EP0083688B1 - Soupape d'étranglement proportionnelle pilotée électro-hydrauliquement - Google Patents

Soupape d'étranglement proportionnelle pilotée électro-hydrauliquement Download PDF

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Publication number
EP0083688B1
EP0083688B1 EP82108826A EP82108826A EP0083688B1 EP 0083688 B1 EP0083688 B1 EP 0083688B1 EP 82108826 A EP82108826 A EP 82108826A EP 82108826 A EP82108826 A EP 82108826A EP 0083688 B1 EP0083688 B1 EP 0083688B1
Authority
EP
European Patent Office
Prior art keywords
piston
differential
choke
valve
pilot
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
EP82108826A
Other languages
German (de)
English (en)
Other versions
EP0083688A3 (en
EP0083688A2 (fr
Inventor
Karl-Heinz Dr. 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.)
Oerlikon Barmag AG
Original Assignee
Barmag Barmer Maschinenfabrik 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 Barmag Barmer Maschinenfabrik AG filed Critical Barmag Barmer Maschinenfabrik AG
Publication of EP0083688A2 publication Critical patent/EP0083688A2/fr
Publication of EP0083688A3 publication Critical patent/EP0083688A3/de
Application granted granted Critical
Publication of EP0083688B1 publication Critical patent/EP0083688B1/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
    • F15B13/042—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

Definitions

  • the invention relates to an electro-hydraulically pilot-controlled proportional throttle valve, the throttle piston of which is mechanically connected to a double-acting control piston which can be controlled hydraulically by an electromagnetically actuated pilot valve on returning the position of the throttle piston to the pilot valve.
  • This proportional throttle valve is known from French FR-A-2 235 300. With this valve, the throttle piston is guided at both ends in pressure chambers which can be acted upon by a pilot valve with different pilot pressures. This causes the throttling of oil flows with the axial displacement of the throttle piston.
  • the pilot valve of the pilot valve is connected to the throttle piston by a spring rod. As a result, the pilot force exerted on the throttle piston is returned to the position of the pilot spool.
  • This valve construction cannot be used for a 2-way cartridge valve.
  • a proportional throttle valve which consists of a 2-way cartridge valve which is acted upon by a control pressure on the side facing away from the pump pressure and by a closing spring in the closing direction.
  • the control pressure is controlled by a pilot spool depending on an electro-magnetically input command variable, the current throttle piston position is returned to the pilot spool by a helical spring clamped between the two ("Oil hydraulics and pneumatics" 1981, page 35).
  • this throttle valve works too slowly in the closing direction for some applications if there is no pressure difference between the oil inlet and the oil outlet.
  • the pilot solenoid is at full pump pressure.
  • the throttle valve according to the invention is also an electro-hydraulic pilot-controlled proportional throttle valve, which is characterized in that the throttle piston is actuated by means of a differential piston.
  • the differential piston is firmly connected to the throttle piston by a piston rod.
  • the differential piston is guided in a differential cylinder and is acted upon on both sides with the control pressures given by the pilot valve and its position in a control loop is fed back to the pilot.
  • the diameter of the differential piston is larger than the throttle piston.
  • the piston rod-side ring surface of the differential piston delimits the opening-side control pressure chamber of the differential cylinder with the second end face of the throttle piston, and the ring surface facing away from the differential piston, together with a locking piston / relief piston arrangement, delimits the closing-side control pressure chamber of the differential cylinder.
  • the locking piston / relief piston arrangement has the same diameter as the throttle piston and is acted upon on the end face facing away from the differential piston with the same working pressure as the first end face of the throttle piston.
  • the mechanical position feedback is preferably done by a spring supported between the throttle piston and the pilot spool.
  • Throttle valves the throttle piston of which is connected to a differential piston
  • US Pat. No. 3,604,459 shows a throttle valve, the throttle piston of which is connected to a larger piston.
  • this valve has no electro-hydraulic pilot control with feedback and the valve only acts as an on / off valve, without the possibility of a constant adjustment of the throttle point.
  • the differential pistons shown in DE-B 2112 813 and DE-A 2 533 829 also lack the possibility of actuating these 2-way cartridge valves. Finally, there is no mechanical position feedback between the throttle piston and the pilot valve.
  • the throttle piston and pilot spool are movable parallel to one another, and the spring supported between the two is a spring rod which is firmly clamped either on the throttle piston, on the piston rod or on the pilot spool.
  • the spring rod avoids a common disadvantage of the coil springs, fatigue.
  • a pressure relief bore can penetrate the throttle piston, piston rod and differential piston and open into a counterpressure chamber sealed by a pressure relief piston.
  • the differential piston can lie in a common differential cylinder, the effective area difference on the closing side from the relief piston being greater than the area difference on the opening side.
  • the solution according to the invention ensures that the actuation of the throttle piston in both directions depends solely on the pilot control. This ensures that the throttle valve closes reliably even when there are no significant pressure differences in the conveyor system. Another advantage is the fact that the throttle valve is useful and effective in both flow directions.
  • the proportional valve 1 has a throttle piston 5, which controls an oil flow in the direction of passage 4.1 or 4.2.
  • This throttle piston is firmly connected to the differential piston 7 by piston rod 6.
  • the differential piston slides in the differential cylinder 23, which is delimited on the closing side 21 by piston surface 16 on the locking piston 20 and on the opening side 22 by piston surface 17 on the throttle piston 5.
  • the pressure relief piston 13 is seated in the counterpressure chamber 15, which is connected to the end face of the throttle piston via a pressure relief duct 12 and is so large that on the unit comprising the throttle piston, piston rod and pressure relief piston the hydraulic medium caused by the medium is balanced Forces occur in the direction of movement of the piston rod.
  • a pilot spool 3 moved by means of an electromagnet 2 can be moved parallel to the unit comprising throttle piston 5, piston rod 6, differential piston 7 and pressure relief piston 13 and - initially - assumes a position (current) corresponding to the pilot signal (current) given to the electromagnet 2, as a result of which one of the two control pressure lines 8 , 9 to the opening side 22 or closing side 21 of the differential cylinder 23 is released; the differential piston moves accordingly and thus the throttle piston.
  • the spring rod exerts one force on the pilot spool on the one hand and the throttle piston on the other Restoring force that is in balance with the magnetic force on the pilot spool on the one hand and the hydraulic force on the differential piston on the other.
  • the throttle piston position is returned to the pilot control.
  • the position of the pilot spool 3 is corrected in accordance with the position of the throttle piston 5 in relation to the pilot signal.
  • the area ratios in the differential pistons are important.
  • the piston surface 10 acts in the closing direction, reduced by the piston surface 16 on the locking piston 20. This surface difference is greater than the surface 14 effective in the opening direction, reduced by the surface 17 on the throttle piston.
  • the pilot pressure is effective via channel 18, connecting channel 19 and leaks both on the piston surface 10 and on the counter surface 14. Because of the area ratio, the throttle piston is pressed in the closing direction. If the electromagnet 2 is excited to open the throttle piston 5 so that the pilot spool moves downward (drawing), the annular space 26 and the channel 8 are connected to the connecting channel 19 and the annular channel 27 to the drain (not shown here) to the tank.
  • the valve according to the invention has the advantage that it can be controlled hydraulically, but independently of the medium and its pressure.
  • the pilot pressure channel 18 is connected to a suitable pressure source that delivers a sufficiently high pressure. This enables safe opening and closing at high speeds, even if the throttle valve controls a medium with very low pressure.
  • the pilot pressure channel (18) can also be connected to one of the lines between which the throttle piston controls the flow. It is worth mentioning that even relatively low system pressures are sufficient, since the closing speed and closing force can also be influenced by specifying the area ratio on the differential piston.
  • the valve has the further advantage that it can be flowed through in both directions (arrows 4.1 and 4.2).
  • FIG. 2 shows a modification of the throttle valve according to FIG. 1, with the same structure and the same properties.
  • the throttle valve can be flowed through in the two flow directions (arrow 4.1 and 4.2).
  • Special measures also ensure that the switching speed and the leak-free seal of the throttle piston are guaranteed both with very small pressure differences between the inlet and outlet (i.e. especially with large flow rates) and with pressure drop in one of the lines 28, 29.
  • Fig. 2 it is shown in Fig. 2 that the magnet 2 has a plunger 30 which acts on the pilot valve 3. Also shown is the tank channel 31 which, through the tank bridge 32, depressurises the pilot cylinder at both ends.
  • the pilot valve acts as a hydraulic bridge (Wheatstone measuring bridge), by means of which different control pressures are generated in the pilot channels 8 and 9 for actuating the differential piston 7. In contrast to the exemplary embodiment according to FIG. 1, this acts on the throttle piston 5 2 in Counter pressure chamber 15 accommodated spring 33 in the closing direction. This achieves the following: It may be desirable to constantly load the closing side 21 of the differential piston with a low pressure.
  • the magnet 2 and pilot spool 3 are set so that there is a small - not representable - gap on the piston collar 25 constantly and also in the zero position of the pilot valve or closed position of the throttle piston 5, through which a small oil flow from the connecting channel 19 to the Closing side of the differential piston 7 arrives.
  • this small gap means a slight displacement of the pilot spool 3 upwards and thus also a correspondingly small deflection of the spring 11, combined with an upwardly directed small spring force.
  • the spring 32 now serves the purpose of compensating for this spring force, which acts undesirably in the opening direction of the throttle piston 5.
  • Fig. 2 it is also shown that the pilot pressure channel 18 is alternately acted upon by the pressure of the lines 28 or 29.
  • a shuttle valve 34 is provided. Its inputs are connected to line 29 on the other hand.
  • the central outlet 35 of the shuttle valve 34 leads into the pilot pressure channel 18.
  • the shuttle valve 34 causes the higher pressure of the lines 28 or 29 to be present in the pilot pressure channel 18. If the pressure is equal, both pressures of the lines 28, 29 are equally effective. When changing the current directions (arrows 4.1, 4.2), the control pressure is automatically switched.
  • the pilot valve is also supplied with the required pressure oil when one of the lines 28 or 29 is depressurized, e.g. by connecting it to the tank.
  • any other pressure-dependent switchable valve can be used.
  • the shuttle valve is characterized by its robust and simple construction.
  • Fig. 3 shows an embodiment in which only one current direction (arrow 4.1) is possible.
  • the control pressure is always taken from line 29 via the central pressure relief channel 12.
  • FIGS. 1 and 2 the advantage of the valves according to FIGS. 1 and 2 is also retained here:
  • This valve is also independent of the pressure difference between lines 29 and 28.
  • the closing force and closing speed also depend on the surface conditions on the differential piston 7, so that even low system pressures are sufficient for pilot control.
  • the seating force can also be promoted in that the closing side of the differential piston 7 is pressurized even when the throttle piston or pilot valve is in the zero position.
  • This can - as described in Fig. 2 - happen that magnet 2 and pilot spool 3 are in turn adjusted so that in the zero position of the pilot spool 3 on the piston collar 25 a small gap for connecting the control pressure line 9 to the connecting channel 19 is opened.
  • a relatively weak compression spring 36 is provided for the slight displacement of the fore). Otherwise, the throttle valve according to FIGS.
  • the pressure relief channel does not have to be in the piston rod. It can also extend parallel to it in the hanger from the channel 29 into the counter-pressure chamber 15, so that the two equally effective piston surfaces at the ends of the piston rod, i.e. the end face of the throttle piston 5 and the effective piston surface of the pressure relief piston 15 (Fig. 1; Fig . 2) or the locking piston 20 (Fig. 3) are pressure balanced.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)
  • Safety Valves (AREA)

Claims (7)

1. Une soupape d'étranglement proportionnelle (1) pilotée électro-hydrauliquement
qui comprend:
un distributeur pilote (2, 3) actionné par voie électromagnétique,
un distributeur principal (1) comportant un piston d'étranglement (5) qui est relié mécaniquement à un piston de commande (7) à double effet, et un organe de rappel mécanique (11) disposé entre le piston d'étranglement (5) et le tiroir pilote (3),
caractérisée en ce
qu'un côté frontal du piston d'étranglement (5) est soumis à l'action du fluide hydraulique, que le piston de commande est réalisé sous forme d'un piston différentiel (7), dont le diamètre est plus grand que celui du piston d'étranglement (5) et qui est relié par une tige de piston (6) au deuxième côté frontal (17) du piston d'étranglement et peut coulisser dans un vérin différentiel (23),
que la chambre de pression de commande (22) du vérin différentiel (23) située au côté d'ouverture du vérin différentiel (23) et de la surface d'anneau (14) de la tige de piston du piston différentiel (7), est bordée par le deuxième côté frontal (17) du piston d'étranglement (5),
que la chambre de pression de commande (21) du vérin différentiel (23) située au côté de fermeture du vérin différentiel (23) et de la surface (10) du piston differentiel (7), est bordée par un ensemble piston de blocage/piston d'équilibrage (20, 13) relié au piston différentiel (7) et ayant le même diamètre que le piston d'étranglement (5), et que le côté frontal de l'ensemble piston de blocage/ piston d'équilibrage (20, 13) opposé au piston différentiel (7) est soumis à l'action de la même pression de fonctionnement que le premier côté frontal du piston d'étranglement (5).
2. Dispositif suivant la revendication 1,
caractérisé en ce
que l'organe de rappel mécanique (11) est un ressort qui est étançonné entre le piston d'étranglement (5) et le tiroir pilote (3).
3. Dispositif suivant la revendication 2,
caractérisé en ce
que le piston d'étranglement (5) et le tiroir pilote (3) sont déplaçable parallellement l'un par rapport à l'autre,
et que le ressort est réalisé sous forme d'une barre elastique (11), dont l'un côté est serré à la tige de piston (6) et dont l'autre côté est articulé sur le tiroir pilote (3).
4. Dispositif suivant l'une quelconque des revendications 1 à 3, caractérisé en ce
qu'un conduit d'équilibrage de la pression (12) traverse le piston d'étranglement (5), la tige de piston (6), le piston différentiel (7) et l'ensemble piston de blocage/piston d'équilibrage (20, 13) et débouche dans une chambre de contre-pression (15) qui est fermée par l'ensemble piston de blocage/piston d'équilibrage (20, 13) au côté regardant le piston d'étranglement (5).
5. Dispositif suivant l'une quelconque des revendications 1 à 3,
caractérisé en ce
qu'un piston d'équilibrage (13) et un piston de blocage (20) sont disposés à une distance axiale sur la tige de piston (6), le piston de blocage (20) bordant au côté de fermeture (21) du vérin différentiel (23) et le piston d'équilibrage (13) fermant à l'extrémité de la tige de piston une chambre de contre-pression (15) qui est reliée (conduit d'équilibrage de la pression 12) au conduit (29) amenant le fluide hydraulique et débouchant coaxialement par rapport à la tige de piston (6) dans la soupape (1),
et que la chambre de cylindre entre le piston de blocage (20) et le piston d'équilibrage de la pression (13) est en communication avec le côté sous pression du côté hydraulique (29 ou 28), d'une part, et, d'autre part, avec le distributeur pilote par l'intermédiaire du canal de raccordement (19).
6. Dispositif suivant la revendication 5,
caractérisé en ce
que la chambre de cylindre entre le piston de blocage (20) et le piston d'équilibrage de la pression (13) est en communication avec les conduits d'amenée et de décharge (28, 29) de fluide hydraulique par l'intermédiaire d'un sélécteur de circuit (34), dont les entrées sont reliées aux conduits (28, 29) et dont la sortie centrale (35) est reliée à l'entrée du distributeur pilote.
7. Dispositif suivant l'une quelconque des revendications 1 à 6,
caractérisé en ce
que la tige de piston (6) est soumise en sens de la fermeture à l'action d'un ressort compensateur (33).
EP82108826A 1981-09-26 1982-09-24 Soupape d'étranglement proportionnelle pilotée électro-hydrauliquement Expired EP0083688B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3138345 1981-09-26
DE3138345 1981-09-26

Publications (3)

Publication Number Publication Date
EP0083688A2 EP0083688A2 (fr) 1983-07-20
EP0083688A3 EP0083688A3 (en) 1984-03-28
EP0083688B1 true EP0083688B1 (fr) 1986-08-13

Family

ID=6142675

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82108826A Expired EP0083688B1 (fr) 1981-09-26 1982-09-24 Soupape d'étranglement proportionnelle pilotée électro-hydrauliquement

Country Status (3)

Country Link
US (1) US4535966A (fr)
EP (1) EP0083688B1 (fr)
DE (1) DE3272593D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023165745A1 (fr) * 2022-03-04 2023-09-07 Hydac Fluidtechnik Gmbh Soupape électromagnétique à commande pilote

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DE3420400A1 (de) * 1984-06-01 1985-12-05 Mannesmann Rexroth GmbH, 8770 Lohr Zwei-wege-sitzventil
US4738104A (en) * 1985-03-23 1988-04-19 Barmag Ag Hydraulic power system
DE3532591A1 (de) * 1985-09-12 1987-03-19 Rexroth Mannesmann Gmbh Hydraulische vorrichtung, insbesondere 2-wege-proportionaldrosselventil
DE3805288A1 (de) * 1988-02-19 1989-08-31 Rexroth Mannesmann Gmbh Regelventil
EP0329813A1 (fr) * 1988-02-26 1989-08-30 Nordson Corporation Dispositif à soupape pour l'application intermittente de colle liquide sur un substrat
US5156177A (en) * 1990-10-24 1992-10-20 Woodward Governor Company Flow loading unloader valve
US5131427A (en) * 1991-08-06 1992-07-21 Flint Hydraulic, Inc. Pilot operated relief valve
LU88384A1 (de) * 1993-07-16 1995-02-01 Hydrolux Sarl 2-Wege-Einbauventil als Sitzventil
US5762316A (en) * 1995-10-04 1998-06-09 Kraft Foods, Inc. Valve mechanism with improved sealing
DE19756600C1 (de) * 1997-12-18 1999-08-26 Brueninghaus Hydromatik Gmbh Leistungsregelventil
KR101259302B1 (ko) * 2008-11-26 2013-05-06 파커 하니핀 게엠베하 압력 평형 방식으로 배열된 폐쇄 요소를 나타내는 카트리지 밸브 인서트를 구비한 유압 밸브 조립체
US8371552B2 (en) * 2008-12-11 2013-02-12 GM Global Technology Operations LLC Shift actuator valve having a pressure dead band
CN101943188B (zh) * 2010-04-29 2013-08-21 上海人豪液压技术有限公司 采用组合式法兰控制盖板的紧凑型二通插装阀
CN107387477B (zh) * 2017-07-20 2018-11-06 徐州工业职业技术学院 一种用于滑阀的先导控制装置、液压缸控制回路
DE102018122437A1 (de) * 2018-09-13 2020-03-19 Eto Magnetic Gmbh Proportionalventil
CN111894928B (zh) * 2020-07-31 2022-03-25 国机铸锻机械有限公司 一种带有电磁隔离的超高压二通插装式比例减压阀

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023165745A1 (fr) * 2022-03-04 2023-09-07 Hydac Fluidtechnik Gmbh Soupape électromagnétique à commande pilote

Also Published As

Publication number Publication date
EP0083688A3 (en) 1984-03-28
US4535966A (en) 1985-08-20
DE3272593D1 (en) 1986-09-18
EP0083688A2 (fr) 1983-07-20

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