orifices 13 bridge one or two simple or redundant safety valves 16 (load holding and / or pressure build-up valves).
  • the fixed apertures 13 are set for the maximum pressure occurring in the system and / or for the suspended load on the hydraulic cylinder.
  • a maximum pressure in the system is throttled through a fixed orifice 13 (parallel to the pressure build-up valve 16 behind the pump 15) before a pressure boost can occur due to unequal areas in the hydraulic cylinder.
  • several directional control valves must be bypassed.
  • the safety valve 16 which is connected between the directional valve 18 and the pump 15, must be bypassed.
  • the safety valve 16 separates the pressure build-up of the pump 15 from the constant pressure system in order to prevent a pressure build-up in the system.
  • a second safety valve 16 is between the hanging load on the ring side or the piston side of the hydraulic cylinder 10 and the directional control valve 18 are introduced.
  • the safety valve 16 secures the hydraulic cylinder from falling down due to the suspended load. To move the hydraulic cylinder, it is necessary to bypass these two safety valves or to open them accordingly. In setup mode and the necessary bridging of the safety valve 16, the safe setup speed must continue to be guaranteed. The movement of the hydraulic cylinder must not exceed a speed of 10 mm / s, for example.
  • the first safety valve 16 for securing the hydraulic pressure in the constant pressure system is bypassed via the parallel branch with the setting valve 17 or without the setting valve 17 and the fixed diaphragm 13.
  • the fixed diaphragm 13 is designed in such a way that, at a maximum pressure of the pump 15, the volume flow which runs over the fixed diaphragm 13 does not reach a speed higher than, for example, 10 mm / s at the hydraulic cylinder.
  • the fixed orifice 13 is therefore designed for the maximum pressure of the pump 15.
  • the volume flow can be provided via the setting valve 17 and the fixed orifice 13 and directed via the directional control valve 18.
  • the suspended load on the ring side or piston side of the hydraulic cylinder can move the hydraulic cylinder.
  • the suspended load and the hydraulic cylinder surface together create a certain pressure on the load side of the hydraulic cylinder.
  • the volume flow passes through the set-up valve 14 and the fixed orifice 13.
  • the fixed orifice 13 is designed in such a way that when the pressure is applied on the ring side due to the suspended load, the volume flow does not reach a speed higher than 10 mm / s.
  • the pump 15, which is secured via the safety valve 16 in front of the directional valve 18, via the setting valve 17 and the fixed panel 13, and the suspended load, which is protected via the safety valve 16, the setting valve 14 and the fixed panel 13, are the two sources can provide the energy and thus a pressure build-up for the constant pressure system.
  • the set-up speed can be safeguarded via a "Safe Limited Speed” (SLS) function in the motor control device 20 and the drive motor of the motor-pump unit 15 or, on the other hand, via a fixed panel 13, with or without additional Set-up valve 14.
  • SLS Safe Limited Speed
  • the energy is applied again, as already shown in FIG was achieved via safety valves and fixed panels, is connected in this system in the Motor control device 20 achieved by the function "Safe Torque Off” (STO).
  • STO Safe Torque Off
  • the motor control device cannot provide power to the motor-pump unit 15 for generating hydraulic power in the hydraulic system. In order to still be able to move the hydraulic cylinder, a volume flow must be fed to the system.
  • the volume flow can only be realized in that the motor control device 20 has a function which limits the speed of the motor pump unit 15 to a predetermined value, for example to a value for a speed of 10 mm / s.
  • This function corresponds to the above-mentioned SLS function.
  • the SLS function represents a special function in the engine control device 20. Rather, a safety-relevant engine control device 20 is required.
  • the SLS function is expensive and requires computing capacity.
  • the motor control device can make a certain computing power available, which is limited by the built-in hardware. A large part of the computing power that can be made available is reserved for the SLS function. Conversely, a necessary regulation can no longer be provided by the motor control device and further components are necessary, which increases the complexity of the control and also increases the costs
  • a protection according to the protection shown in FIG. 2 takes place for the second energy impression by means of the hanging load.
  • the suspended load acts on the second cylinder chamber 12.
  • the safety valve 16 or the safety valves 16, which shut off the hydraulic cylinder 10, so that the volume flow passes through the adjustment valve 14 and the fixed diaphragm 13, are safeguarded.
  • the fixed panel 13 is set to the pressure of the hanging load A possible lowering of the hydraulic cylinder above the hanging load is thus set via the fixed panel 13.
  • the hydraulic cylinder is moved by the SLS function, as well as via the fixed panel 13. For this movement, the fixed panel must 13 can no longer be interpreted. This is only designed for movement through the hanging load.
  • the fixed diaphragm would have to be designed in such a way that the pressure on the fixed diaphragm would correspond to the maximum pressure of the motor-pump unit.
  • the motor-pump unit has a pressure of 350 bar.
  • the fixed diaphragm would have to be designed for a very high pressure level and thus a very high energy level, the suspended load being in a pressure range of 10 bar to 20 bar. Due to the necessary design for a higher pressure, extreme losses would be generated in the system, for example, and thus energy would be destroyed.
  • a first aspect of the present invention comprises an electrohydrostatic system according to the invention with a hydraulic cylinder.
  • the hydraulic cylinder has a first cylinder chamber and a second cylinder chamber.
  • the electrohydrostatic system comprises a fluid-hydraulic supply device for providing a hydraulic fluid and a fluid-hydraulic motor-pump unit.
  • the fluid-hydraulic motor-pump unit is set up to provide a fluid-hydraulic volume flow for moving the hydraulic cylinder.
  • the electrohydrostatic system also includes an engine control device.
  • the motor control device is set up to provide a nominal current for an electrical drive of the fluid-hydraulic motor-pump unit.
  • the electrohydrostatic system is connected to at least one fluid-hydraulic safety valve, which is connected on a first valve side to one of the cylinder chambers or the second cylinder chamber of the hydraulic cylinder and on a second valve side to the fluid-hydraulic motor-pump unit. Furthermore, the electrohydrostatic system has a bypass connection with a fixed panel for bridging the at least one fluid-hydraulic safety valve. The bypass connection is connected to the first valve side and to the second valve side of the at least one fluid-hydraulic safety valve.
  • the electrohydrostatic system also has a pressure sensor.
  • the pressure sensor is connected to one of the cylinder chambers of the hydraulic cylinder, for example to the second cylinder chamber, and is set up to detect a fluid-hydraulic pressure at one of the cylinder chambers and, according to the detected fluid-hydraulic pressure, a release signal for the To provide a motor control device for providing the nominal current for the electrical drive of the fluid-hydraulic motor-pump unit.
  • the present invention is thus based on the knowledge that the motor control device for controlling the motor pump unit only needs the STO function, which prevents the introduction of energy into the system.
  • the SLS function of the motor control device is no longer required in the inventive embodiment of the electrohydrostatic system, whereby the set-up speed is not detected / monitored via the motor control device either.
  • the suspended load is secured by at least one safety valve and a fixed panel.
  • a pressure sensor is advantageously provided, for example on the ring side, which determines the pressure on the ring side for further processing.
  • the pressure on the fixed diaphragm is advantageously detected via the pressure sensor.
  • the suspended load is thus also secured via the fixed panel, in addition to a certain pressure.
  • the minimum that is secured includes the pressure (energy) impressed by the suspended load and a corresponding reserve, for example 20 bar. Accordingly, the evaluation of the pressure sensor must be set to the selected pressure.
  • this can include an increase in the speed of the hydraulic cylinder above a specified value, whereby the energy input into the motor-pump unit is switched off via the STO function of the motor control device.
  • the electrohydrostatic system comprises, in particular, a first safety device which is set up to receive an electrical signal corresponding to a detected fluid-hydraulic pressure from the pressure sensor and to provide a release signal for the motor control device for providing the rated current for the electrical drive of the fluid-hydraulic motor-pump unit.
  • the pressure can advantageously be detected via the pressure sensor.
  • the pressure sensor is monitored by the first safety device.
  • the first safety device can be designed as a safety PLC (programmable logic controller), in particular as a safety controller.
  • the pressure sensor or the value the determined pressure is read out via the first safety device, which monitors whether the system is still in safe setup mode.
  • the motor control device can also be addressed via the safety device, in particular the STO function can be controlled.
  • the hydraulic cylinder is designed as a differential cylinder, synchronous cylinder, multi-surface cylinder or as a separate cylinder arrangement.
  • different hydraulic cylinders can be addressed accordingly by the electrohydrostatic system according to the invention.
  • the fluid-hydraulic supply device comprises a pressure accumulator, a safety valve, a fluid source, at least one check valve and a fluid reservoir.
  • the fluid for the motor-pump unit is partially made available via the fluid-hydraulic supply device.
  • the pressure accumulator represents a storage device for pressurized fluid which can be discharged into the system.
  • the fluid reservoir represents a tank for the auxiliary unit, from which the fluid source can also be supplied.
  • a safe torque off safety function is provided via the motor control device.
  • the motor control device can be designed as a frequency converter.
  • the frequency converter can be designed as a converter which generates an alternating voltage of variable frequency and amplitude from an alternating voltage for the direct supply of the motor-pump unit.
  • the Safe Torque Off (STO) function is a drive-integrated safety function in the frequency converter.
  • the STO function ensures that no more torque-generating energy can act on a motor, in particular on the motor-pump unit, and that unwanted start-up is prevented.
  • the STO function is a device to avoid unexpected start-ups in accordance with EN 60204-1 section 5.4.
  • the impulses of a drive can be safely deleted via the STO function.
  • the drive is secured torque-free. This state can be monitored internally.
  • the pressure sensor is designed as a pressure sensor with increased functional safety.
  • the pressure sensor with increased functional safety is specially designed for use in safety circuits / safety functions in the context of the functional safety of machines and systems up to PL d-Kat 3 (according to ISO 13849 ) designed pressure sensor.
  • the pressure sensor with increased functional safety is designed with two channels, each channel consisting of a sensor element and evaluation electronics. Due to the redundant design, the pressure sensor generates increased functional Safety two separate, independent, pressure-proportional output signals. The output signal is thus available in redundant form.
  • a signal fails, a second signal is still available for processing, whereby the failure of a signal already initializes error handling.
  • the safety function and error handling can be checked by evaluating and comparing the two analog output signals in a first safety device.
  • the first safety device and the pressure sensor with increased functional safety are used to indirectly check whether the set-up speed of the hydraulic cylinder is exceeded or not. If the pressure rises above a certain value, a control signal is provided to the frequency converter via the first safety device in order to switch off the motor-pump unit.
  • a redundant arrangement with two parallel simple pressure sensors can be provided, which map the requirement for a pressure sensor with increased functional safety. These thus represent a pressure sensor arrangement with increased functional safety.
  • Usual or available pressure sensors can be used as pressure sensors for the pressure sensor arrangement.
  • the resistance of the fixed diaphragm has at least one value which is determined in the hydraulic cylinder by the pressure generated by a suspended load on the hydraulic cylinder.
  • the suspended load is thus also secured via the fixed panel. The safe set-up speed is guaranteed.
  • the fixed diaphragm can be designed for the pressure generated by the suspended load, plus a certain pressure.
  • the resistance of the fixed panel is set to a pressure for providing a set-up speed of the hydraulic cylinder in a range of 5 to 40 mm / s, preferably 10 mm / s.
  • This set pressure means that set-up speeds are rated as "safe" according to standardization guaranteed affordable.
  • the pressure sensor is connected to the second cylinder chamber of the hydraulic cylinder. This arrangement may be necessary depending on the cylinder arrangement, as shown above, the maximum pressure of the individual cylinder chambers, the area ratios on the cylinders, and energetic limitations in the set-up mode.
  • a fluid-hydraulic setup valve is switched in the bypass connection.
  • the setup mode can advantageously be switched on or off via this setup valve.
  • this set-up valve secures the cylinder against falling off due to its own weight and the force of attraction when the motor-pump unit is switched off.
  • a pressure limiting valve is switched in the bypass connection.
  • the setting valve can be replaced via the pressure limiting valve in combination with a check valve.
  • the pressure limiting valve can be used to set the direction of movement for which the set-up speed is to be set.
  • the pressure limiting valve can be selectively overpressured.
  • a check valve is connected in parallel to the pressure limiting valve.
  • a set-up valve can be replaced / saved via the check valve in combination with the pressure limiting valve.
  • the check valve in combination with the throttle valve enables load holding and the limited set-up speed during the extension of the hydraulic cylinder. During the retraction of the hydraulic cylinder, the pressure relief valve is bypassed via the branch of the check valve and the limited set-up speed is also achieved
  • the electrohydrostatic system comprises a second safety device comprising a path measuring system and / or a mechanical safety device.
  • the second safety device in combination with the first safety device, forms a redundant safety device. Should one of the two safety devices show a defect, the remaining safety device can guarantee the full safety of the system.
  • the second safety device can alternatively also be designed as a second hydraulic safety valve. In particular, the second safety device can correspond to the first safety device.
  • the path measuring system can provide information about the actual speed of the hydraulic cylinder. The speed determined via the distance measuring system can then be used to limit the same via the motor control device and the motor pump unit.
  • the determined pressure in combination with the defined resistance of the fixed diaphragm to the volume flow and thus the speed of the hydraulic cylinder is determined.
  • the displacement signal is used to determine the speed of the hydraulic cylinder, taking time into account.
  • a mechanical brake and / or a clamping device can be provided, for example, as mechanical safety.
  • the first cylinder chamber of the hydraulic cylinder is connected to the fluid-hydraulic motor-pump unit and the second cylinder chamber of the hydraulic cylinder is connected to the at least one fluid-hydraulic safety valve.
  • the first cylinder chamber of the hydraulic cylinder is with the connected to at least one fluid-hydraulic safety valve and the second cylinder chamber of the hydraulic cylinder with the fluid-hydraulic motor-pump unit.
  • a second aspect of the present invention comprises the use of the electrohydrostatic system according to the invention for controlling the set-up speed of a hydraulic cylinder in a powder press, forging press and / or forming press.
  • FIG. 1 shows a schematic representation of an electrohydrostatic system according to a first embodiment
  • FIG. 4 shows a schematic representation of an electrohydrostatic system according to a second embodiment
  • FIG. 5 shows a schematic representation of an electrohydrostatic system according to a third embodiment
  • FIG. 6 shows a schematic representation of an electrohydrostatic system according to a fourth embodiment
  • 7 shows a schematic representation of an electrohydrostatic system according to a fifth embodiment
  • FIG. 8 shows a schematic illustration of an electrohydrostatic system according to a sixth embodiment
  • the electrohydrostatic system 1 has a hydraulic cylinder 10 with a first cylinder chamber 11 and a second cylinder chamber 12. Furthermore, the electrohydrostatic system 1 has a motor-pump unit 15 for supplying pressure and a supply device 90 for supplying fluid. In the embodiment shown in FIG. 1, the motor-pump unit 15 is connected to the first cylinder chamber 11 of the hydraulic cylinder 10 and the supply device 90 via a check valve 93 at a first connection. At a second connection, the motor-pump unit 15 has a connection to a safety valve 16, which is also connected to the second cylinder chamber 12 of the hydraulic cylinder 10.
  • the supply device 90 comprises a safety valve 91, a fluid source 92, a check valve 93, a pressure accumulator 95 and a fluid reservoir 96.
  • the electrohydrostatic system 1 has a motor control device 20, which can be designed as a frequency converter.
  • the electrohydrostatic system 1 has a pressure sensor 60, in particular a pressure sensor with increased functional safety.
  • the pressure sensor 60 provides a pressure value determined on the fixed panel 13 of a first safety device 30, preferably a safety PLC as a safety controller 30.
  • the first safety device 30 is electrically coupled to the motor control device 20 and forms an electrical signal from the safety device 30 in response to a to receive increased pressure corresponding to a setup speed outside of the requirement.
  • the frequency converter 20 preferably has a “safe torque off” (STO) function for switching off the torque of the motor-pump unit in order to set the set-up speed in accordance with the requirements.
  • STO safety torque off
  • the present invention is characterized by the pressure sensor with increased functional safety.
  • two pressure sensors of a simple design can be used in redundant combination, in which an evaluation of the signals provided is implemented analogously to the pressure sensor with increased functional safety.
  • a simple pressure sensor without a redundant design can be used and evaluated.
  • the pressure sensor (s) 60 in the embodiment, as well as in the alternative embodiment as shown above, can be introduced into the electrohydrostatic system 1 on the first cylinder chamber 11 and / or the second cylinder chamber 12 of the hydraulic cylinder 10.
  • the hydraulic cylinder 10 can be used as a differential cylinder, as a synchronous cylinder Multi-surface cylinders or can be used as an exploded cylinder arrangement.
  • An unintentional build-up of pressure in the electrohydrostatic system 1 can be safeguarded via the STO safety function of the frequency converter 20 and the motor-pump unit 15.
  • the safety against a drop in the suspended load can be ensured by means of one or a plurality of safety-relevant valves 16.
  • the setting of the safe speed in the setup process takes place via the fixed screen 13.
  • the fixed screen 13 represents a bypass of the safety valve 16 and is connected to the second cylinder chamber 12 of the hydraulic cylinder 10 and the motor-pump unit 15 or the supply device 90.
  • the fixed panel 13 has a connection to the pressure sensor 60 with increased functional safety.
  • the fixed screen 13 is designed without an additional set-up valve.
  • the pressure difference for which the fixed screen 13 is designed is set by the pressure sensor 60 with increased functional safety as an upper limit in the set-up mode. If this specified pressure value is exceeded, the first safety device 30 triggers the STO safety function of the frequency converter 20. When the STO safety function is triggered, the safe setup speed is not exceeded.
  • a safe set-up speed can be achieved, although pressure differences occur in the hydraulic chambers due to unequal areas or other reasons. Thus, no pressure limiting device is overpressed and the maximum
  • Set-up speed limited The set-up speed is specified by the speed and / or the delivery volume of the variable-speed motor pump unit 15, whereby the maximum set-up speed can be freely determined by the resistor and the pressure sensor 60 with increased functional reliability between the pressure of the suspended load and the maximum pressure of the pressure relief valves .
  • FIG. 4 shows a schematic illustration of an electrohydrostatic system 1 according to a second embodiment.
  • the electrohydrostatic system 1 is extended by a setting valve 14 in the bypass connection of the safety valve 16 or the safety valves 16 with reference to the embodiment of FIG. 1.
  • the setting valve 14 is between the fixed diaphragm 13 and the second cylinder chamber 12 of the hydraulic cylinder 10 introduced.
  • the pressure sensor 60 with increased functionality determines the pressure on the fixed panel 13 via the setting valve 14.
  • the setting mode can be switched on and off via the setting valve 14.
  • the hydraulic cylinder can be prevented from sagging due to its own weight in the event of a failure of the motor-pump unit 15.
  • Electrohydrostatic system 1 expanded by a pressure limiting valve 70 in the bypass connection of the safety valve 16 or the safety valves 16 with reference to the embodiment of FIG. 1.
  • the pressure limiting valve 70 is placed between the fixed orifice 13 and the second cylinder chamber 12 of the hydraulic cylinder 10.
  • the pressure sensor 60 with increased functionality determines the pressure at the fixed orifice 13 via the pressure limiting valve 70.
  • the pressure limiting valve 70 serves as a load-holding valve to prevent the piston of the hydraulic cylinder 10 from dropping to be avoided by its own weight.
  • the pressure limiting valve 70 can be set up in the extending direction of the hydraulic cylinder 10.
  • FIG. 6 shows a schematic illustration of an electrohydrostatic system 1 according to a fourth embodiment.
  • the electrohydrostatic system 1 is expanded to include a pressure limiting valve 80 in the bypass connection of the safety valve 16 or the safety valves 16 with reference to the embodiment of FIG. 1.
  • the pressure limiting valve 80 is inserted between the fixed orifice 13 and the second cylinder chamber 12 of the hydraulic cylinder 10.
  • the pressure sensor 60 with increased functionality determines the pressure at the fixed orifice 13 via the pressure limiting valve 80.
  • a check valve 81 is provided in a bypass connection to the pressure limiting valve 80.
  • the pressure limiting valve 80 serves as a load holding valve in order to prevent the piston of the hydraulic cylinder 10 from sinking under its own weight.
  • the function of the setting valve 14 is replaced by the pressure holding valve 80 in combination with the check valve 81.
  • the pressure relief valve 80 is adjusted to the suspended load
  • FIG. 7 shows a schematic illustration of an electrohydrostatic system 1 according to a fifth embodiment.
  • the pressure sensor 60 is connected with increased functional safety to the cylinder chamber of the hydraulic cylinder 10, which has no connection to the safety valve 16.
  • the exact position of the pressure sensor 60 with increased functionality can be selected as a function of the overall system and thus the alignment and type of hydraulic cylinder, further axes that can overpress this axis and / or the acting weight. This enables a safe set-up speed to be provided for each system in an efficient and flexible manner.
  • the electrohydrostatic system 1 additionally has a second safety device 50.
  • the second safety device 50 can be a distance measuring system and / or a mechanical safety device include. Redundant security can be provided by the second safety device 50 in combination with the first safety device 30. A defect in one of the two safety devices 30, 50 can be compensated for by the other functional safety device 30, 50, whereby full safety is guaranteed.
  • the second safety device 50 can also be designed as a second hydraulic safety valve 16.
  • the path measuring system supplies information about the actual speed of movement of the hydraulic cylinder 10 with increased functional safety.
  • the determined actual speed of movement can be used to limit the same via the frequency converter 20 in combination with the motor-pump unit 15.
  • the path signal is derived over time.
  • the mechanical safety can be set up using a mechanical brake and / or clamping device. This increases the safety of the electrohydrostatic system 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

La présente invention concerne un système électrohydrostatique doté d'un vérin hydraulique comprenant une première chambre de vérin et une seconde chambre de vérin. Le système électrohydrostatique comporte en outre un dispositif d'alimentation en fluide hydraulique destiné à fournir un fluide hydraulique, une unité motopompe à fluide hydraulique, conçue de sorte à fournir un flux volumique de fluide hydraulique pour déplacer le vérin hydraulique. Un dispositif de commande de moteur est conçu de sorte à fournir un courant nominal pour un entraînement électrique de l'unité motopompe à fluide hydraulique. Le système électrohydrostatique comporte en outre au moins une soupape de sécurité à fluide hydraulique qui est reliée sur un premier côté de soupape à une des chambres de vérin du vérin hydraulique et sur un seconde côté de soupape, à l'unité motopompe à fluide hydraulique. La soupape de sécurité à fluide hydraulique peut être contournée par l'intermédiaire d'une liaison de dérivation à membrane fixe, la liaison de contournement étant reliée au premier côté de soupape et au second côté de soupape de ladite au moins une soupape de sécurité à fluide hydraulique. Le système électrohydrostatique comprend par ailleurs un capteur de pression qui est relié à une des chambres de vérin du vérin hydraulique. Le capteur de pression est conçu de sorte à détecter une pression de fluide hydraulique sur une des chambres de vérin et à fournir en fonction de la pression de fluide hydraulique un signal de libération pour le dispositif de commande de moteur destiné à fournir le courant nominal pour l'entraînement électrique de l'unité motopompe à fluide hydraulique.
EP20811548.5A 2019-11-26 2020-11-18 Système électrohydrostatique à capteur de pression Active EP4065360B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019131980.3A DE102019131980A1 (de) 2019-11-26 2019-11-26 Elektrohydrostatisches System mit Drucksensor
PCT/EP2020/082546 WO2021104966A1 (fr) 2019-11-26 2020-11-18 Système électrohydrostatique à capteur de pression

Publications (2)

Publication Number Publication Date
EP4065360A1 true EP4065360A1 (fr) 2022-10-05
EP4065360B1 EP4065360B1 (fr) 2023-12-20

Family

ID=73544139

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20811548.5A Active EP4065360B1 (fr) 2019-11-26 2020-11-18 Système électrohydrostatique à capteur de pression

Country Status (5)

Country Link
US (1) US20230026318A1 (fr)
EP (1) EP4065360B1 (fr)
CN (1) CN114761221B (fr)
DE (1) DE102019131980A1 (fr)
WO (1) WO2021104966A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021005824B4 (de) 2021-11-24 2023-08-10 Hydac International Gmbh Sicherheitsventilvorrichtung
DE102022111781B4 (de) * 2022-05-11 2023-11-30 Festo Se & Co. Kg Pneumatisches Aktorsystem
DE102022121962A1 (de) * 2022-08-31 2024-02-29 Bucher Hydraulics Ag Elektrisch-hydraulischer Aktor
DE102024103693A1 (de) * 2024-02-09 2025-08-14 Bucher Hydraulics Ag Zur Rekuperation fähiger hydraulischer Aktor

Family Cites Families (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4066103A (en) * 1975-04-18 1978-01-03 Danfoss A/S Hydraulic regulator
DE3237103C3 (de) * 1982-10-07 1997-01-23 Wessel Hydraulik Sicherheitsventil als Lasthalteventil in der Hebezeughydraulik
DE3901475C2 (de) * 1989-01-19 1994-07-14 Danfoss As Fluidgesteuerte Servoanordnung
DE4140408A1 (de) * 1991-12-07 1993-06-09 Robert Bosch Gmbh, 7000 Stuttgart, De Elektrohydraulische steuereinrichtung
JP2809096B2 (ja) * 1994-04-25 1998-10-08 株式会社新潟鉄工所 射出成形機の油圧回路
JPH10203755A (ja) * 1997-01-17 1998-08-04 Hitachi Building Syst Co Ltd 油圧エレベータの異常診断装置
JP4292322B2 (ja) * 1998-06-24 2009-07-08 株式会社アマダ 穴明け機の油圧回路
WO2001053016A1 (fr) * 2000-01-17 2001-07-26 Amada Company, Limited Procede de controle de la vitesse du verin d'une presse a plier, presse a plier mettant en oeuvre ledit procede et procede et appareil de regulation de la position du verin de la presse a plier
JP3783582B2 (ja) * 2001-07-05 2006-06-07 ダイキン工業株式会社 液圧回路装置
US6899012B2 (en) * 2003-05-21 2005-05-31 Actuant Corporation Fluid flow control valve assembly with independent feedback pressure
US6892534B2 (en) * 2003-07-18 2005-05-17 Young & Franklin Inc. Electro-hydrostatic actuator with a failsafe system
CA2476032C (fr) * 2004-08-27 2008-11-04 Westport Research Inc. Commande hydraulique et methode d'exploitation
SE531309C2 (sv) * 2006-01-16 2009-02-17 Volvo Constr Equip Ab Styrsystem för en arbetsmaskin och förfarande för styrning av en hydraulcylinder hos en arbetsmaskin
SE529941C2 (sv) * 2006-05-19 2008-01-08 Nordhydraulic Ab Hydrauliskt system och förfarande för dämpning av svängningar hos en lastbärande kran samt dess användning
US7624671B2 (en) * 2007-02-07 2009-12-01 Sauer-Danfoss Aps Hydraulic actuator for a servomotor with an end lock function
AU2012354296B2 (en) * 2011-12-20 2017-04-13 Syncwind Power Limited Power generating system and hydraulic control system
EP2639657B1 (fr) * 2013-04-24 2018-04-04 MOOG GmbH Saisie d'une grandeur de réglage auxiliaire avec un retard minimal
KR102319371B1 (ko) * 2014-06-20 2021-11-01 파커-한니핀 코포레이션 오버-센터 링키지 시스템에서의 유압 액추에이터의 속도를 제어하는 방법
CN107735530B (zh) * 2015-04-10 2020-06-05 沃尔沃建筑设备公司 用于工程机械的负荷感测液压系统及控制负荷感测液压系统的方法
US10344784B2 (en) * 2015-05-11 2019-07-09 Caterpillar Inc. Hydraulic system having regeneration and hybrid start
EP3109488B1 (fr) * 2015-06-25 2017-12-13 MOOG GmbH Entraînement hydraulique de fonctionnement sécurisé
EP3112698B1 (fr) * 2015-06-30 2019-09-04 Goodrich Actuation Systems SAS Actionneurs électro-hydrauliques
JP6002285B1 (ja) * 2015-07-10 2016-10-05 アイダエンジニアリング株式会社 スライドクッション装置兼用ダイクッション装置及びその制御方法
DE102016113882A1 (de) * 2016-07-27 2018-02-01 Moog Gmbh Elektro-hydrostatisches Antriebssystem
JP6356198B2 (ja) * 2016-10-31 2018-07-11 アイダエンジニアリング株式会社 プレス機械のダイクッション装置
CN106640792A (zh) * 2016-12-26 2017-05-10 中国船舶重工集团公司第七〇九研究所 一种应用于单出杆液压缸压机的直驱式电液伺服系统
DE102017124948A1 (de) * 2017-10-25 2019-04-25 Wessel-Hydraulik Gmbh Hydraulische Schaltungsanordnung
CN108266413B (zh) * 2017-12-15 2021-02-12 中国航空工业集团公司金城南京机电液压工程研究中心 基于压力选择阀的非对称电静液作动器

Also Published As

Publication number Publication date
WO2021104966A1 (fr) 2021-06-03
CN114761221A (zh) 2022-07-15
US20230026318A1 (en) 2023-01-26
EP4065360B1 (fr) 2023-12-20
DE102019131980A1 (de) 2021-05-27
CN114761221B (zh) 2024-06-11

Similar Documents

Publication Publication Date Title
EP4065360A1 (fr) Système électrohydrostatique à capteur de pression
LU87794A1 (fr) Proportional-wegeventil in sitzbauweise
EP2220377A1 (fr) Mécanisme à soupape
DE4108915C2 (de) Hydraulische Einrichtung zur Druckmittelversorgung eines bevorrechtigten Primärlastkreises
DE102012108027A1 (de) Ölpumpenregelungssystem für ein Fahrzeug und Betriebsverfahren davon
EP2698545B1 (fr) Dispositif de commande de l'état de charge d'au moins un accumulateur de pression
EP3816455A1 (fr) Dispositif de commande hydraulique destiné à l'alimentation en fluide de pression d'au moins deux consommateurs hydrauliques
EP2387523A1 (fr) Procédé pour exploiter un système hydraulique ou pneumatique
DE102018202416A1 (de) Verbrauchersteuervorrichtung und Steuerungsverfahren
EP3277551B1 (fr) Dispositif à air comprimé pour des véhicules équipés d'une soupape à double relais
EP3592991A1 (fr) Procédé pour la commande d'un actionneur hydraulique, dispositif de commande et commande d'actionneur
DE102008019148A1 (de) Druckerzeuger einer hydraulischen Fahrzeug-Bremsanlage und Betriebsverfahren
EP2403742A1 (fr) Procédé destiné à faire fonctionner un système hydraulique ou pneumatique
EP3555475A1 (fr) Système de pompe à vide et son procédé de fonctionnement
DE102017104792A1 (de) Systeme und Verfahren zur Kalibrierung elektrohydraulischer Ventile
EP4455488A1 (fr) Dispositif de fonctionnement d'un système d'alimentation hydraulique à commande de charge d'un tracteur agricole
DE102020131046B4 (de) Hydraulisches Hubsystem
DE102015122929A1 (de) Steuerung für ein hydraulisch betätigbares Ventil
DE102014220743A1 (de) Pneumatischer Positionierantrieb, Verfahren zum Betrieb
DE102021005824B4 (de) Sicherheitsventilvorrichtung
EP4130493B1 (fr) Agencement de commande hydraulique
DE102005055309A1 (de) Hydraulische Steuervorrichtung
DE102007057023A1 (de) Aktuatorregelungssystem
EP1264109A1 (fr) Dispositif pour commander un actionneur hydraulique
DE3725635C2 (fr)

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20220427

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

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

RIC1 Information provided on ipc code assigned before grant

Ipc: F15B 20/00 20060101ALI20230622BHEP

Ipc: F15B 7/00 20060101ALI20230622BHEP

Ipc: B30B 15/28 20060101ALI20230622BHEP

Ipc: F15B 11/00 20060101ALI20230622BHEP

Ipc: F15B 13/01 20060101ALI20230622BHEP

Ipc: B30B 15/20 20060101AFI20230622BHEP

INTG Intention to grant announced

Effective date: 20230726

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

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: DE

Ref legal event code: R096

Ref document number: 502020006473

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

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: 20240321

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20231220

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20231220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20231220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20231220

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: 20240321

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: 20231220

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: 20231220

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: 20240320

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: 20231220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20231220

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: 20231220

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: 20240320

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: 20231220

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: 20231220

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: 20231220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20240420

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20231220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20231220

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: 20231220

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: 20231220

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: 20231220

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: 20231220

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: 20240420

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: 20231220

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: 20231220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20231220

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: 20240422

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: 20240422

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: 20231220

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502020006473

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: 20231220

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: SI

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: 20231220

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20231220

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: 20231220

26N No opposition filed

Effective date: 20240923

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: 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: 20231220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20241118

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20241118

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20241130

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20241130

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: 20241130

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20241118

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20241130

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: 20241118

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20251119

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20260113

Year of fee payment: 5

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: 20201118

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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; INVALID AB INITIO

Effective date: 20201118