EP0528103B2 - Dispositif de commande électro-hydraulique - Google Patents

Dispositif de commande électro-hydraulique Download PDF

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Publication number
EP0528103B2
EP0528103B2 EP92104566A EP92104566A EP0528103B2 EP 0528103 B2 EP0528103 B2 EP 0528103B2 EP 92104566 A EP92104566 A EP 92104566A EP 92104566 A EP92104566 A EP 92104566A EP 0528103 B2 EP0528103 B2 EP 0528103B2
Authority
EP
European Patent Office
Prior art keywords
piston
control
force
travel
main piston
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
EP92104566A
Other languages
German (de)
English (en)
Other versions
EP0528103A1 (fr
EP0528103B1 (fr
Inventor
Detlef Tolksdorf
Gerd Pidde
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gft Gesellschaft fur Hydraulik-Technologie GbR
Original Assignee
Gft Gesellschaft fur Hydraulik-Technologie GbR
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Publication date
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Application filed by Gft Gesellschaft fur Hydraulik-Technologie GbR filed Critical Gft Gesellschaft fur Hydraulik-Technologie GbR
Publication of EP0528103A1 publication Critical patent/EP0528103A1/fr
Application granted granted Critical
Publication of EP0528103B1 publication Critical patent/EP0528103B1/fr
Publication of EP0528103B2 publication Critical patent/EP0528103B2/fr
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Expired - Lifetime legal-status Critical Current

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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
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0435—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being sliding 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
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • 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
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot 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
    • 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
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0433—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being pressure control 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/16—Special measures for feedback, e.g. by a follow-up device

Definitions

  • the invention relates to an electro-hydraulic control unit, in particular for control of construction machinery, according to the generic part of the first claim.
  • an electro-hydraulic actuator is known, the one displaceable piston-like part, in particular has a control slide whose two end faces each have a control chamber arranged via control means can be pressurized or relieved of pressure to move the part is.
  • the control means is an electro-magnetic associated with each control chamber actuatable control valve, which is mechanically fed back to the control valve acts.
  • the mechanical feedback is designed as a spring that each on the mutually facing end faces of the movable part and Control valve supports. Further centering springs are provided for the piston-like part.
  • This control unit is intended to provide feedback for the position control of the displaceable Part can be achieved, the setting should be particularly accurate.
  • the Control valves are designed as 3/2-way valves.
  • a disadvantage of this control unit is that due to the interaction a pressure of the magnetic force and spring force is set on the valve (after which Current divider principle), which over the surface of the movable part as adjusting force works. It follows that the control pressure only with constant proportional magnetic force is still set depending on the spool position, i.e. there is one Slider position only one setting value. But since the disturbances occurring which occur in a wide range adjust the spool must be constant Magnetic force, the control pressure can be adjusted in a wide range to be able to position the piston correctly. In addition, this actuator unit efficiency is poor because the control oil volume flow requirement is high due to the flow divider function for control pressure generation, furthermore is a high one Control pressure is required as the main piston is moved against a spring. As a result of the constant pressure, there is a high loss of performance due to the circulating oil.
  • DE-C 28 35 771 shows a cartridge valve with a device its control by means of a hydraulic tracking system consisting of a Cartridge element for regulating a main flow valve flowing through hydraulic volume flow, with an inlet throttle between the flow Main power connection and the control side of the cartridge element and with one interacting via a linkage with an adjustable discharge throttle Pilot piston of a pilot valve and with a control valve for actuation of the pilot piston.
  • the control valve forms an independent control device to connect the incoming main power connection with the upper or Bottom of the pilot piston with a return line leading the pilot piston moved proportional to a control signal, the control device with a Connection via a pipe to the top or bottom of the pilot spool and with a further connection via a pipeline to the other side of the Pilot piston is connected.
  • a disadvantage of this design is that that only two positions can be brought about by this cartridge valve and a positioning of the main piston within the Housing is not feasible.
  • DE-A 28 30 332 is an electro-hydraulic valve unit, known according to the preamble of claim 1 with a proportional servo valve, one with this coupled directional control valve for control a working cylinder and with an electro-mechanical converter for generation a linearly dependent force for the adjustment of the electrical input signal of the servo valve is known, the directional control valve having a valve spindle, which is a neutral position, a first working position for connecting one Fluid pressure source with a chamber of the working cylinder and a second working position to connect this chamber to the sump.
  • the valve stem of the Directional control valve is coupled to the valve stem of the servo valve via a spring.
  • a second spring On the other side of the valve stem of the servo valve is a second spring arranged and counteracts the first spring.
  • the spring constant of the second Spring is larger than that of the first, the second spring being arranged so that in de-energized state of the electro-mechanical converter the valve spindle of the servo valve is in its neutral position.
  • the spring constant of the second spring can be here be greater by a factor of 5-12 than the spring constant of the first spring.
  • the change in force of the magnetic core with respect to the change in Position of the same is always smaller than the combined spring constants of the compression springs, so that the magnet, when excited, does not move to its maximum position can move.
  • a variety of different spring constants are used having springs, so that one of disturbances of individual or all springs independent positioning of the main piston within the housing is not can be realized.
  • the object of the invention is the further development of the generic electrohydraulic Actuator in that a closed position control loop is formed is the, even with occurring disturbances such as flow forces, pressure changes and the like. With high setting accuracy or reproducibility of position and speed of the components to be controlled can be maintained.
  • the field of application of the subject matter of the invention essentially relates to control of hydraulic cylinders and hydraulic motors in the stationary industrial sector, whereby a preferred area of application is formed by the mobile construction machinery area becomes.
  • FIG. 2 shows a schematic diagram of the electro-hydraulic actuating unit according to the invention, which essentially contains the following components: a longitudinally movable main piston 2 within a housing 1, a pilot valve 3 together with piston 4, electromagnets 5, 6 and a spiral spring 7 (can also be a different type of spring) as a displacement-force converter.
  • the pilot valve 3 is a directionally proportional 4/3 valve. Through the electronic control of the magnet 6, for example, the valve 3 opens the connection P to A and B to T.
  • the piston 4 moves in the direction of the main piston 2 and the control oil flows into the control chamber 8 and moves the main piston 2 in the direction of the piston 4.
  • the main piston 2 is connected via the spiral spring 7 designed as a compression spring to the piston 4 of the pilot valve 3, in such a way that it is attached to the mutually facing end faces 9, 10 of the two pistons 2, 4.
  • the main piston 2 is adjusted until the compression spring 7 has adjusted due to its characteristic curve so that the spring force of the compression spring 7 and the magnetic force of the magnet 6 are in equilibrium. This means that the main piston 2 closes the piston 4 of the pilot valve 3 via the compression spring 7. Any positive or negative positional deviation of the main piston 2 causes a force imbalance between the compression spring 7 and the electronic magnetic force, so that the piston 4 moves into the control position until the main piston 2 is positioned again.

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

Claims (5)

  1. Dispositif de commande électro-hydraulique, destiné en particulier au réglage d'engins de chantier, comportant un piston principal mobile, sur les côtés frontaux duquel sont prévues des chambres de réglage qui peuvent être soumises à ou libérées d'une charge à l'aide de moyens à air comprimé, par l'intermédiaire de moyens de réglage actionnés électro-magnétiquement, un seul moyen de réglage (3), pouvant être actionné à l'aide de deux électroaimants (5, 6),sous la forme d'une soupape-pilote (3) qui est agencée en série avec le piston principal (2), ainsi que par au moins un convertisseur déplacement-force (7) qui est en liaison active avec le piston principal (2) et le piston (4) de la soupape-pilote (3), la mise en action d'un des électro-aimants (5 ou 6) par l'intermédiaire de la soupapepilote (3) faisant couler de l'huile de réglage dans la chambre de réglage (8 ou 11) associée, caractérisé en ce que la soupape-pilote (3) est un distributeur proportionnel, en ce que le convertisseur déplacement-force (7) est relié aux côtés frontaux (9, 10), tournés l'un vers l'autre, du piston principal (2) ainsi que du piston (4) de la soupape-pilote (3) et, le piston principal (2), dans la direction correspondante (s) et le piston (4) de la soupape-pilote (3), par l'intermédiaire du convertisseur déplacement-force (7), grâce au piston principal (2), étant déplacés aussi longtemps que l'élasticité du convertisseur déplacementforce (7) et la force magnétique sont en équilibre, une régulation en boucle fermée étant formée indépendamment des perturbations de telle sorte que, pour chaque écart de position du piston principal (2) s'établisse un déséquilibre de forces, entre l'élasticité du convertisseur déplacementforce (7) relié aux pistons (2, 4) et la force électromagnétique de l'aimant, le piston (4) allant dans la position de réglage jusqu'à ce que le piston principal (2) soit de nouveau positionné indépendamment des perturbations.
  2. Dispositif de commande électro-hydraulique selon la revendication 1, caractérisé en ce que le convertisseur déplacement-force (7) relié aux pistons (2, 4) est formé comme un ressort spiral.
  3. Dispositif de commande électro-hydraulique selon la revendication 2, caractérisé en ce que le ressort spiral (7) est un ressort de pression.
  4. Dispositif de commande électro-hydraulique selon la revendication 2, caractérisé en ce que le ressort spiral (7) est un ressort combiné de pression/de traction.
  5. Dispositif de commande électro-hydraulique selon la revendication 2, caractérisé en ce que le convertisseur déplacement-force (7) relié aux pistons (2, 4) est formé comme un ressort à disques.
EP92104566A 1991-07-20 1992-03-17 Dispositif de commande électro-hydraulique Expired - Lifetime EP0528103B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4124140 1991-07-20
DE4124140A DE4124140C2 (de) 1991-07-20 1991-07-20 Einrichtung zur lagegerechten Positionierung des Hauptkolbens einer elektro-hydraulischen Stelleinheit

Publications (3)

Publication Number Publication Date
EP0528103A1 EP0528103A1 (fr) 1993-02-24
EP0528103B1 EP0528103B1 (fr) 1995-10-11
EP0528103B2 true EP0528103B2 (fr) 2000-06-28

Family

ID=6436652

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92104566A Expired - Lifetime EP0528103B2 (fr) 1991-07-20 1992-03-17 Dispositif de commande électro-hydraulique

Country Status (2)

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EP (1) EP0528103B2 (fr)
DE (2) DE4124140C2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4302130C2 (de) * 1993-01-27 1995-04-13 Orenstein & Koppel Ag Elektro-hydraulische Stelleinheit
US5921279A (en) * 1998-04-29 1999-07-13 Husco International, Inc. Solenoid operated dual spool control valve
DE19823529A1 (de) * 1998-05-26 1999-12-09 Mannesmann Rexroth Ag Wegbestimmungssystem

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3783901A (en) † 1972-03-20 1974-01-08 Bosch Gmbh Robert Electro hydraulic control unit
DE2830332A1 (de) † 1977-07-11 1979-01-25 Cessna Aircraft Co Elektro-hydraulische ventileinheit

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2835771A1 (de) * 1978-08-16 1980-02-28 Schwelm & Towler Hydraulics Anordnung zur aussteuerung eines cartridgeelementes
DE3125386A1 (de) * 1981-06-27 1983-01-13 Robert Bosch Gmbh, 7000 Stuttgart Elektro-hydraulische stelleinrichtung insbesondere zur fernsteuerung eines wegeventils
DE3527026A1 (de) * 1985-07-27 1987-01-29 Bosch Gmbh Robert Elektrohydraulische stelleinheit

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3783901A (en) † 1972-03-20 1974-01-08 Bosch Gmbh Robert Electro hydraulic control unit
DE2830332A1 (de) † 1977-07-11 1979-01-25 Cessna Aircraft Co Elektro-hydraulische ventileinheit

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Prospect Nr. 625 D 1.80 der Firma MOOG GmbH mit der Titel: "Servoverstellgeräte für Verstellpumpen und Verstellmotoren" †

Also Published As

Publication number Publication date
DE4124140C2 (de) 1995-04-13
DE4124140A1 (de) 1993-01-21
DE59203972D1 (de) 1995-11-16
EP0528103A1 (fr) 1993-02-24
EP0528103B1 (fr) 1995-10-11

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