EP1003939B1 - 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 Download PDF

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Publication number
EP1003939B1
EP1003939B1 EP98945142A EP98945142A EP1003939B1 EP 1003939 B1 EP1003939 B1 EP 1003939B1 EP 98945142 A EP98945142 A EP 98945142A EP 98945142 A EP98945142 A EP 98945142A EP 1003939 B1 EP1003939 B1 EP 1003939B1
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EP
European Patent Office
Prior art keywords
control
valve
pressure
hydraulic
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.)
Expired - Lifetime
Application number
EP98945142A
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German (de)
English (en)
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EP1003939A1 (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
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Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP1003939A1 publication Critical patent/EP1003939A1/fr
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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, for a mobile machine, especially for a wheel loader is used and the characteristics from the Preamble of claim 1.
  • shut-off valve arranged on the hydraulic accumulator and the lift cylinders is closed as long as the shovel is working and can be opened by the driver or automatically, as soon as pitch vibrations occur while driving or as soon as the driving speed above a certain value, e.g. over 6 km / h lies.
  • the branch of the filling line in front of the directional control valve block brings with it that the hydraulic accumulator is not only one Actuation of the directional valve assigned to the lift cylinders, but when actuating any directional valve that leads to a Pressure build-up in the pump line leads, is charged.
  • the hydraulic accumulator is not only one Actuation of the directional valve assigned to the lift cylinders, but when actuating any directional valve that leads to a Pressure build-up in the pump line leads, is charged.
  • the hydraulic accumulator is not only one Actuation of the directional valve assigned to the lift cylinders, but when actuating any directional valve that leads to a Pressure build-up in the pump line leads, is charged.
  • the hydraulic accumulator is not only one Actuation of the directional valve assigned to the lift cylinders, but when actuating any directional valve that leads to a Pressure build-up in the pump line leads, is charged.
  • the hydraulic accumulator is not only one Actuation of the directional valve assigned
  • a pressure rupture valve can also be used in a pressure chamber of a hydraulic cylinder be upstream, usually immediately sits on the hydraulic cylinder.
  • a pipe rupture safety valve is designed so that the pressure chamber has a pressure medium check valve opening towards the pressure chamber without further ado can flow. For the discharge of pressure medium from the pressure chamber becomes a bypass to the check valve more or less wide open.
  • a control piston is adjusted proportionally. He can to the pipe rupture valve from the above The same pilot pressure is applied to the document, with which the directional valve moves in one direction is controlled.
  • the invention has for its object a hydraulic Control arrangement with the features from the preamble of the claim 1 evolve so that the pressure chamber of a hydraulic cylinder can be blocked off, but that nevertheless connection necessary for damping pitching vibrations can be produced to a hydraulic accumulator.
  • Tax arrangement can be found in the subclaims.
  • control lines are provided, wherein the third control line, to the unlocking means of the check valve are connected via switching means when actuated of the directional valve with a first control line and at an actuation of the control valve with a second control line is connected.
  • the third control line to the unlocking means of the check valve are connected via switching means when actuated of the directional valve with a first control line and at an actuation of the control valve with a second control line is connected.
  • Control lines, electrical control signals and electrical Switching means conceivable.
  • the directional control valve can be operated hydraulically, then is a Pilot oil circuit with a pilot oil source available which according to claim 6 expediently also the control oil for the unlocking of the check valve is removed.
  • a Pilot oil circuit with a pilot oil source available which according to claim 6 expediently also the control oil for the unlocking of the check valve is removed.
  • Usually are used for hydraulic actuation of the directional valve on the Pilot valves working on the basis of pressure reducing valves uses an inlet connection and an outlet connection and one connected to a control room on the directional valve Own exit. There is a constant maximum in the inlet connection Pilot pressure. In the exit is depending on the adjustment of a pressure reducing valve compared to the maximum Pilot pressure reduced pressure with which the Directional control valve is applied. Depending on the amount of pressure on The directional valve becomes different at the outlet of a pressure reducing valve adjusted proportionally. It is expedient now the second control line to the part of the pilot oil circuit connected 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 via the second Control line can be connected to the hydraulic accumulator. Operational namely the hydraulic accumulator up to the load pressure, primarily until a maximum pressure is always reached by highest occurred in the pressure chamber of the hydraulic cylinder Load pressure charged so that when the control chamber is connected of the check valve with the hydraulic accumulator one for opening sufficient pressure force is available stands.
  • the hydraulic control arrangements shown are each for wheel loaders, tractors, telescopic handlers or other machines provided and comprise a control block 10 with several Directional control valves, in particular with a directional control valve 11, the can take a spring-centered position and with the two hydraulic cylinders designed as differential cylinders 12 can be controlled with which e.g. the boom of a wheel loader can be raised and lowered.
  • the directional valve 11 has a first working connection 13, of which a first working line 14 to the bottom pressure chambers 15 of the hydraulic cylinders 12 leads.
  • a second working line 16 runs between a second working connection 17 of the directional valve 11 and the piston rod-side pressure chambers 18 of the hydraulic cylinders 12. Via a pressure connection and a tank connection the two working connections 13 and 17 with a pressure medium source and connected to a tank 27.
  • the Check valve 22 is designed as a 2-way cartridge valve and has a movable valve member 23. This is a step piston the one with the face of the smaller one in diameter Piston section in the manner of a seat valve on a Seat cone can sit on. On the said face the valve member 23 from the prevailing in the working line 14 Pressure, that is, the load pressure of the two hydraulic cylinders 12 in the opening direction applied. On the ring surface between the Both piston sections of the valve member 23 act via one Terminal 61 of a plate 26 in which the valve member 23rd the accumulator pressure is in the opening direction. In the closing direction the valve member 23 from one to the rear Control room 24 prevailing pressure and a compression spring 25 applied, which is equivalent to a pressure of about 3 to 4 bar is.
  • the first valve 30 is a 3/2-way valve with a first input 31, which with the between the working line 14 and the check valve 22 section the filling line 20 is connected, and with a second Input 32, which is connected to the hydraulic accumulator 21.
  • An output 33 of the directional control valve 30 is dependent on Load pressure in the working line 14 either with the input 31 or connectable to the input 32. It works in the sense a connection of the output 33 to the input 32 a adjustable compression spring 34 on the not shown Valve member of the valve 30. In the sense of a connection of the Output 33 with the input 31, the valve member of the Pressure in the inlet 31, i.e. from the load pressure of the hydraulic cylinders 12 applied.
  • a control channel 41 leads from the outlet 33 of the directional control valve 30 a port P of a control valve 42, which is a 4/2-way valve is. Its valve member takes effect a compression spring 43 a rest position in the passage exists between the port P and a port A, which with the control chamber 24 of the check valve 22 is connected.
  • On Tank connection T and another connection B of the control valve 42 are locked in its rest position.
  • the tank connection is through the housing of the various valves Channels with a leakage connection Y of the plate 26 connected.
  • the port B of the control valve 42 is connected to the rear control space of a second located in the plate 26 located 2-way cartridge valve 45 connected through which pressure chambers 18 of the hydraulic cylinder 12 on the piston rod side a tank port T of the plate 26 can be connected.
  • the valve member of the control valve 42 may be an electromagnet 44 are brought into a switching position in which the port P shut off and the two ports A and B connected to the terminal T.
  • a control line 52 connected to the versions according to Figures 1 and 2 with the output of a shuttle valve 53 is connected.
  • the control line 52 is the third control line within the meaning of the claims.
  • a control line 54 which is the first control line in the sense of the claims.
  • Another control line 55 runs according to the explanations Figures 1 and 2 between the second input of the shuttle valve 53 and a connection 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 with a tank port T is connected, and an electromagnet 59 can be brought into a position in which the Port 56 is connected to a pressure port P.
  • the directional valve 11 is the Control blocks 10 can be actuated hydraulically in proportion, wherein the pilot pressures with the help of a hydraulic pilot device 65 generated and via control lines 66 to the directional control valve 11 are given.
  • the control oil supply is used Control oil pump 67, from which a pressure line 68 to the pilot control unit 65 leads.
  • a pressure relief valve 69 is in 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 applied.
  • the pressure port P of the Switch valve 57 is connected to the pressure line 68.
  • the directional valve is actuated in such a direction, that the working line 14 pressure medium from a hydraulic pump can flow.
  • the check valve 50 opens and the Piston rods extend, the hydraulic cylinders in the pressure chambers 15 12 as well as in the working line 14 by the Load moved by the hydraulic cylinders more specific Load pressure prevails.
  • the load pressure in the work line 14 below that on the compression spring 34 of the directional valve 30 set pressure remains, this switches the memory pressure via the control valve 42 to the rear control chamber 24 of the check valve 22 through.
  • the load pressure now opens that Check valve 22 whenever it is at least the Force of the compression spring 25 equivalent small pressure difference is above the store pressure.
  • the check valve 50 can 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 one the force of this closing spring is equivalent to a small pressure difference greater than the pressure in the pressure chambers 15 of the hydraulic cylinders 12.
  • the equivalent pressure differences of the Closing spring and the compression spring 25 of the valve 22 are the same large, the pressure in the hydraulic accumulator 21 is equal to the largest pressure occurred in the pressure rooms 15.
  • the check valve 22 remains closed. Because after one Switching of the valve 30 is in the rear control room 24 of the check valve 22 of the load pressure, 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 be that at the compression spring 34 of the valve 30 do not exceed the set value. For safety reasons, however, there is also a pressure relief valve 60 provided, the input with the hydraulic accumulator 21 is connected.
  • the valve member 23 of the check valve 22 is the storage pressure and lifted from its seat by the pressure in the working line 14.
  • the control line 55 is via the changeover valve 57 connected to the pressure line 68, so that at one input of the shuttle valve 53 a pressure in the amount of the maximum Pilot pressure pending. This pressure is there on the other Input of the shuttle valve 53
  • valve 45 can pressure fluid from the piston rod side Pressure chambers 18 of the hydraulic cylinder 12 displaced into the tank become. Refill can be done using refill valves, which are assigned to the directional valve 11. So that can Volume changes of the pressure spaces 18 are compensated for during the open connection of the pressure chambers 15 to the hydraulic accumulator 21 occur.
  • FIG. 2 The embodiment according to FIG. 2 is largely the same as that according to Figure 1, so that only the differences in the following discussed, but otherwise to the description of the execution is referred to Figure 1.
  • the pressure port P of the switching valve 57 is therefore the memory pressure.
  • the directional control valve 10 can as be hydraulically actuated in the embodiment according to FIG. However, it is also an electrical or mechanical one Operation possible. A pilot oil circuit is not necessary.
  • FIG. 3 is also correct with regard to the Control block 10, the hydraulic cylinders 12, the hydraulic accumulator 21, the valves 22, 30, 42, 45 and 50 with the designs according to Figures 1 and 2 match.
  • FIG. 2 there is further agreement in that the check valve 50 to unlock from the hydraulic accumulator 21 with Pressure is applied.
  • the shuttle valve 53 according to Figure 2 replaced by a changeover valve 75, the under assumes a rest position due to the action of a compression spring 76, in which the third control line 52 with the first Control line 54 is connected.
  • the valve 75 can by a Electromagnet 77, the same with the electromagnet 44 of the control valve 42 is driven into a second Switch position in which the third control line 52 is connected to the second control line 55 which leads directly to connection 60 of plate 26.
  • a relief the control line 55 to the tank is therefore in execution not provided according to Figure 3, but could also be there e.g. 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)

Claims (9)

  1. Un dispositif de pilotage hydraulique pour une machine fournissant du travail mobile, en particulier pour un chargeur mobile,
    doté d'au moins un vérin (12) hydraulique, permettant d'actionner un outil de travail,
    doté d'un distributeur (11), destiné au pilotage des voies de pression reliant une chambre (15) de pression du vérin (12) hydraulique, une source de fluide de pression et un réservoir (27),
    doté d'un accumulateur (21) hydraulique, pouvant être raccordé à la source de fluide de pression au travers d'une conduite (20) de remplissage,
    et doté d'une valve (42) de pilotage, permettant le pilotage dans le sens d'une ouverture et d'une fermeture d'une connexion entre l'accumulateur (21) hydraulique et la chambre (15) de pression du vérin (12) hydraulique,
    caractérisé par une valve (50) d'isolation pilotée, qui est branchée en amont de la chambre (15) de pression et qui ouvre dans le sens de cette dernière et qui peut être pilotée de façon à ouvrir dans le sens de l'évacuation du fluide de pression de la chambre (15) de pression vers le réservoir (27) lorsque le distributeur (11) est actionné, et de façon à ouvrir dans le sens de l'établissement d'une connexion par voie fluide de la chambre (15) de pression vers l'accumulateur (21) hydraulique lorsque la valve (42) de pilotage est actionnée.
  2. Un dispositif de pilotage hydraulique conforme à la revendication n° 1, caractérisé en ce que la valve (50) d'isolation peut être sollicitée par un signal de pilotage au travers d'une première conduite (54) de pilotage, lors d'un actionnement du distributeur (11), et par un signal de pilotage au travers d'une deuxième conduite (55) de pilotage, lors d'un actionnement de la valve (42) de pilotage, et que des moyens (53, 75) de commutation sont prévus, lesquels raccordent une troisième conduite (52) de pilotage, disposée entre eux et les moyens (51) de déblocage de la valve (50) d'isolation, soit à la première conduite (54) de pilotage, soit à la deuxième conduite (55) de pilotage, en fonction de l'actionnement de la valve (42) de pilotage.
  3. Un dispositif de pilotage hydraulique conforme à la revendication n° 2, caractérisé en ce que la valve (50) d'isolation peut être déverrouillée par voie hydraulique et présente une chambre (51) de pilotage, vers laquelle mène la troisième conduite (52) hydraulique de pilotage, qu'une valve (53, 75) de commutation est présente, laquelle peut être actionnée à l'aide de la valve (42) de pilotage, et que la troisième conduite (52) de pilotage est raccordée a la première conduite (54) hydraulique de pilotage, pour une des positions de commutation de la valve (53, 75) de commutation et lors d'un actionnement du distributeur (11) dans le sens d'une évacuation du fluide de pression hors de la chambre (15) de pression du vérin (12) hydraulique, et est raccordée à la deuxième conduite (55) hydraulique de pilotage pour l'autre position de commutation de la valve (53, 75) de commutation.
  4. Un dispositif de pilotage hydraulique conforme à la revendication n° 3, caractérisé en ce que la première conduite (54) de pilotage est raccordée à une deuxième chambre (18) de pression du vérin (12) hydraulique.
  5. Un dispositif de pilotage hydraulique conforme à la revendication n° 3, caractérisé en ce que le distributeur peut être actionné par voie hydraulique, en étant sollicité par une pression de pilotage, et que la pression de pilotage règne également dans la première conduite de pilotage.
  6. Un dispositif de pilotage hydraulique conforme à une des revendications n° 3 à n° 5, caractérisé en ce que un circuit d'huile de pilotage doté d'une source (67) d'huile de pilotage est présent et le distributeur (11) peut être actionné par voie hydraulique grâce à l'afflux d'huile de pilotage du circuit d'huile de pilotage et que la valve (50) d'isolation peut être déverrouillée par l'afflux, par la deuxième conduite (55) de pilotage, d'huile de pilotage en provenance du circuit d'huile de pilotage.
  7. Un dispositif de pilotage hydraulique conforme à une des revendications n° 3 à n° 5, caractérisé en ce que la chambre (51) de pilotage de la valve (50) d'isolation peut être raccordée à l'accumulateur (21) hydraulique, par la deuxième conduite (55) de pilotage.
  8. Un dispositif de pilotage hydraulique conforme à la revendication n° 6 ou n° 7, caractérisé en ce que une valve (57) de commutation est présente et que la deuxième conduite (55) de pilotage est raccordée au réservoir (27), pour une première position de commutation de la valve (57) de commutation, et à une source de pression (21, 67), pour une seconde position de commutation de la valve (57) de commutation.
  9. Un dispositif de pilotage hydraulique conforme à la revendication n° 8, caractérisé en ce qu'il présente une valve (53) de sélection, qui agit dans le sens de la sélection de la pression maximum entre la première conduite (54) de pilotage et la deuxième conduite (55) de pilotage et qui, le cas échéant, raccorde celle de ces deux conduites (54, 55) de pilotage, où règne la pression supérieure, à la troisième conduite (52) de pilotage.
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
DE19734658A DE19734658A1 (de) 1997-08-11 1997-08-11 Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Radlader
DE19734658 1997-08-11
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 EP1003939A1 (fr) 2000-05-31
EP1003939B1 true EP1003939B1 (fr) 2002-05-15

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ID=7838569

Family Applications (1)

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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)

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6357230B1 (en) * 1999-12-16 2002-03-19 Caterpillar Inc. Hydraulic ride control 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
US6397409B1 (en) 2000-04-14 2002-06-04 Freedom Bath, Inc. Bath lifting system
GB2365407B (en) 2000-05-25 2003-10-08 Bamford Excavators Ltd 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
JP2004011168A (ja) * 2002-06-04 2004-01-15 Komatsu Ltd 建設機械
DE10227966A1 (de) 2002-06-22 2004-01-08 Deere & Company, Moline Hydraulische Steueranordnung für eine mobile Arbeitsmaschine
US20050066655A1 (en) * 2003-09-26 2005-03-31 Aarestad Robert A. Cylinder with internal pushrod
GB2418903B (en) * 2004-10-08 2008-06-25 Caterpillar Inc Ride control circuit for a work machine
DE102004056418B4 (de) * 2004-11-23 2013-02-28 Deere & Company Hydraulische Anordnung
DE102005033154A1 (de) * 2005-07-13 2007-01-18 Deere & Company, Moline Hydraulische Anordnung
DE102005038333A1 (de) * 2005-08-11 2007-02-15 Deere & Company, Moline Hydraulische Anordnung
ITTO20050629A1 (it) * 2005-09-15 2007-03-16 Cnh Italia Spa Disposizione idraulica per un braccio di sollevamento incernierato ad un veicolo
US7441405B2 (en) * 2006-03-31 2008-10-28 Caterpillar Inc. Cylinder with internal pushrod
KR101264661B1 (ko) 2008-02-27 2013-05-15 울산대학교 산학협력단 유압실린더의 위치에너지 회생용 유압회로
CN103119307B (zh) * 2010-08-09 2015-07-01 派克·汉尼汾制造瑞典公司 液压控制系统
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
CN103030065B (zh) * 2012-12-26 2014-11-19 三一重工股份有限公司 一种液压锁止控制系统、起重机的液压总成和起重机
AU2018202033B2 (en) * 2017-03-23 2023-06-01 The Raymond Corporation Systems and methods for mast stabilization on a material handling vehicle

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4286432A (en) * 1979-08-30 1981-09-01 Caterpillar Tractor Co. Lock valve with variable length piston and hydraulic system for a work implement using the same
DE3239930A1 (de) 1982-10-28 1984-05-10 Mannesmann Rexroth GmbH, 8770 Lohr Hydraulisch steuerbares sperrventil, insbesondere fuer die rohrbruchsicherung
JPS60250128A (ja) 1984-05-25 1985-12-10 Mitsubishi Heavy Ind Ltd 液圧再生回路
NL8801644A (nl) * 1988-06-28 1990-01-16 Applied Power Inc Hydraulische bedieningseenheid, meer in het bijzonder voor het heffen van een last, zoals een ziekenhuisbed.
US4951767A (en) 1988-10-28 1990-08-28 Allied Systems Company Vehicle suspension lock system
DE68918930T2 (de) * 1989-02-06 1995-03-23 Kobe Steel Ltd Vorrichtung zur Unterdrückung von Vibrationen für Baumaschinen auf Rädern.
DE3909205C1 (fr) * 1989-03-21 1990-05-23 Hanomag Ag, 3000 Hannover, De
JPH0662270B2 (ja) * 1989-05-10 1994-08-17 株式会社神戸製鋼所 移動式クレーンの変位抑制装置
JP2582310B2 (ja) * 1990-09-10 1997-02-19 株式会社小松製作所 作業機の位置エネルギー回収・活用装置
DE4221943C2 (de) * 1991-09-04 1996-01-25 Orenstein & Koppel Ag Hydraulikanlage für mit Arbeitsgeräten versehene fahrbare Arbeitsmaschinen
DE4129509C2 (de) * 1991-09-05 1994-06-16 Rexroth Mannesmann Gmbh Hydraulische Steueranordnung für Baumaschinen
CZ279137B6 (cs) * 1991-12-04 1995-01-18 František Ing. Krňávek Zařízení pro rekuperaci polohové energie praco vního zařízení stavebního, nebo zemního stroje
JP3129495B2 (ja) * 1991-12-13 2001-01-29 株式会社小松製作所 昇降作業機の位置エネルギ回収装置
DE4212184A1 (de) * 1992-04-10 1993-10-14 Bosch Gmbh Robert Hydraulische Steuereinrichtung für einen Arbeitszylinder
US5388857A (en) * 1992-08-27 1995-02-14 Badger Equipment Company Operator controlled vehicle stabilizer
JP3153864B2 (ja) 1993-03-29 2001-04-09 株式会社小松製作所 ホイール式建設車両の走行振動抑制装置
SE500967C2 (sv) * 1993-11-18 1994-10-10 Pressmaster Tool Ab Förfarande för drivning av ett hydrauliskt arbetsverktyg och anordning för genomförande av förfarandet
DE4416228A1 (de) * 1994-05-07 1995-11-09 Rexroth Mannesmann Gmbh Hydraulische Anlage für ein mobiles Arbeitsgerät, insbesondere für einen Radlader

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Publication number Publication date
EP1003939A1 (fr) 2000-05-31
DE59804150D1 (de) 2002-06-20
JP2001512797A (ja) 2001-08-28
US6370874B1 (en) 2002-04-16
DE19734658A1 (de) 1999-02-18
WO1999007950A1 (fr) 1999-02-18

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