EP0016719B1 - Dispositif de commande pour moteur hydraulique - Google Patents

Dispositif de commande pour moteur hydraulique Download PDF

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Publication number
EP0016719B1
EP0016719B1 EP80710005A EP80710005A EP0016719B1 EP 0016719 B1 EP0016719 B1 EP 0016719B1 EP 80710005 A EP80710005 A EP 80710005A EP 80710005 A EP80710005 A EP 80710005A EP 0016719 B1 EP0016719 B1 EP 0016719B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
control
line
hydraulic motor
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
EP80710005A
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German (de)
English (en)
Other versions
EP0016719A1 (fr
Inventor
Roland Ewald
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
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Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP0016719A1 publication Critical patent/EP0016719A1/fr
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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
    • F15B11/003—Systems with load-holding valves
    • 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
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control

Definitions

  • the invention relates to a device for controlling a hydraulic motor with two lines, with a lowering brake valve arranged in the first line, the passage cross section of which can be controlled hydraulically by means of an associated control element, with a control valve connected to the control element and the second line and with a directional control valve. which is connected directly to the hydraulic motor via the second line and to the hydraulic motor via the first line via the throttle element.
  • a check valve opening in the direction of the hydraulic motor is connected in parallel with the lowering brake valve and a throttle point arranged between it and the directional valve.
  • the directional control valve has three defined switching positions.
  • the control valve is a 4/2-way valve, the control member in its one end position is controlled by the pressure prevailing in the two lines connected to the hydraulic motor, the pressure in the first line being reduced between the lowering brake valve and a throttling point connected downstream .
  • the pressure in the second line then acts on the control element of the lowering brake valve.
  • the pressure in the first line acts both on the two sides of the control element of the control valve and on the control member.
  • the control element of the control valve can take intermediate layers.
  • the lowering brake valve serves to dampen the movement of the hydraulic motor when it is under the effect of a load and does not allow any leakage-free shut-off. It is also controlled by changing pressures, which results in changing load-dependent equilibrium positions. Different lowering speeds occur with different loads (FR-A-2 254 728).
  • DE-A-2 209 506 shows a lowering brake shut-off valve whose control piston is acted upon in the closing direction by the pressure between the consumer and the lowering brake shutoff valve and in the opening direction by the pressure on one side of the consumer.
  • the control piston of the lowering brake check valve is thus controlled depending on the load.
  • the well-known lowering brake valve serves to dampen the movement of the hydraulic motor. If this is under the action of a load, different lowering speeds occur here also with different loads.
  • a pressure compensator has the disadvantage that it is fully open when the hydraulic motor is separated from the pressure medium source. When connecting the hydraulic motor to the pressure medium source, this leads to a disadvantageous jump in the starting of the hydraulic motor, since in the beginning open pressure medium paths are reduced in their cross-section and may have to be closed completely (DE-AS 1 650 312).
  • the present invention is based on the object of reliably compensating the load acting on the hydraulic motor in order to avoid different lowering speeds with different loads with the same opening cross section of the lowering brake check valve.
  • This object is achieved in that the directional control valve is designed as a throttling directional control valve, that the control valve is designed as a pressure reducing valve and that the lowering brake valve is designed as a lowering brake blocking valve which enables a leakage-free shut-off, the control piston of which is in the control member on one side with the pressure reducing valve and is connected on its other side to the part of the second line which is present between the lowering brake blocking valve and the directional control valve.
  • the compensation of the load is achieved in that the control pressure on the control device of the controllable valve designed as a lowering brake shut-off valve is kept the same by the pressure reducing valve, as a result of which the pressure drop at the throttle point of the proportional valve and thus the latter Flow current remains constant.
  • the lowering brake check valve also acts as a pressure compensator, 'which ensures load-independent lowering of the load.
  • the lowering brake check valve therefore has a double function.
  • the invention has the advantage that when the hydraulic motor is connected to the pressure medium source, a jump in the start of the hydraulic motor is avoided.
  • the lowering brake check valve is closed when the hydraulic motor is disconnected from the pressure medium source and only opens when the hydraulic motor is connected to the pressure medium source.
  • the lowering brake shut-off valve also shuts off the pressure medium passage leading to the hydraulic motor without leakage and prevents loads from leading with a double-acting hydraulic motor, e.g. a double-acting cylinder.
  • the arrangement of the pressure reducing valve enables a constant pressure to be maintained between two connecting lines of the directional valve, namely one from the hydraulic motor and one connecting line leading to the reservoir.
  • the spring side of the pressure reducing valve with the connection of the throttling directional control valve to the supply container connected so that even with changing pressure in the connection of the throttling directional control valve to the reservoir, the pressure difference controlled by the lowering brake valve on the directional control valve remains constant.
  • the check valve and the throttle device between the controllable valve and the pressure reducing valve are switched on in such a way that the check valve can be opened to the controllable valve, as a result of which the passage of the lowering brake check valve is opened quickly and allows this passage to be closed slowly.
  • a throttling 4/3-way valve 1 is designed as an electrohydraulic servo valve, also called a proportional valve, as it is e.g. is described in DE-AS 17 76 190.
  • the directional control valve 1 has two with a hydraulic motor 2 with a constant displacement and with a flow direction, e.g. a working cylinder or the like, connectable connections A1 and B1, to which lines 3 and 4 are connected.
  • a port P is connected to a pump 5 and a port T is connected to a reservoir 6.
  • the device described has a single reservoir 6 for all of its associated devices.
  • the slide of the directional control valve 1 can be controlled by means of an electromagnet.
  • the position of the armature of this magnet depends on the voltage applied.
  • the slide of the directional valve 1 does not have three specific control positions, but is continuously adjustable. The flows through the directional control valve 1 are, as shown, throttled.
  • the line 3 leads directly to the hydraulic motor 2, the line 4 to a connection A2 on a lowering brake check valve 7, the connection B2 of which is connected to the hydraulic motor 2 via a line 8.
  • the lowering brake check valve 7 has a control connection X, which is connected via a line 9 to a check valve 10 which can be opened to the connection X.
  • This check valve 10 is connected via a line 11 to a pressure reducing valve 12, which is also connected to line 3.
  • the check valve 10 can be bypassed via a bypass line 14 having an orifice 13 (viscosity-stable throttle point).
  • the pressure reducing valve 12 has a control line 15 which is connected to the line 11.
  • the control line 15 is connected to this line via a check valve 16 which can be opened in the direction of the line.
  • a control return line 17 of the pressure reducing valve 12 is connected to the reservoir 6.
  • the lowering brake check valve 7, the check valve 10 together with the orifice 13 and the pressure reducing valve 12 including the control line 15 and the check valve 16 are accommodated in a common, dash-dotted and possibly multi-part housing 8.
  • the lowering brake check valve 7 has a main valve member 19 designed as a conical closing member and a control piston 20 which can be actuated and which can be acted upon by the same cross sections from the connections X and A2.
  • a compression spring 21 is clamped between the side of the control piston 20 adjacent to the valve member 19 and the housing of the lowering brake check valve 7.
  • the control piston 20 also serves to actuate the pilot valve member accommodated in the main valve member 19 and under the load of a pilot spring.
  • In the main valve member 19 there is a 2/2-way valve which, in cooperation with the spherical pilot control member, connects the rear of the main valve member 19 to line 8 or line 4.
  • the control pressure at the connection point X is opposed by the force of the spring 21.
  • connection point B2 The flow from the connection point B2 to the connection point A2 begins at a certain pressure in the line 8.
  • the throttling effect of the main valve member 19 is determined by the respective position of the main valve member.
  • the main valve element 19 acts as a check valve element that can be opened by the pressure medium pressure.
  • the line 4 is connected to the pump 5 and pressure medium flows via the lowering brake check valve 7, through the check valve opening to the hydraulic motor 2, and via line 8 to the hydraulic motor 2.
  • the line 3 serves as a return line. If the load is to be reduced by the hydraulic motor, the feed pump 5 delivers pressure medium into the line 3, the lines 8, 4 serving as return lines.
  • the pressure reducing valve 12 keeps the pressure at port X of the lowering brake check valve 7 constant. The pressure at the connection A2 of the lowering brake shutoff valve 7 thus also remains constant, since the same cross sections are acted upon by the control piston 20 from the two ports X and A2 of the lowering brake shutoff valve 7.
  • the pressure in port A2 corresponds to the difference from the Pressure at the control port X and the pressure necessary to overcome the bias of the spring 21. If, for example, a pressure of 10 bar is required at port X in order to move the control piston 20 against the force of the spring 21, and if there is a pressure of 30 bar at port X of the lowering brake check valve 7, the pressure at port A2 of the lowering brake is -Lock valve 7 20 bar.
  • the lowering brake check valve 7 acts like a pressure compensator and reduces the excess pressure between the connections A2 and B2. In the open position of the main valve member 19 of the lowering brake check valve 7, there is practically no pressure drop when pressure medium flows through this valve between the connections A2 and B2.
  • connection of the control line 15 of the pressure reducing valve 12 via the check valve 16 to the line 3 enables pressure fluid from the control line 15 to overflow into this line 3 when the pressure in the line 3 drops rapidly, as a result of which the pressure at the connection point X of the lowering brake check valve 7 can be dismantled quickly.
  • a counterbalance check valve 7 of the type described above acts as a pressure compensator for loads regardless of their direction, that this prevents an advance of loads and that its main valve member shuts off the fluid passage it monitors, since the main valve member is on its seat is conical.

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

Claims (4)

1. Dispositif pour commander un moteur hydraulique (2) comportant deux conduits (3, 4, 8) et une valve de freinage de descente (7) disposée dans le premier conduit (4, 8), dont la section libre peut être réglée hydrauliquement au moyen d'un organe de commande (20, 21 une valve de commande (12) reliée à l'organe de commande (20, 21) et au second conduit (3) et une valve distributrice (1) qui, par le second conduit (3), est reliée directement au moteur hydraulique (2) et par le premier conduit (4), à travers la valve de freinage de descente (7), au moteur hydraulique (2), caractérisé en ce que la valve distributrice (1) est réalisée sous la forme d'une valve distributrice restrictive, en ce que la valve de commande (12) est réalisée comme une valve de réduction de pression, en ce que la valve de freinage de descente (7) est réalisée sous la forme d'une valve d'arrêt et de freinage de descente permettant un blocage sans fuite, dont le piston de commande (20) est relié, dans l'organe de commande (20, 21) d'un côté, avec la valve de réduction de pression (12) et, de l'autre côté, avec la partie du second conduit (4) présente entre la valve d'arrêt et de freinage de descente (7) et la valve distributrice (1).
2. Dispositif selon la revendication 1, caractérisé en ce que le côté de la valve de réduction de pression (12) comportant le ressort est relié, en même temps que le raccord de la valve distrubutrice restrictive (1), au réservoir d'alimentation (6).
3. Dispositif selon la revendication 1 ou 2, comportant une valve de non-retour (10) qui peut être contournée par un dispositif d'étranglement (13), caractérisé en ce que la valve de non-retour (10) et le dispositif d'étranglement (13) sont intercalés entre la valve de freinage de descente (7) et la valve de réduction de pression (12), de façon que la valve de non-retour (10) peut s'ouvrir en direction de la valve de freinage de descente (7).
4. Dispositif selon l'une quelconque des revendications précédentes, caractérisé en ce que entre le conduit de commande (15) de la valve de reduction de pression (12) et le conduit (3) reliant le moteur hydraulique (2) à la valve de réduction de pression (12), est intercalée une valve de non-retour (16) s'ouvrant en direction du moteur hydraulique (2).
EP80710005A 1979-03-26 1980-02-29 Dispositif de commande pour moteur hydraulique Expired EP0016719B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2911891A DE2911891C2 (de) 1979-03-26 1979-03-26 Vorrichtung zum Steuern eines Hydromotors
DE2911891 1979-03-26

Publications (2)

Publication Number Publication Date
EP0016719A1 EP0016719A1 (fr) 1980-10-01
EP0016719B1 true EP0016719B1 (fr) 1985-01-09

Family

ID=6066485

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80710005A Expired EP0016719B1 (fr) 1979-03-26 1980-02-29 Dispositif de commande pour moteur hydraulique

Country Status (4)

Country Link
US (1) US4732076A (fr)
EP (1) EP0016719B1 (fr)
JP (1) JPS55132401A (fr)
DE (1) DE2911891C2 (fr)

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FR2531175B1 (fr) * 1982-07-27 1986-04-04 Bennes Marrel Valve pilotee pour le freinage ou la limitation de vitesse dans un circuit hydraulique
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DE3705170C1 (de) * 1987-02-18 1988-08-18 Heilmeier & Weinlein Hydraulische Steuervorrichtung
IT1208866B (it) * 1987-04-14 1989-07-10 Chs Vickers Spa Circuito idraulico di comando per organi di lavoro di macchine movimento terra con circuito di sovrali mentazione
US5140815A (en) * 1988-02-24 1992-08-25 Hitachi Construction Machinery Co., Ltd. Valve apparatus
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DE4021347A1 (de) * 1990-07-05 1992-01-16 Heilmeier & Weinlein Hydraulische steuervorrichtung
DE4105459A1 (de) * 1991-02-21 1992-08-27 Heilmeier & Weinlein Hydraulische steuervorrichtung
JPH086723B2 (ja) * 1991-02-21 1996-01-29 ハイルマイア ウント バインライン ファブリク フュル オエル − ハイドロリク ゲ−エムベ−ハー ウント コンパニー，カーゲー 油圧制御装置
US5168937A (en) * 1991-10-02 1992-12-08 Ingersoll-Rand Company Drill feed control utilizing a variable overcenter valve
US5251705A (en) * 1992-03-19 1993-10-12 Deere & Company Electrical trigger for quick drop valve
JP3478931B2 (ja) * 1996-09-20 2003-12-15 新キャタピラー三菱株式会社 油圧回路
US6699311B2 (en) 2001-12-28 2004-03-02 Caterpillar Inc Hydraulic quick drop circuit
KR100631067B1 (ko) * 2004-05-04 2006-10-02 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 홀딩밸브의 응답성이 개선된 유압제어밸브
DE102008058589A1 (de) * 2008-11-22 2010-05-27 Alpha Fluid Hydrauliksysteme Müller GmbH Modulares Ventil- und Kennlinienkonzept
CN103174697B (zh) * 2013-03-22 2015-04-15 江苏恒立高压油缸股份有限公司 具有压力补偿功能的液压阀系统
CN104454736B (zh) * 2014-12-15 2016-06-15 山东华伟液压科技有限公司 一种负载保持阀及其工作方法

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Also Published As

Publication number Publication date
EP0016719A1 (fr) 1980-10-01
JPS55132401A (en) 1980-10-15
US4732076A (en) 1988-03-22
DE2911891A1 (de) 1980-10-02
JPH034763B2 (fr) 1991-01-23
DE2911891C2 (de) 1983-10-13

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