EP1135613B1 - Procede et dispositif de commande pour consommateur hydraulique - Google Patents

Procede et dispositif de commande pour consommateur hydraulique Download PDF

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Publication number
EP1135613B1
EP1135613B1 EP99963215A EP99963215A EP1135613B1 EP 1135613 B1 EP1135613 B1 EP 1135613B1 EP 99963215 A EP99963215 A EP 99963215A EP 99963215 A EP99963215 A EP 99963215A EP 1135613 B1 EP1135613 B1 EP 1135613B1
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EP
European Patent Office
Prior art keywords
pressure
control
pump
spring
consumer
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.)
Expired - Lifetime
Application number
EP99963215A
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German (de)
English (en)
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EP1135613A1 (fr
Inventor
Burkhard KNÖLL
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Bosch Rexroth AG
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Bosch Rexroth AG
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Publication of EP1135613A1 publication Critical patent/EP1135613A1/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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F15B13/0418—Load sensing elements sliding within a hollow main valve spool
    • 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
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid 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
    • F15B2211/40—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
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • 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
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of a differential 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
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means

Definitions

  • the invention relates to a method for control a consumer according to the preamble of the claim 1 and a control arrangement for controlling a hydraulic consumer according to the preamble of the claim Second
  • Such a control arrangement is, for example, from WO 95/32364 A1 known.
  • a variable displacement pump is regulated in such a way that it Output creates a pressure that is around a certain Differential amount above the highest load pressure of all hydraulic Consumer of the tax arrangement lies. Let it go constant pumps in connection with a 3-way flow control valve or variable displacement pumps with changeable Use stroke volume.
  • a load sensing controller is provided, which in Meaning of a reduction in the volume of the variable displacement pump of pump pressure and in the sense of increasing the stroke volume the pump of the highest load pressure and one Compression spring can be acted upon.
  • the difference between that Pump pressure and the highest load pressure corresponds to the Force of this compression spring.
  • downstream pressure compensators are in which the pump adjusts to the maximum pressure volume has been and the pressure medium flow is not sufficient to the specified pressure drop across the orifice plates of all Consumers maintain the pressure balances of all controlled hydraulic consumers in the closing direction adjusted so that all pressure medium flows to the individual consumers reduced by the same percentage become.
  • LUDV systems load-independent flow distribution
  • the flow channels are used for reporting the highest load pressure for pump control and the Pressure springs of the individual pressure compensators designed in such a way that the load pressure is reported to the pump controller in an unadulterated manner becomes.
  • the hydraulic pump delivers one Stand-by pressure, which is, for example, 20 bar and to control some consumers or valve arrangements is needed.
  • the one corresponding to the stand-by print Pressure difference must be assigned to the other consumers Orifices are broken down, so that considerable Energy losses occur.
  • the invention is based on the object a method and a control arrangement for control to create at least one hydraulic consumer, where the energy losses are reduced to a minimum are.
  • the invention is reduced Load pressure to the pump reported.
  • the stroke volume of the pump depending on this reported (reduced) Load pressure set, so that the pressure loss accordingly above the orifice plate is less than the pressure difference on the pump controller (variable pump). That is, the pressure drop over the orifice plate is compared to the conventional Solutions reduced, so that a corresponding energy saving he follows.
  • Control arrangement When used to carry out the procedure Control arrangement will reduce this for pump control reported load pressure by interpreting the reaches a control piston of the pressure compensating control spring. This is compared with the state of the Technology much higher spring stiffness or preload designed so that the spring force is about that Pressure corresponds to the one reported to the pump controller Load pressure compared to the actually applied load pressure should be reduced. That is, the control arrangement differs essentially compared to conventional solutions by the choice of the spring, so that already existing Control arrangements easily converted can be.
  • the effective spring force preferably set such that they approximately half of the pressure difference corresponding to Pump controller is present or the state of the art the orifice plate falls off.
  • the response behavior of the control arrangement is special well if the spring force of the spring over the entire Hub, d. H. from a position with fully closed Control piston up to the fully open position remains about constant. This is particularly easy by means of a suitable pressure medium flow guide, where the resulting from the pressure medium flow Flow forces both in the closing direction and act in the opening direction of the pressure compensator and designed in this way are that they become one with the control spring force Add constants independent of the control piston stroke.
  • Such a pressure medium flow guide is, for example from the subsequently published P 198 36 564.0 known, the disclosure of which is expressly referred to here is taken.
  • the pressure compensator is preferably with a nozzle bore, through which at complete controlled pressure compensator the load pressure in the load pressure channel is fed.
  • the pressure compensator is preferably with a nozzle bore, through which at complete controlled pressure compensator the load pressure in the load pressure channel is fed.
  • the pressure in the load pressure reporting line is preferred via another connection hole in the pressure compensator reported in the spring chamber of the control piston, whereby this connection bore a damping nozzle for damping of pressure fluctuations.
  • control arrangement can with a Variable pump and associated control unit or with one Constant pump with inlet pressure balance (3-way flow control valve) be executed.
  • FIG. 1 shows a circuit diagram of a valve disk 2 a valve block with two working ports A, B, one Tank connection T and a pump connection P.
  • a consumer for example a hydraulic motor 116 or a double-acting one Cylinder (not shown) connected.
  • Via the hydraulic Circuit can be one of the working connections Connect A, B to pump port P while the other working connection B, A with the tank connection T is connected.
  • the valve disc also has a control connection LS, over which the load pressure at the assigned Consumer can be tapped.
  • the pump is a variable displacement pump executed, the delivery rate depending on Load pressure of the consumer is regulated.
  • load-sensing circuits are adequate in the prior art known, so that a basic description is dispensed with can be.
  • Figure 1 Construction When controlling several consumers via circuits with that shown in Figure 1 Construction is the highest in terms of consumers applied load pressure to the pump and the delivery rate depending on this highest load pressure set.
  • valve disc 2 In the valve disc 2 is a continuously adjustable Directional control valve 4 with a control direction of the Consumer defining direction and a Speedometer forming orifice plate added.
  • the orifice formed by the directional control valve 4 (Speed section) is connected to a pressure compensator 5, whose control piston 40 in its control position the pressure drop across the orifice independent of the load pressure keeps constant.
  • the output connection of the pressure compensator 5 is hydraulic with the directional part of the directional valve 4 connected, depending on the control one of the Working ports A, B supplied with pressure medium and the another is connected to the tank connection T.
  • In the work lines to the work connections A, B are continuous adjustable, unlockable check valve arrangements 6, 8 switched, the reverse flow in its blocking position prevent from the consumer and in the unlocked Pass position a backflow from the corresponding Working connection A or B towards tank connection T. enable.
  • the directional control valve 4 is activated via Pilot valves 10, 12, through which the end faces of a Directional valve spool 28 of the directional valve 4 with one Control pressure can be applied to this from his to shift the neutral position shown.
  • the Directional valve slide 28 is by two compression springs 30, 32nd biased to its neutral position.
  • the control piston 40 the pressure compensator 5 is in the closing direction of the force a control spring 44 and the highest load pressure Consumer loads through a load pressure channel 22 is tapped by the consumer.
  • the pressure downstream of the directional valve 4 is via a Control line 38 to the one acting in the opening direction End face of the control piston 40 out.
  • the pilot valves 10, 12 are continuously adjustable executed so that a pressure of the order between the tank pressure and the pressure at the pump connection P can be applied to the end faces of the directional valve slide 28 is. This control pressure is also used to unlock the Check valve assemblies 6 and 8 used.
  • a pressure relief valve 45 provided, via which the load pressure in the load pressure channel 22nd is limited.
  • the pressure relief valve 45 is in Spring closing direction and opening direction acted upon by the highest load pressure of the consumers. at If the maximum pressure is exceeded, control oil becomes tank T dissipated.
  • the load pressure channel 22 is furthermore connected to the tank via a tank throttle 47.
  • Figure 2 shows a specifically designed valve disc 2, in which the circuit according to FIG. 1 is implemented.
  • valve disc 2 has the two working connections A, B and a pump connection P and the tank connection T, which is the valve disc packing of the valve block perpendicular to the plane of the drawing.
  • the highest load pressure is all over the Valve block controlled consumers to one with the Load pressure channel 22 connected control connection LS performed.
  • the valve disc 2 has mounting holes for the Directional control valve 4, the directional control valve 28 as Hollow slide is formed.
  • the only in Figure 2 Dashed piston 40 is inside the Directional valve slide 28 out.
  • Each of the check valve assemblies 6 has a pre-opening main cone 72 which cooperates with an impact piston 92, via which the Main cone 72 for unlocking from its valve seat can be lifted off.
  • the two pilot valves 10, 12 are in Cartridge design and in the lower in Figure 2 End face of the valve disc 2 screwed in. Both Pilot valves 10, 12 are, for example electrically operated pressure reducing valves, via which the Pressure at the pump connection P to a system pressure at axial outlet connection of the respective pilot valve 10, 12 is reducible. As can be seen from Figure 1, has each pilot valve 10, 12 next to that with the pump connection P connected input port another one with the Tank connection T connected radial connection.
  • DE 196 46 428 A1 discloses a valve arrangement for Actuation of a double-acting consumer at the hydraulic fluid delivered by a pump via a Directional control valve optionally one of two working connections Can be fed, each of which a check valve assembly assigned. Each check valve arrangement is about controlled a pilot valve assigned to this, the Output control pressure also on one end of the Directional valve spool is present. By energizing both Pilot valves can be found in the directional valve spool Clamp the zero position and the two Unlock check valve assemblies so that the Working connections with the check valve arrangements with a tank can be connected and thus a floating position is adjustable.
  • valve disc 2 for receiving the Directional valve slide 28, a valve bore 50 in which Annular spaces 52, 54, 56, 58 extending radially outward and 60 are formed.
  • annular space 52 is dashed over a in Figure 2 indicated load pressure signaling line 62 with the Load pressure channel 22 connected to the control connection LS is led.
  • the two annular spaces 54 and 56 are over Working channels 66, 68 to the working connections A and B guided.
  • the annular space 58 is on the one hand Pump line 70 connected to the pump port P and on the other hand via a connecting channel 74 to one Radial connection of the pilot valves 10, 12 out.
  • the Annulus 60 is also hydraulic with the pump connection P connected.
  • the directional valve slide 28 is 30.32 in via compression springs biased its basic position shown in Figure 3.
  • the two compression springs 30, 32 are on locking screws 90 supported, the valve bore 50 in the axial direction to lock.
  • the Directional valve slide 28 is designed as a hollow piston and has an axial bore 94, which is shown in the illustration Figure 3 from the left end portion of the directional valve spool 28 extends into the area of the ring channel 60.
  • this axial bore 94 opens a measuring aperture bore star 96, whose breakthroughs as radial bores are formed in the directional valve spool jacket.
  • the orifice hole star 96 arranged between the two annular spaces 58, 60.
  • a directional bore star 98 formed in the shown basic position between the two annular spaces 54, 56 is arranged.
  • the control piston 40 is inside the axial bore 94 slidably guided and via the control spring 44 with a Ring face 100 against a stop shoulder Axial bore 94 biased into its closed position.
  • On Control piston spring chamber 104 is via a connecting bore 106, a damping throttle 108 and an opening 109 connected in the directional valve slide 28 to the annular space 52, so that the load pressure the control piston 40 also in Closing direction applied.
  • Control piston 40 an axial blind hole 110 which in the right ( Figure 4) end face of the control piston 40 opens.
  • the jacket of the control piston 40 is in the mouth region penetrated radially crown-shaped by openings 112.
  • a compensation bore star 114 is at a distance from these trained in the position shown in the area of the annular space 54 is arranged.
  • control piston 40 In the area between the openings 112 and the Bore star 114 is the control piston 40 radial downgraded so that a 112 in the area of the openings first control edge 116 and in the area of Compensation bore star 110 a second control edge 118 is formed.
  • the radially stepped section 115 is in the Area of the first control edge 116 as an inclined surface trained while in the area of the second Control edge 118 is designed as a radial stage.
  • the directional valve slide 28 has two according to Figure 4 axially spaced annular grooves 120, 122 which in the Inner peripheral surface of the axial bore 94 are formed.
  • the two ring grooves 120, 122 are through one Center web 124 separated from each other, the one with the second Control edge 118 cooperates.
  • the one in the illustration 4 right circumferential edge of the first annular groove 120 interacts with the first control edge 116, so that at Axial displacement of the control piston 40 through cooperation the first control edge 116 and the first annular groove 120 a control cross section is opened while by interaction of the second control edge 118 and the Mittelsteg 124 a compensation control cross section is opened.
  • the closed both tax cross sections Regarding further details of this compensation flow guidance on the subsequently published application 198 36 564.0 directed.
  • the directional bore star 98 opens into the first Ring groove 120.
  • the connecting bore 106 designed as an angle bore, with a radial bore leg 126 of the connection bore 106 in the opening 109 of the directional control valve 28 opens.
  • the radial bore leg 126 is arranged so that the connection between the ring channel 52 and the spring chamber 104 over the entire Stroke of the control piston 40 is open. That is, the Control piston 40 is always in the closing direction by the Force of the control spring 44 and the load pressure in the load pressure channel 22 acted upon.
  • the axial bore 110 of the control piston 40 opens its left end portion in a nozzle bore 128, the in turn in a radial bore 130 of the control piston 40 transforms.
  • the opening cross section of the nozzle bore 128 is that when the opening is open Pressure relief valve 45 from the load pressure channel 22 to the tank T flowing control oil quantity reduced so that the responsiveness and efficiency of the hydraulic Control can be improved.
  • the control spring 44 is in the embodiment shown with a large preload or a high spring stiffness executed so that about half the stand-by pressure the variable pump must be applied to the Shift control piston 40 against the force of the control spring 44. That is, at a stand-by pressure of about 20 bar, which in the circuit shown for actuating the Pilot valves 10, 12 is required, the control spring 44th designed as a 10 bar spring.
  • the pressure medium flow along the control piston 44 is by suitable geometric Design of the control cross section described at the beginning and in the opposite direction effective control cross-section designed so that the resultant from the force of the control spring 44 and the flow forces acting on the control piston is a constant that is independent of the control piston stroke. With in other words, the control spring 44 and the flow forces are coordinated so that the result is a horizontal spring characteristic, where the spring force is independent of the stroke of the control piston 40 is.
  • the pressure medium passes through the open orifice hole star 96 in the axial bore 94, see above that the control piston 40 of the pressure compensator against the force of the Control spring 44 is acted upon in the opening direction.
  • the control piston 40 of the pressure compensator against the force of the Control spring 44 is acted upon in the opening direction.
  • the control piston 40 of the pressure compensator against the force of the Control spring 44 is acted upon in the opening direction.
  • the control piston 40 By the pressure build-up at the inlet of the pressure compensator 5 becomes the control piston 40 brought into its left end position in FIG. 3, so that the compensation cross section and the control cross section are fully controlled on.
  • the radial bore 130 is opened via the control edge 132, so that the pressure at the input of the pressure compensator 5 over the axial blind bore 110, the nozzle bore 128, the Radial bore 130 and the opening 109 in the load pressure reporting line 62 and thus into the load pressure channel 22 is reported.
  • load pressure corresponds to the force of the control spring 44 lower than that at the inlet
  • the Stand-by pressure of the variable pump is 20 bar.
  • the Load pressure at the inlet of the pressure compensator, d. H. in the working channel 66, for example, should be 200 bar.
  • a method and a control arrangement are disclosed to control at least one hydraulic consumer.
  • the control arrangement has a pump whose output adjustable depending on the load pressure of a consumer is. Its control takes place via a Proportional directional control valve, one Pressure compensator is assigned, via which the pressure drop over the orifice plate is kept constant regardless of the load pressure. According to the invention, when the pressure compensator is fully open a lower load pressure to the pump is reported, so that the pressure drop across the orifice plate is reduced.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un procédé et un dispositif de commande qui permettent de commander au moins un consommateur hydraulique. Le dispositif de commande comporte une pompe dont le rendement peut être réglé en fonction de la pression de charge du consommateur et qui est commandée par l'intermédiaire d'un distributeur proportionnel (4) formant un diaphragme de mesure. Une balance de pression (5), associée au distributeur, maintient constante la diminution de pression par l'intermédiaire du diaphragme de mesure, indépendamment de la pression. Selon l'invention, quand la balance de pression est totalement ouverte, une charge de pression moindre est appliquée à la pompe, qui atténue la diminution de pression par l'intermédiaire du diaphragme.

Claims (10)

  1. Procédé de commande d'un consommateur par l'intermédiaire d'un dispositif de commande, avec une pompe dont la puissance est régulée en fonction d'une pression de pilotage dans un canal de pression de pilotage de telle sorte que la pression de la pompe soit supérieure d'une différence de pression spécifiée à la pression de pilotage, et avec un distributeur (4), par lequel est réalisé un diaphragme de mesure et dans le tiroir de distributeur (28) duquel est guidé un piston de régulation (40) d'une balance de pression (5), par laquelle la chute de pression à travers le diaphragme de mesure est maintenue constante indépendamment de la pression de charge d'un consommateur, le piston de régulation (40) étant soumis dans le sens de l'ouverture à la pression en aval du diaphragme de mesure et dans le sens de la fermeture à un ressort de régulation (44) et à la pression de pilotage et, quand la balance de pression (5) est complètement ouverte, la pression en aval du diaphragme de mesure est signalée dans le canal de pression de pilotage (22), caractérisé en ce que, quand la balance de pression (5) est complètement ouverte, une pression est signalée dans le canal de pression de pilotage (22), cette pression étant nettement inférieure à la pression de charge du consommateur, mais la différence d'avec la pression de charge étant inférieure à la différence de pression spécifiée.
  2. Dispositif de commande pour la commande d'au moins un consommateur hydraulique, avec une pompe dont la pression de refoulement est réglable en fonction d'une pression de pilotage dans un canal de pression de pilotage (22) de telle sorte que la pression de refoulement de la pompe est située d'une différence de pression spécifiée au-dessus de la pression de pilotage, avec un distributeur (4) pour la commande du consommateur, distributeur par lequel est formé un diaphragme de mesure et dans le tiroir de distributeur (28) duquel est guidé un piston de régulation (40) d'une balance de pression (5), par lequel la perte de charge à travers le diaphragme de mesure peut être maintenue constante indépendamment de la pression de charge d'un consommateur, et qui est soumis dans le sens de l'ouverture à la pression en aval du diaphragme de mesure et dans le sens de la fermeture à un ressort de régulation (44) et à la pression de pilotage, la pression en aval du diaphragme de mesure pouvant être signalée dans le canal de pression de pilotage (22) quand la balance de pression (5) est complètement ouverte, caractérisé en ce que la raideur et / ou la précharge du ressort de régulation est calculée de telle sorte que, quand la balance de pression (5) est complètement ouverte, une pression de charge du consommateur nettement diminuée, mais diminuée d'une valeur moindre que la différence de pression spécifiée, est signalée à la pompe comme pression de pilotage.
  3. Dispositif de commande selon la revendication 2, caractérisé en ce que la force élastique du ressort de régulation (44) correspond à peu près à la moitié de la force de pression correspondant à la différence de pression.
  4. Dispositif de commande selon une des revendications 2 ou 3, caractérisé en ce que l'écoulement du fluide sous pression est guidé de telle sorte que les forces hydrodynamiques qui agissent sur le piston de régulation (40), avec la force du ressort de r é gulation (44), exercent sur le piston de r é gulation (40) une force à peu près constante sur toute la course de ce dernier.
  5. Dispositif de commande selon la revendication 4, caractérisé en ce que le piston de régulation (40) a deux arêtes de commande (116, 118), par lesquelles peut être commandée l'ouverture d'une section de commande, respectivement d'une section de commande de compensation, par lesquelles des écoulements de sens opposé du fluide sous pression peuvent être provoqués.
  6. Dispositif de commande selon une des revendications 2 à 5, caractérisé en ce que le piston de régulation (40) est percé d'une buse (128), par laquelle peut être commandée l'ouverture d'une communication entre un compartiment en aval du diaphragme de mesure et le canal de pression de pilotage (22) dans lequel est disposée une valve de limitation de pression (45) pour limiter la pression de pilotage.
  7. Dispositif de commande selon la revendication 6, caractérisé par un trou de communication (106), par lequel le compartiment du ressort (104) du piston de ré gulation (40) peut être mis en communication avec le canal de pression de pilotage (62, 22).
  8. Dispositif de commande selon la revendication 7, caractérisé en ce qu'une buse d'amortissement (108) est prévue dans le trou de communication (106).
  9. Dispositif de commande selon une des revendications 2 à 8, caractérisé en ce que la différence de pression correspond à environ 20 bar et la force du ressort de régulation (44) à environ 10 bar.
  10. Dispositif de commande selon une des revendications 2 à 9, caractérisé en ce que la pompe est une pompe à cylindrée constante avec une balance de pression à l'entrée, ou une pompe à cylindrée variable.
EP99963215A 1998-11-30 1999-11-11 Procede et dispositif de commande pour consommateur hydraulique Expired - Lifetime EP1135613B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19855187 1998-11-30
DE19855187A DE19855187A1 (de) 1998-11-30 1998-11-30 Verfahren und Steueranordnung zur Ansteuerung eines hydraulischen Verbrauchers
PCT/DE1999/003601 WO2000032944A1 (fr) 1998-11-30 1999-11-11 Procede et dispositif de commande pour consommateur hydraulique

Publications (2)

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EP1135613A1 EP1135613A1 (fr) 2001-09-26
EP1135613B1 true EP1135613B1 (fr) 2003-04-09

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US (1) US6516614B1 (fr)
EP (1) EP1135613B1 (fr)
DE (2) DE19855187A1 (fr)
WO (1) WO2000032944A1 (fr)

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Also Published As

Publication number Publication date
WO2000032944B1 (fr) 2000-08-31
WO2000032944A1 (fr) 2000-06-08
EP1135613A1 (fr) 2001-09-26
DE59905000D1 (de) 2003-05-15
DE19855187A1 (de) 2000-05-31
US6516614B1 (en) 2003-02-11

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