EP0877169B1 - Dispositif de commande hydraulique indépendante de la pression de charge d'un moteur à double effet - Google Patents

Dispositif de commande hydraulique indépendante de la pression de charge d'un moteur à double effet Download PDF

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Publication number
EP0877169B1
EP0877169B1 EP98102270A EP98102270A EP0877169B1 EP 0877169 B1 EP0877169 B1 EP 0877169B1 EP 98102270 A EP98102270 A EP 98102270A EP 98102270 A EP98102270 A EP 98102270A EP 0877169 B1 EP0877169 B1 EP 0877169B1
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EP
European Patent Office
Prior art keywords
slide
control
pressure
control device
bore
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
EP98102270A
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German (de)
English (en)
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EP0877169A3 (fr
EP0877169A2 (fr
Inventor
Wolfgang Koetter
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
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Publication of EP0877169A2 publication Critical patent/EP0877169A2/fr
Publication of EP0877169A3 publication Critical patent/EP0877169A3/fr
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Publication of EP0877169B1 publication Critical patent/EP0877169B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15C—FLUID-CIRCUIT ELEMENTS PREDOMINANTLY USED FOR COMPUTING OR CONTROL PURPOSES
    • F15C3/00—Circuit elements having moving parts
    • F15C3/06—Circuit elements having moving parts using balls or pill-shaped disks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and the 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • 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
    • F15B2211/78—Control of multiple output members

Definitions

  • the invention is based on a hydraulic Control device for load pressure independent control of a double-acting engine according to the in the preamble of Claim 1 specified genus.
  • Such a hydraulic control device is already used load pressure compensated control of a double acting Motors known from DE 36 34 728 C2, two of which Directional control valves for parallel actuation of the assigned Motors from a common variable displacement pump with pressure medium are supplied, the controller with a control line a shuttle valve chain with the maximum load pressure of the two motors is applied.
  • the pressure compensator used for load pressure compensation downstream of a metering orifice on the control slide, the Pressure compensator also used for direction control Piston sections of the control spool is connected upstream.
  • the Throttle valve in the downstream pressure compensator is in Opening direction from the pressure downstream of the orifice plate and in Closing direction of the highest load pressure and the Control pressure difference applied by the control spring.
  • DE 40 26 720 A1 is a hydraulic Control device for load pressure independent control of a known double-acting engine, in which a pressure compensator upstream of that formed on the spool Orifice plate is switched.
  • This directional valve can be used with a check valve separated from the pressure compensator Meet security requirements, with discharge of a cross channel between the check valve and orifice plate controlled via a piston section of the control slide which is also designed as a full slide valve. Also points the directional control valve has a second individual orifice Limit the oil flow to.
  • this directional valve with the Orifice plate upstream pressure compensator is Throttle slide in the closing direction from the pressure upstream of the Orifice plate on the control slide and in the opening direction from Pressure downstream of the orifice plate, i.e. plus the load pressure acted upon by the force of a spring.
  • the pressure compensator holds thus the pressure difference across the measuring throttle on the directional valve constant even with different load pressure, so that too the associated flow rate remains constant and the am Directional control valve set working speed is kept constant.
  • a disadvantage of this Control device is that it is not a supply dependent Allows oil flow sharing.
  • the hydraulic control device load-independent control of a double-acting Motors with the characterizing features of claim 1 on the other hand the advantage that they are at a supply-dependent oil flow distribution an increased degree Offers security and an extended usability. So can be separated by the arrangement of the pressure compensator of the check valve in connection with the control of the Pressure relief in the cross channel directly above the Control spool achieve that the load pressure with falling Pump pressure can be kept safer and faster. This also applies if the pressure in the control circuit Leakage or line break decreases.
  • the lines be formed as simply as possible in the control circuit, whereby Connecting lines in the control slide itself are omitted, see above that this as a simple, inexpensive building Full slide can be executed.
  • the directional valve with a fourth Equip switching position for an open gear the with the load pressure line connected to the pump is relieved.
  • a second individual orifice with this directional control valve integrate which the oil flow to the engine limited regardless of the deflection of the control spool.
  • FIG. 1 shows a longitudinal section through a hydraulic control device with a directional valve and Combined pressure compensator in a simplified representation
  • figure 2 as a detail a shuttle valve from a control circuit according to II-II in Figure 1
  • Figure 3 is a schematic Representation of a control block for two double-acting Motors with two control devices according to FIG. 1.
  • Figure 1 shows a longitudinal section through a hydraulic Control device 10 for load pressure-independent control of a double-acting engine.
  • the control device 10 are the actual directional control valve 11 in the load-sensing version and the associated pressure compensator 12 in one common housing 13 arranged.
  • the housing 13 has one between the two end faces continuous longitudinal bore 14, in the by annular Extensions trained a total of seven chambers 15 to 21 of which the five adjacent chambers 15 to 19 serve to control the direction of the pressure medium flow, while the two outer chambers 20, 21 one Measuring aperture 22 are assigned, which of Speed control of the engine is used.
  • the five adjacent chambers 15 to 19 serve the middle one Chamber as inlet chamber 17, while those lying next to it two chambers a first motor chamber 16 and a second Form motor chamber 18, which with a motor connection 23 or 24 are connected.
  • a return chamber 15 and 19, respectively, which are not shown in FIG drawn way with a return port in the housing 13 are connected.
  • 21 serves the first lying next to the second return chamber 19
  • Orifice chamber 20 as a discharge orifice chamber and the other as the inlet-side, second orifice chamber 21.
  • a spool 25 is tight and slidably guided.
  • the control slide 25 is by annular grooves divided into six piston sections 27 to 32.
  • the three adjacent piston sections 27, 28, 29 are with Control edges equipped and serve the direction control.
  • An adjoining fourth piston section 30, which in the drawn neutral position of the spool 25 in the outlet-side measuring orifice chamber 20 is used all to relieve a control circuit.
  • the one about it subsequent fifth piston section 31 is part of the Measuring aperture 22 and determines with its control edges Deflection of the control spool in both working positions the size of the volume flow to the motor and thus its speed.
  • the outer, sixth piston section 32 protrudes from the longitudinal bore 14 so that a attack actuator not shown can.
  • Control slide 25 with the first piston section 27 in one double-acting return device 33, the type of which is known per se and which the spool in its Neutral position 34 centered, out of which he in two Working positions 35 and 36 can be deflected. Furthermore, the Control slide 25 to a fourth switching position 37, which as Free position is executed.
  • FIG. 1 also shows, is in the housing 13 below the longitudinal bore 14 a second bore 39 and below a third bore 41 is arranged, all parallel to the Longitudinal bore 14 run.
  • the second bore 39 is trained like a blind hole and takes up inside Check valve 42 with its spherical closing member 43 on.
  • the discharge-side orifice chamber 20 a perpendicular to Spool 25 extending extension 45, which intersects the third bore 41.
  • Extension 45 also extends in the housing 13 perpendicular to the longitudinal slide 25 a circulation chamber 46, in whose end near the slide opens into the second bore 39, while with its end facing away from the longitudinal slide 25 penetrates the third bore 41. That way it forms one between the extension 45 and the circulation chamber 46 extending wall of the housing 13 an annular web 47, the both as a control edge for the second orifice 44, and serves for a throttle slide 48 of the pressure compensator 12.
  • the Throttle slide 48 is a hollow slide with a Blind bore 49 and a radial bore 51 executed, see above that he is in the starting position centered by the control spring 52 the circulation chamber 46 with the discharge-side orifice chamber 20 connects in a throttled manner.
  • the Throttle valve 48 is on its right front side Pressure in the extension 45 in the opening direction, that is acted against the force of the spring 52. In The closing direction acts on the throttle slide 48 the control spring 52 and the maximum load pressure in the spring chamber 53, via a control opening 54 from a control circuit is fed.
  • FIG. 1 also shows, lies in the second hole 39 in the area between the securing the inlet chamber 17 Check valve 42 and the circulation chamber 46 a Pressure tap opening 55, through which the maximum load pressure of the connected motor is tapped.
  • Form shuttle valve 56 and control channel 57 thereby parts of a known control circuit 58 in which in a manner known per se via shuttle valve chains maximum load pressure selected and for a load sensing control is used.
  • the two flange surfaces of the housing 13 connects to each other discharge-side orifice chamber 20 via a transverse channel 62 with the inlet chamber 17 in connection, in which Cross channel 62 one behind the other, the individual orifice 44, the Pressure compensator 12 and the separate check valve 42 are switched.
  • the throttle slide 48 is thus downstream of the orifice 22 and is such of Tax pressures that with him a supply-dependent oil flow distribution is achieved.
  • FIG. 3 shows a schematic representation of a Control block in which, in addition to the first control device 10 a similar, second control device 70 are flanged together so that at least two double-acting motors can be operated in parallel.
  • the Control devices 10, 70 are between one Connection plate 71 and an end plate 73 switched and connected in parallel to the continuous inlet channel 61.
  • the inlet channel 61 is from a pressure medium supply unit 73 supplied with pressure medium, with the Control circuit 58 of the maximum load pressure is returned.
  • the shuttle valves 56 form in both Control devices 10, 70 a valve chain, via which the maximum load pressure is selected or one Relief of the control circuit 58 is made.
  • control device 10 The operation of the control device 10 is as follows explained, the basic function of such Load-sensing valves are assumed to be known per se.
  • the pressure compensator 12 Measuring aperture 20 is connected downstream and is also upstream from the directional control edges in the directional control valve 11.
  • the LS pressure tap that is, the one that taps the load pressure Pressure tap opening 55 in the directional control valve 11 lies between the Pressure compensator 12 and the check valve 42, so that the respective pressure signal via the shuttle valve 56 in the Control circuit 58 is given.
  • the one in the control circuit 58 The selected, highest load pressure becomes pump 73 on the one hand and on the other hand into the spring chambers 53 of the pressure compensators 12 passed, this load pressure signal via control lines and the control openings 54 enter the spring chambers 53.
  • On the opposite end is the throttle slide 48 from the pressure downstream of the orifice 22 in the opening direction applied. This type of interconnection and the Pressurization of the throttle slide 48 enables one supply-dependent oil flow distribution at Parallel actuation of both control devices 10, 70.
  • control device 10 If the control device 10 is operated by itself and deflected into one of the working positions 35 or 36, so a load pressure independent control of the connected motor.
  • the throttle slide 48 in the pressure compensator 12 opens, controls he the relief connection via the radial bore 51.
  • the control edge also closes at the fourth piston section 30 the connection to the return chamber 19 before the orifice 22 opens. In this way there is no loss of oil to the return on.
  • the pressure compensator 12 maintains the pressure drop the measuring aperture 22 constant in a manner known per se, so that the speed of the motor proportional to the displacement of the spool 25 and regardless of Load pressure fluctuations is controlled. Should do this Leakage or a sticking shuttle valve the function of the Pressure compensator 12 may be impaired, in any case close the check valve 42 and prevent oil from the load flows towards the pump connection. Independent of the pressure conditions in the spring chamber 53 of the pressure compensator 12 a load on the motor becomes safe when the pump pressure drops held.
  • the check valve 42 designed as a seat valve ensures low leakage.
  • downstream Pressure compensator 12 which always keeps the pressure at the highest Load pressure plus regulating pressure difference regulates.
  • the Pressure differences at the orifice plates 22 become smaller and less oil flows to the engines.
  • the oil flow through the directional valves 11 increases in relation to the given Setpoints.
  • the directional valve 11 also has a fourth Switch position, this free position 37 by Pressing the control slide 25 into the housing 13 is achieved. Both are in this release position Motor connections 23, 24 with the return chambers 15 and 19 connected and the LS pressure line is relieved.
  • the volume flow can be independent of Limit the stroke of the control slide 25 for the directional valve 11, as is known in itself.
  • control spool 25 is designed as a full slide valve particularly advantageous combination.

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

Claims (12)

  1. Dispositif de commande hydraulique indépendante de la pression de charge d'un moteur double effet comportant un distributeur (10) dont le boítier ( 13) reçoit un distributeur à tiroir (25) dans un perçage longitudinal ( 14), qui présente des sections de piston pour la commande de la vitesse et de la direction du moteur, dont la section de piston au distributeur à tiroir qui sert en tant que diaphragme de mesure (22) à la commande de vitesse, est reliée par un canal transversal (62) côté boítier avec les sections de piston (27 à 29) qui sont disposées séparément, pour la commande de direction, au distributeur à tiroir, alors que dans ce canal transversal (62), une jauge de pression 2 voies (12) commandant le débit est raccordée, dont la vanne d'étranglement (48), en direction de fermeture, se voit appliquer un ressort (52) et une pression maximale de charge et, en position d'ouverture, la pression dans le canal transversal (62) en aval du diaphragme de mesure (22) et en amont de la jauge de pression (12), et avec une ouverture de prise de pression (55) pour une boucle de commande, qui repose dans le canal transversal (62) en aval de la vanne d'étranglement (48) et qui, par un dispositif de déchargement au distributeur à tiroir est déchargeable vers une chambre de retour (19),
    caractérisé en ce que
    dans le canal transversal (62) en aval de la jauge de pression (12) et en amont du distributeur à tiroir (25), une soupape anti-retour (42) séparée de la vanne d'étranglement (48) est raccordée, l'ouverture de prise de pression (55) est en amont de la soupape anti-retour (42), le dispositif de déchargement présente une section de piston (30) au distributeur à tiroir (25) qui commande la liaison entre une chambre de diaphragme de mesure (20) côté évacuation et la chambre de retour ( 19) avoisinante, et la vanne d'étranglement (48) dans sa position de sortie (74) crée une liaison étranglée (51, 49) entre l'ouverture de prise de pression (55) et cette chambre de diaphragme de mesure (20), et obture cette liaison (51, 49) en ses positions de travail (75).
  2. Dispositif de commande hydraulique selon la revendication 1,
    caractérisé en ce que
    dans le canal transversal (62) en aval du diaphragme de mesure (22) et en amont de la jauge de pression (20), un deuxième diaphragme individuel de mesure (44) est raccordé qui, en particulier, est réalisé de manière réglable.
  3. Dispositif de commande hydraulique selon la revendication 1 ou 2,
    caractérisé en ce que
    le distributeur à tiroir (25) outre une position neutre (34) et deux positions de travail (35, 36) présente une quatrième position de réglage (37) pour le passage libre.
  4. Dispositif de commande hydraulique selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que
    le distributeur à tiroir (25) est réalisé en tant que tiroir plein sans canalisations de liaison à l'intérieur pour du liquide hydraulique de commande ou de travail.
  5. Dispositif de commande hydraulique selon l'une quelconque des revendications 2 à 4,
    caractérisé en ce que
    le boítier (13) présente deux perçages (39, 41) parallèles au perçage longitudinal (14) pour le distributeur à tiroir (25), figurant tous dans un plan et dont le deuxième perçage (39) central reçoit la soupape anti-retour (42) alors que dans l'autre, troisième perçage (41), la jauge de pression (12) et le diaphragme individuel de mesure (44) sont disposés.
  6. Dispositif de commande hydraulique selon la revendication 5,
    caractérisé en ce que
    le perçage central (39) est constitué en tant que trou borgne et, par son extrémité intérieure, pénètre dans une chambre de circulation (46) s'étendant perpendiculairement par rapport à l'axe longitudinal du distributeur à tiroir (25) qui traverse le troisième perçage (41).
  7. Dispositif de commande hydraulique selon la revendication 6,
    caractérisé en ce que
    la chambre de diaphragme de mesure (20) se trouvant en aval possède une prolongation (45) s'étendant perpendiculairement par rapport au distributeur à tiroir (25), disposée pour l'essentiel parallèlement par rapport à la chambre de circulation (46) et traversant le troisième perçage (41), alors que la chambre de diaphragme de mesure (21) située en amont possède une liaison avec un canal d'arrivée (61).
  8. Dispositif de commande hydraulique selon l'une quelconque des revendications 1 à 7,
    caractérisé en ce que
    les chambres de diaphragme de mesure (20, 21) affectées au diaphragme de mesure (22), sont disposées dans le boítier (13), dans le perçage longitudinal ( 14), latéralement à côté des cinq chambres de travail (15 à 19) pour la commande de direction.
  9. Dispositif de commande hydraulique selon l'une quelconque des revendications 1 à 8,
    caractérisé en ce que
    la vanne d'étranglement (48) est constituée en tant que tiroir creux avec perçage borgne (49) et, pour la commande de déchargement de l'ouverture de prise de pression (55), présente un perçage radial (51) dépassable en fonction de la position.
  10. Dispositif de commande hydraulique selon l'une quelconque des revendications 6 à 9,
    caractérisé en ce que
    la paroi reposant dans le boítier (13) entre la chambre de circulation (46) et la chambre de diaphragme de mesure (20) côté évacuation, forme dans le troisième perçage (41) une entretoise annulaire (47) qui forme l'arête de commande côté boítier pour la vanne d'étranglement (48) et la jauge individuelle de pression (44).
  11. Dispositif de commande hydraulique selon la revendication 10,
    caractérisé en ce que
    l'entretoise annulaire (47) repose sensiblement dans le même plan radial que la section de piston (30) au distributeur à tiroir (25) en sa position neutre (34) commandant le déchargement.
  12. Dispositif de commande hydraulique selon l'une quelconque des revendications 1 à 11,
    caractérisé en ce que
    la vanne d'étranglement (48) présente une position de fermeture (76) entre sa position de sortie (74) et ses positions de travail (75) dans laquelle la liaison étranglée (51) est commandée en fermeture et le canal transversal (62) n'est pas encore commandé en ouverture.
EP98102270A 1997-05-07 1998-02-10 Dispositif de commande hydraulique indépendante de la pression de charge d'un moteur à double effet Expired - Lifetime EP0877169B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19719228A DE19719228A1 (de) 1997-05-07 1997-05-07 Hydraulische Steuereinrichtung zur lastdruckunabhängigen Steuerung eines doppeltwirkenden Motors
DE19719228 1997-05-07

Publications (3)

Publication Number Publication Date
EP0877169A2 EP0877169A2 (fr) 1998-11-11
EP0877169A3 EP0877169A3 (fr) 2000-01-19
EP0877169B1 true EP0877169B1 (fr) 2003-12-03

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EP98102270A Expired - Lifetime EP0877169B1 (fr) 1997-05-07 1998-02-10 Dispositif de commande hydraulique indépendante de la pression de charge d'un moteur à double effet

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EP (1) EP0877169B1 (fr)
DE (2) DE19719228A1 (fr)

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DE10027382A1 (de) 2000-06-02 2001-12-06 Bosch Gmbh Robert Hydraulische Steuereinrichtung
US6318079B1 (en) * 2000-08-08 2001-11-20 Husco International, Inc. Hydraulic control valve system with pressure compensated flow control
CN109798270B (zh) * 2019-02-25 2020-05-19 哈尔滨工业大学 多模态节能伺服作动器及实现多模态节能的方法

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DE3629850A1 (de) * 1986-09-02 1988-03-03 Bosch Gmbh Robert Hydraulisches wegeventil
DE3634728A1 (de) * 1986-10-11 1988-04-21 Rexroth Mannesmann Gmbh Ventilanordnung zum lastunabhaengigen steuern mehrerer gleichzeitig betaetigter hydraulischer verbraucher
DE4026720A1 (de) * 1989-12-19 1991-06-20 Bosch Gmbh Robert Hydraulisches wegeventil
DE4136991C2 (de) * 1991-11-11 2000-11-02 Bosch Gmbh Robert Hydraulisches Wegeventil
DE69225392T2 (de) * 1991-12-25 1998-09-03 Kayaba Industry Co., Ltd., Tokio/Tokyo Einrichtung zur Steuerung mehrerer Servomotoren

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DE19719228A1 (de) 1998-11-12
EP0877169A3 (fr) 2000-01-19
DE59810308D1 (de) 2004-01-15
EP0877169A2 (fr) 1998-11-11

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