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EP0471884B1 - Servodistributeur electrohydraulique - Google Patents
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EP0471884B1 - Servodistributeur electrohydraulique - Google Patents

Servodistributeur electrohydraulique Download PDF

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Publication number
EP0471884B1
EP0471884B1 EP19900116279 EP90116279A EP0471884B1 EP 0471884 B1 EP0471884 B1 EP 0471884B1 EP 19900116279 EP19900116279 EP 19900116279 EP 90116279 A EP90116279 A EP 90116279A EP 0471884 B1 EP0471884 B1 EP 0471884B1
Authority
EP
European Patent Office
Prior art keywords
control
control piston
pressure
valve
servo 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
EP19900116279
Other languages
German (de)
English (en)
Other versions
EP0471884A1 (fr
Inventor
Herbert Handte
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.)
Moog GmbH
Original Assignee
Moog GmbH
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 Moog GmbH filed Critical Moog GmbH
Priority to EP19900116279 priority Critical patent/EP0471884B1/fr
Priority to DE59010152T priority patent/DE59010152D1/de
Priority to JP20564991A priority patent/JPH0626501A/ja
Priority to US07/749,216 priority patent/US5165448A/en
Publication of EP0471884A1 publication Critical patent/EP0471884A1/fr
Application granted granted Critical
Publication of EP0471884B1 publication Critical patent/EP0471884B1/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
    • F15B13/042—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
    • 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
    • Y10T137/8659—Variable orifice-type modulator
    • Y10T137/86598—Opposed orifices; interposed modulator
    • 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

Definitions

  • the invention relates to an electro-hydraulic servo valve according to the preamble of claim 1.
  • Such a valve is generally known prior art.
  • proportional valves With electro-hydraulic valves, a distinction is made between proportional valves and servo valves. While proportional valves are designed for smaller pressure differences for a nominal flow of up to 10 bar, servo valves are designed for high pressure differences up to 70 bar. Servo valves are only used in controlled drives and proportional valves are only used in controlled drives. For this reason, proportional valves have a positive overlap, but not servo valves, from which a precisely defined position is required (see publication "Oil hydraulics and pneumatics, 33 (1989) No.
  • a proportional valve in which the two control chambers can be connected via a bypass channel and a valve therein in order to bring the control piston into the zero position when the valve is de-energized.
  • the present invention has for its object to provide an electrohydraulic servo valve, in which a safe standstill of a system connected to it can be achieved in the de-energized state of the valve.
  • the present invention is based on the knowledge that it is nevertheless possible via a detour to prevent leakage current in a servo valve in the zero position by nevertheless providing the servo valve, which usually has no overlap, with an overlap and this overlap by means of an electrical compensation circuit compensates.
  • the bypass channel ensures that the control piston is forced to the safe zero position when the valve is de-energized.
  • the servo valve has a cylinder 1 with a central pressure inlet channel 2, two pressure outlet channels 3 and 4 arranged offset in the axial direction, and a return channel 5 which is connected to the supply tank.
  • a control piston 6 is mounted between two driver pistons 22.
  • the end faces 7 of the driver pistons 22 can be acted upon by a control pressure in the axial direction via the control chambers 9 and 10.
  • a pair of piston rings 11 are formed on the control piston above the two pressure outlet channels 3 and 4, respectively.
  • the control piston has 11 annular recesses between the piston rings so that the hydraulic fluid can flow around the piston better.
  • Corresponding (ring-shaped) chambers are formed in the opposite sections of the cylinder wall. The pressure on the piston rings 11 therefore acts on the entire circumference of the piston surface.
  • the two pressure outlet channels 3, 4 have a diameter a, which corresponds to the thickness of the annular chambers.
  • the two piston rings 11 are spaced apart in the axial direction such that the total thickness D of the two piston rings is greater than that Thickness of the annular chambers a and the diameter of the pressure outlet openings 3 and 4 on the inside of the cylinder wall. Half of the difference between the total thickness D and the thickness of the annular chambers or the diameter of the pressure outlet channels a is intended to define the positive overlap x.
  • the maximum deflection of the control piston 6 from the rest position should be denoted by y.
  • the pressure-free outer spaces of the cylinder 1 are connected to one another via a compensating line 12 and the common return duct 5.
  • the control piston 6 is axially centered in the valve housing by means of two springs 8, which also act on the end faces 7 of the driver pistons 22, in the zero position.
  • An electrical position sensor 13 is connected in axial extension to the control piston 6 and is fed back to a torque motor 14 via an electrical position control circuit 20 known from the prior art.
  • Position control loop and compensation circuit 21 according to the invention are located in an electrically insulated part of the valve housing.
  • the armature 15 of the torque motor 14 acts directly on the baffle plate 16 of a nozzle 17 baffle plate 16 system.
  • the control rooms 9 and 10 have a bypass channel 18 and an electrically operated valve 19 located in this channel in order to be connected to one another when the valve is open.
  • the circuit shows a preferred embodiment of the compensation circuit.
  • the circuit consists of an inverting amplifier with a Input resistor R and a feedback circuit, consisting of three feedback branches, which react to the negative input of the operational amplifier.
  • One of these feedback branches consists only of an adjustable ohmic resistor R3, the other two each from the series circuit of an adjustable voltage source U1 or U2, a diode D1 and D2 and an adjustable resistor R1 or R2.
  • the diodes D1 and D2 are switched with respect to the polarities of the voltage sources U1 and U2 in the reverse direction.
  • Fig. 3 the relationship between the input and the output signal is shown graphically.
  • the graph is defined in sections by the equations given above.
  • the slopes of the straight sections are determined by the ratios of the feedback resistors R1, R2, and R3 to the input resistance R. The lower the ratio, the flatter the respective straight line section.
  • variable voltage sources U 1 are decisive for the position of the break points of the non-linearity and U2. Increasing or decreasing the voltage shifts the respective break point in the direction of the positive or negative Y axis of the diagram in Fig. 3.
  • the feedback channel with the resistance R3, which is always effective, is dependent on the output signal in the manner indicated above connected in parallel to either resistor R1 or R2.
  • valve 19 located in the bypass channel 18 opens when the power supply is interrupted, the control chambers 9, 10 are hydraulically short-circuited. This means that an existing pressure difference in the Control chambers immediately out and the return springs 8 move the control piston 6 in the area of positive overlap.
  • the absolute safe standstill of the consumer is guaranteed, since no leakage currents can occur in the overlap area. This takes account of the need for security.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Servomotors (AREA)

Claims (4)

  1. Servodistributeur électrohydraulique, le servodistributeur comportant un cylindre (1) et un piston de commande (6) qui y est logé, et le piston de commande reposant sur ses deux côtés frontaux (7) dans des chambres de commande (9, 10) auxquelles une pression peut être appliquée pour écarter de sa position neutre le piston (6) en cas de différence de pression entre ces deux chambres de commande (9, 10), le cylindre comportant un canal d'entrée médian (2) de pression et deux canaux de sortie (3, 4) de pression qui sont disposés de façon déportée en direction axiale et sont fermés par le piston de commande (6) lorsqu'il se trouve dans sa position neutre et qui sont partiellement à totalement ouverts, lorsque le piston de commande (6) est décalé, de manière à libérer entre l'un des canaux de sortie (3, 4) et le canal d'entrée (2) une section transversale de passage qui dépend de la position du piston de commande, la différence de pression entre les chambres de commande (9, 10) étant engendrée par un signal électrique de réglage,
       caractérisé en ce que le piston de commande (6) est réalisé d'une manière telle qu'il ne commence à ouvrir les canaux de sortie (3, 4) que pour un écart axial prédéterminé (x) par rapport à sa position neutre (recouvrement positif), et en ce qu'un circuit électrique de compensation (21) est prévu pour compenser la non linéarité, provoquée par le recouvrement positif, entre le signal électrique de commande et l'écart du piston de commande (6), et en ce que les deux chambres de commande (9, 10) peuvent être reliées entre elles, en vue d'un équilibrage de pression, par un canal de dérivation (18) au moyen d'une vanne (19) à actionnement électrique située dans le canal et que la vanne (9) est réalisée de manière à s'ouvrir dans l'état d'absence de courant.
  2. Servodistributeur selon la revendication 1, caractérisé en ce que l'écart axial prédéterminé (x) est de préférence égal à 10% du trajet maximal de réglage (y).
  3. Servodistributeur selon la revendication 1 ou 2, caractérisé en ce que le circuit électrique de compensation (21) est intégré dans le carter de vanne.
  4. Servodistributeur selon l'une au moins des revendications 1 à 3, caractérisé en ce que le circuit électrique de compensation (21) comporte au moins un amplificateur opérationnel, en ce que l'amplificateur opérationnel est pourvu d'un circuit de rétroaction qui lui confère une non linéarité qui compense la non linéarité qui résulte du recouvrement positif.
EP19900116279 1990-08-24 1990-08-24 Servodistributeur electrohydraulique Expired - Lifetime EP0471884B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP19900116279 EP0471884B1 (fr) 1990-08-24 1990-08-24 Servodistributeur electrohydraulique
DE59010152T DE59010152D1 (de) 1990-08-24 1990-08-24 Elektrohydraulisches Servoventil
JP20564991A JPH0626501A (ja) 1990-08-24 1991-07-23 電子油圧サーボ弁
US07/749,216 US5165448A (en) 1990-08-24 1991-08-23 Two-stage servovalve with compensatoin circuit to accommodate "dead zone" du

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19900116279 EP0471884B1 (fr) 1990-08-24 1990-08-24 Servodistributeur electrohydraulique

Publications (2)

Publication Number Publication Date
EP0471884A1 EP0471884A1 (fr) 1992-02-26
EP0471884B1 true EP0471884B1 (fr) 1996-02-21

Family

ID=8204370

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900116279 Expired - Lifetime EP0471884B1 (fr) 1990-08-24 1990-08-24 Servodistributeur electrohydraulique

Country Status (4)

Country Link
US (1) US5165448A (fr)
EP (1) EP0471884B1 (fr)
JP (1) JPH0626501A (fr)
DE (1) DE59010152D1 (fr)

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5285715A (en) * 1992-08-06 1994-02-15 Hr Textron, Inc. Electrohydraulic servovalve with flow gain compensation
DE4227563C2 (de) * 1992-08-20 2000-04-13 Mannesmann Rexroth Ag Geregelter hydraulischer Vorschubantrieb
US5884894A (en) * 1996-08-20 1999-03-23 Valtek, Inc. Inner-loop valve spool positioning control apparatus
US6318182B1 (en) * 1999-06-04 2001-11-20 Eaton Corporation Measurement of transmission oil pressure by monitoring solenoid current
CN1295441C (zh) * 2004-11-05 2007-01-17 宁波华液机器制造有限公司 一种比例压差控制阀
RU2346187C2 (ru) * 2007-03-30 2009-02-10 Валерий Иванович Разинцев Трехкаскадный электрогидравлический усилитель мощности
RU2489607C1 (ru) * 2011-12-09 2013-08-10 Валерий Иванович Разинцев Двухкаскадный электрогидравлический усилитель с электрической обратной связью по расходу
RU2467215C1 (ru) * 2011-09-27 2012-11-20 Валерий Иванович Разинцев Трехкаскадный электрогидравлический усилитель с электрической обратной связью по расходу
WO2013048283A1 (fr) * 2011-09-27 2013-04-04 Razintsev Valery Ivanovich Amplificateur électrohydraulique comprenant une liaison de retour électrique sur le débit
RU2482341C1 (ru) * 2011-12-01 2013-05-20 Валентин Григорьевич Жарков Сервоклапан со струйным управлением
RU2488719C1 (ru) * 2011-12-09 2013-07-27 Валерий Иванович Разинцев Однокаскадный электрогидравлический усилитель с электрической обратной связью по расходу
DE102014205041A1 (de) * 2014-03-19 2015-09-24 Robert Bosch Gmbh Druckreduzierventil
JP6775288B2 (ja) * 2015-10-08 2020-10-28 株式会社堀場エステック 流体制御弁及びその制御プログラム
JP6650471B2 (ja) * 2016-01-29 2020-02-19 株式会社小松製作所 油圧シリンダ用スプール弁装置
US10927866B2 (en) 2017-12-15 2021-02-23 Eaton Intelligent Power Limited Leakage modulation in hydraulic systems containing a three-way spool valve
JP7008499B2 (ja) * 2017-12-27 2022-01-25 株式会社堀場エステック 校正データ作成装置及び校正データ作成方法、並びに、流量制御装置
CN113710902B (zh) 2019-02-05 2024-08-30 多明流体动力有限公司 旋转伺服阀
GB2581160B (en) * 2019-02-05 2022-10-19 Domin Fluid Power Ltd Rotary servo valve
CN110109348B (zh) * 2019-05-13 2023-03-10 河南工学院 一种基于深度的液压比例阀双向死区补偿方法
US11473598B2 (en) 2019-10-25 2022-10-18 Woodward, Inc. Failsafe electro-hydraulic servo valve
US11852250B2 (en) 2022-04-11 2023-12-26 Fisher Controls International Llc Adjustable spool valve for a digital valve controller
CN119934105A (zh) * 2025-04-03 2025-05-06 苏州海卓伺服驱动技术有限公司 以旋转直驱阀为先导的电液伺服阀及其控制方法

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4192551A (en) * 1978-10-10 1980-03-11 Bethlehem Steel Corporation Remote control system for mining machines
DE2845079A1 (de) * 1978-10-17 1980-05-08 Bosch Gmbh Robert Elektrohydraulisches wegeventil
US4466337A (en) * 1982-01-25 1984-08-21 Sundstrand Corporation Electro hydraulic control with dead zone compensation
US4766921A (en) * 1986-10-17 1988-08-30 Moog Inc. Method of operating a PWM solenoid valve
DE3844336A1 (de) * 1988-12-30 1990-07-05 Bosch Gmbh Robert Elektrohydraulisches porportionalwegeventil

Also Published As

Publication number Publication date
EP0471884A1 (fr) 1992-02-26
DE59010152D1 (de) 1996-03-28
US5165448A (en) 1992-11-24
JPH0626501A (ja) 1994-02-01

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