WO2023007151A1 - Dispositif de commande et appareil hydraulique utilisant une fluctuation - Google Patents

Dispositif de commande et appareil hydraulique utilisant une fluctuation Download PDF

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Publication number
WO2023007151A1
WO2023007151A1 PCT/GB2022/051960 GB2022051960W WO2023007151A1 WO 2023007151 A1 WO2023007151 A1 WO 2023007151A1 GB 2022051960 W GB2022051960 W GB 2022051960W WO 2023007151 A1 WO2023007151 A1 WO 2023007151A1
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WO
WIPO (PCT)
Prior art keywords
hydraulic
movement
controller
actuator
input signal
Prior art date
Application number
PCT/GB2022/051960
Other languages
English (en)
Inventor
Douglas P ANDERSON
Bennett TORRANCE
John HUTCHESON
Daniel ABRAHAMS
Matteo Pellegri
Christopher Williamson
Luke Wadsley
Connor SZCZEPANIAK
Original Assignee
Danfoss Scotland Limited
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 Danfoss Scotland Limited filed Critical Danfoss Scotland Limited
Publication of WO2023007151A1 publication Critical patent/WO2023007151A1/fr

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Classifications

    • 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
    • E02F9/221—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for generating actuator vibration
    • 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
    • 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
    • F15B21/082—Servomotor systems incorporating electrically operated control means with different modes
    • 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
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/77—Control of direction of movement of the output member
    • F15B2211/7733—Control of direction of movement of the output member providing vibrating movement, e.g. dither control for emptying a bucket

Definitions

  • the present invention relates to a controller for a hydraulic machine, and to a hydraulic apparatus.
  • vibration of the bucket can improve the emptying of the bucket of dirt or soil, or can improve the ability of the edge of the bucket to penetrate into a region of material to be excavated.
  • a dedicated vibration component can be used which is arranged to introduce a required vibration to the movement of the mechanical component.
  • a controller for a hydraulic machine the hydraulic machine in a hydraulic circuit including a hydraulic actuator, having a rotatable shaft in driven engagement with a prime mover, and defining a plurality of working chambers in the hydraulic circuit.
  • Each working chamber is defined partially by a movable working surface mechanically coupled to the rotatable shaft, such that, in operation, the hydraulic machine exchanges energy with the hydraulic circuit and the prime mover by movement of the working surfaces and the rotatable shaft.
  • the controller is configured to: receive a movement input signal indicative of a demand to move the hydraulic actuator; determine a hydraulic machine control signal depending on the movement input signal and a fluctuation input signal; and control the hydraulic machine to exchange hydraulic fluid with the hydraulic circuit in accordance with the hydraulic machine control signal to cause movement of the hydraulic actuator in accordance with the movement input signal and the fluctuation input signal.
  • the hydraulic machine is controlled taking into account both the movement input signal indicative of the demand to move the hydraulic actuator, as well as the fluctuation input signal. Operation of the hydraulic machine causes the hydraulic actuator to move in accordance with both the movement input signal and the fluctuation input signal. Accordingly, the fluctuation in the movement of the hydraulic actuator can be caused by controlling the operation of the hydraulic machine, rather than through a separate component to introduce the fluctuation in movement, or through a manual fluctuation introduced by an operator directly when generating the movement input signal. As a result, fluctuation in the movement of the hydraulic actuator can be achieved using a system having fewer components and/or without requiring constant fluctuation of the input provided by an operator.
  • a fluctuation input signal is typically any signal indicative of a demand to cause a deviation in the movement of the hydraulic actuator, during the movement (including where the demanded movement is zero) of the hydraulic actuator in accordance with the movement input signal.
  • the deviation may be a controlled deviation. Initiating or stopping the fluctuation input signal may be used to control an onset of deviation, and initiating or stopping the signal may be used to control a ceasing of deviation in the movement.
  • the deviation may be sustained for a significant time.
  • the deviation may be an oscillation.
  • the controller may be configured to receive the fluctuation input signal.
  • the fluctuation input signal may be determined by the controller depending on the movement input signal.
  • the fluctuation input signal may be determined depending one or more state signals indicative of a state of the hydraulic actuator.
  • the control of the hydraulic machine to exchange hydraulic fluid with the hydraulic circuit in accordance with the hydraulic machine control signal may be different than if no demand to cause the deviation in the movement is present.
  • the hydraulic machine control signal may be a fluctuating signal. Thus, it may be that the hydraulic machine is controlled to exchange hydraulic fluid with the hydraulic circuit in accordance with the fluctuation input signal.
  • the hydraulic machine control signal is used to control the hydraulic machine.
  • the hydraulic machine control signal may be used to control one or more valves of the hydraulic machine, the one or more valves to control ingress and egress of hydraulic fluid to and from each working chamber.
  • the movement input signal is typically a movement demand input signal.
  • the movement input signal is typically determined or provided before the hydraulic actuator is caused to move in accordance with the movement input signal.
  • the fluctuation input signal is typically a fluctuation demand input signal.
  • the fluctuation input signal is typically determined or provided before the hydraulic actuator is caused to move in accordance with the fluctuation input signal.
  • the present invention extends to a hydraulic apparatus comprising the controller.
  • the hydraulic apparatus may further comprise: a prime mover; a hydraulic circuit; a hydraulic machine having a rotatable shaft in driven engagement with the prime mover and defining a plurality of working chambers in the hydraulic circuit, each working chamber being defined partially by a movable working surface mechanically coupled to the rotatable shaft, such that, in operation, the hydraulic machine exchanges energy with the hydraulic circuit and the prime mover by movement of the working surfaces and the rotatable shaft; and a hydraulic actuator in the hydraulic circuit.
  • the hydraulic machine may exchange energy with the hydraulic circuit by displacing working fluid from at least one of the plurality of working chambers into the hydraulic circuit, orfrom the hydraulic circuit into at least one of the plurality of working chambers.
  • the hydraulic apparatus may include one or more valves in the hydraulic circuit, for controlling routing of hydraulic fluid through the hydraulic circuit.
  • the hydraulic apparatus may include one or more further hydraulic actuators in the hydraulic circuit.
  • the hydraulic apparatus may include one or more further hydraulic machines in the hydraulic circuit.
  • the hydraulic apparatus may further comprise a first input interface for receiving a first user input and configured to provide a movement input signal to the controller depending thereon.
  • the movement input signal may be indicative of a demand to move the hydraulic actuator.
  • an operator can use the first input interface to supply the first user input to request that the hydraulic actuator moves. It will be understood that the fluctuation input signal is typically not determined using the first input interface.
  • the hydraulic apparatus may further comprise a second input interface for receiving a second user input and configured to provide a fluctuation input signal to the controller depending thereon.
  • the fluctuation input signal may be indicative of a demand to cause a deviation in the movement of the hydraulic actuator during the movement of the hydraulic actuator in accordance with the movement input signal.
  • the operator uses the second input interface to supply the second user input to cause a deviation in the movement of the hydraulic actuator.
  • the operator can separately supply the first user input and the second user input, with the second user input only being used to cause fluctuation of the movement of the hydraulic actuator.
  • the second input interface may be separate from the first input interface.
  • the second input interface may comprise a button. It may be that the second input interface is configured to provide the fluctuation input signal only whilst operated. In other examples, it may be that the second input interface is configured to provide the fluctuation input signal for a pre-determined time from operation of the second input interface. The second input interface may be configured to provide the fluctuation input signal only whilst the first user input is not provided to the first input interface.
  • the fluctuation input signal may be indicative of a demand to cause an alternating variation in the movement of the hydraulic actuator.
  • the variation in movement of the hydraulic actuator is in a first sense away from the demanded movement (where that demanded movement may be zero) indicated by the movement input signal, and at a second time during the movement of the hydraulic actuator in accordance with the movement input signal and the fluctuation input signal, the variation in movement of the hydraulic actuator is in a second sense, and said variation may be in position or velocity or acceleration, and is opposite from the first sense, and also away from the demanded movement indicated by the movement input signal.
  • the variation in the movement may alternate between being sometimes in the first sense and sometimes in the second sense. This alternation may be sustained for a significant period of time, such that the hydraulic actuator changes its variation multiple repeated times. In other words, it can be considered that the actuated component of the hydraulic actuator is caused to oscillate or vibrate. This can sometimes be referred to as dither.
  • a frequency of the alternating variation may be greater than 0.5 hertz.
  • the frequency may be less than 50 hertz.
  • the frequency may be between 1 and 20 hertz.
  • the hydraulic actuator may be a linear actuator. In other examples, the hydraulic actuator may be a rotary actuator, such as a wheel motor.
  • the movement input signal may be directly proportional to the first user input received via the first input interface.
  • the movement input signal may be indirectly related to the first user input via another control method such as a pressure control loop. It may be that operation of the first input interface opens a valve, which thus changes the pressure in the system, which causes a change in the pressure control loop, whose output is the movement input signal.
  • the hydraulic actuator may have a first actuator chamber fluidly connected to a first working chamber of the hydraulic machine and a second actuator chamber, opposing the first actuator chamber. External hydraulic actuator force arising from supply of pressurised fluid to the first actuator chamber counteracts and is antagonistic to external force arising from pressure in the second actuator chamber. Thus, the hydraulic actuator can be moved in opposite senses depending on the relative pressures of the first actuator chamber and the second actuator chambers. It may be that the first working chamber is part of a first group of working chambers, configured to operate as one of a pump and a motor, and that the second actuator chamber is fluidly connected to a second chamber of the hydraulic machine. The second working chamber may be part of a second group of working chambers configured to operate as the other one of a pump and a motor, different to the first group of working chambers.
  • the second working chamber may be fluidly connected to a further hydraulic machine.
  • the further hydraulic machine may be a pump, a motor or a pump/motor.
  • the second chamber may be fluidly connected to a fluid reservoir via a throttle valve.
  • the fluid reservoir may be a low pressure fluid reservoir, such as an atmospheric pressure fluid reservoir.
  • the linear actuator may be a double-acting ram.
  • the hydraulic apparatus may be configured to determine the fluctuation input signal depending on determining that the linear actuator is at an end-position of possible movement.
  • the deviation in the movement of the hydraulic actuator can cause the hydraulic actuator to introduce the deviation movement automatically at the end- stops of the linear actuator’s available range of movement.
  • the linear actuator is moving a bucket of an excavator
  • the bucket can be caused to shake to improve emptying of material from the bucket.
  • the hydraulic apparatus may be configured to detect a position of the linear actuator, and to determine the fluctuation input signal depending on the detected position.
  • the position of the linear actuator may be determined by detecting a pressure indicative of the ram being at the end-stop.
  • a limit switch may be provided associated with the actuator and/or a component connected thereto (such as a bucket).
  • the apparatus may be configured such that when the actuator is at a position indicative of the end of the bucket's travel, the limit switch is actuated, and thereby causes determination of the fluctuation input signal to cause the deviation movement.
  • the load increases, and thus the average pressure (over a period of time e.g. 50ms, or number of samples e.g. 100 samples) in the hydraulic machine is increased.
  • This effect can be used, in a similar way to the limit switch, to cause determination of the fluctuation input signal.
  • the increase in pressure can be detected by a pressure sensor (or equivalent means such as using electrical signals generated from a valve solenoid) of the hydraulic apparatus to determine a pressure-related reading for causing determination of the fluctuation input signal when the pressure-related reading satisfies a predetermined threshold.
  • the invention may relate particularly to electronically commutated hydraulic machines which intersperse active cycles of working chamber volume, where there is a net displacement of hydraulic working fluid, with inactive cycles of working chamber volume, where there is no net displacement of hydraulic working fluid between the working chamber and the hydraulic circuit, to achieve a demanded fractional displacement.
  • the majority or all of the active cycles are full stroke cycles, in which the working chambers displace a predetermined maximum displacement of working fluid by suitable control of the timing of valve actuation signals.
  • the controller may be configured (e.g. programmed) to control the low- and optionally high-pressure valves of the working chambers to cause each working chamber to carry out either an active or an inactive cycle of working chamber volume during each cycle of working chamber volume.
  • active cycles we refer to cycles of working chamber volume which make a net displacement of working fluid.
  • active cycles we refer to cycles of working chamber volume which make no net displacement of working fluid (typically where one or both of the low-pressure valve and high-pressure valve remain closed throughout the cycle).
  • active and inactive cycles are interspersed to meet the demand indicated by the demand signal. This contrasts with machines which carry out only active cycles, the displacement of which may be varied.
  • the demand signal for one or more working chambers of the hydraulic machine is typically processed as a ‘displacement fraction’, Fd, being a target fraction of maximum displacement of working hydraulic fluid per rotation of the rotatable shaft.
  • a demand expressed in volumetric terms can be converted to displacement fraction taking into account the current speed of rotation of the rotatable shaft and the number of working chambers connected in a group to the same high pressure manifold and one or more hydraulic components (e.g. the hydraulic actuator) of the hydraulic apparatus.
  • the demand signal relates to a demand for the combined fluid displacement of the group of one or more working chambers fluidically connected to the said one or more hydraulic components of the hydraulic apparatus via the hydraulic circuit. There may be other groups of one or more working chambers fluidically connected to one or more other hydraulic components having respective demand signals.
  • the low-pressure valves are electronically controlled valves
  • the controller or a further controller is configured to control the (e.g. electronically controlled) valves in phased relationship with cycles of working chamber volume to thereby determine the net displacement of hydraulic fluid by each working chamber on each cycle of working chamber volume.
  • the method may comprise controlling the (e.g. electronically controlled) valves in phased relationship with cycles of working chamber volume to thereby determine the net displacement of hydraulic fluid by each working chamber on each cycle of working chamber volume.
  • Groups of one or more working chambers may be dynamically allocated to respective groups of one or more hydraulic components in the hydraulic circuit (e.g. the hydraulic actuator) to thereby change which one or more working chambers are connected to (e.g. a group of) hydraulic components, for example by opening or closing electronically controlled valves (e.g. high-pressure valves and low-pressure valves, described herein), e.g. under the control of a controller.
  • Groups of (e.g. one or more) working chambers may be dynamically allocated to (respective) groups of (e.g. one or more) hydraulic components to thereby change which working chambers of the machine are coupled to which hydraulic components, for example by opening and/or closing (e.g. electronically controlled) valves, e.g.
  • each working chamber can be regulated by regulating the net displacement of the working chamber or chambers which are connected to the hydraulic component or components.
  • Groups of one or more working chambers are typically connected to a respective group of one or more said hydraulic components through a said manifold.
  • each working chamber is independently controllable. It may be that the flow of hydraulic fluid accepted by, or produced by each working chamber can be independently controlled by selecting the net displacement of hydraulic fluid by each working chamber on each cycle of working chamber volume. This selection is typically carried out by the controller.
  • the hydraulic machine is operable as a pump, in a pump operating mode or is operable as a motor in a motor operating mode. It may be that some of the working chambers of the hydraulic machine may pump (and so some working chambers may output hydraulic fluid) while other working chambers of the hydraulic machine may motor (and so some working chambers may input hydraulic fluid).
  • a first group of the working chambers are configured to act as a pump, and a second group of the working chambers are configured to act as a motor
  • at least one of the first group of working chambers is configured to be connected to a first side of the hydraulic actuator, to supply hydraulic fluid to the first side of the hydraulic actuator.
  • At least one of the second group of working chambers may be configured to be connected to a second side of the hydraulic actuator (e.g. opposite the first side), to receive hydraulic fluid from the second side of the hydraulic actuator.
  • the controller may be configured to cause the supply of hydraulic fluid having a first time-varying fluid flow rate to the first side of the hydraulic actuator, and to cause receipt of hydraulic fluid having a second time-varying fluid flow rate from the second side of the hydraulic actuator.
  • first time-varying fluid flow rate is configured to be out of phase with the second time-varying fluid flow rate.
  • oscillation can be introduced into the movement of the hydraulic actuator.
  • the phase difference may be between 45 degrees and 315 degrees, for example approximately 180 degrees.
  • first group of working chambers have been described as being configured to function as a pump
  • second group of working chambers have been described as being configured to function as a motor
  • first group of working chambers may be configured to function as the motor
  • second group of working chambers may be configured to function as the pump, such that the hydraulic actuator moves in the opposite direction.
  • both the first group of working chambers and the second group of working chambers are both configured to function as a pump, or separately both configured to function as a motor.
  • oscillation can be introduced into the movement of the hydraulic actuator.
  • the hydraulic machine may be an electronically commutated hydraulic machine, in which the displacement of hydraulic fluid through the working chambers is regulated by electronically controllable valves.
  • the hydraulic machine may be a variable displacement hydraulic machine.
  • the hydraulic machine may be a pump.
  • the hydraulic machine may be a motor.
  • the hydraulic machine may be a pump/motor.
  • the controller may be configured to determine the hydraulic machine control signal by determining a first signal depending on the fluctuation input signal, and a second signal depending on the movement input signal.
  • the controller may be configured to combine the first signal and the second signal to provide a combined movement input signal, and to determine the hydraulic machine control signal depending on the combined movement input signal.
  • the movement input signal may be modified based on the fluctuation input signal by combining the first signal with the second signal. In some examples, it may be that the first signal is combined with the second signal by summation.
  • the controller may be configured to modify the hydraulic machine control signal to cause resonance in the portion of the hydraulic apparatus moved by the hydraulic actuator (i.e. that is physically connected in some way to the machine in some way).
  • the hydraulic actuator i.e. that is physically connected in some way to the machine in some way.
  • the controller may be configured to determine one or more resonance hydraulic machine control signals known to cause resonance. There will for example be a few of these signals, for each machine speed. Thus, the one or more hydraulic machine control signals that cause resonance of the portion of the hydraulic apparatus moved by the hydraulic actuator can be determined.
  • the controller may be configured to cause movement of the hydraulic actuator at a speed closest to the demanded movement of the hydraulic actuator compared to any other movement of the hydraulic actuator known to cause resonance.
  • the hydraulic machine control signal may be set to the resonance hydraulic machine control signal.
  • the controller may be configured to determine a first hydraulic machine control signal.
  • the first hydraulic machine control signal can be used to control the hydraulic machine to cause a first movement of the hydraulic actuator, less than the demanded movement (e.g. position, velocity, or acceleration), and known to cause resonance.
  • the controller may be further configured to determine a second hydraulic machine control signal.
  • the second hydraulic machine control signal can be used to control the hydraulic machine to cause movement of the hydraulic actuator greater than the demanded movement and known to cause resonance.
  • the hydraulic machine control signal may be set to the first hydraulic machine control signal at a first time, changed to the second hydraulic machine control signal at a second time, and further changed back to the first hydraulic machine control signal at a third time.
  • the hydraulic machine control signal can be dithered between the first hydraulic machine control signal and the second hydraulic machine control signal to cause fluctuation in the movement of the hydraulic actuator relative to the demanded movement.
  • the controller may modulate the hydraulic machine control signal between the first hydraulic machine control signal and the second hydraulic machine control signal in such a proportion that the hydraulic actuator moves, on average, in accordance with the demand to move the hydraulic actuator.
  • the hydraulic machine control signal may be set to the first hydraulic machine control signal for a first proportion of time, to cause movement of the hydraulic actuator at a first average rate and to the second hydraulic machine control signal for a second proportion of time, to cause movement of the hydraulic actuator at a second average rate.
  • the first average rate for the first proportion of time combined with the second average rate for the second proportion of time is equivalent to the rate of the requested movement. In other words, the controller still causes an average movement equivalent to the requested movement.
  • the controller may be configured to receive a variation signal indicative of at least one time-varying movement characteristic of one or both of the hydraulic machine and the hydraulic actuator.
  • the hydraulic machine control signal may be determined in further dependence on the variation signal.
  • the hydraulic machine control signal can be determined taking into account variations and/or instabilities which already exist in the hydraulic machine and/or the hydraulic actuator. It may be that the hydraulic machine control signal is determined so as to reinforce the at least one time-varying characteristic indicated by the variation signal.
  • the variation signal may be combined with the movement input signal. It may be that at least one time-varying component of the variation signal is combined with the movement input signal. The at least one time-varying component of the variation signal may be combined with the movement input signal by summation.
  • the two signals can still be combined and will result in increasing the variations in movement caused by the instabilities which already exist in the hydraulic machine and/or the hydraulic actuator.
  • Any phase difference may be less than 90 degrees, for example less than 45 degrees.
  • the variation signal and the movement input signal can be substantially in-phase. Thus, the movements can be reinforced.
  • the controller may be configured to determine the time-varying component of the variation signal by applying a high pass filter to the variation signal.
  • the variation signal is indicative of a physical movement characteristic, such as a pressure, a position or a speed of movement of the one or both of the hydraulic machine and the hydraulic actuator.
  • the low frequency components of the variation signal can be omitted in the time-varying component of the variation signal, leaving only the time varying component thereof.
  • techniques other than the high-pass filter may be used to obtain a hydraulic machine control signal suitable to exaggerate fluctuation of the movement of the hydraulic actuator and/or the hydraulic machine.
  • the controller is configured to determine a difference between the variation signal and the demanded movement of the hydraulic actuator, and to determine the fluctuation input signal depending on the determined difference. It may be that the hydraulic machine control signal is determined as the combination of the movement input signal and the determined difference.
  • the controller may be configured to restrict at least a portion of the variation signal.
  • the movements are not reinforced to such an extent that the movement of the hydraulic actuator becomes unwieldy or extreme.
  • the controller is configured to restrict the portion of the variation signal using dynamic saturation.
  • the controller is configured to restrict the portion of the variation signal using signal compression.
  • the controller may be configured to determine the hydraulic machine control signal depending on receiving a value from a resonance lookup table.
  • the resonance values can be pre-determined and retrieved when needed.
  • a resonance lookup table is a table of known values of a parameter, the values expected to cause resonance in the portion of the hydraulic apparatus moved by the hydraulic actuator.
  • the controller may be configured to combine the value from the resonance lookup table with the movement input signal to determine the combined movement input signal, and to determine the hydraulic machine control signal depending on the combined movement input signal.
  • the controller may be configured to cause movement of the hydraulic actuator in response to a calibration signal, and determine one or more values for the lookup table based on a resultant movement of the hydraulic actuator in response to the calibration signal.
  • the lookup table can be populated based on movement of the hydraulic actuator during calibration.
  • the controller may be configured to cause movement of the hydraulic actuator in accordance with a displacement chirp pattern demand in response to the calibration signal.
  • the controller may be configured to demand a step movement of the hydraulic actuator in response to the calibration signal.
  • the resulting movement of the hydraulic actuator may be measured.
  • One or more values to be populated into the lookup table may be determined based on the measured movement of the hydraulic actuator.
  • oscillation or decay of the movement of the hydraulic actuator can be used to determine the resonant properties of the portion of the hydraulic apparatus moved by the hydraulic actuator. It may be that the values in the lookup table are changed and/or re-populated.
  • the movement of the hydraulic actuator in response to the calibration signal may be performed after the movement input signal is received, but before the hydraulic machine is controlled in accordance with the hydraulic machine control signal.
  • Such embodiment is more likely to be of use, and to be acceptable, in an automated system rather than one with hydraulic actuator which is controlled directly by human operator.
  • the calibration movement of the hydraulic actuator may be performed immediately before the demanded movement of the hydraulic actuator, so that the portion of the hydraulic apparatus moved by the hydraulic actuator has substantially the same physical properties during calibration as during use.
  • the movement of the hydraulic actuator in response to the calibration signal may be performed during an idle time of the hydraulic actuator. Thus, no delay is introduced between the operator demanding movement of the hydraulic actuator and the hydraulic actuator’s movement in accordance with the demand.
  • the idle time is typically before the movement input signal is received.
  • the lookup table may be a multi-dimensional lookup table. Thus, the value may be retrieved from the lookup table depending on multiple variables.
  • the variables may include one or more of a mass of the portion of the hydraulic apparatus moved by the hydraulic actuator (including any load), temperature, pressure, position of actuator, and demanded movement speed.
  • the controller may comprise one or more processors and a memory configured to store instructions which when executed by the one or more processors cause the hydraulic apparatus to carry out the functions of the controller described herein.
  • the memory may be non-transitory, computer readable memory.
  • the memory may have the instructions stored thereon.
  • the present invention extends to a non-transitory computer-readable medium (e.g. memory) having the instructions stored thereon to control the apparatus as described herein.
  • the memory may be solid-state memory.
  • the controller may be provided in a single device. In other example, the controller may be distributed, having a plurality of processors. A first processor may be separated from a second processor in a distributed manner.
  • the present invention extends to a vehicle comprising the hydraulic apparatus.
  • the present invention extends to a method of controlling a hydraulic machine in a hydraulic circuit with a hydraulic actuator.
  • the hydraulic machine may be as described hereinbefore.
  • the method comprises: receiving a movement input signal indicative of a demand to move the hydraulic actuator; determining a hydraulic machine control signal depending on the movement input signal and a fluctuation input signal; and controlling the hydraulic machine to exchange hydraulic fluid with the hydraulic circuit in accordance with the hydraulic machine control signal to cause movement of the hydraulic actuator in accordance with the movement input signal and the fluctuation input signal.
  • the method may also include any of the steps performed by the controller as elsewhere described herein.
  • Figure 1 is a schematic illustration of an example of hydraulic apparatus as described herein;
  • Figure 2 is a schematic illustration of an example of hydraulic apparatus as described herein;
  • Figure 3 is a schematic illustration of systems of a vehicle according to an example of the present disclosure
  • Figure 4 is a flowchart illustrating a method of controlling a hydraulic machine as described herein.
  • Figure 5 is a schematic diagram of an example of a hydraulic machine. Detailed Description of an Example Embodiment
  • FIG. 1 is a schematic illustration of an example of hydraulic apparatus as described herein.
  • the hydraulic apparatus 100 comprises a hydraulic machine 110 in a hydraulic circuit 120.
  • a hydraulic actuator 130 is fluidly connected to the hydraulic machine 110 via the hydraulic circuit 120.
  • the hydraulic apparatus is part of an excavator, including a bucket 140 which can be pivoted by operation of the hydraulic actuator 130.
  • the hydraulic apparatus 100 further comprises a controller 150 for controlling the operation of the hydraulic machine 110 to thereby cause movement of the bucket 140 mechanically connected to the hydraulic actuator 130.
  • the hydraulic apparatus 100 also comprises a first input interface 160 in the form of a joystick control 160 and a second input interface 170 in the form of a pushbutton 170, provided on an end of the joystick control 160.
  • the controller 150 is configured to receive a movement input signal 165 from operation of the joystick control 160, and a fluctuation input signal 175 caused by operation of the pushbutton 170.
  • the fluctuation input signal 175 is in the form of a sinusoidally varying alternating signal 175.
  • the controller 150 is configured to determine a hydraulic machine control signal 115 by combining the movement input signal 165 with the fluctuation input signal 175, in this instance by summing the movement input signal 165 and the fluctuation input signal 175.
  • the hydraulic machine control signal 115 is used to control the hydraulic machine 110 to exchange energy in the form of hydraulic fluid with the hydraulic circuit 120 at a flow rate indicated by the hydraulic machine control signal 115.
  • the hydraulic machine 110 is a pump/motor 110, as described further with reference to Figure 5 hereinafter.
  • the hydraulic machine control signal 115 will cause the hydraulic machine 110 to exchange hydraulic fluid with the hydraulic circuit 120 at a substantially steady flow-rate, determined by the position of the joystick control 160.
  • the hydraulic machine 110 is controlled to operate as a pump and to pump hydraulic fluid into the hydraulic circuit 120, towards the hydraulic actuator 130, to cause retraction of the ram of the hydraulic actuator 130.
  • the joystick control 160 is moved in a second direction, opposite the first direction, (e.g.
  • the hydraulic machine 110 is controlled to operate as a motor and to draw hydraulic fluid from the hydraulic circuit 120 through the hydraulic machine 110, away from the hydraulic actuator 130, to cause extension of the ram of the hydraulic actuator 130.
  • the hydraulic machine 110 is controlled to operate as a pump to supply pressurised fluid to the hydraulic actuator, to cause respective extension.
  • the opposite actuator motion may be realised by a simple cross-over spool valve, located upstream, to pressurise the opposing piston face.
  • the hydraulic machine control signal 115 also includes a fluctuation component, causing the hydraulic machine 110 to exchange hydraulic fluid with the hydraulic circuit 120 at a cyclically-varying flow rate.
  • the frequency of variation in the flow rate is the same as the frequency of the variation signal 175.
  • the cyclically-varying flow rate causes a cyclically-varying dither in the movement of the hydraulic actuator 130, and therefore in the movement of the bucket 140.
  • the pushbutton 170 is operated, but the joystick control 160 is not operated (e.g. where no input is provided to the joystick control 160)
  • a fluctuation input signal 175 is generated but the movement input signal will be zero, resulting in no net movement of the actuator, but a relatively small oscillating movement of the actuator.
  • FIG 2 is a schematic illustration of an example of hydraulic apparatus as described herein.
  • the hydraulic apparatus 200 functions similarly to the hydraulic apparatus 100 described with reference to Figure 1, though only the hydraulic actuator 230 and hydraulic machines 210a, 210b, are shown.
  • the hydraulic actuator 230 is in the form of a double-acting ram 230 having a movable rod 236, a first actuator chamber 232 and a second actuator chamber 234.
  • the first actuator chamber 232 is fluidly connected to a first hydraulic machine 210a, in the form of a motor 210a, via a hydraulic circuit first portion 222.
  • the motor 210a is configured to extract hydraulic fluid from the hydraulic circuit first portion 222.
  • the second actuator chamber 234 is fluidly connected to a second hydraulic machine 210b, in the form of a pump 210b, via a hydraulic circuit second portion 224.
  • the pump 210b is configured to supply hydraulic fluid to the hydraulic fluid second portion 224.
  • each may be a separate hydraulic machine 210a, 210b, such as two pump/motors, or each may represent a different groups of working chambers of the same pump/motor, such that the first hydraulic machine 210a is provided by a first group of working chambers of a hydraulic machine and the second hydraulic machine 210b is provided by a second group of working chambers of the same hydraulic machine.
  • the hydraulic apparatus 200 is operated in the configuration shown in Figure 2, with the first hydraulic machine 210a in the form of a motor 210a and the second hydraulic machine 210b in the form of a pump 210b, it will be understood that the rod 236 will be retracted due to a reduction in the volume of the first actuator chamber 232, and an expansion in the volume of the second actuator chamber 234.
  • a first periodically-varying flowrate is caused by the first hydraulic machine 210a
  • a second periodically- varying flowrate is caused by the second hydraulic machine 210b.
  • the first periodically-varying flowrate is in the opposite sense, of differing average flowrate and phase- shifted with respect to the second periodically-varying flowrate, to enhance the vibration of the movement of the rod 236. It may be that both sides act as pumps, but with differing average flowrates and/or phases, in such a way that either there is no net movement of the actuator, or that there is a net movement, due to the difference in the average flowrates of each side of the actuator.
  • FIG. 3 is a schematic illustration of systems of a vehicle according to an example of the present disclosure.
  • the vehicle 300 comprises hydraulic apparatus 310 as described herein, such as in the form of a hydraulic machine 310, and a controller 320.
  • the controller 320 is configured to exchange signals 325 with the hydraulic apparatus 310 to control the hydraulic apparatus 310 in accordance with input signals received by the controller 320, for example from user inputs by an operator of the vehicle 300.
  • the controller 320 in this example is realised by one or more processors 330 and a computer-readable memory 340.
  • the memory 340 stores instructions which, when executed by the one or more processors 330, cause the hydraulic apparatus 310 to operate as described herein.
  • controller 320 is shown as being part of the vehicle 300, it will be understood that one or more components of the controller 320, or even the whole controller 320 can be provided separate from the vehicle 300, for example remotely from the vehicle 300, to exchange signals with the vehicle 300 by wireless communication.
  • FIG. 4 is a flowchart illustrating a method of controlling a hydraulic machine as described herein.
  • the method 400 comprises determining a hydraulic machine control signal depending on a movement input signal and a fluctuation input signal, and controlling a hydraulic machine in accordance with the hydraulic machine control signal.
  • the method 400 comprises receiving 410 a demand to move the hydraulic actuator.
  • a movement input signal is indicative of the demand to move the hydraulic actuator.
  • the method 400 further comprises determining 420 a hydraulic machine control signal depending on the movement input signal and a fluctuation input signal.
  • the method 400 further comprises controlling 430 the hydraulic machine to exchange hydraulic fluid with the hydraulic circuit in accordance with the hydraulic machine control signal.
  • the hydraulic actuator is caused to move in accordance with the movement input signal and the fluctuation input signal.
  • Figure 5 is a schematic diagram of part of the hydraulic apparatus shown in Figures 1a and 1b, and shows a single group of working chambers currently connected to one or more hydraulic components (e.g. an actuator) through a high pressure manifold 554.
  • Figure 5 provides detail on the first group 500, said group comprises a plurality of working chambers (8 are shown) having cylinders 524 which have working volumes 526 defined by the interior surfaces of the cylinders and pistons 528 (providing working surfaces 528) which are driven from a rotatable shaft 530 by an eccentric cam 532 and which reciprocate within the cylinders to cyclically vary the working volume of the cylinders.
  • the rotatable shaft is firmly connected to and rotates with a drive shaft.
  • a shaft position and speed sensor 534 sends electrical signals through a signal line 536 to a controller 550, which thus enables the controller to determine the instantaneous angular position and speed of rotation of the shaft, and to determine the instantaneous phase of the cycles of each cylinder.
  • the working chambers are each associated with Low Pressure Valves (LPVs) in the form of electronically actuated face-sealing poppet valves 552, 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 554, which may connect one or several working chambers, or indeed all as is shown here, to the low-pressure hydraulic fluid manifold hydraulic circuit.
  • 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.
  • the valves may alternatively be normally closed valves. As well as force arising from the pressure difference across the valve, flow forces from the passage of fluid across the valve, also influence the net force on the moving valve member.
  • the working chambers are each further associated with a respective High-Pressure Valve (HPV) 564 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 through a valve block to a high-pressure hydraulic fluid manifold 558, which may connect one or several working chambers, or indeed all as is shown in Figure 5.
  • 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 562 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 controller selects the net rate of displacement of hydraulic fluid, displaced 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 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 566 may protect the first group from damage.
  • the controller (320) is configured to: receive a movement input signal indicative of a demand to move the hydraulic actuator; determine a hydraulic machine control signal depending on the movement input signal and a fluctuation input signal; and control the hydraulic machine (310) to exchange hydraulic fluid with the hydraulic circuit in accordance with the hydraulic machine control signal to cause movement of the hydraulic actuator in accordance with the movement input signal and the fluctuation input signal.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)

Abstract

L'invention concerne un dispositif de commande (320) pour une machine hydraulique (310), la machine hydraulique (310) dans un circuit hydraulique comprenant un actionneur hydraulique, ayant un arbre rotatif en prise entraînée avec un moteur d'entraînement, et définissant une pluralité de chambres de travail dans le circuit hydraulique, chaque chambre de travail étant définie partiellement par une surface de travail mobile couplée mécaniquement à l'arbre rotatif, de telle sorte que, en fonctionnement, la machine hydraulique (310) échange de l'énergie avec le circuit hydraulique et le moteur principal par déplacement des surfaces de travail et de l'arbre rotatif. Le dispositif de commande (320) est configuré pour : recevoir un signal d'entrée de mouvement indicatif d'une demande pour déplacer l'actionneur hydraulique ; déterminer un signal de commande de la machine hydraulique en fonction du signal d'entrée de mouvement et d'un signal d'entrée de fluctuation ; et commander la machine hydraulique (310) pour échanger un fluide hydraulique avec le circuit hydraulique en fonction du signal de commande de machine hydraulique pour provoquer le mouvement de l'actionneur hydraulique en fonction du signal d'entrée de mouvement et du signal d'entrée de fluctuation.
PCT/GB2022/051960 2021-07-26 2022-07-26 Dispositif de commande et appareil hydraulique utilisant une fluctuation WO2023007151A1 (fr)

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Application Number Priority Date Filing Date Title
EP21187784.0 2021-07-26
EP21187784.0A EP4124695A1 (fr) 2021-07-26 2021-07-26 Organe de commande et appareil hydraulique utilisant des signaux fluctuants pour le movement d'une actuateur hydraulique

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Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5287699A (en) * 1990-01-16 1994-02-22 Kabushiki Kaisha Komatsu Seisakusho Automatic vibration method and device for hydraulic drilling machine
JPH08165678A (ja) * 1994-12-12 1996-06-25 Yanmar Diesel Engine Co Ltd 掘削制御装置
US20040176894A1 (en) * 2003-03-07 2004-09-09 Deere & Company, A Delaware Corporation Valve command signal processing system
US20090056322A1 (en) * 2007-09-05 2009-03-05 Caterpillar Inc. System and method for rapidly shaking an implement of a machine
WO2016180686A1 (fr) * 2015-05-11 2016-11-17 Caterpillar Sarl Dispositif de vibration automatique d'engin de chantier
US20180180067A1 (en) * 2016-12-23 2018-06-28 Robert Bosch Gmbh Hydraulic system and method of operating the same
US20190093310A1 (en) * 2017-09-27 2019-03-28 Deere & Company Implement vibration system and method
EP3620583A1 (fr) * 2018-09-10 2020-03-11 Artemis Intelligent Power Limited Vehicule industriel avec controle de couple de la machine hydraulique
EP3748155A1 (fr) * 2019-06-04 2020-12-09 Danfoss Scotland Limited Machines et systèmes hydrauliques

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5287699A (en) * 1990-01-16 1994-02-22 Kabushiki Kaisha Komatsu Seisakusho Automatic vibration method and device for hydraulic drilling machine
JPH08165678A (ja) * 1994-12-12 1996-06-25 Yanmar Diesel Engine Co Ltd 掘削制御装置
US20040176894A1 (en) * 2003-03-07 2004-09-09 Deere & Company, A Delaware Corporation Valve command signal processing system
US20090056322A1 (en) * 2007-09-05 2009-03-05 Caterpillar Inc. System and method for rapidly shaking an implement of a machine
WO2016180686A1 (fr) * 2015-05-11 2016-11-17 Caterpillar Sarl Dispositif de vibration automatique d'engin de chantier
US20180180067A1 (en) * 2016-12-23 2018-06-28 Robert Bosch Gmbh Hydraulic system and method of operating the same
US20190093310A1 (en) * 2017-09-27 2019-03-28 Deere & Company Implement vibration system and method
EP3620583A1 (fr) * 2018-09-10 2020-03-11 Artemis Intelligent Power Limited Vehicule industriel avec controle de couple de la machine hydraulique
EP3748155A1 (fr) * 2019-06-04 2020-12-09 Danfoss Scotland Limited Machines et systèmes hydrauliques

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