EP0017592B1 - Dispositif d'actionnement hydraulique à cinq positions - Google Patents

Dispositif d'actionnement hydraulique à cinq positions Download PDF

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Publication number
EP0017592B1
EP0017592B1 EP80400457A EP80400457A EP0017592B1 EP 0017592 B1 EP0017592 B1 EP 0017592B1 EP 80400457 A EP80400457 A EP 80400457A EP 80400457 A EP80400457 A EP 80400457A EP 0017592 B1 EP0017592 B1 EP 0017592B1
Authority
EP
European Patent Office
Prior art keywords
output element
equilibrium
neutral position
hydraulic actuating
positions
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
EP80400457A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0017592A1 (fr
Inventor
Philippe Debrus
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.)
DBA SA
Original Assignee
DBA SA
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 DBA SA filed Critical DBA SA
Publication of EP0017592A1 publication Critical patent/EP0017592A1/fr
Application granted granted Critical
Publication of EP0017592B1 publication Critical patent/EP0017592B1/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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F15B11/12—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action
    • F15B11/13—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action using separate dosing chambers of predetermined volume
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F15B11/12—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action
    • F15B11/121—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action providing distinct intermediate positions
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F15B11/12—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action
    • F15B11/121—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action providing distinct intermediate positions
    • F15B11/123—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action providing distinct intermediate positions by means of actuators with fluid-operated stops
    • 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
    • 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
    • Y10T137/86622—Motor-operated
    • Y10T137/8663—Fluid motor

Definitions

  • the subject of the present invention is a hydraulic actuation device with five positions and digital input, and more precisely a device of this kind comprising a movable output member occupying at rest a neutral position towards which the elastic centering means urge it and capable of moving against the latter on either side of said neutral position to occupy one or the other of two working positions defined by stop means, the movements of this movable member being caused by opposing hydraulic actuating means each assigned to a direction of movement and themselves selectively controlled by two control members in two positions receiving input orders of a digital nature.
  • the movable outlet member is constituted by the drawer of a four-way hydraulic distributor, which can for example control a double-acting hydraulic cylinder; in this case, the neutral position of the distributor drawer isolates the two working chambers of the jack from a source of pressurized fluid, thus immobilizing its piston, while both of the working positions of the drawer cause the placing in communication with this source of pressurized fluid of one or the other of the working chambers of the jack, thus causing the displacement of its piston in one direction or the other at an identical speed or not.
  • the dispenser drawer is capable of occupying only three distinct positions, this as a function of the input orders issued in the form of binary control words to the control members themselves constituted, for example, by three-way and two-position solenoid valves. And there is therefore only one speed for each direction of movement of the piston of the hydraulic cylinder.
  • the dispenser drawer can occupy a total of five distinct positions, namely, in addition to its neutral position, two successive working positions on either side thereof, these successive working positions corresponding to increasing values of the gain in flow rate of the pressurized fluid towards the considered working chamber of the jack.
  • Such a result can be obtained, for example, by means of movable stops intervening in turn on the dispenser drawer, but requires a priori an increased complexity of the control members, since, obviously, the two two-position solenoid valves each cannot receive a maximum of four separate binary command words.
  • the document DF-A-1 946 044 also describes a hydraulic actuation device with five positions comprising a movable outlet member, two centering springs, two auxiliary actuation pistons at the ends of the movable outlet member, and a control member which is constituted by a six-way and five-position slide valve, manually actuated, each of the distinct positions of the slide valve corresponding to the different positions of the hydraulic actuation device.
  • the object of the present invention is to propose a hydraulic control device of the type mentioned first above, and making it possible, with two two-position solenoid valves, to produce, simply, economically and reliably, a hydraulic actuation device with digital input with five distinct balance positions by means of only four binary control words.
  • the hydraulic actuation device with digital input comprising a movable output distributor member whose ends form opposing hydraulic actuating pistons, two elastic antagonistic centering means arranged in the vicinity of the ends of the outlet member and capable of urging the latter by means of two auxiliary pistons, the outer face of which is located in a control pressure chamber, the control means connected to the control and command pressure chambers, by opposing hydraulic actuating means, the displacement of the output member between five distinct equilibrium positions defined by stop means, is characterized in that the auxiliary pistons are biased by the elastic means towards the ends of the movable member and in that the control means comprise two control members nd electromagnetic two positions receiving digital input commands and whose output pipes are respectively connected to the control pressure chambers, the hydraulic actuating means having two active surfaces acting in the same direction on the output and intervening successively to communicate to this output member two successive displacement steps, the two active surfaces of each of the hydraulic actuating means are respectively constituted by said face of the auxiliary piston and by the face of
  • the scope of the invention is also not limited to obtaining two successive equilibrium positions on either side of the neutral position of the movable member Release; it can also extend in certain particular applications to obtaining an equilibrium position only on one side of the neutral position and three successive equilibrium positions on the other side of the latter; in such a case, the hydraulic cylinder controlled by such a device would be provided with a single speed of movement in one direction and three different speeds in the other direction. Other combinations would still be possible within the framework of the present invention.
  • the hydraulic actuation device comprises a movable outlet member 10 here constituted by a hydraulic distributor slide, which is provided with five cylindrical bearings 12, 14, 16, 18 and 20.
  • This drawer 10 is slidably received in a fixed bore 22, which is itself pierced with a certain number of orifices intended to cooperate with the edges delimiting the cylindrical surfaces of the drawer 10 to define fluid cross-sections. More specifically, one of these orifices, designated by the reference 24, is connected via a pipe 25 to a source of high pressure HP fluid (not shown in the drawing); while four other orifices 26, 28, 30 and 32 are connected via another line 27 to a BP fluid return tank (not shown either in the drawing either).
  • Two other orifices 34 and 36 are respectively connected, by means of outlet pipes U "U ?, To the two working chambers of a double-acting hydraulic cylinder, which is not in itself part of the invention and is not shown in the drawing.
  • Two other additional orifices 38 and 40 are connected respectively, via pipes 42 and 44, to two pressure chambers 46 and 48 as well as to the outputs of two EV electrovalves, and EV 2 constituting the actual control members of the device, each of the two pressure chambers 46 and 48, which are arranged coaxially with respect to the distributor slide 10 inside the body 22, contains a compression spring 50 or 52 which, by means of a bowl 54, or 56, tends to push towards the dispenser drawer a piston 58 or 60 which slides in leaktight manner in a fixed wall of the body 22, and the end of which is normally maintained in contact with one of the ext faces re-emitted from the drawer 10.
  • Each of the electrovalves EV, and EV 2 has two inputs respectively connected by branch pipes to the conduits 25 and 27.
  • Switches 1, and 1 2 are respectively provided for the actuation of these two solenoid valves, this so that, when the switch is open, the associated solenoid valve occupies a position such that it puts its output in communication with the return tank BP, while, when 'it is excited, it puts this same output into communication with the HP pressurized fluid source.
  • the hydraulic actuating means which control the movements of the outlet member to the right or to the left against the elastic centering means constituted by the springs 50 and 52 each consist of two active surfaces acting in the same direction on this outlet member (drawer 10) and intervening one after the other to communicate two successive displacement steps to it, the pressurization of the first of these surfaces being caused by the one of the electrovalves of control EV, or EV 2 and that of the second surface being it by the other of these electrovalves, but being however made possible only when this output member has already accomplished a first step of displacement in the intended meaning.
  • each of these hydraulic actuation means are respectively constituted by the face of a first piston 58 or 60 of relatively small section whose stroke is limited to a first step of displacement of the output member 10, and by the end face of the latter playing the role of a second piston of relatively large section which is mounted in series with the previous one and whose stroke also limited allows to cover a second step of movement .
  • the face of the second piston cannot itself be pressurized only provided that the movable outlet member 10 has already accomplished a first step of movement in the direction considered. It is obvious that the application of this general principle of the invention can be carried out by other technological means than those described above, which cannot therefore limit the scope of the invention.
  • control solenoid valves with reverse logic function, that is to say solenoid valves whose non-excitation state would result in a communication of their output with the source of pressurized fluid; in such a case, the binary command word corresponding to the neutral position would obviously be "11", those controlling the intermediate equilibrium positions would be “01” and “10” respectively, and the single command word for the positions of extreme balance would be "00 'succeeding the previous ones.
  • FIG. 4 of the drawings illustrates, simply by way of example, an alternative embodiment in which a single equilibrium position of the movable outlet member is provided on one side of the neutral position and three equilibrium positions of the other side of this same position, the representation of the design corresponding to the neutral position.
  • the ranges 14 'and 18' of the movable slide 10 ' are no longer symmetrically shaped with respect to its central range 16', as was the case in the embodiment of FIGS. 1 to 3.
  • control members here consist of two solenoid valves EV ', and EV' 2 with opposite logic functions, the first establishing communication with the source of fluid under pressure HP when it is not energized ( switch I ' 1 open), while the second establishes on the contrary this same communication when it is excited (switch 1 2 closed).
  • the pressure chamber 46 is connected to the source of HP fluid while chamber 48 is isolated therefrom; it follows that the piston 58 is pressed to the left and pushes the slide 10 'against the force developed by the spring 52; the distributor is however constructed in such a way that, for this position, the central cylindrical bearing surface 16 'of the slide 10' closes on its two sides the orifice for admission of pressurized fluid 24, while the bearing surfaces 14 'and 18' close the return orifices 28 and 30 respectively.
  • the outlet pipes U and U 2 are, as well as the working chambers of the hydraulic control cylinder, completely closed, which corresponds to the immobilization of the piston of this cylinder.
  • the closing of the switch 1 2 will have the effect of moving the drawer 10 'to the left, until it comes into abutment on its end face left against the wall of the fixed body 22.
  • closing the switch l ' would have the effect of eliminating the imbalance between the hydraulic thrusts acting on the slide 10', so that the latter would move one first step to the right under the action of the centering means constituted by the springs 50 and 52.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Driven Valves (AREA)
  • Servomotors (AREA)
  • Multiple-Way Valves (AREA)
  • Actuator (AREA)
EP80400457A 1979-04-06 1980-04-04 Dispositif d'actionnement hydraulique à cinq positions Expired EP0017592B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7908814 1979-04-06
FR7908814A FR2453306B1 (fr) 1979-04-06 1979-04-06 Dispositif d'actionnement hydraulique a cinq positions

Publications (2)

Publication Number Publication Date
EP0017592A1 EP0017592A1 (fr) 1980-10-15
EP0017592B1 true EP0017592B1 (fr) 1983-11-02

Family

ID=9224088

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80400457A Expired EP0017592B1 (fr) 1979-04-06 1980-04-04 Dispositif d'actionnement hydraulique à cinq positions

Country Status (5)

Country Link
US (1) US4319609A (enrdf_load_stackoverflow)
EP (1) EP0017592B1 (enrdf_load_stackoverflow)
JP (1) JPS55135271A (enrdf_load_stackoverflow)
DE (1) DE3065442D1 (enrdf_load_stackoverflow)
FR (1) FR2453306B1 (enrdf_load_stackoverflow)

Families Citing this family (31)

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US4531536A (en) * 1982-08-02 1985-07-30 Modular Controls Corporation Flow divider-combiner valve
JPS5983878A (ja) * 1982-11-04 1984-05-15 Toshiba Mach Co Ltd 流量調整弁
US4593719A (en) * 1984-11-30 1986-06-10 Leonard Willie B Spool valve
JPH0623563B2 (ja) * 1985-04-12 1994-03-30 株式会社豊田自動織機製作所 電気式比例制御弁制御装置
JP2544693Y2 (ja) * 1992-04-30 1997-08-20 エスエムシー株式会社 安全制御装置
US6257499B1 (en) 1994-06-06 2001-07-10 Oded E. Sturman High speed fuel injector
US6161770A (en) * 1994-06-06 2000-12-19 Sturman; Oded E. Hydraulically driven springless fuel injector
US6148778A (en) 1995-05-17 2000-11-21 Sturman Industries, Inc. Air-fuel module adapted for an internal combustion engine
US5577434A (en) * 1995-09-14 1996-11-26 Danfoss Inc. Hydraulic valve assembly
US6105616A (en) * 1997-03-28 2000-08-22 Sturman Industries, Inc. Double actuator control valve that has a neutral position
JP3959565B2 (ja) * 1997-12-16 2007-08-15 Ｓｍｃ株式会社 電磁パイロット式３位置切換弁
AU2459799A (en) * 1998-01-20 1999-08-02 Triconex, Incorporated Two out of three voting solenoid arrangement
US6085991A (en) * 1998-05-14 2000-07-11 Sturman; Oded E. Intensified fuel injector having a lateral drain passage
SE515685C2 (sv) * 1998-11-26 2001-09-24 Volvo Penta Ab Styrservo, t ex för båtar
US6478048B2 (en) 1999-01-19 2002-11-12 Triconex, Incorporated Two out of three voting solenoid arrangement
DE10010690B4 (de) * 2000-03-04 2004-03-25 Festo Ag & Co. Ventil
DE10023340A1 (de) * 2000-05-12 2001-11-15 Claas Industrietechnik Gmbh Steuerventil zum Umschalten einer hydraulischen Kolben-Zylinder-Einheit für den Antrieb eines oszillierenden Maschinenteils
US6739293B2 (en) * 2000-12-04 2004-05-25 Sturman Industries, Inc. Hydraulic valve actuation systems and methods
US20030221730A1 (en) * 2002-01-17 2003-12-04 Porter Don B. Multi-stage multi-piston valve
US6585004B1 (en) * 2002-01-17 2003-07-01 Delaware Capital Formation, Inc. Multi-stage flow control
US20040051066A1 (en) * 2002-09-13 2004-03-18 Sturman Oded E. Biased actuators and methods
DE102004048689B3 (de) * 2004-10-06 2005-10-20 Siemens Ag Zweistufiges Servoventil
WO2008051212A1 (en) * 2006-10-23 2008-05-02 Norgren, Inc. Exhaust venting for a fluid control device
US20100130958A1 (en) * 2008-11-26 2010-05-27 David Kang Device and Methods for Subcutaneous Delivery of High Viscosity Fluids
US8640787B2 (en) * 2009-12-30 2014-02-04 Daniel F. Rohrer Portable post driving apparatus
DE102010005229A1 (de) * 2010-01-21 2011-07-28 Hydac Fluidtechnik GmbH, 66280 Ventilvorrichtung
BR112012023689A2 (pt) * 2010-03-19 2016-08-23 Halozyme Inc dispositivo de dispensa de medicação pressurizado a gás
DE102010050325A1 (de) * 2010-11-05 2012-05-10 Parker Hannifin Gmbh Hydraulisches Steuerventil mit einem in dessen hohl ausgebildeten Steuerschieber angeordneten vier Steuerkanten aufweisenden Vorsteuerkolben
DE102010050323A1 (de) * 2010-11-05 2012-05-10 Parker Hannifin Gmbh Hydraulisches Steuerventil mit einem in dessen hohl ausgebildeten Steuerschieber angeordneten Vorsteuerkolben
WO2014106230A1 (en) * 2012-12-31 2014-07-03 Vanderbilt University Directional control valve with double-solenoid configurations
EP3502487B1 (en) * 2017-12-22 2021-08-25 Hamilton Sundstrand Corporation Servo valve

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US1970530A (en) * 1930-11-11 1934-08-14 Donald H West Hydraulic actuating mechanism
US2157240A (en) * 1935-02-21 1939-05-09 Ex Cell O Corp Valve structure
DE1946044A1 (de) * 1969-09-11 1971-03-18 Frisch Geb Kg Eisenwerk Steuerung doppeltwirkender Hydraulikzylinder
US4067357A (en) * 1974-06-14 1978-01-10 Herion-Werke Kg Pilot-operated directional control valve
DE2517205A1 (de) * 1975-04-18 1976-10-28 Danfoss As Hydraulische stellvorrichtung

Also Published As

Publication number Publication date
EP0017592A1 (fr) 1980-10-15
US4319609A (en) 1982-03-16
FR2453306A1 (fr) 1980-10-31
FR2453306B1 (fr) 1986-03-14
DE3065442D1 (en) 1983-12-08
JPH0114474B2 (enrdf_load_stackoverflow) 1989-03-13
JPS55135271A (en) 1980-10-21

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