EP2199622B1 - Système hydraulique - Google Patents

Système hydraulique Download PDF

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Publication number
EP2199622B1
EP2199622B1 EP09177880.3A EP09177880A EP2199622B1 EP 2199622 B1 EP2199622 B1 EP 2199622B1 EP 09177880 A EP09177880 A EP 09177880A EP 2199622 B1 EP2199622 B1 EP 2199622B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic system
control unit
hydraulic
pressure differential
variable displacement
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP09177880.3A
Other languages
German (de)
English (en)
Other versions
EP2199622A3 (fr
EP2199622A2 (fr
Inventor
Marcus Bitter
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Publication of EP2199622A2 publication Critical patent/EP2199622A2/fr
Publication of EP2199622A3 publication Critical patent/EP2199622A3/fr
Application granted granted Critical
Publication of EP2199622B1 publication Critical patent/EP2199622B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement 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
    • 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
    • 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
    • F04B49/10—Other safety measures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. torque or rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6343—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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure control

Definitions

  • the invention relates to a hydraulic system with a drive motor, a driven by the drive motor hydraulic variable displacement pump driven by the variable displacement hydraulic consumer and an electronic control unit, wherein the variable displacement pump is equipped with a flow regulator, with which adjusting between consumer and variable pressure difference on a preset control pressure differential value is adjustable.
  • the US 5,226,800 shows a hydraulic system with a load sensing valve and a speed sensor, wherein the load sensing valve between position 1 and a position 2 is movable. In position 2, the output of the pump is increased at high engine speed. In position 1, the output of the pump is reduced at low engine speed.
  • Agricultural machines are known, for example tractors, or other types of working machines, such as construction machines or telescopic loaders, which have a hydraulic system with which one or more hydraulic consumers are operated, eg hydraulic cylinders, hydraulic motors or other hydraulically operated components.
  • hydraulic systems include hydraulic pumps which translate directly or via a rigid transmission gear into fast or slow, with the drive shaft, a drive motor are connected.
  • the maximum deliverable volume flow of the hydraulic pump thus changes with the speed of the drive motor. The faster the drive motor turns, the larger the volume flow, which can be funded by the hydraulic pump.
  • adjustable load-sense controlled hydraulic pumps so-called hydraulic variable displacement pumps, as they are used today as state of the art, the subsidized maximum delivery volume can be adapted to the demand required by the hydraulic consumer.
  • a so-called flow regulator which is a preset control pressure difference between the pressure at the output of the variable and the consumer reported Load sense signal (called LS signal below) regulates or maintains.
  • the delivery flow regulator of an LS-controlled variable displacement pump now works in such a way that it adjusts the delivery volume flow of the variable displacement pump so that the preset control pressure difference, which can be set permanently on the delivery flow regulator via an adjusting spring, is always kept constant.
  • the exact mode of action of such a (pressure) flow regulator can be read in the relevant literature and is as such prior art.
  • the delivery volume flow which can be delivered from a hydraulic valve to a consumer, for example a hydraulic cylinder or a hydraulic motor, is directly dependent on this preset control pressure difference.
  • a certain pressure to be regulated is set, which forces the variable to maintain a set pressure corresponding control pressure difference between the output of the variable and consumer (LS signal) upright.
  • the adjustable in accordance with an adjusting piston or adjustable counselnverstelltechnik the variable and starts to promote a corresponding flow rate.
  • the adjusting piston is hydraulically connected to the flow controller and changes its position in dependence on the control pressure difference present or set on the flow regulator.
  • the baintellhim may for example comprise a swash plate which is connected to control or reciprocating piston, wherein the rotary motion is converted into a longitudinal movement of the reciprocating piston by rotating the swash plate becomes.
  • the volume flow conveyed by the variable flow pump flows through the lines and valves of the hydraulic system and generates certain pressure losses in the lines and at the respective valves to the consumers.
  • the pressure, which then sets behind the valves or at the consumer, is reported as load pressure (LS signal) back to the variable displacement pump (via a load pressure line (LS line), which is connected to the flow regulator) and causes the variable displacement pump to do so
  • LS signal load pressure
  • LS line load pressure line
  • valves which are farther away from the variable displacement pump than other valves will allow less volumetric flow to reach a consumer, although there are valves of the same type.
  • valves that report an increased load signal to the pump such as in the EP 176 0 325 A2 is disclosed.
  • EP 349 092 B1 discloses another way to allow high volume flows at low engine speeds, but to limit the flow rate at high engine speeds.
  • the maximum delivery volume delivered by the variable displacement pump is limited, the delivery rate of the variable displacement pump being measured (eg by measuring the position of the delivery volume adjustment mechanisms, eg the adjustment angle of an adjusting disc or swashplate) and monitored.
  • these variable displacement pumps and the corresponding control electronics are complex and expensive.
  • the object underlying the invention is seen to provide a hydraulic system of the type mentioned, by which the aforementioned problems are overcome.
  • a hydraulic system is to be created with simple, safe and cost-effective means, which provides a large delivery volume at low input speeds, but limits this at higher input speeds to a certain maximum value.
  • a hydraulic system of the type mentioned above is formed such that the flow regulator by the control unit comprises controllable actuating means, through which the control pressure differential value on the delivery flow controller via the electronic control unit is variable, wherein the electronic control unit detects a drive speed-dependent signal, as a function of which a control signal for the controllable actuating means can be generated by the control unit, which change the control pressure difference value on the flow controller.
  • variable displacement pump has the option of delivering delivery volumetric flows of Vmax l / min at a maximum input speed, which would lead to high losses in the lines and valves.
  • this pump now conveys eg a maximum volumetric flow rate of Vleer l / min (Vleer ⁇ V1 ⁇ Vmax) and with increasing input speed (U +) the volumetric flow rate (V) increases.
  • the control pressure difference value of the variable displacement pump can be reduced.
  • the presettable input rotational speed value which triggers the adjustment of the control pressure differential value, can preferably be predetermined via an input module on a driver's display of a working device or via another suitable input interface of the control unit.
  • a fixed drive speed value may already be predetermined and stored in the control unit.
  • control pressure difference value When a presettable input speed value is exceeded, the control pressure difference value can be changed in proportion to the input speed, wherein the control unit reduces the control pressure difference value with increasing input speed and increases with decreasing input speed.
  • control signal generated by the control unit is preferably continuously adapted to a drive speed change, so that an operator of the Systems does not notice the change in the volume of delivery directly.
  • control pressure difference value via the adjusting means is variable, such that the control pressure difference value can be reduced or increased independently of the drive speed.
  • an operator can quasi “override” the control of the control means taken control of the flow control valve and disable by appropriate inputs to the setting means, for example on an input module or on an input button with thumbwheel or a potentiometer the drive speed-dependent control function of the control unit and by directly specifying a via the setting means predeterminable input signal modify the control signal, so that despite the original drive speed-dependent generation of a control signal, the signal input by the setting means is prioritized.
  • the hydraulic system may further include a temperature sensor that detects the temperature in the hydraulic system and provides a corresponding signal to the control unit.
  • the viscosity of a hydraulic fluid depends on the temperature, so that it may be advantageous, at low temperatures, or at a high viscosity of the hydraulic fluid to adjust the control pressure difference value on the flow regulator further depending on the viscosity or temperature, for example, to increase .
  • control pressure difference value on the delivery flow regulator may be advisable to adapt to the lower flow losses at higher temperatures, that is to say to reduce it, for example.
  • both depending on the input speed alone, as well as in combination depending on the temperature in the hydraulic system can enter state conditions for which an adjustment of the control pressure differential value at the flow controller is advantageous.
  • Corresponding control functions or control algorithms can be implemented in the electronic control and stored as corresponding state diagrams be. Based on these control functions or control algorithms corresponding control signals, both in dependence on the drive speed, as well as in dependence on the temperature, for driving the actuating means or for adjusting the control pressure difference value can be generated at the flow controller.
  • the adjusting means on the delivery flow regulator preferably comprise an electric motor, which can be activated by the control unit and can adjust the adjusting spring in the delivery flow regulator.
  • an electromagnet which adjusts the adjusting spring in the flow regulator.
  • the adjustment of the flow control valve or the adjusting spring should be made directly to the bias of the adjusting spring of the flow control valve.
  • This adjustment can be effected electrically or electromagnetically as mentioned above, but also hydraulically, pneumatically or purely mechanically, with an electrical or electromagnetic adjustment being preferred, since this adjustment is easier to handle than other types of adjustment.
  • This adjustment can now increase or decrease the spring preload, whereby the control pressure difference is automatically adjusted.
  • the adjustment can take place, for example, via a proportional magnet which is effective in both directions.
  • a proportional magnet which is effective in both directions.
  • the stepper motor has the advantage that it has a certain self-locking and can be moved very precisely in a certain position (angle of rotation), which he does not leave, unless he gets a new control signal or a very strong force pulls at him.
  • Such a stepper motor can be easily connected to the adjusting screw for adjusting the control pressure difference of the flow control valve and can then very accurately and very quickly turn this adjusting screw depending on the control signal, so that the control pressure difference can be adjusted very sensitively. Should a failure of the electronics occur, the stepper motor would simply remain in its last position, thus ensuring that at least a certain minimum operation of the hydraulic system remains ensured.
  • An inventive hydraulic system is used in work vehicles used in agriculture, ie in agricultural vehicles, such as tractors with or without front loader and telescopic loaders. Furthermore, such a hydraulic system is also suitable for use in construction machines, for example in excavators or wheel loaders.
  • the hydraulic system according to the invention enables optimum operation of a hydraulic system in all drive-dependent operating states of the vehicle and serves, in particular, to reduce power losses and to provide large volume flows at low drive speeds. Furthermore, existing smaller line cross-sections and valves can be used in spite of a variable displacement pump. If required, very large flow rates are possible despite small pipe cross-sections and valves. A retention of existing valves and lines, regardless of the use of a larger variable displacement pump, this is possible. Furthermore, it can be ensured in spite of electronic control of the flow control valve in case of failure of the electrical system that the existing hydraulic system is still available.
  • FIG. 1 shows a hydraulic system 10 for operating a hydraulic consumer 12, for example a hydraulic cylinder for raising and lowering a front loader 14.
  • the hydraulic system 10 comprises a hydraulic tank 16, a hydraulic variable displacement pump 18 with a delivery flow regulator 20 for setting a regulating pressure difference value between the variable displacement pump 18 and the consumer 12, a pressure limiter 22 for limiting the operating pressure for the variable displacement pump 18, and an adjusting piston 23 for adjusting and limiting the delivery volume of the variable displacement pump 18 which can be adjusted via a delivery volume adjusting unit 18. Further, a stop 23 designed as an adjusting spindle is provided provided for the adjusting piston 23 which is engageable with the adjusting piston 23 into engagement and with which a maximum delivery volume of the variable displacement pump 18 is adjustable.
  • the variable displacement pump 18 is driven by a drive motor 25. Between the consumer 12 and variable displacement pump 18, a hydraulic control valve 26 is connected, via which the hydraulic consumer 12 is controlled.
  • a load pressure line 28 is connected, which is connected to the flow controller 20, wherein the load pressure line 28 has a connected to the tank 16 pressure relief diaphragm 29 and a closing 12 in the direction of the consumer check valve 30, wherein the check valve 30 between the Pressure relief diaphragm 29 and the consumer 12 is arranged.
  • the hydraulic system 10 has an electronic control unit 32 which is connected to a speed sensor 34 and an adjusting device 36.
  • the delivery flow regulator 20 has adjusting means 38, which are designed as electric motors, preferably as stepping motors, and can be controlled by the electronic control unit 32.
  • the drive motor 25 is connected directly to the variable displacement pump 18, which is shown here only by way of example. Of course, here also sub or transmission gear can be interposed.
  • the electronic control unit 32 may receive input signals from the adjustment device 36, which then takes into account in the generation of a control signal for the actuating means 38. In the generation of a control signal, only a speed signal supplied by the rotational speed sensor 34 is considered in the first place, as a function of which the electronic control unit 32 generates the control signal for the actuating means 38.
  • the delivery flow regulator 20 which is preset with a fixed control pressure difference value via a biasing spring 40, can now be adjusted by adjusting the bias of the biasing spring 40 via the adjusting means 38, so that the control pressure differential value can be both raised and lowered.
  • a pressure difference which is the flow controller 20 via the load-sensing pressure line 28 and a connected to the output of the variable displacement pump 18 control pressure line 42.
  • the adjusting piston 23 connected to the delivery flow regulator 20 via the pressure limiter 22 is brought into a corresponding control position.
  • the delivery volume adjusting unit 24 of the variable displacement pump 18 is adjusted.
  • the delivery volume of the variable displacement pump 18 is controlled or regulated via the regulating pressure differential value set on the delivery flow regulator 20.
  • the regulating pressure difference value on the delivery flow regulator 20 can be adjusted by way of the biasing spring 40, so that the regulating pressure difference value can be adjusted via the adjusting means 38 connected to the pretensioning spring 40 and can thus be controlled or adjusted or regulated via the electronic control unit.
  • a control of the actuating means 38 on the delivery flow regulator 20 and thus of the delivery volume of the variable displacement pump 18 can be made.
  • stored or stored threshold values are preferably implemented in the electronic control unit 32, by means of which a corresponding control program can be started so that, for example, after reaching a predefinable speed value on the drive motor 25, the control pressure differential value is reduced further as a function of the further increasing speed To reduce delivery volume accordingly and to limit the flow rate.
  • an operator can now "lever out” or “override” the preset threshold values, so that independently of the rotational speed, a control of the actuating means 38 which can be predetermined via the adjusting means 36 can take place.
  • the control pressure difference value can be set to a constant value via the setting means 36, wherein the control unit 32 then controls the setting means 38 independently of the rotational speed of the drive motor 25.
  • the adjusting means 36 may comprise a plurality of occupied switches or an input display or an adjustable potentiometer, etc., with which corresponding setting variables can be specified.
  • activation or deactivation of the speed-dependent control of the delivery flow regulator 20 can also take place via the adjustment means 36.
  • the temperature sensor 37 detects, as already mentioned, the temperature of the hydraulic fluid and supplies a corresponding temperature signal to the control unit 32.
  • the control unit 32 both in dependence on the input speed alone and in combination depending on the temperature, the control pressure difference value on the flow controller by adjusting the Adjusting means 38 change or control or regulate.
  • the control pressure difference value on the delivery flow regulator can additionally be reduced or increased as a function of the temperature of a hydraulic fluid of the hydraulic system 10.
  • Corresponding control signals are generated by control functions or control algorithms implemented in the control unit 32 as a function of the drive speed and / or of the temperature.
  • an electric proportional solenoid 38 ' is used as shown in FIG. 2 .
  • the proportional magnet 38 ' is preferably also effective in both directions, wherein generally an adjustment of the flow controller 20 in only one direction is quite conceivable, so that, for example, only a reduction of the control pressure difference value is made possible.
  • FIG. 3 shows an agricultural vehicle 44 in the form of a tractor, which is equipped with a front loader 14, which by a in FIG. 1 or 2 described hydraulic system is operated.
  • a front loader 14 which by a in FIG. 1 or 2 described hydraulic system is operated.
  • other applications for the hydraulic system according to the invention are conceivable, for example for use in construction machines or telescopic loaders.
  • the hydraulic system according to the invention can also be used to supply other hydraulic consumers not explicitly listed here, for example for supplying three-point hitch devices to agricultural tractors.

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

Claims (7)

  1. Système hydraulique (10) comportant un moteur d'entraînement (25), une pompe d'ajustement hydraulique (18) pouvant être entraînée par le moteur d'entraînement (25), une charge hydraulique (12) pouvant être entraînée par la pompe d'ajustement hydraulique (18) et une unité de commande électronique (32), dans lequel la pompe d'ajustement (18) est équipée d'un régulateur de débit d'entraînement (20) au moyen duquel il est possible de réguler une différence de pression s'établissant entre la charge (12) et la pompe d'ajustement (18) à une valeur de différence de pression de régulation préalablement réglée, dans lequel le régulateur de débit d'entraînement (20) comprend des moyens de réglage (38, 38') pouvant être commandés par l'unité de commande (32), au moyen desquels la valeur de différence de pression de régulation peut être modifiée par l'intermédiaire de l'unité de commande (32) sur le régulateur de débit d'entraînement (20), dans lequel l'unité de commande électronique (32) détecte un signal dépendant de la vitesse de rotation d'entraînement, en fonction duquel un signal de commande destiné aux moyens de réglage pouvant être commandés (38, 38') peut être généré au moyen de l'unité de commande (32), caractérisé en ce que le signal de commande réduit la valeur de différence de pression de régulation au niveau du régulateur de débit d'entraînement (20) lorsqu'une valeur de vitesse de rotation d'entraînement pouvant être prédéfinie est dépassée, afin de réduire de manière correspondante le volume d'entraînement et de limiter le débit volumique d'entraînement.
  2. Système hydraulique (10) selon la revendication 1, caractérisé en ce que le signal de commande modifie la valeur de différence de pression de régulation proportionnellement à la vitesse de rotation d'entraînement lors du dépassement d'une valeur de vitesse de rotation d'entraînement pouvant être réglée à l'avance, dans lequel l'unité de commande (32) réduit la valeur de différence de pression de régulation lorsque la vitesse de rotation d'entraînement augmente et l'augmente lorsque la vitesse de rotation d'entraînement diminue.
  3. Système hydraulique (10) selon l'une quelconque des revendications 1 et 2, caractérisé en ce qu'il est prévu des moyens de réglage (36) en fonction desquels le signal de commande peut être modifié, et en ce que la valeur de différence de pression de régulation est modifiée par l'intermédiaire des moyens de réglage (36) de manière à ce que la valeur de différence de pression de régulation puisse être réduite ou augmentée indépendamment de la vitesse de rotation d'entraînement.
  4. Système hydraulique (10) selon l'une quelconque des revendications 1 à 3, caractérisé en ce qu'il est prévu un capteur de température (37) et en ce que le signal de commande peut être modifié en fonction d'un signal de température délivré par le capteur de température (37) de manière à ce que le volume d'entraînement maximal puisse en outre être réduit ou augmenté en fonction de la température d'un fluide hydraulique du système hydraulique.
  5. Système hydraulique (10) selon l'une quelconque des revendications 1 à 4, caractérisé en ce que les moyens de réglage (38) comprennent un moteur électrique.
  6. Système hydraulique (10) selon l'une quelconque des revendications 1 à 4, caractérisé en ce que les moyens de réglage (38') comprennent un électroaimant, de préférence un électroaimant proportionnel.
  7. Véhicule de travail (44), notamment véhicule agricole ou machine de chantier, comportant un système hydraulique (10) selon l'une quelconque des revendications 1 à 6.
EP09177880.3A 2008-12-18 2009-12-03 Système hydraulique Active EP2199622B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008054880A DE102008054880A1 (de) 2008-12-18 2008-12-18 Hydrauliksystem

Publications (3)

Publication Number Publication Date
EP2199622A2 EP2199622A2 (fr) 2010-06-23
EP2199622A3 EP2199622A3 (fr) 2013-03-06
EP2199622B1 true EP2199622B1 (fr) 2017-09-20

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US (1) US8495871B2 (fr)
EP (1) EP2199622B1 (fr)
DE (1) DE102008054880A1 (fr)

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DE102008054880A1 (de) 2010-07-01
US20100154404A1 (en) 2010-06-24
US8495871B2 (en) 2013-07-30
EP2199622A3 (fr) 2013-03-06
EP2199622A2 (fr) 2010-06-23

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