EP0828945B1 - Servo-soupape a commande pilote - Google Patents

Servo-soupape a commande pilote Download PDF

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Publication number
EP0828945B1
EP0828945B1 EP95937068A EP95937068A EP0828945B1 EP 0828945 B1 EP0828945 B1 EP 0828945B1 EP 95937068 A EP95937068 A EP 95937068A EP 95937068 A EP95937068 A EP 95937068A EP 0828945 B1 EP0828945 B1 EP 0828945B1
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EP
European Patent Office
Prior art keywords
main
spring
main control
control piston
control
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
EP95937068A
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German (de)
English (en)
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EP0828945A1 (fr
Inventor
Arsène Bourkel
Bernd Lanfermann
Karl Tratberger
Karl-Heinz Post
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Hydrolux SARL
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Hydrolux SARL
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Publication of EP0828945A1 publication Critical patent/EP0828945A1/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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • 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

Definitions

  • the invention relates to a pilot operated servo valve with four Power terminals.
  • Pilot operated electrohydraulic servo valves in two or more stages Version with four main power connections are used as 4-way valves Control of position, speed and force in cylinders for Linear movements, respectively position, speed and torque at Hydraulic motors for rotary movements. They are known in the Design as a panel-mounted valve, which means that they have one prismatic valve housing for mounting on a connection surface of a Hydraulic blocks on.
  • the four main power connections of the valve are in one planar connection surface of the valve housing and its openings in the
  • the guide bore of a main control piston is symmetrical. Control chambers are arranged in end caps on both sides of the Valve housing are flanged. These tax chambers are over Control holes connected to a pilot servo valve.
  • the hydraulic The symmetrical main spool is actuated by Pressurization of its two end faces in the front Control chambers.
  • the well-known pilot operated 4-way servo valves all have one spring-centered rest position. In most cases this is done Centering of the main spool over two opposite Return springs which are arranged in the front control chambers and work against each other. However, centering is also known to accomplish by a single spring. This single spring is then in a spring chamber on the front clamped between two spring plates.
  • a pilot operated 4-way proportional valve with one one-sided spring centering is described in the book "Der Hydraulik Trainer Band 2", Publisher and publisher: Mannesmann Rexroth GmbH, DE-8770 Lohr am Main, 3rd edition 1989, page 31, picture 33 shown.
  • the tax chambers of this Valves are arranged in end caps on both sides of the valve housing are flanged.
  • DE-A-4011908 describes a multi-way valve (five ways) known with one-sided spring centering and opposite actuating piston. Both valves have a valve housing for mounting on a connection surface of a hydraulic block.
  • Pilot operated 4-way servo valves with valve body for mounting on a pad of a hydraulic block are very space consuming and require complicated drilling in the hydraulic block for the four Main power connections.
  • the invention is therefore based on the object of a piloted To create servo valve, which saves space in a hydraulic block can be integrated and has a clearly defined center position, without sacrificing good dynamic behavior of the servo valve to have to. According to the invention, this object is achieved by pilot control Servo valve according to claim 1 solved.
  • the pilot operated 4-way servo valve according to the invention has one Control sleeve on the directly in a stepped bore of a hydraulic block is mountable.
  • This control sleeve includes openings for a first, second and third side working connection in the hydraulic block.
  • the It opens into the control sleeve for the fourth main power connection on the other hand, arranged at the front end of the control sleeve that this fourth Main power connector opens axially into the control sleeve.
  • the hydraulic block, in which the control sleeve is used then has three lateral block holes for the first, second and third main power connection. Regarding the Arrangement of the block hole for the fourth main power connection exists however maximum freedom.
  • This block hole for the fourth Main power connection can, for example, directly in the axial extension of the Stepped bore for the control sleeve to be carried out, which is conventional pilot operated servo valves with more than two main ports so far not possible. Bridge formation in the hydraulic block between individual Main power connections are also no longer required.
  • the servo valve according to the invention thus becomes a much more compact design of the control blocks than is the case with conventional servo valves is.
  • This can also be done in more complex hydraulic controls servo valve according to the invention together with various additional valves, for example 2-way cartridge valves, space-saving in a hydraulic block to get integrated.
  • a direct installation in the cylinder cover of larger ones Cylinders are also possible.
  • the main control piston of the valve according to the invention is axial slidably arranged in the control sleeve.
  • One of the two Piston face of the main control piston lies the fourth axial Working connection axially opposite.
  • the second piston face of the The main control piston forms in an extension of the spring chamber Control sleeve one, the first piston face hydrostatic counteracting, pressure compensation surface of the piston.
  • the spring chamber is through a pressure relief duct in the main spool with the fourth Main power connection hydraulically connected. This pressure relief channel also connects an auxiliary connection chamber to the fourth Main power supply.
  • a return spring is in the spring chamber clamped and engaged with the main spool via spring plates that them in both stroke directions of the piston of the hydraulic actuating force in the Control chambers opposed a spring force proportional to the piston stroke and one for the main control piston in unpressurized control chambers pressure-centered position defined.
  • a pilot valve with regulator is hydraulically connected to the two control chambers. On Position sensor of the main control piston delivers a feedback signal for the regulator of the pilot valve.
  • This hydrostatic compensation are the required actuation forces for the main control piston is reduced, whereby the actuating surfaces in the Control chambers can be designed smaller. It follows smaller control oil volumes, that is, with the same large pilot valve shorter positioning times can be achieved.
  • This hydrostatic compensation for the Main control piston also enables the easy use of a one - sided return spring for the spring centering of the main control piston in both stroke directions. As a result, with the same signal for each stroke direction ensures an equal deflection. Furthermore, the mechanical Return spring acting directly on the main control piston Center position of the main spool reliably determined.
  • the pump connection (P) can axially into the Control sleeve are introduced; the tank connection (T) is between the first and second work connection.
  • Other assignments of the Main power connections are also possible, however, without the to dispense with the main advantages of the servo valve according to the invention.
  • hydraulic is generally under pump Pressure source, under the tank a vessel or a line without essential Back pressure and under consumer a hydraulic consumer with two Displacement chambers (for example a rotary or linear drive) is understood.
  • the working connections (A) and (B) are thus spring-centered Center position of the main control spool connected to the tank connection (T). in other words, the two displacement chambers of one connected Consumers are in the spring-centered center position of the main control spool both relieved of pressure.
  • the four control edges of the Main control piston preferably has a zero overlap. This will For example, excellent positioning accuracy when using the Valve in a position control loop of a hydraulic cylinder, and a excellent dynamic behavior when using the valve Pressure control achieved. However, other arrangements of the control edges are also possible. For example, in a spring-centered center position of the main control piston all connections through the control edges to be introverted.
  • the spring centering is preferably designed as follows.
  • the The main control piston has an axial one in the spring chamber Extension shaft on.
  • a first and a second spring plate are axial slidably guided on this extension shaft.
  • the return spring presses the first spring plate against a valve Stop surface on the main control piston and the second spring plate against one Stop surface at the free end of the extension piston.
  • the spring chamber is then dimensioned such that in this rest position both spring plates in the Apply spring chamber axially.
  • the servo valve according to the invention is as such with the Reference number 10 denotes.
  • a control sleeve 12 is in a stepped bore 14 one (only indicated) hydraulic block 16 used.
  • the control sleeve 12 forms an axial guide bore into which a main control piston 18 axially is slidably fitted.
  • the servo valve 10 shown in the figures is a 4-way servo valve and has a pump connection (P), a tank connection (T), and a first working connection (A) and a second working connection (B).
  • the Pump connection (P) is hydraulically connected to a pressure line (Not shown).
  • the tank connection (T) is in hydraulic connection with an unpressurized line (not shown).
  • the working connections (A) and (B) are in hydraulic connection with a first or second Displacement chamber of a hydraulic linear or rotary drive (not shown).
  • Three block bores 22, 20, 24 in the hydraulic block 16 for the Tank connection (T) 22, the first working connection (A) 20 and the second Working connection (B) 24, are arranged transversely to the stepped bore 14 and open laterally into the stepped bore 14.
  • the Control sleeve 12 each have an annular junction 22 ', 20', 24 'in the area the corresponding block bores 22, 20, 24. Any of these Mouths 22 ', 20', 24 'has several transverse bores 25 through the wall the control sleeve 12, which each have a hydraulic connection with the Make the guide bore of the main control piston 18.
  • a fourth Block bore 26 for the pump connection (P) is in a coaxial extension the stepped bore 14 arranged.
  • the control sleeve 12 has this fourth Block bore 26 an end opening 26 '.
  • a first axial hydraulic Connection 28 the end opening 26 'for the pump connection (P) with the lateral mouth 20 'for the work connection (A); a second axial hydraulic connection 30 the mouth 22 'for the tank connection (T) with the mouth 20 'for the working connection (A); a third axial hydraulic connection 32 with the mouth 22 'for the tank connection (T) the mouth 24 'for the work connection (B); and a fourth axial hydraulic connection 34 the mouth 24 'for the working connection (B) with one inside the control sleeve 12 by the main control piston 18th delimited auxiliary connection chamber 36.
  • the main control piston 18 has a first coaxial piston collar 38 on which is assigned to the working connection (A) and axially in the first and second axial hydraulic connection 28 and 30 is slidable. He also has a second coaxial piston collar 40, which the Working connection (B) is assigned and axially in the third and fourth axial hydraulic connection 32 and 34 is displaceable.
  • the first piston collar 38 forms a first, assigned to the first hydraulic connection 28 Control edge 28 'and one of the second hydraulic connection 30 assigned second control edge 30 '. Both control edges 28 ', 30' point a zero coverage.
  • the second piston collar 40 forms one, the third hydraulic connection 32 assigned, third control edge 32 ', and a fourth control edge assigned to the fourth hydraulic connection 34 34 '.
  • the auxiliary connection chamber 36 is annular in the control sleeve around the Main control piston 18 is formed. It is on one side through the Piston collar 40 and on the other side by a piston collar 42 axially sealed.
  • auxiliary connection chamber 36 Via an axial piston bore 44 and a piston transverse bore 46 through the main control piston 18 is the auxiliary connection chamber 36 with the Pump connection (P) connected.
  • the main spool can therefore over its coaxial piston collar 38 the first working port (A) and over its coaxial piston collar 40 optionally the second working port (B) connect to the pump connection (P) or the tank connection (T), whereby the respective flow of the hydraulic fluid over the four control edges 28 ', 30 ', 32', 34 'is regulated.
  • the spring chamber 52 is in the axial extension of the control sleeve 12 in a valve cover 54 is arranged.
  • This valve cover 54 is on the Hydraulic block 16 fastens and fixes the control sleeve 12 in the stepped bore 14.
  • the second end of the main spool 18 is axially sealed by a sealing insert 56 is inserted into the spring chamber 52 and forms one therein Pressure equalization approach 58.
  • This points in the pressure compensation chamber 52 one hydrostatically counteracting the first piston face 48 Pressure compensation surface 60.
  • the pressure compensation area 60 is equal to that Piston face 48 so that there is a complete hydrostatic Pressure equalization of the pump pressure results.
  • the main control piston 18 is actuated via a processed coaxial actuating piston collar 62, by appropriate Pressurizing its ring-shaped first, respectively second Actuating surface 64, 66. Between the piston collar 42 and the Actuating surface 64 becomes a first annular in the control sleeve Control chamber 68 and between sealing insert 56 and the actuating surface 66 a second annular control chamber 68 is formed.
  • the first tax chamber 68 is via a pilot port 72 in the valve cover 54 with the Working port (A ') and the second control chamber 70 is via a pilot port 74 in the valve cover 54 with the working connection (B ') one Flanged 4-way pilot servo valve 76 connected.
  • the Actuating surfaces 64, 66 are designed so large that the Overflow of the control edges 28 ', 32' or 30 ', 34' Flow forces are surely overcome. That’s why Control oil volumes are very small and very short positioning times can be achieved to reach.
  • the main control piston 18 by pressurizing the first Control chamber 68 from its central position in the direction of spring chamber 52 is moved, the return spring 78 by the, on the end face 60 of Main control piston 18 adjacent, first spring plate 80 in the spring chamber 52 compressed.
  • she exercises one on the main control piston 18 Spring force that opposes this movement and its module is proportional to the stroke of the main control piston 18.
  • Will the Main control piston 18 by pressurizing the second control chamber 70 moves from its central position in the direction of the pump connection 26, exercises the extension shaft 84 on the second spring plate a tensile force, so that the return spring 78 now through the second spring plate 82 in the Spring chamber 52 is compressed.
  • This spring force arises here against the movement of the main control piston 18 and its module proportional to the stroke of the main spool 18.
  • Extension shaft 84 is screwed into the main control piston and through a pin 90 is secured.
  • the axial piston bore 44 is in the Extension shaft 84 continued to the transverse bore 46.
  • Another Cross bore 92 is located directly above the end face 60 of the Main control piston 18. This second transverse bore 92 has one for the purpose To ensure pressure equalization above and below the spring plate 80. In the second spring plate 82, this pressure equalization through holes 94 in Spring plate 82 reached.
  • the main control piston is over a Position sensor 96 in a closed position control loop involved.
  • a shaft 98 of the position sensor 96 is mechanical connected to the extension shaft 84 of the main control piston.
  • the Output signal of the position sensor 96 (that of the position of the Main control piston 18) is included in a control amplifier 100 compared to a target value (S), and the pilot servo valve 76 is in the Ratio to the determined target / actual value difference.
  • the Pilot control valve 76 then regulates the control oil pressure in the two Control chambers 68 and 70 of the main stage and places, against the action of Return spring 78, the piston stroke firmly, so that a closed, electro-hydraulic Control loop is formed.
  • the work connections are thus in this spring-centered center position (A) and (B) depressurized to the tank.
  • the main spool 18 is off this center position in the direction of the pump connection (P) remains the work connection (A) to the tank is relieved.
  • the work connection (B) will however via the auxiliary connection chamber 36 and the axial piston bore 44 the pump connection (P) hydraulically connected.
  • the Main control piston 18 from this central position in the direction of the spring chamber 52 driven, the work connection (B) to the tank remains unloaded.
  • the working connection (A) becomes the tank through the second control edge 30 ' blocked, and via the first control edge 32 'with the pump connection (P) hydraulically connected.
  • the main spool takes off 18 in its spring-centered center position, in which both working connections (A) and (B) are relieved to the tank as described above.

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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)
  • Reciprocating Pumps (AREA)

Claims (7)

  1. Servo-soupape à commande pilote avec quatre raccords principaux, comprenant
    un boítier de soupape (12, 54) avec:
    un alésage de guidage pour un piston pilote principal (18),
    une première connexion hydraulique (28) entre le quatrième raccord principal et le premier raccord principal, dans ledit alésage de guidage,
    une deuxième connexion hydraulique (30) entre le premier raccord principal et le deuxième raccord principal, dans ledit alésage de guidage,
    une troisième connexion hydraulique (32) entre le deuxième raccord principal et le troisième raccord principal, dans ledit alésage de guidage,
    une quatrième connexion hydraulique (34) entre le troisième raccord principal et une chambre de connexion auxiliaire, dans ledit alésage de guidage,
    un piston pilote principal (18) placé dans l'alésage de guidage de manière à pouvoir être déplacé axialement, avec:
    un premier bord pilote (28') affecté à la première connexion hydraulique axiale (28) pour régler l'écoulement,
    un deuxième bord pilote (30') affecté à la deuxième connexion hydraulique axiale (30) pour régler l'écoulement,
    un troisième bord pilote (32') affecté à la troisième connexion hydraulique axiale (32) pour régler l'écoulement,
    un quatrième bord pilote (34') affecté à la quatrième connexion hydraulique axiale (34) pour régler l'écoulement,
    le piston pilote principal (18) délimitant une première et une seconde chambres pilotes (68, 70) à l'intérieur du boítier de soupape et formant, à l'intérieur de la première chambre pilote (68), une première surface d'actionnement (64) ainsi que, à l'intérieur de la seconde chambre pilote (70), une seconde surface d'actionnement (66) axialement antagoniste de la première surface d'actionnement (64);
    un ressort de rappel (78) encastré dans un logement de ressort (52) frontal et en prise sur le piston pilote principal (18) de manière telle qu'il oppose un effet de ressort audit piston pilote principal (18) dans les deux sens de la course de ce dernier et qu'il définit ainsi, par son effet de centrage, une position centrale dudit piston pilote principal (18);
    une soupape pilote (76) raccordée hydrauliquement à l'une des deux chambres pilotes (68, 70) au moins;
    un régulateur (100) de la soupape pilote (76);
    un capteur de position (96) connecté au piston pilote principal (18) et indiquant la position du piston pilote principal (18) sous la forme d'un signal de rétroaction aux fins du régulateur (100) de la soupape pilote (76);
    caractérisée en ce que
    le boítier de soupape comprend un manchon pilote (12) pouvant être disposé axialement dans un alésage (14) d'un bloc hydraulique (16) et réalisé de manière à délimiter des embouchures annulaires (20', 22', 24') dans ledit alésage (14) pour les premier, deuxième et troisième raccords principaux,
    une embouchure (26') pour le quatrième raccord principal est placée axialement à l'extrémité frontale du manchon pilote (12), une première face frontale du piston pilote principal (18) étant située axialement à l'opposé de ladite embouchure (26'),
    une surface d'équilibrage de pression (60) est formée par la seconde face frontale du piston pilote principal (18) dans le logement de ressort (52),
    un canal de décompression (44) traversant le piston pilote principal (18) raccorde hydrauliquement le logement de ressort (52) au quatrième raccord principal de sorte que la surface d'équilibrage de pression (60) est soumise à la pression dans le quatrième raccord principal et
    en ce qu'un alésage transversal (46) raccorde le canal de décompression à la chambre de connexion auxiliaire (36).
  2. Soupape selon la revendication 1, caractérisée en ce que
    le premier raccord principal forme un premier raccord de service (A), le deuxième raccord principal forme un raccord à un réservoir (T), le troisième raccord principal forme un deuxième raccord de service (B) et le quatrième raccord principal forme un raccord à une pompe (P).
  3. Soupape selon la revendication 1, caractérisée en ce que les bords pilotes sont placés de manière à prendre les positions suivantes lorsque le piston pilote principal (18) occupe une position centrale sous l'effet de centrage du ressort:
    la première connexion hydraulique axiale (28) est obturée par le premier bord pilote (28'),
    la deuxième connexion hydraulique axiale (30) est dégagée,
    la troisième connexion hydraulique axiale (32) est dégagée et
    la quatrième connexion hydraulique axiale (34) est obturée par le quatrième bord pilote (34').
  4. Soupape selon l'une des revendications 1 à 3, caractérisée en ce que les première et seconde surfaces d'actionnement (64, 66) sont des surfaces annulaires.
  5. Soupape selon l'une des revendications 1 à 4, caractérisée par
    une tige axiale prolongatrice (84) du piston pilote principal (18) dans le logement de ressort (52),
    une première et une seconde cuvettes de ressort (80, 82) montées sur ladite tige prolongatrice (84) de manière à pouvoir être déplacées axialement,
    une surface de butée axiale (60) pour la première cuvette de ressort (80) au niveau du piston pilote principal,
    une surface de butée axiale (86) pour la deuxième cuvette de ressort (82) au niveau de la tige prolongatrice (84),
    le ressort de rappel (78) poussant chacune des deux cuvettes de ressort (80, 82) contre la surface de butée correspondante (60, 86) lorsque la soupape est en position de repos et
    le logement de ressort (52) étant dimensionné de manière que, dans ladite position de repos, les deux cuvettes de ressort (80, 82) prennent axialement appui dans le logement de ressort.
  6. Soupape selon la revendication 5, caractérisée en ce que le canal de décompression (44) est réalisé sous la forme d'un alésage axial pénétrant dans la tige prolongatrice (84) et y débouchant sur le logement de ressort (52) via un premier alésage transversal (50).
  7. Soupape selon la revendication 6, caractérisée en ce que la tige prolongatrice (84) présente un deuxième alésage transversal (92) à proximité immédiate de la première surface de butée (60) pour la première cuvette de ressort (80).
EP95937068A 1994-11-16 1995-11-13 Servo-soupape a commande pilote Expired - Lifetime EP0828945B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
LU88558A LU88558A1 (de) 1994-11-16 1994-11-16 Vorgesteuertes Servoventil
LU88558 1994-11-16
PCT/EP1995/004454 WO1996015373A1 (fr) 1994-11-16 1995-11-13 Servo-soupape a commande pilote

Publications (2)

Publication Number Publication Date
EP0828945A1 EP0828945A1 (fr) 1998-03-18
EP0828945B1 true EP0828945B1 (fr) 2002-09-11

Family

ID=19731505

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95937068A Expired - Lifetime EP0828945B1 (fr) 1994-11-16 1995-11-13 Servo-soupape a commande pilote

Country Status (11)

Country Link
US (1) US5896890A (fr)
EP (1) EP0828945B1 (fr)
JP (1) JP3638286B2 (fr)
CN (1) CN1070584C (fr)
AT (1) ATE224012T1 (fr)
AU (1) AU3928595A (fr)
CA (1) CA2205441C (fr)
DE (1) DE59510375D1 (fr)
LU (1) LU88558A1 (fr)
RU (1) RU2153105C2 (fr)
WO (1) WO1996015373A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011154056A1 (fr) 2010-06-11 2011-12-15 Bühler AG Dispositif de soupape

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US7422033B2 (en) * 2004-12-16 2008-09-09 Husco International, Inc. Position feedback pilot valve actuator for a spool control valve
CN100348873C (zh) * 2005-11-03 2007-11-14 武汉科技大学 一种数字输入式电液伺服阀
DE102006034366A1 (de) * 2006-02-24 2007-08-30 Robert Bosch Gmbh Wege- oder Stromventil
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US20080224353A1 (en) * 2007-03-14 2008-09-18 Husky Injection Molding Systems Ltd. Hydraulic Valve of Molding System
DE102008058694B4 (de) * 2007-12-06 2019-12-19 Schaeffler Technologies AG & Co. KG Verfahren zum Ansteuern eines hydraulischen Folgesystems
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CN102996814B (zh) * 2012-12-08 2015-01-28 中国航天科技集团公司第六研究院第十一研究所 一种活塞与阀芯分体式设置的控制阀
CN105545856B (zh) * 2016-02-17 2017-07-14 武汉市汉诺优电控有限责任公司 一种数控旋芯式比例伺服阀
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US5896890A (en) 1999-04-27
AU3928595A (en) 1996-06-06
JP3638286B2 (ja) 2005-04-13
CN1163657A (zh) 1997-10-29
CA2205441C (fr) 2005-02-08
RU2153105C2 (ru) 2000-07-20
CA2205441A1 (fr) 1996-05-23
DE59510375D1 (de) 2002-10-17
WO1996015373A1 (fr) 1996-05-23
LU88558A1 (de) 1996-07-15
ATE224012T1 (de) 2002-09-15
CN1070584C (zh) 2001-09-05
EP0828945A1 (fr) 1998-03-18
JPH10508679A (ja) 1998-08-25

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