EP2344700A1 - Dispositif de compensation des pressions différentielles hydrauliques - Google Patents

Dispositif de compensation des pressions différentielles hydrauliques

Info

Publication number
EP2344700A1
EP2344700A1 EP09737365A EP09737365A EP2344700A1 EP 2344700 A1 EP2344700 A1 EP 2344700A1 EP 09737365 A EP09737365 A EP 09737365A EP 09737365 A EP09737365 A EP 09737365A EP 2344700 A1 EP2344700 A1 EP 2344700A1
Authority
EP
European Patent Office
Prior art keywords
pressure
hydraulic
valve
control
control valve
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
EP09737365A
Other languages
German (de)
English (en)
Other versions
EP2344700B1 (fr
Inventor
Rüdiger HONSBEIN
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.)
Hydac System GmbH
Original Assignee
Hydac System GmbH
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 Hydac System GmbH filed Critical Hydac System GmbH
Publication of EP2344700A1 publication Critical patent/EP2344700A1/fr
Application granted granted Critical
Publication of EP2344700B1 publication Critical patent/EP2344700B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/021—Installations or systems with accumulators used for damping
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8616—Control during or prevention of abnormal conditions the abnormal condition being noise or vibration

Definitions

  • the invention relates to a device for compensating hydraulic effective pressures in a hydraulic accumulator and a Hydroaktuator a hydraulic system.
  • hydraulic accumulator as hydraulically coupled to the actuator spring or damper element.
  • an unsprung, rigid operative connection between the actuator and the equipment operated by this is required, for example, if it is a hydraulically operated boom, which is to form a rigid support element, or a working device, the vibration-free controlled in use shall be.
  • the connection between the relevant actuator and the hydraulic accumulator must be blocked.
  • the differential pressure in the hydroactuator changes according to the working load to be provided by it. If now the system is transferred from the state of the locked suspension back into the state with a switched on hydraulic accumulator, a difference of the differential pressure between hydraulic accumulator and actuator leads to An uncontrolled movement on the actuator, which represents a threat to the system and a security risk for system operators.
  • the object of the invention is to provide a device which prevents such a security risk.
  • this object is achieved by a pressure compensation device, which has the features of claim 1 in its entirety.
  • the valve arrangement blocking the connection between the hydroactuator and the hydraulic accumulator has an additional control valve device which effects a pressure equalization when a predetermined difference of the effective pressures is exceeded. This avoids the risk of uncontrolled movement when transferring the system from the state of the locked suspension to the state with the suspension released, because the respective effective pressures of the hydraulic accumulator and of the hydroactuator are adapted to each other.
  • valve assembly comprises a directional valve, which establishes a direct fluid connection between the hydraulic actuator and hydraulic accumulator in its release state and interrupts this fluid connection in its blocking state, wherein the control valve device in dependence Transferring the directional control valve is activated in the blocking state and contains a drain valve that is controllable by a predetermined size exceeding difference of the effective pressures in its release state in which a pressure difference reducing drain path to the tank side of the hydraulic system is formed.
  • Hydroaktuator at least one lifting cylinder of a working machine, the lifting force generating piston side and the rod side are connected to a control block of the machine, wherein the piston side of the lift cylinder via the directional control valve with the hydraulic accumulator is connected and the control valve means a connection to the hydraulic accumulator and fluid paths to the piston side and the rod side of the lift cylinder, both of which fluid paths contain check valves that release the fluid path only to the higher effective pressure side leading the lift cylinder.
  • the arrangement can be made such that a discharge valve in the form of a pressure compensator is provided which, in the release state, leads the discharge path leading from the connection to the tank side the hydraulic accumulator ago and released from each shared, leading to the lifting cylinder fluid path forth.
  • the arrangement may be such that the discharge process from the reservoir to the tank side only occurs when the pressure difference is slightly greater than zero. It can be effective on the pressure compensator a the effect of the closing pressure amplifying bias.
  • the pressure compensator on a spool which is loaded for its displacement in the locking position on a piston surface both with the closing pressure from the hydraulic circuit and is loaded with the force of a biasing spring.
  • Fig. 1 is a schematically simplified side view drawn a mobile machine in the form of a wheel loader, provided with a
  • FIG. 2 shows a symbol representation of the circuit of the hydraulic system of the embodiment of the device according to the invention, shown in the operating state with released suspension.
  • FIG. 3 is a representation corresponding to FIG. 2, wherein the operating state is shown with an effective pressure in the hydraulic accumulator, which is smaller than the differential pressure on the piston side of the lifting cylinder;
  • Fig. 4 is a corresponding view, wherein the differential pressure in the memory is greater than on the piston side of the lifting cylinder;
  • 5 shows a corresponding representation in which the differential pressure on the rod side of the lifting cylinder is greater than on the piston side or in the hydraulic accumulator;
  • FIG. 6 shows a functional sketch of a pressure compensator serving as a discharge valve of the exemplary embodiment
  • Fig. 7 is a symbol view of the pressure compensator of Fig. 6 and Fig. 8 is a longitudinal section of a pressure compensator serving as a slide valve, which can be used in a valve block, not shown.
  • Fig. 1 shows a mobile machine in the form of a wheel bearing 1, with the blade 3, a lifting cylinder 5 is coupled.
  • FIGS. 2 to 5 show in a symbol representation the circuit of the hydraulic system in respectively different operating states.
  • Fig. 2 shows the
  • a main assembly of the hydraulic system forming valve assembly 1 1 has inputs 17 and 19, on which the piston side 7 and the rod side 15 of the lifting cylinder 5 are connected.
  • At outputs 21 and 23 of the valve assembly 11 of the hydraulic accumulator 9 and the tank 25 of the hydraulic system are connected.
  • the state of the released suspension is shown.
  • a directional control valve 27 is in its release state due to its mechanical preload 29, the piston side 7 being connected directly to the hydraulic accumulator 9 at the outlet 1 7 and the rod side 15 of the lifting cylinder 5 being connected directly to the tank 25 via the inlet 19 are connected at the output 23.
  • the other hydraulic components are not involved in the operation, ie that the system causes a conventional suspension / damping of the activity of the lifting cylinder 5.
  • suspension is unfavorable or harmful in certain work situations.
  • a blade 3 of a loader 1 When a blade 3 of a loader 1 is actuated, for example, a compression or rebounding with regard to the accuracy of the position adjustment of the blade 3 has an unfavorable effect.
  • the transfer of the system in the state of the locked suspension happens in such a way that by supplying a hydraulic control pressure via a control line 50, the directional control valve 27 is brought against the bias voltage 29 in the blocking state, which will be explained in more detail below.
  • Figs. 3 to 5 illustrate three different modes with each locked suspension.
  • 3 relates to the state in which, due to the operation, a higher effective pressure prevails on the piston side 7 of the lifting cylinder 5 than in the hydraulic accumulator 9.
  • the thicker line shows the fluid connection leading to higher pressure. namely from the input 17 of the valve assembly 1 1 to the blocked directional control valve 27 via a branch line 31 and branched off from the line branch 31 via a dicklinig dashed Sch thoroughly horr- control line 33 to a control terminal 35 of a drain valve 37.
  • This control terminal 35 is referred to here as a second control terminal.
  • a further control connection 47 of the discharge valve 37 which is designated here as the first control connection, is connected via a control valve 49, when it is in its opening state shown in FIG. 3, to the storage line 43 which, in turn, corresponds to one or the other fluid path. of, that is, depending on which of the check valves 41 or 45 is opened, with the input 17 or the input 19 is connected.
  • the control valve 49 In the previously-mentioned state of the released suspension in Fig. 2, the control valve 49 is in its closed state, which is caused by the fact that its actuating magnet 51 is energized, so that the valve 49 is closed against its opening spring 52.
  • the first control connection 47 of the discharge valve 37 and the control line 50 of the directional valve 27 are depressurized by connection to the tank side 25.
  • the bias voltage 29 therefore keeps the directional valve 27 in its open state. If the energization of the actuating magnet 51 is interrupted and the control valve 49 is opened, then the control valve 50, the directional control valve 27 against its bias 29 hydraulically controlled in the locked state and the system goes into the state of the locked suspension, as shown in Fig. 3 to 5 is shown.
  • FIG. 4 shows a state in which, also with locked suspension, the differential pressure in the hydraulic accumulator 9 is higher than that due to operational conditions on the piston side 7 of the lifting cylinder 5 and thus over the piston Input 17 in the valve assembly 11 effective system pressure.
  • the storage line 43 is shown in the upper part with a thick solid line in the figure and with a thick dashed line in its lower half. According to the prevailing in the hydraulic accumulator 9 higher effective pressure than in the lifting cylinder 5, the check valve 41 is closed.
  • the higher effective pressure of the hydraulic accumulator 9 is thus applied to the first control connection 47 of the discharge valve 37 via the non-energized control valve 49 which is opened by the spring tension 52, while the second control connection 35 leads via the line branch 31 to the lower differential pressure of the input 17.
  • the discharge valve 37 has a pressure compensator, which is shown in FIG. 7 in symbol representation and in FIG. 6 in the form of a functional diagram.
  • Fig. 8 shows a longitudinal section of a practical embodiment. As can be seen, it is a slide valve with slide piston 65 axially displaceable in the valve housing 63, shown in the closed position, which is effected by a hydraulic closing pressure acting on the second control connection 35, reinforced by a mechanical biasing force, which is shown in FIGS 7 is designated 67.
  • the discharge valve 37 opens by an opening hydraulic pressure acting on the first control port 47, provided that the opening pressure at the spool 65 causes a higher opening force than the closing pressure prevailing at the control port 35, amplified by the biasing force 67.
  • condition is in that the discharge valve 37 opens to form a discharge path from the inlet port 53 to the outlet port 55 and thus to the tank 25, that for the forces acting on the spool 65, the closing force resulting from the pressure at the second control port 35 plus the mechanical preload 67 results, is less than the opening force, generated by the hydraulic pressure at the first control terminal 47th So:
  • FIG. 8 shows an exemplary embodiment in which two fferenfe- 69 and 71 engage on a two-part spool 65 for generating the biasing force 67, which bias the piston 65 in the figure to the right in the illustrated closed position in which the input port 53rd , which is located at the right in the Fig. Right axial end of the valve body 53, is locked relative to the output terminal 55.
  • the hydraulic pressure of the second control port 35 acts on the left side of the piston 65 in FIG ,
  • Fig. 5 refers to a further state in which at the input 19 of the valve assembly 1 1, the higher effective pressure prevails, compared with the pressure at the input 17 or the pressure in the hydraulic accumulator 9.
  • Such an operating condition results when operating a work machine with the suspension locked, equipment runs onto an obstacle. This may for example be the case when a mobile device, such as a wheel loader 1, runs with its blade 3 on an elevation forming an obstacle, whereby the standing on the blade 3 weight of the wheel loader 1, the piston of the respective lifting cylinder 5 in the rod side 15th shifts, creating an overpressure on the rod side 15.
  • this overpressure is effective, as well as via the open control valve 49 at the first control connection 47 of the discharge valve 37, so that upon fulfillment of the opening condition, i. a higher pressure at the port 53 opposite the control port 35, which is connected via the line branch 31 to the input 17, the discharge valve 37 opens, which in turn the discharge path to the tank 25 is opened, whereby the pressure relief of the storage line 43 takes place.
  • the higher pressure in the control port 47 ensures that the valve 37 is not in the locked position.
  • the actual pressure compensator is formed by the coil spring 69 and by the effective pressure surfaces of the axially displaceable spool 65.
  • the locking piston is designed as a spool is in turn formed by the coil spring 71 and the effective piston surface 81 of said locking piston part ,
  • the piston designated by 65 in FIG. 6 can be made of several parts, as shown in FIG.
  • the multi-part design prevents, when at the port 55, a higher pressure than the pressure of the is formed by the biasing forces of the coil springs 69 and 71 plus the effective pressure force by the pressure at the second control port 35, it comes to an opening of the valve seat 55 and insofar to an unwanted backflow of the fluid into the system. If one would like to dispense with the pertinent check valve function, the indicated slide piston arrangement can also be in one piece (not shown).
  • the construction of the drain valve 37 is not mandatory. Any valve construction whose function corresponds to the above-mentioned opening and closing conditions can be used.
  • the construction of the two-part slide piston 65 shown in FIG. 8 is also not mandatory, in which the piston part located on the right in this figure forms a check valve at the inlet connection 53, which is loaded by the spring with a low closing force designated by 69.
  • the closing spring denoted by 71 forms the main part of the in Fig. 6 and 7 designated at 67 bias, which increases the closing force of the valve.

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)
  • Vehicle Body Suspensions (AREA)

Abstract

L'invention concerne un dispositif de compensation des pressions hydrauliques exercées dans un accumulateur hydraulique (9) et un actionneur hydraulique (5) d'un système hydraulique (11, 13), avec un agencement de vannes (27) destiné à interrompre une liaison entre l'actionneur hydraulique (5) et l'accumulateur hydraulique (9) et avec un équipement de vannes de commande (11) qui réalise une compensation de pressions en cas de dépassement d'une différence prédéterminée des pressions exercées.
EP09737365A 2008-11-07 2009-10-16 Dispositif de compensation des pressions différentielles hydrauliques Not-in-force EP2344700B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008057723A DE102008057723A1 (de) 2008-11-07 2008-11-07 Vorrichtung zum Ausgleich hydraulischer Wirkdrücke
PCT/EP2009/007422 WO2010051907A1 (fr) 2008-11-07 2009-10-16 Dispositif de compensation des pressions différentielles hydrauliques

Publications (2)

Publication Number Publication Date
EP2344700A1 true EP2344700A1 (fr) 2011-07-20
EP2344700B1 EP2344700B1 (fr) 2012-11-14

Family

ID=41509078

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09737365A Not-in-force EP2344700B1 (fr) 2008-11-07 2009-10-16 Dispositif de compensation des pressions différentielles hydrauliques

Country Status (6)

Country Link
US (1) US9016054B2 (fr)
EP (1) EP2344700B1 (fr)
KR (1) KR101650692B1 (fr)
CN (1) CN102209814B (fr)
DE (1) DE102008057723A1 (fr)
WO (1) WO2010051907A1 (fr)

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DE102010062694A1 (de) * 2010-12-09 2012-06-14 Robert Bosch Gmbh Hydraulische Bremsanlage und Verfahren zum Druckabgleich in einer hydraulischen Bremsanlage
DE102014000695A1 (de) * 2014-01-14 2015-07-16 Hydac System Gmbh Vorrichtung zum Sperren und zum Druckanpassen
DE102014000696A1 (de) 2014-01-14 2015-07-16 Hydac System Gmbh Vorrichtung zum Sperren und zum Druckanpassen
US9869359B2 (en) 2014-08-29 2018-01-16 Caterpillar Inc. Hydraulic system with an unloading valve
JP6084264B1 (ja) * 2015-09-28 2017-02-22 Ｋｙｂ株式会社 スプール弁装置
US10151080B2 (en) 2015-11-30 2018-12-11 The Charles Machine Works, Inc. Valve assembly for work attachment
JP6549543B2 (ja) * 2016-09-29 2019-07-24 日立建機株式会社 作業機械の油圧駆動装置
CN106930988A (zh) * 2017-03-24 2017-07-07 南京航空航天大学 基于蓄能器的动静态双向液压加载装置及其控制方法
US10988915B2 (en) 2017-04-10 2021-04-27 Doosan Infracore Co., Ltd. Hydraulic system of construction machinery
CN108482049B (zh) * 2018-03-01 2021-05-28 燕山大学 一种应急救援车辆用馈能型主动悬挂液压控制系统

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Also Published As

Publication number Publication date
CN102209814A (zh) 2011-10-05
EP2344700B1 (fr) 2012-11-14
WO2010051907A1 (fr) 2010-05-14
KR101650692B1 (ko) 2016-08-24
DE102008057723A1 (de) 2010-05-12
US9016054B2 (en) 2015-04-28
CN102209814B (zh) 2014-08-27
KR20110097795A (ko) 2011-08-31
US20110197573A1 (en) 2011-08-18

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