EP0464305B1 - Hydraulische Steuervorrichtung - Google Patents

Hydraulische Steuervorrichtung Download PDF

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Publication number
EP0464305B1
EP0464305B1 EP91101694A EP91101694A EP0464305B1 EP 0464305 B1 EP0464305 B1 EP 0464305B1 EP 91101694 A EP91101694 A EP 91101694A EP 91101694 A EP91101694 A EP 91101694A EP 0464305 B1 EP0464305 B1 EP 0464305B1
Authority
EP
European Patent Office
Prior art keywords
line
drive
control device
valve
pressure
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
EP91101694A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0464305A1 (de
Inventor
Rudolf Ing. Brunner
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.)
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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 Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Priority to JP12579191A priority Critical patent/JP2788134B2/ja
Publication of EP0464305A1 publication Critical patent/EP0464305A1/de
Application granted granted Critical
Publication of EP0464305B1 publication Critical patent/EP0464305B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/18—Control systems or devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/62—Constructional features or details
    • B66C23/82—Luffing gear
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and the return line
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check valve
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
    • 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
    • F15B2211/8613—Control during or prevention of abnormal conditions the abnormal condition being oscillations

Definitions

  • the invention relates to a hydraulic control device of the type specified in the preamble of claim 1.
  • a crane is a vibrating load movement system in which oscillating movements occur at the beginning or end of a load movement, also due to large lever ratios, which affect the hydraulic consumer (s) and lead to pressure fluctuations in the hydraulic system.
  • the hydraulic columns of the theoretically incompressible medium show elastic reactions in practice, so that the oscillating movements and the pressure fluctuations are disruptively maintained over a long period of time from the interaction of various factors, ie also during the load movement.
  • a generic control device (EP-A-0 172 524) has no hydraulic damping device for pressure fluctuations in the control pressure line of the load holding valve.
  • the control pressure or pressure fluctuations in the system have an undamped effect on the load holding valve.
  • a bypass line to the tank branches off from a control pressure line leading to one side of a control piston of a drain control valve, in which a throttle passage is arranged.
  • a rheostat is arranged in the control pressure line, which generates constant pressure for the control piston with the throttle passage.
  • the other side of the control piston is subjected to variable pressure from the working line containing the control valve.
  • the invention has for its object to provide a hydraulic control device of the type mentioned, in which an effective damping of pressure fluctuations is achieved easily and inexpensively.
  • the damping is presumably due to the fact that the disturbance flowing out of the pilot pressure line cuts the upper and lower crests in the pressure curve in the event of pressure fluctuations, and that an oscillating pressure curve in the working lines and in the hydraulic consumer is disturbed so that pressure fluctuations quickly subside.
  • the amount of disturbance flowing out for steaming is small.
  • the block containing the load holding valve remains conventional. It is modified for the additional function with little manufacturing effort. Simply by replacing the block, a hydraulic control device that was already in operation can be retrofitted.
  • the embodiment according to claim 3 corresponds to the modern modular principle for optionally combinable components.
  • the unit can be easily integrated in the control circuit at a suitable point. In a previously undamped system, damping is subsequently achieved by attaching the structural unit. If necessary, the unit is integrated into the working group, in which case the bypass line and the choke passage are dimensioned larger.
  • a bore is used as a throttle passage with a diameter of 0.8mm and a bore with a diameter of 1.0mm used as a choke passage.
  • the size ratio and the sizes of the passages are individually adapted to the respective requirements.
  • bypass channel in the cylinder containing the control piston of the load holding valve or in the control piston itself and to connect it to the cylinder part on the rear of the control piston, which is possibly relieved of pressure anyway.
  • a motion damping throttle is additionally present in the control circuit.
  • the motion damping throttle is set so close to warm pressure medium or for other reasons that it could delay the rapid actuation of the load holding valve when the pressure medium is cold or when the consumer stops quickly. It would then come to run after the hydro consumer is under.
  • the non-return valve in the parallel line eliminates this danger, because when the load holding valve is activated, pressure fluid passes the motion damping throttle if the pressure difference at the motion damping throttle becomes too large. In the event of pressure fluctuations while the load is being lowered, the motion damping damper interacts with the damping device.
  • the damping device and the movement damping throttle cooperate in an optimal manner.
  • control movement of the control piston is not affected by the check valve according to claim 7, because the pressure medium flows out via the bypass channel.
  • bypass channel through the bypass channel and the interference throttle passage pressure medium flows into the working line containing the load holding valve. There is no connection between the bypass duct and the return.
  • the check valve in the bypass channel ensures that when the other working line is pressurized, no pressure medium reaches a working line via the bypass channel.
  • the pressure medium flowing out for steaming glows directly into the return line or tank.
  • the pressure accumulator according to claim 10 helps to let the pressure fluctuations subside quickly.
  • a further expedient embodiment emerges from claim 11.
  • a geometric area ratio of 1: 3 between the valve seat and the control piston is usually used worldwide in the load holding valve.
  • this area ratio which is implemented as standard, however, the pressure difference resulting from the pressure medium flowing through the bypass channel is compensated for and the advantage is achieved that a larger quantity of pressure medium moves around the pressure line for effective damping and also for control from the working line providing the control pressure Move the control piston with the same force as before.
  • Claim 12 gives the person skilled in the art an easy-to-understand instruction, such as an optimal damping of the pressure fluctuations with constant regulation or control behavior of the hydraulic Control device can be achieved.
  • both working lines of the hydraulic consumer are secured with a load holding valve. Effective damping of pressure fluctuations is achieved regardless of the direction of movement of the load. Linking the bypass channels is a structural simplification.
  • a vibrating load movement system S according to Fig. 1 is, for example, a hydraulic crane 3 mounted on a truck 1 on its vehicle frame 2, the boom components of which are supplied by hydraulic consumers V, e.g. double-acting hydraulic cylinders, are moved when a load F is to be manipulated. Forces occur at the beginning or at the end of or even during the movement of the load F, which cause the boom components to vibrate, primarily because of the large leverage ratios, which leads to noticeable pressure fluctuations in the hydraulic consumers V, which results in dangerous or unpleasant load movements.
  • hydraulic consumers V e.g. double-acting hydraulic cylinders
  • a hydraulic control device L can be seen in the block diagram from FIG. 2, with which the left-hand hydraulic consumer V shown in FIG. 1 is actuated, for example.
  • the hydraulic control device L contains a load holding valve H with a control part A and a damping device X as well as a schematically indicated control valve C, and is derived from a pressure source P to which a return tank T is assigned. supplied with pressure medium.
  • the hydraulic consumer V is a double-acting differential cylinder 4 with a piston 5, to which the load F acts via a piston rod 8.
  • the chambers 6 and 7 of the cylinder 4 are connected to the control valve C via working lines 9, 10 and can be connected alternately to the pressure source P or the return flow T in order to move the piston 5 in both directions.
  • the control valve has a zero position to stop the load.
  • the load holding valve H is arranged in the other working line 9 and, in order to lower the load F from the one working line 10, is acted upon by pilot pressure which is set by the control valve C.
  • the load holding valve H contains a valve 11 with a closing element 13 which is loaded in the control direction by a spring 12 and by a control pressure in a control line 15b branching off from the control valve C of the part of the other working line 9.
  • a check valve 14 blocking the flow direction to the control valve C bypasses the valve 11.
  • the valve element 13 is acted upon by the control pressure of an indicated control line 15a against the force of the spring 12, which branches off from the part of the other working line 9 facing the hydraulic consumer V.
  • the control part A has a control pressure line 16 which branches off from a branch 17 of the one working line 10 and leads to a connection 18 of the valve 11.
  • a component 19 can be contained in the control pressure line 16 to dampen the movements of the closing element 13 or the control piston assigned to it (see FIG. 5)
  • a bypass line 23 branches off in a branch 22 of the pilot pressure line 16 and contains an interference throttle D2.
  • the bypass line 23 leads to a node 24 in the part of the other working line 9 facing the control valve C.
  • a throttle passage D1 is provided which is smaller than the interference throttle passage D2 (for example throttle passage D1 0.8mm, choke passage D2 1.0mm).
  • a check valve 25 blocking in the direction of the interference throttle passage D2 can be provided between the interference throttle passage D2 and the node 24.
  • valve 11 holds the load.
  • the check valve 14 blocks.
  • the part of the working line 9 located between the load holding valve H and the control valve C is relieved to the return flow T.
  • control valve C is adjusted so that the working line 9 is connected to the pressure source P and the working line 10 to the return T.
  • the closing element 13 remains in its closed position.
  • the check valve 14 opens.
  • the chamber 7 is pressurized.
  • the piston 5 extends. Pressure medium is discharged from the chamber 6 through the working line 10.
  • the chamber 6 and the opening pressure line 16 are pressurized, which opens the closing element 13 against the force of the spring 12.
  • the load F begins to decrease.
  • Pressure medium constantly flows through the bypass channel 23 to the other working line 9, which is connected to the return line T. If there are pressure fluctuations in the chambers 6 and 7, the working lines 9, 10 and in the control circuit of the load holding valve H, these are damped because of the pressure medium flowing out via the bypass duct 23 and the interference throttle passage D2 and because of the movement damping throttle 20.
  • the work line 10 is relieved.
  • the check valve 14 is in its blocking position.
  • the closing element 13 is closed, the movement damping throttle 20 damping this movement.
  • Pressure medium flows to a working line 10 and / or through the bypass duct 23 via the check valve 25.
  • the hydraulic control device H according to FIG. 3 differs from that of FIG. 2 in that the bypass channel 23 is connected directly to the return T. Furthermore, a check valve 26 which blocks in the direction of a working line 10 is provided in the pilot pressure line 16. The check valve 26 can also be arranged at the same location in the embodiment according to FIG. 2. The function of the control device is the same as that of FIG. 2. Only no pressure medium can flow back into the one working line 10.
  • a pressure accumulator 27 is connected to the pilot pressure line 16, expediently between the component 19 and the branch 22.
  • the check valve 26 from FIG. 3 could be provided at the same location. It is also indicated that the bypass duct 23 either leads directly to the return T or, as in FIG. 2, to the other working line 9.
  • Fig. 5 the hydraulic consumer V (e.g. the articulated cylinder in Fig. 1) is secured in both working directions by load holding valves H.
  • the bypass channels 23 of both damping devices X are connected to the other pilot pressure line 16.
  • the valve 11 of the load holding valve is shown schematically in FIG. 6.
  • the closing element 13 designed as a ball 29 is pressed by the spring 12 onto a valve seat 30 which connects two chambers 31 and 32 to one another.
  • the part of the other working line 9 leading to the chamber 7 is connected to the chamber 31; to the chamber 32, on the other hand, the part of the working line 9 leading to the control valve C.
  • the check valve 14 is located between the chambers 31 and 32.
  • a control piston 34 can be acted upon by the pressure in the control line 16 in order to open the closing element 13 via a tappet 33.
  • the chamber part 35 located behind the control piston 34 is relieved of pressure.
  • the valve seat 30 has a cross-sectional area A1, which is in a geometrical area ratio to the application area A2 of the control piston 34, is greater than 1: 4 and preferably greater than 1: 6.5.
  • the pressure in the chamber 32 acts on the closing element 13 parallel to the spring 12 in the closing direction.
  • the pressure in the chamber 31 acts on the closing element 13 parallel to Control piston 34 in the control direction.
  • bypass channel 23 could also run through the control piston 34 to the chamber 35 and contain the interference throttle passage D2. It would also be conceivable to lead the bypass channel 23 out on the loading side of the control piston 34.
  • Fig. 7 in a diagram, the vertical axis represents pressure and the horizontal axis represents time.
  • the curve P17 represents the pressure curve at the branch 17.
  • the lower curve P18 represents the pressure curve at the connection 18. Both pressures oscillate strongly at the beginning and then calm down until they finally remain constant.
  • a pressure difference dP prevails between the pressures P17 and P18 due to the pressure medium flowing out via the bypass channel 23 and the interference throttle passage D2. This pressure difference is compensated for by the size of the pressure surface of the control piston 34 (FIG. 5), so that the load holding valve H operates in the usual way.
  • the throttle passage D1 has a diameter of 0.8 mm
  • the interference throttle passage D2 has a diameter of 1.0 mm
  • the control piston 34 has a diameter of 17 mm.
  • the pressure at branch 17 is approximately 90 bar; the pressure P 18 at the connection P18, on the other hand, is approximately 40 bar.
  • a pressure difference of approximately 40 bar is reduced via the bypass duct 23 and the interference throttle passage D2.
  • a parallel line 36 is provided, which extends from the pilot pressure line 16 between the components 19 and branches off the valve 11 and opens into the pilot pressure line 16 between the throttle passage D1 and the branch 17. It bypasses the movement damping throttle 20 and contains a check valve 37 which opens in the direction of a working line 10.
  • the parallel line 36 can also be connected directly to the one working line 10.
  • the check valve 37 allows 11 pressure medium to flow past the throttle 20 when the pressure medium is cold or when the damping throttle 20 is set strictly.
  • the check valve 37 contributes to the damping because it passes pressure peaks.
  • the bypass channel 23 can be connected to the other working line 9 or directly to the tank T. In the event of pressure fluctuations in the system, the pressure prevailing at the throttle passage D1 keeps the check valve 37 closed, so that the movement damping throttle 20 is properly effective.
  • the damping device X with or without check valve 37 is particularly useful for control devices in oscillatable load movement systems, in which relatively complex control valves are provided with inlet regulators and load pressure sensing, which on the one hand are unaffected by pressure changes on the pump side and work independently of the load, but on the other hand the tendency itself to create or maintain pressure fluctuations in the system. With the design according to the invention, the pressure fluctuations in the system are effectively and quickly dampened regardless of where they originate.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
EP91101694A 1990-07-05 1991-02-07 Hydraulische Steuervorrichtung Expired - Lifetime EP0464305B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP12579191A JP2788134B2 (ja) 1990-07-05 1991-05-29 液圧式制御装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4021347 1990-07-05
DE4021347A DE4021347A1 (de) 1990-07-05 1990-07-05 Hydraulische steuervorrichtung

Publications (2)

Publication Number Publication Date
EP0464305A1 EP0464305A1 (de) 1992-01-08
EP0464305B1 true EP0464305B1 (de) 1994-09-07

Family

ID=6409672

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91101694A Expired - Lifetime EP0464305B1 (de) 1990-07-05 1991-02-07 Hydraulische Steuervorrichtung

Country Status (6)

Country Link
US (1) US5191826A (enrdf_load_stackoverflow)
EP (1) EP0464305B1 (enrdf_load_stackoverflow)
AT (1) ATE111052T1 (enrdf_load_stackoverflow)
DE (2) DE4021347A1 (enrdf_load_stackoverflow)
DK (1) DK0464305T3 (enrdf_load_stackoverflow)
ES (1) ES2063386T3 (enrdf_load_stackoverflow)

Families Citing this family (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4231399A1 (de) * 1992-08-20 1994-02-24 Rexroth Mannesmann Gmbh Hydraulische Steuereinrichtung
JP3382981B2 (ja) * 1992-11-12 2003-03-04 帝人製機株式会社 舵面の制御装置
DE4243973C1 (de) * 1992-12-23 1994-07-07 Heilmeier & Weinlein Hydraulische Steuervorrichtung
DE4416194A1 (de) * 1994-05-06 1995-11-09 Rexroth Mannesmann Gmbh Regelsystem für einen hydraulisch betätigten Verbraucher eines Nutzfahrzeugs
DE4416228A1 (de) * 1994-05-07 1995-11-09 Rexroth Mannesmann Gmbh Hydraulische Anlage für ein mobiles Arbeitsgerät, insbesondere für einen Radlader
DE9412530U1 (de) 1994-08-03 1994-11-10 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulische Dämpfungsvorrichtung
US5499503A (en) * 1994-09-22 1996-03-19 Iowa Mold Tooling Company, Inc. Hydraulic swing circuit
DE19528981C1 (de) * 1995-08-07 1996-10-02 Heilmeier & Weinlein Verfahren zum Steuern eines Hydroverbrauchers und hydraulische Steuervorrichtung zur Durchführung des Verfahrens
WO1997013072A2 (de) * 1995-09-29 1997-04-10 Beringer Hydraulik Ag Dämpfung von druckschwingungen in hydraulikanlagen
EP0883753B1 (de) * 1996-02-28 2002-04-17 Bucher Hydraulics AG Lasthalte-bremsventil
US6338247B1 (en) * 1998-11-20 2002-01-15 Sauer-Danfoss Inc. System for controlling a hydraulic vehicle drive
DE19925204B4 (de) * 1999-06-01 2008-04-10 Bosch Rexroth Aktiengesellschaft Entsperrbares Lasthalteventil
US6382148B1 (en) * 1999-06-10 2002-05-07 Unisia Jecs Corporation Oil pressure control apparatus for an internal combustion engine
DE10047632B4 (de) * 2000-09-26 2014-01-02 Linde Hydraulics Gmbh & Co. Kg Ventileinrichtung für einen doppelt wirkenden hydraulischen Verbraucher
DE10221276B4 (de) * 2002-05-14 2005-05-19 Eaton Fluid Power Gmbh Hydrauliksystem mit druckabhängiger Dämpfung
HRPK20041139B3 (en) * 2002-05-24 2006-02-28 Metso Lindemann Gmbh Hydraulic control in a hydraulic system, especially for the operation of scrap cutters
NL1023583C2 (nl) * 2003-06-02 2004-12-03 Actuant Corp Hydraulische bedieningsinrichting.
DE10336684A1 (de) * 2003-08-09 2005-03-03 Deere & Company, Moline Hydraulische Steueranordnung für eine mobile Arbeitsmaschine
SE531754C2 (sv) * 2007-05-11 2009-07-28 Nordhydraulic Ab Hydraulisk lastkontrollventilanordning
CN101786577B (zh) * 2009-01-23 2013-05-15 柳州欧维姆机械股份有限公司 双机负重行走式液压数控跨缆吊机及控制系统及控制方法
DE102009058371A1 (de) * 2009-12-15 2011-06-16 Hydac Filtertechnik Gmbh Ventilanordnung zur Ansteuerung eines Verbrauchers
EP2341253B8 (en) * 2010-01-05 2013-10-16 Nem S.R.L. Device for piloting by means of a substantially incompressible fluid
EP2696080B1 (de) * 2012-08-09 2016-12-14 HAWE Hydraulik SE Elektrohydrauliksteuerung
GB2514112C (en) * 2013-05-13 2016-11-30 Caterpillar Inc Valve Arrangement
CN105593438B (zh) 2013-05-31 2019-07-05 伊顿智能动力有限公司 用于通过平衡保护来降低动臂跳动的液压系统及方法
CN103321975B (zh) * 2013-06-05 2016-08-10 天津航天瑞莱科技有限公司 一种低-高压软启动液压油源系统
US10036407B2 (en) 2013-08-30 2018-07-31 Eaton Intelligent Power Limited Control method and system for using a pair of independent hydraulic metering valves to reduce boom oscillations
US10316929B2 (en) 2013-11-14 2019-06-11 Eaton Intelligent Power Limited Control strategy for reducing boom oscillation
EP3069030B1 (en) 2013-11-14 2020-12-30 Eaton Intelligent Power Limited Pilot control mechanism for boom bounce reduction
CN106661894B (zh) * 2014-07-15 2019-12-10 伊顿公司 实现悬臂弹跳减少以及防止液压系统中的非指令运动的方法和设备
CN111542703B (zh) 2017-04-28 2022-12-06 丹佛斯动力系统Ii技术有限公司 具有用于抑制机器中的质量感应振动的运动传感器的系统
CN111542702B (zh) 2017-04-28 2022-09-23 丹佛斯动力系统Ii技术有限公司 用于抑制具有液压控制的吊杆或细长构件的机器中的质量感应振动的系统
IT201700062799A1 (it) * 2017-06-08 2018-12-08 Vbr S R L Dispositivo di controllo di un cilindro idraulico
FR3083578B1 (fr) * 2018-07-09 2021-01-22 Safran Landing Systems Circuit hydraulique d'alimentation d'un verin, notamment utilise pour manœuvrer une porte de soute d'aeronef

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1256383B (de) * 1960-02-05 1967-12-14 Acme Alfred Dehle K G Hydraulisches Geraet zum Betaetigen von Be- und Entlueftungseinrichtungen
DE2036547C3 (de) * 1970-07-23 1973-10-31 Fried. Krupp Gmbh, 4300 Essen Brems und Sperreinrichtung fur em hydrostatisches Triebwerk
DE2314590A1 (de) * 1973-03-23 1974-09-26 Parker Hannifin Corp Ventilanordnung
US3792715A (en) * 1973-03-26 1974-02-19 Koehring Co Single seat holding valve
FR2268177A1 (en) * 1974-04-22 1975-11-14 Bennes Marrel Hydraulic lorry hoist ram control system - has circuit by-passing variable quantity from pump outlet back to tank
DE2526154A1 (de) * 1975-06-12 1976-12-16 Wessel Hydraulik Vorrichtung zum antrieb hydraulischer motoren und zylinder
DD129984B1 (de) * 1977-04-12 1981-02-25 Goetz Kamm Bremsventil hoher regelguete
DE2911891C2 (de) * 1979-03-26 1983-10-13 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zum Steuern eines Hydromotors
IT1207907B (it) * 1979-07-11 1989-06-01 Oil Control Spa Valvola perfezionata a sbloccaggiooleodinamico bilanciata in particolare per consentire comandi in serie ad elevata pressione a piu azionatori idraulici
JPS5614604A (en) * 1979-07-18 1981-02-12 Hitachi Constr Mach Co Ltd Hydraulic circuit
EP0063025A1 (en) * 1981-04-06 1982-10-20 Ruston-Bucyrus Limited Hydraulic control circuit for an hydraulic ram
DE3201546C2 (de) * 1982-01-20 1986-03-27 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zum Steuern eines Hydromotors
DE3237103C3 (de) * 1982-10-07 1997-01-23 Wessel Hydraulik Sicherheitsventil als Lasthalteventil in der Hebezeughydraulik
GB2163126B (en) * 1984-08-18 1987-07-22 Bamford Excavators Ltd A boom and method of operating it
DE3733740A1 (de) * 1987-10-06 1989-04-20 Danfoss As Daempfungsanordnung zur schwingungsdaempfung von mit druckfluessigkeit gesteuerten ventilen
JPH0662269B2 (ja) * 1989-04-21 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
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

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ES2063386T3 (es) 1995-01-01
US5191826A (en) 1993-03-09
DK0464305T3 (da) 1994-11-07
ATE111052T1 (de) 1994-09-15
DE4021347A1 (de) 1992-01-16
DE4021347C2 (enrdf_load_stackoverflow) 1993-07-08
EP0464305A1 (de) 1992-01-08
DE59102813D1 (de) 1994-10-13

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