EP3754121B1 - Vorrichtung mit einem hydraulischen kreislauf - Google Patents

Vorrichtung mit einem hydraulischen kreislauf Download PDF

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Publication number
EP3754121B1
EP3754121B1 EP20186393.3A EP20186393A EP3754121B1 EP 3754121 B1 EP3754121 B1 EP 3754121B1 EP 20186393 A EP20186393 A EP 20186393A EP 3754121 B1 EP3754121 B1 EP 3754121B1
Authority
EP
European Patent Office
Prior art keywords
pressure
hydraulic
demand
torque
displacement
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
Application number
EP20186393.3A
Other languages
English (en)
French (fr)
Other versions
EP3754121A1 (de
Inventor
Niall James Caldwell
Jill MACPHERSON
Matthew Green
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Artemis Intelligent Power Ltd
Original Assignee
Artemis Intelligent Power Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Artemis Intelligent Power Ltd filed Critical Artemis Intelligent Power Ltd
Priority to EP20186393.3A priority Critical patent/EP3754121B1/de
Priority to FIEP20186393.3T priority patent/FI3754121T3/fi
Priority to PL20186393.3T priority patent/PL3754121T3/pl
Priority to ES20186393T priority patent/ES2930125T3/es
Publication of EP3754121A1 publication Critical patent/EP3754121A1/de
Application granted granted Critical
Publication of EP3754121B1 publication Critical patent/EP3754121B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/96—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
    • E02F3/963—Arrangements on backhoes for alternate use of different tools
    • E02F3/964—Arrangements on backhoes for alternate use of different tools of several tools mounted on one machine
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E02F9/2207—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for reducing or compensating oscillations
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2282—Systems using center bypass type changeover valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0447—Controlling
    • F03C1/045—Controlling by using a valve in a system with several pump or motor chambers, wherein the flow path through the chambers can be changed, e.g. series-parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/053—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the inner ends of the cylinders
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/063—Control by using a valve in a system with several pumping chambers wherein the flow-path through the chambers can be changed, e.g. between series and parallel flow
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
    • 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
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • 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
    • F04B49/22—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 means of valves
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • F15B21/087—Control strategy, e.g. with block diagram
    • 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
    • F04B2203/06—Motor parameters of internal combustion engines
    • F04B2203/0603—Torque
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/09—Flow through the 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
    • 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
    • F15B2211/20523—Internal combustion engine
    • 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
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • 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
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41554—Flow control characterised by the connections of the flow control means in the circuit being connected to a return line and a directional control valve
    • 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
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • 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
    • 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
    • F15B2211/6306—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
    • F15B2211/633—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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/634—Electronic controllers using input signals representing a state of a valve
    • 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
    • F15B2211/6346—Electronic controllers using input signals representing a state of input means, e.g. joystick position
    • 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
    • F15B2211/6655—Power control, e.g. combined pressure and 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6658—Control using different modes, e.g. four-quadrant-operation, working mode and transportation mode

Definitions

  • the engine may be caused to run at prime mover speed below the prime mover speed setpoint (e.g. at at least 90% of the prime mover speed setpoint, preferably at at least 95% of the prime mover speed set point).
  • PRV opening pressures for example, the PRV opening pressure for raising an arm of an excavator may be different to (e.g. higher or lower than) the PRV opening pressure for lowering an arm of an excavator).
  • the controller may be configured to receive demand and/or user commands and to take into account demand and/or user commands when determining whether the measured pressure is within a margin of the pressure limit.
  • the method may comprise taking into account demand and/or user commands (e.g. commands input via one or more joysticks) when calculating where the measured pressure is within a margin of the pressure limit (i.e. the respective PRV opening pressure).
  • the pressure limit and/or the margin may vary with demand and/or user commands or other parameters, e.g. actuator position or speed of movement.
  • the method may comprise measuring an input from a user (e.g. an input delivered via a joystick) to generate a control signal which is used to determine a displacement from the hydraulic machine, or at least the group of one or more working chambers.
  • the controller may receive a user input and generate a control signal which is used to determine a displacement from the hydraulic machine, or at least the group of one or more working chambers This operates in open-loop mode, so there is no feedback system with which to correct an error. Such machines are typically very accurate.
  • the apparatus further comprises at least one spool valve in the hydraulic circuit, through which hydraulic fluid flows in use from the group of one or more working chambers to the one or more of the hydraulic actuators, and pressure sensors configured to measure the pressure of hydraulic fluid before and after the at least one spool valve, for example at the hydraulic machine outlet and at the one or more actuators.
  • the controller is typically configured to determine a pressure drop across the at least one spool valve from measurements of pressure from the pressure sensors, and to receive either a (measured) spool valve position signal, indicative of the position of the spool valve, or a spool valve control signal, and to limit the displacement of the one or more working chambers if the determined pressure drop exceeds a threshold pressure drop which threshold pressure drop is determined in dependence on the spool valve position signal or spool valve control signal respectively.
  • the method typically comprises determining a pressure drop across the at least one spool valve from measurements of pressure from the pressure sensors, and receiving either a (measured) spool valve position signal, indicative of the position of the spool valve, or a spool valve control signal, and limiting the displacement of the one or more working chambers if the determined pressure drop exceeds a threshold pressure drop which threshold pressure drop is determined in dependence on the spool valve position signal or spool valve control signal respectively.
  • Spool valves typically comprise one or more further ports which may be closed by default (i.e. normally closed) and which may be opened in response to a user command (optionally a controller command). Typically, when a further port is opened the main (e.g. central) port is closed. It is possible to determine how open a port of a spool valve is by measuring a control signal associated with the spool valve (for example, the control signal may be a pilot pressure). It is also possible to prove a spool valve position sensor (which may for example determine the position of a spool valve member relative to a valve body).
  • the group of one or more working chambers may be connected to the one or more actuators through a specific port of a spool valve having a plurality of ports. In that case, it is the openness of that specific port which will determine the flow rate leading to the pressure drop which is to be measured.
  • the spool valves comprise a main port, which may be open by default, to thereby provide a default flow path through which fluid displaced by the group of one or more working chambers may flow, optionally to a tank, and one or more further ports which may be closed by default and which may be opened in response to a user or controller command.
  • Said specific port may be a said main port or a said further port.
  • the controller may be configured to receive a user input, a measurement of a spool valve control signal and a measurement of speed of rotation of the rotatable shaft, to thereby determine (e.g. calculate), optionally with reference to a look-up table, an open-loop estimate of required displacement and typically also to determine (e.g. calculate) an estimate of flow on the basis of the measurement of speed of rotation of the rotatable shaft and the open-loop estimate of required displacement.
  • the method may comprise receiving and processing a spool valve control signal (e.g.
  • pilot pressure responsive to a user input, and a measurement of speed of rotation of the rotatable shaft to thereby calculate (for example with reference to a look-up table) an open-loop estimate of required displacement and to calculate an estimated flow on the basis of the measurement of shaft speed and the open-loop estimate of required displacement.
  • the method may comprise determining a value representative of a pressure drop across the spool valve on the basis of the control signal (and hence on the basis of spool valve openness), and measuring the actual drop in pressure (e.g. by receiving pressure measurements from pressure sensors at the hydraulic machine and at the actuator) and comparing the actual drop in pressure with a threshold drop in pressure and reducing the displacement if the actual drop in pressure exceeds the threshold pressure drop.
  • the controller may be configured to determine a value representative of a pressure drop across the spool valve on the basis of the control signal (and hence on the basis of spool valve openness), and to measure the actual drop in pressure (e.g. by receiving pressure measurements from pressure sensors at the hydraulic machine and at the actuator) and to compare the actual drop in pressure with a threshold drop in pressure and to reduce the displacement if the actual drop in pressure exceeds the threshold pressure drop
  • an operator may adjust the spool valve control signal (e.g. the pilot signal), typically via a joystick, to thereby increase the openness of the (e.g. spool valve) and hence to cause an increase in velocity at the one or more actuators.
  • the pressure drop for a given flow through a larger (e.g. spool) valve opening is smaller.
  • the controller causes the flow to be reduced if the actual pressure drop exceeds the threshold pressure drop using a proportional-integral control loop.
  • the method may comprise causing the flow to be reduced if the actual pressure drop exceeds the threshold pressure drop using a proportional-integral control loop.
  • a proportional-integral control loop is configured such that the integral part of the control loop is only permitted to integrate when the actual pressure drop exceeds the threshold pressure drop or to return the integrated value to zero in the case that the actual pressure drop is lower than the acceptable pressure drop.
  • the proportional part of the control loop is applied when the actual pressure drop does not exceed the acceptable pressure drop.
  • the proportional part of the control loop is configured to cause substantially no change in flow if the actual pressure drop does not exceed the threshold pressure drop.
  • Resonant oscillations in vehicles have a number of negative effects, e.g. damage to components, unacceptable noise and vibration as experienced by the operator.
  • Vehicles comprising hydraulic transmissions can be damaged by resonant oscillations arising from the operation of a hydraulic machine within or connected to the hydraulic transmission, including resonant oscillations arising from the operation of the hydraulic transmission.
  • vibrations may arise, resulting from the pulsatile nature of the flow through the hydraulic machine, which may lead to oscillations if they coincide with a resonant frequency of one or more components.
  • Vibration of a component at its resonant frequency will only be caused if there is a mechanical transmission path from the source of the excitation to the component. Vibrations may arise which are dependent on the frequency with which active cycles are selected. For example, if ten active cycles are selected per second, spaced equally apart in time, vibrations may arise at 10 Hz. Similarly, problems may also arise from vibrations associated with the frequency of inactive cycles of working chamber volume. For example, if on every revolution of the shaft, all working chambers undertake an active cycle but one working chamber per 0.1 second carries out an inactive cycle, where inactive cycles are spaced equally apart in time, there may be a vibration of 10 Hz, as a result. Such vibrations can be more damaging, simply because they become relevant when the machine is operating at a high proportion of maximum displacement, and therefore in circumstances where there is a high-power throughput, and greater forces are acting.
  • a hydraulic machine within a vehicle e.g. an excavator
  • the controller may be configured to determine (and the method may comprise determining) whether the vibrations are categorised as unacceptable vibrations, undesirable vibrations or acceptable vibrations in dependence on factors comprising the magnitude of these vibrations and/or the frequency of these vibrations and/or is the presence of a mechanical transmission path for these vibrations to allow for other components to be excited.
  • the output pulsations of the hydraulic machine may contain a certain frequency content comprising frequencies that are not considered unacceptable or undesirable since they do not cause vibration as felt by the driver, or do not result in audible noise, or result in vibrations that could be expected to cause damage to components.
  • the frequency content may cause pulsations in the pressure which we not wish to use when calculating the torque of the hydraulic machine.
  • the frequency content of the pressure is known, and this can be removed by using a moving average filter. (In the instance that the window size is dynamically adjusted such that the moving average filter will remove this particular acceptable frequency, the filter will also remove the harmonics of that frequency, and since the moving average filter is a type of low pass filter it will also partially attenuate all frequencies above the acceptable frequency.
  • the demand signal is used by the hydraulic machine (e.g. by a hydraulic machine controller) to make decisions as to whether each working chamber of the group of one or more working chambers carries out an active cycle or an inactive cycle for each working chamber on each cycle of working chamber volume.
  • the demand signal is calculated in response to a measured property of the hydraulic circuit or one or more actuators we have found that there may be unwanted vibrations or oscillations arising from frequencies of cylinder activation or inactivation resulting from the pattern of active and inactive cycles implemented by the hydraulic machine in response to the demand signal.
  • the measured property is the pressure or flow rate at a location in the hydraulic circuit in fluid communication with the group of one or more working chambers, and/or a position or speed of movement of one or more of the actuators in fluid communication with the group of one or more working chambers. It would be advantageous to suppress these frequencies from the feedback loop.
  • the demand signal to which the hydraulic machine responds is quantised, having one of a plurality of discrete values. It may be that a (optionally continuous) demand signal is received and is quantised, for example by selecting the discrete value closest to the received demand, or the next discrete value above or below the received demand. Hysteresis may be applied in the quantisation step, to avoid chatter.
  • the plurality of discrete values may be representative of the average fraction of full displacement of fluid by the group of one or more working chambers). There may be a step of determining the discrete values, for example calculating them or reading them from memory, and they may be variable, for example depending on the speed of rotation of the rotatable shaft.
  • the controller is configured to calculate, and the method may comprise calculating, the demand signal by filtering a control signal based on the measured property of the hydraulic circuit or one or more actuators using a filter, wherein the filter attenuates one or more frequencies arising from a pattern of active and inactive cycles of working chamber volume resulting from the hydraulic machine selecting the net displacement of hydraulic fluid by each working chamber responsive to the demand signal.
  • the said one or more filters comprise at least one moving average filter.
  • the measured property of the hydraulic circuit is a measured pressure (e.g. at an output of the hydraulic machine, at one or more actuators, before or after one or more control valves etc.)
  • the filter may be varied in dependence on a current or previous value of the demand signal to thereby suppress frequencies arising from the pattern of working chambers undergoing active or inactive cycles arising from the (quantised) demand signal.
  • the plurality of discrete values of the demand signal may or may not be equally spaced.
  • the discrete values may or may not vary with the speed of rotation of the rotatable shaft. If they vary with the speed of rotation of the rotatable shaft, they may be selected to reduce the generation of low frequency components. There may for example be less than 1000, or less than 100 discrete values.
  • the demand signal is digital, we do not refer to the possible values imposed by binary logic but to a subset of the values which could be represented digitally given the bit size of the demand signal.
  • the discrete values typically represent less than 10%, less than 1% or less than 0.1% of the digital values which the demand signal could have, given its bit length.
  • the values of the discrete values vary with speed of rotation of the rotatable shaft and are selected to avoid the generation of undesirable and/or unacceptable frequencies when the hydraulic machine controls the net displacement of the group of one or more working chambers to implement the quantised demand.
  • the moving average filter typically has a filter window. It may be that the filter window has a filter window length selected in dependence on the discrete value of the demand signal and the speed of rotation of the rotatable shaft to attenuate a frequency arising from the group of one or more working chambers carrying out active or inactive cycles of working chamber volume at that discrete value of the demand signal and that speed of rotation of the rotatable shaft. It might be that the filter window has a filter window length corresponding to an inverse value of a predetermined minimum frequency. Thus, the filter will remove components at the predetermined minimum frequency and typically also attenuate lower frequency components. Typically, the predetermined minimum frequency is proportional to speed of rotation of the rotatable shaft, for a given pattern of active and inactive cycles/given demand. The predetermined minimum frequency may be determined from a parameter stored in memory for a given discrete value of the demand signal and from the speed of rotation of the rotatable shaft.
  • the filter window length may be fixed, typically the hydraulic machine controller is configured to cause periodic adjustments of the filter window length in dependence on the demand signal.
  • the method may comprise causing periodic adjustments of the filter window length in dependence on the demand signal, for example once per rotation of the rotatable shaft.
  • Individual working chambers are selectable, e.g. by a valve control module, on each cycle of working chamber volume, to either displace a predetermined fixed volume of hydraulic fluid (an active cycle), or to undergo an inactive cycle (also referred to as an idle cycle) in which there is no net displacement of hydraulic fluid, thereby enabling the net fluid throughput of the machine to be matched dynamically to the demand indicated by the demand signal.
  • the controller and/or the valve control module may be operable to cause individual working chambers to undergo active cycles or inactive cycles by executing an algorithm (e.g. for each cycle of working chamber volume).
  • the method may comprise executing an algorithm to determine whether individual working chambers undergo active cycles or inactive cycles (e.g. for each cycle of working chamber volume).
  • the algorithm typically processes the (e.g. quantised) demand signal.
  • the pattern of active and inactive cycles of working chamber volume carried out by the working chambers has a frequency spectrum with one or more intensity peaks. For example, if the working chambers carried out, on an alternating basis, active and inactive cycles, there would be an intensity peak at a frequency equal to half the frequency of cycles of working chamber volume. More generally, the working chambers will undergo a more complex pattern of active and inactive cycles, having a frequency spectrum with one or more intensity peaks.
  • the pattern of active and inactive cycles of working chamber volume carried out by the working chambers typically has a finite period, wherein the finite period may vary within a range of acceptable values.
  • the pattern of active and inactive cycles may have a minimum period of at least 0.001 s, or at least 0.005 s, or at least 0.01 s and/or may have a maximum period of at most 0.1 s, or at most 0.5 s.
  • the minimum period may be 2 ms (caused by the frequency of activation of all 12 cylinders at a maximum speed of 2050 RPM).
  • the minimum period could be 1 ms (or lower).
  • the range of acceptable periods is selected in dependence on the acceptable frequency content. From this maximum acceptable period an acceptable finite range of displacement demands will be selected dependent on the number of cylinders and on the operating range of the prime mover.
  • the range of acceptable Fd values may be selected to comprise of a finite number of integer fractions of the displacement demand.
  • the denominators of the finite number of integer fractions may be selected in dependence on the rotational speed of the rotational shaft, for example, the denominators may be selected such that the period is lower than a maximum period.
  • acceptable values of the denominators of the finite number of integer fractions vary in dependence on the rotational speed of rotation of the rotatable shaft. It is beneficial to have a short period because this corresponds to more frequent cycles of active or inactive working chamber volume and it therefore removes low frequency content from the chamber activations.
  • the window size of the moving average filter is selected in dependence on the frequency of the pattern of active and inactive cycles of working chamber volume. For example, if the pattern of active and inactive cycles of working chamber volume has a frequency of 10.5 Hz, the window size of the moving average filter may be selected such that it has a period of 0.095 s.
  • the frequency of working chambers carrying out active or inactive cycles is proportional to the speed of rotation of the rotatable shaft (revolutions per second). This is because there will typically be one point during each cycle of working chamber volume where a given working chamber is committed to either carry out an active cycle or an inactive cycle. For example, a decision is typically made whether or not to close an electronically controlled valve regulating the flow of hydraulic fluid between a working chamber and the low-pressure hydraulic fluid manifold.
  • the (potentially undesirable) frequencies arising from a particular sequence of active and inactive cycles are proportional to the speed at which cycles take place, that is to say proportional to the speed of rotation of the rotatable shaft.
  • the window size of the moving average filter is typically selected in dependence on the demand signal and on the speed of rotation of the rotatable shaft.
  • frequencies e.g. range of frequencies
  • a portion of a hydraulic machine and/or one or more resonant frequencies of a portion of the vehicle (e.g. the excavator), which is part of or in mechanical communication with (e.g. mechanically coupled to) the hydraulic machine, which resonant frequencies does not vary proportionately to the speed of rotation of the rotatable shaft.
  • the invention recognises that the hydraulic machine will generate vibrations having intensity peaks at frequencies which depend on the pattern of active and inactive cycles carried out by the working chambers and which, for a given sequence of active and inactive cycles, is proportional to the speed of rotation of the rotatable shaft.
  • the pattern of valve command signals is controlled to reduce unwanted vibrations by preventing certain ranges of Fds which means that the target net displacement is sometimes not met exactly.
  • the pattern of valve command signals typically affects the frequency at which the one or more intensity peaks of the frequency spectrum occur, by determining whether each working chamber undergoes active or inactive cycles. However, if the amount of hydraulic fluid displaced by working chambers varies between cycles then the net displacement determined by the pattern of valve control signals during each cycle of working chamber volume also affects the frequency at which the one or more intensity peaks of the frequency spectrum occurs.
  • the method may comprise dynamically adjusting (and the controller may be configured to adjust) the window size of the moving average filter, such that the moving average filter totally attenuates the lowest known frequency.
  • the method may comprise adjusting (and the controller may be configured to adjust) the window size of the moving average filter in dependence on the speed of rotation of the rotatable shaft and/or the current hydraulic fluid displacement.
  • the window size of the moving average filter may be selected to also have a 10 ms period to thereby attenuate e.g. filter) a 10 Hz cylinder enabling pattern.
  • the controller receives a demand signal (typically a continuous demand signal) and determines a corresponding series of values, said series of values corresponding to a pattern of active and/or inactive cycles of working chamber volume to thereby meet the demand signal (i.e. when the demand signal (F d ) resulting from the pattern of active and/or inactive cycles of working chamber volume is averaged over a time period).
  • the method may comprise receiving a demand signal (typically a continuous demand signal) and determining a corresponding series of values, said series of values corresponding to a pattern of active and/or inactive cycles of working chamber volume to thereby meet the demand signal (i.e. when the demand signal (F d ) resulting from the pattern of active and/or inactive cycles of working chamber volume is averaged over a time period).
  • the controller may receive a continuous demand signal for 90% of the maximum displacement and may determine a series of values comprising at least 100 values, or preferably at least 500 values, or more preferably at least 1000 values.
  • the series of values may comprise a repeating sequence and hence the pattern of active and/or inactive cycles may comprise a period which corresponds to the repeating sequence.
  • the method may comprise selecting a minimum allowable frequency (e.g. 5 Hz, 10 Hz), and then creating a quantised list of the plurality of discrete values of the demand (e.g. Fd), said values (e.g. of Fd) selected to cause one or more patterns of cylinder activation, wherein said patterns only have frequency content above the minimum allowable frequency.
  • the controller may be configured to determine a minimum allowable frequency (e.g. 5 Hz, 10 Hz), and then to create a quantised list of the plurality of discrete values of the demand (e.g. Fd), said values (e.g. of Fd) selected to cause one or more patterns of cylinder activation, wherein said patterns only have frequency content above the minimum allowable frequency.
  • the quantised list of allowable values of demand may be dependent on the number of cylinders in the machine and/or on the operational speed of rotation of the rotatable shafts of the machine (since the speed of rotation of the rotatable shaft and number of cylinders will affect the frequencies present for a given demand value.) For each value of demand in the list it is possible to calculate the minimum frequency present.
  • the (filtered) demand signal is transmitted to the controller of the hydraulic machine.
  • the method may comprise receiving a value representative of a demand (e.g.
  • the method comprises dynamically adjusting the selected window size.
  • the controller may be configured to dynamically adjust the selected window size.
  • the window size is dependent on the lowest frequency present (which is in turn dependent on speed of rotation of the rotatable shaft).
  • the window size may be synchronised (i.e. adjusted) once per revolution signal.
  • the moving average filter can totally attenuate this frequency from the received control signal or demand signal. This has the advantage of improving prime mover speed and allowing a hydraulic machine to operate closer to the prime mover speed (or torque) limit for a greater percentage of the time during which it is in use.
  • This method is useful for attenuating known frequencies from a hydraulic machine that is controlled to output quantised displacement.
  • the low frequency pattern of continuous displacement may in some cases cause large window sizes (e.g. if the frequency is very low) and as such considerable control lag. Additionally, since the displacement is continuous (and not in fixed steps) the patterns of working chamber actuations do not reach a repeating pattern state.
  • At least one of the said filters receives a signal and outputs a signal, wherein the output signal does not change as a result of the input signal changing within a band.
  • the input signal is the control signal (e.g. measured pressure, flow or actuator position or speed) or a signal derived therefrom.
  • the output is the demand signal or is further processed to give the demand signal.
  • Contributions from individual working chamber actuations can cause pulsatile pressure ripple.
  • changes in pressure are used to allow decisions to be made (e.g. a decision to change Fd, etc) small changes in pressure caused by pulsatile pressure ripple could be misinterpreted as real, deliberate pressure changes, which could lead to a decision being made in error.
  • the predetermined rejection range may be selected in response to an expected range of pressure pulsation.
  • the predetermined rejection range may comprise a pressure range of at least 10 bar, at least 20 bar or at least 30 bar (e.g. 20 bar).
  • the predetermined rejection range is typically selected dependent on the specific hydraulic system in which it is intended to be used.
  • the predetermined rejection range may optionally be adjustable, for example if the compliance and/or stiffness of the hydraulic system changes (e.g. when an accumulator is provided).
  • the method comprises regulating, and the apparatus is configured to regulate, the prime mover control signal to cause the prime mover governor to increase the applied torque of the prime mover and then to subsequently, after a delay period, (and optionally in dependence on a measured speed and/or pressure and/or Fd, etc), to regulate the demand signal to increase the displacement of working fluid and the torque exerted by the group of one or more working chambers.
  • a delay period and optionally in dependence on a measured speed and/or pressure and/or Fd, etc
  • the demand signal to increase the displacement of working fluid and the torque exerted by the group of one or more working chambers.
  • the increase in torque exerted by the one or more working chamber is applied concurrently with (e.g. at the same time as) the increase in torque of the prime mover.
  • the invention extends to a method of operating the apparatus comprising applying a torque limit to the one or more hydraulic machines.
  • the apparatus may comprise a controller which may be operable to apply a torque limit to the one or more hydraulic machines.
  • the controller e.g. hydraulic machine controller
  • the controller may be configured to receive a measurement of the rotational speed of the rotatable shaft and a value representative of displacement demand and thereby calculate an estimate of the flow delivered (e.g. by calculating a product of displacement demand and speed of rotation of the rotatable shaft).
  • the method may comprise receiving a measurement of the rotational speed of the rotatable shaft and a value representative of displacement demand and thereby calculating an estimate of the flow delivered (e.g. by calculating a product of displacement demand and speed of rotation of the rotatable shaft).
  • the controller e.g. the hydraulic machine controller
  • the controller may further calculate an estimate of the mechanical power absorbed.
  • the method may comprise receiving a measurement of the rotational speed of the rotatable shaft and calculating an estimate of exerted torque and optionally further calculating an estimate of the mechanical power absorbed.
  • the controller e.g. the hydraulic machine controller
  • the controller may further calculate an estimate of the fluid power.
  • the method may comprise receiving a measurement of the outlet pressure and calculating an estimate of the flow delivered and optionally further calculating an estimate of the fluid power.
  • the controller e.g. the hydraulic machine controller
  • the controller may be configured to receive one or more further parameters associated with the hydraulic machine (e.g. volumetric displacement and mechanical efficiency, optionally as a function of pressure, speed, temperature, etc) and may take the one or more further parameters into account to thereby improve the accuracy of the estimate.
  • the method may comprise receiving one or more further parameters associated with the hydraulic machine (e.g. volumetric displacement and mechanically efficiency, optionally taking into account (e.g. measurements of) pressure, speed, temperature etc.) to thereby improve the said estimate of the mechanical power absorbed or the fluid power.
  • the controller e.g. the hydraulic machine controller
  • the controller may be configured to receive a measurement of current pressure, calculate a displacement limit required to exert a torque at the said pressure and limit the output displacement such that it does not exceed the displacement limit to thereby limit the torque.
  • the method may comprise receiving a measurement of current pressure, calculating a displacement limit required to exert a torque at the said pressure and limiting the output displacement such that it does not exceed the displacement limit to thereby limit the torque.
  • the controller (e.g. the hydraulic machine controller) may be configured to receive a measurement of current rotational speed of the rotatable shaft, calculate a displacement limit required to supply a flow at the said rotational speed of the rotatable shaft and limit the output displacement such that it does not exceed the displacement limit to thereby limit the flow.
  • the method may comprise receiving a measurement of current rotational speed of the rotatable shaft, calculating a displacement limit required to supply a flow at the said rotational speed of the rotatable shaft and limit the output displacement such that it does not exceed the displacement limit to thereby limit the flow.
  • the controller may be configured to receive a measurement of current pressure, and current rotational speed of the rotatable shaft, and calculate a displacement limit required to absorb a power at the said pressure and rotational speed and limit the output displacement (such that it does not exceed the displacement limit to thereby limit the power).
  • the method may comprise receiving a measurement of current pressure, and current rotational speed of the rotatable shaft, and calculating a displacement limit required to absorb a power at the said pressure and rotational speed and limit the output displacement (such that it does not exceed the displacement limit to thereby limit the power).
  • the controller e.g. the hydraulic machine controller
  • the controller may be configured to receive, and the method may comprise receiving, one or more signals indicative of a displacement, flow, pressure, power and/or torque demand.
  • the one or more signals may be limited by one or more limiting functions, the one or more limiting functions typically being dependent on one or more further parameters (e.g. temperature).
  • the controller may receive, and the method may comprise receiving, a signal indicative of a flow demand of 100 L/min, wherein the signal indicative of the flow demand is limited by a pressure limit of 200 bar and a power limit of 20 kW, and the machine may be configured to output flow in response to that flow demand, up to a limit of 100 L/min, only when a measurement of pressure indicates that the pressure is at or below 200 bar and a measurement of power indicates that the power output is at or less than 20 kW.
  • the one or more limiting functions may be non-linear limiting functions.
  • the controller e.g. hydraulic machine controller
  • the controller may be configured to receive (and/or calculate) an estimate of the available torque of the prime mover (e.g. the engine) and set a hydraulic machine torque limit wherein the torque limit is dependent on the prime mover speed.
  • the method may comprise receiving and/or calculating an estimate of the available torque of the prime mover (e.g. the engine) and setting a hydraulic machine torque limit wherein the torque limit is dependent on the prime mover speed. For example, at relatively low prime mover speeds, the hydraulic machine torque limit may be selected to be zero to thereby prevent stall (e.g. engine stall); conversely, at relatively high prime mover speeds the hydraulic machine torque limit may be selected to prevent machine damage.
  • the hydraulic machine torque limit may be increased to thereby increase the machine load, causing the prime mover speed to decrease until the machine load matches the available torque of the prime mover. This has the advantage of providing a temporary increase in available power until the prime mover speed is reduced.
  • a relatively high or low prime mover speed will be dependent on the individual prime mover and/or vehicle.
  • a vehicle comprises a prime mover in the form of an engine, the engine having a controller comprising an engine governor
  • the engine governor may comprise a variable speed setpoint and the controller may be configured to receive a measurement of engine speed droop to thereby calculate an estimate of engine load.
  • the method may comprise implementing a variable speed setpoint of the engine.
  • the method may comprise receiving a measurement of engine speed droop and thereby calculating an estimate of the engine load.
  • the hydraulic machine torque limit may be limited by a limiting function wherein the limiting function is dependent on the measurement of engine speed droop.
  • the controller implements the torque limit while independently varying the demand signals of two or more said groups of working chambers.
  • the controller may comprise prioritising, the torque of one or more said groups of working chambers, or to maintain the torque of one or more said groups of working chambers at a predetermined (e.g. guaranteed, while sufficient prime mover torque is available) torque.
  • the controller causes, and the method comprises causing, one or more of said groups of working chambers to carry out motoring cycles while one or more other of said groups of working chambers carry out pumping cycles, to thereby use torque from the motoring to supplement the engine torque and thereby assist the torque generated by said pumping.
  • controller limits the torque, and the method may comprise limiting the torque, to implement a maximum torque slew rate, either of the group of one or more working chambers or the hydraulic machine as a whole.
  • prime mover is an engine.
  • prime movers may also be chosen as appropriate.
  • the working chambers are each associated with Low Pressure Valves (LPVs) in the form of electronically actuated face-sealing poppet valves 52, which have an associated working chamber and are operable to selectively seal off a channel extending from the working chamber to a low-pressure hydraulic fluid manifold 54, which may connect one or several working chambers, or indeed all as is shown here, to the low-pressure hydraulic fluid manifold of the ECM 54.
  • the LPVs are normally open solenoid actuated valves which open passively when the pressure within the working chamber is less than or equal to the pressure within the low-pressure hydraulic fluid manifold, i.e.
  • valves may alternatively be normally closed valves.
  • the working chambers are each further associated with a respective High-Pressure Valve (HPV) 64 each in the form of a pressure actuated delivery valve.
  • HPV High-Pressure Valve
  • the HPVs open outwards from their respective working chambers and are each operable to seal off a respective channel extending from the working chamber to a high-pressure hydraulic fluid manifold 58, which may connect one or several working chambers, or indeed all as is shown in Figure 2 , to the high-pressure hydraulic fluid manifold 60.
  • the HPVs function as normally-closed pressure-opening check valves which open passively when the pressure within the working chamber exceeds the pressure within the high-pressure hydraulic fluid manifold.
  • the HPVs also function as normally-closed solenoid actuated check valves which the controller may selectively hold open via HPV control lines 62 once that HPV is opened by pressure within the associated working chamber.
  • the HPV is not openable by the controller against pressure in the high-pressure hydraulic fluid manifold.
  • the HPV may additionally be openable under the control of the controller when there is pressure in the high-pressure hydraulic fluid manifold but not in the working chamber, or may be partially openable.
  • the controller selects the net rate of displacement of hydraulic fluid from the working chamber to the high-pressure hydraulic fluid manifold by the hydraulic motor by actively closing one or more of the LPVs typically near the point of maximum volume in the associated working chamber's cycle, closing the path to the low-pressure hydraulic fluid manifold and thereby directing hydraulic fluid out through the associated HPV on the subsequent contraction stroke (but does not actively hold open the HPV).
  • the controller selects the number and sequence of LPV closures and HPV openings to produce a flow or create a shaft torque or power to satisfy a selected net rate of displacement.
  • the hydraulic machine controller selects the net rate of displacement of hydraulic fluid, displaced by the hydraulic machine, via the high-pressure hydraulic fluid manifold, actively closing one or more of the LPVs shortly before the point of minimum volume in the associated working chamber's cycle, closing the path to the low-pressure hydraulic fluid manifold which causes the hydraulic fluid in the working chamber to be compressed by the remainder of the contraction stroke.
  • the associated HPV opens when the pressure across it equalises and a small amount of hydraulic fluid is directed out through the associated HPV, which is held open by the hydraulic machine controller.
  • the controller then actively holds open the associated HPV, typically until near the maximum volume in the associated working chamber's cycle, admitting hydraulic fluid from the high-pressure hydraulic fluid manifold to the working chamber and applying a torque to the rotatable shaft.
  • the controller is operable to vary the precise phasing of the closure of the HPVs with respect to the varying working chamber volume and thereby to select the net rate of displacement of hydraulic fluid from the high-pressure to the low-pressure hydraulic fluid manifold or vice versa.
  • a pressure relief valve 66 may protect the hydraulic machine from damage.
  • each joystick 10 is coupled to an open-centre spool valve 8 to regulate flow therethrough.
  • the pressure monitor 4 measures the pressure 24 of hydraulic fluid in the conduit in a position upstream of the throttle (i.e. in a position downstream of the group of hydraulic actuators).
  • the controller 14 regulates the displacement of hydraulic fluid by a group of working chambers defined by cylinders in which pistons reciprocate in use (the working chambers being in fluid communication with the group of hydraulic actuators 6) in response to the measured pressure 24. This can be done in a feedback loop (e.g. if the pressure monitor 4 records a pressure that is below a desired level, the controller 14 can increase the displacement of hydraulic fluid and thus the pressure 24 will increase).
  • the controller 14 may also take into account a flow demand 16 and a hydraulic machine outlet pressure 18 and may include a torque control module 20 and a negative flow control module 12.
  • the two ECMs 32 are each controlled by an ECM controller 50 such that cycle by cycle decisions can be made regarding whether or not an ECM will displace hydraulic fluid.
  • Each ECM can transmit hydraulic fluid through a fluid manifold and through two open-centre spool valves 8 and to a tank 2 at atmospheric pressure.
  • Each open-centre spool valve is in electronic communication with a joystick 10 via which a user may input a command.
  • the spool valves have normally open centres, operable to close when a command is input via a joystick, in which case hydraulic fluid is diverted to a hydraulic actuator 6 (here shown as a single hydraulic actuator although it will be appreciated that it would be possible to divert hydraulic fluid to multiple hydraulic actuators) to thereby meet a demand.
  • Pressure sensors 4 detect the pressure of hydraulic fluid between each ECM 32 and the tank 2. Although two open-centre spool valves are shown connected to each of the two machines 32, it will be appreciated that this number may vary upwards or downwards and may differ between the two electronically commutated machines.
  • Oil functioning as a hydraulic fluid, is supplied from a tank to the input side of the hydraulic machine through a low-pressure fluid working manifold.
  • the pressure in the high-pressure manifold is sensed using a pressure sensor.
  • the excavator also has an engine controller 26 and a system controller 14.
  • the system controller controls the ECM by sending control signals (e.g. displacement demand signals 16) to the machine controller in order to regulate the displacement.
  • the control signals demand displacement by the ECM, expressed as a fraction of maximum displacement, F d , (the displacement demand).
  • F d the displacement demand
  • the absolute volume of the displacement (volume of hydraulic fluid displaced per second) is the product of the fraction of maximum displacement, the maximum volume which can be displaced per cycle of a working chamber, the number of working chambers and the rate of cycles of working chamber volume.
  • the hydraulic machine controller can regulate the torque applied and the pressure in the high-pressure hydraulic fluid manifold.
  • the pressure in the high-pressure hydraulic fluid manifold increases when the rate of displacement of hydraulic fluid increases faster than the hydraulic fluid is supplied to a hydraulic actuator and vice versa.
  • Multiple hydraulic actuators may be in fluid communication with the high-pressure fluid manifold. The displacement of each ECM is taken into account by the hydraulic machine controller in regulating the torque.
  • the controllers 50 of the ECMs 32 are operable to make cycle-by-cycle decisions regarding whether each cylinder of the machine should complete an active or an inactive cycle. These decisions are made on the basis of a hydraulic fluid displacement demand associated with a given hydraulic actuator (or a combination of hydraulic actuators). Accordingly, there is a high frequency of decisions during the operation of such an ECM, and a correspondingly short response time of the machine when a hydraulic fluid displacement demand is applied or changed.
  • each joystick 10 is (in addition to being coupled to an open centre spool valve 8) in electronic communication with the system controller 14.
  • This example excavator may, as a result, be operated without the feedback loop indicated in Figure 1 , in which case the system controller receives signals from the joysticks indicative of a demand and increase or decrease the displacement of hydraulic fluid in response to that demand.
  • an engine speed error 138 is calculated.
  • the engine speed setpoint 126 is further supplied to a look-up table 140 to thereby calculate the maximum engine torque 142 available and this is compared 144 to an engine torque safety factor 130 to calculate a maximum ECM torque 146 that can be applied to cause an acceptable level of engine droop.
  • the output pressure of each hydraulic machine is filtered 150A, 150B to remove the lowest frequencies arising due to quantisation and the negative flow control pressure is fed into a further look-up table 152A, 152B to thereby calculate a maximum flow displacement 154A, 154B.
  • One of the filtered output pressures is also limited 158.
  • the maximum flow displacement for each hydraulic machine is summed 156, and a corresponding torque is calculated. The difference between the current engine speed and the speed setpoint is determined, a gain is applied and a torque offset is applied to the maximum allowable ECM torque.
  • the hydraulic machine controller may cause the first hydraulic machine to undergo an active cycle while the second hydraulic machine undergoes an inactive cycle, or it may cause the first hydraulic machine to undergo an inactive cycle while the second hydraulic machine undergoes an active cycle, or it may cause both the first hydraulic machine and the second hydraulic machine to undergo an active cycle, or it may cause both the first hydraulic machine and the second hydraulic machine to undergo an inactive cycle.
  • FIG. 6 is a schematic diagram of the machine controller 50 of the motor 32.
  • a processor 70 such as a microprocessor or microcontroller, is in electronic communication through a bus 72 with memory 74 and an input-output port 76.
  • the memory 74 stores a program 78 which implements execution of a displacement determination algorithm to determine the net volume of hydraulic fluid to be displaced by each working chamber on each cycle of working chamber volume, as well as one or more variables 80 which store an accumulated displacement error value.
  • the memory also stores a database 82 which stores data concerning each working chamber, such as the angular position of each working chamber 84 and whether or not it is deactivated 86 (for example, because it is broken).
  • the database may store the number of times each working chamber has undergone an active cycle 88.
  • the database may store one or more look-up tables.
  • the program may comprise program code 90, functioning as the resonance determining module, which calculates one or more undesirable frequencies and/or ranges of undesirable frequencies.
  • FIG. 7 is a schematic diagram of an example embodiment of a vehicle 170, in this case an excavator with a hydraulically actuated arm.
  • the hydraulically actuated arm is formed of a first jointed portion 174A and a second jointed portion 174B. Each of the first and second jointed portions can be independently actuated.
  • suitable vehicles include telehandlers, backhoe loaders, etc.
  • Figure 3A is a flow chart of a system according to the invention, wherein the system takes in an initial value of pressure 114 into the negative flow control system 100, the output of which is compared to a maximum pressure 116 giving a value of F d 118 which is fed to a low pass filter 102 (in this case a low pass filer with a 300 ms time constant).
  • the output of this filter is passed to a speed limiter 106 which also takes in a pressure measurement 104, a current engine speed measurement 110 and an engine speed setpoint 112.
  • This allows the calculation of a torque limit by a torque limiter 108 and hence a final output demand is passed to the electronically commutated machine(s) 118.
  • the present invention provides the function of emulating the behaviour of an analogue pump (e.g. a conventional swash plate pump).
  • an open loop torque limit is below the maximum engine torque 224 and represents the maximum summed torque that may be provided by all hydraulic machines in combination for a given engine speed (optionally for an engine speed setpoint). Accordingly, there is a range 228 of acceptable engine speeds for a given engine torque. For example, if a vehicle had two hydraulic machines driven by the same engine, each hydraulic machine could be limited such that it could provide, at maximum, 45% of the torque limit, with the result that the sum of the torque from both hydraulic machines would be 90% of the torque maximum (i.e. a safety margin 226 is provided). This choice is made so that the absolute torque limit of the machine is never exceeded (for example when excessive demands are input) to thereby prevent the vehicle from stalling.
  • the ECU calculates the expected sum of displacement demands on the basis of the input commands of the user.
  • the spools valves are controlled via hydraulic joysticks to open in proportion to the displacement command (this requires no electronic control).
  • the ECU uses proportional solenoid valves to cause the spool valves to open in proportion to the displacement demand.
  • the controller is configured to receive a demand signal and determine a series of discrete values where the discrete values representative of displacement of fluid by one or more working chambers, i.e. a pattern of active and inactive cycles of working chamber volume.
  • Figure 18 is a plot of output as the result of an example series of discrete values (and hence an example pattern of active and inactive cycles of working chamber volume). Over time, the total output of working chamber volume averages such that the hydraulic machine (i.e. F d ) meets the demand in response to the demand signal.
  • the series of discrete values may be represented as a non-linear function.
  • the series of discrete values may be determined with reference to a number of predetermined series of discrete values or from a database, or the controller may carry out one or more calculations to thereby determine the series of discrete values.
  • the non-linear function is not simply a transfer function and/or a low-pass filter.
  • the present invention applies a moving average filter with a variable period to filter the low frequency vibrations.
  • the period of the moving average filter By setting the period of the moving average filter to be equal to the period of the decision pattern that gives rise to the vibrations (in the above example, the period would be 37.5 ms) the low frequency vibration is completely attenuated (as are the harmonics of the vibration). If the period of the pattern of active and inactive cycles is changed, or if the speed of rotation of the rotatable shaft is changed, the period of the moving average filter is also changed in dependence thereon.
  • the low amplitude ripple reject filter is a non-linear function (not a transfer function or a low-pass filter). These are two ways, i.e. common objective, of suppressing ripple on a higher-level system.
  • Hydraulic machine torque arising from a variable displacement hydraulic machine is a function of the hydraulic machine displacement and hydraulic machine outlet pressure.
  • Use of unfiltered pressure could result in fast decrease or increase in hydraulic machine torque which would be beneficial for engine stability and maximising hydraulic machine productivity.
  • due to the pressure ripple use of unfiltered pressure for torque control would result in unstable displacement.
  • the low amplitude ripple-reject filter retains the previous output value of the filter and compares the new input pressure to this retained value. If the difference between the new pressure and the retained pressure value is within a rejection band ('deadband'), the output pressure is held constant and is not modified. If the new pressure is outside of the rejection band, the output pressure is modified to this new value.
  • a rejection band 'deadband'
  • the range of the deadband is set on expectation of a particular range of pressure pulsation - e.g. 20 bar pressure pulsation.
  • the deadband is typically tuned and set for the specific hydraulic system to which it is fitted. However, the band may change if the compliance / stiffness of the hydraulic system changes (e.g. if an accumulator is provided).
  • the hydraulic machine controller applies a torque limit where the hydraulic machine torque limit is above a torque limit of the engine.
  • the torque limit is dependent on the current engine speed.
  • the engine controller receives a measurement of the current engine speed and determines a corresponding engine torque limit, with reference to a lookup table (e.g. a lookup table stored in a database) containing a torque-speed curve.
  • the torque limit may be set as a function of speed to match the available torque of the engine.
  • Figure 13 is a plot of an example of torque functions; a torque function representing torque determined in accordance with available engine speed 330 and a torque function determined in accordance with available hydraulic machine speed 328, where the torque 324 is plotted as a function of both engine speed 326 and with reference to a minimum speed demand 322 and a maximum speed demand 320.
  • the torque of the hydraulic machine is limited to prevent engine stall.
  • the torque of the hydraulic machine is limited prevent internal damage.
  • the hydraulic machine torque may be increased (as shown by curve 328) to cause the engine speed to reduce until the load on the hydraulic machine corresponds to the available engine torque. This takes place over a short time period until the engine speed reduces.
  • Figure 16 is a plot of torque 362 as a function of time 360 indicating an example of torque response to a steady torque limit 364, an instant torque limit 366 and a slew rate limit 368.
  • Figures 17A and 17B are plots of torque 362 as a function of time 360 indicating torque response associated with a first and second outlet of a hydraulic machine without exceeding a predetermined torque slew limit 368.
  • 370 is the actual torque associated with the first outlet of the hydraulic machine and 372 is the actual torque associated with the second outlet of the hydraulic machine.
  • 374 is the torque demand associated with the first outlet of the hydraulic machine.
  • 376 is the guaranteed amount of torque associated with the first outlet.
  • these outlets are simply fluid connections to (one or more working chambers of) the hydraulic machine which act as outlets when the machine operating in a pumping mode and as inlets when the hydraulic machine operated in a motoring mode.
  • the torque demand of a second actuator may be restricted and de-prioritised because the first actuator is of greater importance and as such the total torque is divided such that more torque is available for the first actuator than is available for the second actuator.
  • Figure 18 is a plot indicating an example of how a continuous demand signal 380 may be quantised 382 into discrete steps. Although the quantised steps may be equally spaced in amount of demand (e.g. displacement) this is not necessary.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
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  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
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Claims (15)

  1. Einrichtung, umfassend ein Antriebsaggregat und eine Mehrzahl von hydraulischen Aktuatoren (6), eine hydraulische Maschine (32) mit einer drehbaren Welle (42) in angetriebenem Eingriff mit dem Antriebsaggregat und umfassend eine Mehrzahl von Arbeitskammern (84) mit einem Volumen (36), das zyklisch mit Drehung der drehbaren Welle variiert, einen Hydraulikkreis, der sich zwischen einer Gruppe von einer oder mehreren Arbeitskammern der hydraulischen Maschine und einem oder mehreren der hydraulischen Aktuatoren erstreckt,
    wobei jede Arbeitskammer der hydraulischen Maschine ein Niederdruckventil (52), das den Durchfluss von Hydraulikfluid zwischen der Arbeitskammer und einem Niederdruckverteiler (54) reguliert, und ein Hochdruckventil (64), das den Durchfluss von Hydraulikfluid zwischen der Arbeitskammer und einem Hochdruckverteiler (58) reguliert, umfasst,
    wobei die hydraulische Maschine ausgelegt ist, zumindest die Niederdruckventile der Gruppe von einer oder mehreren Arbeitskammern aktiv zu steuern, um die Nettoverdrängung an Hydraulikfluid durch jede Arbeitskammer in jedem Zyklus eines Arbeitskammervolumens und dadurch die Nettoverdrängung an Hydraulikfluid durch die Gruppe von einer oder mehreren Arbeitskammern in Reaktion auf ein Anforderungssignal (94, 380) auszuwählen, wobei die Einrichtung eine Steuerung (14) umfasst, die ausgelegt ist, das Anforderungssignal in Reaktion auf eine gemessene Eigenschaft des Hydraulikkreises oder eines oder mehrerer Aktuatoren zu berechnen, wobei das Anforderungssignal quantisiert (382) wird, wobei es einen einer Mehrzahl von diskreten Werten aufweist.
  2. Einrichtung nach Anspruch 1, wobei das Anforderungssignal (94, 380), optional durch Auswählen des diskreten Werts der Mehrzahl von diskreten Werten, der der empfangenen Anforderung am nächsten liegt, empfangen und quantisiert (382) wird.
  3. Einrichtung nach Anspruch 1, wobei das Anforderungssignal (94, 380) empfangen und quantisiert (382) wird, wobei das Anforderungssignal einen Bruchteil einer maximalen Verdrängung an Hydraulikfluid durch die Gruppe von einer oder mehreren Arbeitskammern anzeigt, das pro Umdrehung der drehbaren Welle verdrängt werden soll, optional wobei ein Bereich an akzeptablen Werten des Anforderungssignals so ausgewählt ist, dass er eine endliche Anzahl an ganzzahligen Bruchteilen der maximalen Verdrängung an Hydraulikfluid durch die Gruppe von einer oder mehreren Arbeitskammern, das pro Umdrehung der drehbaren Welle verdrängt werden soll, umfasst.
  4. Einrichtung nach Anspruch 1 oder Anspruch 2, wobei die Mehrzahl von diskreten Werten mit der Drehzahl der drehbaren Welle (42) variiert.
  5. Einrichtung nach einem der vorhergehenden Ansprüche, wobei es weniger als 1.000 diskrete Werte gibt.
  6. Einrichtung nach einem der vorhergehenden Ansprüche, wobei die diskreten Werte weniger als 10 % der digitalen Werte darstellen, die das Anforderungssignal (94, 380) aufgrund seiner Bitlänge aufweisen könnte.
  7. Einrichtung nach einem der vorhergehenden Ansprüche, wobei die Steuerung ausgelegt ist, eine minimale zulässige Frequenz zu bestimmen und dann eine quantisierte Liste der Mehrzahl von diskreten Werten der Anforderung zu erstellen, wobei die Werte ausgewählt werden, um ein oder mehrere Muster einer Zylinderaktivierung zu bewirken, wobei die Muster ausschließlich einen Frequenzgehalt über der minimalen zulässigen Frequenz aufweisen.
  8. Verfahren zum Betreiben einer Einrichtung, wobei die Einrichtung ein Antriebsaggregat und eine Mehrzahl von hydraulischen Aktuatoren (6), eine hydraulische Maschine (32) mit einer drehbaren Welle (42) in angetriebenem Eingriff mit dem Antriebsaggregat und umfassend eine Mehrzahl von Arbeitskammern (84) mit einem Volumen (36), das zyklisch mit Drehung der drehbaren Welle variiert, einen Hydraulikkreis, der sich zwischen einer Gruppe von einer oder mehreren Arbeitskammern der hydraulischen Maschine und einem oder mehreren der hydraulischen Aktuatoren erstreckt, umfasst,
    wobei jede Arbeitskammer der hydraulischen Maschine ein Niederdruckventil (52), das den Durchfluss von Hydraulikfluid zwischen der Arbeitskammer und einem Niederdruckverteiler (54) reguliert, und ein Hochdruckventil (64), das den Durchfluss von Hydraulikfluid zwischen der Arbeitskammer und einem Hochdruckverteiler (58) reguliert, umfasst,
    wobei die hydraulische Maschine ausgelegt ist, zumindest die Niederdruckventile der Gruppe von einer oder mehreren Arbeitskammern aktiv zu steuern, um die Nettoverdrängung an Hydraulikfluid durch jede Arbeitskammer in jedem Zyklus eines Arbeitskammervolumens und dadurch die Nettoverdrängung an Hydraulikfluid durch die Gruppe von einer oder mehreren Arbeitskammern in Reaktion auf ein Anforderungssignal (94, 380) auszuwählen,
    wobei das Verfahren den Schritt Berechnen des Anforderungssignals in Reaktion auf eine gemessene Eigenschaft des Hydraulikkreises oder eines oder mehrerer Aktuatoren umfasst, wobei das Verfahren einen Quantisierungsschritt umfasst, wobei der Quantisierungsschritt Berechnen eines quantisierten Anforderungssignals, das einen oder eine Mehrzahl von diskreten Werten aufweist, umfasst.
  9. Verfahren nach Anspruch 8, wobei das Verfahren Empfangen des Anforderungssignals (94, 380) und Quantisieren des Anforderungssignals umfasst, optional wobei das Quantisieren des Anforderungssignals Auswählen des diskreten Werts der Mehrzahl von diskreten Werten, der der empfangenen Anforderung am nächsten liegt, umfasst.
  10. Verfahren nach Anspruch 8 oder 9, wobei das Verfahren Ausführen eines Algorithmus zum Bestimmen, ob einzelne Arbeitskammern (84) aktiven Zyklen (88) oder inaktiven Zyklen unterliegen, umfasst.
  11. Verfahren nach einem der Ansprüche 8 bis 10, wobei das Verfahren Empfangen eines Anforderungssignals (94, 380) und Bestimmen einer entsprechenden Reihe von Werten umfasst, wobei die Reihe von Werten einem Muster von aktiven (88) und/oder inaktiven Zyklen eines Arbeitskammervolumens (36) entsprechen, um dadurch das Anforderungssignal zu erfüllen.
  12. Verfahren nach Anspruch 11, wobei das Muster von aktiven (88) und/oder inaktiven Zyklen eines Arbeitskammervolumens (36) eine endliche Zeitdauer aufweist, wobei die endliche Zeitdauer in einem Bereich von akzeptablen Werten mit einer maximalen Zeitdauer von höchstens 0,1 s variieren kann, wobei der Bereich von akzeptablen Werten in Abhängigkeit von einem akzeptablen Frequenzgehalt ausgewählt wird,
    und wobei aus der maximalen Zeitdauer ein akzeptabler endlicher Bereich an Verdrängungsanforderungen (316) in Abhängigkeit von der Anzahl an Zylindern (34) und von dem Betriebsbereich des Antriebsaggregats ausgewählt wird, wobei der akzeptable Bereich an Verdrängungsanforderungen so ausgewählt wird, dass er eine endliche Anzahl an ganzzahligen Bruchteilen der Verdrängungsanforderung umfasst,
    wobei die Nenner der endlichen Anzahl an ganzzahligen Bruchteilen der Verdrängungsanforderung in Abhängigkeit von der Drehzahl der Drehwelle (42) ausgewählt werden,
    optional wobei die Nenner derart ausgewählt werden, dass die Zeitdauer kleiner als die maximale Zeitdauer ist.
  13. Verfahren nach Anspruch 11 oder 12, wobei die Reihe von Werten eine sich wiederholende Abfolge umfasst.
  14. Verfahren nach einem der Ansprüche 8 bis 13, wobei das Verfahren Auswählen einer minimalen zulässigen Frequenz und dann Erstellen einer quantisierten Liste der Mehrzahl von diskreten Werten der Anforderung umfasst, wobei die Werte ausgewählt werden, um ein oder mehrere Muster einer Zylinderaktivierung zu bewirken, wobei die Muster ausschließlich einen Frequenzgehalt über der minimalen zulässigen Frequenz aufweisen.
  15. Verfahren nach einem der Ansprüche 8 bis 13, wobei das Verfahren Auswählen einer minimalen zulässigen Frequenz und dann Erstellen einer quantisierten Liste der Mehrzahl von diskreten Werten der Anforderung umfasst, oder Verfahren nach Anspruch 14, wobei die quantisierte Liste von Werten einer Anforderung von der Anzahl an Zylindern (34) in der Maschine (32) und/oder von der Betriebsdrehzahl der drehbaren Wellen (42) der Maschine abhängt.
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FIEP20186393.3T FI3754121T3 (fi) 2018-09-10 2018-09-10 Hydraulipiirin käsittävä laitteisto
PL20186393.3T PL3754121T3 (pl) 2018-09-10 2018-09-10 Urządzenie zawierające obwód hydrauliczny
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SE545533C2 (en) * 2021-03-04 2023-10-17 Husqvarna Ab A hydraulic system for construction machines and a method for controlling the hydraulic system
CN113697729B (zh) * 2021-10-28 2022-02-18 宁波如意股份有限公司 一种叉车横移旋转联动控制方法及控制系统

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AU641438B2 (en) * 1988-09-29 1993-09-23 Artemis Intelligent Power Ltd. Improved fluid-working machine
KR100407297B1 (ko) * 1994-12-30 2004-05-31 혼다 기켄 고교 가부시키가이샤 내연기관의연료분사제어장치
US7832126B2 (en) * 2007-05-17 2010-11-16 Siemens Industry, Inc. Systems, devices, and/or methods regarding excavating
WO2011034061A1 (ja) * 2009-09-15 2011-03-24 住友重機械工業株式会社 ハイブリッド型建設機械
GB2477996B (en) * 2010-02-23 2014-06-11 Artemis Intelligent Power Ltd Fluid-working machine and method of operating a fluid-working machine
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EP3620581A1 (de) 2020-03-11
EP3754121A1 (de) 2020-12-23

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