EP0656100A1 - Dispositif de commande hydraulique. - Google Patents

Dispositif de commande hydraulique.

Info

Publication number
EP0656100A1
EP0656100A1 EP93917748A EP93917748A EP0656100A1 EP 0656100 A1 EP0656100 A1 EP 0656100A1 EP 93917748 A EP93917748 A EP 93917748A EP 93917748 A EP93917748 A EP 93917748A EP 0656100 A1 EP0656100 A1 EP 0656100A1
Authority
EP
European Patent Office
Prior art keywords
control
valve
control device
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.)
Granted
Application number
EP93917748A
Other languages
German (de)
English (en)
Other versions
EP0656100B1 (fr
Inventor
Wolfgang Kauss
Armin Stellwagen
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 EP0656100A1 publication Critical patent/EP0656100A1/fr
Application granted granted Critical
Publication of EP0656100B1 publication Critical patent/EP0656100B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/0422—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with manually-operated pilot valves, e.g. joysticks
    • 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
    • E02F9/2278—Hydraulic circuits
    • E02F9/2285—Pilot-operated systems

Definitions

  • the invention relates to a hydraulic control device with a directional control valve with which the direction of movement and the speed of a hydraulic consumer, in particular a mobile working device, can be influenced.
  • a hydraulic control device which also has the other features from the preamble of claim 1, is known from practical use on excavators.
  • Control spool of the directional control valve then in a steeply increasing area of the characteristic curve of the directional control valve and thus in the area of high amplification, so that the tendency to oscillate is still promoted.
  • the invention is based on the object of further developing a hydraulic control device with the features from the preamble of claim 1 such that the tendency of the overall system to vibrate can be further reduced without unacceptable delays in the movement sequence of a working tool occurring.
  • Control device solved which has the features from the preamble of claim 1 and in which, according to the characterizing part of claim 1, the damping of the movement of the control spool of the directional control valve can be controlled as a function of the control pressure in a second control chamber.
  • a hydraulic control device according to the invention the two apparently opposite demands for good damping of vibrations and for a delay-free start and end of the work process can be met at the same time.
  • the movement of the control spool is damped primarily only when the pilot control device is in the range of high control pressures and thus a steep increase in the stroke / volume flow characteristic of the directional valve.
  • an area of the characteristic curve is also traversed in which the control pressure and the slope of the characteristic curve are small, and which is generally referred to as the fine control area.
  • the damping is greatly reduced or, as is provided in the advantageous embodiment according to claim 2, completely switched off. The movement start and movement end of a workflow are therefore not delayed.
  • a hydraulic control device can also be advantageously configured by the features from the further subclaims.
  • the characteristic curve of known directional valves has a gently rising area and a steeply rising area, the transition between the two areas being approximately one third of the maximum control pressure.
  • the movement of the control spool can be damped from a control pressure which is approximately one third of the maximum control pressure. As long as the control pressure is below a third of the maximum control pressure, the movement is not dampened.
  • a second directional control valve is expediently used, depending on the position of which the damping can be changed. It is conceivable to use a continuous valve as a directional valve, the degree of damping depending on the position of a valve body of the directional valve.
  • the directional control valve can, however, also be a switching valve, the movement of the control slide not being damped in one switching position and damped by a throttle with a fixed throttle cross-section in the other switching position.
  • the throttle can be inexpensive and, from the design side, not very expensive if, according to claim 5, a fixed throttle that cannot be influenced by the position of the second directional control valve is provided and one from the second directional control valve this fixed throttle bypass is switchable, which is open in the rest position of the second directional valve, so that no throttling of the volume flow occurs, and which is more or less far, in particular completely blocked, in a working position of the second directional valve.
  • the throttle can then be arranged on a valve body of the check valve and can be moved therewith, wherein a cleaning effect for the throttle is also achieved.
  • this solution appears to be cheaper than another one in which, when the second directional valve is in the rest position, the pilot control unit and the first control chamber are connected to one another without throttling via the directional valve and in a working position of the second directional valve a throttle point is connected to the first control line.
  • a throttle point is connected to the first control line.
  • such an execution offers the possibility of integrating the throttle point in the directional control valve and, for example, forming it by means of a groove on a control piston of the directional control valve, so that installation space can be saved. At the same time it is achieved that the throttle is moved with the control piston and a certain cleaning effect also occurs.
  • Free inflow and throttled outflow of control oil is achieved in a simple manner according to claim 8 in that a non-return valve opening towards the first control chamber is connected in parallel with the second directional control valve and that the directional control valve is in a blocking position for the first control depending on the control pressure ⁇ line is switchable.
  • the second directional control valve is preferably designed such that a valve body tries to assume a rest position under the action of at least one valve spring and can be actuated hydraulically against the force of a valve spring.
  • a first control chamber can be acted upon with the control pressure prevailing in one control line and a second spring-side control chamber with the tank pressure prevailing in the other control line.
  • An embodiment according to claim 10 permits the use of only a single valve spring, which is also easy to arrange and adjust. Actuation of the second directional control valve appears easier, however, when its valve body tries to assume a middle rest position under the action of at least one valve spring and the first control chamber is connected to one control line and the second control chamber to the other control line.
  • control lines it is then not necessary, depending on the pressurization of the control lines, to switch between them so that the first control chamber is connected to the control line in which a control pressure is present. Rather, the two control chambers can be fixed with the one or to the other control line, since when the pilot control is actuated in a certain direction there is control pressure in one control line and tank pressure in the other control line, and this is reversed when the pilot control is actuated from the middle position in the opposite direction .
  • both control lines are provided with a valve arrangement for throttling the control oil outflow.
  • the throttling can be controlled with relatively little effort by means of a single directional valve with four working connections. If two way valves are used, they can be set to different switching pressures.
  • the damping of the movement of the control slide is impaired if the control oil in the control lines and in the control spaces contains air bubbles.
  • the air contained can be reduced in that a flushing nozzle is connected between the two control lines, through which control oil can flow from the control line to which control pressure is applied to the control line in which the tank pressure prevails.
  • the flushing nozzle is integrated in the second directional valve. It appears particularly favorable if, according to claim 17, the connection of the two control lines via the flushing nozzle is closed in an actuated position of the second directional valve, in which a high control pressure prevails in one control line. The flushing nozzle can therefore not impair the build-up of the control pressure.
  • valve arrangement and the second directional valve are preferably accommodated in a common housing, an advantageous arrangement being specified in claim 20.
  • FIG. 1 shows a hydraulic control device with a single, two-way valve assigned to two control lines, with a control chamber which can be connected alternately to one or the other control line,
  • FIG. 2 shows a second directional valve, which in turn is provided for both control lines and has three switching positions and is accommodated in a single housing with two valve arrangements for throttling the control oil outflow,
  • FIG. 3 shows a further embodiment of a second directional valve, in which two throttles are integrated, which can be switched into the control lines,
  • FIG. 4 shows an embodiment with two second directional valves, one of which is assigned to a control line
  • FIG. 5 shows a partial section through a valve, to which a second directional valve and two throttle check valves belong in a common housing and whose switching symbol is that according to FIG. 2,
  • Figure 6 is a partial section along the line VI-VI of Figure 5 and
  • FIGS. 5 and 6 show the overlap of the control piston of the directional control valve from FIGS. 5 and 6.
  • FIG. 1 shows a wheel excavator 10 in which the various parts of the boom 11 which are movable relative to one another can be moved via double-acting hydraulic cylinders 12.
  • a hydraulic cylinder 12 can be actuated via a first directional valve 13 with a control slide 9, from which two consumer lines 14 to the hydraulic cylinder Linder 12 lead, and which is a continuous valve known per se, which has a spring-centered central position from which it can be brought hydraulically into its lateral working position. It is controlled with the aid of a manually operated pilot control device 15, from which a control line 16 leads to a control room 17 and a control line 18 to a control room 19 of the directional control valve 13.
  • a throttle check valve with a throttle 20 and a check valve 21 is installed in each of the two control lines and opens to the respective control chamber 17 or 19.
  • the pilot control device 15 works on the basis of directly controlled pressure reducing valves. Depending on the deflection of the actuating element 22, a certain control pressure can be built up in one of the two control lines 16 or 18. The other control line is connected to the tank. It is now assumed that the actuating lever 22 is deflected in such a way that a control pressure is built up in the control line 16. Control oil then flows through the corresponding check valve 21 into the control chamber 17, while control oil is displaced from the control chamber 19, which, because the other check valve closes, flows back via the corresponding throttle 20 and the control line 18 to the pilot control device 15. The outflowing tax oil is therefore throttled. When the actuating lever 22 is deflected in the opposite direction, pressure is present in the control line 18 and control oil flows into the control chamber 19. Control oil is throttled out of the control chamber 17.
  • the two throttles 20 should only be effective when the control pressure exceeds a certain pressure.
  • This pressure essentially depends on the stroke / volume flow characteristic of the directional control valve 13 and lies in the range in which this characteristic changes from a flat to a steep section. This pressure is normally about a third of the highest control pressure. If the latter is 30 bar, the throttles 20 should only be effective when the control pressure rises above 10 bar.
  • a second directional control valve 25 is provided, which has two inputs 40, 42 and two outputs 41, 43, one input on one side and the corresponding output on the other side of a throttle 20 each with one of the two control lines 16 or 18 is connected.
  • the directional control valve 25 has a rest position and a working position, the rest position being assumed due to the action of a compression spring 26 and the working position being obtained by hydraulic actuation by pressurizing a control chamber 27.
  • the control chamber 27 can be connected to the control line, in which a control pressure is present, via a shuttle valve 28.
  • the chamber in which the compression spring 26 is located is connected via a control line to an inverted shuttle valve 29 and is connected by this to the control line in which the tank pressure prevails.
  • the compression spring 26 is set so that the directional control valve 25 is then switched from its rest position to its working position when a control pressure of 10 bar prevails in the control chamber 27.
  • the two control lines 16 and 18 are connected between the throttle 20 and the pilot control unit 15 via a flushing nozzle 30, via which a certain amount of control oil is supplied by the control pressure during each actuation of the pilot control unit 15 Control line to the other control line and from there flows into the tank.
  • a dash-dotted line indicates that the two throttle check valves, the second directional valve 25, the shuttle valve 28, the inverted shuttle valve 29, the flushing nozzle 30 and the hydraulic connections between these components are housed in a single housing block 31.
  • control oil is displaced from the pressurized control room. Because of the check valve 21 which blocks the pilot control device 15, this control oil is also throttled when the second directional valve 25 is in its working position.
  • a throttle 20 and a check valve 21 are located in each control line 16 or 18.
  • the throttling of the oil flow in both control lines can be influenced by the second directional valve 25.
  • one or the other control line is the first or the second and the one and the other control chamber 17, 19 is the first or the second.
  • a second directional control valve 25 which has a central position centered by two oppositely acting pressure springs 26 that are biased to 10 bar, in each of which a bypass is connected to the two throttle check valves 20, 21, and two lateral working positions points in which all working ports 40 to 43 of the directional control valve 25 are blocked.
  • the directional control valve 25 now has two control chambers 32 and 33, one of which is connected to the control line 16 and the other to the control line 18.
  • the flushing nozzle 30 is integrated in the directional control valve 25. Because the directional valve 25 now has two lateral working positions and from the central If the position can be actuated in opposite directions, the change-over valve and the inverted change-over valve can be omitted compared to the embodiment according to FIG. Since there is control pressure in one control line 16 and 18 and in the other tank pressure, the corresponding pressures in the control chambers 32 and 33 also result when these chambers are connected directly to the control lines.
  • the directional control valve 25 according to FIG. 3 is actuated in exactly the same way as that according to FIG. 2 and, just like that, has three switching positions, namely a spring-centered central position and two lateral working positions. However, the connections are not blocked in the working positions. Rather, in a working position of the directional control valve 25 according to FIG. 3, one control line 16 or 18 remains open and a throttle 20 integrated in the directional control valve is connected to the other control line. A check valve as in the explanations in FIGS. 1 and 2 is not present. After the control spool of the first directional control valve overshoots, oil flowing back from the first control chamber is not throttled.
  • the embodiment according to FIG. 4 largely corresponds to that according to FIG. 1.
  • one directional control valve 25 with four working connections is divided into two directional control valves 35, each of which has only two working connections.
  • This division also means that a directional valve 35, which is assigned to one control line 16 or 18, can be connected directly to this control line with the spring-side control chamber 36 and directly to the other control line with the control chamber 27 .
  • the connection of the control chamber 36 to the corresponding control line only has the function of discharging leakage oil. Possibly. control pressure prevailing in the control chamber 36 has no effect.
  • a housing block 44 can be seen in FIGS. 5 and 6, which is indicated in FIG. 2 with a dash-dotted line.
  • This housing block 44 has two parallel through bores 45 and 46, in which between a aisle 40 or 42 and an outlet 41 or 43 a throttle check valve 20, 21 is installed.
  • the directional control valve 25 has a control piston 47 which is displaceable in a central section 48 of a further through bore 49 of the housing block 44, which runs parallel to a plane 50 spanned by the two bores 45 and 46 and perpendicular to the bores 45 and 46. From opposite directions, two sealing plugs 60 are screwed into the bore 49 and receive a helical compression spring 26 in a blind hole 61.
  • Each of the two helical compression springs is supported on the bottom of the blind hole 61 and on a disk 62 which rests on a step 63 of the bore 49, provided that the control piston 47 is in the central position.
  • the distance between the two stages 63 is only slightly greater than the length of the control piston 47, so that when the control piston 47 is displaced out of its central position via the corresponding disc 62 which extends radially inwards over the control piston 47, this is one of the two compression springs 26 is further tensioned.
  • the other compression spring is supported on the other disk 62 on the housing block 44 and remains ineffective during a displacement of the control piston 47 in one direction.
  • Both compression springs 26 are preloaded such that a control pressure of approximately 10 bar is necessary in order to displace the control piston 47.
  • the spring constant of the compression springs 26 is selected to be very small, so that the pressure range within which the control piston 47 is displaced from the central position into a lateral working position is very small.
  • control piston 47 In order to move the control piston 47, a control pressure must be built up in one of the two control chambers 32 and 33, in which the compression springs 26 are also located.
  • the control chamber 33 is connected to the input 42 via a transverse bore 64.
  • a blind bore 66 From the end face 65 facing the control chamber 33 of the control piston 47 a blind bore 66 extends in the axial direction of the control piston 47, into which a transverse bore 67 opens into the control piston 47 at a distance from the end face 65.
  • the control piston 47 In the area of the transverse bore, the control piston 47 has a circumferential annular groove 68 which is on one side from an end Ring collar 69 and on the other side is bounded by a central ring collar 70.
  • a channel 71 extends from the central section 48 of the bore 49, towards which the annular groove 68 is open in the central position of the control piston 47 shown in the upper half of FIG. In the one lateral working position of the control piston 47, on the other hand, which is shown in the lower half of FIG. 7, the annular collar 69 hides the channel 71.
  • the channel 71 is closed by a blind-hole-like opening running parallel to the bore 49 and closed by a plug 72. connected to the outlet 43 of the housing block 44 towards another channel and through a further transverse bore 73 parallel to the transverse bore 64.
  • the central annular collar of the control piston 47 has a further annular groove 80 at a distance from the two annular grooves 68, the depth of which, however, is far less than the depth of an annular groove 68.
  • the web 81 remaining between the two ring grooves 80 has a narrow longitudinal cut 82, via which the two channels 71 and 73 and thus the inputs and the outputs of the housing block 44 are connected to one another in the central position of the control piston 47.
  • the longitudinal incision 82 thus represents the flushing nozzle 30. In a lateral working position of the control piston 47, the connection mentioned is interrupted.
  • a dashed line in each end collar 69 indicates a groove 83 which is open axially towards the end face 65. Through such a groove a throttle 20 can be replaced under certain circumstances.
  • one of the channels 71 is connected to the corresponding control chamber, which in turn is connected to the pilot control device 15.

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)
  • Servomotors (AREA)
  • Multiple-Way Valves (AREA)

Abstract

L'invention concerne un dispositif de commande hydraulique comprenant un distributeur (13) grâce auquel il est possible d'influer sur le sens de mouvement et la vitesse d'un consommateur hydraulique (12), en particulier d'un engin de chantier. Un dispositif de commande hydraulique connu comprend en outre un appareil hydraulique de commande pilote (15) au moyen duquel une pression de commande peut être appliquée à un premier espace de commande (17) par le biais d'une conduite de pilotage (16) et à un second espace de commande (19) du distributeur (13) par le biais d'une seconde conduite de pilotage (18), ainsi qu'un ensemble de soupapes (20, 21) dans une première conduite de pilotage (16) par laquelle un afflux très libre d'huile hydraulique est admis jusqu'à un premier espace de commande (17) et par laquelle le mouvement du tiroir du distributeur (13) peut être amorti par une limitation de l'écoulement de l'huile hydraulique. Afin d'obtenir un amortissement efficace, tout en évitant de différer le début ou la fin du mouvement de l'outil d'un engin de chantier mobile (10), l'invention prévoit que l'amortissement du mouvement du tiroir (9) du distributeur puisse être régulée en fonction de la pression de commande dans un premier espace de commande (17) et/ou en fonction de la pression de commande dans un second espace de commande (19).
EP93917748A 1992-08-20 1993-08-05 Dispositif de commande hydraulique Expired - Lifetime EP0656100B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE4227564 1992-08-20
DE4227564 1992-08-20
DE4231399A DE4231399A1 (de) 1992-08-20 1992-09-19 Hydraulische Steuereinrichtung
DE4231399 1992-09-19
PCT/EP1993/002082 WO1994004829A1 (fr) 1992-08-20 1993-08-05 Dispositif de commande hydraulique

Publications (2)

Publication Number Publication Date
EP0656100A1 true EP0656100A1 (fr) 1995-06-07
EP0656100B1 EP0656100B1 (fr) 1997-05-28

Family

ID=25917693

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93917748A Expired - Lifetime EP0656100B1 (fr) 1992-08-20 1993-08-05 Dispositif de commande hydraulique

Country Status (5)

Country Link
US (1) US5640892A (fr)
EP (1) EP0656100B1 (fr)
JP (1) JPH08500418A (fr)
DE (1) DE4231399A1 (fr)
WO (1) WO1994004829A1 (fr)

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DE29713296U1 (de) 1997-07-25 1997-10-16 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Schieberventil für die Hochdruckhydraulik
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US6581909B2 (en) 1999-11-01 2003-06-24 Clore Automotive, Llc Simplified hydraulic circuit for a quick-rise hydraulic lifting jack
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DE10355329A1 (de) * 2003-11-27 2005-06-23 Bosch Rexroth Ag Hydraulische Steueranordnung
JP4100425B2 (ja) * 2005-11-22 2008-06-11 コベルコ建機株式会社 作業機械の制御装置
DE102007014550A1 (de) * 2007-03-27 2008-10-09 Hydac Filtertechnik Gmbh Ventilanordnung
WO2008135039A2 (fr) * 2007-05-08 2008-11-13 UNIVERSITÄT KARLSRUHE (TH) FORSCHUNGSUNIVERSITÄT-GEGRüNDET 1825 Procédé et dispositif pour chariots élévateurs
CN104454689A (zh) * 2014-11-20 2015-03-25 刘涛 压力调节系统及其应用的工程机械
JP6554444B2 (ja) * 2016-06-09 2019-07-31 日立建機株式会社 作業機械
US11592072B2 (en) * 2020-06-05 2023-02-28 The Boeing Company Dynamic load damping apparatus

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Also Published As

Publication number Publication date
DE4231399A1 (de) 1994-02-24
WO1994004829A1 (fr) 1994-03-03
US5640892A (en) 1997-06-24
EP0656100B1 (fr) 1997-05-28
JPH08500418A (ja) 1996-01-16

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