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EP0546300B1 - Dispositif de commande électrohydraulique - Google Patents

Dispositif de commande électrohydraulique Download PDF

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Publication number
EP0546300B1
EP0546300B1 EP92118374A EP92118374A EP0546300B1 EP 0546300 B1 EP0546300 B1 EP 0546300B1 EP 92118374 A EP92118374 A EP 92118374A EP 92118374 A EP92118374 A EP 92118374A EP 0546300 B1 EP0546300 B1 EP 0546300B1
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EP
European Patent Office
Prior art keywords
pressure
valve
proportional
control device
motor
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
EP92118374A
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German (de)
English (en)
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EP0546300A1 (fr
Inventor
Hartmut Dipl.-Ing. Sandau (Fh)
Uwe Dipl.-Ing. Altmann
Horst Dr. Dr.-Ing. Hesse
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Publication of EP0546300A1 publication Critical patent/EP0546300A1/fr
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    • 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

Definitions

  • the invention relates to an electrohydraulic control device for load-compensated control of a hydraulic motor according to the type specified in the preamble of claim 1.
  • Such an electrohydraulic control device for load-compensated control of a hydraulic motor is already known from DE-OS 25 23 600, in which the pressure difference at the inlet and outlet of the proportional valve is measured and the position of the control slide is adjusted with the aid of a control circuit so that the influence the pressure difference dependent on changes in load is compensated so that the volume flow is independent of the applied pressure difference. This is achieved by squaring the pressure difference in the control circuit and dividing the setpoint for the spool stroke or volume flow by the squared value. This output signal is fed to a known position control loop as a setpoint for the valve lift.
  • This control device works with a complex 4-way proportional valve, that is less suitable for mobile applications.
  • the directional control valve requires a position sensor with position control loop that picks up the slide stroke in order to carry out the electronic load compensation.
  • control electronics for an electrically adjustable actuator in which the characteristic field of the actuator is written into a table memory in order to achieve a linear control behavior and thus a corrected control signal for the actuator is obtained from a setpoint in a microprocessor .
  • Characteristics can not only be linearized but also changed arbitrarily, so that the flow load function of a valve can also be taken into account at different pressures.
  • the construction of special electrohydraulic control devices is not taught here.
  • each motor connection is controlled via an identical proportional throttle valve.
  • Each proportional throttle valve is designed as a 3-way valve in slide valve design, is electro-hydraulically pilot-controlled and is located in a position control loop, so that the volume flows to and from each motor connection can be controlled individually via an electrical control unit, the signals from electro-hydraulic pressure sensors at each motor connection also being able to be supplied to the control unit .
  • This control device several additional functions such as differential switching, fail-safe function, force limitation or avoidance of hollow suction are to be fulfilled in a locking cylinder of an injection molding machine. This control device is not intended for load pressure-compensated control of a single-acting motor in mobile applications.
  • the electrohydraulic control device for load-compensated control of a hydraulic motor with the characterizing features of claim 1 has the advantage that it can be realized with existing components in a relatively simple and inexpensive construction and allows electronic load-compensated control of the hydraulic motor in both directions, i.e. with Raising and lowering.
  • the proportional throttle valve as a seat valve, the leakage can be kept low.
  • sensitive control can be achieved when lifting and lowering.
  • the control device is relatively compact and lightweight and is therefore particularly suitable for use in mobile applications.
  • control device is equipped with a double-tight proportional throttle valve, so that an electronically load-compensated lifting and lowering is possible with a single proportional throttle valve of the seat valve type.
  • control device is designed in such a way that the proportional throttle valve is connected in the diagonal of a hydraulic rectifier circuit designed as a full bridge. In this way, electronic load compensation for the lifting and lowering functions can be achieved with only one proportional throttle valve, and the effort in the control electronics can also be kept relatively low, since the characteristic field of the proportional throttle valve only has to be saved for one direction of flow.
  • control device results in an embodiment according to claims 14, 15, wherein all the necessary components can be sensibly arranged in a confined space and linked together.
  • claims 16 to 18 there are particularly advantageous applications of the control device according to the invention, it being particularly expedient if it is used in an electric stacker to control the load hydraulics.
  • FIG. 1 shows a first electrohydraulic control device for load-compensated control of a hydraulic motor in a simplified representation
  • FIG. 2 shows a longitudinal section through part of the first control device according to FIG. 1 in a more constructive embodiment
  • FIG. 3 shows a diagram with the flow characteristics of the proportional throttle valve according to FIG 1 in a simplified representation
  • FIGS. 4, 5 and 6 each show a second, third or fourth electrohydraulic control device in a simplified representation.
  • FIG. 1 shows an electrohydraulic control device 10 for load-compensated control of a hydraulic motor 11, which is designed here as a single-acting working cylinder, as is used in hoists for lifting and lowering loads, especially in forklifts.
  • the control device 10 has an inlet line 12 which leads from a constant pump 13 to the hydraulic motor 11.
  • the hydraulic motor 11 is connected via a drain line 14 to a tank 15 from which the constant pump 13 draws its pressure medium.
  • the load pressure prevailing in the hydraulic motor 11 is tapped by a first electrohydraulic pressure transducer 16, which gives an electrical output signal proportional to the pressure to control electronics 17.
  • a pressure compensator 18 is connected into the inlet line 12, the inlet connection 19 of which is directly connected to the pump 13. Downstream of the pressure compensator 18, a first check valve 21 is connected into the feed line 12, which prevents a lowering function of the engine 11, e.g. if the volume flow of the pump 13 fails, a pressure-controlled measuring orifice 22 is also connected downstream of the first check valve 21 and can be combined in an expedient manner with the first check valve 21.
  • the flow orifice 22 is designed in such a way that it has a linear flow characteristic, i.e. their flow rate over the pressure drop occurring forms a straight line in the corresponding diagram.
  • the construction of this orifice plate 22 in connection with the first check valve 21 will be discussed in more detail in connection with FIG. 2.
  • the pressure in the inlet line 12 between the pressure compensator 18 and the first check valve 21 is tapped by a second electrohydraulic pressure sensor 23, which also transmits its pressure-dependent electrical signal to the electronics 17.
  • the pressure compensator 18 has a 3-way function and for this purpose has, in addition to a motor connection 24, a continuation connection 25 which is secured by a second check valve 26.
  • the pressure compensator 18 has a control element 27 which can be loaded by the force of a spring 28 and by the pressure in a first control connection 29 in the direction of a basic position 31, in which it blocks the continuation connection 25 and the connection from the inlet connection 19 to the motor connection 24 controls.
  • the control member 27 is loaded by the pressure in a second control connection 32 and thus by the pressure in the inlet connection 19, as a result of which it can be deflected into a working position 33 in which the motor connection 24 is blocked and the inlet connection 19 is connected to the further connection 25 Has.
  • control member 27 can assume intermediate transition positions corresponding to the throttling function of the pressure compensator 18.
  • the second check valve 26 is connected downstream of the flow connection 25; it biases the pressure with the help of its spring to such an extent that the control element 27 of the pressure compensator is always moved fully to the right against the force of the spring 29 and the line to port A is closed.
  • a proportional pressure valve 34 is provided, which controls the pressure in the first control connection 29 and is supplied with pressure medium from the supply line 12 via a first throttle point 35.
  • a second throttle point 36 serves to relieve the hydraulic connection 24 when the continuation is loaded.
  • the proportional pressure valve 34 is controlled by the control electronics 17, for which purpose its proportional magnet is connected to an output of the control electronics 17.
  • a proportional throttle valve 37 which is designed as a pilot-operated 2-way valve and is designed to seal off the motor 11 in a seat valve type, is connected into the drain line 14. With the proportional valve 37, the volume flow in the drain line 14 can be controlled in proportion to an electrical input signal, for which purpose its proportional magnet is also connected to the control electronics 17.
  • the proportional valve 37 is a valve as is explained in more detail in the earlier patent applications P 40 32 078.2 and P 40 30 952.5.
  • This proportional throttle valve 37 has a characteristic field in which the individual flow characteristic curves differ from one another as a function of the pressure drop that occurs in each case. Such a characteristic field is shown in a simplified and schematic manner in the diagram according to FIG. 3, with a plurality of flow characteristic curves 38 being plotted for the volume flow Q as a function of the flow signal I for several pressures, so that the control behavior of the proportional throttle valve 37 can be recognized in principle.
  • the control electronics 17 can be designed as a microcomputer known per se, in which the functions of a controller, a computer and a table memory are integrated.
  • the control electronics 17 has a setpoint input 41, at which the various values for a specific function of the motor 11 can be entered.
  • the characteristic field for the pressure-dependent different flow characteristics 38 (in FIG. 3) of the proportional throttle valve 37 is stored in the table memory of the control electronics 17 in a manner known per se.
  • the control electronics 17 also contains suitable means in its controller, with which not only the proportional magnets of the proportional pressure valve 34 and the proportional throttle valve 37 can be controlled, but also via which an electric motor 42 driving the constant pump 13 can be controlled.
  • FIG. 2 shows in more detail, the pressure compensator 18, the check valve 21 with the pressure-controlled measuring orifice 22, the pilot-controlling proportional pressure valve 34, the proportional throttle valve 37 and the two pressure sensors 16, 23 are combined in an electrohydraulic control module 45.
  • the control module 45 has a cuboid housing 46 on which these components are arranged and interconnected.
  • the housing 46 has a longitudinal bore 49 extending between its two end faces 47, 48, which is offset several times and penetrated by chambers, in which the proportional throttle valve 37, the pressure compensator 18 and the proportional pressure valve 34 are arranged coaxially to one another.
  • the proportional throttle valve designed as a cartridge valve with a seat construction, is installed in the longitudinal bore 49 from the first end face 47, while the control element 27 of the pressure compensator 18, designed as a hollow slide valve, is installed in the longitudinal bore 49 from the second end face 48.
  • the longitudinal bore 49 is closed in the second end face 48 by the proportional pressure valve 34, which the Pressure compensator 18 piloted.
  • In the longitudinal bore 49 leads in the area between the proportional throttle valve 37 and the pressure compensator 18, a channel 51 which is connected to the inlet connection 19.
  • the inlet connection 19 lies in a narrow longitudinal side 52 of the cuboid housing 46, in which the flow connection 25 is also arranged.
  • a consumer connection 50 which can be connected to the motor connection and a tank connection 54 are formed in a second longitudinal side 53 of the housing 46 opposite the first narrow longitudinal side 52.
  • the consumer connection 50 and the continuation connection 25 lie essentially in a plane running perpendicular to the longitudinal bore 49.
  • the check valve 21 and the pressure-controlled measuring orifice 22 are formed in the housing 46 and have a common closing element 55.
  • the housing recess 56 receiving the closing member 55 is then designed in the form of the actual valve seat in such a way that the measuring orifice 22 reaches its linear flow characteristic in a manner known per se.
  • the first pressure sensor 16 tapping the load pressure is installed in the first end face 47 above a proportional magnet 57 of the proportional throttle valve 37.
  • the second pressure transducer 23 which picks up the pressure in the feed line 12 upstream of the measuring orifice 22, is installed in the second end face 48, so that it comes to rest above the proportional pressure valve 34. Both pressure transducers 16, 23 are thus essentially coaxial with one another and in an axis parallel to the longitudinal bore 49. With this configuration of the control module 45, essentially all electrohydraulic components can be arranged in a particularly compact and advantageous manner, with the integration of orifice plate 22 and the first Check valve 21 is extremely advantageous.
  • control device 10 The mode of operation of the control device 10 is explained as follows, reference being made to FIGS. 1 to 3.
  • the control electronics 17 can switch on the first pressure sensor 16 and thus use its electrical signals for any additional functions, for example for safety functions or for weighing a load which acts on the motor 11.
  • control electronics 17 can switch off the electric motor 42, a load acting on the motor 11 being held hydraulically by the first check valve 21 and the proportional throttle valve 37 designed as a seat valve second check valve intercepted.
  • the electric motor 42, the two pressure sensors 16, 23 and the proportional pressure valve 34 are switched on or activated.
  • the proportional throttle valve 37 is not energized and therefore shuts off the drain line 14 to the tank 15.
  • a value is specified at the setpoint input 41, the size of which is proportional to the size of the desired volume flow to the motor 11.
  • the control valve 17 excites the proportional pressure valve 34, which now blocks the connection to the tank and one in the first control connection 29 Throttles control pressure, which shifts the control member 27 into an intermediate position in which pressure medium flows to the engine 11 via the feed line 12.
  • This volume flow flows downstream of the pressure compensator 18 through the measuring orifice 22, the pressure upstream from the second pressure sensor 23 and the pressure downstream from the first pressure sensor 16 being measured and passed on to the control electronics 17.
  • the pressure drop effective via the orifice plate 22 is therefore determined, from which an associated volume flow can be determined from the linear flow characteristic of the orifice plate 22.
  • the magnitude of this volume flow is compared with the target value at the input 41 and from the resulting difference value in the control electronics 17 such a current value for actuating the proportional pressure valve 34 is determined that this control deviation becomes zero.
  • the measuring orifice 22 is, as can be seen in more detail from Figure 2, designed in the region of the housing recess 56 by a special profile of the bore so that there is a linear dependence of the volume flow Q on the pressure drop ⁇ p. In contrast to a parabolic flow characteristic of a fixed orifice, this straight-line flow characteristic of the measuring orifice 22 ensures that the volume flow can still be fine-tuned even with a very small value.
  • the volume flow when lifting the hydraulic motor 11 can thus be kept constant regardless of pressure changes at the constant pump 13 or in the continuation connection 25, so that an electronically load-compensated lifting function can be achieved.
  • the control electronics 17 For the lowering function of the hydraulic motor 11, only the first pressure sensor 16 and the proportional throttle valve 37 are switched on or activated by the control electronics 17. All other components are not controlled, at least as long as no additional hydraulic motors are operated.
  • the control electronics 17 is given a value proportional to the volume flow when lowering at the setpoint input 41.
  • the current signal generated by the control electronics 17 opens the proportional throttle valve 37, so that a volume flow flows out of the motor 11 via the drain line 14 to the tank 15.
  • the respective load pressure of the engine 11 is reported by the first pressure sensor 16 to the control electronics 17.
  • the proportional throttle valve 37 has different flow characteristics depending on the pressure. These flow characteristics 38 of the proportional throttle valve 37 are stored in the table memory of the control electronics 17.
  • control electronics 17 its computer takes the associated values of the flow characteristic from the table memory in accordance with the load pressure reported by the pressure sensor 16, determines the deviation of the volume flow from the predetermined setpoint and finally calculates a suitable current value for actuating the proportional throttle valve 37, so that the influence of the load pressure in Motor 11 is compensated.
  • the seat valve 37 With the seat valve 37, an electronically load-compensated lowering can thus be achieved, with a perfect fine control being possible.
  • the motor 11 can also be lowered even when the force acting on it from the outside is very low and the pressure drop available for the volume flow control is therefore low. If the control electronics 17 fails, an emergency manual control 58 arranged on the proportional throttle valve 37 can be actuated, so that the piston rod on the motor 11 can still be retracted.
  • FIG. 4 shows a second electrohydraulic control device 60 in a simplified representation, which differs from the first control device 10 according to FIG. 1 as follows, the same reference symbols being used for the same components.
  • the parallel actuation of additional hydraulic motors is dispensed with, so that a 3-way pressure compensator according to FIG. 1 is omitted and a simpler construction is possible.
  • a preload valve 61 is connected in the inlet line 12 connecting the constant pump 13 to the hydraulic motor 11 upstream of the first check valve 21 and the measuring orifice 22, which secures the pressure medium source 13.
  • the drain line 14 is connected downstream of the proportional throttle valve 37 and a third check valve 62 and downstream of the latter a proportional pressure valve 63.
  • the third check valve 62 secures the proportional throttle valve 37.
  • the proportional pressure valve 63 is designed here as a pilot-operated pressure valve which is normally open, that is, when the proportional magnet is not energized, the drain line 14 opens.
  • a cross connection 64 is created between the inlet line 12 and the outlet line 14, which is designed here as a simple node.
  • This cross-connection 64 connects the section of the feed line 12 between the preload valve 61 and the measuring throttle 22 to the section of the discharge line 14 between the third check valve 62 and the proportional pressure valve 63 , a separate, second pressure sensor can be omitted.
  • the function of the second pressure transducer according to FIG. 1 is taken over by the proportional pressure valve 63 in the second control device 60, from whose control signals the respective pressure in the discharge line 14 upstream of the proportional valve 63 can be determined.
  • the mode of operation of the second control device 60 essentially corresponds to the mode of operation of the first control device 10 according to FIG. 1, so that reference is made above all to the differences: With the second control device 60, the neutral circulation function is omitted, since there is no 3-way pressure compensator is available. In the function of holding the hydraulic motor 11, neither the proportional throttle valve 37 nor the proportional pressure valve 63 is actuated by the control electronics 17. The control electronics 17 has only switched on the first pressure sensor 16 in order to use its signals for additional functions.
  • the electronic load pressure-compensated control is achieved in principle in a manner comparable to that of the first control device 10 according to FIG. 1.
  • the electric motor 42 driven by the control electronics 17, generates a volume flow via the constant pump 13, which flows to the motor 11 via the preload valve 61 and the measuring orifice 22.
  • the effective pressure drop across the orifice 22 is determined by reporting the load pressure in the engine 11 from the first pressure sensor 16 to the control electronics 17, while the pressure upstream of the orifice 22 is determined indirectly from the control signal of the pilot-controlled pressure control valve 63.
  • the control electronics 17 can throttle the discharge via the discharge line 14 to the tank by a correspondingly large current signal with the aid of the proportional pressure valve 63 to such an extent that a suitable pressure value is generated upstream of the measuring orifice 22.
  • the effective pressure drop across the measuring throttle 22 can thus be regulated to a constant value regardless of the load in the motor 11, so that a volume flow proportional to the size of the setpoint signal at the input 41 can be controlled independently of the load pressure to the motor 11.
  • the function of lowering the hydraulic motor 11 in the second control device 60 is achieved in the same way as in the first control device according to FIG. 1, in that an electronic load-compensated lowering is achieved with the help of the proportional throttle valve 37 and the first pressure sensor 16 in cooperation with the electronic control device 17, in which the volume flow flows via the drain line 14 to the tank. Since the proportional pressure valve 63 is designed as a normally open valve, it does not need to be actuated by the control electronics 17 when lowering. The preload valve 61 prevents the volume flow from flowing to the pressure medium source 13 when lowering.
  • FIG. 5 shows a third electrohydraulic control device 70, which differs from the second control device 60 according to FIG. 4 as follows, the same reference symbols being used for the same components.
  • a proportional throttle valve 71 is used instead of the orifice plate 22 according to FIG. 4, which is designed as a double-tight seat valve and in which the function of the third check valve 62 is thus also integrated.
  • the drain line 14 branches off from the feed line 12 in the region between the preload valve 61 and the proportional throttle valve 71 and leads to the tank 15 via the normally open proportional pressure valve 63.
  • the mode of operation of the third control device 70 largely corresponds to that of the second control device according to FIG. 4, wherein when the hydraulic motor 11 is functioning, only the signals from the first pressure sensor 16 are used in the control electronics 17, while the proportional throttle valve 71 and the pressure control valve 63 are not activated.
  • the proportional throttle valve 71 can take over the function of the measuring throttle, via which the effective pressure drop is kept constant with the help of the proportional pressure valve 63, so that a load pressure-compensated lifting is possible.
  • the third control device 70 an electronically load-compensated lifting and lowering function can thus be achieved, a double-tight seat valve 71 ensuring a perfect seal of the lifted load on the consumer 11.
  • the third control device 70 advantageously manages with a single throttle valve 71.
  • FIG. 6 shows a fourth electrohydraulic control device 80, which differs from the first control device 10 according to FIG. 1 follows differs, the same reference numerals being used for the same components.
  • the fourth control device 80 manages the two functions of lifting and lowering with a single proportional throttle valve 37, which for this purpose lies in a hydraulic rectifier circuit 81, which consists of hydraulic full bridge 82 and four check valves 83 and a bridge diagonal 84 into which the proportional throttle valve 37 is switched.
  • the check valves 83 shown, the branches 85, 86 of the full bridge 82 form parts of the inlet line 12.
  • the other branches 87 and 88 form parts of the outlet line 14.
  • the first pressure sensor 16 determines the load pressure in the engine 11.
  • the second pressure transducer 23 determines the pressure downstream of the proportional throttle valve 37 when lifting as well as when lowering.
  • a proportional pressure valve 89 is connected downstream of a summing point 91 on the inlet side into the discharge line 14.
  • the proportional pressure valve 89 is designed here as a normally closed valve.
  • a continuation connection 92 branches off from the summation point 91.
  • the mode of operation of the fourth control device 80 is comparable to that of the first control device 10 according to FIG. 1, in that an electronic load-compensated control of the hydraulic motor 11 is possible when lifting and lowering, and in addition that additional hydraulic motors can be operated in parallel via the continuation connection 92. While in the first control device 10 according to FIG. 1, the electronic load compensation using the characteristic field of the flow characteristic curves of the proportional throttle valve 37 stored in the control electronics 17 is carried out only for the lowering function, in the fourth control device 80 this type of load compensation is also used for the lifting function .
  • control electronics 17 need not control a valve and only receives load-dependent signals from the first pressure sensor 16.
  • control electronics 17 In the lifting function, the control electronics 17, in addition to the two pressure transducers 16 and 23, activate the proportional throttle valve 37 located in the diagonal 84 of the bridge and work in the manner described, so that the volume flow flowing from the constant pump 13 to the motor 11 is electronically load compensated.
  • the proportional pressure valve 89 which is designed as a normally closed valve, is not actuated by the control electronics 17.
  • the proportional pressure valve 89 When lowering, the proportional pressure valve 89 is actuated or opened in addition to the components activated by the control electronics 17 during lifting, so that pressure medium can be relieved to the tank 15 via the drain line 14.
  • the constant pump 13 can be switched on or off as required.
  • a comparable function of neutral circulation can also be carried out with the fourth control device 80 if, with the constant pump 13 switched on and the normally closed proportional pressure valve 89, the volume flow conveyed is passed into the further connection 92 for actuating further hydraulic motors.
  • the proportional throttle valve 37 is not energized and, together with the check valves 83, hydraulically shuts off the motor 11.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (19)

  1. Installation de commande électrohydraulique pour la commande avec compensation de charge d'un moteur hydraulique (11) comprenant des moyens à vanne (37, 34 ; 37, 63 ; 71, 63 ; 37, 89) prévus entre une source de liquide sous pression (13) et un moteur (11), ces moyens étant commandés électriquement, précommandés et fonctionnant de façon proportionnelle, ainsi qu'un capteur de pression électrohydraulique (16) pour détecter la pression de charge dans le moteur (11) et une électronique de commande (17) pour former un signal de commande pour la vanne, caractérisée en ce que les moyens à vanne sont des vannes d'étranglement proportionnelles à deux voies (37 ; 71) de construction de type soupape à siège et une vanne proportionnelle (34 ; 63 ; 89), l'électronique de commande (17) enregistrant un champ de caractéristiques de la vanne d'étranglement proportionnelle (37 ; 71) avec ses caractéristiques de débit (38) variables en fonction de la pression, et à l'aide desquelles l'électronique de commande (17) forme un signal de commande pour la vanne d'étranglement proportionnelle (37 ; 71) assurant la compensation de charge en utilisant le signal de valeur de consigne introduit par l'entrée 41 et en ce que l'électronique de commande (17) coopère avec la vanne à pression proportionnelle (34 ; 63 ; 89) limitant la pression de la pompe.
  2. Installation de commande électrohydraulique selon la revendication 1, caractérisée en ce que l'électronique de commande (17) est alimentée par un second signal fourni par un élément (23 ; 63) en fonction de la pression pour déterminer une différence de pression efficace.
  3. Installation de commande électrohydraulique selon la revendication 1, caractérisée en ce que la vanne d'étranglement proportionnelle (37) est branchée sur la conduite de sortie (14) entre le moteur (11) et le réservoir (15), et une conduite d'alimentation (12) relie le moteur (11) et la source de liquide sous pression (13), cette conduite comportant une balance de pression (18) à commande préalable par la vanne de pression proportionnelle (34) et en aval de celle-ci un clapet anti-retour (21) protégeant le moteur (11) ainsi qu'un diaphragme de mesure (22) commandé en pression, et le composant indépendant de la pression fournissant le second signal est un second capteur de pression (23) qui détermine la chute de pression sur le diaphragme de mesure (22) avec le premier capteur de pression (16 (figure 1).
  4. Installation de commande électrohydraulique selon la revendication 3, caractérisée en ce que le diaphragme de mesure (22) a une caractéristique de débit essentiellement linéaire.
  5. Installation de commande électrohydraulique selon la revendication 3 ou 4, caractérisée en ce que la balance de pression (18) est une vanne à trois voies à branchement de poursuite de mouvement (25) et elle présente une position de base (31) centrée par un ressort (28) pour laquelle les communications entre le branchement d'alimentation (19) et le branchement de poursuite de mouvement (25) sont fermées et celui du moteur (24) est ouvert, et peut être déplacé par la pression d'alimentation, contre la force du ressort (28) et d'une pression de commande dans le branchement de commande (28) dans une position de travail (33) pour laquelle la communication avec le branchement de poursuite de mouvement (25) est ouverte et la communication avec le branchement du moteur (24) est fermée.
  6. Installation de commande électrohydraulique selon l'une des revendications 3 à 5, caractérisée en ce que le branchement hydraulique du second capteur de pression (23) est réalisé avec la conduite d'alimentation (12) entre la balance de pression (18) et le clapet anti-retour (21) et communique avec le réservoir (15) par l'intermédiaire d'un point d'étranglement (36).
  7. Installation de commande électrohydraulique selon la revendication 1 ou 2, caractérisée en ce que la vanne d'étranglement proportionnelle (37) est montée dans la conduite de sortie (14) entre le moteur (11) et le réservoir (15), et une conduite d'alimentation (12) est prévue entre le moteur (11) et la source de liquide sous pression (13) et comporte un clapet anti-retour (21) protégeant le moteur (11) ainsi qu'un diaphragme de mesure à commande de pression (22) et dans la conduite d'alimentation (12), en amont du clapet anti-retour (21), il est prévu une soupape à précontrainte (61) et dans la conduite de sortie (14), en aval de la vanne d'étranglement proportionnelle (37), il y a un troisième clapet anti-retour (63), protégeant la vanne d'étranglement et la vanne de pression proportionnelle (63) et un perçage transversal (64) part de la conduite d'alimentation (12) entre la soupape précontrainte (61) et le diaphragme de mesure (22), cette liaison allant de la conduite de sortie (14) dans sa zone comprise entre le troisième clapet anti-retour (62) et la soupape de pression proportionnelle (63) (figure 4).
  8. Installation de commande électrohydraulique selon la revendication 7, caractérisée en ce que le diaphragme de mesure (22) présente une caractéristique de débit pratiquement linéaire.
  9. Installation de commande électrohydraulique selon la revendication 7 ou 8, caractérisée en ce que la vanne de pression proportionnelle (63) est une vanne à commande préalable et son signal de commande est formé par le second signal pour déterminer la différence de pression efficace.
  10. Installation de commande électrohydraulique selon la revendication 1 ou 2, caractérisée en ce que la vanne d'étranglement proportionnelle à deux voies (71) est une soupape à siège à double étanchéité, prévue dans la conduite d'alimentation (12) entre le moteur (11) et la source de liquide sous pression (13), conduite dans laquelle entre la vanne d'étranglement proportionnelle (71) et la source de liquide sous pression (13), il y a une soupape de précontrainte (61) et de la conduite d'alimentation (12), entre la vanne d'étranglement proportionnelle (71) et la soupape de précontrainte (61) dérive la conduite de sortie (14) en allant au réservoir (15) à travers la vanne de pression proportionnelle (63) et en ce que les caractéristiques de débit de la vanne d'étranglement proportionnelle (71) notamment pour les deux sens de passage sont enregistrées dans l'électronique de commande (17) et servent à former les signaux de commande (figure 5).
  11. Installation de commande électrohydraulique selon la revendication 1 ou 2, caractérisée en ce qu'un montage-redresseur hydraulique (81) à pont entier (82) et clapets anti-retour (83) est branché dans la conduite d'alimentation (12) rejoignant la source de fluide sous pression (13) vers le moteur (11), et la vanne d'étranglement proportionnelle à deux voies (27) se situe dans la diagonale (84) du pont, la conduite de sortie (14) étant reliée à la conduite d'alimentation (12) en amont du circuit-redresseur (81) et arrivant au réservoir (15) à travers la vanne de pression proportionnelle (89) (figure 6).
  12. Installation de commande électrohydraulique selon la revendication 11, caractérisée en ce qu'une conduite de poursuite de mouvement (92) dérive du point de dérivation (91) de la conduite de sortie (14) pour d'autres moteurs hydrauliques.
  13. Installation de commande électrohydraulique selon la revendication 11 ou 12, caractérisée en ce qu'aux deux sommets de la diagonale (84) du pont, il est prévu chaque fois un capteur de pression (16, 23).
  14. Installation de commande électrohydraulique selon l'une ou plusieurs des revendications 3 à 6, caractérisée en ce que la vanne d'étranglement proportionnelle (37), la vanne de pression proportionnelle (34) et la balance de pression (18) en amont de celle-ci, le diaphragme de mesure (22) à commande de pression et les deux capteurs de pression (16, 23) sont prévus dans un boîtier commun (46) dans lequel se trouvent coaxialement la vanne d'étranglement proportionnelle (37), la vanne de pression proportionnelle (34) et la balance de pression (18) alors que le diaphragme de mesure (22) se situe dans un plan perpendiculaire à cette direction.
  15. Installation de commande électrohydraulique selon la revendication 14, caractérisée en ce que le boîtier (46) est de forme parallélépipédique et reçoit la balance de pression (18) dans un perçage longitudinal (49) passant entre les deux faces frontales (47, 48) alors qu'au niveau de la première face frontale (47) sont montés la vanne d'étranglement proportionnelle (37) dans le perçage longitudinal (49) et le premier capteur de pression (16) qui détecte la pression de charge dans le premier branchement d'utilisateur (50) alors qu'au niveau de l'autre face frontale (48) sont montés la vanne de pression proportionnelle (34) et le second capteur de pression (23) et en ce que sur l'un des petits côtés longitudinaux (52) du branchement d'alimentation (29) et du branchement de poursuite de mouvement (25) alors que sur les autres petits côtés longitudinaux (53) du boîtier (46) se trouvent le branchement d'utilisateur (50) ainsi que le branchement de réservoir (54).
  16. Installation de commande électrohydraulique selon l'une ou plusieurs des revendications 1 à 15, caractérisée en ce que le moteur (11) est un vérin à simple effet.
  17. Installation de commande électrohydraulique selon la revendication 15, caractérisée en ce que la source de liquide sous pression est une pompe électrique (13, 42) notamment une pompe constante commandée par l'électronique de commande (17).
  18. Installation de commande électrohydraulique selon l'une des revendications 1 à 17, caractérisée par son application à un moyen de levage notamment à un chariot-élévateur électrique.
  19. Installation de commande électrohydraulique selon l'une ou plusieurs des revendications 1 à 9 et 14 à 18, caractérisée en ce que le premier clapet anti-retour (21) et le diaphragme de mesure (22) ont une construction intégrée et un même organe de fermeture (55).
EP92118374A 1991-12-07 1992-10-28 Dispositif de commande électrohydraulique Expired - Lifetime EP0546300B1 (fr)

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DE4140409A DE4140409A1 (de) 1991-12-07 1991-12-07 Elektrohydraulische steuereinrichtung
DE4140409 1991-12-07

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EP0546300B1 true EP0546300B1 (fr) 1996-04-10

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CN112855252A (zh) * 2019-11-28 2021-05-28 太原理工大学 一种全自动矿井安全门

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DE4140409A1 (de) 1993-06-09
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