EP4065360A1 - Elektrohydrostatisches system mit drucksensor - Google Patents
Elektrohydrostatisches system mit drucksensorInfo
- 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
Links
- 239000012530 fluid Substances 0.000 claims abstract description 27
- 238000005242 forging Methods 0.000 claims description 3
- 239000000843 powder Substances 0.000 claims description 3
- 230000001360 synchronised effect Effects 0.000 claims description 3
- 238000013461 design Methods 0.000 description 7
- 238000011156 evaluation Methods 0.000 description 3
- 238000007792 addition Methods 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000007665 sagging Methods 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/024—Pressure relief 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/18—Combined units comprising both motor and pump
-
- 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.
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Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102019131980.3A DE102019131980A1 (de) | 2019-11-26 | 2019-11-26 | Elektrohydrostatisches System mit Drucksensor |
PCT/EP2020/082546 WO2021104966A1 (de) | 2019-11-26 | 2020-11-18 | Elektrohydrostatisches system mit drucksensor |
Publications (2)
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EP4065360A1 true EP4065360A1 (de) | 2022-10-05 |
EP4065360B1 EP4065360B1 (de) | 2023-12-20 |
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EP20811548.5A Active EP4065360B1 (de) | 2019-11-26 | 2020-11-18 | Elektrohydrostatisches system mit drucksensor |
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US (1) | US20230026318A1 (de) |
EP (1) | EP4065360B1 (de) |
CN (1) | CN114761221B (de) |
DE (1) | DE102019131980A1 (de) |
WO (1) | WO2021104966A1 (de) |
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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 |
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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 |
TW514568B (en) * | 2000-01-17 | 2002-12-21 | Amada Co Ltd | Ram speed monitoring method in a press brake and the press brake using the ram speed monitoring method, and ram position control method and ram position controlling device using the ram position control method |
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 |
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CA2476032C (en) * | 2004-08-27 | 2008-11-04 | Westport Research Inc. | Hydraulic drive system and method of operating a hydraulic drive system |
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 |
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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 |
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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 |
-
2019
- 2019-11-26 DE DE102019131980.3A patent/DE102019131980A1/de active Pending
-
2020
- 2020-11-18 WO PCT/EP2020/082546 patent/WO2021104966A1/de active Search and Examination
- 2020-11-18 EP EP20811548.5A patent/EP4065360B1/de active Active
- 2020-11-18 CN CN202080082101.1A patent/CN114761221B/zh active Active
- 2020-11-18 US US17/779,622 patent/US20230026318A1/en active Pending
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US20230026318A1 (en) | 2023-01-26 |
CN114761221B (zh) | 2024-06-11 |
WO2021104966A1 (de) | 2021-06-03 |
DE102019131980A1 (de) | 2021-05-27 |
EP4065360B1 (de) | 2023-12-20 |
CN114761221A (zh) | 2022-07-15 |
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