EP0005818B1 - Vanne à 3 voies à commande hydraulique - Google Patents

Vanne à 3 voies à commande hydraulique Download PDF

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Publication number
EP0005818B1
EP0005818B1 EP19790101638 EP79101638A EP0005818B1 EP 0005818 B1 EP0005818 B1 EP 0005818B1 EP 19790101638 EP19790101638 EP 19790101638 EP 79101638 A EP79101638 A EP 79101638A EP 0005818 B1 EP0005818 B1 EP 0005818B1
Authority
EP
European Patent Office
Prior art keywords
control
piston
valve
way seat
connection
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
Application number
EP19790101638
Other languages
German (de)
English (en)
Other versions
EP0005818A1 (fr
Inventor
Wolfgang Beyer
Peter Graner
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth 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 Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP0005818A1 publication Critical patent/EP0005818A1/fr
Application granted granted Critical
Publication of EP0005818B1 publication Critical patent/EP0005818B1/fr
Expired 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 hydraulically operated 3-way seat valve with two switching positions.
  • Directional valves are actuated in a known manner by pilot valves, the directional valve occupying one switching position in the one switching position of the respective pilot valve and the directional valve assuming the other switching position in the other switching position of the pilot valve. So that the directional control valve remains in the respective switching position, it is necessary that the control pressure acts continuously on the control piston side in question. If this control pressure fails due to a fault in the system, the switch position of the directional valve in question is no longer guaranteed.
  • a valve according to the preamble of claim 1 is known.
  • the only pilot valve is operated electromagnetically.
  • the object of the invention is to provide a hydraulically actuated 3-way seat valve with two switch positions, which, regardless of the failure of the control fluid pressure, maintains the switch position once it has been taken, similar to how this is ensured using mechanical catches and at the same time offers the possibility of combining it with one further to create a valve unit that also fulfills the function of a 4-way seat valve, regardless of the control pressure, maintaining its switching position.
  • Fig. 1 denotes a hydraulically operated 3-way seat valve with two switching positions and 2 the other hydraulically operated 3-way seat valve with two switching positions.
  • Each 3-way seat valve has a control piston 3, 4, which has seat surfaces 3a, 3b and 4a, 4b, which interact with corresponding seat surfaces 5a, 5b and 6a, 6b in the housing.
  • Each control piston 3, 4 has cylindrical projections 3c, 3d and 4c, 4d on both sides, which cooperate with housing bores 8, 9 and 10, 11, respectively.
  • the actuating piston 12 is connected to the control piston 4 via a connecting rod 13.
  • the actuating piston 12 has a larger surface 12a and a smaller ring surface 12b.
  • the control chamber 15 delimited by the smaller annular surface 12b is in direct connection with the housing bore 11 which, depending on the switching position of the control piston 4, can be closed or opened by its cylindrical extension 4d.
  • the actuating piston 16 With the cylindrical projection 3d of the closing body 3, the actuating piston 16 is in a non-positive contact via a bolt-shaped extension.
  • the larger surface 16a of the actuating piston 16 delimits the control chamber 17.
  • the control chamber 17 is connected to the control chamber 20 of the control piston 12 via the control line 18.
  • the control chamber 21, delimited by the smaller annular surface 16b of the actuating piston 16, is in direct connection with the housing bore 9.
  • the control chamber 15 of the 3-way seat valve 2 is permanently connected to the pressure medium source 23 via the pressure line 22 and the control chamber 21 of the 3-way seat valve 1 via the tank line 24 to the tank T.
  • the housing bore 8 corresponds to the cylindrical projection 3c of the control piston 3 of the 3-way seat valve 1 cooperates, is connected via the connecting line 26 with the control chamber 15 and thus also with the pressure medium source, so that the cylindrical extension 3c is constantly acted upon by the control medium pressure, so that the closing body 3 in Direction of the control chamber 21 connected to the tank is loaded.
  • the cylindrical extension 3c forms the actuating piston in the direction of the switching position of the control piston 3 shown.
  • the housing bore 10, with which the cylindrical extension 4c of the control piston 4 of the 3-way seat valve 2 interacts, is in permanent connection via the line 27 with the tank line 24 and thus with the tank T.
  • the valve chamber 30 of the 3-way seat valve 1 is connected via line 31 to the working line connection A and the valve chamber 33 of the 3-way seat valve 2 is connected via line 34 to the working line connection B. From the line 34 branches off a control line 35 which opens into the control line 18 via a throttle 36 and is thus connected both to the control chamber 20 of the 3-way seat valve 2 and to the control chamber 17 of the 3-way seat valve 1 .
  • the control rooms 17, 20 are also located via the control line 18 and via the control line sections 18a, 18b with the pilot valve 38 and via the control line 18 and the control line sections 18a, 18c to the pilot valve 39 in connection.
  • the pilot valves 38, 39 are designed as 3-way seat valves with two switching positions a and b.
  • the connection St of the pilot valve 38 is connected via the control line 40 to the control medium source, which is formed by the pressure medium source 23.
  • the junction of the control line 40 into the pressure medium line 22 of the pressure medium source 23 takes place between the pressure medium source 23 and the check valve 41, which is arranged between the pressure medium source 23 and the directional control valve 2.
  • the connection Ta of the pilot valve 38 is connected to the control line 42 leading to the tank.
  • the connection Ta and the connection K of the pilot valve 39 are connected to the control line 42 and thus to the tank T via the control line sections 42a, 42b.
  • the connecting line 35 is connected to the working line 34 with throttle 36 also the control line section 18 and thus also the control rooms 17 and 20 in connection with the tank. Since the control chamber 15 is in permanent connection with the pressure medium source 23, the actuating piston 12 is subjected to a greater force as a result of its larger annular surface 12b compared to the annular surface 4da of the cylindrical extension 4d of the control piston 4 in the direction of the control chamber 20, and thus the switching position shown with certainty guaranteed.
  • the switching position of the control piston 3 shown is also ensured. If the pilot valve 38 is briefly switched from the switching position b to the switching position a, the control line section 18b is connected to the control center line 40 via the check valve 45, so that the control chambers 17 and 20 of the 3-way seat valves are connected via the control line sections 18a, 18b, 18 1 and 2 are acted upon by the control medium pressure.
  • the actuating piston 12 displaces the control piston 4 in the direction of the housing seat surface 6a until the latter has reached the relevant new switching position in which the connection of the valve chamber 33 with the Housing bore 10 prevented and a connection between the valve chamber 33 with the housing bore 11 and valve chamber 15 is made and thus there is a connection of the working port B with the pressure medium source 23.
  • control piston 16 moves the control piston 3 in the direction of the housing seat surface 5a until the latter has reached the switch position in question, in which the connection between the valve chamber 30 and the housing bore 8 is interrupted and therefore the connection of the valve chamber 30 with the housing bore 9 and thus with the space 21 connected to the tank connection T via the tank line 24, so that the work line connection A is connected to the tank connection Tin.
  • the pilot valve 38 can be moved back into the starting position shown.
  • the required control pressure in the control rooms 17 and 20 to ensure the switching position is ensured on the one hand by the fact that the control rooms in the direction of the tank connection Y are closed by the closed pilot valve 39 designed as a seat valve and the check valve 45 arranged in the control line section 18b, and on the other hand via the connecting line 35 with throttle 36 and via the 3-way seat valve 2 there is a connection to the pressure medium connection after the working line connection B is connected to the pressure medium connection P in the new switching position of the 3-way seat valve 2.
  • the control piston 16 of the 3-way seat valve 1 is pressure-balanced, so that the closing body 3 is displaced back in the direction of the switching position shown by the pressure medium acting in the bore 8 on the shoulder 3c.
  • the closing body 4 of the 3-way seat valve 2 in his shifted position shown moved back, by the pressure medium acting in the control chamber 11 and the control piston 12 in the direction of the control chamber 20.
  • the pressure resulting therefrom acts both in the control chamber 11 of the 3-way seat valve 2 and in the valve chamber 30 of the 3-way seat valve 1. Pressure relief in the direction of the pressure medium source 23 is prevented by the check valve 41 in the pressure line 15.
  • the cylindrical lugs 3c, 3d and 4c, 4d of the closing body 3, 4 have such a length that when the closing body 3, 4 is shifted from one to the other switching position, the one cylindrical extension is in operative connection with the relevant housing bore stands until the other cylindrical extension is inserted into the relevant housing bore. This prevents the housing space 30 or 33 from being connected to the pressure medium source and the tank at the same time, that is to say a short-circuit position occurs.
  • Fig. 2 the same reference numerals as in Fig. 1 denote the same parts.
  • the closing bodies 3, 4 are guided in guide bodies 50, 51, which are connected to the valve spaces 30, 33 via transverse bores 52, 53, so that, depending on the switching position of the closing bodies 3, 4, the valve spaces 30 and 33 are connected to the respective ones Housing bores 8, 9 and 10, 11 is guaranteed.
  • the housings for the valves 1 and 2 are formed by a common housing block 55.
  • the dacalethsene- do g s are embedded as channels in this housing block 55th
  • the pilot valves 38, 39 which are designed as solenoid-operated 3-way seat valves with two switching positions, are screwed directly onto the valve housing block 55, so that no pipe connections are required between pilot valves and the 3-way seat valves 1 and 2 forming the main valves.

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

Claims (5)

1. Valve à sièges à trois voies et à deux positions de commutation, commandée hydrau- liquement et comportant un piston d'actionnement (12) en liaison d'entraînement avec le piston d'actionnement, agissant dans une direction de commutation et à soumettre à la pression de commande, présente une plus grande surface efficace que la face (12b) dudit piston d'actionnement, agissant dans l'autre direction de commutation et à soumettre à ladite pression de commande, la surface efficace la plus petite (12b) étant à soumettre en permanence à la pression de commande (23) et la surface efficace la plus importante (12a) étant à soumettre soit à ladite pression de commande, soit à la pression du réservoir, valve caractérisée par deux distributeurs pilotes (38, 39) consistant en deux valves à sièges à trois voies et à deux positions de commutation (a, b), dont l'un (39) commande la communication de la chambre de commande (20), associée à la surface la plus importante (12a) du piston d'actionnement, avec le réservoir (T), l'autre distributeur pilote (38) commandant la communication entre cette chambre de commande (20) et la source (23) de fluide de commande par l'intermédiaire d'un clapet anti- retour (45), ladite chambre de commande (20) étant reliée par l'intermédiaire d'un étranglement (36) au raccord d'utilisation (B) de la valve principale.
2. Valve à trois voies commandée hydraulique- ment selon la revendication 1, caractérisée par le fait que le piston d'actionnement (12) en liaison d'entraînement avec te piston de commande (4) est fixé à ce dernier (4), la surface efficace (12b) de ce piston d'actionnement orientée vers ledit piston de commande (4), étant plus petite que sa surface efficace (12a) opposée audit piston de commande (4).
3. Valve à trois voies commandée hydraulique- ment et comportant un chevauchement positif de commutation, selon les revendications 1 et 2, dans laquelle ledit chevauchement positif de commutation est assuré par des saillies cylindriques (4c,4d) disposées des deux côtés du piston de commande (4) et associées à des alésages du carter parcourus par le fluide de travail, valve caractérisée par le fait que l'un (11) desdits alésages du carter, communiquant avec le raccord (P) de la pompe et coopérant avec l'une (4b) desdites saillies cylindriques dudit piston de commande (4), est directement en communication avec la chambre de commande (15) délimitée par la surface la plus petite (12b) du piston d'actionnement (12).
4. Valve à trois voies commandée hydraulique- ment selon la revendication 1, caractérisée par le fait qu'elle est combinée avec une autre valve (1) à sièges à trois voies, commendée hydraulique- ment et comportant un chevauchement positif de commutation assuré par des saillies cylindriques disposées des deux côtés du piston de commande, dans laquelle une saillie cylindrique (3c) soumise à la pression de la pompe constitue en même temps le piston d'actionnement présentant la plus petite surface efficace, le piston d'actionnement (16), qui présente la surface efficace la plus grande (16a), constituant une partie distincte mise en liaison de transmission d'efforts par un prolongement (16c) en forme de tige avec le piston de commande (3), la chambre (9) entre ledit piston d'actionnement (16) et l'autre saillie cylindrique (3b) du piston de commande (17) dudit piston d'actionnement (16), opposée à ladite chambre (9), étant reliée par un étranglement (36) au raccord d'utilisation (3) de la première valve (2) à sièges et à trois voies.
5. Valve à trois voies commandée hydraulique- ment, dans laquelle le fluide de travail constitue le fluide de commande, selon une ou plusieurs des revendications précédentes, caractérisée par le fait qu'un clapet antiretour (41) est disposé entre la source (23) de fluide sous pression et la valve (1, 2), le fluide de commande pouvant être évacué entre ladite source de fluide sous pression et ledit clapet anti-retour.
EP19790101638 1978-06-03 1979-05-29 Vanne à 3 voies à commande hydraulique Expired EP0005818B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19782824461 DE2824461C2 (de) 1978-06-03 1978-06-03 Druckmittelsteuereinrichtung für einen doppelseitig beaufschlagbaren Verbraucher
DE2824461 1978-06-03

Publications (2)

Publication Number Publication Date
EP0005818A1 EP0005818A1 (fr) 1979-12-12
EP0005818B1 true EP0005818B1 (fr) 1981-11-25

Family

ID=6040979

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19790101638 Expired EP0005818B1 (fr) 1978-06-03 1979-05-29 Vanne à 3 voies à commande hydraulique

Country Status (2)

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EP (1) EP0005818B1 (fr)
DE (1) DE2824461C2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3102505A1 (de) * 1981-01-27 1982-08-19 Robert Bosch Gmbh, 7000 Stuttgart "steuereinrichtung fuer ein hydraulisches arbeitsgeraet"
CN109296816B (zh) * 2018-11-28 2023-12-01 陕西航天泵阀科技集团有限公司 机械切换分注装置

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7704002U1 (fr) * 1900-01-01 Kugelfischer Georg Schaefer & Co, 8720 Schweinfurt
GB685925A (en) * 1949-10-07 1953-01-14 Electro Hydraulics Ltd Improvements in or relating to valve devices
FR1078604A (fr) * 1953-04-02 1954-11-19 Lecq Et Cie Soc Dispositif d'enclenchement et de déclenchement pneumatique
US3318331A (en) * 1964-01-18 1967-05-09 W E & F Control valve for high pressure hydraulic cylinders and the like
FR1391950A (fr) * 1964-01-29 1965-03-12 Merlin Gerin Dispositif de commande hydropneumatique, notamment pour disjoncteurs électriques
US3646968A (en) * 1970-09-30 1972-03-07 Sperry Rand Corp Power transmission valve with detent
FR2116863A5 (fr) * 1970-12-10 1972-07-21 Gratzmuller Jean Louis Commande hydraulique a deux voies
DE2632547A1 (de) * 1976-07-20 1978-01-26 Helmut Prof Dipl Ing Kampmann Mehrwegeventil fuer die ausbauhydraulik im bergbau

Also Published As

Publication number Publication date
DE2824461A1 (de) 1979-12-06
DE2824461C2 (de) 1986-12-11
EP0005818A1 (fr) 1979-12-12

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