EP0900963B1 - Soupape à siège - Google Patents

Soupape à siège Download PDF

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Publication number
EP0900963B1
EP0900963B1 EP98108827A EP98108827A EP0900963B1 EP 0900963 B1 EP0900963 B1 EP 0900963B1 EP 98108827 A EP98108827 A EP 98108827A EP 98108827 A EP98108827 A EP 98108827A EP 0900963 B1 EP0900963 B1 EP 0900963B1
Authority
EP
European Patent Office
Prior art keywords
closing member
seat
closing
sleeve
seat 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
EP98108827A
Other languages
German (de)
English (en)
Other versions
EP0900963A1 (fr
Inventor
Martin Heusser
Anton Estendorfer
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.)
Hawe Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Publication of EP0900963A1 publication Critical patent/EP0900963A1/fr
Application granted granted Critical
Publication of EP0900963B1 publication Critical patent/EP0900963B1/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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet 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
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • 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
    • F15B2013/041—Valve members; Fluid interconnections therefor with two positions

Definitions

  • the invention relates to a seat valve specified in the preamble of claim 1 Art.
  • Such seat valves known from prior use in practice, as a rule Black / white valves have a switching magnet as the adjustment drive, which , Locking element adjusted against a spring.
  • 2/2-way seat valve are the two ways from each other in the locked position of the closing member Cut; in the through position of the closing member, however, with each other connected.
  • the lock for holding the locking element in the shut-off position is formed by the switching magnet and the spring.
  • a 3/2-way seat valve with electromagnetic actuation known from EP-A-0 492 242 has a two-way locking for the locking members Rocker arm on by a spring in the direction of rotation and in the respective Closing direction is then acted upon when it reaches its pivot dead center in one or other direction. There is a lot of space for locking needed. The closing force that can be generated for the closing element is low.
  • a change seat valve is known, the two closing members are coupled via a connecting lever pivotally mounted in the housing.
  • the link lever carries a control cam with an apex.
  • One in Ball with linear movement and loaded by a compression spring lies on the control cam.
  • the locking is structurally complex and stressed lots of installation space.
  • the adjustment shaft carries of the closing member a ball, which during the opening or closing movement of the Closing member between two spring-loaded, counteracting sliding elements is squeezed through.
  • the invention has for its object a seat valve of the type mentioned to create that structurally simple, inexpensive to manufacture and with low energy consumption adjustable and yet lockable with high force.
  • the adjustment drive can remain ineffective or be switched off, because the latching the closing member in the shut-off position holds. Because with a seat valve, a leak-free shut-off position has a certain shut-off position holding force required, the mechanical, positive and non-positive Then the catch will not be in a weak or relaxed position, but in an intermediate position in which they hold the locking member with the blocking position presses and holds against the valve seat. The holding force is determined by the frictional connection the latching in interaction with the form closure.
  • the latch leaves can be integrated into the seat valve in a structurally simple manner is simple and inexpensive. Since the adjustment drive only for initiating one Adjustment is needed, the seat valve can be used with little energy and therefore adjust with a simple and inexpensive adjustment drive.
  • angles of approximately 45 ° are according to claim 3 for both adjustment directions achieved essentially symmetrical force ratios.
  • the lock is from the working area of the closing member laid.
  • the straight passive latching does not generate a disruptive counterforce for active locking.
  • the closing member is in the adjustment supports the two catches in the respective adjustment direction. The adjustment drive only needs to generate the adjustment pulse.
  • the manufacture and assembly of the seat valve are simplified.
  • the latching can be accommodated well, without such proven training concepts To adversely affect seat valves.
  • a mechanical latching is for both shut-off positions provided so that the seat valve is bistable without the influence of the adjustment drive.
  • a spring that the adjustment drive would have to overcome in between is not required.
  • the latching is an adjusting auxiliary drive for the closing element, which largely relieves the actual adjustment drive.
  • a poppet valve S in Fig. 1 e.g. a 2/2-way seat valve, has a in a housing 1 Valve seat 2 for cooperation with a closing member 3, which deals with a seat 3a can be placed on the valve seat 2.
  • the valve seat 2 is between flow paths A, C provided. In the shut-off position of the seat valve S shown, the Connection between paths A, C broken.
  • an adjustment drive 5, 7 is provided, which with the closing member 3 is connected, for example, via the elements 4, 6.
  • An axial force holds in the direction of the dashed arrow or a blocking position holding force Z. the closing member 3 in the shut-off position.
  • a force in the direction of the extended, upward arrow moves the closing member 3 to the open position.
  • the adjustment drive 5, 7, which is, for example, in two parts, can either be operated manually operate or consists of switching magnets or is operated by a hydraulic or pneumatic pilot control.
  • the seat valve S is actuated by a mechanical, and frictional locking R held.
  • An element 8 is in the latching two oppositely sloping cam surfaces N1 and N2, e.g. provided on part 4.
  • the cam surfaces N1 and N2 are acted upon by a cam member F, which is loaded by a spring G.
  • the cam member F produces thanks to the shape and Force closure and the force of the spring G, the blocking position holding force Z for the Locking member 3, since the locking R of the locking member 3, at least in the shut-off position, is prevented from reaching a relaxed position.
  • the adjustment drive 5, 7 is because the locking R as an adjustment auxiliary drive acts in both adjustment directions, only required as an adjustment pulse generator 12, 11, to initiate an adjustment of the seat valve S, which then runs automatically, until a stable position of the closing element is reached again. That is how it is Seat valve S is bistable even without the adjustment drive, i.e. that in that one locked position of the locking member remains until a new one in the opposite impulse is introduced.
  • a 3/2-way seat valve S is shown in a symbolic representation in FIG creates the connection between two paths C, B or C, A and thereby the connection to the third route A or B.
  • Two are used as adjusting drives 5, 7 Switching magnets with opposite directions of action, which may only be adjusting adjusting devices Form I1 and I2 because the poppet valve with a mechanical catch R is equipped, which in the two shut-off positions of this seat valve S Closing member holds with axial holding force.
  • the structure of the seat valve according to FIG. 2 is indicated in FIG. 3, partly in section.
  • the two switching magnets 5, 7 are then energized via connections 9, if the seat valve S is to be adjusted.
  • the switching magnets are adjustable pulse generators and can be switched off or de-energized after the adjustment.
  • the housing 1 In the housing 1 is in a housing bore 10 equipped with the locking R cartridge-like insert 11, which contains the closing member 3, which means the switching magnet M1, M2 of the adjustment drive 5, 7 is adjustable back and forth.
  • the stroke of the seat valve is indicated by X and is relatively small. For example, it is only a few 1/10 mm, e.g. 0.5 mm.
  • the elements 4, 6 are plungers with which the Switching magnet transmit the respective adjustment pulse to the closing element 3. The detailed structure of the seat valve in FIG. 3 is explained with reference to FIG. 4.
  • the closing member 3 which in the embodiment shown is arranged on an adjustment shaft 3 ', in a two-part sleeve 12a, 12b linearly adjusted.
  • a valve seat 2a, 2b is formed in each sleeve part 12a, 12b.
  • the two valve seats 2a, 2b mutually cooperate with the seat surfaces 3a1 and 3a2 of the closing member 3, in order (see symbol in FIG. 2) either path A with the path Connect C and thereby shut off B from A, C, or connect B to C, and shut off A from C, B
  • the seat surfaces 3a1, 3a2 are for example conical, while the valve seats 2a, 2b from the mouths of cylindrical bores be formed.
  • the plunger engages at the lower adjusting end 3c2 of the closing element 3 6 on, while at the upper adjusting end 3c1 the plunger 4 of the other switching magnet attacks.
  • the catch R is contained in the cartridge-shaped insert 11.
  • the mess 3 two axially spaced circumferential grooves 19 are formed, which are opposite to each other have inclined groove flanks 21 and internal spaces 20.
  • the groove flanks 21 form the cam surfaces N1, N2, which in the embodiment shown formed as a rotationally symmetrical conical surfaces to the axis of the closing member 3 are.
  • a plurality of balls 16 serve as cam members F of the latching R, which are arranged axially in two spaced radial bore rows 15 in the sleeve part 12a guided radially movable are.
  • a cylindrical circumferential section may lie between the two cam surfaces N1, N2 with a slightly reduced diameter of the adjustment shaft 3 '. aligned on the radial bore rows 15 there are two outwards in the sleeve part 12a Open circumferential grooves 14 are formed, in which the balls 16, ring-shaped Spring elements G are arranged.
  • an O-ring 22 which is knotted into a circumferential groove 13 and is under radial prestress, so that the balls 16 acted upon by it against the adjustment shaft 3 'are pressed inwards.
  • the O-rings 22 is a pressure sleeve 17 with a reduced diameter End portion 13 of the sleeve part 12a is pushed, on which the O-rings 22nd support inside, so that they with their tension and compression Act.
  • an inner end of the pressure sleeve 17 is included a funnel-shaped expansion 18 is formed.
  • the angle ⁇ , which each cam surface N1, N2 encloses with the axis of the closing member 3, is, for example, 45 °.
  • the Hardness or compression of the O-rings 22 and / or the angle ⁇ of each cam surface N1, N2 it is possible to use the same blocking position holding forces or different ones Set the blocking position holding forces Z. So that the latching the respective Shut-off position holding force can be the axial distance between the cam surfaces N1, N2 so matched to the stroke of the closing member 3 that in the respective Locking position, the balls 16 in a radial bore row their assigned Fully apply cam surface while the balls of the other radial bore row sit on the cylindrical outer circumference of the adjustment shaft 3 '. With this Voting is also achieved that the locking R when adjusting the closing member helps between the two shut-off positions, so that the adjustment drive only needs to generate an adjustment pulse and then at least the actual adjustment largely runs automatically.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lift Valve (AREA)
  • Magnetically Actuated Valves (AREA)

Claims (10)

  1. Vanne à siège (S) comportant au moins un organe de fermeture (3), dont la surface de fermeture (3a, 3a1, 3a2) coopère avec au moins un siège de vanne (2, 2a, 2b), comportant un actionneur (5, 7) pour déplacer l'organe de fermeture (3) pour bloquer ou libérer le siège de vanne, et comportant un encliquetage (R) par correspondance de formes et conjugaison de forces, contraignant l'organe de fermeture (3) pouvant être relâché par l'actionneur (5, 7), pour maintenir l'organe de fermeture au moins dans la position d'arrêt sur le siège de vanne, avec une force de maintien de position de blocage (Z) agissant dans la position de fermeture, caractérisée en ce que des rainures annulaires (19) écartées axialement sont prévues sur l'organe de fermeture (3), en ce que dans une douille (12a, 12b) entourant l'organe de fermeture, des billes (16) sont supportées dans au moins deux alésages (15) orientés dans la direction périphérique, écartés axialement, et en ce que chaque bille (16) dans chaque alésage est contrainte par une précontrainte radiale par un joint torique (22) qui entoure la douille dans la région de l'alésage considéré.
  2. Vanne à siège selon la revendication 1, caractérisée en ce que chaque joint torique (22) est disposé dans une rainure périphérique extérieure (14) de la douille et vient en appui sur une paroi entourant la douille, et en ce que respectivement plusieurs alésages (15) orientés dans la direction périphérique, forment un groupe d'alésages à axes radiaux.
  3. Vanne à siège selon la revendication 1, caractérisée en ce que la rainure annulaire présente au moins un chanfrein ou un flanc de rainure arrondi (21), qui de préférence est incliné selon un angle (á) d'approximativement 45° vers l'axe de l'organe de fermeture (3).
  4. Vanne à siège selon la revendication 1, caractérisée en ce que les rainures annulaires (19) sont disposées sur une tige de déplacement reliée avec l'organe de fermeture (3), contenue dans la douille (12a, 12b).
  5. Vanne à siège selon la revendication 3, caractérisée en ce qu'un espace libre (20) est prévu intérieurement adjacent au flanc de rainure (21), et en ce que l'écartement axial entre la bille (16), le flanc de rainure (21) lui correspondant et la surface de siège (3a1, 3a2) de l'organe de fermeture (3), est choisi de manière telle que, dans la position d'arrêt, la bille (16) est pressée sur le flanc de rainure (21) et qu'un jeu radial est maintenu dans l'espace libre pour la bille (16).
  6. Vanne à siège selon au moins l'une des revendications précédentes, caractérisée en ce que les flancs de rainures (21) dans leur largeur axiale, les diamètres des billes (16) et leurs écartements axiaux sont adaptés les uns aux autres de manière telle qu'à l'intérieur d'une course (X) d'environ 0,5 mm de l'organe de fermeture, alternativement une bille est en appui sur son flanc de rainure et l'autre bille libère son flanc de rainure.
  7. Vanne à siège selon au moins l'une des revendications précédentes, caractérisée en ce que deux sièges de vannes (2a, 2b) sont formés dans une douille (12a, 12b) insérée dans un alésage de corps (10) divisée entre les deux sièges de vanne, qui reçoit l'organe de fermeture (3) de manière étanche, capable de translation telle que les extrémités de déplacement (3c1, 3c2) de l'organe de fermeture (3) sont accessibles aux deux extrémités de la douille, et en ce que l'encliquetage (R) est prévu dans la douille et sur l'organe de fermeture entre les extrémités de déplacement.
  8. Vanne à siège selon au moins l'une des revendications précédentes, caractérisée en ce qu'une section d'extrémité (13) de diamètre réduit de la douille (12a, 12b) portant les deux joints toriques (22) est entourée par une douille de pression (17), qui de préférence présente à une extrémité un élargissement (18) en forme d'entonnoir.
  9. Vanne à siège selon la revendication 1, caractérisée en ce que dans le cas de deux sièges de vanne (2a, 2b) et d'un seul organe de fermeture (3) comportant deux surfaces de fermeture (3a1, 3a2) ou de deux organes de fermeture couplés comportant chacun une surface de fermeture (vanne à siège 3/2 voies ou 2/2 voies), un encliquetage mécanique (R) est prévu à chaque fois pour les deux positions d'arrêt.
  10. Vanne à siège selon au moins l'une des revendications précédentes, caractérisée en ce que l'encliquetage (R) est formé à partir de son point de détachement en tant qu'actionneur auxiliaire pour l'élément de fermeture (3).
EP98108827A 1997-09-02 1998-05-14 Soupape à siège Expired - Lifetime EP0900963B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE29715748U 1997-09-02
DE29715748U DE29715748U1 (de) 1997-09-02 1997-09-02 Sitzventil

Publications (2)

Publication Number Publication Date
EP0900963A1 EP0900963A1 (fr) 1999-03-10
EP0900963B1 true EP0900963B1 (fr) 2003-02-26

Family

ID=8045433

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98108827A Expired - Lifetime EP0900963B1 (fr) 1997-09-02 1998-05-14 Soupape à siège

Country Status (2)

Country Link
EP (1) EP0900963B1 (fr)
DE (2) DE29715748U1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019202052B4 (de) * 2019-02-15 2022-09-01 Hawe Hydraulik Se Wegesitzventil
DE102020003973A1 (de) 2020-07-02 2022-01-05 Hydac Fluidtechnik Gmbh Ventilvorrichtung

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB313653A (en) 1928-03-16 1929-06-17 Shell Mex Ltd Improvements in or relating to taps for controlling the supply of a fluid
DE1005794B (de) 1955-01-25 1957-04-04 Kissing & Moellmann Armaturenf Wechselventil
DE1029639B (de) 1955-11-11 1958-05-08 Kromschroeder Ag G Handbetaetigtes Schnellschlussventil
US3602245A (en) * 1970-02-26 1971-08-31 Abex Corp Universal detent positioner
DE2407136B2 (de) * 1974-02-15 1979-10-25 G.L. Rexroth Gmbh, 8770 Lohr Wegeventil mit Rasteinrichtung zur Festlegung der Schaltstellungen seines Steuerkolbens
US4796860A (en) 1987-10-16 1989-01-10 Eaton Corporation Valve spool detent
DE4042084A1 (de) 1990-12-28 1992-07-02 Eberspaecher J Magnet-wegeventil zur volumenstromsteuerung

Also Published As

Publication number Publication date
EP0900963A1 (fr) 1999-03-10
DE59807291D1 (de) 2003-04-03
DE29715748U1 (de) 1997-11-06

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