EP0603722B1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP0603722B1
EP0603722B1 EP93120202A EP93120202A EP0603722B1 EP 0603722 B1 EP0603722 B1 EP 0603722B1 EP 93120202 A EP93120202 A EP 93120202A EP 93120202 A EP93120202 A EP 93120202A EP 0603722 B1 EP0603722 B1 EP 0603722B1
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EP
European Patent Office
Prior art keywords
control
valve
line
hydraulic
pressure
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
EP93120202A
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German (de)
English (en)
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EP0603722A1 (fr
Inventor
Rudolf Brunner Obering
Martin Dipl.-Ing. Heusser
Harald Dipl.-Ing. Klemens
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.)
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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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
    • F15B11/003—Systems with 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
    • 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
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • 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
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure

Definitions

  • the invention relates to a hydraulic control device of the type specified in the preamble of claim 1.
  • the inflow regulating pressure compensator regulates the amount allocated to the proportional directional control slide valve to such an extent that the hydraulic consumer stops when a load limit is reached. This is brought about by the response of a pressure limiting valve connecting the control line to the return line to the load pressure prevailing in the control line. Until this load limit is reached, the hydraulic consumer can be moved independently of the load at the speed selected by the setting of the slide piston, ie, if necessary at the maximum speed. Because of the maximum speed of the hydraulic consumer or the respective load that is possible until the load limit is reached, a relatively high safety factor must be taken into account for a mobile crane equipped with this control device, which greatly limits the permissible load and / or the range.
  • a relatively large safety factor must be taken into account for safety reasons, which limits the load capacity and / or the range.
  • the safety factor depends on the speed of movement.
  • the amount of hydraulic medium flowing to the hydraulic consumer and thus the speed of movement of the hydraulic motor are reduced in a hydraulic control device according to EP-B-0 340 235 depending on the load.
  • the safety factor to be taken into account when calculating the hoist is then lower as soon as the critical load condition is reached due to the reduced speed.
  • a throttle travel control slide is used, in which a load-independent speed control is not possible.
  • the quantity reduction device is built into the spool of the throttle travel control spool and uses the load pressure of the hydraulic motor to reduce the inflow quantity via a bypass control for the return. Since the load pressure controls the reduction in quantity, no load holding valve can be used to hold the load. The full pump pressure is applied to the throttle valve on the respective pressure side. Since hydraulic medium is drained to the tank via the bypass control means this results in a high mechanical load on the hydraulic medium and an undesirable development of heat. Furthermore, the bypass control is unsuitable if a plurality of directional control slides arranged in parallel control hydraulic motors which can be loaded at different levels simultaneously. A particularly serious disadvantage results from the scanning of the load pressure to reduce the feed quantity if the load pressure does not represent a meaningful reference value in special operating conditions.
  • the invention has for its object to provide a hydraulic control device of the type mentioned, which is structurally simple, enables load-independent speed control of the hydraulic consumer, and in which the quantity reduction can be controlled very reliably.
  • the proportional directional spool valve with the inlet control pressure compensator always ensures load-independent speed control of the hydraulic motor. Since the quantity-reducing device is arranged separately from the slide piston, it can advantageously be operated with a hydraulic or electrical or Control mechanical signal that meaningfully represents a critical load condition of the hoist. This increases the reliability of the quantity reducing device, because it does not have to respond to the load pressure tapped off on the spool if this is not meaningful enough.
  • the hydraulic control device is structurally simple because it works with proven proportional directional spool valves and inlet regulating pressure compensators, which only require simple and inexpensive modifications, which can be retrofitted if necessary, for the quantity reduction function.
  • the use of load holding valves which is advantageous for safety reasons, is possible without restriction.
  • the gripping range and / or the load capacity of the hoist can be increased because the speed of movement can be freely reduced in the critical loading state of the hoist. If the quantity-reducing device intervenes between the inlet control pressure compensator and the proportional travel spool, then the quantity of hydraulic medium flowing in upstream of the spool is reduced, without any bypass control for the return, which is disadvantageous for other parallel consumers. If the quantity reduction device attacks the inlet control pressure compensator, then the quantity supplied to the proportional directional control slide is correspondingly withdrawn in the inlet control pressure compensator.
  • the slide piston is either reset to a lower speed setting or prevented from reaching a setting for an impermissibly high speed.
  • a meaningful signal can be used to control the pressure reducing device, so that the quantity reducing device is at a critical level Load condition intervenes reliably even if there is no critical load condition on the hydraulic motor itself.
  • the control device is particularly useful for mobile cranes, but can also be used for other lifting equipment such as forklifts or lift trucks, tail lifts, concrete pumping devices or even rail-bound and stationary cranes. In principle, modified accordingly, it can also be used to reduce the speed of hoists with load hooks and / or trolleys, even when moving with an electric motor.
  • the hydraulic consumers can be moved at the maximum speed as long as there is no critical load in the hoist. The speed is only reduced when the critical load condition is reached. Then a large load can be moved up to the long range with a lower movement speed. This leads to an increased gripping range and a higher permissible load of the hoist, with the load being moved at a reduced speed at high load in the gripping range gained.
  • the orifice when the orifice is switched on, the pressure difference across the slide piston and thus the amount flowing to the hydraulic consumer are reduced.
  • the aperture can be switched on in at least one step or continuously.
  • the load pressure in the control line or the signal from another signal transmitter that represents a critical load state of the lifting device can serve as a signal for switching on the diaphragm.
  • a 2/2-way switching or control valve is inexpensive and reliable and can also be retrofitted.
  • the prestressing of the control spring of the inlet control pressure compensator is withdrawn to reduce the supply quantity.
  • the inlet control pressure compensator reduces the amount of hydraulic medium flowing into the spool. You can work with a pressure signal in the control line or with an external signal to operate the servo actuator.
  • the secondary pressure relief valve responds as soon as the control pressure in the control line generates a pressure signal that represents the critical load condition.
  • the secondary pressure relief valve allows hydraulic pressure medium to flow off to the return, whereby the amount of hydraulic medium allocated by the inlet control pressure compensator for the proportional directional control slide is correspondingly reduced.
  • the orifice and / or the characteristic curve of the pressure relief valve which is set even steeper by the orifice as desired, ensures that the supply control pressure compensator increases the quantity reduction as the quantity increases.
  • the quantity reduction is controlled only in one direction of movement of the hydraulic consumer.
  • pressure-independent leakage via the two-way controller is used in a particularly advantageous manner to reduce the amount.
  • the quantity reduction can be controlled in only one direction of movement or in both directions of movement of the hydraulic consumer.
  • This embodiment can also be implemented retrospectively in the case of conventional proportional directional control slide valve concepts.
  • the pressure-independent quantity reduction can be modulated with a control valve.
  • the embodiment according to claim 8 is advantageous.
  • the increased switching hysteresis or the hydraulic self-holding compensates for brief interferences. It is possible to use a time relay so that, for example, the quantity can only be reduced after e.g. 0.2 seconds, but the quantity reduction is only canceled when the signal is longer than e.g. 0.7 seconds no longer occurs.
  • the embodiment according to claim 9 is advantageous because usually several hydraulic consumers that can be operated simultaneously and simultaneously can be controlled in one hoist.
  • the speed reduction is only controlled if necessary with the proportional directional control valve, which is responsible for reaching the critical load condition or for which the greatest leakage occurs via the Two-way controller occurs.
  • the hydraulic self-retention of the switching valve or the adjustable switching hysteresis of the switching valve prevent the quantity reduction from swinging in and out.
  • the slide piston is reset by the return servo drive from a setting position for a higher speed to a setting position for a reduced speed when a critical load condition occurs.
  • the reset device either resets the spool from a setting position for a higher speed to a setting position for a low speed or limits the spool stroke.
  • the signal for controlling the quantity reduction is derived hydraulically or electrically from the lifting or articulating cylinder or from a working line of the lifting or articulating cylinder, at a point at which a signal that is meaningful under all operating conditions can be tapped, the represents a critical load condition in the hoist.
  • the signal transmitter can be arranged at any point within the structure of the hoist at which a signal that is meaningful under all circumstances can be determined.
  • the signal transmission to the quantity reduction device is particularly simple in terms of construction.
  • a swivel boom 2 is arranged on a mast 1 in a joint 14, from which a pivotable telescopic boom 3 extends with an extension part 3a, on which a gripper 4 (or a Load harness, a lifting fork, or the like.
  • the swing arm 2 can be pivoted by means of a lifting cylinder 5.
  • An articulated cylinder 6 is inserted between the telescopic boom 3 and the swivel boom 2.
  • the extension part 3a can be extended and retracted with an extension cylinder 7.
  • the cylinders 5, 6, 7 and the gripper 4 are driven by a hydraulic control device (not shown in FIG. 1).
  • the signal generator 8 senses the pressure in the push-out space of the lifting cylinder 5.
  • the signal generator 9 senses the pressure in the push-out space of the articulated cylinder 6.
  • the signal generator 10 is a shuttle valve which transmits the higher pressure in the lifting cylinder 5 or in the articulated cylinder 6 as signal Y.
  • the signal Y can be a hydraulic pressure signal or be an electrical signal that is generated, for example via a pressure switch.
  • the signal generator 11 is arranged at the pivot pin 13 of the lifting cylinder 5 on the mast 1 and is designed as a strain gauge or pressure sensor or similar electronically scannable element.
  • the signal generator 12 is arranged at the joint 14 between the mast 1 and the swivel arm 2 and electronically scanned as a strain gauge or the like.
  • One or more signal generators are used to operate in the hydraulic control device V, e.g. 3 to control a quantity reduction device M.
  • V hydraulic control device
  • FIG. 3 different embodiments of quantity-reducing devices are shown in six units separated by dash-dotted lines. 4 and 5 illustrate further possible variations for quantity reducing devices M.
  • a proportional travel control slide valve S1 to S6 with an associated inlet control pressure compensator Z for load-independent speed control.
  • the hydraulic consumer controlled by the proportional travel control spool S1 to S6 e.g. cylinders 5, 6, 7 in Fig. 1 moves independently of the load at a speed which is based solely on the adjustment of the proportional travel control spool. This is achieved in that the inlet control pressure compensator Z keeps the pressure drop set on the proportional travel control valve constant regardless of the load.
  • Each proportional travel control valve S1 to S6 is connected via a branch pressure line 15a to a common pressure line 15, in which the inlet control pressure compensator Z is arranged.
  • a common return line 16 is connected via branch return lines 16a to all proportional directional control spools S1 to S6.
  • Two working lines 17, 18 each lead from the proportional travel control spools S1 to S6 to the hydraulic motor. In the case of a hydraulic motor which can only be acted upon in one direction and adjustable in the opposite direction under load, only one working line 17 or 18 would be provided.
  • the proportional travel control slides S1 to S6 shown in FIG. 3 have manual adjustment devices 19, with which a slide piston 21 can be adjusted from a zero position against a return spring device 20 into two control positions a and b.
  • a control line 22 carrying the respective load pressure is connected to the control side of the inlet control pressure compensator Z.
  • the control line 22 is connected via an orifice 23 to bleed lines 24a, 24b which can be connected to the working lines 17, 18 via the slide piston 21.
  • a control line 25 connects the bleed lines 24a, 24b via a shuttle valve 26 to a common main control line 27, which leads to a control device of a constant pump or a control pump (not shown) for adjusting the pressure in the pressure line 15.
  • a common return control line 28 is connected to a tank.
  • a further control line 29 is subjected to a constant control pressure during operation of the control device, for example 25 bar.
  • a regulating member 30 is continuously adjustable between a through position and a shut-off position.
  • the control element 30 In the direction of the through position, the control element 30 is acted upon by the pressure in the control line 22 and by a control spring 31.
  • the control element 30 In the opposite direction, the control element 30 via an auxiliary control line 32 with an orifice from the pressure in the pressure line 15a downstream of the inlet control pressure compensator Z.
  • the quantity reducing device M has for the proportional directional control valve S1, e.g. of the lifting cylinder 5 of FIG. 1, a control or switching valve 33 with a fixed or variable orifice 34, which can be activated when the signal Y occurs in the pressure line 15a.
  • the control or switching valve 33 can be actuated by a magnet 35, to which the signal Y is supplied in electrical form.
  • the aperture 34 is not effective during normal operation.
  • the speed is determined by the setting position of the slide piston 21.
  • the pressure difference across the spool 21 is kept constant by the inlet control pressure compensator.
  • signal Y occurs, the aperture 34 is switched on. This means a reduction in volume and thus a reduction in speed for the hydraulic consumer.
  • the curve of FIG. 2 shows how (solid curve) the quantity Q increases over the stroke of the slide piston 21 without the orifice plate 34 being switched on.
  • the dashed curve 20% means that only 20% of the original amount will flow in each point of the stroke of the slide piston 21 after the orifice 34 has been switched on. If, as indicated in FIG.
  • a control valve or a variable orifice 34 is used, then the orifice 34 can be switched on continuously and one for each Set the quantity curve adapted to the requirements, for example as indicated by the dot-dash line in FIG. 2 at "var".
  • the quantity reduction device M has a servo actuator 36 for the control spring 31 of the inlet control pressure compensator Z in order to reduce the preload of the control spring in order to reduce the quantity.
  • a spring-loaded piston displaceable against a return spring is controlled with a switching valve 37 which is connected to the control line 28 via an auxiliary control line 38 and to the pressure line 15a via a further auxiliary control line 39. If the switching valve has a magnet 35, this is excited via the signal Y in order to remove the bias of the control spring 31. This can also be done continuously in one step. By reducing the spring preload, the control pressure difference becomes smaller and the quantity reduction in both working lines 17, 18 is the same in percentage terms.
  • Another auxiliary control line 40 connects the pressure side of the spring-loaded piston to the outlet of the switching valve 37.
  • the quantity reducing device M is equipped with a secondary pressure limiting valve 43, which is arranged in an auxiliary control line 42 connected to the control line 22 to the return line 16a and is set to a pressure value in the control line 22 which represents a critical load state, for example in the hydraulic consumer .
  • An orifice 44 is provided upstream of the secondary pressure relief valve 43.
  • the secondary pressure relief valve 43 has - with or without an orifice 44 - a pressure characteristic curve that increases with an increasing flow rate, and thus from response with increasing load pressure an increasing amount flows through the valve 43.
  • the quantity reducing device M acts in both directions of movement of the hydraulic consumer.
  • the quantity reduction device M is designed analogously to that of the third proportional travel control spool S3 and is equipped with a secondary pressure valve 43 and an upstream orifice 44 in the auxiliary control line 42 '.
  • This quantity reduction device M is only effective in one direction of movement of the hydraulic motor, namely in the control position a of the proportional travel control spool S4.
  • the auxiliary control line 42 ' is guided through a passage 45 in the slide piston 21, which is only open in the control position a. This passage is blocked in the neutral position and in the control position b.
  • the quantity reduction device M works with pressure-independent leakage and only in one direction of movement.
  • the auxiliary control line 42 which is led through the passage 45 in the spool 21 to a tank T, contains a two-way controller 46 to which a switching or control valve 47 is assigned, e.g. downstream, is.
  • a switching or control valve 47 is assigned, e.g. downstream, is.
  • the slide piston 21, which is manually adjustable by means of the adjusting device 19 is a reset servo drive 48 is provided which engages via a valve 49 controllable with the signal Y.
  • the valve 49 is connected to a tank control line 51 and, via a line 50, the control line 29 (which carries a constant pressure).
  • the reset servo drive is activated and the spool 21 is either pushed back from the previously selected setting or is prevented from any further adjustment at all. If the quantity reduction device is to work in both directions of movement, then two counter-acting return servo drives 48 are required.
  • the spool 21 - as is often the case - is hydraulically or electro-hydraulically piloted (indicated at 61), e.g. Via an electromagnetic (magnet 54a) adjustable pressure reducing valve 54 in a control line 52, a further pressure reducing valve 56 can then be inserted into the control line 52, which is activated by the signal Y and reduces the pressure for adjusting the slide piston 21.
  • the further pressure reducing valve 55 can be controlled either hydraulically or electromagnetically. In both variants it is ensured that the speed of the hydraulic motor is reduced from the occurrence of a signal Y or that the low speed is not exceeded.
  • the fourth proportional directional control spool S5 corresponds to the proportional travel control spool S5 of FIG. 3, with the difference that an electro-hydraulic pilot control 61 is also provided, which is connected to the control line 29 and the control line 28 (to the tank).
  • Any quantity reduction device M has in the auxiliary control line 42 to a common collective control line 57 a two-way controller 46 with a check valve 58, which is expediently spring-loaded and opens in the flow direction to the collective control line 57.
  • the quantity is reduced in both directions of movement when the quantity reduction device responds.
  • the switching valve 59 is a 2/2-way switching valve or a magnetically lockable check valve 62.
  • the switching valve 59 is put into the open position. In the open position, a pressure-independent leak occurs via the two-way controller 46 of the proportional travel control spool S5, S7 or S8, which contributes to the critical load state, which leads to a reduction in the quantity because the respective inlet control pressure compensator Z now only allocates a reduced quantity.
  • the switching valve 59 is designed with an increased switching hysteresis so that pressure or load fluctuations occurring during the speed reduction or an unwanted change in the signal Y lead to the switching valve 59 being reset immediately.
  • a time relay can be used which holds the signal for a pre-settable time period and does not cancel the quantity reduction until the signal change remains beyond the set time period.
  • auxiliary control line 42 leads to the control line 57.
  • a two-way controller 46 with an associated check valve 58 is provided in each auxiliary control line 42.
  • the two-way controller 46 enables pressure-independent leakage as soon as the switching valve 59 switches to passage when a signal Y occurs in the control line 64.
  • the switching valve 59 can be a so-called snap holder or a valve 63 with hydraulic self-holding, which, for example, holds its respective position, for example when the pressure signal Y disappears, for a predetermined period of time.
  • the check valves 58 prevent the pressure prevailing in the collective control line 57 from acting back into a control line 22 with a lower control pressure.
  • control pressure in the control line 64 switches the switching valve 59 into the through position, then only the reduced amount is fed to the lifting cylinder 5, so that it moves at a reduced speed.
  • the proportional directional control spool becomes S7 adjusted to move the articulated cylinder 6, then the amount fed to the articulated cylinder 6 is reduced due to the pressure-independent leakage via the two-way controller 46. If both proportional travel control spools S5, S7 are actuated, then only a slight reduced movement speed is permitted for both cylinders 5, 6 or only for that of the two cylinders which is responsible for the critical load condition.
  • the signal Y controlling the respective quantity reducing device M in the control devices V according to FIGS. 4 and 5 can also come from any of the signal transmitters indicated in FIG. 1 or also from another external signal transmitter not shown but meaningfully representing a critical load condition .
  • the components of the quantity reducing devices M used in each case can either be integrated in the proportional directional control slide valve or can be provided on its housing or in the connection block which is usually provided.
  • the proportional directional control spool can therefore also be retrofitted with regard to the speed reduction function. Basic modifications of the proportional directional spool are not necessary for this.

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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)
  • Valve Device For Special Equipments (AREA)
  • Jib Cranes (AREA)

Claims (13)

  1. Dispositif de commande hydraulique (V) pour au moins un récepteur hydraulique (5, 6) dans un engin de levage (K), en particulier dans une grue mobile, comportant un distributeur proportionnel (S1 à S8) qui, pour la commande de la vitesse jusqu'à une valeur maximale déterminée et pour la commande de direction du récepteur hydraulique (5, 6), est relié d'une part à une conduite sous pression (15, 15a) et une conduite de retour (16, 16a) et d'autre part à deux conduites de travail (17, 18) allant au récepteur hydraulique, et présente un tiroir cylindrique (21) manoeuvrable par un dispositif de manoeuvre manuel ou piloté, et un compensateur de pression-régulateur d'arrivée (Z) monté sur la conduite sous pression (15a) en amont du distributeur proportionnel (S1 à S8) et chargé, dans le sens d'ouverture, en fonction de la pression de charge depuis une conduite de commande (22) et par un ressort régulateur (31) et, dans le sens de fermeture, depuis la conduite sous pression (15a), le réglage du tiroir cylindrique (21) permettant de présélectionner, indépendamment de la charge, la vitesse de mouvement du récepteur hydraulique (5, 6), caractérisé par le fait que dans le dispositif de commande (V) est prévu un dispositif réducteur de débit (M) séparé du tiroir cylindrique (21), que ce dispositif réducteur de débit (M) peut être, par un signal (Y) représentant un état de charge de l'engin de levage (K) critique d'après la vitesse présélectionnée, mis en intervention de façon à limiter le débit de fluide hydraulique allant au récepteur hydraulique (5, 6) et ainsi exclusivement réduire la vitesse présélectionnée, et que le dispositif réducteur de débit (M), à l'apparition du signal (Y), intervient entre le compensateur de pression-régulateur d'arrivée (Z) et le distributeur proportionnel (S1) ou sur le compensateur de pression-régulateur d'arrivée (Z) du distributeur proportionnel (S2, S3, S4, S5, S7, S8) ou sur le tiroir cylindrique (21) du distributeur proportionnel (S6).
  2. Dispositif de commande hydraulique selon la revendication 1, caractérisé par le fait que le dispositif réducteur de débit (M) présente sur la conduite sous pression (15a) en aval du compensateur de pression-régulateur d'arrivée (Z) un diaphragme (34) pouvant être mis en service, de préférence dans un distributeur 2/2 de commutation ou dans un distributeur 2/2 de réglage (33), et que la mise en service de ce diaphragme peut être commandée de préférence en au moins un échelon ou de manière progressive au moyen du signal (Y) d'un générateur de signaux (8, 9, 10, 11, 12) ou dans la conduite de commande (22).
  3. Dispositif de commande hydraulique selon la revendication 1, caractérisé par le fait que le dispositif réducteur de débit (M) présente un servo-actionneur (36) qui modifie la contrainte initiale du ressort régulateur (31) du compensateur de pression-régulateur d'arrivée (Z) et peut être actionné au moyen du signal (Y), de préférence en au moins un échelon ou de manière progressive.
  4. Dispositif de commande hydraulique selon la revendication 3, caractérisé par le fait que le servo-actionneur (36) présente un piston de tension de ressort, manoeuvrable hydrauliquement contre l'action d'un ressort de rappel, et dont le côté actif peut être relié au choix par un distributeur 3/2 de commutation (37) à la conduite sous pression (15a) ou à la conduite de retour (16), et que le distributeur 3/2 de commutation (37) est à commande électromagnétique ou hydraulique.
  5. Dispositif de commande hydraulique selon la revendication 1, caractérisé par le fait que le dispositif réducteur de débit (M) présente un limiteur de pression secondaire (43) monté sur la conduite de commande (22), relié à la conduite de retour (43) et ouvert au moyen du signal (Y) dans la conduite à pression de commande (22), qu'un diaphragme (44) est prévu dans la conduite de commande (22) entre le limiteur de pression secondaire (43) et le compensateur de pression-régulateur d'arrivée (Z), et/ou que le limiteur de pression secondaire (43) a une caractéristique de pression qui monte lorsque le débit augmente.
  6. Dispositif de commande hydraulique selon la revendication 5, caractérisé par le fait que le limiteur de pression secondaire (43) est monté avec le diaphragme (44) dans au moins une conduite de commande auxiliaire (42, 42') branchée sur la conduite de commande (22) du compensateur de pression-régulateur d'arrivée (Z), et que la conduite de commande auxiliaire (42') passe par le distributeur proportionnel (S4) et ne peut y être rendue passante que dans une seule position de distribution (a) du tiroir cylindrique (21).
  7. Dispositif de commande hydraulique selon la revendication 1, caractérisé par le fait que le dispositif réducteur de débit (M) présente un régulateur de débit série (46) menant à la conduite de retour (16) auquel la conduite de commande (22) peut être reliée soit directement par une conduite de commande auxiliaire (42), soit par un passage (45) du tiroir (21) ouvert dans une seule position de distribution du distributeur proportionnel (S5, S6, S7, S8), et que près du régulateur de débit série (46) est prévu un appareil de commutation ou de réglage (47, 59) qui peut être commandé par le signal (Y) d'un générateur de signaux (64) ou dans la conduite de commande (22).
  8. Dispositif de commande hydraulique selon la revendication 7, caractérisé par le fait que l'appareil de commutation (47, 59, 63) comporte une hystérésis de commutation renforcée ou un maintien hydraulique.
  9. Dispositif de commande hydraulique selon au moins l'une des revendications 1 à 8, caractérisé par le fait qu'il y est prévu plusieurs distributeurs proportionnels (S6 à S8) montés en parallèle sur la conduite sous pression (15) et la conduite de retour (16), et pourvus chacun d'un compensateur de pression-régulateur d'arrivée (Z) et d'une conduite de commande auxiliaire (42) branchée sur la conduite de commande (22) et pourvue d'un régulateur série (46) et d'un clapet de non-retour (58) placé en amont ou en aval de celui-ci et s'ouvrant vers le retour (T), que le régulateur série (46) est monté sur une conduite collectrice de retour commune (57) allant à un réservoir (T), que cette conduite collectrice de retour (57) contient avant le réservoir (T) un distributeur 4/2 de commutation (63) ou une électrovanne de commutation (62), et que cette vanne (63 ou 62) peut être commandée au moyen du signal (Y).
  10. Dispositif de commande hydraulique selon la revendication 1, caractérisé par le fait que le dispositif réducteur de débit (M) présente pour le tiroir cylindrique (21), manoeuvrable manuellement, à partir d'une position de repos, contre l'action d'un ressort de rappel, au moins un servo-actionneur de rappel partiel (48) à commande hydraulique ou électrique.
  11. Dispositif de commande hydraulique selon la revendication 1, caractérisé par le fait que le dispositif réducteur de débit (M) présente pour le tiroir cylindrique (21), manoeuvrable par voie hydraulique ou électrohydraulique, à partir d'une position de repos, contre l'action d'un ressort de rappel, au moins un dispositif de rappel électrique ou électrohydraulique (55) qui, à l'apparition du signal (Y), rappelle le tiroir cylindrique (21) en direction de sa position de repos ou réduit la pression de manoeuvre du tiroir cylindrique (21).
  12. Dispositif de commande hydraulique selon au moins une des revendications 1 à 11, caractérisé par le fait que le signal (Y) peut être produit au moyen d'un générateur de signaux (8, 9, 10, 11, 12) qui est un capteur de pression hydraulique ou électrique dans un vérin de levage ou de pliage (5, 6) ou dans une conduite de travail (18) du vérin de levage (5) ou du vérin de pliage (6) de l'engin de levage constitué d'une grue mobile (K).
  13. Dispositif de commande hydraulique selon la revendication 12, caractérisé par le fait que le générateur de signaux (11, 12) est une jauge extensométrique à lecture électronique ou une capsule manométrique placée dans une articulation (14) significative en ce qui concerne un état de charge critique de l'engin de levage ou à un point d'articulation (13) à l'intérieur de l'ossature de l'engin de levage, par exemple sur l'axe d'articulation du vérin de levage ou de pliage (5, 6).
EP93120202A 1992-12-23 1993-12-15 Dispositif de commande hydraulique Expired - Lifetime EP0603722B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4243973 1992-12-23
DE4243973A DE4243973C1 (de) 1992-12-23 1992-12-23 Hydraulische Steuervorrichtung

Publications (2)

Publication Number Publication Date
EP0603722A1 EP0603722A1 (fr) 1994-06-29
EP0603722B1 true EP0603722B1 (fr) 1997-04-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP93120202A Expired - Lifetime EP0603722B1 (fr) 1992-12-23 1993-12-15 Dispositif de commande hydraulique

Country Status (4)

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EP (1) EP0603722B1 (fr)
AT (1) ATE152213T1 (fr)
DE (2) DE4243973C1 (fr)
DK (1) DK0603722T3 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29515829U1 (de) * 1995-10-05 1995-11-30 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulische Steuervorrichtung und Zweiwege-Regelventil
DE29611526U1 (de) * 1996-07-02 1996-09-05 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulische Steuervorrichtung
DE29611525U1 (de) 1996-07-02 1996-09-05 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulische Steuervorrichtung
KR100559291B1 (ko) * 2003-06-25 2006-03-15 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 중장비 옵션장치용 유압회로
KR100527378B1 (ko) * 2003-06-25 2005-11-09 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 붐합류용 스플을 이용한 중장비 옵션장치용 유압회로
DE102006060334B4 (de) * 2006-12-20 2011-08-25 Sauer-Danfoss Aps Hydraulische Ventilanordnung
DE502008002003D1 (de) * 2008-08-20 2011-01-20 Hawe Hydraulik Se Hydrauliksteuerung für einen Hydromotor
CN109306976B (zh) * 2018-11-05 2023-05-23 无锡市钻通工程机械有限公司 一种负载敏感控制系统

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE346762C (sv) * 1970-11-04 1979-05-14 Hiab Foco Ab Sperr- och sekerhetsanordning vid hydrauliskt drivna kranar av vippkrantyp
DE2513399A1 (de) * 1975-03-26 1976-10-07 Toussaint & Hess Gmbh Kran, insbesondere hydraulischer ladekran
DE3503374A1 (de) * 1985-02-01 1986-08-07 Robert Bosch Gmbh, 7000 Stuttgart Hydraulische ueberlastungsschutzvorrichtung fuer ein hebezeug
DE3644737C2 (de) * 1985-09-13 1995-11-23 Rexroth Mannesmann Gmbh Steueranordnung für mindestens zwei von mindestens einer Pumpe gespeiste hydraulische Verbraucher
ES2004356A6 (es) * 1986-12-26 1989-01-01 Hiac Valman S A Distribuidor para cilindros hidraulicos
DE3703576A1 (de) * 1987-02-06 1988-08-18 Rexroth Mannesmann Gmbh Steueranordnung fuer mindestens zwei von mindestens einer pumpe gespeiste hydraulische verbraucher
DE3710699C1 (de) * 1987-03-31 1988-08-18 Heilmeier & Weinlein Hydraulische Steuervorrichtung fuer eine Verbrauchergruppe
DE8800747U1 (de) * 1988-01-22 1988-03-10 Danfoss A/S, Nordborg Steuervorrichtung für einen hydraulischen Motor
SE8803181D0 (sv) * 1988-09-09 1988-09-09 Atlas Copco Ab Hydraulic driving system with a priority function for hydraulic motors
DE4021347A1 (de) * 1990-07-05 1992-01-16 Heilmeier & Weinlein Hydraulische steuervorrichtung
DE9111569U1 (de) * 1991-09-17 1991-11-14 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Steuervorrichtung für wenigstens einen Hydromotor

Also Published As

Publication number Publication date
DK0603722T3 (da) 1997-09-08
DE4243973C1 (de) 1994-07-07
EP0603722A1 (fr) 1994-06-29
DE59306264D1 (de) 1997-05-28
ATE152213T1 (de) 1997-05-15

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