[go: up one dir, main page]

EP0968334B1 - Systeme de commande hydraulique pour une machine de travail mobile, en particulier pour un chargeur sur roues - Google Patents

Systeme de commande hydraulique pour une machine de travail mobile, en particulier pour un chargeur sur roues Download PDF

Info

Publication number
EP0968334B1
EP0968334B1 EP98916979A EP98916979A EP0968334B1 EP 0968334 B1 EP0968334 B1 EP 0968334B1 EP 98916979 A EP98916979 A EP 98916979A EP 98916979 A EP98916979 A EP 98916979A EP 0968334 B1 EP0968334 B1 EP 0968334B1
Authority
EP
European Patent Office
Prior art keywords
valve
control
pressure
hydraulic
directional
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
EP98916979A
Other languages
German (de)
English (en)
Other versions
EP0968334A1 (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
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP0968334A1 publication Critical patent/EP0968334A1/fr
Application granted granted Critical
Publication of EP0968334B1 publication Critical patent/EP0968334B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • E02F9/2203—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
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • 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
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2267—Valves or distributors

Definitions

  • the invention is based on a hydraulic control arrangement, for a mobile machine, especially for one Wheel loader is used and the features from the generic term of claim 1.
  • 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 invention has for its object a hydraulic Control arrangement with the features from the preamble of the claim 1 evolve so that uncontrolled movements to dampen pitch vibrations of the machine the hydraulic cylinder that can be connected to the hydraulic accumulator is largely avoided become.
  • the hydraulic cylinder is usually a double-acting and controllable with the help of a directional valve, which consists of a medium Rest out in two opposite directions Working positions is adjustable.
  • a directional valve which consists of a medium Rest out in two opposite directions Working positions is adjustable.
  • the hydraulic accumulator only when the directional valve is actuated in which one direction can be filled. The tax arrangement this simplifies. With a wheel loader e.g. is it are sufficient if the hydraulic accumulator only when the Flow pressure medium flow in the direction of lifting the lift cylinder can.
  • control the fillability of the hydraulic accumulator advantageously uses a control valve that by actuating the directional valve from a first switching position, in which it prevents the hydraulic accumulator from being filled, in which the filling line is so blocked that even then no pressure medium flows to the hydraulic accumulator when the pump pressure or the load pressure is higher than the storage pressure, in a second switching position is switchable, in which the hydraulic accumulator can be filled.
  • the control valve that can be switched by actuating the directional control valve is advantageously a seat valve, so that a largely Leak-free shut-off of the filling line guaranteed is.
  • Directional control valves used in mobile hydraulics are increasingly no longer directly mechanical, but via pre-control signals that can be specified using a pilot control device driven. According to claim 5, a pilot signal is now for the directional valve also used to generate a control signal to switch the control valve from the first Bring switching position into the second switching position.
  • An embodiment according to claim 6 is particularly preferred, after which the filling line from one between the directional valve and branches off the hydraulic cylinder running working line and itself a pressure-controlled shut-off valve with a Valve member is that of the prevailing in the working line Load pressure in the opening direction and from the pressure in a rear Control room can be acted upon in the closing direction.
  • To the The rear control room is filled with the hydraulic accumulator connected to the hydraulic accumulator.
  • the working machine must have an open connection between the hydraulic accumulator and the hydraulic cylinder. For this the Relieved control room to the tank.
  • To fill the Prevent hydraulic accumulator when the directional valve is not actuated is the rear control room against the outflow of Lockable pressure medium. The check valve can then from the load pressure cannot be opened.
  • Claims 7 to 10 contain advantageous developments a hydraulic control arrangement according to claim 6.
  • the hydraulic control arrangements shown are each for Wheel loaders, tractors, telescopic handlers or other machines provided and comprise a control block 10 with a plurality of directional valves, in particular with a directional valve 11, the one can take spring-centered position and with the two Hydraulic cylinder 12 designed as a differential cylinder can be controlled with which the boom of a wheel loader is lifted and can be lowered.
  • the directional control valve 11 has a first one Working connection 13, from which a first working line 14 to the bottom pressure chambers 15 of the hydraulic cylinder 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.
  • a check valve 22 is arranged, which is a 2-way cartridge valve is formed and a movable valve member 23 has.
  • This is a stepped piston with the Face of the piston section smaller in diameter kind of a seat valve can sit on a seat cone.
  • On the said end face becomes the valve member 23 from in the working line 14 prevailing pressure, i.e. the load pressure of the two Hydraulic cylinder 12 acted upon in the opening direction.
  • the valve member 23 is one in one rear control chamber 24 prevailing pressure and one weak compression spring 25 is applied.
  • 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.
  • On Output 33 of the directional control valve 30 is dependent on the load pressure in the working line 14 either with the input 31 or with the input 32 connectable. It works in the sense of a connection of the output 33 with the input 32 an adjustable Compression spring on the valve member not shown Valve 30. In the sense of a connection of the output 33 with the Input 31, the valve member from the pressure in input 31, So acted upon by the load pressure of the hydraulic cylinder 12.
  • a pilot valve 40 is placed on the directional control valve 30 is designed as a 2/2-way seat valve and as an unlockable Check valve can be considered.
  • a connection P one another pilot valve 50, which is a 4/2-way valve.
  • a tank connection T and another connection B of the pilot valve 50 are blocked in its rest position. The tank connection is over through the housing of the various Channels leading through valves with a leakage connection Y of the plate 26 connected.
  • Port B of the pilot valve 50 is with the rear control room of a second yourself connected in the plate 26 2-way cartridge valve 60, via which the piston rod-side pressure chambers 18 of the hydraulic cylinders 12 connected to a tank port T of the plate 26 can be.
  • the valve member of the pilot valve 50 can be of one Electromagnets 52 are brought into a switching position, in which the port P is shut off and the two ports A and B are connected to the terminal T.
  • the pilot valve 40 is in a line 53 between the connection A of the pilot valve 50 and the rear control chamber 24 of the check valve 22 arranged. Its valve member is from one Compression spring 42 and of that in the rear control chamber of the check valve 22 prevailing pressure towards a rest position pressurized in which there is an outflow of pressure medium from the rear control chamber 24 for connection A of the pilot valve 50 prevents an inflow of pressure medium from port A of the pilot valve 50 to the rear control room 24 but allows.
  • the valve member can be moved from an electromagnet 43 into a switching position in which there is a free passage between the port A of the pilot valve 50 and the rear control room 24 of the check valve 22.
  • the directional control valve 11 of the control block 10 is hydraulically proportional operable, the pilot pressures using a hydraulic Pilot control unit 55 is generated and via control lines 56 are given to the directional valve 11.
  • a hydraulic Pilot control unit 55 To the pilot line, into which a pilot pressure is set when the Hydraulic cylinder 12 are operated in the direction of lifting the boom and the bottom-side pressure chambers 15 with pressure medium is an electrical pressure switch 57 connected, which switches at a certain pilot pressure.
  • This particular pilot pressure is preferably that Pilot pressure at which the spring-centered valve spool of the directional valve 11 begins to move.
  • By switching the Pressure switch 57 becomes the electromagnet 43 of the pilot valve 40 excited and put this pilot valve in the switch position, in which there is an open connection between port A of the pilot valve 50 and the rear control chamber 24 of the check valve 22 prevails.
  • the solenoid 52 of the pilot valve 50 is arbitrarily by the driver if pitching vibrations occur, or automatically at a certain speed of the mobile machine, e.g. at a speed of 6 km / h on Suspense.
  • the hydraulic accumulator 21 is therefore in its state of charge due to the pressure build-up in the pressure rooms 15 not affected. The same applies if the directional valve in the direction of lowering the hydraulic cylinder 12 is actuated. Also then the pilot valve 40 remains in the switching position shown, so that the check valve 22 does not depend on the pressure in the pressure chambers 15 the hydraulic cylinder 12 can be opened.
  • the memory pressure 21 Since the memory pressure 21 the during the work cycle corresponds to the maximum pressure reached when opening the Check valve 22 no sagging, but at most a light one Raise the loading shovel. It may be that during the working game Load pressures occur that cause valve 30 to switch bring and therefore the state of charge of the hydraulic accumulator 21 does not follow. However, these load pressures occur only in special Situations, e.g. when tearing one off in the ground anchored object or when driving the loading shovel against a stop on, but are not by the weight of the Loading shovel and the cargo due to driving alone of the wheel loader works. The state of charge of the hydraulic accumulator 21 is therefore always sufficient to keep the bucket level keep that it takes when opening the check valve 22.
  • Valve 60 can pressure fluid from the piston rod side Pressure chambers 18 of the hydraulic cylinder 12 displaced into the tank or fed from the tank to make volume changes to equalize the pressure spaces 18 during the open connection the pressure chambers 15 occur with the hydraulic accumulator 21.
  • the embodiment of Figure 2 differs only in With regard to the pilot valves 40 and 50 from that of Figure 1. It is therefore with regard to the control block 10 that Hydraulic cylinder 12, the hydraulic accumulator 21, the check valves 22 and 60, the directional control valve 30 and the pilot control unit 55 to the corresponding Description of Figure 1 referenced. Differently to the embodiment of Figure 1 is that now the two pilot valves 40 and 50 combined into a single pilot valve 60 are, which is placed on the directional control valve 30.
  • the pilot valve 60 has a spring-centered central position in which the connections T and B are blocked off and between the connections P and A only a flow from P to A is possible.
  • the valve member of the pilot valve 60 can be activated by driving a Electromagnet 52 from the central position into a side Switch position in which the connections A and B are connected to the terminal T. From the middle position in the opposite direction, the valve member can be acted upon with the pressure prevailing in the pilot line 56 be adjusted in the for the supply of pressure medium in the bottom-side pressure chambers 15 of the hydraulic cylinder 12 a pilot pressure is built up. In this other switching position of the directional valve 60, port A is freely connected to port P. Port A is now directly connected to the rear control room 24 of the check valve 22 connected.
  • the pilot valve 60 In the middle position or in the lower position of the directional valve 11, the pilot valve 60 assumes its central position, if the speed of the work machine a certain one Value does not exceed or the electromagnet 52 is not arbitrary has been switched on. In the raised position of the directional valve 11 becomes the valve member of the directional valve 60 with pressure acts and reaches the switch position in which the connection P is connected to port A. In the back Control chamber 24 of the check valve 22 is then depending on the position of the valve 30 the accumulator pressure or the load pressure. The hydraulic accumulator is up to the maximum load pressure reached or to the pressure set on the compression spring 34 of the valve 30 charged.
  • the solenoid 52 is energized so that the valve member of the directional control valve 60 reaches the switching position in which the Ports A and B are connected to port T.
  • the back Control rooms of the check valves 22 and 60 are pressurized relieved, so that the two check valves 22 and 60 open and an open connection between the hydraulic accumulator 21 and the Pressure rooms 15 of the hydraulic cylinder 12 and consists of the pressure rooms 18 pressure medium displaced and in the pressure chambers 18 pressure medium can be fed.
  • the pressure at port T of a Valve blocks are usually a few bar above the tank pressure there is at the leakage oil connection Y, so that the check valve 60th of the pressure at the tank connection T against the tank pressure in the rear Control room can be opened.
  • the filling line 20 branches out the valve control block 10 from a pump line 65.
  • a 2/2-way valve 70 In the filling line 20 leading to several hydraulic accumulators 21, in Flow direction of the pressure medium from the pump line 65 to seen the hydraulic cylinders 21, first a 2/2-way valve 70, a pressure control valve 71 and a check valve 72 are arranged.
  • the directional control valve In the rest position brought about by a compression spring
  • Directional control valve 70 whose two connections are shut off from each other.
  • the directional control valve can be controlled by an electromagnet 73 can be switched into a through position. And the electromagnet 73 is energized whenever that happens
  • Directional valve 11 located within the control block 10 for actuation the hydraulic cylinder 12 In the middle position of the directional valve 11 and when it is actuated the directional control valve 70 is in its direction Starting position.
  • a maximum pressure is set on the pressure control valve 71 to to which the hydraulic accumulator 21 can be charged. As long as this pressure is not reached, the pressure control valve switches the outlet of the directional valve 70 to the check valve 72 through. When the pressure is reached, the valve with the outlet of the directional valve 70 connected input of the valve 71 blocked and the with the connection connected to the recoil is connected to the tank.
  • the hydraulic accumulator 21 can via a line 74 with the between the working connection 13 of the directional control valve and the pressure chambers 15 of the hydraulic cylinder 12 extending working line 14 connected become.
  • this line 74 is a 4/2-way valve 75 installed, the rest position under the action of a compression spring 76 occupies in the two sections of line 74 against each other are cordoned off and therefore no connection between the hydraulic accumulators 21 and the working line 14.
  • the directional valve 75 has two further connections for two sections of a line 77 by the work line 15 between the directional control valve 11 and the pressure chambers 18 the hydraulic cylinder 12 leads to the tank 27.
  • the directional control valve 75 At rest of the directional control valve 75 are also the two sections of the line 77 cordoned off from each other.
  • the directional control valve 75 can be of one Electromagnets 78 are brought into a switching position in each of the two sections of line 74 and the two Sections of line 77 are interconnected.
  • the electromagnet 78 is energized when the hydraulic with the shown Control arrangement equipped work machine a certain Driving speed exceeds.

Landscapes

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

Claims (10)

  1. Un dispositif de commande hydraulique pour une machine de travail mobile, en particulier pour un chargeur à roues, doté d'au moins un vérin (12) hydraulique, qui permet d'actionner un outil de travail, doté d'un distributeur (11), qui est dédié à la commande des voies de fluide de pression entre le vérin (12) hydraulique, une source de fluide de pression et un réservoir (27), doté d'un accumulateur (21) hydraulique, qui peut être raccordé à une source de fluide de pression par une conduite (20) de remplissage, et doté d'une valve (50, 60, 75) de commande, qui permet de commander l'ouverture et la fermeture d'une connexion entre l'accumulateur (21) hydraulique et le vérin (12) hydraulique, caractérisé en ce que l'accumulateur (21) hydraulique ne peut être rempli que lorsque le distributeur (11) est actionné.
  2. Un dispositif de commande hydraulique conforme à la revendication n° 1, caractérisé en ce que le distributeur (11) peut être actionné vers des positions de travail dans deux sens opposés à partir d'une position médiane de repos et que l'accumulateur (21) hydraulique ne peut être rempli que lorsque le distributeur (11) est actionné dans un sens donné.
  3. Un dispositif de commande hydraulique conforme à la revendication n° 1 ou 2, caractérisé par une valve (40, 60, 70) de pilotage, qu'un actionnement du distributeur (11) peut faire commuter hors d'une première position de commutation, dans laquelle elle empêche tout remplissage de l'accumulateur (21) hydraulique, vers une seconde position de commutation, dans laquelle l'accumulateur (21) hydraulique peut être rempli.
  4. Un dispositif de commande hydraulique conforme à la revendication n° 3, caractérisé en ce que la valve (40, 60) de pilotage, pouvant être commutée par le distributeur (11), est une valve à siège de clapet.
  5. Un dispositif de commande hydraulique conforme à la revendication n° 3 ou 4, caractérisé en ce que le distributeur (11) peut être commandé par un signal de pilotage, lequel est donné en consigne par un pilotage (55), et qu'un signal de commande pour une commutation de la première position de commutation dans la seconde commutation peut être amené vers la valve (40, 60, 70) de pilotage, laquelle peut être commutée par un actionnement du distributeur (11), lorsqu'un signal de pilotage est donné pour le distributeur (11).
  6. Un dispositif de commande hydraulique conforme à une revendication précédente, caractérisé en ce que la conduite (20) de remplissage est dérivée d'une conduite (14) de travail, qui relie le distributeur (11) au vérin (12) hydraulique, qu'une valve (22) de fermeture à commande par pression est disposée dans la conduite (20) de remplissage et dotée d'un corps (23) de valve, qui peut être sollicité dans le sens d'une ouverture par la pression en charge régnant dans la conduite (14) de travail et dans le sens d'une fermeture par la pression régnant dans une chambre (24) de commande arrière, et que la chambre (24) de commande arrière peut être raccordée à l'accumulateur (21) hydraulique, pour le remplissage de l'accumulateur (21) hydraulique, et au réservoir (27), pour l'ouverture de la connexion entre l'accumulateur (21) hydraulique et le vérin (12) hydraulique, et peut être fermée lorsque le distributeur (11) n'est pas actionné, afin de prévenir l'évacuation du fluide de pression.
  7. Un dispositif de commande hydraulique conforme à la revendication n° 6, caractérisé en ce que la chambre (24) de commande arrière de la valve (22) de fermeture peut être sollicitée par le fluide de pression en provenance de l'accumulateur (21) hydraulique, lorsque le distributeur (11) n'est pas actionné, au travers d'un clapet (40, 60) anti-retour ouvrant dans le sens de la chambre (24) de commande.
  8. Un dispositif de commande hydraulique conforme à la revendication n° 6 ou 7, caractérisé par une valve (60) de pilotage, qui dans une position médiane permet de fermer la chambre (24) de commande arrière de la valve (22) de fermeture contre l'évacuation du fluide de pression, qui peut être actionnée à partir de la position médiane pour prendre une première position de commutation latérale, dans laquelle la chambre (24) de commande arrière est déchargée vers le réservoir (27), et qui par un actionnement du distributeur (11) peut être amenée à quitter la position médiane pour prendre une seconde position de commutation latérale, dans laquelle la chambre (24) de commande arrière peut être sollicitée par la pression de l'accumulateur.
  9. Un dispositif de commande hydraulique conforme à la revendication n° 6 ou 7, caractérisé par une première valve (50) de pilotage avec une position de commutation, dans laquelle la chambre (24) de commande arrière de la valve (22) de fermeture peut être déchargée vers le réservoir (27), et avec une position de commutation, dans laquelle la chambre (24) de commande arrière peut être sollicitée par la pression de l'accumulateur (21), et par une seconde valve (40) de pilotage, qui est disposée dans le canal (53) de fluide de pression menant de la chambre (24) de commande arrière vers la première valve (50) de pilotage et qui présente une position de commutation, dans laquelle le canal (53) de fluide de pression est fermé contre toute évacuation de fluide de pression hors de la chambre (24) de commande arrière, et une position de commutation, dans laquelle le canal (53) de fluide de pression est ouvert.
  10. Un dispositif de commande hydraulique conforme à la revendication n° 9, caractérisé en ce que les deux valves (40, 50) de pilotage peuvent être actionnées par un solénoïde (43, 52) chacune.
EP98916979A 1997-03-21 1998-03-17 Systeme de commande hydraulique pour une machine de travail mobile, en particulier pour un chargeur sur roues Expired - Lifetime EP0968334B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19711769A DE19711769C2 (de) 1997-03-21 1997-03-21 Hydraulische Steueranordnung für eine mobile Arbeitsmaschine insbesondere für einen Radlader
DE19711769 1997-03-21
PCT/EP1998/001543 WO1998042923A1 (fr) 1997-03-21 1998-03-17 Systeme de commande hydraulique pour une machine de travail mobile, en particulier pour un chargeur sur roues

Publications (2)

Publication Number Publication Date
EP0968334A1 EP0968334A1 (fr) 2000-01-05
EP0968334B1 true EP0968334B1 (fr) 2002-06-12

Family

ID=7824098

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98916979A Expired - Lifetime EP0968334B1 (fr) 1997-03-21 1998-03-17 Systeme de commande hydraulique pour une machine de travail mobile, en particulier pour un chargeur sur roues

Country Status (6)

Country Link
US (1) US6260355B1 (fr)
EP (1) EP0968334B1 (fr)
JP (1) JP2001519009A (fr)
KR (1) KR100491841B1 (fr)
DE (2) DE19711769C2 (fr)
WO (1) WO1998042923A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102587444A (zh) * 2012-03-07 2012-07-18 浙江大学 一种具有能量差动回收的挖掘机油液混合动力系统
CN102995523A (zh) * 2012-09-07 2013-03-27 徐州万邦道路工程装备服务股份公司 一种摊铺机熨平板液压控制装置

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3796376B2 (ja) * 1999-02-22 2006-07-12 カヤバ工業株式会社 作業車両用制御装置
US6634653B2 (en) * 2001-07-17 2003-10-21 Probir Chatterjea & Associates, Inc. Ride control system for construction equipment
DE10148962C1 (de) * 2001-10-04 2003-02-27 Hydac Technology Gmbh Steuervorrichtung
US6612375B2 (en) * 2001-11-02 2003-09-02 Husco International, Inc. Apparatus for counteracting vehicle pitch variation resulting from the operation of an electronic draft control system
GB2418903B (en) * 2004-10-08 2008-06-25 Caterpillar Inc Ride control circuit for a work machine
US7661251B1 (en) * 2008-08-22 2010-02-16 Deere & Company Header float system for use with an agricultural windrower or combine
US7793740B2 (en) 2008-10-31 2010-09-14 Caterpillar Inc Ride control for motor graders
KR101021773B1 (ko) 2009-04-06 2011-03-15 울산대학교 산학협력단 직동형 유정압 구동기
CN102691700B (zh) * 2012-06-20 2014-12-03 山河智能装备股份有限公司 一种上车回转能量回收利用系统
CN103243751B (zh) * 2013-05-07 2015-09-02 山东理工大学 弹性橡胶带蓄能器式装载机动臂势能回收再生装置
CN103243752B (zh) * 2013-05-07 2015-09-02 山东理工大学 压簧蓄能器式装载机动臂势能回收再生装置
CN103243750B (zh) * 2013-05-07 2015-11-18 山东理工大学 复合蓄能器式装载机动臂势能回收再生装置
CN103243753A (zh) * 2013-05-07 2013-08-14 山东理工大学 弹性橡胶带蓄能式装载机动臂势能回收再生控制系统
CN103225321A (zh) * 2013-05-07 2013-07-31 山东理工大学 弹性橡胶带蓄能式装载机动臂势能回收再生控制方法
CN105421509B (zh) * 2015-11-16 2017-11-10 潍柴动力股份有限公司 一种混合动力挖掘机动臂势能回收装置及混合动力挖掘机
US10246854B2 (en) 2016-10-26 2019-04-02 Wacker Neuson Production Americas Llc Material handling machine with ride control system and method
CN108757593B (zh) * 2018-06-12 2020-11-10 北京理工大学 一种扭力轴齿根滚压强化机床液压供油系统
RU2719295C9 (ru) * 2019-06-18 2020-09-03 Федеральное государственное бюджетное образовательное учреждение высшего образования " Псковский государственный университет" Гидропривод землеройной машины непрерывного действия
JP7214610B2 (ja) * 2019-10-28 2023-01-30 株式会社クボタ 作業機の油圧システム
RU2768769C1 (ru) * 2021-03-26 2022-03-24 Федеральное государственное бюджетное образовательное учреждение высшего образования «Псковский государственный университет» Траншеекопатель
CN115750471B (zh) * 2022-11-29 2025-08-22 山东泰丰智能控制股份有限公司 一种压力平衡系统

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3717995A (en) * 1971-10-12 1973-02-27 Hesston Corp Hydraulic flotation for implement header
US3971215A (en) * 1974-06-06 1976-07-27 Marion Power Shovel Company, Inc. Power shovel and crowd system therefor
JPH0663264B2 (ja) 1984-07-20 1994-08-22 株式会社小松製作所 旋回式建設機械の旋回エネルギ回収再利用装置
JPS63106404A (ja) 1986-10-22 1988-05-11 Komatsu Ltd 慣性体駆動用油圧装置
JPS6466324A (en) * 1987-09-08 1989-03-13 Kobe Steel Ltd Vibration suppressor for vehicular construction machine
US5116188A (en) * 1987-09-16 1992-05-26 Kabushiki Kaisha Kobe Seiko Sho Vibration suppressing device for wheeled construction equipment
JP2688966B2 (ja) 1989-01-13 1997-12-10 油谷重工株式会社 車輪式建設機械の走行振動抑制安定回路
EP0381788B1 (fr) * 1989-02-06 1994-10-19 KABUSHIKI KAISHA KOBE SEIKO SHO also known as Kobe Steel Ltd. Dispositif pour supprimer les oscillations dans les engins de terrassement munis de roues
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
JP2602728B2 (ja) * 1990-03-31 1997-04-23 東洋運搬機株式会社 車両のダイナミックダンパー
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
US5195864A (en) * 1991-08-28 1993-03-23 Case Corporation Hydraulic system for a wheel loader
DE9208942U1 (de) * 1991-09-04 1993-01-14 O & K Orenstein & Koppel Ag, 1000 Berlin Hydraulikanlage für mit Arbeitsgeräten versehene Arbeitsmaschinen
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
SK368091A3 (en) * 1991-12-04 1994-05-11 Frantisek Krnavek Device for potential energy recuperation of working device of building or earth machine
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
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
JPH06286446A (ja) 1993-03-30 1994-10-11 Hitachi Constr Mach Co Ltd 車両系建設機械のサスペンション制御装置
DE4416228A1 (de) * 1994-05-07 1995-11-09 Rexroth Mannesmann Gmbh Hydraulische Anlage für ein mobiles Arbeitsgerät, insbesondere für einen Radlader
US5992146A (en) * 1996-04-12 1999-11-30 Caterpillar Inc. Variable rate ride control system
US6167701B1 (en) * 1998-07-06 2001-01-02 Caterpillar Inc. Variable rate ride control

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102587444A (zh) * 2012-03-07 2012-07-18 浙江大学 一种具有能量差动回收的挖掘机油液混合动力系统
CN102587444B (zh) * 2012-03-07 2014-07-30 浙江大学 一种具有能量差动回收的挖掘机油液混合动力系统
CN102995523A (zh) * 2012-09-07 2013-03-27 徐州万邦道路工程装备服务股份公司 一种摊铺机熨平板液压控制装置

Also Published As

Publication number Publication date
EP0968334A1 (fr) 2000-01-05
KR100491841B1 (ko) 2005-05-27
US6260355B1 (en) 2001-07-17
WO1998042923A1 (fr) 1998-10-01
DE19711769A1 (de) 1998-10-01
DE59804420D1 (de) 2002-07-18
DE19711769C2 (de) 1999-06-02
KR20010005508A (ko) 2001-01-15
JP2001519009A (ja) 2001-10-16

Similar Documents

Publication Publication Date Title
EP0968334B1 (fr) Systeme de commande hydraulique pour une machine de travail mobile, en particulier pour un chargeur sur roues
EP1003939B1 (fr) Dispositif de commande hydraulique destine a une machine de travail mobile, notamment a une chargeuse a roues
DE19754828C2 (de) Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Radlader, zur Dämpfung von Nickschwingungen
EP0615583B1 (fr) Recuperateur d'energie
EP1165895B1 (fr) Dispositif de commande hydraulique sensible a une charge pour une machine de travail
EP0759109B1 (fr) Systeme hydraulique pour engin de chantier mobile, notamment un chargeur a roues
DE10307346A1 (de) Ventilanordnung
EP0789816B1 (fr) Dispositif de recuperation d'energie
DE4342642C2 (de) Elektro-hydraulische Schnellfallschaltung
EP1687542B1 (fr) Dispositif de commande hydraulique d'un equipement mobile
EP1800012B1 (fr) Clapet anti-retour a soupape pilote
WO2006042499A2 (fr) Unite de coulee actionnee par voie hydraulique
DE19548943B4 (de) Ventilanordnung
EP0735275B1 (fr) Dispositif à crans
DE10104298A1 (de) Hydraulische Steueranordnung
EP2157319B1 (fr) Commande hydraulique pour un moteur hydraulique
EP0670230B1 (fr) Alimentation en fluide sous pression pour une suspension hydropneumatique et à régulation de niveau d'un véhicule utilitaire
DE19751357B4 (de) Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Radlader, zur Dämpfung von Nickschwingungen
DE102007007337A1 (de) Hydraulisches System zur Rückgewinnung von frei werdender Energie
DE29723825U1 (de) Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Radlader
WO2005052268A1 (fr) Dispositif de commande hydraulique
WO1999024720A1 (fr) Circuit hydraulique
DE19753503A1 (de) Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Radlader oder Gabelstapler, zur Dämpfung von Nickschwingungen
DE19850457A1 (de) Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Radlager
WO2005116457A1 (fr) Dispositif distributeur

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19990911

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 20010810

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 59804420

Country of ref document: DE

Date of ref document: 20020718

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20020912

ET Fr: translation filed
RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: BOSCH REXROTH AG

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20030313

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20110325

Year of fee payment: 14

Ref country code: FR

Payment date: 20110401

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20110324

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20110329

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20120502

Year of fee payment: 15

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120318

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20120317

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20121130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120317

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120402

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120317

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59804420

Country of ref document: DE

Effective date: 20131001

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131001