EP1664551B1 - Dispositif de commande et procede d'alimentation d'un moyen de pression a au moins deux charges hydrauliques - Google Patents

Dispositif de commande et procede d'alimentation d'un moyen de pression a au moins deux charges hydrauliques Download PDF

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Publication number
EP1664551B1
EP1664551B1 EP04786730A EP04786730A EP1664551B1 EP 1664551 B1 EP1664551 B1 EP 1664551B1 EP 04786730 A EP04786730 A EP 04786730A EP 04786730 A EP04786730 A EP 04786730A EP 1664551 B1 EP1664551 B1 EP 1664551B1
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EP
European Patent Office
Prior art keywords
pressure
meter
consumers
orifice
load
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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.)
Expired - Lifetime
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EP04786730A
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German (de)
English (en)
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EP1664551A1 (fr
Inventor
Horst Hesse
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Bosch Rexroth AG
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Bosch Rexroth AG
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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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • 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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • F15B21/087—Control strategy, e.g. with block diagram
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40561—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged upstream of the flow control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6346—Electronic controllers using input signals representing a state of input means, e.g. joystick position

Definitions

  • the invention relates to a control arrangement for pressure medium supply of at least two hydraulic consumers according to the preamble of claim 1 and a method for controlling such consumer according to the preamble of claim. 6
  • variable displacement pump is adjusted depending on the highest load pressure of the actuated hydraulic consumers so that the inlet pressure is above the highest load pressure by a certain pressure difference.
  • the downstream pressure compensators in the opening direction of the pressure to the respective metering orifice and in the closing direction of a control pressure, which usually corresponds to the highest load pressure of all driven consumers acted upon. If the metering orifices are opened so far in a simultaneous actuation of several hydraulic consumers, that the pressure medium supplied by the hydraulic pump to the stop is smaller than the total required pressure medium, the pressure fluid quantities flowing to the individual hydraulic consumers will be independent of the respective load pressure of the hydraulic consumers reduced (load-independent flow distribution).
  • the pressure compensator upstream or downstream of the metering orifice is acted upon in the closing direction by the pressure before the metering orifice and in the opening direction by the individual load pressure of the respective hydraulic consumer, so that no load-independent flow distribution is obtained.
  • Such a control arrangement is for example in the EP 0 972 138 B1 disclosed, wherein the pressure compensators are connected upstream of the metering orifices.
  • the pressure compensators are connected downstream of the metering orifices.
  • variable displacement pump is actuated depending on the highest load pressure picked up via an LS line such that a pressure is established in the pump line which is equivalent to the force of a control spring of a pump control valve pressure difference above the highest load pressure lies.
  • Electrohydraulic LS system described in which the control of the pump setting is carried out electronically.
  • the effective at the consumers pressures, the pump pressure, the drive speed and the drive torque of the variable is detected and issued depending on eg. Via a joystick predetermined setpoints control signals to the pump control valve and the consumers upstream proportional valves.
  • the function of the individual pressure compensators assigned to the metering orifices is implemented electronically.
  • the pump pressure is adjusted so that it is above the highest load pressure by a predetermined pressure difference, so that in this type of control corresponding system losses occur.
  • Electro-hydraulic LS systems are known in which the Total volumetric flow either from the deflections of the directional control valves forming the metering or from the settings of the setpoint generator (joysticks) determined and this sum volume flow is compared with a maximum flow rate of the pump.
  • the stroke of all controlled directional control valves is electrically reduced so far that the respective flow rates are proportionally reduced and thus the set trajectory of the driven consumers is maintained at a reduced adjustment speed.
  • the document EP 0 587 902 A1 which represents the closest prior art, relates to a control arrangement in which the maximum load pressure is used to drive the pump.
  • the valve associated with the maximum load pressure hydraulic cylinder is maximally opened to minimize pressure loss across this valve.
  • the invention has the object, a control arrangement and a method for pressure medium supply of at least two hydraulic consumers in such a way that a control of multiple consumers with a predetermined speed with reduced energy losses is possible.
  • the individual load pressures of the consumers are detected via suitable sensors and the load-pressure-highest consumers are determined from these signals.
  • the metering orifice associated with the load-pressure-highest consumer is completely opened by the setting resulting from the predetermined setpoint, so that the pressure loss exceeds that which is the highest in the load associated metering orifice is minimal.
  • this metering orifice is associated with an individual pressure compensator, this is also completely controlled, as well as a small excess of the funded by the pump pressure medium flow at the fully open metering orifice can not produce a pressure drop, the pressure compensator against the force of one of these associated control spring could adjust in the closing direction.
  • control arrangement according to the invention or the method according to the invention can be used in control arrangements in which the individual pressure compensators are arranged upstream or downstream of the metering orifices.
  • the control arrangement is designed with a further sensor for detecting the system pressure, ie the pressure upstream of the metering orifices
  • the pressure difference across the respective metering orifices can be determined via the signals detected by the pressure sensors.
  • the metering orifices are then adjusted so that the desired pressure medium flow rate flows to the consumers. That is, in such a variant, the function of the individual pressure compensators is realized electronically, but in contrast to the aforementioned document (O + P), the metering orifice of the load pressure highest consumer is always completely turned on, so that the energy losses compared to the known solution are reduced.
  • the control arrangement according to the invention with the metering orifices upstream or downstream individual pressure compensators is executed, which are acted upon in the closing direction of the pressure upstream of the metering orifice and in the opening direction of the pressure downstream of the metering orifice.
  • variable displacement pump In the case of a pulling load, this can be detected by the sensors used according to the invention and the variable displacement pump can be reset and the pressure medium can be sucked into the low pressure side of the consumers via suction valves.
  • the flow rates of the metering orifices associated with the lower-load consumers can be reduced proportionally. This reduction is preferably in the ratio of the maximum pump delivery to the desired target amount.
  • the load pressures simultaneously actuated consumers are compared and in the case in which these load pressures differ by less than the rule ⁇ p of the pressure compensator, the metering orifice of the load pressure lower consumer further opened than that of Setpoint is specified, so that this pressure difference is compensated.
  • illustrated control arrangement 1 operates on the current regulator principle, in which a plurality of current regulator are connected in parallel.
  • the illustrated control arrangement 1 has a variable displacement pump 2, via which two or more consumers 4, 6 can be supplied with pressure medium. Their control is carried out by means of a control device, such as a joystick 8, are discharged via the control signals to an electronic control device 10. These signals represent a command to move the loads at a certain speed and along a given trajectory.
  • variable displacement pump 2 The output of the variable displacement pump 2 is connected to a pump line 12, which in two supply lines 14, 16 branches.
  • a pump line 12 which in two supply lines 14, 16 branches.
  • an electronically proportionally adjustable metering orifice 18 and 20 is arranged, which are each adjustable via a proportional solenoid 22, which is controlled by the control device 10.
  • the metering orifices 18, 20 formed, for example, by a proportional valve are respectively followed by a pressure compensator 24 or 26, which is acted upon in the opening direction by the force of a control spring and by the pressure downstream of the metering orifices 18, 20 and in the closing direction by the pump or system pressure is tapped off from the pump line 12 via a branching control line 28.
  • the outputs of the pressure compensators 24, 26 are connected via flow lines 30 and 32 to the consumers 4, 6.
  • these consumers are 4, 6 hydraulic cylinders whose cylinder chambers are connected to the flow line 30 and 32, respectively.
  • the return and discharge lines connecting the cylinder chambers to the tank T are omitted, whose flow cross-sections are also opened or closed via the proportional valve forming the metering orifice 18, 20.
  • the load pressures of the consumers 4, 6 are detected and the setting of the metering orifices 18, 20 changed as a function of these load pressures.
  • these load pressures are detected by pressure sensors 34, 36, which are arranged in the flow lines 30, 32 and whose signals are processed by the control device 10.
  • the pressure sensors 34, 36 and the joystick 8 via signal lines to the control device
  • Control signals via signal lines to the electrically operated pump control valve as well as the two proportionally adjustable metering orifices 18, 20 are delivered via the then corresponding to the predetermined set values and the detected load pressures.
  • variable displacement pump with variable tilt angle instead of a variable displacement pump with variable tilt angle, for example, a constant displacement pump with variable speed drive can be used.
  • the variable displacement pump 2 is preferably designed with a pressure sensor for detecting the pump pressure, a speed sensor for detecting the pump speed and a swivel angle sensor for detecting the pump swivel angle. Furthermore, the characteristic curves of the variable displacement pump 2 and the two proportionally adjustable metering orifices 18, 20 are stored in the control device so that with the aid of all or some of the aforementioned sensors and characteristic curves an extremely exact volume flow control via the variable displacement pump 2 is possible.
  • the function of the control arrangement according to the invention is as follows.
  • variable displacement pump 2 To actuate the two consumers 4, 6 8 control signals are generated by the operator via one or more joysticks, which are delivered to the control device 10.
  • the variable displacement pump 2 For the corresponding control of the consumers 4, 6, the variable displacement pump 2 must provide a certain pressure medium volume flow which corresponds to the sum of the setpoint volume flows set via the joystick 8. That is, the variable displacement pump 2 must be adjusted in dependence on the setting of the joystick 8 to a swivel angle at which this sum volume flow is delivered.
  • the corresponding setting of the variable displacement pump 2 can be easily determined by detecting the current pump pressure as a function of the desired value. the current pump speed and the set swivel angle via the pump curve.
  • the pump controller thus receives no pressure signal, which usually corresponds to the highest load pressure, but the control of the variable displacement pump 2 takes place in dependence on the desired values. This eliminates the need to tap the load pressures over complex shuttle valve assemblies to the consumers and lead over comparatively long lines to the variable displacement pump 2.
  • volumetric flow errors due to volumetric losses of the variable displacement pump 2 can be compensated because the operator immediately readjusted via the joystick 8, if the consumers 4, 6 are not operated at the desired speed.
  • the highest load pressure then adjusts accordingly to the most heavily loaded consumer and the pressure difference to the lower-load consumers is throttled away by current control of the individual pressure compensators 24, 26.
  • the consumer is determined via the pressure sensors 34, 36, to which the highest load pressure is applied.
  • the signals detected by the pressure sensors 34, 36 are compared with each other in the control device 10 and delivered to the metering orifice 18, 20, which is assigned to the consumer 4, 6 with the highest load pressure, a control signal through which these metering orifice 18, 20 completely is opened.
  • a control signal through which these metering orifice 18, 20 completely is opened.
  • the associated pressure compensator 24 and 26 of the load pressure highest consumer 4 and 6 is then also completely open, since the pressure difference across the associated metering orifice 18 and 22 is not sufficient to adjust the pressure compensator against the force of the control spring in the closing direction.
  • the current regulator circuit with the metering orifices 18, 20 downstream pressure compensators 24, 26 executed. Since in the LUDV systems described above, the pressure compensators always have to be connected downstream of the metering orifices, for the in FIG. 1 shown system and used for LUDV systems identical or only slightly modified housing.
  • control arrangement according to the invention can also be realized in circuits in which the individual pressure compensators 24, 26 are connected upstream of the metering orifices 18 and 20 respectively. These pressure compensators are also acted upon in the opening direction by the pressure downstream of the metering orifices 18, 20 and in the closing direction by the pressure upstream of the metering orifices 18, 20, ie the pump pressure supplied by the variable displacement pump 2.
  • the other structure and function of in FIG. 2 shown control arrangement correspond to the embodiment according to FIG. 1 , so that further explanations are dispensable.
  • FIG. 3 a variant is shown in which the metering orifices 18, 20 are assigned no individual pressure compensators.
  • the function of the individual pressure compensators is practically taken over by the electronics.
  • the pressure in the pump line 12, ie the pressure upstream of the metering orifices 18, 20 must be detected via a further pressure sensor 38. From this pressure and the pressure detected via the pressure sensors 34, 36, downstream of the metering orifices 18, 20 can then calculate the pressure drop across the metering orifices 18, 20.
  • the flow cross section of the respective metering orifices 18, 20 can then be adjusted via the control device 10 using the stored characteristic curves so that the desired volume flow flows to the consumers 4, 6.
  • the setting of the variable displacement pump 2 takes place in the manner described above in dependence on the set values set via the joystick 8.
  • variable-displacement pump is set to the desired total flow and the individual pressure medium flows are distributed to the consumers by suitable control of the valve diaphragms, with the metering orifice associated with the load-pressure-highest consumer being completely opened.
  • Such a control makes it possible, for example in the case of an undersupply, ie in the case in which the desired amount is greater than the maximum pump quantity, to proportionally reduce the flow through the metering orifices of the load-pressure-reduced consumers.
  • a LUDV behavior can be generated practically by reducing the opening cross sections of the metering orifices 18, 20 having lower load pressure. This reduction can be done, for example, in the ratio of the maximum pump delivery rate to the target amount. This will be explained with reference to an example in which the control arrangement according to the invention is designed to control three consumers.
  • the set on joysticks 8 at the three consumers set currents 40, 60 and 20 liters / minute, ie, the target total volume flow is 120 liters / minute
  • the Lasttikonnee consumers should be supplied with 20 liters / minute.
  • the maximum flow rate of the pump is for example 100 liters / minute - there is thus a shortage.
  • This deficiency is compensated according to the invention in that the setpoint values for the two lower-load consumers (40, 60 liters / minute) are reduced via the control device 10 in the ratio of the maximum delivery rate of the pump to the total volume flow, ie in the ratio 100/120.
  • the first-mentioned consumer is supplied with 33.33 liters / minute, the second-named consumer with 50 liters / minute (per unit time).
  • the metering orifice of the load pressure-highest consumer is fully controlled according to the invention - the adjusting volume flow over this metering orifice is 16.66 liters / minute, so that the maximum flow rate of the pump of 100 L / minute divided proportionally and thus practically a load-independent flow distribution (LUDV) is realized ,
  • FIGS. 1 and 2 explained embodiments are characterized by a low susceptibility to vibration.
  • the setpoint values can be determined instead of via the electric joystick 8 also in the case of proportional valves with spool travel measurement from the spool travel actual value of the metering orifices 18, 20.
  • the system according to the invention is also effective when only a single consumer is driven - in this case, the metering orifice of this consumer is completely opened and controlled the pressure medium flow through the variable displacement pump 2.
  • FIG. 4 shows a control arrangement in which the individual load pressures of the consumers 4, 6 are not detected by pressure sensors or the like. It is again a flow control system, wherein the two individual pressure compensators 24, 26 are connected downstream of the two proportionally adjustable metering orifices 18, 20. That is, apart from the two non-existing sensors 34, 36 corresponds to in FIG. 4 shown control arrangement of those FIG. 1 , Also in the control arrangement according to FIG. 4 the variable displacement pump 2 is adjusted as a function of the set values set via the joystick 8 so that it delivers the desired total pressure medium flow.
  • this pressure medium total flow then takes place via the flow regulators (metering orifices 18, 20, pressure compensators 24, 26), the metering orifices 18, 20 in turn being adjusted as a function of the setpoint values set on the joystick 8.
  • About the individual pressure compensators 24, 26 is then applied to the output of the metering orifices 18, 20 load pressure corresponding approximately to the highest effective load pressure of the consumer, throttled to the individual load pressures.
  • the load pressure higher consumers associated metering orifice remains on depending on the given Setpoints set opening cross-section and is not fully open.
  • a control arrangement and a method for pressure medium supply of at least two hydraulic consumers which are supplied via a variable displacement pump with pressure medium.
  • each metering orifice is provided in the pressure medium flow path between the consumers and the variable displacement.
  • the setting of the variable displacement pump and the metering orifices is carried out electronically via a control device as a function of the setpoint values entered by an operator.
  • the metering orifice associated with the load-pressure-highest consumer is completely opened, so that the pressure loss across this metering orifice is minimal.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
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Claims (7)

  1. Système de commande servant à alimenter en fluide sous pression au moins deux consommateurs hydrauliques (4, 6) avec un agencement de pompe à débit réglable (2), dont le débit peut être modifié, et avec au moins deux diaphragmes de dosage (18, 20) réglables, qui sont affectés respectivement à un des consommateurs (4, 6) et qui sont réglables respectivement en fonction d'une valeur de consigne réglée au niveau d'un transmetteur de valeur de consigne (8) par le biais d'un dispositif de commande (10) et avec un dispositif (10) servant à émettre un signal de commande à la pompe à débit réglable (2) en fonction des valeurs de consigne réglées, avec un capteur (34, 36) prévu dans le chemin d'écoulement de fluide sous pression en aval des diaphragmes de dosage pour détecter la pression de charge individuelle, et avec un dispositif (10) de détection du consommateur (4, 6) ayant la pression de charge la plus élevée à partir des signaux détectés par les capteurs (34, 36) et de commande du diaphragme de dosage (18, 20) associé au consommateur (4, 6) ayant la pression de charge la plus élevée,
    caractérisé en ce qu'une balance de pression (24, 26), qui est alimentée dans le sens de fermeture par la pression en amont du diaphragme de dosage (18, 20) et dans le sens d'ouverture par la pression en aval du diaphragme de dosage (18, 20) associé, est placée en amont ou en aval de chaque diaphragme de dosage (18, 20).
  2. Dispositif de commande selon la revendication 1, comprenant une valve de réaspiration permettant de réaspirer du fluide sous pression côté basse pression des consommateurs (4, 6).
  3. Dispositif de commande selon l'une quelconque des revendications 1 et 2, le transmetteur de valeur de consigne étant au moins un manche à balai (8).
  4. Procédé de commande d'un agencement de commande servant à alimenter en fluide sous pression au moins deux consommateurs hydrauliques, avec un agencement de pompe à débit réglable (2), dont le débit peut être modifié, et avec au moins deux diaphragmes de dosage (18, 20) réglables, qui sont affectés respectivement à un des consommateurs (4, 6) et qui sont réglables respectivement en fonction d'une valeur de consigne réglée au niveau d'un transmetteur de valeur de consigne (8) par le biais d'une unité de commande (10), et avec un dispositif (10) servant à émettre un signal de commande à la pompe à débit réglable (2) en fonction des valeurs de consigne réglées, la pression de charge individuelle des consommateurs (4, 6) étant détectée et le diaphragme de dosage (18, 20) associé au consommateur (4, 6) ayant la pression de charge la plus élevée étant entièrement ouvert, caractérisé en ce qu'une balance de pression (24, 26), qui est placée en amont ou en aval de chaque diaphragme de dosage (18, 20), est alimentée dans le sens de fermeture par la pression en amont du diaphragme de dosage (18, 20) et dans le sens d'ouverture par la pression en aval du diaphragme de dosage (18, 20) associé.
  5. Procédé selon la revendication 4, les sections transversales d'écoulement des diaphragmes de dosage (18, 20) associés aux consommateurs (4, 6) ayant la pression de charge la plus faible étant réduites dans le cas d'une sous-alimentation - de préférence selon le rapport débit de pompe maximal et débit volumétrique total de consigne.
  6. Procédé selon la revendication 4 ou 5, une charge de traction étant décelée par exploitation des signaux détectés par les capteurs (34, 36), et la pompe à débit réglable (2) étant freinée en conséquence.
  7. Procédé selon l'une quelconque des revendications 4 à 6, le diaphragme de dosage (18, 20) associé au consommateur (4, 6) ayant la pression de charge la plus faible étant ouvert jusqu'à ce que cette différence pression de charge-pression soit compensée en cas de commande simultanée de plusieurs consommateurs (4, 6), dont la pression de charge est comparée et en cas de pression de charge différentielle, qui est inférieure à Δp de réglage de la balance de pression.
EP04786730A 2003-09-11 2004-09-09 Dispositif de commande et procede d'alimentation d'un moyen de pression a au moins deux charges hydrauliques Expired - Lifetime EP1664551B1 (fr)

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DE10342037A DE10342037A1 (de) 2003-09-11 2003-09-11 Steueranordnung und Verfahren zur Druckmittelversorgung von zumindest zwei hydraulischen Verbrauchern
PCT/DE2004/002008 WO2005024245A1 (fr) 2003-09-11 2004-09-09 Dispositif de commande et procede d'alimentation en milieu sous pression d'au moins deux charges hydrauliques

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EP1664551A1 EP1664551A1 (fr) 2006-06-07
EP1664551B1 true EP1664551B1 (fr) 2008-04-16

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WO2005024245A1 (fr) 2005-03-17
JP2007505270A (ja) 2007-03-08
ATE392555T1 (de) 2008-05-15
EP1664551A1 (fr) 2006-06-07
US20070006580A1 (en) 2007-01-11
DE10342037A1 (de) 2005-04-07
DE502004006859D1 (de) 2008-05-29
US7434393B2 (en) 2008-10-14

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