EP3839256B1 - Method for operating a variable-speed adjustable pump - Google Patents
Method for operating a variable-speed adjustable pump Download PDFInfo
- Publication number
- EP3839256B1 EP3839256B1 EP20213692.5A EP20213692A EP3839256B1 EP 3839256 B1 EP3839256 B1 EP 3839256B1 EP 20213692 A EP20213692 A EP 20213692A EP 3839256 B1 EP3839256 B1 EP 3839256B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- speed
- setpoint
- soll
- variable
- working cycle
- 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.)
- Active
Links
- 238000000034 method Methods 0.000 title claims description 22
- 238000006073 displacement reaction Methods 0.000 claims description 58
- 230000008859 change Effects 0.000 claims description 19
- 230000007246 mechanism Effects 0.000 claims description 11
- 230000001105 regulatory effect Effects 0.000 claims description 9
- 238000004590 computer program Methods 0.000 claims description 5
- 230000006978 adaptation Effects 0.000 claims description 4
- 238000005457 optimization Methods 0.000 claims description 3
- 230000006399 behavior Effects 0.000 description 7
- 230000006870 function Effects 0.000 description 4
- 239000000654 additive Substances 0.000 description 3
- 230000000996 additive effect Effects 0.000 description 3
- 238000013459 approach Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000015654 memory Effects 0.000 description 2
- 230000004913 activation Effects 0.000 description 1
- 230000003321 amplification Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 238000005070 sampling Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
- F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
- F04B49/065—Control using electricity and making use of computers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
- F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2203/00—Motor parameters
- F04B2203/02—Motor parameters of rotating electric motors
- F04B2203/0209—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
- F15B2211/20—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
- F15B2211/20546—Type of pump variable capacity
-
- 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
- F15B2211/20561—Type of pump reversible
-
- 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
- F15B2211/60—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
- F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply 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
- F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6333—Electronic controllers using input signals representing a state of the pressure source, e.g. swash plate angle
-
- 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
- F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
-
- 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
- F15B2211/6653—Pressure control
-
- 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
- F15B2211/6654—Flow rate control
-
- 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
- F15B2211/6656—Closed loop control, i.e. control using feedback
-
- 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
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/765—Control of position or angle of the output member
- F15B2211/7656—Control of position or angle of the output member with continuous position control
Definitions
- the present invention relates to a method for operating a variable-speed variable-speed pump, in which a delivery mechanism that can be adjusted in terms of a displacement volume per working cycle is driven by means of a variable-speed drive, and an electrohydraulic system.
- Pumps on which the invention is based have a delivery system with variable displacement volume per working cycle (so-called hydraulic displacement machine, e.g. axial piston machine), which is driven by a drive with variable speed.
- hydraulic displacement machine e.g. axial piston machine
- the volumetric flow and/or the delivery pressure are usually regulated by appropriately adjusting the displacement volume of the delivery system and the speed, i.e. such pumps have two degrees of freedom in regulation.
- the invention deals with the operation of a variable-speed variable displacement pump, such as in particular an axial piston pump with e.g. two-point adjustment or proportional adjustment, in which a displacement mechanism that can be adjusted in a displacement volume per working cycle is driven by means of a variable-speed drive such as an electric motor.
- a so-called swash plate for example, can be provided to adjust the conveying mechanism.
- At least one variable such as a pressure
- a target value the at least one variable
- the at least one variable is preferably selected from a pressure and/or a volume flow of a medium such as oil, with which the variable displacement pump is operated (or which is used as the operating medium), a force that is generated directly or indirectly by the medium, and a position of an element moved directly or indirectly through the medium.
- force and position can relate not only to the variable displacement pump and drive system, but also to a higher level system in which the variable displacement pump and drive is used, e.g. an electro-hydraulic axle or an electro-hydraulic system in general.
- the parameter determining the displacement volume per working cycle can be a swivel angle - e.g. in the case of the mentioned axial piston pump with swivel disk.
- an adjustment of the swivel angle causes a change in the stroke of the individual pistons in the delivery system of the pump and thus the displacement volume per working cycle by changing the angle of attack of the swivel disk.
- variable displacement pump with a specific, in particular small, displacement volume per working cycle is expedient and, in particular, energy-efficient. This is based on the fact that - at least with constant pressure - the required torque drops. If now during operation the need for a change or adjustment of the displacement volume per cycle - recognized and initiated - via the corresponding parameter such as the swivel angle, then a readjustment of the Speed is necessary in order - as is often desired - to keep the (superordinate) controlled at least one variable such as the pressure (as much as possible) constant.
- the speed setpoint (and preferably also a torque setpoint) when there is a change in the setpoint for the characteristic variable that determines the displacement volume per working cycle by way of a pilot control as a function of a dynamic or speed of an adjustment of the conveyor, in particular also working point dependent, is adjusted.
- This pre-control of the speed setpoint which takes place in particular parallel to the change or adaptation of the displacement volume per working cycle, makes it possible to prevent a readjustment of the speed and thus also a possible drop in pressure.
- the (higher-level) controller does not have to intervene at all, rather the relevant at least one variable remains constant. This is particularly effective when a change or adaptation of the speed of the drive takes place or can take place faster than a change or adjustment of the displacement volume per working cycle.
- the specification of the speed setpoint and/or the adjustment of the speed setpoint and/or the specification of the setpoint for the characteristic variable that determines the displacement volume per working cycle is preferably carried out using a model in which the speed of the adjustment of the conveying mechanism is taken into account, and particularly preferably using a model predictive control (with such a model).
- a model predictive control (MPC) enables a particularly simple and precise and therefore also efficient control, in particular because the non-linear behavior of the present electrohydraulic system with variable displacement pump and drive can be mapped particularly well.
- Model predictive control is a control concept that is already being used in industry. A very high control quality is achieved by predicting the future system behavior in each sampling step, i.e. a specific time interval. In contrast to classic control concepts, input, output and state restrictions can be explicitly taken into account. The effect of changing the controller parameters on the system behavior is usually very intuitive. For the realization of the computationally intensive control concept for fast mechatronic systems, approaches such as move blocking to reduce the optimization parameters on the prediction horizon, or other approaches such as explicit model predictive control can be used.
- the speed of the adjustment of the conveyor system is preferably taken into account using at least one of the following parameters: a maximum possible displacement volume per working cycle, a minimum possible displacement volume per working cycle, a pressure of a medium with which the variable displacement pump is operated, an actual value of the Speed of the drive, a viscosity of the medium, and mechanical and/or electrical parameters of an adjustment system of the variable displacement pump.
- the maximum and the minimum possible displacement volume per working cycle can also be taken into account as a quotient.
- the speed of the adjustment of the conveying system is preferably taken into account as a modeled actual value for the characteristic variable that determines the displacement volume per working cycle.
- a speed correction value can be derived from this modeled actual value (e.g. an additive speed value) to adjust the speed setpoint.
- the speed setpoint is preferably further adjusted as a function of at least one optimization criterion, which is selected in particular from: a noise generated by the variable displacement pump, an efficiency of the variable displacement pump, and a utilization of the drive. This allows the operation to be further optimized, especially when the pump is operated at partial load.
- a torque setpoint for the drive when there is a change in the setpoint for the characteristic variable that determines the displacement volume per working cycle, by means of a pre-control as a function of the dynamics or speed of an adjustment of the conveying mechanism, in particular also as a function of the operating point, is adjusted.
- a product of the modeled actual value for the parameter determining the displacement volume per working cycle and the actual pressure can flow in here, i.e. in particular a modeled value for a hydraulic moment is pre-controlled.
- the points presented above then also apply to the torque pre-control.
- the pilot control of a torque value is particularly advantageous if, during the operation of an electric drive, a torque controller is subordinate to the speed controller.
- a computing unit for example a control and/or regulating unit for a variable-speed variable-speed pump with a variable-speed drive, is set up, in particular in terms of programming, to carry out a method according to the invention.
- the subject of the invention is also an electrohydraulic drive system such as an electrohydraulic axle comprising a variable-speed variable displacement pump with a variable-speed drive and a computing unit according to the invention.
- Suitable data carriers for providing the computer program are, in particular, magnetic, optical and electrical memories, such as hard drives, flash memories, EEPROMs, DVDs, etc. It is also possible to download a program via computer networks (Internet, intranet, etc.).
- FIG 1 is an electrohydraulic system 100, as it may be the basis of the invention, shown schematically.
- the electrohydraulic system 100 has an actuator designed as a hydraulic cylinder 110 with a piston 111 that can move along an x-axis and is actuated by a variable-speed variable-speed pump 120 .
- a hydraulic circuit 130 with, for example, oil as the medium or operating medium is arranged between the variable-speed variable displacement pump 120 and the hydraulic cylinder 110 .
- the variable-speed variable-speed pump 120 has a variable-speed drive designed as an electric motor 121 and a delivery system 122 and is designed in particular as an axial piston pump with a swashplate design.
- a swashplate By adjusting the angle of the swashplate, i.e. the so-called slewing angle, the displacement volume of the conveyor system can be changed for each working cycle.
- a control and/or regulating unit 140 is programmed to carry out a preferred embodiment of a method according to the invention and specifies a speed setpoint n setpoint and a swivel angle setpoint ⁇ setpoint as a setpoint for the parameter determining the displacement volume per working cycle. Feedback of the actual values n actual and ⁇ actual is provided for controlling the manipulated variables. This can be accomplished using conventional sensors, for example.
- FIG 2 a control circuit according to a preferred embodiment of the invention or a method according to the invention is shown, as it can be implemented in terms of programming in a control and/or regulating unit.
- a pressure p actual in a hydraulic circuit 130 as is shown, for example, in figure 1 is shown , regulated to a setpoint p setpoint.
- a speed setpoint n' set or n set (the difference between these set values will be discussed later) for a speed of drive 121 and a set value ⁇ set for a swivel angle than the determines or presets the characteristic that determines the displacement volume per working cycle.
- These setpoint values for the rotational speed and swivel angle are then converted accordingly in the drive 121 or in the conveyor 122.
- Drive 121 and swivel angle adjustment of the conveying system 122 usually react to the setpoint specifications in accordance with a PT1 behavior with corresponding time constants T1 or T2.
- the swivel angle or generally the displacement volume per working cycle of the conveying system is to be changed, e.g of the conveyor and adjusted by means of a pre-control, so that the (adapted) speed setpoint n target is obtained, which is then used further.
- a ratio or quotient of the maximum possible to the minimum possible swivel angle can be included in the determination of the adjusted speed setpoint, which in turn can depend on a current swivel angle, which here - through the model - as an estimated or calculated value ⁇ * is taken into account.
- the type of adjustment or the adjustment system for the swivel angle can also have an effect on the speed.
- an electronic swivel angle adjustment can be provided, in which a magnetic force is generated by means of electricity, which counteracts a (mechanical) spring force in an adjustment cylinder.
- FIG 3 a control circuit according to a further preferred embodiment of the invention or a method according to the invention is shown, as it can be implemented in terms of programming in a control and/or regulation unit.
- a pressure p actual in a hydraulic circuit 130, as is shown, for example, in FIG figure 1 is shown , regulated to a setpoint p setpoint.
- a speed setpoint n setpoint for a speed of the drive 121 is determined or specified as a manipulated variable by a controller which is also designed here as a PI controller 150 .
- a speed error e n is calculated from the speed setpoint n setpoint , taking into account a correction or pre-control term ⁇ n* (this will be discussed later) by subtracting the actual speed value n actual and fed to a speed controller 151 (here also designed as a PI controller), which outputs a setpoint torque M setpoint and acts on the drive 121, which is again modeled with a PT1 behavior. This then results in an electric drive torque M A of the pump 120.
- a swivel angle ⁇ is specified as the parameter determining the displacement volume per working cycle for the conveyor 122, whose swivel angle adjustment is again modeled with a PT1 behavior, from which the swivel angle (or a corresponding volume variable) ⁇ * results.
- An effective torque M eff of the pump 120 which acts on the speed, results from the drive torque MA, taking into account a hydraulic torque M hyd to be overcome.
- the hydraulic moment M hyd results as above as the product of the volume variable ⁇ * and the actual pressure, which can be weighted or amplified via a P element if necessary.
- the product of the speed n actual and the volume variable ⁇ * results in a volume flow Q, which can optionally be weighted or amplified via a P element, and then in the hydraulic circuit 130 taking into account the compression factor and volume of the medium that is compressed , the corresponding actual pressure pist.
- the speed setpoint n setpoint initially determined or specified by the controller 150 is changed adjusted by means of a pre-control with the correction or pre-control term ⁇ n*.
- the pre-control term ⁇ n* is determined in particular within the framework of a model-predictive control 160 with a corresponding model (often also referred to as "DigitalTwin") for the variable displacement pump (whose swivel angle reaction to the swivel angle specification ⁇ is modeled within block 160 with a PT1 behavior).
- the resulting modeled actual swivel angle is fed via a P element for weighting or amplification and applied to the speed setpoint n set as an additive speed value ⁇ n *.
- the modeled actual swivel angle (or the volume) is multiplied by the actual pressure via a P-element and applied to the torque setpoint M set as an additive torque value M* hyd .
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Computer Hardware Design (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Description
Die vorliegende Erfindung betrifft ein Verfahren zum Betreiben einer drehzahlvariablen Verstellpumpe, bei der ein in einem Verdrängervolumen je Arbeitsspiel verstellbares Förderwerk mittels eines drehzahlvariablen Antriebs angetrieben wird, sowie ein elektrohydraulisches System.The present invention relates to a method for operating a variable-speed variable-speed pump, in which a delivery mechanism that can be adjusted in terms of a displacement volume per working cycle is driven by means of a variable-speed drive, and an electrohydraulic system.
Der Erfindung zugrunde liegende Pumpen weisen ein Förderwerk mit variablem Verdrängervolumen pro Arbeitsspiel (sog. hydraulische Verdrängermaschine, z.B. Axialkolbenmaschine) auf, welches mittels eines Antriebs mit variabler Drehzahl angetrieben wird. Beim Betrieb solcher Pumpen werden üblicherweise der Volumenstrom und/oder der Förderdruck (d.h. Druckdifferenz zwischen Zulauf und Ablauf) durch entsprechende Anpassung des Verdrängervolumens des Förderwerks und der Drehzahl geregelt, d.h. solche Pumpen besitzen zwei Freiheitsgrade bei der Regelung.Pumps on which the invention is based have a delivery system with variable displacement volume per working cycle (so-called hydraulic displacement machine, e.g. axial piston machine), which is driven by a drive with variable speed. When such pumps are operated, the volumetric flow and/or the delivery pressure (i.e. pressure difference between inlet and outlet) are usually regulated by appropriately adjusting the displacement volume of the delivery system and the speed, i.e. such pumps have two degrees of freedom in regulation.
Aus der
Erfindungsgemäß werden ein Verfahren und ein elektrohydraulisches System mit den Merkmalen der unabhängigen Patentansprüche vorgeschlagen. Vorteilhafte Ausgestaltungen sind Gegenstand der Unteransprüche sowie der nachfolgenden Beschreibung.According to the invention, a method and an electrohydraulic system with the features of the independent patent claims are proposed. Advantageous configurations are the subject of the dependent claims and the following description.
Die Erfindung beschäftigt sich mit dem Betreiben einer drehzahlvariablen Verstellpumpe wie insbesondere einer Axialkolbenpumpe mit z.B. Zweipunktverstellung oder Proportionalverstellung, bei der ein in einem Verdrängervolumen je Arbeitsspiel verstellbares Förderwerk mittels eines drehzahlvariablen Antriebs wie z.B. eines Elektromotors angetrieben wird. Zur Verstellung des Förderwerks kann bei einer solchen Verstellpumpe z.B. eine sog. Schwenkscheibe vorgesehen sein.The invention deals with the operation of a variable-speed variable displacement pump, such as in particular an axial piston pump with e.g. two-point adjustment or proportional adjustment, in which a displacement mechanism that can be adjusted in a displacement volume per working cycle is driven by means of a variable-speed drive such as an electric motor. In such a variable displacement pump, a so-called swash plate, for example, can be provided to adjust the conveying mechanism.
Beim Betrieb einer solchen Verstellpumpe wird in aller Regel im Rahmen einer Regelung wenigstens eine Größe, wie z.B. ein Druck, durch Vorgabe eines Drehzahlsollwerts für eine Drehzahl des Antriebs und eines Sollwerts für eine das Verdrängervolumen je Arbeitsspiel bestimmende Kenngröße auf einen Sollwert (der wenigstens einen Größe) geregelt.When operating such a variable displacement pump, at least one variable, such as a pressure, is usually adjusted to a target value (the at least one variable ) regulated.
Bevorzugt ist die wenigstens eine Größe ausgewählt aus einem Druck und/oder einem Volumenstrom eines Mediums wie z.B. Öl, mit dem die Verstellpumpe betrieben wird (bzw. das als Betriebsmedium verwendet wird), einer Kraft, die direkt oder indirekt durch das Medium erzeugt wird, und einer Position eines Elements, das direkt oder indirekt durch das Medium bewegt wird. Insbesondere Kraft und Position können sich nicht nur auf das System mit Verstellpumpe und Antrieb, sondern auch auf ein übergeordnetes System beziehen, in dem die Verstellpumpe mit dem Antrieb verwendet wird, z.B. eine elektrohydraulische Achse oder allgemein ein elektrohydraulisches System.The at least one variable is preferably selected from a pressure and/or a volume flow of a medium such as oil, with which the variable displacement pump is operated (or which is used as the operating medium), a force that is generated directly or indirectly by the medium, and a position of an element moved directly or indirectly through the medium. In particular, force and position can relate not only to the variable displacement pump and drive system, but also to a higher level system in which the variable displacement pump and drive is used, e.g. an electro-hydraulic axle or an electro-hydraulic system in general.
Bei der das Verdrängervolumen je Arbeitsspiel bestimmenden Kenngröße kann es sich - z.B. im Falle der erwähnten Axialkolbenpumpe mit Schwenkscheibe - um einen Schwenkwinkel handeln. Eine Verstellung des Schwenkwinkels bewirkt in diesem Beispiel durch eine Veränderung des Anstellwinkels der Schwenkscheibe eine Änderung des Hubs der einzelnen Kolben im Förderwerk der Pumpe und damit des Verdrängervolumens je Arbeitsspiel.The parameter determining the displacement volume per working cycle can be a swivel angle - e.g. in the case of the mentioned axial piston pump with swivel disk. In this example, an adjustment of the swivel angle causes a change in the stroke of the individual pistons in the delivery system of the pump and thus the displacement volume per working cycle by changing the angle of attack of the swivel disk.
Es hat sich gezeigt, dass je nach Situation der Betrieb der Verstellpumpe mit einem bestimmten, insbesondere geringen, Verdrängervolumen je Arbeitsspiel zweckmäßig und insbesondere energieeffizient ist. Dies basiert darauf, dass - zumindest bei konstantem Druckdas nötige Drehmoment sinkt. Wird nun während des Betriebs der Bedarf nach einer Veränderung bzw. Anpassung des Verdrängervolumen je Arbeitsspiel - über die entsprechende Kenngröße wie den Schwenkwinkel - erkannt und veranlasst, so ist eine Nachregelung der Drehzahl nötig, um - wie oftmals erwünscht - die (übergeordnet) zu regelnde wenigstens eine Größe wie den Druck (möglichst) konstant zu halten.It has been shown that, depending on the situation, operating the variable displacement pump with a specific, in particular small, displacement volume per working cycle is expedient and, in particular, energy-efficient. This is based on the fact that - at least with constant pressure - the required torque drops. If now during operation the need for a change or adjustment of the displacement volume per cycle - recognized and initiated - via the corresponding parameter such as the swivel angle, then a readjustment of the Speed is necessary in order - as is often desired - to keep the (superordinate) controlled at least one variable such as the pressure (as much as possible) constant.
Es hat sich nun jedoch herausgestellt, dass eine solche Veränderung bzw. Anpassung des Verdrängervolumens je Arbeitsspiel Rückwirkungen auf die (übergeordnete) zu regelnde Größe bzw. deren Istwert hat, sodass hier eine Nachregelung dieser wenigstens eine Größe nötig wird bzw. der entsprechende Regler eingreifen muss. Dies liegt, wie erkannt wurde, darin begründet, dass die Drehzahldynamik des Antriebs meist nicht gut genug ist, um die Verstellung des Verdrängervolumens je Arbeitsspiel entsprechend schnell auszugleichen, was z.B. zu einem Druckeinbruch führen kann.However, it has now been found that such a change or adjustment of the displacement volume per working cycle has repercussions on the (superordinate) variable to be controlled or its actual value, so that a readjustment of this at least one variable is necessary or the corresponding controller has to intervene . As has been recognized, this is due to the fact that the speed dynamics of the drive are usually not good enough to quickly compensate for the adjustment of the displacement volume per working cycle, which can lead to a drop in pressure, for example.
Im Rahmen der Erfindung wird nun vorgeschlagen, dass der Drehzahlsollwert (und vorzugsweise auch ein Momentensollwert) bei einer Änderung des Sollwerts für die das Verdrängervolumen je Arbeitsspiel bestimmende Kenngröße im Wege einer Vorsteuerung in Abhängigkeit von einer Dynamik bzw. Geschwindigkeit einer Verstellung des Förderwerk, insbesondere auch arbeitspunktabhängig, angepasst wird. Durch diese insbesondere parallel zur Veränderung bzw. Anpassung des Verdrängervolumens je Arbeitsspiel erfolgende Vorsteuerung des Drehzahlsollwerts kann eine Nachregelung der Drehzahl und somit auch eine etwaiger Druckeinbruch verhindert werden. Der (übergeordnete) Regler muss also gar nicht eingreifen, vielmehr bleibt die betreffende wenigstens eine Größe konstant. Dies ist besonders effektiv, wenn eine Veränderung bzw. Anpassung der Drehzahl des Antriebs schneller erfolgt bzw. erfolgen kann als eine Veränderung bzw. Anpassung des Verdrängervolumens je Arbeitsspiel.In the context of the invention, it is now proposed that the speed setpoint (and preferably also a torque setpoint) when there is a change in the setpoint for the characteristic variable that determines the displacement volume per working cycle by way of a pilot control as a function of a dynamic or speed of an adjustment of the conveyor, in particular also working point dependent, is adjusted. This pre-control of the speed setpoint, which takes place in particular parallel to the change or adaptation of the displacement volume per working cycle, makes it possible to prevent a readjustment of the speed and thus also a possible drop in pressure. The (higher-level) controller does not have to intervene at all, rather the relevant at least one variable remains constant. This is particularly effective when a change or adaptation of the speed of the drive takes place or can take place faster than a change or adjustment of the displacement volume per working cycle.
Die Vorgabe des Drehzahlsollwerts und/oder die Anpassung des Drehzahlsollwerts und/oder die Vorgabe des Sollwerts für die das Verdrängervolumen je Arbeitsspiel bestimmende Kenngröße erfolgt vorzugsweise unter Verwendung eines Modells, in dem die Geschwindigkeit der Verstellung des Förderwerks berücksichtigt wird, und besonders bevorzugt unter Verwendung einer modellprädiktiven Regelung (mit einem solchen Modell). Eine modellprädiktive Regelung (engl. "Model Predictive Control", MPC) ermöglicht eine besonders einfache und genaue und damit auch effiziente Regelung, insbesondere deshalb, da das nichtlineare Verhalten des hier vorliegenden elektrohydraulischen Systems mit Verstellpumpe und Antrieb besonders gut abgebildet werden kann.The specification of the speed setpoint and/or the adjustment of the speed setpoint and/or the specification of the setpoint for the characteristic variable that determines the displacement volume per working cycle is preferably carried out using a model in which the speed of the adjustment of the conveying mechanism is taken into account, and particularly preferably using a model predictive control (with such a model). A model predictive control (MPC) enables a particularly simple and precise and therefore also efficient control, in particular because the non-linear behavior of the present electrohydraulic system with variable displacement pump and drive can be mapped particularly well.
Die modellprädiktive Regelung ist ein Regelungskonzept, welches bereits Anwendung in der Industrie findet. Durch die Prädiktion des zukünftigen Systemverhaltens in jedem Abtastschritt, d.h. einem bestimmten Zeitintervall, wird eine sehr hohe Regelungsgüte erzielt. Im Gegensatz zu klassischen Regelungskonzepten können Eingangs-, Ausgangs- und Zustandsbeschränkungen explizit berücksichtigt werden. Die Auswirkung einer Veränderung der Reglerparameter auf das Systemverhalten ist zumeist sehr intuitiv. Zur Realisierung des rechenaufwendigen Regelungskonzeptes für schnelle mechatronische Systeme können Ansätze wie das Move-Blocking zur Reduktion der Optimierungsparameter auf dem Prädiktionshorizont, oder weitere Ansätze wie die explizite modellprädiktive Regelung verwendet werden.Model predictive control is a control concept that is already being used in industry. A very high control quality is achieved by predicting the future system behavior in each sampling step, i.e. a specific time interval. In contrast to classic control concepts, input, output and state restrictions can be explicitly taken into account. The effect of changing the controller parameters on the system behavior is usually very intuitive. For the realization of the computationally intensive control concept for fast mechatronic systems, approaches such as move blocking to reduce the optimization parameters on the prediction horizon, or other approaches such as explicit model predictive control can be used.
In dem erwähnten Modell wird die Geschwindigkeit der Verstellung des Förderwerks bevorzugt unter Verwendung wenigstens einer der folgenden Parameter berücksichtigt: einem maximal möglichen Verdrängervolumen je Arbeitsspiel, einem minimal möglichen Verdrängervolumen je Arbeitsspiel, einem Druck eines Mediums, mit dem die Verstellpumpe betrieben wird, einem Istwert der Drehzahl des Antriebs, einer Viskosität des Mediums, und mechanische und/oder elektrische Parameter eines Verstellsystems der Verstellpumpe. Das maximal und das minimal mögliche Verdrängervolumen je Arbeitsspiel können auch als ein Quotient berücksichtigt werden.In the model mentioned, the speed of the adjustment of the conveyor system is preferably taken into account using at least one of the following parameters: a maximum possible displacement volume per working cycle, a minimum possible displacement volume per working cycle, a pressure of a medium with which the variable displacement pump is operated, an actual value of the Speed of the drive, a viscosity of the medium, and mechanical and/or electrical parameters of an adjustment system of the variable displacement pump. The maximum and the minimum possible displacement volume per working cycle can also be taken into account as a quotient.
Diese Parameter beeinflussen, typischerweise in verschiedenem Maße, die Geschwindigkeit der Verstellung des Förderwerks, d.h. wie schnell oder langsam die Verstellung nach Ansteuerung erfolgen wird. Je nach aktueller Geschwindigkeit der Verstellung des Förderwerks - im Falle einer Axialkolbenpumpe mit Schwenkscheibe auch als Schwenkwinkelgeschwindigkeit bezeichnet - wird eine Umsetzung einer Veränderung des Verdrängervolumens je Arbeitsspiel schneller oder langsamer erfolgen, was auch Einfluss auf die Angleichung der Drehzahl des Antriebs hat. Bei langsamer Verstellung des Verdrängervolumens je Arbeitsspiel - also geringer Dynamik bzw. Geschwindigkeit - ist beispielsweise eine geringere oder geringer ansteigende Vorsteuerung der Drehzahl nötig als bei hoher Geschwindigkeit.These parameters affect, typically to varying degrees, the speed of displacement of the conveyor, i.e. how fast or slow the displacement will be after activation. Depending on the current speed of the adjustment of the conveyor - in the case of an axial piston pump with a swash plate also referred to as the slewing angle speed - a change in the displacement volume per working cycle will be implemented faster or slower, which also has an influence on the adjustment of the speed of the drive. With slow adjustment of the displacement volume per working cycle - ie low dynamics or speed - for example a lower or less increasing pre-control of the speed is necessary than at high speed.
In dem erwähnten Modell wird die Geschwindigkeit der Verstellung des Förderwerks bevorzugt als modellierter Istwert für die das Verdrängervolumen je Arbeitsspiel bestimmende Kenngröße berücksichtigt. Aus diesem modellierten Istwert kann insbesondere ein Drehzahlkorrekturwert (z.B. ein additiver Drehzahlwert) zur Anpassung des Drehzahlsollwerts bestimmt werden.In the model mentioned, the speed of the adjustment of the conveying system is preferably taken into account as a modeled actual value for the characteristic variable that determines the displacement volume per working cycle. In particular, a speed correction value can be derived from this modeled actual value (e.g. an additive speed value) to adjust the speed setpoint.
Vorzugsweise wird der Drehzahlsollwert bei einer Änderung des Sollwerts für die das Verdrängervolumen je Arbeitsspiel bestimmende Kenngröße weiterhin in Abhängigkeit von wenigstens einem Optimierungskriterium angepasst, das insbesondere ausgewählt ist aus: einem von der Verstellpumpe erzeugten Geräusch, einer Effizienz der Verstellpumpe, und einer Auslastung des Antriebs. Hiermit lässt sich der Betrieb weiter optimieren, insbesondere wenn die Pumpe in Teillast betrieben wird.When there is a change in the setpoint for the characteristic variable that determines the displacement volume per working cycle, the speed setpoint is preferably further adjusted as a function of at least one optimization criterion, which is selected in particular from: a noise generated by the variable displacement pump, an efficiency of the variable displacement pump, and a utilization of the drive. This allows the operation to be further optimized, especially when the pump is operated at partial load.
Je nachdem ob nun z.B. ein Aus- oder Einschwenkvorgang der Verstellpumpe (bzw. der Schwenkscheibe) eingeleitet werden soll, wird zweckmäßigerweise abhängig von der Schwenkrichtung (d.h. in Richtung höheres oder geringeres Verdrängervolumen), Systemparametern, sonstigen Komponentenparametern und/oder aktuellen Zuständen des (elektrohydraulischen) Systems eine Soll-Trajektorie für die Drehzahl und das notwendige Veränderungsdrehmoment ermittelt. Gleichzeitig wird dann insbesondere das sich verändernde hydraulische Moment z.B. abhängig vom aktuellen Druck und einem Modell der Änderung des Fördervolumens der Pumpe, direkt vorgesteuert.Depending on whether, e.g ) system determines a target trajectory for the speed and the necessary torque change. At the same time, the changing hydraulic torque, e.g. depending on the current pressure and a model of the change in the delivery volume of the pump, is then directly pre-controlled.
Zusätzlich zum Vorsteuern der Drehzahl ist vorzugsweise vorgesehen, dass auch ein Momentensollwert für den Antrieb bei einer Änderung des Sollwerts für die das Verdrängervolumen je Arbeitsspiel bestimmende Kenngröße im Wege einer Vorsteuerung in Abhängigkeit von einer Dynamik bzw. Geschwindigkeit einer Verstellung des Förderwerks, insbesondere auch arbeitspunktabhängig, angepasst wird. Insbesondere kann hier ein Produkt aus dem modellierten Istwert für die das Verdrängervolumen je Arbeitsspiel bestimmende Kenngröße und dem Istdruck einfließen, d.h. insbesondere ein modellierter Wert für ein hydraulisches Moment wird vorgesteuert. Die oben dargestellten Punkte gelten dann ebenso für die Momentenvorsteuerung. Das Vorsteuern eines Momentenwerts ist insbesondere vorteilhaft, wenn beim Betrieb eines elektrischen Antriebs dem Drehzahlregler ein Drehmomentregler unterlagert ist.In addition to the pre-control of the speed, it is preferably provided that a torque setpoint for the drive, when there is a change in the setpoint for the characteristic variable that determines the displacement volume per working cycle, by means of a pre-control as a function of the dynamics or speed of an adjustment of the conveying mechanism, in particular also as a function of the operating point, is adjusted. In particular, a product of the modeled actual value for the parameter determining the displacement volume per working cycle and the actual pressure can flow in here, i.e. in particular a modeled value for a hydraulic moment is pre-controlled. The points presented above then also apply to the torque pre-control. The pilot control of a torque value is particularly advantageous if, during the operation of an electric drive, a torque controller is subordinate to the speed controller.
Eine erfindungsgemäße Recheneinheit, z.B. eine Steuer- und/oder Regeleinheit für eine drehzahlvariable Verstellpumpe mit drehzahlvariablem Antrieb, ist, insbesondere programmtechnisch, dazu eingerichtet, ein erfindungsgemäßes Verfahren durchzuführen.A computing unit according to the invention, for example a control and/or regulating unit for a variable-speed variable-speed pump with a variable-speed drive, is set up, in particular in terms of programming, to carry out a method according to the invention.
Gegenstand der Erfindung ist weiterhin ein elektrohydraulisches Antriebssystem wie z.B. eine elektrohydraulische Achse umfassend eine drehzahlvariablen Verstellpumpe mit einem drehzahlvariablen Antrieb sowie eine erfindungsgemäße Recheneinheit.The subject of the invention is also an electrohydraulic drive system such as an electrohydraulic axle comprising a variable-speed variable displacement pump with a variable-speed drive and a computing unit according to the invention.
Auch die Implementierung eines erfindungsgemäßen Verfahrens in Form eines Computerprogramms oder Computerprogrammprodukts mit Programmcode zur Durchführung aller Verfahrensschritte ist vorteilhaft, da dies besonders geringe Kosten verursacht, insbesondere wenn ein ausführendes Steuergerät noch für weitere Aufgaben genutzt wird und daher ohnehin vorhanden ist. Geeignete Datenträger zur Bereitstellung des Computerprogramms sind insbesondere magnetische, optische und elektrische Speicher, wie z.B. Festplatten, Flash-Speicher, EEPROMs, DVDs u.a.m. Auch ein Download eines Programms über Computernetze (Internet, Intranet usw.) ist möglich.The implementation of a method according to the invention in the form of a computer program or computer program product with program code for carrying out all method steps is advantageous because this causes particularly low costs, especially if an executing control unit is also used for other tasks and is therefore available anyway. Suitable data carriers for providing the computer program are, in particular, magnetic, optical and electrical memories, such as hard drives, flash memories, EEPROMs, DVDs, etc. It is also possible to download a program via computer networks (Internet, intranet, etc.).
Weitere Vorteile und Ausgestaltungen der Erfindung ergeben sich aus der Beschreibung und der beiliegenden Zeichnung.Further advantages and refinements of the invention result from the description and the attached drawing.
Es versteht sich, dass die vorstehend genannten und die nachfolgend noch zu erläuternden Merkmale nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Kombinationen oder in Alleinstellung verwendbar sind, ohne den Rahmen der vorliegenden Erfindung zu verlassen.It goes without saying that the features mentioned above and those still to be explained below can be used not only in the combination specified in each case, but also in other combinations or on their own, without departing from the scope of the present invention.
Die Erfindung ist anhand eines Ausführungsbeispiels in der Zeichnung schematisch dargestellt und wird im Folgenden unter Bezugnahme auf die Zeichnung ausführlich beschrieben.The invention is shown schematically in the drawing using an exemplary embodiment and is described in detail below with reference to the drawing.
Figurenbeschreibung
- Figur 1
- zeigt schematisch ein elektrohydraulisches System, das erfindungsgemäß betrieben werden kann.
- Figur 2
- zeigt schematisch einen Ablauf eines erfindungsgemäßen Verfahrens einer bevorzugten Ausführungsform als Regelkreis.
- Figur 3
- zeigt schematisch einen Ablauf eines erfindungsgemäßen Verfahrens einer weiteren bevorzugten Ausführungsform als Regelkreis.
- figure 1
- shows schematically an electro-hydraulic system that can be operated according to the invention.
- figure 2
- shows schematically a sequence of a method according to the invention of a preferred embodiment as a control loop.
- figure 3
- shows schematically a sequence of a method according to the invention of a further preferred embodiment as a control loop.
In
Die drehzahlvariable Verstellpumpe 120 weist einen als Elektromotor 121 ausgebildeten drehzahlvariablen Antrieb und ein Förderwerk 122 auf und ist insbesondere als Axialkolbenpumpe in Schwenkscheibenbauweise ausgebildet. Durch Verstellung des Winkels der Schwenkscheibe, also des sog. Schwenkwinkels, kann das Verdrängervolumen des Förderwerks je Arbeitsspiel verändert werden.The variable-speed variable-
Eine Steuer- und/oder Regeleinheit 140 ist programmtechnisch zur Durchführung einer bevorzugten Ausführungsform eines erfindungsgemäßen Verfahrens eingerichtet und gibt einen Drehzahlsollwert nsoll sowie einen Schwenkwinkelsollwert αsoll als einen Sollwert für die das Verdrängervolumen je Arbeitsspiel bestimmende Kenngröße vor. Zur Regelung der Stellgrößen ist jeweils eine Rückführung der Istwerte nist sowie αIst vorgesehen. Dies kann z.B. unter Einsatz herkömmlicher Sensoren bewerkstelligt werden.A control and/or regulating
In
Hierzu werden als Stellgrößen von einem hier als PI-Regler 150 ausgebildeten Regler ein Drehzahlsollwert n'soll bzw. nsoll (auf den Unterschied zwischen diesen Sollwerten wird später eingegangen) für eine Drehzahl des Antriebs 121 und ein Sollwert αsoll für einen Schwenkwinkel als die das Verdrängervolumen je Arbeitsspiel bestimmende Kenngröße ermittelt bzw. vorgegeben. Diese Sollwerte für Drehzahl und Schwenkwinkel werden dann entsprechend im Antrieb 121 bzw. im Förderwerk 122 umgesetzt. Antrieb 121 und Schwenkwinkelverstellung des Förderwerks 122 reagieren auf die Sollvorgaben üblicherweise gemäß einem PT1-Verhalten mit entsprechenden Zeitkonstanten T1 bzw. T2. Dabei erhaltene Istwerte, ein Drehzahlistwert nist und ein Schwenkwinkelistwert αist, ergeben dann einen Volumenstrom Q und dann im Hydraulikkreislauf 130 unter Berücksichtigung von Kompressionsfaktor und Volumen des Mediums, das komprimiert wird, den entsprechenden Istwert pist für den Druck des Mediums im Hydraulikkreislauf 130. Dies hat, über ein zu überwindendes hydraulisches Moment Mhyd, entsprechend auch Einfluss auf die Drehzahl des Antriebs.For this purpose , a speed setpoint n' set or n set (the difference between these set values will be discussed later) for a speed of
Wenn nun der Schwenkwinkel bzw. allgemein das Verdrängervolumen je Arbeitsspiel des Förderwerks z.B. aus Effizienzgründen verändert werden soll, so wird zugleich bzw. parallel hierzu der zunächst von dem Regler 150 ermittelte bzw. vorgegebene Drehzahlsollwert n'soll in Abhängigkeit von einer aktuellen Geschwindigkeit 165 einer Verstellung des Förderwerks und im Wege einer Vorsteuerung angepasst, sodass der (angepasste) Drehzahlsollwert nsoll erhalten wird, der dann weiter verwendet wird. Dies erfolgt insbesondere im Rahmen einer modellprädiktiven Regelung 160 mit einem entsprechenden Modell (oftmals auch als "DigitalTwin" bezeichnet) für die Verstellpumpe.If the swivel angle or generally the displacement volume per working cycle of the conveying system is to be changed, e.g of the conveyor and adjusted by means of a pre-control, so that the (adapted) speed setpoint n target is obtained, which is then used further. This takes place in particular within the framework of a model-
Dabei werden insbesondere auch verschiedene Parameter berücksichtigt. Bei der Geschwindigkeit 165 kann z.B. ein Verhältnis bzw. Quotient von maximal möglichem zu minimal möglichem Schwenkwinkel (oder eines entsprechenden Quotienten der Verdrängervolumina) in die Ermittlung des angepassten Drehzahlsollwerts eingehen, das wiederum von einem aktuellen Schwenkwinkel abhängen kann, was hier - durch das Modell - als Schätzwert oder berechneter Wert α*ist berücksichtigt ist.In particular, various parameters are also taken into account. At the
Ebenso kann die Art der Verstellung bzw. des Verstellsystems für den Schwenkwinkel einen Einfluss auf die Geschwindigkeit haben. So kann beispielsweise eine elektronische Schwenkwinkelverstellung vorgesehen sein, bei der mittels Strom eine Magnetkraft erzeugt wird, die einer (mechanischen) Federkraft in einem Verstellzylinder entgegenwirkt.The type of adjustment or the adjustment system for the swivel angle can also have an effect on the speed. For example, an electronic swivel angle adjustment can be provided, in which a magnetic force is generated by means of electricity, which counteracts a (mechanical) spring force in an adjustment cylinder.
Auf diese Weise wird die Drehzahl zugleich mit dem Schwenkwinkel angepasst und es erfolgt keine Veränderung des Drucks im Hydraulikkreislauf 130, sodass kein Eingriff des (übergeordneten) Reglers 150 nötig ist. An dieser Stelle sei angemerkt, dass als die (übergeordnet) zu regelnde Größe anstatt des Drucks z.B. auch die Position x des Elements bzw. Kolbens 111 gemäß
In
Hierzu wird als Stellgröße von einem hier ebenfalls als PI-Regler 150 ausgebildeten Regler ein Drehzahlsollwert nsoll für eine Drehzahl des Antriebs 121 ermittelt bzw. vorgegeben. Aus dem Drehzahlsollwert nsoll wird unter Berücksichtigung eines Korrektur- bzw. Vorsteuerterms Δn* (auf diesen wird später eingegangen) durch Abzug des Drehzahlistwerts nist ein Drehzahlfehler en berechnet und einem Drehzahlregler 151 (hier ebenfalls als PI-Regler ausgeführt) zugeführt, der ein Sollmoment Msoll ausgibt und auf den Antrieb 121, der wieder mit einem PT1-Verhalten modelliert ist, einwirkt. Hieraus ergibt sich dann ein elektrisches Antriebsmoment MA der Pumpe 120.For this purpose , a speed setpoint n setpoint for a speed of the
Ebenso wird ein Schwenkwinkel α als die das Verdrängervolumen je Arbeitsspiel bestimmende Kenngröße dem Förderwerk 122, dessen Schwenkwinkelverstellung wieder mit einem PT1-Verhalten modelliert ist, vorgegeben, woraus sich der Schwenkwinkel (bzw. eine entsprechende Volumengröße) α* ergibt.Likewise, a swivel angle α is specified as the parameter determining the displacement volume per working cycle for the
Aus dem Antriebsmoment MA ergibt sich unter Berücksichtigung eines zu überwindenden hydraulischen Moments Mhyd ein effektives Moment Meff der Pumpe 120, welches auf die Drehzahl wirkt. Dabei ergibt sich das hydraulische Moment Mhyd wie oben als Produkt aus Volumengröße α* und Istdruck, welches ggf. über ein P-Glied gewichtet bzw. verstärkt werden kann.An effective torque M eff of the
Aus dem Produkt der Drehzahl nist und der Volumengröße α* ergibt sich ein Volumenstrom Q, welcher ggf. über ein P-Glied gewichtet bzw. verstärkt werden kann, und dann im Hydraulikkreislauf 130 unter Berücksichtigung von Kompressionsfaktor und Volumen des Mediums, das komprimiert wird, der entsprechende Istdruck pist.The product of the speed n actual and the volume variable α* results in a volume flow Q, which can optionally be weighted or amplified via a P element, and then in the
Wenn nun der Schwenkwinkel α bzw. allgemein das Verdrängervolumen je Arbeitsspiel des Förderwerks z.B. aus Effizienzgründen verändert werden soll, so wird zugleich bzw. parallel hierzu der zunächst von dem Regler 150 ermittelte bzw. vorgegebene Drehzahlsollwert nsoll im Wege einer Vorsteuerung mit dem Korrektur- bzw. Vorsteuerterm Δn* angepasst. Der Vorsteuerterm Δn* wird insbesondere im Rahmen einer modellprädiktiven Regelung 160 mit einem entsprechenden Modell (oftmals auch als "DigitalTwin" bezeichnet) für die Verstellpumpe (deren Schwenkwinkelreaktion auf die Schwenkwinkelvorgabe α innerhalb des Blocks 160 mit einem PT1-Verhalten modelliert ist), ermittelt. Im vorliegenden Beispiel wird der sich hieraus ergebende modellierte Ist-Schwenkwinkel über ein P-Glied zur Gewichtung bzw. Verstärkung geführt und als additiver Drehzahlwert Δn*auf den Drehzahlsollwert nsoll aufgeschaltet. Gleichzeitig wird der modellierte Ist-Schwenkwinkel (bzw. das Volumen) multipliziert mit dem Istdruck über ein P-Glied geführt und als additiver Momentenwert M*hyd auf den Momentensollwert Msoll aufgeschaltet.If the swivel angle α or, in general, the displacement volume per working cycle of the conveying mechanism is to be changed, for example for reasons of efficiency, then at the same time or parallel to this, the speed setpoint n setpoint initially determined or specified by the
Durch das beschriebene Schema können im Falle der Anpassung bzw. Variation einer Übersetzung (also des Schwenkwinkels) im Hydraulikkreislauf bestimmte Einflüsse berücksichtigt werden. Einer Änderung der Verstärkung des offenen Regelkreises kann durch eine Anpassung der Verstärkung kp im Druckregler 150 begegnet werden, einer Änderung des Volumenstroms Q des Mediums durch eine Anpassung der Drehzahl der Pumpe (über Δn*), und einer Änderung des hydraulischen Moments durch eine Anpassung des Sollmoments (über M*hyd) für den Antrieb. Dies kann entsprechend im erwähnten Modell bzw. in der modellprädiktiven Regelung berücksichtigt werden. Im Vergleich zum Beispiel aus
Claims (12)
- Method for operating a variable-speed adjustable pump (120), in which a delivery mechanism (122) that can be adjusted in a displacement volume per working cycle is driven by means of a variable-speed drive (121), wherein, within the context of control, at least one variable is controlled to a setpoint (psoll) by specifying a speed setpoint (nsoll) for a speed of the drive and a setpoint (αsoll) for a characteristic variable determining the displacement volume per working cycle,
wherein, in the event of a change in the setpoint (αsoll) for the characteristic variable determining the displacement volume per working cycle, the speed setpoint (nsoll) is adapted by means of feedforward control, depending on a current speed (1065) of an adjustment of the delivery mechanism (122). - Method according to Claim 1, wherein the specification of the speed setpoint (nsoll) and/or the adaptation of the speed setpoint (nsoll) and/or the specification of the setpoint (αsoll) for the characteristic variable determining the displacement volume per working cycle is carried out by using a model in which the speed of the adjustment of the delivery mechanism (122) is taken into account.
- Method according to Claim 2, wherein the specification of the speed setpoint (nsoll) and/or the adaptation of the speed setpoint (nsoll) and/or the specification of the setpoint (αsoll) for the characteristic variable determining the displacement volume per working cycle is carried out by using model-predictive control (160).
- Method according to Claim 2 or 3, wherein, in the model, the speed (165) of the adjustment of the delivery mechanism (122) is taken into account by using at least one of the following parameters: a maximum possible displacement volume per working cycle, a minimum possible displacement volume per working cycle, a pressure of a medium with which the adjustable pump is operated, a current value of the speed (nist) of the drive, a viscosity of the medium, and mechanical and/or electrical parameters of an adjustment system of the adjustable pump (120) .
- Method according to one of the preceding claims, wherein, within the context of the control, at least one variable regulated to the setpoint (psoll) is selected from: a pressure and/or a volume flow of a medium with which the adjustable pump is operated, a force which is generated directly or indirectly by the medium, and a position (x) of an element (111) which is moved directly or indirectly by the medium.
- Method according to one of the preceding claims, wherein, in the event of a change in the setpoint (αsoll) for the characteristic variable determining the displacement volume per working cycle, the speed setpoint (nsoll) is further adapted on the basis of at least one optimization criterion, which is in particular selected from: a noise generated by the adjustable pump (120), an efficiency of the adjustable pump (120), and a load factor of the drive (121).
- Method according to one of the preceding claims, wherein, in the event of a change in the setpoint (αsoll) for the characteristic variable determining the displacement volume per working cycle, a torque setpoint (Msoll) for the drive (121) is adapted by means of feedforward control, depending on a speed (165) of an adjustment of the delivery mechanism (122).
- Method according to one of the preceding claims, in which an axial piston pump is used as the adjustable pump (120), in particular with two-point adjustment or proportional adjustment.
- Computing unit (140) which is set up to carry out a method according to one of the preceding claims in a variable-speed adjustable pump (120).
- Electrohydraulic system (100) comprising a variable-speed adjustable pump (120) with a variable-speed drive (121) and a computing unit (140) according to Claim 9.
- Computer program which causes a computing unit (140) to carry out a method according to one of Claims 1 to 8 in a variable-speed adjustable pump (120) when it is executed on the computing unit (140).
- Machine-readable storage medium having a computer program according to Claim 11 stored thereon.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102019220322.1A DE102019220322A1 (en) | 2019-12-20 | 2019-12-20 | Method for operating a variable-speed variable displacement pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3839256A1 EP3839256A1 (en) | 2021-06-23 |
EP3839256B1 true EP3839256B1 (en) | 2022-08-24 |
Family
ID=74141258
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20213692.5A Active EP3839256B1 (en) | 2019-12-20 | 2020-12-14 | Method for operating a variable-speed adjustable pump |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3839256B1 (en) |
CN (1) | CN113007055A (en) |
DE (1) | DE102019220322A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102022203051B3 (en) | 2022-03-29 | 2023-10-12 | Robert Bosch Gesellschaft mit beschränkter Haftung | Method for operating a variable speed pump |
DE102022205233B4 (en) | 2022-05-25 | 2023-12-07 | Robert Bosch Gesellschaft mit beschränkter Haftung | Method for operating an electro-hydraulic unit |
DE102022206540B3 (en) | 2022-06-28 | 2023-10-12 | Robert Bosch Gesellschaft mit beschränkter Haftung | Method for controlling variable-speed fluid pumps |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2192309B1 (en) | 2008-11-29 | 2017-04-05 | Robert Bosch GmbH | Method and control circuit for regulating a supply of pressure fluid for a hydraulic actuator |
DE102011119299A1 (en) * | 2011-11-24 | 2013-05-29 | Robert Bosch Gmbh | Method for operating a variable-speed variable-displacement pump |
DE102013006137B4 (en) * | 2013-04-10 | 2024-04-18 | Robert Bosch Gmbh | Control of variable speed pumps using model-based optimization |
DE102014001981B4 (en) * | 2014-02-17 | 2023-04-27 | Robert Bosch Gmbh | Dynamic setpoint compensation for variable-speed pumps |
-
2019
- 2019-12-20 DE DE102019220322.1A patent/DE102019220322A1/en active Pending
-
2020
- 2020-12-14 EP EP20213692.5A patent/EP3839256B1/en active Active
- 2020-12-18 CN CN202011508905.1A patent/CN113007055A/en active Pending
Also Published As
Publication number | Publication date |
---|---|
EP3839256A1 (en) | 2021-06-23 |
DE102019220322A1 (en) | 2021-06-24 |
CN113007055A (en) | 2021-06-22 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP3839256B1 (en) | Method for operating a variable-speed adjustable pump | |
EP2121280B1 (en) | Electro-hydraulic control arrangement | |
EP2597310B1 (en) | Method for operating a variable-speed adjustable pump | |
DE102013006137A1 (en) | Control of variable speed variable displacement pumps using model based optimization | |
EP1236558B1 (en) | Method for fluid supply regulation of an hydraulic actuator | |
DE3827075A1 (en) | METHOD FOR CONTROLLING OR REGULATING THE OPERATION OF A SWASH DISC COMPRESSOR WITH VARIABLE FLOW RATE | |
AT515590B1 (en) | Dynamic setpoint compensation for variable speed variable displacement pumps | |
DE102009018071B4 (en) | Method and control device for controlling a pressure medium supply for a hydraulic actuator | |
DE102015221684A1 (en) | A method for pressure sensorless setting of the pressure of a pumped by means of a variable speed pump fluid | |
DE102021201895A1 (en) | Method for operating a variable-speed electro-hydraulic pump, computing unit and variable-speed electro-hydraulic pump | |
DE60215672T2 (en) | METHOD OF CONTROL | |
WO2010015460A1 (en) | Method for operating a multi-pulse piston pump, multi-pulse piston pump, and the production thereof | |
EP3988801A1 (en) | Method for operating a hydraulic drive | |
DE102020213293A1 (en) | Method for operating a hydraulic drive | |
EP1460505A2 (en) | System for controlling alternatively the pressure and the flow of a hydraulic fluid | |
DE102022203051B3 (en) | Method for operating a variable speed pump | |
DE102022206540B3 (en) | Method for controlling variable-speed fluid pumps | |
DE102021210117A1 (en) | Method for a hydraulic drive, control unit, computer program and machine-readable storage medium | |
DE102011008923B4 (en) | Method for controlling and/or regulating a hydraulic drive unit, hydraulic drive unit and injection molding machine | |
EP1904750B1 (en) | Electrohydraulic control apparatus | |
DE102022208574A1 (en) | Method for operating a hydraulic drive of a machine and hydraulic drive | |
WO2023156279A1 (en) | Method for operating a hydraulic assembly of a work machine, and work machine | |
WO2023016855A1 (en) | Method for a low-noise operation of an electrically driven hydraulic system | |
WO2013171041A1 (en) | Control device for a hydraulic cylinder unit with an individual valve controller | |
DE102021200693A1 (en) | Procedure for model parameter adjustment of an axial piston pump |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED |
|
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 |
|
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: 20211223 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F15B 11/042 20060101ALI20220330BHEP Ipc: F03C 1/26 20060101ALI20220330BHEP Ipc: F03C 1/06 20060101ALI20220330BHEP Ipc: F04B 49/06 20060101ALI20220330BHEP Ipc: F04B 49/20 20060101ALI20220330BHEP Ipc: F04B 1/26 20060101ALI20220330BHEP Ipc: F04B 1/324 20200101ALI20220330BHEP Ipc: F04B 1/32 20200101AFI20220330BHEP |
|
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 |
|
INTG | Intention to grant announced |
Effective date: 20220520 |
|
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: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1513810 Country of ref document: AT Kind code of ref document: T Effective date: 20220915 Ref country code: DE Ref legal event code: R096 Ref document number: 502020001579 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG9D |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20220824 |
|
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: 20220824 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: 20220824 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: 20221226 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: 20221124 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: 20220824 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: 20220824 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: 20220824 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: 20220824 |
|
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: 20220824 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: 20221224 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: 20220824 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: 20221125 |
|
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: 20220824 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: 20220824 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: 20220824 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: 20220824 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: 20220824 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502020001579 Country of ref document: DE |
|
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: 20220824 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: 20220824 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20221231 Year of fee payment: 3 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230509 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220824 |
|
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 |
|
26N | No opposition filed |
Effective date: 20230525 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20221231 |
|
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: 20220824 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20221214 |
|
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: 20221214 |
|
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: 20221231 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20221231 |
|
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 Effective date: 20220824 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20240227 Year of fee payment: 4 |