EP0238782B1 - Unité de vanne à 5/3 voies - Google Patents

Unité de vanne à 5/3 voies Download PDF

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Publication number
EP0238782B1
EP0238782B1 EP19860890351 EP86890351A EP0238782B1 EP 0238782 B1 EP0238782 B1 EP 0238782B1 EP 19860890351 EP19860890351 EP 19860890351 EP 86890351 A EP86890351 A EP 86890351A EP 0238782 B1 EP0238782 B1 EP 0238782B1
Authority
EP
European Patent Office
Prior art keywords
control
valve unit
cylinder end
casing
slides
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
EP19860890351
Other languages
German (de)
English (en)
Other versions
EP0238782A2 (fr
EP0238782A3 (en
Inventor
Herbert Ing. Frisch
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.)
ENFO Grundlagen Forschungs AG
Original Assignee
ENFO Grundlagen Forschungs AG
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 ENFO Grundlagen Forschungs AG filed Critical ENFO Grundlagen Forschungs AG
Publication of EP0238782A2 publication Critical patent/EP0238782A2/fr
Publication of EP0238782A3 publication Critical patent/EP0238782A3/de
Application granted granted Critical
Publication of EP0238782B1 publication Critical patent/EP0238782B1/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
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves

Definitions

  • the invention relates to a 5/3-way valve unit for positioning a double-acting pneumatic cylinder, with a control element displaceable under the action of a control pressure against a restoring force in a controllable medium connections housing, which at control pressures below the pressure level required to overcome the restoring force in its zero position blocking all medium connections.
  • Valves are required for the controlled positioning of penumatic cylinders, the flow cross-sections of which must be very precise and easily adjustable in any intermediate position between zero and the maximum.
  • sealless spool valves are mostly used, which, due to their pressure-balanced design, can be operated with very little adjustment forces and, due to the air lubrication, also have very little friction.
  • the variant with a 5/3-way valve unit of the type mentioned at the outset has the advantage that the middle position is closed even when the position control is switched off; At the same time, however, there is also the disadvantage of a relatively large control air clearance, which is also inherent in the 3/3-way valves, which arises because the central position of the control element is in the middle of the control stroke due to the function, and which disadvantageously reduces the response speed of the proportional control valves.
  • the object of the present invention is to improve a valve unit of the type mentioned at the outset in such a way that the disadvantages of the known designs are avoided and, in particular, that there is a minimal control air clearance in the region around the zero position blocking all medium connections and a short response time to fluctuations in the control pressure in this area without great design effort and with high operational reliability.
  • control element is formed by two control slides arranged separately in the housing, each of which has two axially offset control edges which cooperate with two medium connections and can be acted upon separately with control pressure, the control edges of the first Control spool supply air of the first and exhaust air of the second cylinder side and the control edges of the second control spool Control the supply air on the second and exhaust air on the first cylinder side.
  • This division of the control element ensures in a very simple manner and while maintaining the above-mentioned advantageous feature of the 5/3-way valves that in the zero position of the control element there is only a very small control air damage space, which practically only results from the supply of the control pressure. Starting from this zero position, both control spools can be acted upon separately with control pressure, each of the two control spools being responsible for a direction of movement of the pneumatic cylinder or the working piston of this pneumatic cylinder.
  • a further advantage of the embodiment according to the invention is the possibility of a very compact design, since the two separate control spools can be accommodated in a compact housing much more easily than a conventional 5/3-way valve.
  • the two separate control slides are guided in insert bushes in the housing, which have control openings connected to the medium connections, and that both the control slide and the insert bushes are designed identically.
  • the two control slides are subjected to the restoring force from the housing via separate compression springs, which ensures complete independence of the movement of the two control slides from one another and allows a largely symmetrical configuration of the valve unit with respect to the two control slides.
  • the two control slides are arranged parallel to one another in the housing and that the connections for the control pressure are each on the same housing side.
  • this also provides simplified connection and assembly conditions, which offers great advantages, in particular in connection with, for example, a direct attachment of the valve unit according to the invention to the cylinder to be controlled.
  • the control openings for the supply air and for the exhaust air can be provided for both cylinder sides at substantially the same intervals for connection to the positions for the control pressure in the housing of the valve unit, which greatly simplifies the routing of the necessary connecting lines between the two separate control slides.
  • pilot valves are placed directly on the connections for the control pressure on the housing. In this way it is ensured that the small control air harmful space made possible with the design according to the invention can be fully used and is not reduced by longer connecting lines to the pilot valves.
  • Fig. 1 shows a circuit diagram for positioning a double-acting pneumatic cylinder with a valve unit according to the invention
  • Fig. 2 shows an embodiment of a valve unit according to the invention in section.
  • the double-acting pneumatic cylinder 1 essentially consists of a cylinder 2 and a piston 3 axially guided therein, which is connected to a piston rod 4 which extends out of the cylinder 2.
  • the valve unit 9, which enables the positioning of the pneumatic cylinder 1 by controlling the supply and exhaust air of the two cylinder sides 5, 6, has a control element which is displaceable in a housing 10 and is here formed by two separate control slides 11, 12 and which acts under the influence of the inputs X and Y applied control pressure against the force of two separate compression springs 13, 14 is displaceable and controls five medium connections.
  • P is the connection for the uncontrolled pressure medium, ie the supply air to both cylinder sides; Instead of the separate connections P here, of course, a common one could also be provided for both control slides.
  • R the connection for the exhaust air from the second cylinder side 6 - ie from the cover side - is designated.
  • S denotes the connection for the exhaust air from the first cylinder side 5; A and B are already referred to above as connections leading directly to the cylinder sides.
  • the two control spools 11, 12 are shown in the circuit diagram of Fig. 1 as 4/2-way valves and also act accordingly - but equivalent is a response of these spool as two mechanically coupled 2/2-way valves, as explained in more detail below 2 comes closer.
  • the valve unit 9 the following should only be mentioned briefly: In the zero position of the control element or the two control slides 11, 12 shown in FIG. 1, all five controllable medium connections A, B, P, S, R are under the action of both Compression springs 13, 14 shut off, whereby the two cylinder sides 5, 6 are closed to the outside and the piston 3 - depending on the pressure level - is held more or less firmly in its position.
  • the two control slides 11, 12 can be acted upon independently by control pressure via the separate inputs X and Y and can each control the movement of the piston 3 in one direction by different joint, simultaneous action on the two cylinder sides, for example the braking of the piston 3 when approaching its target position or bracing at this target position can be achieved with very simple means.
  • control slides 11, 12 used in the housing bores 34 together with the insert bushes 15, 16 are supported by separate compression springs 13, 14 on a lower housing cover 35 and are pressed into their zero position under the action of these compression springs, in which they rest on an upper housing cover 36.
  • Two axially offset control edges 37, 38 and 39, 40 are arranged on each of the two control spools 11, 12, which more or less release the opening cross section of the control openings 20, 22, 23, depending on the axial position of the control spools.
  • 36 inlet bores for the connections X, Y for the respective control pressure are made in the upper housing cover.
  • control pressure is applied to the inlet Y, whereby the first control edge 39 opens the control openings 23 and the second control edge 40 opens the control openings 20 and the exhaust air connection 5 is connected to the first cylinder side 5 and the pressure connection P to the second cylinder side 6.
  • the actuation of the two control slides 11, 12 can, however, also take place together, so that differentiated movement or pressure conditions can be realized on both cylinder sides depending on the control pressure applied on both sides.
  • Pilot valves for the control pressure could also be attached directly to the inputs X, Y for the control pressure, which means that there is very little clearance for the control pressure, especially in the delicate area around the zero position of the two control spools, and a very quick response to changes in the control pressure, which is particularly the case the vicinity of the zero crossing is very advantageous for precise positioning.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (6)

1. Unité-vanne multivoie du type 5/3, pour le positionnement d'un vérin pneumatique à double action (2, 3), comportant un élément de commande (11, 12) déplaçable sous l'action d'une pression de commande, contre une force de rappel, dans un corps présentant des organes de raccordement de fluide pouvant être commandés, ledit élément de commande se trouvant, pour des pressions de commande inférieures au niveau de pression nécessaire pour surmonter la force de rappel, à sa position zéro fermant tous les organes de raccordement de fluide, caractérisée par le fait que l'élément de commande est constitué par deux tiroirs de commande (11, 12) agencés séparément dans le corps (10), lesquels présentent chacun deux arêtes de commande décalées axialement (37, 38; 39, 40) coopérant avec deux organes de raccordement de fluide (A, B, S, P, R), et peuvent être sollicités séparément par de la pression de commande, les arêtes de commande (37, 38) du premier tiroir de commande (11) commandant l'air entrant du premier côté (5) et l'air sortant du deuxième côté (6) du cylindre, et les arêtes de commande (39, 40) du deuxième tiroir de commande (12) commandant l'air entrant du deuxième côté (6) et l'air sortant du premier côté (5) du cylindre.
2. Unité-vanne selon revendication 1, caractérisée par le fait que les deux tiroirs de commande séparés (11, 12) sont guidés dans des douilles d'insertion (15, 16) dans le corps (10), lesquelles présentent des orifices de commande (17 à 23) se trouvant en communication avec les organes de raccordement de fluide (A, B, S, P, R), et par le fait qu'aussi bien les tiroirs de commande (11, 12) que les douilles d'insertion (15, 16) sont réalisés de manières identiques.
3. Vanne selon revendication 1 ou 2, caractérisée par le fait que les deux tiroirs de commande (11, 12) sont sollicités par la force de rappel, à partir du corps (10), par des ressorts de compression séparés (13, 14).
4. Unité-vanne selon l'une des revendications 1 à 3, caractérisée par le fait que les deux tiroirs de commande (11, 12) sont agencés parallèlement dans le corps (10), l'un à côté de l'autre, et par le fait que les organes de raccordement (X, Y) pour la pression de commande se trouvent chacun du même côté du corps.
5. Unité-vanne selon l'une des revendications 1 à 4, caractérisée par le fait qu'en partant à chaque fois du côté de l'organe de raccordement (X, Y) pour la pression de commande, la première arête de commande (37) du premier tiroir de commande (11) commande l'air de sortie du deuxième côté (6) du cylindre, la deuxième arête de commande (38) du premier tiroir de commande (11) commande l'air d'entrée du premier côté (5) du cylindre, la première arête de commande (39) du deuxième tiroir de commande (12) commande l'air de sortie du premier côté (5) du cylindre et la deuxième arête de commande (40) du deuxième tiroir de commande (12) commande l'air d'entrée du deuxième côté (6) du cylindre.
6. Unité-vanne selon l'une des revendications 1 à 5, caractérisée par le fait que, pour solliciter séparément les deux tiroirs de commande avec de la pression de commande, des vannes-pilotes sont rapportées sur le corps, directement sur les organes de raccordement pour la pression de commande.
EP19860890351 1985-12-30 1986-12-19 Unité de vanne à 5/3 voies Expired - Lifetime EP0238782B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT377485A AT391178B (de) 1985-12-30 1985-12-30 5/3-wege-ventileinheit
AT3774/85 1985-12-30

Publications (3)

Publication Number Publication Date
EP0238782A2 EP0238782A2 (fr) 1987-09-30
EP0238782A3 EP0238782A3 (en) 1988-02-10
EP0238782B1 true EP0238782B1 (fr) 1991-07-17

Family

ID=3555245

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19860890351 Expired - Lifetime EP0238782B1 (fr) 1985-12-30 1986-12-19 Unité de vanne à 5/3 voies

Country Status (5)

Country Link
EP (1) EP0238782B1 (fr)
JP (1) JPH0660697B2 (fr)
CN (1) CN1010242B (fr)
AT (1) AT391178B (fr)
DE (1) DE3680324D1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5921279A (en) * 1998-04-29 1999-07-13 Husco International, Inc. Solenoid operated dual spool control valve
US7114521B2 (en) * 2003-09-03 2006-10-03 Ross Operating Valve Company Double valve constructed from unitary single valves
CN1295440C (zh) * 2004-03-08 2007-01-17 尚继良 装载机用整体式手动多路换向阀
DE102008054977B4 (de) * 2008-12-19 2014-01-23 Zf Friedrichshafen Ag Schaltanordnung
US8794123B2 (en) * 2010-03-12 2014-08-05 Ross Operating Valve Company Double valve constructed from unitary single valves
CN105697441A (zh) * 2016-01-08 2016-06-22 洪子云 液压行程自动换向阀及旋泵成孔桩机液压控制系统
CN107830212B (zh) * 2017-11-30 2024-03-26 安徽中捷矿山运输设备有限责任公司 三位五通气控换向阀
CN110530074B (zh) * 2019-08-30 2021-01-19 杭州师范大学钱江学院 一种六通阀、基于六通阀的热交换系统及其热交换方法

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3709244A (en) * 1970-11-04 1973-01-09 H Zadow Free foil flow control device
BE789975A (fr) * 1971-10-12 1973-02-01 Sanders Associates Inc Valve de controle de pression et de debit
GB1600155A (en) * 1977-02-28 1981-10-14 Budzich Tadeusz Load responsive fluid control valve
US4349041A (en) * 1979-08-20 1982-09-14 Nl Industries, Inc. Control valve system for blowout preventers
US4461449A (en) * 1980-05-01 1984-07-24 The Boeing Company Integral hydraulic blocking and relief valve

Also Published As

Publication number Publication date
AT391178B (de) 1990-08-27
CN86108885A (zh) 1987-09-23
DE3680324D1 (de) 1991-08-22
JPS62237180A (ja) 1987-10-17
CN1010242B (zh) 1990-10-31
EP0238782A2 (fr) 1987-09-30
EP0238782A3 (en) 1988-02-10
ATA377485A (de) 1990-02-15
JPH0660697B2 (ja) 1994-08-10

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