EP4163446A1 - Method and control system for a hydraulic circuit of a work vehicle - Google Patents

Method and control system for a hydraulic circuit of a work vehicle Download PDF

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Publication number
EP4163446A1
EP4163446A1 EP22199761.2A EP22199761A EP4163446A1 EP 4163446 A1 EP4163446 A1 EP 4163446A1 EP 22199761 A EP22199761 A EP 22199761A EP 4163446 A1 EP4163446 A1 EP 4163446A1
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EP
European Patent Office
Prior art keywords
hydraulic
value
hydraulic pump
rotation speed
prime mover
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.)
Pending
Application number
EP22199761.2A
Other languages
German (de)
French (fr)
Inventor
Antonio Venezia
Andrea Gravili
Stefano Liberti
Adriano GARRAMONE
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CNH Industrial Italia SpA
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CNH Industrial Italia SpA
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Filing date
Publication date
Application filed by CNH Industrial Italia SpA filed Critical CNH Industrial Italia SpA
Publication of EP4163446A1 publication Critical patent/EP4163446A1/en
Pending legal-status Critical Current

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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
    • E02F9/2246—Control of prime movers, e.g. depending on the hydraulic load of work tools
    • 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
    • E02F9/2058—Electric or electro-mechanical or mechanical control devices of vehicle sub-units
    • E02F9/2062—Control of propulsion units
    • E02F9/207—Control of propulsion units of the type electric propulsion units, e.g. electric motors or generators
    • 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
    • F04B49/08—Regulating by delivery pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/05—Pressure after the pump outlet
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/11—Outlet temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant 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
    • F15B2211/60—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
    • F15B2211/6343—Electronic controllers using input signals representing a temperature
    • 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
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed

Definitions

  • the present invention relates to the field of hydraulic circuits and in particular of the type comprising an electro-hydraulic circuit for the actuation of at least one hydraulic member, including an arm and/or a bucket.
  • the hydraulic circuit is powered by a hydraulic pump driven in rotation by a prime mover, very often an internal combustion engine.
  • a hydraulic pump driven in rotation by a prime mover
  • electric motors such as a hydraulic circuit for the actuation of at least one hydraulic actuator enslaved to the movement of a hydraulic work member.
  • hydraulic work member it is meant one of those components such as arms, buckets, etc .. distinct and separate from those inherent to the movement of the work vehicle, such as for example transmissions, braking systems, etc.
  • hydraulic member meaning a “working hydraulic member”.
  • the lifting and lowering of the arm is carried out by means of at least one double-action linear hydraulic actuator. It includes a pair of opposing chambers, which fill and empty alternately to raise or lower the arm.
  • the valve for controlling a hydraulic actuator is generally controlled by the operator using a joystick placed in the vehicle's cockpit.
  • the electrical signal generated by the joystick is acquired by a processing unit, which processes it to control the directional control valve.
  • the directional control valve is evidently of the electro-hydraulic type.
  • the volumetric efficiency of a hydraulic pump essentially depends on the pressure, i.e. the load applied to the hydraulic member, and on the temperature of the hydraulic oil. Indeed, the temperature affects the viscosity of the hydraulic oil.
  • the theoretical or nominal flow rate Qn of a hydraulic pump is defined as the product between the volumetric efficiency V and the rotation speed of the pump RPMn. Under these conditions it is assumed that the volumetric efficiency is unitary. This definition can be identified, for example, in the manual" Oleodinamica e Pneumatica" prof. Nicola Nervegna, Edition May 2003 POLITEKO .
  • a change in volumetric efficiency involves a change in the flow of hydraulic oil generated by the hydraulic pump.
  • the manufacturers of hydraulic pumps provide tables that describe the efficiency of the pump as a function of pressure in a predetermined sub-temperature range. Therefore, considering the entire operating temperature range of a hydraulic pump, the manufacturer provides as many tables as there are sub-ranges or temperature values into which the entire temperature range is divided.
  • the lever When the hydraulic pump is driven in rotation by an electric motor, the lever, generally a joystick placed in the vehicle cabin, controlling the hydraulic actuator controls both the opening of the directional valve and the rotation speed of the electric motor.
  • the object of the present invention is to indicate a method and system for controlling a hydraulic circuit of a work vehicle in particular to improve the response of the hydraulic circuit to the requests of an operator.
  • the idea is to compensate for the volumetric efficiency variability of the hydraulic pump by correcting the rotation speed of the prime mover.
  • FIG 1 shows an example of an electro-hydraulic circuit for powering a hydraulic actuator A1, A2 shown in figure 2 .
  • the hydraulic circuit HC is powered by a fixed displacement hydraulic pump P, driven in rotation by an electric prime mover E, powered by battery or fuel cells.
  • the pump draws oil from a storage tank T and sends it to a directional valve (not shown).
  • the actuator extracts or retracts its shaft allowing the relative working member to move in two opposite directions.
  • the arm B of the compact wheel loader CWL of figure 2 raises or lowers.
  • the lever JOYSTICK preferably arranged in the cab of the work vehicle CWL, in relation to the deflection imposed by an operator, is capable of generating an electrical signal, detected by a control unit CONTROL UNIT.
  • the control unit on the basis of this electrical signal, is configured to generate a control signal for the directional valve and to control the prime mover E.
  • the control unit commands the opening of the directional valve and at the same time the rotation speed of the prime mover E.
  • a pressure sensor PS and a temperature sensor TS are associated with the delivery port of the hydraulic pump. These sensors are operationally connected with the control unit.
  • the volumetric efficiency tables supplied by the manufacturer of the hydraulic pump or experimentally detected on the work vehicle are stored in the control unit, so that according to the volumetric efficiency the rotation speed of the prime mover is increased in order to compensate for the effects on the flow of hydraulic oil generated by the hydraulic pump.
  • the real flow rate Qr Er * V * RPMn, where Er is the real volumetric efficiency lower than 1, V the displacement of the hydraulic pump P and RPMn the nominal speed of rotation of the hydraulic pump as a function of the angular position of the control lever.
  • the value of the RPMn speed is a function of the deflection of the control lever of the hydraulic actuator according to a linear proportional factor.
  • Th is a settable threshold.
  • the process can iterate as long as the real flow differs by less than a predetermined threshold Th from the theoretical flow rate or it can be stopped after a predetermined number of iterations.
  • the correct rotation speed values (RPMc2, RPMc3, .., RPMcn) for each of the 2,3, .. n iterations subsequent to the first are preferably calculated as the average of the last two values previously identified. Thanks to the present invention, regardless of the temperature conditions of the hydraulic oil and the load applied to the mechanical member, an angular position of the control lever corresponds to approximately the same flow generated by the hydraulic pump.
  • the method object of the present invention can be summarized by the following steps:
  • the iterative process performs a gradual change in the rotation speed of the hydraulic pump.
  • the volumetric efficiency value is calculated on the basis of the variation of the rotation speed, of a temperature and pressure value measured by the sensors TS and PS, in order to force the real flow Qr of hydraulic oil pumped by the hydraulic pump to converge towards the theoretical value Qn.
  • the wording "..is far more (or less) than said predetermined threshold Th of said theoretical flow rate value Qn" means that a given value is outside (or inside) an interval having an width equal to the threshold Th and centered on the flow rate theoretical value.
  • the present invention can be advantageously carried out by means of a computer program, which comprises coding means for carrying out one or more steps of the method, when this program is executed on a computer. Therefore, it is intended that the scope of protection extends to said computer program and further to computer readable means comprising a recorded message, said computer readable means comprising program coding means for carrying out one or more steps of the method, when said program is run on a computer.

Abstract

Method of controlling a hydraulic circuit of a work vehicle, the vehicle comprising a hydraulic circuit (HC) operatively connected to a fixed displacement hydraulic pump (P) and a prime mover (E) arranged to drive the hydraulic pump in rotation, said prime mover (E), electric, a hydraulic actuator (A1) arranged to be powered by the hydraulic circuit, and in which the hydraulic circuit comprises a supply valve of the hydraulic actuator (A1), a lever (JOYSTICK) for controlling said feed valve and said prime mover (E), a temperature sensor (TS) and a pressure sensor (PS) operatively associated with a delivery port of the hydraulic pump (P), the method comprising an iterative process of variation of the rotation speed of the hydraulic pump which provides for the recalculation of a volumetric efficiency value based on a variation of the rotation speed, in order to force the real flow (Qr) of ol I hydraulic to converge towards the theoretical flow (Qn) of hydraulic oil pumped by the hydraulic pump.

Description

    Field of the invention
  • The present invention relates to the field of hydraulic circuits and in particular of the type comprising an electro-hydraulic circuit for the actuation of at least one hydraulic member, including an arm and/or a bucket.
    • State of the art
  • In the field of work and agricultural vehicles, the operation of users, such as arms and related tools, is carried out by means of a hydraulic circuit.
  • The hydraulic circuit is powered by a hydraulic pump driven in rotation by a prime mover, very often an internal combustion engine. However, the progressive technological development of battery power systems makes it possible to design work vehicles with electric traction and/or with hydraulic systems operated by electric motors, such as a hydraulic circuit for the actuation of at least one hydraulic actuator enslaved to the movement of a hydraulic work member.
  • By "hydraulic work member" it is meant one of those components such as arms, buckets, etc .. distinct and separate from those inherent to the movement of the work vehicle, such as for example transmissions, braking systems, etc. Hereinafter, for convenience, reference is made to a "hydraulic member" meaning a "working hydraulic member".
  • In working machines the most known and implemented members are the arms equipped with bucket or forks or other devices.
  • The lifting and lowering of the arm is carried out by means of at least one double-action linear hydraulic actuator. It includes a pair of opposing chambers, which fill and empty alternately to raise or lower the arm.
  • The valve for controlling a hydraulic actuator is generally controlled by the operator using a joystick placed in the vehicle's cockpit.
  • The electrical signal generated by the joystick is acquired by a processing unit, which processes it to control the directional control valve. The directional control valve is evidently of the electro-hydraulic type.
  • Wear of the hydraulic pump or a malfunction in the hydraulic circuit can lead to unexpected behaviour of the actuator or the inability to lift a load.
  • The volumetric efficiency of a hydraulic pump essentially depends on the pressure, i.e. the load applied to the hydraulic member, and on the temperature of the hydraulic oil. Indeed, the temperature affects the viscosity of the hydraulic oil.
  • The theoretical or nominal flow rate Qn of a hydraulic pump is defined as the product between the volumetric efficiency V and the rotation speed of the pump RPMn. Under these conditions it is assumed that the volumetric efficiency is unitary. This definition can be identified, for example, in the manual" Oleodinamica e Pneumatica" prof. Nicola Nervegna, Edition May 2003 POLITEKO.
  • A change in volumetric efficiency involves a change in the flow of hydraulic oil generated by the hydraulic pump.
  • The manufacturers of hydraulic pumps provide tables that describe the efficiency of the pump as a function of pressure in a predetermined sub-temperature range. Therefore, considering the entire operating temperature range of a hydraulic pump, the manufacturer provides as many tables as there are sub-ranges or temperature values into which the entire temperature range is divided.
  • When the hydraulic pump is driven in rotation by an electric motor, the lever, generally a joystick placed in the vehicle cabin, controlling the hydraulic actuator controls both the opening of the directional valve and the rotation speed of the electric motor.
  • There is an approximately linear relationship between the angle of deviation of the joystick and the opening of the directional valve and between the angle of deviation of the joystick and the speed of rotation of the motor.
  • However, in relation to the operating conditions, the behavior of the hydraulic member may appear significantly different.
  • If not specifically excluded in the detailed description that follows, what is described in this chapter is to be considered as an integral part of the detailed description.
    • Summary of the invention
  • The object of the present invention is to indicate a method and system for controlling a hydraulic circuit of a work vehicle in particular to improve the response of the hydraulic circuit to the requests of an operator.
  • The basic idea of the present invention is to calculate the effective flow rate of the hydraulic pump on the basis of
    • The position of the control lever of the directional valve,
    • The temperature of the hydraulic oil,
    • The pressure at the delivery port of the hydraulic pump, and to modify the rotation speed of the electric motor in order to generate a flow of hydraulic oil which is exclusively a function of the position of the control lever and independent of the volumetric efficiency of the hydraulic pump which in turn is a function of the temperature and pressure at the port of the hydraulic pump.
  • In other words, the idea is to compensate for the volumetric efficiency variability of the hydraulic pump by correcting the rotation speed of the prime mover.
  • This means that in order to obtain a preordained flow of hydraulic oil, in conditions of halving the volumetric efficiency, the rotation speed of the prime mover approximately doubles.
  • This means that for the operator who controls the vehicle, the hydraulic system responds in a predictable and transparent way to the changes in terms of pressure and temperature.
  • The dependent claims describe preferred variants of the invention, forming an integral part of this description.
    • Brief description of the figures
  • Further objects and advantages of the present invention will become clear from the following detailed description of an example of its embodiment (and its variants) and from the attached drawings given purely for explanatory and non-limiting purposes, in which:
    • Figure 1 shows a preferred variant of an electro-hydraulic circuit modified according to the present invention;
    • Figure 2 shows an example of a work vehicle in which the present invention is implemented;
    • Figure 3 shows a volumetric efficiency diagram at different rotation speeds of the hydraulic pump as the pressure at the port of the hydraulic pump varies and for a given temperature value;
    • Figure 4 shows an exemplary flow chart of the present invention.
  • The same reference numbers and letters in the figures identify the same elements or components or functions.
  • It should be noted that the terms "first", "second", "third", "upper", "lower" and the like can be used here to distinguish various elements. These terms do not imply a spatial, sequential or hierarchical order for the modified elements unless specifically indicated or inferred from the text.
  • The elements and features illustrated in the various preferred embodiments, including the drawings, can be combined with each other without however departing from the scope of this application as described below.
    • Detailed description of exemplary embodiments
  • Figure 1 shows an example of an electro-hydraulic circuit for powering a hydraulic actuator A1, A2 shown in figure 2. The hydraulic circuit HC is powered by a fixed displacement hydraulic pump P, driven in rotation by an electric prime mover E, powered by battery or fuel cells.
  • The pump draws oil from a storage tank T and sends it to a directional valve (not shown).
  • In figure 1, the remaining electro-hydraulic circuit is summarized with the block "HYDRAULIC FUNCTIONS".
  • In relation to the chamber fed by the hydraulic circuit, the actuator extracts or retracts its shaft allowing the relative working member to move in two opposite directions. For example, the arm B of the compact wheel loader CWL of figure 2 raises or lowers.
  • The lever JOYSTICK, preferably arranged in the cab of the work vehicle CWL, in relation to the deflection imposed by an operator, is capable of generating an electrical signal, detected by a control unit CONTROL UNIT.
  • The control unit, on the basis of this electrical signal, is configured to generate a control signal for the directional valve and to control the prime mover E. In particular, on the basis of this electrical signal, the control unit commands the opening of the directional valve and at the same time the rotation speed of the prime mover E.
  • A pressure sensor PS and a temperature sensor TS are associated with the delivery port of the hydraulic pump. These sensors are operationally connected with the control unit. The volumetric efficiency tables supplied by the manufacturer of the hydraulic pump or experimentally detected on the work vehicle are stored in the control unit, so that according to the volumetric efficiency the rotation speed of the prime mover is increased in order to compensate for the effects on the flow of hydraulic oil generated by the hydraulic pump.
  • The real flow rate Qr = Er * V * RPMn,
    where Er is the real volumetric efficiency lower than 1, V the displacement of the hydraulic pump P and RPMn the nominal speed of rotation of the hydraulic pump as a function of the angular position of the control lever.
  • As mentioned above, the value of the RPMn speed is a function of the deflection of the control lever of the hydraulic actuator according to a linear proportional factor.
  • It is worth noting that the efficiency is also a function of the pump rotation speed and therefore the symbol Er shows the subscript "r" to indicate that as the pump rotation speed varies, the efficiency curve also varies. A bundle of efficiency curves is shown in the exemplary diagram of Figure 3 for a given temperature value (T = 80 ° C) or temperature range.
  • To compensate for the fact that the volumetric efficiency Er is a value lower than unity, according to the present invention, a correct speed value RPMc = RPMn/Er is required. This implies that RPMc > RPMn.
  • A change in the rotation speed of the hydraulic pump from RPMn to RPMc involves a change in the efficiency by moving to another curve of the beam in Figure 3, therefore, the real efficiency Er is passed to the correct one Ec. Therefore, the correct real flow rate is Qc = Ec * V * RPMc.
  • Once Qc has been calculated, this can be compared with Qn and it is decided whether to stop the correction procedure of the rotation speed of the hydraulic pump or not.
  • For example if Qn - Qc < Th then the process stops. Th is a settable threshold.
  • The process can iterate as long as the real flow differs by less than a predetermined threshold Th from the theoretical flow rate or it can be stopped after a predetermined number of iterations.
  • During the iterative calculation operations of the final correct rotation speed value RPMcn obtained after n number of iterations, the correct rotation speed values (RPMc2, RPMc3, .., RPMcn) for each of the 2,3, .. n iterations subsequent to the first, are preferably calculated as the average of the last two values previously identified. Thanks to the present invention, regardless of the temperature conditions of the hydraulic oil and the load applied to the mechanical member, an angular position of the control lever corresponds to approximately the same flow generated by the hydraulic pump.
  • The method object of the present invention can be summarized by the following steps:
    • (a) Acquisition of a deflection angle of the control lever and calculation of a corresponding nominal value (RPMn) of rotation speed of the prime mover, proportional to said deflection angle,
    • (b) acquisition of a temperature and pressure value at the delivery port of the hydraulic pump,
    • (c) calculation of a theoretical flow (Qn) of hydraulic oil pumped by said hydraulic pump,
    • (d) calculation of a real flow (Qr) of hydraulic oil pumped by said hydraulic pump as a function of a table expressing a first volumetric efficiency value (Er) as a function of said temperature values, pressure and nominal rotation speed,
    • (e) calculation of a first corrected rotation speed value (RPMc = RPMn/Er) as a function of said first volumetric efficiency value,
    • (f) Calculation of a first corrected flow rate value (Qc) as a function of said first corrected rotational speed value (RPMc) and of a corresponding first corrected volumetric efficiency value (Ec), in which the first volumetric efficiency value corrected (Ec) is obtained from said table,
    • (g1) if said first corrected flow rate value (Qc1) is less than a predetermined threshold (Th) of said theoretical flow rate value (Qn) then the process stops, otherwise
    • (g2) if said first corrected flow rate value is less than said predetermined threshold (Th) of said theoretical flow rate value (Qn) then the process restarts from step (e), calculating in succession a second, third, ..., n-th correct rotation speed value (RPMc2, RPMc3, .., RPMcn)) and in parallel a second, third, ..., n-th correct flow rate value (Qc2, Qc3, .., Qcn) as long as the corrected flow rate value (Qc2,3, .., n) is far less than said predetermined threshold (Th) from said theoretical flow rate value (Qn).
    When the process converges to a calculated rotation speed value, this is set (Set) by the control unit forcing the electric motor to adapt to this calculated rotation speed value.
  • The recursive portion of the flowchart is enclosed in the hh block.
  • The iterative process performs a gradual change in the rotation speed of the hydraulic pump. At each step the volumetric efficiency value is calculated on the basis of the variation of the rotation speed, of a temperature and pressure value measured by the sensors TS and PS, in order to force the real flow Qr of hydraulic oil pumped by the hydraulic pump to converge towards the theoretical value Qn.
  • The wording "..is far more (or less) than said predetermined threshold Th of said theoretical flow rate value Qn" means that a given value is outside (or inside) an interval having an width equal to the threshold Th and centered on the flow rate theoretical value.
  • The present invention can be advantageously carried out by means of a computer program, which comprises coding means for carrying out one or more steps of the method, when this program is executed on a computer. Therefore, it is intended that the scope of protection extends to said computer program and further to computer readable means comprising a recorded message, said computer readable means comprising program coding means for carrying out one or more steps of the method, when said program is run on a computer.
  • Implementation variants of the described non-limiting example are possible, without however departing from the scope of protection of the present invention, including all the equivalent embodiments for a person skilled in the art, to the content of the claims.
  • From the above description, the person skilled in the art is able to realize the object of the invention without introducing further construction details.

Claims (4)

  1. Method for controlling a hydraulic circuit of a work vehicle, the vehicle including
    - a hydraulic circuit (HC) operatively connected to a fixed displacement hydraulic pump (P) and a prime mover (E) arranged to drive the hydraulic pump in rotation,
    - said prime mover (E), being electric type,
    - a hydraulic actuator (A1) arranged to be powered by the hydraulic circuit, and in which the hydraulic circuit includes a hydraulic actuator supply valve (A1),
    - a lever (JOYSTICK) for controlling said feed valve and said prime mover (E),
    - a temperature sensor (TS) and a pressure sensor (PS) operatively associated with a delivery port of the hydraulic pump (P),
    the method comprising
    - (a) Acquisition of a deflection angle of the control lever and calculation of a corresponding nominal value (RPMn) of rotation speed of the prime mover, proportional to said deflection angle,
    - (b) acquisition of a temperature and pressure value at the delivery port of the hydraulic pump,
    - (c) calculation of a theoretical flow (Qn) of hydraulic oil pumped by said hydraulic pump,
    - (d) calculation of a real flow (Qr) of hydraulic oil pumped by said hydraulic pump as a function of a table expressing a first volumetric efficiency value (Er) as a function of said values of temperature, pressure and nominal rotation speed,
    and subsequently
    - (hh) execution of an iterative process of variation of the rotation speed of the hydraulic pump which includes, at each iteration, the calculation of a volumetric efficiency value on the basis of said variation of the rotation speed, of the temperature value and of pressure measured by said sensors, so as to force the real flow (Qr) of hydraulic oil pumped by the hydraulic pump to converge towards said theoretical flow value (Qn).
  2. Method according to claim 1 wherein said iterative process comprises the following steps in succession:
    - (e) calculation of a first corrected rotation speed value (RPMc = RPMn/Er) as a function of said first volumetric efficiency value,
    - (f) Calculation of a first corrected flow rate value (Qc) as a function of said first corrected rotational speed value (RPMc) and of a corresponding first corrected volumetric efficiency value (Ec), wherein the first volumetric efficiency value corrected (Ec) is obtained from said table,
    - (g1) if said first corrected flow rate value (Qc) is less than a predetermined threshold (Th) of said theoretical flow rate value (Qn) then the process stops, otherwise (g2) if said first corrected flow rate value is lower than said predetermined threshold (Th) of said theoretical flow rate value (Qn) then the process restarts from step (e) by calculating in succession a second, third, ..., n -th correct rotation speed value (RPMc2, RPMc3, .., RPMcn)) and in parallel a second, third, ..., n-th correct flow rate value (Qc2, Qc3, .., Qcn) as long as the value of the corrected flow rate (Qc2,3, .., n) is far, less than said predetermined threshold (Th), from said theoretical flow rate value (Qn).
  3. Control system a hydraulic circuit of a work vehicle, including the vehicle
    - a hydraulic circuit (HC) operatively connected to a fixed displacement hydraulic pump (P) and a prime mover (E) arranged to drive the hydraulic pump in rotation,
    - said prime mover (E), of the electric type,
    - a hydraulic actuator (A1) arranged to be powered by the hydraulic circuit, and wherein the hydraulic circuit includes a hydraulic actuator supply valve (A1),
    - a lever (JOYSTICK) for controlling said feed valve and said prime mover (E),
    - a temperature sensor (TS) and a pressure sensor (PS) operatively associated with a delivery port of the hydraulic pump (P),
    a processing unit configured for
    - (a) Acquiring a deflection angle of the control lever and calculate a corresponding nominal value (RPMn) of rotation speed of the prime mover, proportional to said deflection angle,
    - (b) acquiring a temperature and pressure value at the delivery port of the hydraulic pump,
    - (c) calculating a theoretical flow (Qn) of hydraulic oil pumped by said hydraulic pump,
    - (d) calculating a real flow (Qr) of hydraulic oil pumped by said hydraulic pump as a function of a table, stored in a non-volatile memory of the processing unit, expressing a first volumetric efficiency value (Er) as a function of said values of temperature, pressure and nominal rotation speed, and subsequently for
    - (hh) carrying out an iterative process of variation of the rotation speed of the hydraulic pump which provides for the recalculation of a volumetric efficiency value on the basis of said variation of the rotation speed, of the temperature and pressure value measured by means of said sensors in so as to force the real flow (Qr) of hydraulic oil pumped by the hydraulic pump to converge towards said theoretical flow value and
    - (Set) controlling said prime mover so as to operate at said varied rotation speed value.
  4. Work vehicle comprising a hydraulic member
    - a hydraulic circuit (HC) operatively connected to a fixed displacement hydraulic pump (P) and a prime mover (E) arranged to drive the hydraulic pump in rotation,
    - said prime mover (E), electric,
    - a hydraulic actuator (A1) arranged to be powered by the hydraulic circuit, and in which the hydraulic circuit includes a hydraulic actuator supply valve (A1),
    - a lever (JOYSTICK) for controlling said feed valve and said prime mover (E),
    - a temperature sensor (TS) and a pressure sensor (PS) operatively associated with a delivery port of the hydraulic pump (P),
    - a processing unit configured for
    - (a) Acquiring a deflection angle of the control lever and calculate a corresponding nominal value (RPMn) of rotation speed of the prime mover, proportional to said deflection angle,
    - (b) acquiring a temperature and pressure value at the delivery port of the hydraulic pump,
    - (c) calculating a theoretical flow (Qn) of hydraulic oil pumped by said hydraulic pump,
    - (d) calculating a real flow (Qr) of hydraulic oil pumped by said hydraulic pump as a function of a table, stored in a non-volatile memory of the processing unit, expressing a first volumetric efficiency value (Er) as a function of said values of temperature, pressure and nominal rotation speed, and subsequently for
    - (hh) carrying out an iterative process of variation of the rotation speed of the hydraulic pump which provides for the recalculation of a volumetric efficiency value on the basis of said variation of the rotation speed, of a temperature and pressure value measured by means of said sensors in so as to force the real flow (Qr) of hydraulic oil to converge towards said theoretical flow (Qn) ed
    - (Set) controlling said prime mover so as to operate at said varied rotational speed value.
EP22199761.2A 2021-10-07 2022-10-05 Method and control system for a hydraulic circuit of a work vehicle Pending EP4163446A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT102021000025574A IT202100025574A1 (en) 2021-10-07 2021-10-07 METHOD AND CONTROL SYSTEM OF A HYDRAULIC CIRCUIT OF A WORK VEHICLE

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014034911A (en) * 2012-08-08 2014-02-24 Jtekt Corp Motor control device and electric pump unit
US20160025113A1 (en) * 2013-04-11 2016-01-28 Hitachi Construction Machinery Co., Ltd. Apparatus for Driving Work Machine
JP2020076223A (en) * 2018-11-06 2020-05-21 ヤンマー株式会社 Construction machine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014034911A (en) * 2012-08-08 2014-02-24 Jtekt Corp Motor control device and electric pump unit
US20160025113A1 (en) * 2013-04-11 2016-01-28 Hitachi Construction Machinery Co., Ltd. Apparatus for Driving Work Machine
JP2020076223A (en) * 2018-11-06 2020-05-21 ヤンマー株式会社 Construction machine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"Oleodinamica e Pneumatica", 2003

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