EP3392488B1 - Procédé de commande d'une vitesse de rotation de moteur d'un véhicule utilitaire - Google Patents

Procédé de commande d'une vitesse de rotation de moteur d'un véhicule utilitaire Download PDF

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Publication number
EP3392488B1
EP3392488B1 EP18167961.4A EP18167961A EP3392488B1 EP 3392488 B1 EP3392488 B1 EP 3392488B1 EP 18167961 A EP18167961 A EP 18167961A EP 3392488 B1 EP3392488 B1 EP 3392488B1
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EP
European Patent Office
Prior art keywords
engine speed
loading device
requested
drive
speed
Prior art date
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Active
Application number
EP18167961.4A
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German (de)
English (en)
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EP3392488A1 (fr
Inventor
Jens Letscher
Florian Reinmuth
Florian Schott
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Deere and Co
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Deere and Co
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Publication date
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Publication of EP3392488A1 publication Critical patent/EP3392488A1/fr
Application granted granted Critical
Publication of EP3392488B1 publication Critical patent/EP3392488B1/fr
Active 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
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
    • E02F3/422—Drive systems for bucket-arms, front-end loaders, dumpers or the like
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
    • E02F3/43—Control of dipper or bucket position; Control of sequence of drive operations
    • E02F3/431—Control of dipper or bucket position; Control of sequence of drive operations for bucket-arms, front-end loaders, dumpers or the like
    • 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
    • E02F9/2066—Control of propulsion units of the type combustion engines
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • E02F9/2228—Control of flow rate; Load sensing arrangements using pressure-compensating valves including an electronic controller
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D31/00—Use of speed-sensing governors to control combustion engines, not otherwise provided for
    • F02D31/001—Electric control of rotation speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D31/00—Use of speed-sensing governors to control combustion engines, not otherwise provided for
    • F02D31/001—Electric control of rotation speed
    • F02D31/002—Electric control of rotation speed controlling air supply
    • F02D31/006—Electric control of rotation speed controlling air supply for maximum speed control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D35/00—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for
    • 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
    • F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/50—Input parameters for engine control said parameters being related to the vehicle or its components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/60—Input parameters for engine control said parameters being related to the driver demands or status
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D29/00—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto
    • F02D29/02—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto peculiar to engines driving vehicles; peculiar to engines driving variable pitch propellers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/021—Introducing corrections for particular conditions exterior to the engine

Definitions

  • the invention relates to a method for controlling a speed of a drive motor of a utility vehicle.
  • Agricultural utility vehicles such as tractors, sometimes have a front loader for completing specific work such as earthmoving or transporting crops.
  • a front loader for completing specific work such as earthmoving or transporting crops.
  • the working movements of the front loader depend on the engine power of a drive motor of the commercial vehicle, this can have an impact on the driving speed of the commercial vehicle.
  • Motor speed controls for a drive motor are known, for example, from: DE 11 2012 005571 T5 , DE 36 26 584 A1 , DE 11 2012 000075 T5 and DE 11 2006 002935 B4 .
  • a method for controlling a speed of a drive motor of a commercial vehicle with a drivable loading device is provided.
  • a movement drive of the charging device is predicted or recognized.
  • a request or execution of a movement drive or a working movement of the charging device is predicted or recognized. If a movement drive or a working movement of the loading device has been predicted or recognized, an increase in the motor speed of the drive motor is requested. As a result, the engine power of the drive motor can be automatically increased and thus adapted to specific drive movements of the charging device.
  • a vehicle speed of the commercial vehicle which is usually defined by an accelerator pedal and a brake pedal, is influenced significantly less or not at all by the operation of the charging device, which means an increase in comfort for the driver.
  • the vehicle speed can be maintained independently of specific drive movements of the charging device.
  • a vehicle transmission in particular a transmission ratio, is preferably controlled automatically as a function of an increase in the engine speed, so that a vehicle speed set by the driver remains constant. In this way, unwanted accelerations or decelerations of the utility vehicle can be avoided.
  • the method Based on the explained control of the engine speed, the method also supports improved control or handling of the commercial vehicle and the charging device.
  • An operating state of the charging device is preferably used in order to predict or recognize a movement drive of the charging device.
  • the operating state can be deactivated or activated, i.e. the charging device is basically switched off (deactivated) or switched on (activated) as a prerequisite for a subsequent movement drive or for a subsequent request or execution of a specific drive movement of the charging device.
  • the operating state is activated, it can be concluded that there is a high probability that the charging device will actually be driven to move. In this way, a future movement drive of the charging device can be predicted.
  • the utility vehicle is preferably designed as an agricultural vehicle, in particular as a tractor, tractor or the like.
  • the loading device is preferably a working device in the front or rear area of the utility vehicle.
  • the loading device has a front loader or consists of a front loader. This has, for example, a movable or swiveling arm on which a working unit or a tool (e.g. shovel, fork, clamp pliers) is mounted.
  • the engine speed is an idle speed of the drive engine when the commercial vehicle is stationary.
  • additional and work functions e.g. PTO operation, additional hydraulic functions
  • the commercial vehicle can already be adapted to an impending motion drive of the charging device when it is stationary.
  • the increased engine speed is preferably reduced again when a predetermined waiting time period (e.g. from the point at which the engine speed was increased) has expired and within this waiting time period no motion drive is still being carried out or at least has not been requested. This limits the additional fuel consumption of the drive motor to implement the comfort function.
  • a status signal is advantageously detected in order to predict or identify a movement drive of the charging device, this status signal signaling whether the charging device is in a specific operating state (e.g. on/activated or off/deactivated).
  • the loading device is hydraulically driven.
  • This drive takes place by means of a hydraulic drive pump of the commercial vehicle, which is hydraulically connected to the loading device and, if necessary, other hydraulic units (e.g. brakes, steering).
  • a target hydraulic flow e.g in liters/minute
  • a hydraulic volume required to carry out this drive movement can first be determined and the target hydraulic flow can be determined from this.
  • the target hydraulic flow is determined as a function of one or more detected valve control signals, with these valve control signals being used to control one or more hydraulic valves for driving the movement of the loading device, in particular a tool of the loading device.
  • these valve control signals being used to control one or more hydraulic valves for driving the movement of the loading device, in particular a tool of the loading device.
  • a percentage of the valve opening and/or a duration of the valve opening can be detected in order to support a determination of the target hydraulic flow in a technically simple manner.
  • the aforementioned features or information can preferably be called up at least partially as stored data and thus support the accuracy in determining the target hydraulic flow. For example, by evaluating certain input commands, the operator can determine along which direction, route or pivot axis the loading device or components thereof (e.g. its working unit or tool) are to be moved. A target hydraulic flow can then be determined from this ascertained information.
  • this target position has preferably already been stored during a previous work process in a device for carrying out the method, for example by means of a single position memory button on an operating unit.
  • a desired target position can be stored by manually entering various data at an operator interface, with the data entered representing the target position.
  • the target position can contain different data, such as a Swivel angle of a boom or a tool (shovel, fork, clamp, etc.) on the boom, a lifting height of the loading device, data from a hydraulic valve, such as a percentage valve opening and/or a time duration of the valve opening to generate a target hydraulic pressure, a clamping force or a clamping pressure of a tool (e.g. fork or clamp pliers) of the loading device.
  • This clamping force serves in particular to support reliable transport of bales or other goods.
  • a current clamping pressure of this tool is preferably determined or set by means of appropriate sensors.
  • This clamping pressure or clamping force can be displayed to a user on a display unit or operating interface. As already mentioned, a user can enter a desired clamping force as data for a desired target position of the tool or request the already stored clamping force for a new work process. A clamping force judged to be suitable thus remains constant and a consistently efficient work process is guaranteed.
  • a clamping force can preferably be entered and/or displayed directly at a user interface.
  • a corresponding hydraulic flow rate and associated time period can be entered and/or displayed if the clamping force is adjusted via a hydraulic cylinder.
  • a pressure measurement in this hydraulic cylinder and characteristic lever ratios and/or other geometric parameters of the tool can be used to determine a current clamping force.
  • This current clamping force can then be compared to a requested target clamping force.
  • a hydraulic flow can then be controlled on the basis of the comparison result in such a way that the target clamping force is set.
  • three functions are preferably controlled with regard to a movement drive of the loading device, namely a position of a boom of the loading device, a position of a tool of the loading device and a clamping force of the tool (e.g. fork or clamping pliers).
  • these three functions can be controlled automatically, namely simultaneously and/or coordinated with one another with regard to their drive movements.
  • a hydraulic cylinder in particular is activated for each function.
  • the automatic reaching of the required target position can replace manual operation of the loading device by an operator, which reliably prevents incorrect operation and thus any damage caused by the loading device (e.g. to adjacent buildings, to the load).
  • the operator can request a stored setpoint position using a suitable operating device. For example, the operator presses a button on a hand lever, joystick or the like. Alternatively, one or more optical buttons on a user interface (e.g. screen) can be touched in order to trigger a drive movement of the charging device in the direction of the target position.
  • a suitable operating device For example, the operator presses a button on a hand lever, joystick or the like.
  • one or more optical buttons on a user interface e.g. screen
  • a user interface e.g. screen
  • a foot pedal that can be actuated by foot is provided as the operating device for triggering a drive movement of the loading device, in particular in the direction of a desired position.
  • a conventional clutch pedal is suitable for this without significant additional technical effort, provided that it is no longer required for clutch purposes due to the transmission used in the commercial vehicle (eg IVT transmission). In such cases, the conventional clutch pedal can then be used to raise or lower a loader.
  • This function of the clutch pedal can be permanently specified in the commercial vehicle.
  • this clutch pedal can be configured with different functions. For this purpose, for example, one of several possible functions can be assigned to the clutch pedal via an operating interface. If necessary, the currently assigned function can be replaced by another function.
  • the foot pedal can flexibly fulfill different user-specific functions.
  • the signals from the actuated foot pedal are preferably processed in a corresponding control device and converted by this into control signals, for example for controlling the movement of a charging device.
  • a foot pedal can improve the ease of use for the driver and thus reduce his workload during the work movements to be carried out by the loading device.
  • the aforementioned drive characteristics contain, in particular, specific features of the charging device used, e.g. hydraulic-specific information about the model used and/or its geometric dimensioning.
  • the target hydraulic flow is determined as a function of at least one hydraulic unit (e.g. brakes, steering) of the utility vehicle, which further improves the accuracy for the requested increase in engine speed.
  • at least one hydraulic unit e.g. brakes, steering
  • a so-called request period In order to limit the additional consumption of the drive engine, it is advantageous to only request an increase in the engine speed for a specific period of time, a so-called request period.
  • This request period is determined or calculated as a function of the determined target hydraulic flow. Determining the request period is particularly useful and possible with great accuracy when the target hydraulic flow is determined for a requested target position, because the hydraulic volume required to reach the target position is then known or can be determined with great accuracy .
  • the determined demand period can also be further processed for the purpose of deciding whether an increased engine speed is actually maintained for the duration of the demand period or for a shorter or longer period of time.
  • the increased engine speed is preferably limited in such a way that it is at most as high as a predetermined limit speed.
  • the drive motor is preferably driven at the limit speed.
  • the engine speed is increased at a predetermined rate of increase that is lower than the requirement.
  • the engine speed is lowered at a specific point in time at a predetermined or determined lowering rate. This takes into account the inertia of the drive motor and additionally limits unnecessary additional fuel consumption of the drive motor.
  • an increased engine speed is maintained for a determined or predetermined hold period of time.
  • This holding period can be shorter or longer than the aforementioned request period.
  • the holding period is preferably dependent on a consumption-oriented process implementation (ie the shortest possible period of time to limit the additional consumption of fuel) or a performance-oriented implementation of the method (ie a relatively long period of time to support the drive power for the charging device and/or the mileage of the commercial vehicle) is predetermined or determined. It is also possible to predetermine the holding period as a function of the determined request period.
  • the increased engine speed is initially maintained after the predetermined hold time has elapsed if the requested engine speed is at least as high as the increased engine speed at the time the hold time elapses. This measure also helps to avoid constantly changing increases in engine speed and thus unnecessary additional consumption for the drive engine.
  • FIG. 1 shows a commercial vehicle designed as a tractor 10, on the front side of which a loading device designed as a front loader 12 is mounted.
  • the front loader 12 has a pivotable boom 14, at the free end of which a tool in the form of a shovel 16 is pivotably mounted.
  • the boom 14 and the shovel 16 are hydraulically driven to move to different positions, e.g 1 Pos_1, Pos_2, Pos_3 and Pos_4 shown positions to be able to take.
  • Pos_1, Pos_2 and Pos_3 the boom 14 assumes different swivel angles relative to the tractor 10.
  • Pos_1, Pos_2, Pos_3 and Pos_4 the shovel 16 assumes different pivoting angles relative to the boom 14.
  • the position Pos_3 can represent a maximum lifting height of the boom 14 or the loading device 12 for certain types of work in order to avoid any damage to adjacent buildings, gateways or the like.
  • the hydraulic movement is driven by means of suitable hydraulic cylinders 18, which are mounted on the loading device 12.
  • the method for controlling an engine speed n of a drive engine of tractor 10 provides for first predicting or recognizing a motion drive of loading device 12 and then requesting an increase in engine speed n of the drive engine.
  • the increase in engine speed n is therefore requested, for example, when a future movement drive is predicted or a movement drive is actually requested and recognized.
  • the engine speed n corresponds to an idle speed n_L when the tractor 10 is stationary (step S1).
  • the idling speed n_L is, for example, 850 rpm (revolutions per minute).
  • a status signal S_Z signals an activated operating status (on) or another drive status, for example deactivated operating status (off), of the charging device 12 . If an activated operating state is detected, it is assumed that there is a high probability that a movement drive or a drive movement will subsequently be requested. A future motion drive is thus predicted. According to the method, an increase in engine speed n is therefore requested.
  • the engine speed n is increased to the engine speed n_H (step S3). For example, it is 1000 rpm.
  • step S5 it is checked whether a movement drive or a drive movement is already being carried out or is at least requested when the time period ⁇ t_W has expired. If so, the increased engine speed n_H is maintained (step S6). If not, the increased engine speed n_H is reduced again (step S7) in order to reduce the increased fuel consumption again.
  • FIG. 3 shows schematically parts of an arrangement 20 for carrying out the method for controlling the engine speed n.
  • the arrangement 20 is used for carrying out the method at any engine speed n outside the idling speed n_L.
  • the working blocks 22, 24, 26, 28 shown here are used to control the engine speed n, which is effective as a function of a hydraulic flow to be described below.
  • further working blocks and components are provided which also control the engine speed n in idling mode according to 2 consider.
  • the arrangement 20 according to 3 assumes that the charging device 12 and possibly also other units (eg steering, brakes) are driven hydraulically.
  • the tractor 10 has a hydraulic drive pump 30 .
  • Their pump characteristics in particular a characteristic curve with a hydraulic flow (litres/minute) as a function of the engine speed) are taken into account in work block 24 in order to determine which higher engine speed n_A should be requested.
  • the engine speed n_A to be requested is calculated as a function of a determined setpoint hydraulic flow F_S.
  • engine speed n_A is requested for a request period ⁇ t_A, ie engine speed n_A should be effective during request period ⁇ t_A.
  • the request period ⁇ t_A is used as the output signal of the working block 24 in particular when a required hydraulic volume V_hyd is calculated in the working block 28 and sent to the working block 24 as a signal.
  • a required hydraulic volume V_hyd is calculated in the working block 28 and sent to the working block 24 as a signal.
  • the hydraulic volume V_hyd represents a hydraulic volume which is estimated or calculated in order to be able to carry out a predicted or recognized movement drive of the loading device 12 .
  • the input signals can be a drive characteristic S_Ch (e.g. drive type, drive geometry, geometry of the hydraulic cylinder 18, etc.) and a requested drive movement S_Bew (e.g.
  • An input signal S_Pos_S in particular is taken into account in working block 28 when determining the hydraulic volume V_hyd.
  • This signal represents in particular the request for a target position Pos_S of the charging device 12 that has already been stored and is therefore known with regard to the hydraulic requirements.
  • the charging device is in the initial position Pos_1 before the target position Pos_S is requested.
  • the required hydraulic volume V_hyd can then be predicted particularly precisely on the basis of the hydraulically known initial and target positions and the known drive characteristic S_Ch.
  • the requested hydraulic flow F_A is an output signal of the working block 22.
  • the output signal for example, input signals relating to the operating state (S_Z) of the loading device 12, a steering (S_L, e.g. steering angle) of the tractor 10, a brake unit (S_B, e.g. status of the brake) and Valve control signals S_V hydraulic valves of the charging device 12 are taken into account.
  • the target hydraulic flow F_S is determined as a function of a movement drive of the charging device 12 that is predicted or recognized in the working block 22 and/or in the working block 28 .
  • the requested engine speed n_A possibly the request period ⁇ t_A and a predetermined limit speed n_G and possibly other parameters or variables are evaluated in work block 26 .
  • an increased engine speed n_H that is actually to be realized is derived from the input signals of work block 26, a holding period ⁇ t_H to maintain the increased engine speed n_H, an increased rate of increase m_an of the engine speed n and a lowering rate m_ab of the increased engine speed n_H are determined or predetermined and transmitted as output signals for controlling the drive motor, in particular a motor controller.
  • the dot-dash lines show requested increases in the Engine speed n and possibly request periods ⁇ t_A.
  • the solid curves show the increased engine speeds n_H and holding times ⁇ t_H, with which the drive engine is actually activated based on the evaluation in work block 26 .
  • n_akt In 4 starting from a time to at a current speed n_akt of the drive motor, a higher speed n_A is requested for a request period ⁇ t_A. However, a lower value is predetermined for the limit speed n_G in comparison to the requested higher speed n_A. The actually realized increased speed n_H therefore corresponds to the limit speed n_G. Due to consumption-oriented boundary conditions, the increased engine speed n_H is only maintained for a holding period of increased engine speed n_H, which is shorter than the request period ⁇ t_A. In addition, the current rotational speed n_akt is increased at a lower rate of increase m_an than was requested in order to limit additional fuel consumption and an additional load on the drive engine.
  • a higher speed n_A is requested for time t 15 .
  • the rotational speed n is increased at a lower rate of increase m_an up to the point in time t 25 .
  • engine speed n initially remains at an increased speed n_H below limit speed n_G, since a further reduction in engine speed n was requested here and constant changes in engine speed are to be avoided.
  • the requested speed is again greater than the increased speed n_H realized between t25 and t35.
  • the engine speed n therefore continues to rise and is limited at time t 45 as an increased engine speed n_H on the basis of the predetermined limit speed n_G.
  • the increased engine speed n_H is maintained for the holding period ⁇ t_H. After that, the increased engine speed n_H is reduced again with the lowering speed m_ab. For time t65, an increase in engine speed n is requested again with a value n_A above limit speed n_G. Correspondingly, the engine speed is again increased at a rate of increase m_an with a limitation by the limit speed n_G (time t 75 ). After the holding period ⁇ t_H has elapsed at time t 85 , the increased engine speed n_H is reduced again at a lowering speed m_ab.
  • the value of the increased engine speed n_H corresponds to the value of the requested higher engine speed n_A, since the latter is below the limit speed n_G. From point in time t 17 , the increased engine speed n_H is maintained for the holding period ⁇ t_H. Since a higher engine speed n_A is still requested when this first holding period ⁇ t_H expires at time t 27 , the increased engine speed n_H remains—similar to Alauf in 6 - Maintained for a further holding period ⁇ t_H.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Civil Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Structural Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Analytical Chemistry (AREA)
  • Operation Control Of Excavators (AREA)
  • Control Of Vehicle Engines Or Engines For Specific Uses (AREA)

Claims (14)

  1. Procédé de commande d'une vitesse de rotation (n) d'un moteur d'entraînement d'un véhicule utilitaire (10) comprenant un dispositif de chargement entraînable (12),
    - un entraînement de mouvement du dispositif de charge (12) étant prédit ou détecté, et
    - lorsqu'un entraînement de mouvement du dispositif de charge (12) est prédit ou détecté, une augmentation de la vitesse de rotation (n_A) du moteur d'entraînement étant demandée, caractérisé en ce que la vitesse de rotation (n) du moteur est augmentée à une vitesse d'augmentation prédéterminé (m_an) inférieure à ce qui est demandé.
  2. Procédé selon la revendication 1, caractérisé en ce que la vitesse de rotation (n) du moteur est une vitesse de rotation au ralenti (n_L) lorsque le véhicule utilitaire (10) est à l'arrêt, ce qui correspond à un état dans lequel des fonctions additionnelles et de travail du véhicule utilitaire (10) sont inactives ou désactivées.
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que, lorsque la vitesse de rotation (n_H) du moteur a été augmentée, celle-ci est à nouveau réduite lorsqu'une durée d'attente prédéterminée (Δt_W) s'est écoulée et qu'aucun entraînement de mouvement du dispositif de charge (12) n'a été demandé jusqu'à ce que cette durée d'attente (Δt_W) soit écoulée.
  4. Procédé selon l'une des revendications précédentes, caractérisé en ce que l'entraînement de mouvement du dispositif de charge (12) est prédit ou reconnu en fonction d'un signal d'état (S_Z) détecté, le signal d'état (S_Z) signalant un état de fonctionnement du dispositif de charge (12).
  5. Procédé selon l'une des revendications précédentes, caractérisé en ce que
    - le dispositif de charge (12) est entraîné hydrauliquement,
    - un débit hydraulique cible (F_S) d'une pompe d'entraînement hydraulique (30) du véhicule utilitaire (10) est déterminé en fonction de l'entraînement de mouvement prédit ou détecté du dispositif de charge (12), et
    - l'augmentation de la vitesse de rotation (n_A) du moteur est demandée en fonction du débit hydraulique cible (F_S) déterminé.
  6. Procédé selon la revendication 5, caractérisé en ce que le débit hydraulique cible (F_S) est déterminé en fonction d'un signal de commande de vanne (S_V) détecté pour au moins une vanne hydraulique du dispositif de charge (12).
  7. Procédé selon l'une des revendications 5 et 6, caractérisé en ce que le débit hydraulique cible (F_S) est déterminé en fonction d'au moins une des caractéristiques suivantes :
    - un mouvement d'entraînement demandé (S_Bew) du dispositif de charge (12),
    - une caractéristique d'entraînement (S_Ch) du dispositif de charge (12),
    - une position cible (Pos_S) demandée du dispositif de charge (12).
  8. Procédé selon l'une des revendications 5 à 7, caractérisé en ce que le débit hydraulique cible (F_S) est déterminé en fonction d'au moins un groupe hydraulique (S_L, S_B) du véhicule utilitaire (10).
  9. Procédé selon l'une des revendications 5 à 8, caractérisé en ce que l'augmentation de la vitesse de rotation (n_A) du moteur est demandée pendant une durée de demande (Δt_A) qui est déterminée en fonction du débit hydraulique cible (F_S) déterminé.
  10. Procédé selon l'une des revendications précédentes, caractérisé en ce que la vitesse de rotation (n_H) augmentée du moteur est inférieure ou égale à une vitesse de rotation limite (n_G) prédéterminée.
  11. Procédé selon l'une des revendications précédentes, caractérisé en ce que la vitesse de rotation (n_H) du moteur est réduite après avoir été augmentée à une vitesse d'abaissement (m_ab) prédéterminée.
  12. Procédé selon l'une des revendications précédentes, caractérisé en ce que la vitesse de rotation (n_H) augmentée du moteur est maintenue pendant une durée de maintien (Δt_H).
  13. Procédé selon la revendication 12, caractérisé en ce que la vitesse de rotation (n_H) augmentée du moteur est maintenue après que le temps de maintien (Δt_H) s'est écoulé si, à l'instant où le temps de maintien (Δt_H) s'est écoulé, la vitesse de rotation (n_A) demandée du moteur est au moins égale à la vitesse de rotation (n_H) augmentée du moteur.
  14. Procédé selon l'une des revendications précédentes, caractérisé en ce que le dispositif de charge comporte un chargeur frontal (12), notamment un chargeur frontal (12) intégré.
EP18167961.4A 2017-04-21 2018-04-18 Procédé de commande d'une vitesse de rotation de moteur d'un véhicule utilitaire Active EP3392488B1 (fr)

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US10570832B2 (en) * 2017-08-16 2020-02-25 Paccar Inc Systems and methods for controlling torque in a vehicle
DE102019101990A1 (de) * 2019-01-28 2020-07-30 Liebherr-Mining Equipment Colmar Sas Mobile Arbeitsmaschine und Verfahren zum Betreiben einer solchen
CN110645235B (zh) * 2019-09-30 2022-04-08 中国石油集团川庆钻探工程有限公司 一种井下作业工具的输出装置
DE102021203660A1 (de) 2021-04-14 2022-10-20 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatischer Antrieb und Verfahren zur Steuerung des hydraulischen Antriebs
CN113202642B (zh) * 2021-05-24 2023-03-28 三一重机有限公司 一种工程机械用发动机转速控制方法、装置及工程机械
DE102022203716A1 (de) 2022-04-13 2023-10-19 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zur Steuerung eines hydraulischen Systems und Hydrauliksteuerung

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JPS62142834A (ja) * 1985-12-17 1987-06-26 Komatsu Ltd クレ−ンのエンジン制御装置
JP4550698B2 (ja) * 2005-09-01 2010-09-22 日立建機株式会社 ダンプトラックの油圧駆動装置
CN101900043B (zh) * 2005-10-28 2012-01-04 株式会社小松制作所 发动机、液压泵以及发电电动机的控制装置
JP2009281149A (ja) * 2008-05-19 2009-12-03 Kobelco Contstruction Machinery Ltd エンジン制御装置及びこれを備えた作業機械
JP5124033B2 (ja) * 2011-05-18 2013-01-23 株式会社小松製作所 作業機械のエンジン制御装置およびそのエンジン制御方法
WO2013103133A1 (fr) 2012-01-05 2013-07-11 日立建機株式会社 Dispositif pour la commande d'engin de construction
JP5828808B2 (ja) * 2012-06-29 2015-12-09 日立建機株式会社 油圧作業機械
JP6237396B2 (ja) * 2014-03-26 2017-11-29 株式会社豊田自動織機 産業車両の走行制御装置

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US20180305900A1 (en) 2018-10-25

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