EP0279315B1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP0279315B1
EP0279315B1 EP88101810A EP88101810A EP0279315B1 EP 0279315 B1 EP0279315 B1 EP 0279315B1 EP 88101810 A EP88101810 A EP 88101810A EP 88101810 A EP88101810 A EP 88101810A EP 0279315 B1 EP0279315 B1 EP 0279315B1
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EP
European Patent Office
Prior art keywords
control
valve
piston
control device
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
EP88101810A
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German (de)
English (en)
Other versions
EP0279315A2 (fr
EP0279315A3 (en
Inventor
Martin Dipl.-Ing.(Eth) Heusser
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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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Application filed by Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Priority to AT88101810T priority Critical patent/ATE68243T1/de
Publication of EP0279315A2 publication Critical patent/EP0279315A2/fr
Publication of EP0279315A3 publication Critical patent/EP0279315A3/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source 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
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow 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
    • F15B2211/46—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
    • F15B2211/40—Flow control
    • F15B2211/465—Flow control with 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
    • F15B2211/40—Flow control
    • F15B2211/47—Flow control in one direction only
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8606—Control during or prevention of abnormal conditions the abnormal condition being a shock

Definitions

  • the invention relates to a hydraulic control device in the preamble of claim 1.
  • control piston which is held in the blocking position by the load pressure in the blocking position for holding the load pressure in the control chamber, requires an exact fit and a large sealing length as well as a large positive overlap in order to also keep the load pressure downstream of the measuring orifice without leakage.
  • the pressure compensator has a directional function in the zero position because the control chamber, in which the other piston end is located, is relieved of pressure by additional valve devices.
  • the invention has for its object to provide a hydraulic control device of the type mentioned, in which a switching jerk is reliably avoided with little technical effort.
  • the load pressure in the zero position of the control device is taken up on the one hand by the locking member and kept away from the pressure compensator and on the other hand by the poppet valve in the control chamber, which seals perfectly in the holding position of the control piston even with conventional fits and a short guide length of the control piston.
  • the control orifice no exaggerated positive overlap is necessary, if at all, because the load pressure is not there.
  • the result is a compact, simple construction of the pressure compensator with a suitably smooth-running control piston with a short control stroke.
  • the additional effort for the seat valve of the control chamber is negligible.
  • a conventional orifice plate construction can be used because the load pressure in the zero position is received by the seat valves in the drain line and in the control chamber and the control piston maintains its shut-off position without leakage.
  • valve seat valve between the control piston end and the valve seat.
  • the given design requirements of the pressure compensator are used to form the seat valve between the control piston end and the valve seat.
  • it means no significant effort to design the control piston end with the conical thickening and in the mouth area of the housing bore in the Control chamber to provide a valve seat.
  • the valve seat is formed by an insert, for example a hardened bushing with a tapered end that extends over the entire length of the control piston, and the conical thickening, if it is not formed in one piece with the control piston, is attached to the control piston. Pressure medium cannot leak from the control chamber to the housing bore in the zero position.
  • the embodiment of claim 5 is also important because the two-position switch valve ensures that the flow resistance of the poppet valve does not enter the control loop, i.e. that the pressure compensator with a small pressure difference can be designed in a sensitive and appealing manner, although the seat valve, which is expediently of a small construction, has a pressure difference which can be a multiple of the pressure difference of the pressure compensator.
  • the changeover valve leads the pressure medium from the control chamber in which the load pressure is maintained, bypassing the seat valve to the other control chamber as soon as it is switched over.
  • the other control line that bypasses the seat valve also serves this purpose. Without the changeover valve, for example, the control spring of the pressure compensator would have to be designed more strongly.
  • the embodiment according to claim 6 is also expedient because the seat valve automatically assumes its shut-off position under the action of the spring force when the control device is brought into the zero position.
  • a sensitive response and easy handling are achieved in the embodiment according to claim 7, wherein a modern small seat valve is inexpensive and manages with a small and inexpensive magnet.
  • the feature of claim 8 is also advantageous because the changeover valve automatically assumes its first passage position under the action of the spring force, in which the pressure-transmitting connection from the control chamber to the side of the seat valve facing away from the measuring orifice is open and the load pressure is kept away from the measuring orifice and directly is at the end of the control piston and holds the control piston in its stop position.
  • the idea of claim 10 is also advantageous because the coupling of the adjusting devices ensures that the shut-off element or seat valve and the changeover valve each change their positions simultaneously when the control device is switched over.
  • Is a changeover valve provided this is when using the pressure compensator for control in both directions together with the poppet valve in a position in which there is a pressure-transmitting connection from the side facing the poppet valve to the control chamber, so that the control piston at both piston ends of the pressures upstream and is acted upon downstream of the orifice plate and regulates the pressure drop set in each case on the orifice plate. If, on the other hand, a separate current regulator is provided for the control when the supply line is loaded, the pressure compensator remains in the shut-off position.
  • At least one further hydraulic motor is supplied with pressure medium from the supply line, the same measuring orifice and pressure compensator being used for the movement control of this further hydraulic motor as for the first hydraulic motor.
  • the non-controlled hydraulic motor is separated from the supply line by its seat valve.
  • the changeover valve nevertheless ensures that the control piston of the pressure compensator is acted upon at both piston ends by the pressures prevailing upstream and downstream of the measuring orifice and that the pressure difference set on the measuring orifice is independent of the load pressure or supply pressure fluctuations.
  • Additional loads can also be connected to the supply line, each of which can be controlled individually via the measuring orifice and the pressure compensator. Only the load pressure of the most heavily loaded hydraulic motor is transmitted to the control chamber, or it is ensured that those that have lower load pressures are shut off in the case of load pressure control lines for each hydraulic motor.
  • FIG. 1 shows a hydraulic control circuit with a hydraulic control device 1 for a hydraulic motor 2 which can be acted upon on one side against a load.
  • a hydraulic control device 1 for a hydraulic motor 2 which can be acted upon on one side against a load.
  • This is, for example, a lifting control device for the lifting piston of a forklift or a tail lift.
  • the hydraulic motor 2 is a cylinder 3, in which a piston 4 under a load 5, e.g. the weight of the lifting fork bracket of a forklift truck is slidable or hydraulically lockable.
  • a pressure source 6 e.g. a switchable hydraulic pump, supply line 7 connected via a check valve 8.
  • the supply line 7 crosses a drain line 32 from the cylinder 3 to a tank 37.
  • a measuring orifice 9 with an adjustable orifice member 10 is arranged, which is a shut-off element A which can be brought into a load-holding shut-off position.
  • An actuating actuator 11 is used for adjustment, in the present case an actuating magnet or proportional magnet.
  • a housing 13 of a pressure compensator 12 Downstream of the orifice 9, a housing 13 of a pressure compensator 12 is inserted into the drain line 32, which contains a control orifice 14, which regulates the pressure difference set on the orifice 9 and thus the speed of the piston 4 in a conventional manner.
  • An annular chamber 15 with a control edge 16 is provided in a housing bore 29.
  • a control piston 17, which is displaceably guided in the housing bore 29, has two piston parts 22 and 21 connected to one another via a piston rod 20 and a recess 19.
  • One side of the piston part 21 forms a control edge 18, which cooperates with the control edge 16 like an aperture when the control piston 17 performs its working cycle executes.
  • the left piston end 23 of the control piston 17 in FIG. 1 lies in a control chamber 30 at the left end of the housing bore 20.
  • the control chamber 30 contains a control spring 35 and is connected via a channel 34 to a channel 33 connected to the discharge line 32 downstream of the orifice plate 9 middle part of the housing bore 29 in connection.
  • the channel 33 could also be omitted if the piston end 23 forms the control edge 18 at the same time. Then pressure medium would flow directly out of the control chamber 30 via the control orifice 14.
  • the right piston end 24 of the control piston 17 is located in a control chamber 31 at the right end of the housing bore 29, the inside diameter of which is larger than the inside diameter of the housing bore 29
  • Control chamber 31 is connected via a channel 39 to a control line 40 in which a throttle 41 is arranged.
  • the control line 40 is connected to the drain line 32 between the measuring orifice 9 and the hydraulic motor 2 and leads the load pressure prevailing on the left side of the piston 4 into the control chamber 31.
  • the right piston end 24 is designed as a closing element 25 with a conical thickening 26.
  • a valve seat 27 is assigned to the closing element 25 in the mouth region of the housing bore 29 into the control chamber 31, which valve seat is attached to an insert 28 in the housing 13 in the present case.
  • the insert 28 could also be a continuous hardened sleeve with a ground valve seat.
  • a channel 36 leads from the annular chamber 15 to a tank line 38.
  • the control device 1 according to FIG. 1 is in the zero position.
  • the pressure source 6 is switched off.
  • the pressure caused by the load 5 on the left side of the piston 4 is from the check valve 8, further from the blocking member A, which is in the load-holding shut-off position, i.e. the orifice 9 and finally held by the closing element 25 which cooperates with the valve seat 27 in the manner of a seat valve.
  • the pressure medium downstream of the measuring orifice 9 is relaxed via the closed control orifice 14 (leakage losses caused by the design). As a result, the control piston 17 can no longer give up its shut-off position.
  • the pressure source 6 is activated. Unless a separate control device is provided for this direction of movement, for example between pump 6 and check valve 7, the measuring orifice 9 adjusted by the magnet 11 to an open position, which corresponds to the desired speed of movement of the piston 4. It loses its function of the locking member A.
  • the control chamber 30 is pressurized until the control piston 17 moves to the right and leaves enough pressure medium via the control orifice 16, 18 that the piston 4 only moves to the right at the set speed, independently on the size or changes in the load 5.
  • a switching jerk is avoided because the check valve 8 only opens when at least the same pressure is built up in the supply line 7 as that prevails in the control chamber 31, and because pressure medium for adjustment of the control piston 17 comes from the pressure source 6.
  • the pressure source 6 is not activated. Rather, the orifice 9 is adjusted to a position which corresponds to the desired speed of movement of the piston 4.
  • the measuring orifice 9 thus gives up its function as a blocking element A.
  • Pressure medium under the load pressure is shifted from the control chamber 31 via the control line 40, the channel 33 and the channel 34 into the control chamber 30; the control panel 14 opens. Since no appreciable positive overlap between the control edges 18, 16 is needed because the load pressure was applied to the blocking element A, no noticeable volume is required for opening the control orifice 14. Since the control spring 35 is also effective, the control piston 17 shifts to the right, the volume which is displaced from the control chamber 31 by the displacement of the control piston 17 to the right being fed to the control chamber 30. For this reason, there is no shift jerk.
  • the hydraulic motor 2 is assigned a seat valve 42 upstream of the metering orifice 9 in the embodiment of FIG the force of a spring 43 assumes its shut-off position automatically and by an actuator 44, for example a switching magnet, is adjustable in a through position.
  • the seat valve 42 forms the blocking member A ⁇ in the shut-off position.
  • the control line 40 is connected to the drain line 32 between the seat valve 42 and the hydraulic motor 2. In the zero position of the control device 1 ⁇ , whose pressure compensator 12 corresponds to that of FIG.
  • the load pressure of the hydraulic motor 2 is thus taken up by the seat valve 42 and by the closing element 25 on the valve seat 27.
  • the measuring orifice 9 can therefore easily remain open in the zero position. This also means that e.g. for a tail lift control with constant speed of movement of the hydraulic motor 2, a fixed measuring orifice 9 can be used.
  • the pressure source 6 is first activated in the zero position and the seat valve 42 is switched to its open position. Then, depending on the setting of the orifice 9, the piston of the hydraulic motor 2 is moved against the load. The pressure medium from the control chamber 31 is displaced under the load pressure with the volume into the control chamber 30 which the control piston 17 displaces. A shift jerk does not occur. If a separate control device is used for this direction of movement (for example between the pressure source 6 and the check valve 7), then the orifice 9 in the Locked position held. The pressure compensator 12 is not working.
  • the same pressure compensator 12 is used again as in the embodiment of FIGS. 1 and 2.
  • the measuring orifice 9 can be adjustable or fixed.
  • a two-position switch valve 45 is provided in the control line 40 in the control device 1 ⁇ according to FIG. 3, which is connected to the drain line 32 between the seat valve 42 and the hydraulic motor 2 and consequently always carries the load pressure.
  • the control line 40 has two parts 40a and 40b, between which the changeover valve 45 is located.
  • a second control line 48 is provided, which is connected to the drain line 32 between the measuring orifice 9 and the seat valve 42 and also leads to the changeover valve 45.
  • the changeover valve 45 is brought into a first through position by a spring 46, in which the two parts 40a and 40b of the control line are connected to one another and the second control line 48 is separated.
  • An actuating device 47 for example a switching magnet, is provided on the changeover valve, with which the changeover valve 45 is converted into a second one Passable position can be brought in which a pressure-transmitting connection between the part 40b of the control line 40 and the second control line 48 is established, while the first part 40a is separated from the part 40b.
  • the actuating devices of the seat valve 42 and the changeover valve 45 can optionally be connected to one another by a coupling 49, so that they are always actuated in the same direction.
  • the pressure source 6 is first activated and the measuring orifice 9 is set for the desired movement speed.
  • the control piston is in its shut-off position, in which it is held by the load pressure from the open control line 40.
  • the seat valve 42 and, at the same time, the switching valve 45 are switched via the coupling 49, so that the seat valve 42 assumes its passage position and the switching valve 45 its second passage position, in which the part 40b of the control line 40 is connected to the second control line 48 and the part 40a of the control line 40 are separated.
  • the control piston is moved to the right, so that the control orifice begins to open gradually.
  • the volume that is in this adjustment of the control piston in the Control chamber 31 is displaced, is supplied via part 40b, the changeover valve 45, the control line 48 and the drain line 32 to the control chamber 30, so that a switching jolt is reliably avoided. If a separate control device (for example a current regulator) is provided for this direction of movement, the pressure compensator 12 does not work. The respective load pressure is kept in the zero position.
  • a separate control device for example a current regulator
  • the poppet valve 42 To move the hydraulic motor 2 under the load - starting from the zero position - the poppet valve 42 is moved into the through position and the changeover valve 45 into its second through position so that the control chambers 30, 31 are acted upon with the pressures upstream and downstream of the orifice plate 9 and the Flow resistance of the seat valve 42 is not included in the control behavior.
  • the control orifice 14 is opened in accordance with the setting of the orifice 9.
  • the pressure medium volume corresponding to the movement of the control piston 17 is displaced from the control chamber 31 into the control chamber 30. There is no switching jerk.
  • the seat valve 42 is switched over together with the changeover valve 45.
  • the load pressure is again held by the seat valve 42 and the seat valve between the closing element 25 and the valve seat 27.
  • the second control line 48 is disconnected.
  • the control chamber 30 is relieved via the control panel 14.
  • the control device 1 ⁇ can be expanded by adding at least one further hydraulic motor 2 ⁇ to a control device 1 ′′ ', with which it is possible to use several hydraulic motors 2, 2 ⁇ with the common measuring orifice 9 and the common pressure compensator 12 and the common switch valve 45 to control independent of the load pressure.
  • the further hydraulic motor 2 ⁇ is connected via its drain line 32 ⁇ to the supply line 7.
  • a seat valve 42 ⁇ corresponding to the seat valve 32 is arranged, which holds the load pressure of the hydraulic motor 2 ⁇ in the shut-off position and allows the pressure medium to be released or supplied in its through position.
  • a control line 40a ⁇ corresponding to part 40a of control line 40 can lead from drain line 32 ⁇ between seat valve 42 ⁇ and hydraulic motor 2 ⁇ to control line part 40a and thus to changeover valve 45.
  • Check valves 51, 52 are expediently provided in the control line parts 40a and 40a ⁇ .
  • Interfaces 50 indicated by dash-dotted lines show where and how the other hydraulic motor (s) 2 ⁇ are connected. If the hydraulic motor 2 has the highest load pressure, the control line part 40a ⁇ can be omitted.
  • the hydraulic motors 2, 2 ⁇ are expediently controlled individually, i.e. as soon as one hydraulic motor moves, the other remains in its load-holding position.
  • control device 1, 1 ⁇ , 1 is that when the control device is switched from the zero position to a position for moving the hydraulic motor under load, there is no switching jerk because this occurs between the closing element 25 and the valve seat 27 formed seat valve in the pressure compensator works practically leak-free, so that no pressure medium is lost even over longer downtimes, but exactly at the beginning of the movement of the pressure medium under load pressure in the control chamber with the seat valve the volume is removed and transferred to the other control chamber, which is required to open the control panel without the undesirable switching jerk.
  • This volume is, so to speak, held ready for retrieval in a pressure accumulator integrated in the control device, without the pressure source having to contribute to this.

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Claims (12)

  1. Dispositif de commande hydraulique (1,1',1",1'"), en particulier dispositif de commande l'elevation, pour au moins un moteur hydraulique (2,2'), susceptible d'être sollicité d'un côté contre une charge (5), maintenant la charge lorsqu'il est à l'arrêt et susceptible de produire un déplacement dans les deux sens, sous la charge, avec un régulateur de débit à deux voies, dans une conduite d'évacuation (32) allant au réservoir (37), le régulateur de débit présentant un diaphragme de mesure (9) et une balance de pression (12), avec un diaphragme de réglage (14), qui est commandée par un piston de réglage (17), déplaçable dans un alésage de carter (29), entre une position de passage et une position de blocage, dont les extrémités de piston (23,24) sont disposées dans deux chambres de commande (31,30), dont la chambre de commande (30), qui contient l'extrémité de piston (23) susceptible d'être sollicitée en direction de la position de passage du piston de réglage, est susceptible d'être sollicitée par la pression aval du diaphragme de mesure (9), et la chambre de commande (31), qui contient l'extrémité de piston susceptible d'être sollicitée en direction de la position de blocage du piston de réglage, est susceptible d'être sollicitée par la pression amont du diaphragme de mesure (9), caractérisé en ce que, sur l'extrémité de piston (24), susceptible d'être sollicitée par la pression amont du diaphragme de mesure (9), du piston de réglage (17), est prévu un élément d'obturation (25), un siège de soupape (27) étant associé à l'élément d'obturation (25), dans la chambre de commande (31), l'élément d'obturation (25) coopérant avec le siège de soupape (27), de façon à produire une étanchéité à la manière d'une soupape à siège, dans la position de blocage du piston de réglage (17), et un organe d'isolement (A,A') réglable en une position d'isolement maintenant la pression de charge étant prévu dans la conduite d'évacuation (32)..
  2. Dispositif de commande hydraulique (1,1',1",1'") selon la revendication 1, caractérisé en ce que l'organe d'isolement (A) est le diaphragme de mesure (9), susceptible d'être amené en une position d'isolement hermétique.
  3. Dispositif de commande hydraulique selon la revendication 1, caractérisé en ce que l'organe d'isolement (A') est une soupape à siège (42,42') disposé en amont du diaphragme de mesure (9), et la chambre de commande (31) étant raccordée à la conduite d'évacuation (32), du côté, opposé au diaphragme (9), de la soupape à siège (42,42').
  4. Dispositif de commande hydraulique selon les revendications 1 à 3, caractérisé en ce que la chambre de commande (31) présente un diamètre intérieur supérieur à l'alésage de carter (29), le siège de soupape (27) étant disposé la chambre de commande (31), dans la zone d'embouchure de l'alésage de carter (29), et réalisé avec une forme conique, l'élément d'obturation (25) étant formé par un épaississement conique (26) ménagé sur l'extrémité de piston de réglage (24).
  5. Dispositif de commande hydraulique selon les revendications 1 à 4, caractérisé en ce qu'une soupape de commutation à deux positions (45) est prévue dans une première conduite de commande (40), à l'aide de laquelle la pression qui règne dans la chambre de commande (31) est susceptible d'être transmise du côté, opposé au diaphragme de mesure (9), de la soupape à siège (42), et une autre conduite de commande (48) menant de la soupape de commutation (45) à la conduite d'évacuation (32), en amont du diaphragme de mesure (9).
  6. Dispositif de commande hydraulique selon les revendications 3 à 5, caractérisé en ce que la soupape à siège (42,42') est réglable, à l'encontre d'une force élastique, de sa position d'isolement à une position de passage.
  7. Dispositif de commande hydraulique selon la revendication 6, caractérisé en ce que la soupape à siège (42,42') est actionnée magnétiquement.
  8. Dispositif de commande hydraulique selon la revendication 5, caractérisé en ce que la soupape de commutation (45) est réglable, contre une force élastique, de sa première position de passage, dans laquelle la première conduite de commande (40) allant à la chambre de commande (31) est ouverte, en une deuxième position de passage, dans laquelle la chambre de commande (31) est raccordée à une deuxième conduite de commande (48).
  9. Dispositif de commande hydraulique selon la revendication 8, caractérisé en ce que la soupape de commutation (45) est actionnée magnétiquement.
  10. Dispositif de commande hydraulique selon les revendications 2 à 8, caractérisé en ce que les dispositifs de réglage (47,44) de l'organe d'isolement (A,A') (par exemple soupape à siège 42) et de la soupape de commutation (45) sont chaque fois couplés à un réglage commun (couplage 49).
  11. Dispositif de commande hydraulique selon au moins l'une des revendications 1 à 10, caractérisé en ce que la conduite d'évacuation (32) coupe, en amont du diaphragme de mesure (9), une conduite d'alimentation (7), alimentée par une source de pression (6), pour un moteur hydraulique (2) travaillant d'un côté contre une charge.
  12. Dispositif de commande hydraulique selon au moins l'une des revendications 1 à 11, caractérisé en ce que la conduite d'alimentation (7) coupe au moins une deuxième conduite d'évacuation (32') d'un moteur hydraulique (2'), travaillant d'un côté contre une charge, pour lequel une soupape à siège (42') est prévue dans l'autre conduite d'évacuation (32'), et une conduite de commande (40'a), allant vers une soupape de commutation (45) commune à tous les moteurs hydrauliques (2,2') prévus, étant prévue le cas échéant, entre la soupape à siège (42') et le deuxième moteur hydraulique (2').
EP88101810A 1987-02-18 1988-02-08 Dispositif de commande hydraulique Expired - Lifetime EP0279315B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88101810T ATE68243T1 (de) 1987-02-18 1988-02-08 Hydraulische steuervorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3705170A DE3705170C1 (de) 1987-02-18 1987-02-18 Hydraulische Steuervorrichtung
DE3705170 1987-02-18

Publications (3)

Publication Number Publication Date
EP0279315A2 EP0279315A2 (fr) 1988-08-24
EP0279315A3 EP0279315A3 (en) 1990-03-07
EP0279315B1 true EP0279315B1 (fr) 1991-10-09

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ID=6321263

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88101810A Expired - Lifetime EP0279315B1 (fr) 1987-02-18 1988-02-08 Dispositif de commande hydraulique

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Country Link
US (1) US4811649A (fr)
EP (1) EP0279315B1 (fr)
JP (1) JP2744004B2 (fr)
AT (1) ATE68243T1 (fr)
DE (2) DE3705170C1 (fr)
ES (1) ES2026213T3 (fr)
FI (1) FI89298C (fr)
GR (1) GR3003518T3 (fr)

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DE4207803A1 (de) * 1991-05-14 1992-11-19 Bosch Gmbh Robert Druckhalteventil
US5170692A (en) * 1991-11-04 1992-12-15 Vickers, Incorporated Hydraulic control system
DE4208980A1 (de) * 1992-03-20 1993-09-23 Rexroth Mannesmann Gmbh Hydraulische antriebsvorrichtung mit einem zylinder
DE4234034A1 (de) * 1992-10-09 1994-04-14 Rexroth Mannesmann Gmbh Wegeventil zur Ansteuerung eines hydraulischen Verbrauchers insbesondere eines mobilen Arbeitsgerätes
JPH06193606A (ja) * 1992-12-22 1994-07-15 Komatsu Ltd 圧力補償弁を備えた操作弁
DE29508394U1 (de) * 1995-05-19 1995-08-03 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Elektrohydraulisches Hubmodul
DE19646427B4 (de) * 1996-11-11 2006-01-26 Bosch Rexroth Aktiengesellschaft Ventilanordnung
DE29713293U1 (de) 1997-07-25 1997-10-23 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Magnetbetätigtes Ablaßventil
DE19813038B4 (de) * 1998-03-25 2007-01-04 Volkswagen Ag Hydraulikkreis und Hydraulikventil
DE10023583B4 (de) * 2000-05-13 2012-05-24 Robert Bosch Gmbh Elektrohydraulischer Senken-Modul
US6467264B1 (en) * 2001-05-02 2002-10-22 Husco International, Inc. Hydraulic circuit with a return line metering valve and method of operation
DE102004020371A1 (de) * 2004-04-23 2005-11-10 Botschafter-Knopff, Ilse Hydraulische Steuereinrichtung
WO2008048927A2 (fr) * 2006-10-17 2008-04-24 Actuant Corporation Robinet doseur haute pression à débit variable sans fuites
GB0912540D0 (en) * 2009-07-20 2009-08-26 Bamford Excavators Ltd Hydraulic system
CN102852900A (zh) * 2012-09-11 2013-01-02 苏州同大机械有限公司 塑料制品成型机械用的油缸的泄漏油收集装置
DE102016012261A1 (de) 2016-10-13 2018-04-19 Hydac Fluidtechnik Gmbh Ablaufdruckwaage und Hub-Senkvorrichtung mit einer solchen Ablaufdruckwaage
JP7091634B2 (ja) * 2017-11-15 2022-06-28 いすゞ自動車株式会社 油圧制御弁
CN110477999B (zh) * 2019-08-29 2021-07-02 湖南瀚德微创医疗科技有限公司 一种输出恒定夹持力的手术夹钳

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Also Published As

Publication number Publication date
ATE68243T1 (de) 1991-10-15
DE3705170C1 (de) 1988-08-18
FI880600A0 (fi) 1988-02-10
DE3865313D1 (de) 1991-11-14
EP0279315A2 (fr) 1988-08-24
FI880600A (fi) 1988-08-19
ES2026213T3 (es) 1992-04-16
FI89298B (fi) 1993-05-31
FI89298C (fi) 1993-09-10
US4811649A (en) 1989-03-14
JPS63225701A (ja) 1988-09-20
GR3003518T3 (fr) 1993-03-16
JP2744004B2 (ja) 1998-04-28
EP0279315A3 (en) 1990-03-07

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