EP0628731B1 - Servo-soupape asservie - Google Patents

Servo-soupape asservie Download PDF

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Publication number
EP0628731B1
EP0628731B1 EP94107440A EP94107440A EP0628731B1 EP 0628731 B1 EP0628731 B1 EP 0628731B1 EP 94107440 A EP94107440 A EP 94107440A EP 94107440 A EP94107440 A EP 94107440A EP 0628731 B1 EP0628731 B1 EP 0628731B1
Authority
EP
European Patent Office
Prior art keywords
pilot
main control
piston
control piston
valve
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
EP94107440A
Other languages
German (de)
English (en)
Other versions
EP0628731A1 (fr
Inventor
Arsène Bourkel
Bernd Lanfermann
Karl Tratberger
Karl-Heinz Post
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.)
Hydrolux SARL
Original Assignee
Hydrolux SARL
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Filing date
Publication date
Application filed by Hydrolux SARL filed Critical Hydrolux SARL
Publication of EP0628731A1 publication Critical patent/EP0628731A1/fr
Application granted granted Critical
Publication of EP0628731B1 publication Critical patent/EP0628731B1/fr
Anticipated expiration legal-status Critical
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
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/002—Electrical failure
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F2007/1684—Armature position measurement using coils
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86606—Common to plural valve motor chambers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/86702—With internal flow passage

Definitions

  • the invention relates to a pilot operated servo valve with at least three main power connections.
  • Pilot operated electrohydraulic servo valves in two and multi-stage version with more than two Main power connections e.g. as 4-way valves, for Control of position, speed, power at Cylinders for linear movements or position, Speed and torque for hydraulic motors for Rotational movements, each of two displacement chambers have used.
  • These 4-way servo valves are conventional Design as a panel valve.
  • a The main spool of the main stage is directly in a valve housing or in one used in the housing Control sleeve fitted.
  • the confluence of the Main power connections are symmetrical with respect to the also formed symmetrical main control piston.
  • the hydraulic actuation of the main control piston takes place doing so by pressurizing its two end faces in Control chambers, which are on both sides of the valve housing flanged end caps are arranged.
  • This Control chambers are with control bores with a Pilot servo valve connected. Return springs are for Centering of the main spool provided.
  • Valves for block installation are available in various designs known. There are also servo valves with large ones Flow for block installation, however, these have only 2 Main power connections and are designed as seat valves. Screw-in block built-in valves are included in the mobile area 4 main power connections known, but as switching Directional valves are designed with direct solenoid actuation.
  • Valves of this type are, for example, in the book "The Hydraulic Trainer / Volume 2: Proportional and Servo valve technology ", publisher Mannesmann Rexroth GmbH (Germany), ISBN 3-8023-0266-4. At these valves is the valve body as a valve block for Build on a flat pad Hydraulic blocks trained. They all have one symmetrical main spool on its two End faces are arranged in control chambers. Return springs cause centering of the Main control piston.
  • the invention is based on the object pilot operated servo valve of the type described above create which saves space in a control block can be integrated and a clearly defined Has security position without losing out on a good one dynamic behavior of the servo valve to do without have to.
  • the pilot operated servo valve according to the invention is with its control sleeve directly into a stepped bore Control blocks used.
  • This control block then points side block holes for the second, third and everyone another main power connection.
  • This block hole for the first main power connection can, for example, directly in axial extension of the stepped bore for the control sleeve be carried out what with conventional piloted Servo valves with more than two main connections so far not possible. Bridge formation in the control block between individual junctions in the control sleeve are also no longer required.
  • inventive Servo valve is thus a much more compact design Control blocks achieved than with conventional ones Servo valves is the case.
  • Even in more complex ones Hydraulic controls can do the inventive Servo valve together with various additional valves, for example 2-way cartridge valves in a control block can be integrated to save space.
  • a direct installation in the The cylinder cover of larger cylinders is also possible.
  • the asymmetrical hydrostatic load on the main control piston appropriate dimensioning of the pressure compensation area of the Main control piston compensated.
  • hydrostatic Compensation will be the required actuation forces for the main spool, reducing the Operating areas in the control chambers are designed to be smaller can be. This results in smaller ones Tax oil volumes, that is, with the same size Pilot valve shorter positioning times can be achieved.
  • the second End of the main control piston axially sealed in the Pressure equalization chamber introduced to the Pressure compensation area as the second piston face to train.
  • This embodiment allows a more compact one Design of the valve than this with an annular Pressure equalization area is possible. The latter embodiment is not excluded, however.
  • a hydrostatic overcompensation of the servo valve is achieved when the axially effective area of the Pressure compensation area larger than the axially effective area the first piston face.
  • the pump connection (P) be axially inserted into the control sleeve; of the Tank connection (T) is between the first and second working connection.
  • Other assignments of the Main power connections are also possible without to the most important advantages of the invention To waive the servo valve.
  • the four control edges of the main spool point preferably a zero coverage.
  • the working connection (A) is therefore in the first End position of the main spool with the Tank connection (T) connected during the Working connection (B) via the pressure chamber with the Pump connection (P) is connected.
  • the second working connection (B) to the pump connection (P) blocked.
  • the Main control piston on a first auxiliary control edge which is assigned to the third and fourth control edge in such a way that in the first axial end position of the Main control piston the fourth axial hydraulic Axially closes the connection.
  • the third and fourth Control edges are then, for example, arranged in such a way that at the first axial end position of the main control piston the third axial hydraulic connection between Tank connection (T) and second working connection (B) is released.
  • the Servo valves become the first working port (A) and the second working connection (B) in the first end position of the Main control piston for pump connection (P) and Tank connection (T) blocked.
  • the main spool has first and second Auxiliary control edge on.
  • the first auxiliary control edge is the assigned third and fourth control edge such that they in the first axial end position of the main control piston fourth axial hydraulic connection closes.
  • the second auxiliary control edge is the first and second Control edge assigned such that it is axial at first End position of the main spool is the second axial hydraulic connection closes.
  • the first and second Control edges are arranged such that the first axial end position of the main spool, the first axial hydraulic connection between pump connection (P) and the first working connection (A) is closed.
  • the the third and fourth control edges are such arranged that in the first axial end position of the Main control piston the third axial hydraulic Connection between tank connection (T) and second Work port (B) is closed.
  • Unlock valve enables when it is relieved in a spring-centered basic position, for example with one Emergency stop or error signal that the main spool by the return spring, respectively by additional hydraulic pressure forces in its first axial end position is operated.
  • a hydraulic cylinder through Blocking of the work connections stopped, or by Connect the work connections to the tank without pressure be switched. This can lead to uncontrolled driving in an end position of the cylinder when errors are detected in the control electronics, machine control or even in Pilot valve itself can be avoided.
  • Valve versions also with a 3-way pilot valve enable the second control chamber with which in Direction of the first end position acting second Actuating area, with an always depressurized Tank line (Y) directly hydraulically connected.
  • the first control chamber with the opposite direction the first actuating surface acting the first end position, on the other hand with the working connection of the 3-way pilot valve hydraulically connected.
  • the main spool position sensor is in a first embodiment as a distance measuring system electrical output executed and in a closed Control loop integrated with the pilot valve.
  • the servo valve can also be used with mechanical Return.
  • a 3-way pilot spool valve in axial Extension of the second end of the main spool arranged which has a pilot pressure connection (P '), a pilot tank connection (T '), a pilot work connection (A ') and has a piston valve.
  • a measuring spring connects the pilot spool valve axially with the main spool, and one proportional to one electrical signal acting, control magnet is mechanical connected to the pilot spool.
  • the main spool is thus positioned in a closed position control loop up to Balance of forces between magnetic and measuring spring force is reached.
  • the pilot pressure connection (P ') is via the isolation valve with the pilot tank connection (T ') directly hydraulically connected, and the pilot valve is designed so that the Pilot work connection (A '), depending on the position of the Pilot spool, either with the pilot tank connection (T ') or the pilot pump connection (P') is directly connected hydraulically.
  • the main control piston drives the release valve as described in its first axial end position.
  • Figure 1 shows a longitudinal section through a first Version of the servo valve 3.
  • a control sleeve 5 is in a stepped bore 2 of a control block 1 is used.
  • a main control piston 6 axially slidably fitted.
  • the one shown in the figures Servo valve 3 is a 4-way servo valve and has one Pump connection (P), a tank connection (T), and one first working connection (A) and a second Working connection (B).
  • the pump connection (P) is hydraulic Connection to a pressure line (not shown). Of the Tank connection (T) is in hydraulic connection with a unpressurized line (not shown).
  • the Work ports (A) and (B) are hydraulic Connection with a first or second Displacement chamber of a hydraulic linear or Rotary drive (not shown).
  • a first control block bore 50 for the Pump connection (P) ends in a coaxial extension of the Stepped bore 2 in the control sleeve 5.
  • Three Block bores 51, 52, 53 for the tank connection (T) 51, first working port (A) 52 and the second Working connection (B) 53 are across the stepped bore 2 arranged and open laterally in the control sleeve 5. You form axially spaced annular openings 51 ', 52', 53 ', with corresponding Cross bores in the control sleeve 5.
  • control sleeve 5 connects a first axial hydraulic connection 28 the mouth 50 'for the Pump connection (P) with the mouth 52 'for the Working connection (A); a second axial hydraulic Connection 29 the mouth 51 'for the tank connection (T) with the mouth 52 'for the working connection (A); a third axial hydraulic connection 30 the junction 51 ' for the tank connection (T) with the mouth 53 'for the Working connection (B); and a fourth axial hydraulic Connection 31 the junction 53 'for the Working connection (B) with a coaxial inside the Control sleeve 5 arranged auxiliary connection chamber 22.
  • the main control piston 6 has a first coaxial Piston collar 8 on which the working connection (A) is assigned and axially in the first and second axial hydraulic connection 28 and 29 is displaceable, and a second coaxial piston collar 9, which the Working connection (B) is assigned and axially in the third and fourth axial hydraulic link 30 and 31 is slidable.
  • the first piston collar 8 forms one assigned to the first hydraulic connection 28 first control edge 28 'and one, the second hydraulic connection 29 assigned second Control edge 29 '. Both control edges 28 ', 29' point a zero coverage.
  • the second piston collar 9 forms one assigned to the third hydraulic connection 30 third control edge 30 'and one, the fourth hydraulic connection 31 assigned fourth Control edge 31 '. Both control edges 30 ', 31' point also a zero coverage.
  • auxiliary connection chamber 22 Via an axial piston bore 18 and a Piston transverse bore 19 is through the auxiliary connection chamber 22 the main control piston 6 with the pump connection (P) connected.
  • the main control piston therefore connects with its coaxial piston collar 8 the first Working connection (A) and with its coaxial piston collar 9 the second working connection (B) alternately with the Pump connection (P) or the tank connection (T), the respective flow of hydraulic fluid over the four Control edges 28 ', 29', 30 ', 31' is regulated.
  • the main control piston 6 is hydrostatically asymmetrical charged.
  • a hydrostatic pressure equalization of the Main control piston is carried out by continuing the coaxial piston bore 18 to the second end of the Main control piston 6, where it has a piston cross bore 20 opens into a pressure compensation chamber 25 which in one Valve cover 40 is arranged.
  • the second end of the Main spool is axially sealed by a Sealing insert 7, in this pressure compensation chamber 25 introduced and forms a pressure equalization approach 21.
  • This has one of the pressure equalization chamber 25 first piston face 12 hydrostatically counteracting Pressure equalization surface 13.
  • a complete one hydrostatic pressure equalization results when the Pressure compensation surface 13 is equal to the piston end surface 12 is chosen.
  • a hydrostatic overcompensation will occur reached when the pressure equalization surface 13 is larger than that Piston face 12 is selected.
  • the main control piston 6 is actuated via a machined coaxial actuating piston collar 11 by pressurizing its annular first or second actuating surface 14, 15.
  • the latter are in a first and second control chamber 26 and 27 arranged in the valve cover 40, where they over Pilot connections 56, 57 with the working connections (A ') and (B ') a flanged 4-way pilot servo valve 60 are connected.
  • Pilot connections 56, 57 with the working connections (A ') and (B ') a flanged 4-way pilot servo valve 60 are connected.
  • the actuating ring surfaces 14, 15 are just as large designed that when the control edges 28 ', 30 ', or 29', 31 'generated flow forces safely be overcome. This allows very short Positioning times for positioning the main control piston 6 at reach the specified pilot control valve 60.
  • the pressure equalization approach 21 enlarged in diameter so that the Pressure compensation area 13 larger than that Piston end face 12, this causes one Overcompensation with an additional hydrostatic Force to reset the main spool 6 in the first end position.
  • release valve 62 is in its spring-centered basic position (i.e. not actuated magnet), the control chamber (A ') 26 with the Operating area (A ') 14 relieved to the tank.
  • the 4-way pilot control valve Main control piston 6 in the first end position. Only at; only when Actuation of the release valve 62 becomes the 4-way pilot servo valve 60 for positioning the Main control piston 6 effective.
  • the positioning of the Main spool 6 also with a simplified 3-way pilot valve 61 can be performed (see Figure 5). It has a pilot pump connection (P '), one Pilot tank connection (T ') and a control connection (A') on.
  • the pilot pump connection (P ') is via the Control pressure line (X) pressurized.
  • the pre-tax tank connection (T ') is with an unpressurized Control line (Y) connected.
  • the control connection (A ') is via a release valve 62 with the first control chamber 26 connected.
  • the control chamber 27 with the actuating surface 15 which, by the above-described enlargement of the Pressure compensation area 13, smaller than that Actuating surface 14 of the control chamber 26 is permanent Relieved to the tank via the unpressurized control line (Y) 54.
  • the uncontrolled 3-way pilot valve 61 the Main control piston 6 in the rest position while at electrical control by pressurizing the larger actuation area 14 compared to the tank-relieved actuating surface 15 a hydraulic Control force arises, the main control piston 6, in the already described type, in electro-hydraulic Position control loop positioned. To do this, however Unlock valve 62 may be actuated. With discharge of the Isolation valve 62 in its basic position, e.g. as a result of an error that has occurred, the control chamber 26 relieved to the tank again, so that independent of the 3-way pilot valve 61, through the hydrostatic Overcompensation and by the return spring 24, the Main control piston 6 moves to the first end position.
  • Unlocking valve 62 does not require, this can also omitted, in which case the control chamber 26 directly with the Control port (A ') of 3-way pilot valve 61 connected is.
  • a Piston spool valve 67 in 3-way version is axial Extension of the main control piston 6 arranged. It points a pilot pump port (P ') 58, a pilot tank port (T ') 59, a control connection (A') 56 and a piston slide 68. The latter supports itself one end on a spring plate 69 in the Pressure compensation chamber 25 and is at its second end connected to a proportional magnet 66.
  • a Measuring spring 65 is in the pressure compensation chamber 25 between Spring plate 69 and main control piston 6 arranged.
  • Piston spool 68 is for the purpose of hydrostatic Pressure equalization, axially pierced. Independent of The position of the spool 68 is the control connection always with the pilot pump connection (P ') or the Pilot tank connection (T ') connected. Of the main control piston 6 is designed as in FIGS. 4 and 5 and thus has identical properties.
  • pilot pump connection (P ') 58' is additional a release valve 62 is arranged in the pilot pump connection (P ') 58'. With its electrical The pilot pump connection is relieved to the basic position (P ') 58 connected to the tank. Independently from the position of the pilot valve 67 is the Actuating surface (A ') 14 is therefore always depressurized to the tank relieved, whereby the main control piston 6 again by the hydrostatic overcompensation and the return spring 24 is operated in the first end position.

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

Claims (14)

  1. Servo-soupape à commande pilote comprenant :
    un piston de commande principal (6) avec une première extrémité et une deuxième extrémité ;
    un corps de soupape (5) dans lequel est disposé le piston de commande principal (6) de façon axialement mobile,
    des embouchures (50', 51', 52', 53') pour au moins trois raccords principaux (50, 51, 52, 53), disposées avec écartement axial dans le corps de soupape (5);
    une première communication hydraulique axiale (28) située à l'intérieur du corps de soupape (5) entre l'embouchure (50') du premier raccord principal (50) et l'embouchure (52') du deuxième raccord principal (52) ;
    une deuxième communication hydraulique axiale (29) située à l'intérieur du corps de soupape (5) entre l'embouchure (52') du deuxième raccord principal (52) et l'embouchure (51') du troisième raccord principal (51) ;
    une première arête de commande (28') du piston de commande principal (6), associée à la première communication hydraulique axiale (28),
    une deuxième arête de commande (29') du piston de commande principal (6), associée à la deuxième communication hydraulique axiale (29),
    une première chambre de commande (26) dans laquelle le piston de commande principal (6) présente une première surface d'actionnement (14) ; une deuxième chambre de commande (27) dans laquelle le piston de commande principal (6) présente une deuxième surface d'actionnement (15), agissant axialement en sens inverse de la première surface d'actionnement (14) ;
    une soupape pilote (60, 67) reliée hydrauliquement à au moins une des deux chambres de commande (26, 27) ; et
    un circuit d'asservissement entre le piston de commande principal (6) et la soupape pilote (60, 67) dans lequel est intégré un capteur de positionnement (65, 66) du piston de commande principal (6) ;
    caractérisée en ce que le corps de soupape se présente sous forme d'un manchon de commande (5) dans lequel l'embouchure (50') du premier raccord principal (50) est formée dans la première extrémité du piston de commande principal (6) en face d'une surface frontale du piston (12), et les embouchures (51', 52', 53') du deuxième, du troisième et de chaque autre raccord principal (51, 52, 53) sont disposées latéralement au piston de commande principal (6), en ce que le piston de commande principal présente dans une chambre de compensation de pression (25) une surface de compensation de pression du piston (13) agissant hydrostatiquement en sens inverse de la surface frontale du piston (12), la chambre de compensation de pression (25) étant reliée hydrauliquement par un canal de décharge de pression (18, 20), situé dans le piston de commande principal (6), au premier raccord principal (50), et
    en ce que le piston de commande principal (6) constitue une surface de butée (16), qui détermine mécaniquement une première position finale axiale du piston de commande principal (6) par interaction avec une surface correspondante de contre-butée (16'), un ressort de rappel (24) étant associé au piston de commande principal (6) de sorte qu'il exerce sur ce dernier une force de rappel dans le sens de sa première position finale axiale.
  2. Servo-soupape à commande pilote selon la revendication 1, caractérisée par
    une embouchure latérale (53') d'un quatrième raccord principal (53), dans le manchon de commande (5),,
    une chambre de raccord auxiliaire (22) reliée par un alésage transversal (19) du piston de commande principal (6) au canal de compensation de pression (18) du piston de commande principal (6),
    une troisième communication hydraulique axiale (30) située à l'intérieur du manchon de commande (5) entre l'embouchure (51') du troisième raccord principal (51) et l'embouchure (53') du quatrième raccord principal (53),
    une quatrième communication hydraulique axiale (31) située à l'intérieur du manchon de commande (5) entre l'embouchure du quatrième raccord principal (53) et la chambre de raccord auxiliaire (22),
    une troisième arête de commande (30') du piston de commande principal (6) associée à la troisième communication hydraulique axiale (30), et
    une quatrième arête de commande (31') du piston de commande principal (6) associée à la quatrième communication hydraulique axiale (31).
  3. Servo-soupape à commande pilote selon la revendication 1 ou 2, caractérisée en ce que la deuxième extrémité du piston de commande principal (6) est guidée de façon axialement étanche dans la chambre de compensation de pression (25) pour y constituer la surface de compensation de pression (13) en tant que deuxième surface frontale du piston.
  4. Servo-soupape à commande pilote selon l'une des revendications 1 à 3, caractérisée en ce que la surface active axialement de la surface de compensation de pression (13) est plus grande que la surface active axialement de la première face frontale du piston (12).
  5. Servo-soupape à commande pilote selon l'une des revendications 1 à 4, caractérisée en ce que le premier raccord principal (50) est relié hydrauliquement à une pompe et constitue ainsi un raccord de pompe,
    en ce que le deuxième raccord principal (52) est relié hydrauliquement à une première chambre de refoulement d'un consommateur et constitue ainsi un premier raccord de travail (A), et
    en ce que le troisième raccord principal (51) est relié hydrauliquement à un réservoir sans pression et constitue ainsi un raccord de réservoir (T).
  6. Servo-soupape à commande pilote selon la revendication 2 et la revendication 5, caractérisée en ce que le quatrième raccord principal (53) est relié hydrauliquement à une deuxième chambre de refoulement d'un consommateur et constitue ainsi un deuxième raccord de travail (B).
  7. Servo-soupape à commande pilote selon l'une des revendications 2, 3, 4 ou 6, caractérisée en ce que les quatre arêtes de commande du piston de commande principal (6) présentent un recouvrement nul, et
    en ce que dans la première position finale axiale du piston de commande principal,
    la première communication hydraulique axiale (28) est obturée par la première et / ou la deuxième arête de commande (28', 29') ,
    la deuxième communication hydraulique axiale (29) est débloquée,
    la troisième communication hydraulique axiale (30) est obturée par la troisième et / ou la quatrième arête de commande (30', 31'),
    la quatrième communication hydraulique axiale (31) est débloquée.
  8. Servo-soupape à commande pilote selon l'une des revendications 2 à 7, caractérisée en ce que la première et la deuxième arête de commande (28', 29') sont disposées de telle sorte qu'en première position finale axiale du piston de commande principal (6), au moins l'une de celles-ci obture la première communication hydraulique axiale (28),
    en ce que la troisième et la quatrième arête de commande (30', 31') sont disposées de telle sorte qu'en première position finale axiale du piston de commande principal (6), au moins l'une de celles-ci obture la troisième communication hydraulique axiale (30),
    en ce qu'une première arête de commande auxiliaire (32') est disposée de telle sorte qu'en première position finale axiale du piston de commande principal (6), elle obture la quatrième communication hydraulique axiale (31) et
    en ce qu'en première position finale axiale du piston de commande principal (6), une deuxième arête de commande auxiliaire (33') est disposée de telle sorte qu'elle obture la deuxième communication hydraulique axiale (29).
  9. Servo-soupape à commande pilote selon l'une des revendications 2 à 7, caractérisée en ce que la première et la deuxième arête de commande (28', 29') sont disposées de telle sorte qu'en première position finale axiale du piston de commande principal (6) au moins l'une de celles-ci obture la première communication hydraulique axiale (28),
    la troisième et la quatrième arête de commande (30', 31') sont disposées de telle sorte, qu'en première position finale axiale du piston de commande principal (6), la troisième communication hydraulique axiale (30) est débloquée,
    en ce qu'une arête de commande auxiliaire (32') est disposée de telle sorte qu'elle obture la quatrième communication hydraulique axiale (31) en première position finale axiale du piston de commande principal (6).
  10. Servo-soupape à commande pilote selon l'une des revendications 6 à 9, caractérisée en ce qu'entre la première chambre de commande (26), avec la première surface d'actionnement (14) agissant en sens inverse de la première position finale axiale, et la soupape pilote (60) est montée une soupape de déconnexion (62), et
    en ce que cette soupape de déconnexion (62) dans sa position initiale relie hydrauliquement la première chambre de commande (26) à une conduite de commande sans pression (Y) (54).
  11. Servo-soupape à commande pilote selon l'une des revendications 6 à 9, caractérisée en ce que la deuxième chambre de commande (27), avec la deuxième surface d'actionnement (15) agissant dans le sens de la première position finale, est reliée hydrauliquement directement à une conduite de commande sans pression (Y) (54), et
    en ce que la première chambre de commande (26), avec la première surface d'actionnement (14) agissant dans le sens inverse de la première position finale, est reliée hydrauliquement à un raccord de commande (A') de la soupape pilote, cette dernière étant une soupape pilote à 3 voies (61).
  12. Servo-soupape à commande pilote selon la revendication 11, caractérisée en ce que le capteur de position du piston de commande principal (6) est exécuté en tant que système de mesure de déplacement (63) avec sortie électrique et est intégré avec la soupape pilote à 3 voies (61) dans un circuit d'asservissement fermé.
  13. Servo-soupape à commande pilote selon la revendication 11, caractérisée en ce que la soupape pilote est une soupape pilote à tiroir à 3 voies (67) dans le prolongement axial de la deuxième extrémité du piston de commande principal (6), qui présente un raccord pilote de pression (P') (58), un raccord pilote de réservoir (T') (59), un raccord pilote de travail (A') (56) et un piston pilote (68),
    en ce qu'un ressort de mesure (65) relie le piston pilote (68) axialement au piston de commande principal (6), et
    en ce qu'un électro-aimant de réglage (66), agissant proportionnellement à un signal électrique est relié mécaniquement au piston pilote.
  14. Servo-soupape à commande pilote selon la revendication 13, caractérisée en ce que
    le raccord de pression pilote (P') (58) est relié hydrauliquement au raccord de réservoir pilote (T') (59) par une soupape de déconnexion (62), dans la position de repos de celle-ci, et
    en ce que la soupape pilote à tiroir (67) est configurée de telle sorte que le raccord de commande (A') (56), selon la position du piston pilote (68), est relié hydrauliquement directement soit au raccord pilote de réservoir (T') (59), soit au raccord pilote de pompe (P') (58).
EP94107440A 1993-05-27 1994-05-13 Servo-soupape asservie Expired - Lifetime EP0628731B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
LU88277A LU88277A1 (de) 1993-05-27 1993-05-27 Vorgesteuertes Servoventil
LU88277 1993-05-27

Publications (2)

Publication Number Publication Date
EP0628731A1 EP0628731A1 (fr) 1994-12-14
EP0628731B1 true EP0628731B1 (fr) 1998-07-15

Family

ID=19731408

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94107440A Expired - Lifetime EP0628731B1 (fr) 1993-05-27 1994-05-13 Servo-soupape asservie

Country Status (9)

Country Link
US (1) US5445188A (fr)
EP (1) EP0628731B1 (fr)
JP (1) JP3519122B2 (fr)
CN (1) CN1041344C (fr)
AT (1) ATE168450T1 (fr)
CA (1) CA2124429C (fr)
DE (1) DE59406438D1 (fr)
LU (1) LU88277A1 (fr)
RU (1) RU2124666C1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005003659A1 (de) * 2005-01-26 2006-07-27 Bosch Rexroth Aktiengesellschaft Wegeventilanordnung und Kraftstoffeinspritzsystem

Families Citing this family (42)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4330073A1 (de) * 1993-09-06 1995-03-09 Frutigen Hydrotechnik Ag Vorgesteuertes Hydraulikventil
LU88558A1 (de) * 1994-11-16 1996-07-15 Hydrolux Sarl Vorgesteuertes Servoventil
DE19856563A1 (de) 1998-12-08 2000-06-15 Mannesmann Rexroth Ag Wegeventil
DE10041386B4 (de) * 2000-08-23 2008-08-21 Daimler Ag System zur Wirkungsgradoptimierung einer Ölversorgung
US6554014B2 (en) * 2000-10-13 2003-04-29 Hydraforce, Inc. Proportional pilot operated directional valve
US6789570B2 (en) 2001-04-23 2004-09-14 Hydraforce, Inc. Hydraulic valve with a position sensor
GB2378744A (en) * 2001-08-13 2003-02-19 Abb Offshore Systems Ltd Control valves
US6725876B2 (en) * 2001-10-15 2004-04-27 Woodward Governor Company Control valve with integrated electro-hydraulic actuator
FR2868145B1 (fr) * 2004-03-26 2006-06-30 Air Liquide Valve de distribution de fluide et utilisation pour la fourniture d'air enrichi aux occupants d'un aeronef
US7066710B2 (en) * 2004-05-27 2006-06-27 Honeywell International, Inc. Pneumatic valve control having improved opening characteristics and an air turbine starter incorporating the same
US7147430B2 (en) * 2004-06-10 2006-12-12 Honeywell International, Inc. Pneumatic valve control using downstream pressure feedback and an air turbine starter incorporating the same
DE102005056167A1 (de) * 2004-12-27 2006-07-13 Continental Teves Ag & Co. Ohg Fahrzeuglenkung und Verfahren zur Regelung einer Fahrzeuglenkung
DE102005006321A1 (de) * 2005-02-11 2006-08-17 Hydac Fluidtechnik Gmbh Ventil, insbesondere Proportinal-Druckbegrenzungsventil
US20080224353A1 (en) * 2007-03-14 2008-09-18 Husky Injection Molding Systems Ltd. Hydraulic Valve of Molding System
US8602060B2 (en) 2008-09-22 2013-12-10 GM Global Technology Operations LLC Multiplexing control valve
CN101598151B (zh) * 2009-06-03 2011-10-26 北京航空航天大学 一种螺旋全桥先导级结构
FR2950124B1 (fr) * 2009-09-17 2011-12-09 Johnson Controls Neige Vanne pour la distribution d'eau et d'air dans les installations de pulverisation d'eau sous pression
CN101806314B (zh) * 2010-04-09 2012-12-05 北京航空航天大学 一种液压螺旋半桥先导级结构
JP5080612B2 (ja) * 2010-05-17 2012-11-21 株式会社鷺宮製作所 流路切換弁
CN102162475B (zh) * 2011-04-13 2015-08-19 重庆大学 一种具有感知功能的压力控制阀
DE102012010522A1 (de) * 2012-05-25 2013-11-28 Hydac Fluidtechnik Gmbh Ventil für Ventilanordnung
DE102013014558A1 (de) * 2013-08-31 2015-03-05 Hydac Fluidtechnik Gmbh Ventil nebst seiner Verwendung für eine Kupplung
DE102013015481A1 (de) * 2013-09-16 2015-03-19 Hydac Fluidtechnik Gmbh Steuervorrichtung zum wahlweisen fluidischen Verbinden und Trennen von Fluid-Anschlussstellen
EP2966287B1 (fr) 2014-07-07 2019-08-28 Goodrich Actuation Systems Ltd. Commutateur à pression pour commande d'inverseur de poussée
US20160208702A1 (en) * 2015-01-19 2016-07-21 Hamilton Sundstrand Corporation Pneumatic actuator low flow servo valve
CN104776255A (zh) * 2015-03-30 2015-07-15 苏州固基电子科技有限公司 压力阀
JP6551740B2 (ja) * 2015-10-28 2019-07-31 Smc株式会社 流体制御弁
CN105546155B (zh) * 2016-01-22 2018-01-09 奉化鑫益气动工程有限公司 一种大流量两位四通阀
CN105546154B (zh) * 2016-01-22 2018-01-09 奉化鑫益气动工程有限公司 一种两位四通阀
CN108266562B (zh) * 2016-12-30 2019-04-12 华中科技大学 一种高压气体流量控制装置
CN107061810B (zh) * 2017-06-27 2023-03-21 眉山中车制动科技股份有限公司 一种具有最小工作压力的溢流式减压阀
DE102017219645A1 (de) 2017-11-06 2019-05-09 Zf Friedrichshafen Ag Ventil, Hydrauliksystem und Kraftfahrzeuggetriebe
RU2697298C2 (ru) * 2018-02-07 2019-08-13 СВМ Шульц Фервальтунгс-ГмбХ энд Ко. КГ Золотниковый клапан с каналом
JP7011526B2 (ja) * 2018-05-07 2022-01-26 川崎重工業株式会社 電磁流量制御弁
CN109372813B (zh) * 2018-11-30 2020-05-08 武汉船用机械有限责任公司 一种电液比例节流阀及其控制方法
US10662979B1 (en) * 2018-12-10 2020-05-26 Sun Hydraulics, Llc Proportional valve for fluid flow control and generation of load-sense signal
US10626892B1 (en) * 2018-12-10 2020-04-21 Sun Hydraulics, Llc Proportional valve for fluid flow control
CN109595358B (zh) * 2018-12-27 2020-11-10 刘永 一种安全型三通比例节流阀结构
CN110319067B (zh) * 2019-08-05 2024-03-22 安徽理工大学 一种基于双电机的比例流量控制和高速开关两用阀
CN110657267B (zh) * 2019-11-15 2021-02-02 临沂市宇顺机械有限公司 一种有溢流功能的卸荷阀
CN111022404B (zh) * 2019-12-16 2022-04-01 江苏汇智高端工程机械创新中心有限公司 换向阀、液压系统以及工程机械
CN111894924B (zh) * 2020-06-19 2022-05-24 太原理工大学 手自一体控制的高水基高压大流量数字比例方向阀

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3010438A (en) * 1957-05-27 1961-11-28 Fife Pneumatic control valve for hydraulic system
US3234968A (en) * 1962-12-21 1966-02-15 White Sales Corp Graham Master and slave valve assembly
US3215163A (en) * 1964-06-23 1965-11-02 Republic Mfg Company Two-position, four-way pilot operated valve
DE2051582A1 (de) * 1970-10-21 1972-07-06 Schneider Co Optische Werke Folgekolbenventil
DE3532237C2 (de) * 1985-09-10 1994-01-20 Rexroth Mannesmann Gmbh Wegeschieberventil mit einem elektrischen Aufnehmer
DE3869407D1 (de) * 1988-01-25 1992-04-23 Moog Inc Servoventil mit integrierter sicherheit und leckregelung in aeusserster stellung.
DE3805288A1 (de) * 1988-02-19 1989-08-31 Rexroth Mannesmann Gmbh Regelventil
LU87640A1 (de) * 1989-12-13 1990-03-13 Hydrolux Sarl Lagegeregeltes proportionalwegeventil

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005003659A1 (de) * 2005-01-26 2006-07-27 Bosch Rexroth Aktiengesellschaft Wegeventilanordnung und Kraftstoffeinspritzsystem
WO2006079315A1 (fr) 2005-01-26 2006-08-03 Bosch Rexroth Ag Systeme distributeur et systeme d'injection de carburant

Also Published As

Publication number Publication date
JP3519122B2 (ja) 2004-04-12
JPH06341409A (ja) 1994-12-13
LU88277A1 (de) 1994-12-01
CN1041344C (zh) 1998-12-23
CA2124429C (fr) 2004-01-27
DE59406438D1 (de) 1998-08-20
ATE168450T1 (de) 1998-08-15
US5445188A (en) 1995-08-29
CN1098484A (zh) 1995-02-08
EP0628731A1 (fr) 1994-12-14
CA2124429A1 (fr) 1994-11-28
RU2124666C1 (ru) 1999-01-10

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