EP1003939A1 - Dispositif de commande hydraulique destine a une machine de travail mobile, notamment a une chargeuse a roues - Google Patents

Dispositif de commande hydraulique destine a une machine de travail mobile, notamment a une chargeuse a roues

Info

Publication number
EP1003939A1
EP1003939A1 EP98945142A EP98945142A EP1003939A1 EP 1003939 A1 EP1003939 A1 EP 1003939A1 EP 98945142 A EP98945142 A EP 98945142A EP 98945142 A EP98945142 A EP 98945142A EP 1003939 A1 EP1003939 A1 EP 1003939A1
Authority
EP
European Patent Office
Prior art keywords
valve
control
hydraulic
pressure
control line
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.)
Granted
Application number
EP98945142A
Other languages
German (de)
English (en)
Other versions
EP1003939B1 (fr
Inventor
Georg Rausch
Dieter Roth
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=7838569&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1003939(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP1003939A1 publication Critical patent/EP1003939A1/fr
Application granted granted Critical
Publication of EP1003939B1 publication Critical patent/EP1003939B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • 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
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • 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
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E02F9/2207—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for reducing or compensating oscillations

Definitions

  • the invention is based on a hydraulic control arrangement which is used for a mobile working machine, in particular for a wheel loader, and which has the features from the preamble of claim 1.
  • the shut-off valve between the hydraulic accumulator and the lift cylinders is closed as long as the loading shovel is in use and can be opened by the driver or automatically as soon as pitching vibrations occur while driving or as soon as the driving speed exceeds a certain value, e.g. over 6 km / h lies.
  • the branching off of the filling line in front of the directional control valve block means that the hydraulic accumulator does not only operate when the directional control valve assigned to the lift cylinders is actuated, but is charged when any directional valve is actuated, which leads to pressure build-up in the pump line.
  • the actuation of the steering valve belonging to a hydraulic steering of the working machine can also lead to an inflow of pressure medium to the hydraulic accumulator. If the check valve is also open, the lift cylinders can move in an uncontrolled manner.
  • the filling line branches off from a working line that runs between the lift cylinders and the directional valve assigned to them.
  • the check valve arranged in the filling line is pressure-controlled and can be opened by the load pressure prevailing in the working line of the lift cylinder against the accumulator pressure, from which a rear control chamber on the valve member of the check valve can be acted upon, and against the force of a weak compression spring.
  • the accumulator pressure is therefore only slightly lower than the highest load pressure of the lift cylinder that occurs during a work cycle.
  • the rear control chamber of the check valve is relieved to the tank via a pilot valve, so that the check valve opens and pressure medium can be pushed back and forth between the hydraulic accumulator and the lift cylinders.
  • a pressure rupture valve which is usually located directly on the hydraulic cylinder, can also be connected upstream of a pressure chamber of a hydraulic cylinder.
  • a pipe rupture safety valve is designed in such a way that pressure medium can easily flow to the pressure chamber via a check valve opening towards the pressure chamber.
  • a bypass to the check valve is opened to a greater or lesser extent for the outflow of pressure medium from the pressure chamber.
  • a control piston is adjusted proportionally. He can do this in the pipe rupture valve from the above
  • the invention has for its object to develop a hydraulic control arrangement with the features from the preamble of claim 1 so that the pressure chamber of a hydraulic cylinder can be shut off, but that nevertheless the connection to a hydraulic accumulator necessary for damping pitching vibrations can be produced.
  • This object is achieved in a hydraulic control arrangement with the features from the preamble of claim 1 according to the characterizing part of claim 1 in that an unlockable check valve is present, which the
  • the pressure chamber of the hydraulic cylinder is connected upstream and opens towards it and this can be controlled when the directional valve is actuated in the sense of the discharge of pressure medium from the pressure chamber to the tank and when the control valve is actuated in the sense of establishing a fluidic connection between the pressure chamber and the hydraulic accumulator is.
  • the pressure chamber on the hydraulic cylinder and hydraulic accumulator can be connected to one another, even if a branch line leading to the hydraulic accumulator is connected between the directional valve and the check valve to a working line leading from the directional valve to the hydraulic cylinder, so that the check valve can also perform its blocking function with regard to this branch line.
  • a lockable non-return valve is generally also a bypassable non-return valve, e.g. is present in the case of pipe burst safety valves.
  • control lines there are three control lines, the third control line, to which the unlocking means of the check valve are connected, via switching means when the directional valve is actuated with a first control line and when the control valve is actuated with a second control line. line is connected.
  • electrical control lines, electrical control signals and electrical switching means are also conceivable here.
  • check valve can very often be unlocked hydraulically.
  • An advantageous embodiment with regard to a hydraulically unlockable check valve is specified in claim 3.
  • a pilot oil circuit with a pilot oil source is present, from which, according to claim 6, the control oil for unlocking the check valve is expediently removed.
  • Pre-control valves which have an inlet connection and an outlet connection and an outlet connected to a control chamber on the directional control valve are usually used for the hydraulic actuation of the directional control valve on the basis of pressure reducing valves.
  • a constant maximum pilot pressure is present in the inlet connection.
  • a pressure is set in the output which is reduced compared to the maximum pilot pressure, with which the
  • Directional control valve is applied. Depending on the level of pressure at the outlet of a pressure reducing valve, the directional valve is adjusted proportionally to different extents.
  • the second control line is expediently connected to the part of the pilot oil circuit in which the maximum pilot pressure prevails.
  • a pilot oil circuit is not necessary if, according to claim 7, the control chamber of the check valve can be connected to the hydraulic accumulator via the second control line.
  • loading namely, the hydraulic accumulator is charged up to the load pressure, primarily until a maximum pressure is always reached up to the highest load pressure that has occurred in the pressure chamber of the hydraulic cylinder, so that when the control chamber of the shut-off valve is connected to the hydraulic accumulator, it is sufficient to open the shut-off valve Compressive force is available.
  • Figure 1 shows the first embodiment, in which a control chamber of an unlockable check valve from the pilot circuit for actuating the directional control valve with a changeover valve and a shuttle valve Pressure can be applied,
  • Figure 2 shows the second embodiment in which the control chamber is pressurized at the check valve from the hydraulic accumulator and
  • FIG. 3 shows the third embodiment, in which a first control line or a second control line can be connected via an electrically actuated changeover valve to a third control line leading to the control chamber of the unlockable check valve.
  • the hydraulic control arrangements shown are each intended for wheel loaders, tractors, telescopic handlers or other machines and comprise a control block 10 with a plurality of directional control valves, in particular also with a directional control valve 11, which can assume a spring-centered central position and can be controlled with the two hydraulic cylinders 12 designed as differential cylinders are with whom, for example the boom of a wheel loader can be raised and lowered.
  • the directional control valve 11 has a first working connection 13, from which a first working line 14 leads to the pressure chambers 15 on the bottom side of the hydraulic cylinders 12.
  • a second working line 16 runs between a second working connection 17 of the directional control valve 11 and the pressure chambers 18 of the hydraulic cylinders 12 on the piston rod side.
  • the two working connections 13 and 17 can be connected to a pressure medium source and to a tank 27 via a pressure connection and a tank connection.
  • a filling line 20 branches off from the working line 14 and leads to a hydraulic accumulator 21 via a check valve 22.
  • the check valve 22 is designed as a 2-way cartridge valve and has a movable valve member 23.
  • This is a stepped piston, which can sit on a seat cone with the end face of the piston section, which is smaller in diameter, in the manner of a seat valve.
  • the valve member 23 is acted upon by the pressure prevailing in the working line 14, that is to say by the load pressure of the two hydraulic cylinders 12 in the opening direction.
  • the accumulator pressure acts in the opening direction on the annular surface between the two piston sections of the valve member 23 via a connection 61 of a plate 26 in which the valve member 23 is located.
  • the valve member 23 is acted upon by a pressure prevailing in a rear control chamber 24 and by a compression spring 25, which is equivalent to a pressure of approximately 3 to 4 bar.
  • the first valve 30 is a 3/2-way valve with a first inlet 31, which is connected to the section of the filling line 20 located between the working line 14 and the check valve 22, and with a second inlet 32, which is connected to the hydraulic accumulator 21 connected is.
  • An output 33 of the directional control valve 30 can be connected either to the input 31 or to the input 32 depending on the load pressure in the working line 14. Namely, in the sense of a connection of the outlet 33 to the inlet 32, an adjustable compression spring 34 acts on the valve member of the valve 30, which is not shown in detail , so acted upon by the load pressure of the hydraulic cylinder 12.
  • a control channel 41 leads to a connection P of a control valve 42, which is a 4/2 way valve.
  • a control valve 42 which is a 4/2 way valve.
  • Whose valve member assumes a rest position under the action of a compression spring 43, in the passage between the port P and a port A, which is connected to the control chamber 24 of the check valve 22.
  • a tank port T and another port B of the control valve 42 are shut off in its rest position.
  • the tank connection is connected to a leakage connection Y of the plate 26 via channels leading through the housings of the various valves.
  • connection B of the control valve 42 is connected to the rear control chamber of a second 2-way cartridge valve 45 located in the plate 26, via which the piston rod-side pressure chambers 18 of the hydraulic cylinders 12 can be connected to a tank connection T of the plate 26.
  • the valve member of the control valve 42 can be brought into a switching position by an electromagnet 44 in which the port P is shut off and the two ports A and B are connected to the port T.
  • a releasable check valve 50 located in the working line 14 is connected upstream of these pressure chambers, which opens towards the pressure chambers.
  • a control line 52 is connected, which is connected to the output of a shuttle valve 53 in the embodiments according to FIGS. 1 and 2.
  • the control line 52 is the third control line within the meaning of the claims.
  • a control line 54 extends, which is the first control line within the meaning of the claims.
  • Another control line 55 the second control line in the sense of the claims, runs in the embodiments according to Figures 1 and 2 between the second input of the shuttle valve 53 and a port * 56 of a 3/2 way valve 57, the movable valve member under the Action of a compression spring 58 assumes a rest position in which the connection 56 is connected to a tank connection T, and can be brought into a position by an electromagnet 59 in which the connection 56 is connected to a pressure connection P.
  • the directional control valve 11 of the control block 10 can be actuated hydraulically proportionally, the pilot control pressures being generated with the aid of a hydraulic pilot control device 65 and being transmitted to the directional control valve 11 via control lines 66.
  • the control oil supply is used
  • Control oil pump 67 from which a pressure line 68 leads to pilot control device 65.
  • a pressure limiting valve 69 in the pressure line 68 a pressure of e.g. Maintain 30 bar. This is the maximum pilot pressure with which the directional valve 11 can be acted on.
  • the pressure connection P of the changeover valve 57 is connected to the pressure line 68.
  • the directional control valve is actuated in such a direction that the working line 14 receives pressure medium from a hydraulic pump can flow.
  • the check valve 50 opens and the piston rods extend, wherein in the pressure chambers 15 of the hydraulic cylinders 12 and in the working line 14 there is a load pressure determined by the load which is moved by the hydraulic cylinders.
  • this switches the accumulator pressure through the control valve 42 to the rear control chamber 34 of the check valve 22.
  • the load pressure now opens the check valve 22 whenever it is at least the small pressure difference equivalent to the force of the compression spring 25 above the storage pressure.
  • Pressure medium can then enter the hydraulic accumulator 21 via the filling line 20, so that this, apart from the force of the weak pressure spring 25, is always charged in the working line 14 to the greatest load pressure that occurred during a working cycle.
  • the check valve 50 can also be equipped with a closing spring. The pressure in the line section of the working line 14 between the directional control valve 11 and the check valve is then by a small pressure difference equivalent to the force of this closing spring greater than the pressure in the pressure chambers 15 of the hydraulic cylinders 12. If the equivalent pressure differences of the closing spring and the compression spring 25 of the Valve 22 is the same size, so the pressure in the hydraulic accumulator 21 is equal to the greatest pressure that occurred in the pressure chambers 15.
  • the check valve 22 remains closed. Because after switching the valve 30, the load pressure is present in the rear control chamber 24 of the check valve 22, so that in association with the compression spring 25, the check valve 22 is held securely. The pressure in the hydraulic accumulator 21 can therefore not exceed the value set on the compression spring 34 of the valve 30. For safety reasons, however, a pressure limiting valve 60 is additionally provided, the input of which is connected to the hydraulic accumulator 21.
  • a pressure in the vicinity of the tank pressure prevails in the working line 16 and in the pressure chambers 18 of the hydraulic cylinders 12 on the piston rod side when the piston rods are extended.
  • the loading shovel of a wheel loader is loaded and driven to an unloading point by the wheel loader.
  • the electromagnet 44 of the control valve 42 and the electromagnet 59 of the changeover valve 57 are energized, so that these two valves switch from the rest positions shown in FIG. 1 to the other switching position.
  • the rear control chamber 24 of the check valve 22 is connected via the control valve 42 to the port Y of the plate 26 and thus relieved to the tank 27.
  • the valve member 23 of the check valve 22 is lifted from its seat by the accumulator pressure and the pressure in the working line 14.
  • the control line 55 is connected via the changeover valve 57 to the pressure line 68, so that at one input of the changeover valve 53 a pressure in the amount of the maximum Pilot pressure pending. Since there is tank pressure at the other inlet of the shuttle valve 53, this pressure is passed from the shuttle valve to the control line 52 and from there into the control chamber 51 of the unlockable check valve 50. This opens so that there is an open connection between the hydraulic accumulator 21 and the pressure chambers 15 of the hydraulic cylinders 12.
  • the accumulator pressure corresponds to the maximum pressure reached during the working cycle, when the last opening valve 22 or 50 is opened there is no sagging of the piston rods of the hydraulic cylinders 12, but at most a slight lifting of the loading shovel. It may be the case that load pressures occur during the working cycle which cause the valve 30 to switch and which therefore do not follow the state of charge of the hydraulic accumulator. However, these load pressures only occur in special situations, e.g. when tearing an object anchored in the ground or when driving the loading shovel against a stop, but are not due to the weight of the loading shovel and the load that only acts when the wheel loader is driving. The state of charge of the hydraulic accumulator 21 is therefore always sufficient to keep the loading shovel at the level which it assumes when the valve 22 or the valve 50 is opened.
  • valve 45 Via the valve 45, which is also opened by the switching of the control valve 42, pressure medium can be displaced from the pressure chambers 18 on the piston rod side of the hydraulic cylinders 12 into the tank. Refill can be carried out via refill valves which are assigned to the directional control valve 11. Changes in volume of the pressure spaces 18 can thus be compensated for occur during the open connection of the pressure chambers 15 to the hydraulic accumulator 21.
  • FIG. 2 The embodiment according to FIG. 2 is largely the same as that according to FIG. 1, so that only the differences are dealt with below, but reference is made to the description of the embodiment according to FIG.
  • a hydraulic line 75 now runs between the pressure connection P of the changeover valve 57 and a connection 60 of the plate 26, which is internally connected to a second connection 61, which lies in the connection between the check valve and the hydraulic accumulator 21.
  • the accumulator pressure is therefore present at the pressure port P of the changeover valve 57.
  • the accumulator pressure is at the arbitrary or automatic actuation of the changeover valve 57, which occurs together with the actuation of the control valve 42 available to unlock the check valve 50.
  • the directional control valves of the control block 10 can be actuated hydraulically, as in the embodiment according to FIG. However, electrical or mechanical actuation is also readily possible. A pilot oil circuit is not necessary.
  • the embodiment according to FIG. 3 also corresponds to the embodiments according to FIGS. 1 and 2.
  • the shuttle valve 53 according to FIG. 2 is now replaced by a changeover valve 75 which, under the action of a compression spring 76, assumes a rest position in which the third control line 52 connects to the first
  • Control line 54 is connected.
  • the valve 75 can be brought into a second switching position by an electromagnet 77, which is controlled at the same time as the electromagnet 44 of the control valve 42, in which the third control line 52 is connected to the second control line 55, which leads directly to the connection 60 of the control valve Plate 26 leads.
  • Relief of the control line 55 to the tank is therefore not provided for in the embodiment according to FIG. be made possible by a further changeover valve.

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  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)

Abstract

L'invention se base sur un dispositif de commande hydraulique destiné à une machine de travail mobile, notamment à une chargeuse à roues. Un tel dispositif présente, de façon continue, au moins un cylindre hydraulique permettant le déplacement d'un outil, une valve de trajet permettant de commander le trajet de l'agent de pression entre un compartiment sous pression du cylindre hydraulique, une source d'agent de pression et un réservoir, un accumulateur hydraulique pouvant être raccordé à la source d'agent de pression par une conduite de remplissage, et une valve de commande. Cette valve permet d'établir ou d'interrompre la liaison entre l'accumulateur hydraulique et le compartiment sous pression du cylindre hydraulique. Un tel dispositif de commande hydraulique nécessite une sécurité supplémentaire empêchant la chute d'un outil. Pour cela, un clapet anti-retour déverrouillable, implanté en amont du compartiment sous pression du cylindre hydraulique et s'ouvrant vers ce compartiment, peut être ouvert en cas d'actionnement de la valve de trajet pour laisser s'écouler l'agent de pression du compartiment sous pression vers le réservoir et en cas d'actionnement de la valve de commande pour établir une liaison fluidique entre le compartiment sous pression et l'accumulateur hydraulique. Cela permet de réaliser, d'une part, la fermeture du compartiment sous pression du cylindre hydraulique, d'autre part, d'assurer sa liaison avec l'accumulateur hydraulique afin d'amortir le tangage.
EP98945142A 1997-08-11 1998-08-04 Dispositif de commande hydraulique destine a une machine de travail mobile, notamment a une chargeuse a roues Expired - Lifetime EP1003939B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19734658 1997-08-11
DE19734658A DE19734658A1 (de) 1997-08-11 1997-08-11 Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Radlader
PCT/EP1998/004848 WO1999007950A1 (fr) 1997-08-11 1998-08-04 Dispositif de commande hydraulique destine a une machine de travail mobile, notamment a une chargeuse a roues

Publications (2)

Publication Number Publication Date
EP1003939A1 true EP1003939A1 (fr) 2000-05-31
EP1003939B1 EP1003939B1 (fr) 2002-05-15

Family

ID=7838569

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98945142A Expired - Lifetime EP1003939B1 (fr) 1997-08-11 1998-08-04 Dispositif de commande hydraulique destine a une machine de travail mobile, notamment a une chargeuse a roues

Country Status (5)

Country Link
US (1) US6370874B1 (fr)
EP (1) EP1003939B1 (fr)
JP (1) JP2001512797A (fr)
DE (2) DE19734658A1 (fr)
WO (1) WO1999007950A1 (fr)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
US7089734B2 (en) 2000-05-25 2006-08-15 J.C. Bamford Excavators Limited Hydraulic system for wheeled loader
US7204086B2 (en) 2000-05-25 2007-04-17 J.C Bamford Excavators Limited Method of operating a hydraulic system for a loader machine

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US6397409B1 (en) 2000-04-14 2002-06-04 Freedom Bath, Inc. Bath lifting system
US20040231043A1 (en) * 2000-04-14 2004-11-25 Pop-In Pop-Out, Inc. Bath lifting system
US6643861B2 (en) 2000-04-14 2003-11-11 Freedom Bath, Inc. Bath lifting system
US20040098801A1 (en) * 2000-04-14 2004-05-27 Pop-In Pop-Out, Inc Bath lifting system
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KR101264661B1 (ko) 2008-02-27 2013-05-15 울산대학교 산학협력단 유압실린더의 위치에너지 회생용 유압회로
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CN103423220A (zh) * 2012-05-24 2013-12-04 合肥神马科技集团有限公司 一种控制伸缩臂的液压系统
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Publication number Priority date Publication date Assignee Title
US7089734B2 (en) 2000-05-25 2006-08-15 J.C. Bamford Excavators Limited Hydraulic system for wheeled loader
US7204086B2 (en) 2000-05-25 2007-04-17 J.C Bamford Excavators Limited Method of operating a hydraulic system for a loader machine

Also Published As

Publication number Publication date
DE59804150D1 (de) 2002-06-20
JP2001512797A (ja) 2001-08-28
EP1003939B1 (fr) 2002-05-15
US6370874B1 (en) 2002-04-16
WO1999007950A1 (fr) 1999-02-18
DE19734658A1 (de) 1999-02-18

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