EP0870112A1 - Systeme de soupapes - Google Patents

Systeme de soupapes

Info

Publication number
EP0870112A1
EP0870112A1 EP96945144A EP96945144A EP0870112A1 EP 0870112 A1 EP0870112 A1 EP 0870112A1 EP 96945144 A EP96945144 A EP 96945144A EP 96945144 A EP96945144 A EP 96945144A EP 0870112 A1 EP0870112 A1 EP 0870112A1
Authority
EP
European Patent Office
Prior art keywords
valve
line
tank
control
connection
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP96945144A
Other languages
German (de)
English (en)
Inventor
Rainer Biener
Richard Rauscher
Winfried RÜB
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP0870112A1 publication Critical patent/EP0870112A1/fr
Withdrawn legal-status Critical Current

Links

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
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements

Definitions

  • the invention relates to a valve arrangement for controlling a hydraulic consumer with two directions of action, according to the preamble of patent claim 1.
  • Valve arrangements of this type are used, for example, in mobile hydraulics to control double-acting cylinders.
  • Such double-acting cylinders are used, for example, in front linkages of agricultural tractors.
  • the rear linkages are in most cases designed to be single-acting, but due to the versatile application possibilities of modern tractors, one also proceeds to design the rear linkages with double-acting cylinders.
  • peripheral devices can be coupled to the agricultural tractor, such as packers, plows, cultivators, rollers, etc.
  • the lifting functions have to be used with the double-acting cylinder , Lowering, pressing, neutral and a floating position in which the tool is freely movable can be carried out.
  • the double-acting cylinder that is to say a cylinder with two oppositely effective surfaces of the same or different sizes
  • a 4-way valve 2 which in the hydraulic circuit diagram shown is a continuously adjustable valve is executed.
  • a valve with switching positions can also be used.
  • the hydraulic fluid is from a pump, not shown, in the In most cases, a variable displacement pump is pumped through a pump line P to the input port of the directional valve 2.
  • the pump line P is connected to the tank T via the directional control valve 2 and the connections A, B of the directional control valve 2 are shut off, so that the hydraulic fluid is clamped in the working lines 4, 6 and thus in the hydraulic cylinder 1.
  • the piston is held in its shown position.
  • the exemplary embodiment shown is an electro-hydraulically adjustable directional valve 2, so that when the valve slide of the directional valve 2 is actuated appropriately, it can be displaced in the direction of the end position marked with b, so that the connections of the connection A with the pump line and the Connection B are opened with the tank line and the left cylinder chamber in FIG. 1 is supplied with hydraulic fluid, while the hydraulic fluid flows out of the rod-side cylinder chamber back into the tank T. That is, the positions indicated by b serve to extend the cylinder 1 (lifting).
  • the piston is retracted when the valve spool is displaced from its neutral position 0 to intermediate positions c, in which the cylinder chamber on the piston rod side is connected to the pump P and the hydraulic fluid in the other cylinder chamber is released towards the tank T.
  • the piston of cylinder 1 is retracted (active lowering or pressing).
  • the object of the invention is to create a valve arrangement which, with minimal expenditure on device technology, enables largely independent control of the feed line and the return line of a double-acting consumer.
  • the supply of the hydraulic fluid can be regulated independently of the return of the hydraulic fluid by appropriate activation of this valve. Since the supply of the hydraulic fluid to the cylinder spaces is dependent on the position of the further valve, the continuously adjustable valve can be made considerably simpler since, in addition to the neutral position, only one end position must be provided in which the connection of the Pump line P is directed towards the working line and a further end position in which the two cylinder spaces are connected to the tank (floating position).
  • the measures according to the invention thus provide a valve arrangement which, with a simple construction in terms of device technology, enables a more flexible adaptation to different control tasks.
  • an unlockable check valve is installed in a supply line downstream of the further valve, that is to say in the line via which the cylinder is brought into its raised position is that must be unlocked to lower the piston.
  • the operational safety of the system is increased.
  • the continuously adjustable valve is designed as a proportional directional valve, the control slide of which can be moved from a neutral position to an end position, so that a connection between the working line and the tank is opened while the control slide is moved in the other direction, the connection of the working line to the tank is opened and the connection to the pump line is closed. This means that in this end position both cylinder spaces are connected to the tank so that the working cylinder is in the floating position.
  • this floating position could only be activated after passing through the intermediate position (lowering) marked with c, so that the consumer - for example the double-acting cylinder - was initially adjusted before the floating position could be reached.
  • This unwanted activation of the consumer when the float position is approached cannot take place in the valve arrangement according to the invention, since the float position can be approached directly from the neutral division 0.
  • the system is particularly versatile when the proportional valve is pre-controlled electrohydraulically (EHR).
  • EHR electrohydraulically
  • valve arrangement in the manner of a valve disc, one valve disc preferably carrying the above-described EHR valve, while the other valve is arranged in the other valve disc, which is preferably designed as an electrohydraulically pilot-operated switching valve.
  • This valve disc can be provided with one or more working connections, which are preferably each via electrical connections. trically switched valve devices can be controlled independently of the double-acting consumer.
  • valve disks can be added, it being possible, for example, to add a third disk with a single-acting EHR valve for controlling a single-acting cylinder.
  • a third disk with a single-acting EHR valve for controlling a single-acting cylinder.
  • the structure of the first valve disc and the third valve disc are identical.
  • valve disk arrangement described above could be added, for example, to the valve disk combination which contains a priority circuit for supplying a steering system, further directional valves and the circuit described above.
  • Figure 1 is a schematic hydraulic circuit diagram of a known hydraulic system with a double-acting cylinder.
  • FIG. 2 shows a hydraulic circuit diagram of a valve arrangement according to the invention
  • FIG. 3 shows a valve disk arrangement of a hydraulic circuit according to FIG. 2.
  • FIG. 2 shows a hydraulic circuit diagram of a valve arrangement which is designed in a valve disk arrangement with two valve disks 8, 10 (dash-dotted lines in FIG. 2).
  • this valve disk arrangement 8, 10 can be combined with further valve disks, one of the valves valve disc 8 upstream valve disc can have, for example, a priority circuit to supply different consumers depending on their priority.
  • Valve blocks of this type which are designed as a central hydraulic valve arrangement in the modular system, are used, for example, in agricultural tractors, with a priority valve supplying a steering valve (not shown) in front of the low-pressure consumers (transmission control, control oil circuit) and in front of the high-pressure consumers, such as a power lift and other directional control valves.
  • valve arrangement implemented by the two valve disks 8, 10 is used to control a double-acting working cylinder 1, the output connections ZI and Z2 of the valve arrangement being connected to the cylinder chamber on the left in FIG. 2 or to the cylinder chamber on the piston rod side.
  • the hydraulic fluid is supplied via the pump connection P, which is connected to a control pump (not shown) via the priority circuit.
  • the valve arrangement also has one or more tank connections T, so that the hydraulic fluid can be supplied to one of the cylinder spaces via the connections ZI or Z2 when the valve arrangement is suitably controlled, while the hydraulic fluid is out the other cylinder chamber is displaced towards the tank T via the valve arrangement.
  • the first valve disc 8 essentially contains an EHR valve which has a control valve 12 to which two pilot valves 14 and 16 are assigned.
  • the control valve 12 is a continuously adjustable directional valve (3/3-proportional directional valve) with a neutral position 0 and two end positions a, b.
  • the pump connection P of the valve arrangement is connected via a pump line 18 to a connection P 'and the tank T via a tank line 20 to a tank connection T of the control valve.
  • the tank connection T and the pump connection P ′ can be connected to an output connection B to which a working line 22 connected. Furthermore, the control valve 12 has three control connections A, C and S, the function of which is explained below.
  • a control line 24 is connected to the control connection C of the control valve 12, which leads to a shuttle valve 25, the output of which is connected to the control connection XgHR unc ⁇ a load signaling line via which the control pump is activated.
  • Each end face of the control piston of the control valve 12 is assigned one of the pilot valves 14, 16, of which the output connection is connected to the end face via a control line.
  • an input connection is guided via a control line 26 to a tank connection TQ of the valve arrangement.
  • a second input connection of each pilot valve 14, 16 is connected via a pressure control line 28 to a pressure connection P ⁇ of the valve arrangement, to which a control pressure is applied and which is emitted by the priority circuit, not shown.
  • the pressure at the pressure connection P] _ can be a low pressure of approximately 20 bar, but variants are also provided in which the output pressure of a pump is present at the connection 31.
  • pilot valve 14 When the pilot valve 14 is actuated with a current signal, a corresponding pilot pressure is passed to the lower end face of the pilot piston in FIG. 2, so that the latter Direction to its end position marked with b is moved.
  • the output pressure of the pilot valve 14 varies proportionally to the current signal between 0 and approximately 18 bar (regardless of the supply pressure of the pilot valves).
  • the connection of the pump connection P 'to the connections B and C is opened, so that the pump line 18 is connected to the working line 22.
  • the load pressure Via the connection C of the control line 24, the load pressure is led to the input of the shuttle valve 25, via which the load pressure is led to the pressure-feed flow regulator of the control pump, which keeps the pressure drop across the control edge of the control valve 12 constant.
  • the output connection ZI of the first valve disk 8 is connected to a feed line 30, in which an unlockable check valve 32 is arranged.
  • the feed line 30 can be connected to the working line 22 via a circuit of the second valve disk 10 which will be described in more detail below.
  • the check valve 32 is unlocked via an unlocking line 34, which is connected via a nozzle 36 to the connection A of the control valve 12.
  • a branch line 38 leading to the tank line 20 branches off from the unlocking line 34, in which a further nozzle 40 is arranged, so that the control pressure required for unlocking is practically tapped between the two nozzles 36 and 40.
  • the working line 22 is connected to the connection of a pilot-operated 4/2-way valve, which in its spring-biased new tral ein connects the working line 22 with the feed line 30.
  • the further output connection Z2 of the second valve disk 10 is connected in the neutral position of the switching valve 42 via a return line 44 to a relief line 46 which in turn opens into the tank line 20.
  • the switching valve 42 is actuated via an electrically operated pilot switching valve 48, which in its de-energized state connects the control surface of the switching valve 42 via a connecting line 50 to the control line 26 and thus to the tank connection T Q , so that the control line 52 is depressurized.
  • the pilot control valve 48 When the pilot control valve 48 is actuated, it is brought into its switching position against the spring bias, in which the control line 52 is connected via a pressure control line 54 to the pressure control line 28 and thus to the control connection P ⁇ .
  • a control pressure is supplied to the control side of the switching valve 42, so that it is brought from the shown neutral position into its switching position, in which the working line 22 with the return line 44 and the supply line 30 with the relief line 46 are connected.
  • the pressure on the control side of the switching valve 43 is led via a connecting line 56 to a connection node between the connection A and the nozzle 36, wherein a check valve 59 is arranged in the connecting line 56, which controls a flow of control oil from the connection A. to the control side of the switching valve 42 prevented.
  • a further working connection A is provided on the second valve disk 10, which can be connected to the pump line 18 via an electrically actuated directional valve 57 and a supply line 58.
  • the connection of the supply line 58 to the connection A is interrupted and the other input of the shuttle valve 25 is closed a load pressure signaling line 60 and a control line 62 are connected to the tank line 20, so that no pressure is present at the load signaling line (XEHR) via the directional valve 57.
  • the directional control valve 57 When the directional control valve 57 is actuated, it is brought into its switch position in which the supply line 58 is connected to the connection A, so that the further consumer is supplied with hydraulic fluid.
  • the control line 42 is shut off and the load pressure signaling line 60 is connected to the connection A via the supply line 58, so that the load pressure is led to the shuttle valve 25 and the control pump is actuated accordingly.
  • the second valve disk 10 shown in FIG. 2 also has a tank connection T, which is also connected to the tank line 20.
  • valve disk 10 is also possible, wherein, for example, a further working connection can be provided, which can be controlled via a suitable valve device of the valve disk 10.
  • the load pressures in the working line 22 and in the supply line 58 are compared with one another and the resulting signal is passed on to the control pump, so that an adequate supply of the double-acting working cylinder 1 and the further consumer is guaranteed at all times.
  • both pilot valves 14, 16 are in the de-energized state, so that the control piston of the control valve 12 is in its neutral position 0, in which the load line is connected to the tank T and the control pump requires no pressure and volume flow is reported.
  • the switching valve 42 is likewise biased into its basic position by the spring preload, in which the cylinder chamber on the piston rod side (connection Z2) via the return line. device 44 are connected to the tank T and the working line 22 to the supply line 30.
  • the hydraulically unlockable check valve 32 prevents a lowering of the load in the neutral position of the valve arrangement.
  • connection ZI can also be connected to the cylinder chamber on the piston rod side and the connection Z2 can be connected to the other cylinder chamber, so that the piston rod is subjected to tensile or compressive loads depending on the cylinder chamber arrangement - both versions are used used on tugs.
  • the pilot valve 14 is driven by a current signal, while the switching valve 42 remains in its neutral position shown.
  • the connection of the pump line 18 to the working line 22 is controlled, so that hydraulic fluid is led via the switching valve 42, the supply line 30 and the check valve 32 to the connection ZI and thus to the corresponding cylinder space of the working cylinder 1 - the piston of cylinder 1 extends.
  • the cylinder chamber on the piston rod side is still connected to the tank connection T, so that the hydraulic fluid can be displaced very quickly.
  • This operating state practically corresponds to the lifting function of a power lift, which is used, for example, in plowing, in which only a force has to be applied to lift the plow, while the plow is lowered (pulled in) by itself due to the reaction forces (passive lowering).
  • the pilot control valve 48 is activated so that the resulting pilot pressure is placed on the end face of the piston of the switching valve 42 and this is brought against spring preload into its switching position in which the working line 22 with the return line 44 and the feed line 30 are connected to the discharge line 46.
  • the control pressure at the forehead Surface of the control piston of the switching valve 42 is guided via the connecting line 56, the nozzle 36 and the unlocking line 34 to the check valve 32, so that it is unlocked and the hydraulic fluid from the cylinder space on the left in FIG. 2 via the connection ZI, the check valve 32 , the switching valve 42 and the relief line 46 can flow into the tank T.
  • This operating state corresponds to the active lowering or pushing function in which the cylinder piston is moved back. This condition is required for pressing tools, for example packers.
  • the supply of the hydraulic fluid to one of the cylinder spaces is regulated via the trailing edge of the control valve 12, while the other "unneeded" cylinder space is always connected to the tank with a full opening cross-section, so that the fastest possible Relief is guaranteed.
  • the control piston of the control valve 12 When the pilot valve 16 is activated, the control piston of the control valve 12 is moved from a neutral position 0 to the end position a, so that the connection of the working line 22 to the tank T is opened. In the neutral position of the switching valve 42 shown, the cylinder chamber on the piston rod side is connected directly to the tank T via the switching valve 42, while the backflow of the hydraulic fluid from the other cylinder chamber takes place via the control valve 12. This state corresponds to the floating position when the pilot valve 16 is activated 100%.
  • the pilot control valve 16 When the pilot control valve 16 is actuated, the connection of the two control connections S and A is also opened, so that the pressure at the connection P 1 is passed via the control line 29, the nozzle 36 and the unlocking line 34 to the check valve 32 so that it is unlocked.
  • the configuration of the valve arrangement according to the invention ensures that the hydraulic fluid supply in a cylinder space is regulated in the required manner, while the other, "not required" side of the working cylinder is connected to the tank.
  • the additional consumer can be controlled independently of the above functions by appropriately controlling the directional valve 57. Since the control of this additional consumer is of subordinate importance for the invention, a further description is not necessary.
  • a third valve disk can be connected, the structure of which corresponds to that of the valve disk 8 and via which a further single-acting hydraulic cylinder can be controlled.
  • valve disk 8 contains the tank connection T, the pump connection P, the connection for the load pressure signaling line XEHR ', the control pressure connection P ] _, the tank connection TQ, via which the control lines can be connected to the tank T and the output connection ZI, which with is connected to the left cylinder space in FIG. 2.
  • the second valve disk 10 contains the output connection Z2, to which the cylinder chamber on the piston rod side is connected, the further tank connection T and the further working connection A.
  • Reference numerals 64, 60 denote the connections of the pilot valves used in the circuit, while reference numeral 68 denotes the connection of a directly actuated valve.
  • the valve disc design makes it possible to combine central hydraulic valves by combining some basic types of valve discs in a modular system, which meet a wide range of requirements.
  • the circuit according to the invention can also be implemented as a pipe installation valve.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un système de soupapes (8, 10) pour assurer la commande d'un consommateur (1) ayant deux directions d'action. Un montage en série d'un distributeur proportionnel (12) et d'une autre soupape de commande (42) permet de piloter l'alimentation en fluide hydraulique par l'intermédiaire de l'arête d'écoulement du distributeur (12), une conduite de retour partant du consommateur (1) pour aller jusqu'au réservoir en passant par la soupape de commande (42). Cette variante permet de réguler l'alimentation en fluide hydraulique indépendamment de l'écoulement actif dans le réservoir.
EP96945144A 1995-12-28 1996-09-23 Systeme de soupapes Withdrawn EP0870112A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19548943A DE19548943B4 (de) 1995-12-28 1995-12-28 Ventilanordnung
DE19548943 1995-12-28
PCT/DE1996/001829 WO1997024534A1 (fr) 1995-12-28 1996-09-23 Systeme de soupapes

Publications (1)

Publication Number Publication Date
EP0870112A1 true EP0870112A1 (fr) 1998-10-14

Family

ID=7781543

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96945144A Withdrawn EP0870112A1 (fr) 1995-12-28 1996-09-23 Systeme de soupapes

Country Status (3)

Country Link
EP (1) EP0870112A1 (fr)
DE (1) DE19548943B4 (fr)
WO (1) WO1997024534A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6092454A (en) * 1998-07-23 2000-07-25 Caterpillar Inc. Controlled float circuit for an actuator
US6892535B2 (en) * 2002-06-14 2005-05-17 Volvo Construction Equipment Holding Sweden Ab Hydraulic circuit for boom cylinder combination having float function
FR2863634A1 (fr) 2003-12-16 2005-06-17 Volvo Constr Equip Holding Se Engin de travaux publics
DE102004012382B4 (de) 2004-03-13 2014-03-13 Deere & Company Hydraulische Anordnung
DE102004050294B3 (de) * 2004-10-15 2006-04-27 Sauer-Danfoss Aps Hydraulische Ventilanordnung
DE102006002309B4 (de) * 2006-01-18 2012-05-16 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Kolben-Zylinder-Anordnung
CN105102732B (zh) 2013-04-03 2018-02-13 斗山英维高株式会社 建筑机械的阀芯位移可变控制装置及控制方法
DE102015015809A1 (de) * 2015-12-07 2017-06-08 Liebherr-Hydraulikbagger Gmbh Ventileinheit für Schnellwechsler sowie Schnellwechselsystem

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Publication number Priority date Publication date Assignee Title
FR2232695A1 (en) * 1973-06-08 1975-01-03 Int Basic Economy Corp Hydraulic control appts. with standardised components - has multi-purpose pipeless units capable of being combined and programmed
DE3016929A1 (de) * 1980-05-02 1981-11-05 G.L. Rexroth Gmbh, 8770 Lohr Hydraulischer antrieb
WO1984002958A1 (fr) * 1983-01-24 1984-08-02 Caterpillar Tractor Co Soupape de signal pour systeme a pression compensee
DE3632416A1 (de) * 1986-09-24 1988-04-07 Schaeff Karl Gmbh & Co Knickgelenktes arbeitsfahrzeug mit hoehenverstellbaren raedern
JP2559619B2 (ja) * 1988-08-16 1996-12-04 株式会社小松製作所 操作弁装置
JPH0374608A (ja) * 1989-08-10 1991-03-29 Nippon Air Brake Co Ltd 流量制御回路
GB2235168A (en) * 1989-08-24 1991-02-27 Gkn Technology Ltd A vehicle suspension system having an adjustable anti-roll bar
FR2656386B1 (fr) * 1989-12-22 1992-04-30 Matairco Hydro Air Sa
DE4212184A1 (de) * 1992-04-10 1993-10-14 Bosch Gmbh Robert Hydraulische Steuereinrichtung für einen Arbeitszylinder
DE4240076A1 (de) * 1992-11-28 1994-06-01 Bosch Gmbh Robert Hydraulische Steuereinrichtung für einen Arbeitszylinder

Non-Patent Citations (1)

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Title
See references of WO9724534A1 *

Also Published As

Publication number Publication date
DE19548943A1 (de) 1997-07-03
WO1997024534A1 (fr) 1997-07-10
DE19548943B4 (de) 2005-05-04

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