EP0503266A1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP0503266A1
EP0503266A1 EP92101815A EP92101815A EP0503266A1 EP 0503266 A1 EP0503266 A1 EP 0503266A1 EP 92101815 A EP92101815 A EP 92101815A EP 92101815 A EP92101815 A EP 92101815A EP 0503266 A1 EP0503266 A1 EP 0503266A1
Authority
EP
European Patent Office
Prior art keywords
pressure
check valve
control
valve
control device
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
EP92101815A
Other languages
German (de)
English (en)
Other versions
EP0503266B1 (fr
Inventor
Martin Dipl.-Ing. Heusser (Eth)
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
Publication of EP0503266A1 publication Critical patent/EP0503266A1/fr
Application granted granted Critical
Publication of EP0503266B1 publication Critical patent/EP0503266B1/fr
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
    • 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
    • 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
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/40—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
    • 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 hydraulic control device according to the preamble of patent claim 1.
  • the damping throttle in the control pressure line is set such that it brings the amplitudes of the pressure fluctuations to decay when the pressure medium is warm and the load holding valve is open. So that the control movement of the load holding valve is not delayed and the hydraulic motor does not run under the load, the damping throttle can be bypassed by a check valve, which ensures rapid pressure reduction when the control is activated. Pressure fluctuations in the control pressure line and the resulting load movements are gradually dampened by the damping throttle, but some are now clearly noticeable because the load-holding valve plays and the hydraulic motor reacts unevenly.
  • the invention has for its object to provide a hydraulic control device of the type mentioned, in which the pressure fluctuations are quickly decay independent of the viscosity and regardless of the setting of the damping throttle.
  • the strongly preloaded check valve opens when the pressure rises during at least the first amplitude as soon as the preload force is overcome.
  • the tip of the amplitude is eliminated to the minimum of the pressure value of the pressure fluctuation, which could not be dampened by the damping throttle.
  • the first and the other amplitudes are quickly decayed on the control side. This is particularly advantageous in the case of cold pressure medium and / or tightly adjusted damping throttle, because the check valves do more than just the damping effect support the damping throttle, but compensate for the undesired effect of the damping throttle under certain operating conditions.
  • the amplitudes of the pressure fluctuations, which become effective on the control side of the load holding valve, are damped as quickly as possible so that the load holding valve immediately permits a uniform movement of the hydraulic motor under the load, practically from the beginning of the movement.
  • the rapid damping of the pressure fluctuations on the control side of the load holding valve has a dampening effect on pressure fluctuations in the entire system.
  • the pressure not passing through the damping throttle opens the strongly biased check valve towards the control side of the load holding valve as soon as it has overcome the biasing force.
  • the upper part of the crest of the at least first amplitude of the pressure fluctuations is no longer effective on the control side of the load holding valve.
  • the other amplitudes are made easier to decay.
  • the second, very slightly pre-stressed check valve also allows a rapid reduction in pressure.
  • the two check valves cooperate with the damping throttle when damping; they take over the parts of the pressure fluctuations with which the damping throttle cannot cope.
  • the strongly biased first check valve responds not only at the first amplitude, but at several initial amplitudes of the pressure fluctuations in order to bring the pressure fluctuations effective on the control side to decay as quickly as possible together with the damping throttle. This is particularly useful with cold and therefore viscous pressure medium because the damping throttle then works unsatisfactorily because of its viscosity dependency.
  • the first amplitude or the first amplitudes of the pressure fluctuations reach the control side of the load holding valve via the only slightly preloaded first check valve bypassing the damping throttle, so that its control movement takes place immediately.
  • the lower region of the first amplitude or the first amplitudes is reduced via the second check valve, which is biased in the opposite direction, which favors the rapid decay of the amplitudes.
  • the second check valve is only biased so that it responds when the pressure drop is controlled to control the load holding valve and bypasses the damping throttle in order to avoid delaying the control movement even when the pressure medium is cold and viscous.
  • the embodiment according to claim 6 is structurally simple, because spring-loaded check valves are simple, reliable and inexpensive hydraulic links. With the adjusting device, the pretensioning force can be precisely adapted to the operating conditions with regard to optimal damping.
  • the embodiment according to claim 7 is also expedient in order to also be able to adapt the damping throttle to the operating conditions.
  • the two check valves cooperating with the damping throttle have the additional advantage that the damping throttle can be adjusted largely independently of the course and extent of the pressure fluctuations and with regard to optimal damping.
  • the bypass line should be connected according to claim 9 to the working line containing the load holding valve or according to claim 10 directly to the tank.
  • a directional control valve with inlet regulators and a blocked middle position can be used, which is critical in such oscillation-prone or strongly oscillating systems because of its long settling behavior.
  • the strong damping effect that can be achieved with the aforementioned measures anyway allows the use of directional control valves equipped with inlet regulators, which benefits the control accuracy and the response of the control device when the hydraulic motor moves in any direction.
  • a hydraulic control device S according to FIG. 1 serves to control the movement of a consumer V with which a load F is moved.
  • the consumer V is, for example, the lifting or folding cylinder of a crane with which the load F is moved.
  • a piston 1 divides a cylinder into two chambers 2 and 3.
  • Each chamber 2 and 3 can be connected alternately to a pressure source B and a tank T via a working line 4, 5 and a directional control valve C.
  • a load holding valve H At least in the working line 4 there is a load holding valve H, which contains a valve 6 with a valve member 7, which is brought by a spring 8 into the illustrated control position blocking the line 4.
  • the pressure prevailing in a pilot line 10 acts
  • the pressure prevailing in a pilot line 9 acts in the opening direction.
  • a line loop 11 bypasses the valve 6 in the working line 4 and contains a check valve 12 opening in the direction of the hydraulic motor V.
  • a control pressure line 13 branches off from the other working line 5 to the control side 16 of the valve 6.
  • A, preferably adjustable, damping throttle D is contained in the control pressure line 13.
  • Two line loops 14 and 15 bypass the damping throttle D.
  • the line loop 14 contains a first check valve R1 with a valve member 17 and a biasing spring 18, which opens in the direction of the control side 16. With an indicated adjusting device E, the biasing force of the Adjust spring 18.
  • a second check valve R2 is contained in the line loop 15, which opens in the direction of the second working line 5 and contains a valve member 19 and possibly a weak biasing spring 20.
  • Both check valves R1, R2 are biased differently.
  • the preload of the second check valve R2 can go to zero.
  • a weak spring is used to position the valve member 20 in the shut-off position in the idle state.
  • the preload of the first check valve R1 is large.
  • the force with which the valve member 17 is biased by the spring 18 has a value which is less than the pressure value of the pressure maximum effective at the valve member 17 of at least the first amplitude (FIG. 4) of the pressure fluctuations in the pressure P1 and slightly greater than that Pressure value of the pressure maximum of the next following amplitudes.
  • the load holding valve H is opened, for example via the directional control valve C, by applying pressure to the working line 5 until the load holding valve H opens the passage of the working line 4.
  • the pressure P1 follows, for example, the solid curve.
  • the pressure fluctuations would have successive and very slowly decreasing amplitudes, each with a pressure maximum and a pressure minimum.
  • Pressure fluctuations constantly act on the control side 16 of the load holding valve, then the movement of the hydraulic motor V would not be uniform.
  • the pressure fluctuations must therefore be brought to an end as quickly as possible, at least on the control side 16 (pressure P2 in FIG. 1, dashed curve in FIG. 4).
  • the damping throttle D and the first check valve R1 Due to the action of the damping throttle D and the first check valve R1, the pressure increase of the first amplitude on the control side 16 becomes effective with a phase shift. If the biasing force of the first check valve is reached, it opens so that the tip of the first amplitude is cut off before the pressure P2 approximately follows the pressure drop on the rear flank of the first amplitude. The damping throttle D is bypassed. At the beginning of the next amplitude, the damping throttle D acts, so that the pressure increase on the control side 16 is already flatter and the second amplitude is damped.
  • the damping choke causes the other amplitudes to decay rapidly on the control side. In this way it is achieved that the lowering movement of the hydraulic motor V takes place smoothly and immediately after the movement has been started, at the speed that is set on the directional control valve.
  • FIG. 2 differs from that of FIG. 1 by exchanging the pretension of both check valves with which the damping throttle D can be bypassed.
  • the first check valve R1 ' which opens in the direction of the control side 16, is pretensioned with a pretensioning force which goes towards zero, ie very small, while the second check valve R2', which opens in the opposite direction, is pretensioned with a large pretensioning force.
  • FIG. 5 there is a damping effect on the control side 16.
  • the first amplitude of the pressure fluctuations of the pressure P1 is followed by the first amplitude of the pressure fluctuation of the pressure P2 on the control side with the phase shift caused by the damping throttle D.
  • the maximum of the pressure value of the first amplitude of the pressure P1 is not reached by the pressure P2 because of the damping throttle D, but the pressure P2 follows the falling edge of the first amplitude of the pressure P1.
  • the biasing force of the second check valve R2 has a value (dashed horizontal line in Fig. 5) which is higher than the minimum of the pressure value of the first amplitude of the pressure P1, but lower than the minimum of the pressure values of the subsequent amplitudes of the pressure P1.
  • the second non-return valve R2 therefore opens when the pre-tensioning force falls below the value before the first amplitude reaches its minimum pressure value.
  • the preload on the second check valve R2 ' is expediently set such that the second check valve R2' opens when the pressure in the control pressure line is released in order to control the load holding valve. A delay in the control movement via the damping throttle is thus avoided.
  • FIG. 3 differs from the two previously described embodiments by an additional damping device in the control circuit of the load holding valve.
  • This damping device consists of a bypass duct 23 branching off at a branch 22 from the control pressure line 13, which leads either to a connection point 24 in the working line 4 or (indicated by dashed lines at 25) directly to the tank.
  • a throttle passage D1 is provided between the working line 5 and the branch 22.
  • the bypass line 23 contains an interference throttle passage D2, which is slightly larger than the throttle passage D1.
  • the damping device contributes to damping the vibration amplitudes by the fact that a pressure medium constantly flows through the two throttle passages and disrupts the propagation of the vibration amplitudes, so that they subside very quickly.
  • the Damping device ensures that pressure fluctuations are damped even when the hydraulic motor V is moved in the load lifting direction and also when the load is stopped.
  • the two check valves R1 and R2 are arranged and biased as in the embodiment according to FIG. 1. However, it is also conceivable to use the reverse arrangement and pretension according to FIG. 2 in the embodiment according to FIG. 3. The effect is similar in both cases.
  • the damping throttle D can also be tightly adjusted with regard to optimal damping. Nevertheless, with cold and therefore viscous pressure medium it is avoided that the closing and opening movements of the load holding valve are delayed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Jib Cranes (AREA)
  • Fluid-Damping Devices (AREA)
EP92101815A 1991-03-11 1992-02-04 Dispositif de commande hydraulique Expired - Lifetime EP0503266B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4107776 1991-03-11
DE4107776A DE4107776A1 (de) 1991-03-11 1991-03-11 Hydraulische steuervorrichtung

Publications (2)

Publication Number Publication Date
EP0503266A1 true EP0503266A1 (fr) 1992-09-16
EP0503266B1 EP0503266B1 (fr) 1995-10-11

Family

ID=6426989

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92101815A Expired - Lifetime EP0503266B1 (fr) 1991-03-11 1992-02-04 Dispositif de commande hydraulique

Country Status (8)

Country Link
US (1) US5263400A (fr)
EP (1) EP0503266B1 (fr)
JP (1) JP3276166B2 (fr)
AT (1) ATE129050T1 (fr)
DE (2) DE4107776A1 (fr)
DK (1) DK0503266T3 (fr)
ES (1) ES2080350T3 (fr)
GR (1) GR3017881T3 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0695877A1 (fr) 1994-08-03 1996-02-07 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif d'amortissement hydraulique
EP0695878A1 (fr) 1994-08-03 1996-02-07 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif de commande hydraulique
FR2734607A1 (fr) * 1995-05-24 1996-11-29 Eha Engineerie Hydromecanique Dispositif hydraulique differentiel pour alimentation et verrouillage de verins de commande a double effet
EP0803630A2 (fr) * 1996-04-24 1997-10-29 HOERBIGER GmbH Dispositif de commande hydraulique
AT408899B (de) * 1999-12-07 2002-03-25 Hoerbiger Hydraulik Dämpfungsanordnung für fluidsysteme
CN102887447A (zh) * 2012-10-17 2013-01-23 中联重科股份有限公司 变幅液压缸液压控制回路、起重机及变幅控制方法
CN104609321A (zh) * 2015-02-16 2015-05-13 徐州重型机械有限公司 一种起重机臂架变幅液压控制系统、变幅装置和起重机
FR3083578A1 (fr) * 2018-07-09 2020-01-10 Safran Landing Systems Circuit hydraulique d'alimentation d'un verin, notamment utilise pour manœuvrer une porte de soute d'aeronef
DE102020212201A1 (de) 2020-09-28 2022-03-31 Hawe Hydraulik Se Separates hydraulisches Dämpfungsmodul und Lasthalteventil mit separatem hydraulischen Dämpfungsmodul

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0877863A1 (fr) * 1996-01-30 1998-11-18 Mannesmann Rexroth AG Dispositif hydraulique de commande de la circulation d'un fluide hydraulique
KR100305742B1 (ko) * 1996-05-25 2001-11-30 토니헬샴 중장비의재생장치
JP3446023B2 (ja) * 1997-03-24 2003-09-16 大淀小松株式会社 油圧装置
DE69928159T2 (de) 1998-04-10 2006-07-20 Canon K.K. Zweikomponenten-Entwickler und Bilderzeugungsverfahren
DE19922866C2 (de) * 1999-05-19 2002-11-14 Sauer Danfoss Holding As Nordb Hydraulische Leitungskupplung
US6557453B2 (en) * 2000-03-30 2003-05-06 Timberjack Inc. Hydraulic boom control
DE10336684A1 (de) * 2003-08-09 2005-03-03 Deere & Company, Moline Hydraulische Steueranordnung für eine mobile Arbeitsmaschine
KR100753988B1 (ko) * 2006-06-09 2007-08-31 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 건설중장비용 엑슬 록킹 실린더 구조
ITPR20090100A1 (it) * 2009-11-30 2011-06-01 Walvoil Spa Dispositivo di controllo del segnale di pressione di pilotaggio

Citations (2)

* Cited by examiner, † Cited by third party
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DE2927646A1 (de) * 1978-07-12 1980-01-31 Teijin Seiki Co Ltd Hydraulische schaltung mit einem wechselventil
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DE3237103A1 (de) * 1982-10-07 1984-04-12 Wessel-Hydraulik Günther Wessel, 2940 Wilhelmshaven Sicherheitsventil als lasthalteventil in der hebezeughydraulik

Cited By (15)

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Publication number Priority date Publication date Assignee Title
EP0695877A1 (fr) 1994-08-03 1996-02-07 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif d'amortissement hydraulique
EP0695878A1 (fr) 1994-08-03 1996-02-07 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif de commande hydraulique
FR2734607A1 (fr) * 1995-05-24 1996-11-29 Eha Engineerie Hydromecanique Dispositif hydraulique differentiel pour alimentation et verrouillage de verins de commande a double effet
EP0803630A2 (fr) * 1996-04-24 1997-10-29 HOERBIGER GmbH Dispositif de commande hydraulique
EP0803630A3 (fr) * 1996-04-24 1998-12-09 HOERBIGER GmbH Dispositif de commande hydraulique
AT408899B (de) * 1999-12-07 2002-03-25 Hoerbiger Hydraulik Dämpfungsanordnung für fluidsysteme
DE10060175B4 (de) * 1999-12-07 2006-09-14 Hoerbiger Hydraulik Gmbh Dämpfungsanordnung für Fluidsysteme sowie fluidisches System und Fluidpumpe mit einer Dämpfungsanordnung
CN102887447A (zh) * 2012-10-17 2013-01-23 中联重科股份有限公司 变幅液压缸液压控制回路、起重机及变幅控制方法
CN102887447B (zh) * 2012-10-17 2014-09-17 中联重科股份有限公司 变幅液压缸液压控制回路、起重机及变幅控制方法
CN104609321A (zh) * 2015-02-16 2015-05-13 徐州重型机械有限公司 一种起重机臂架变幅液压控制系统、变幅装置和起重机
FR3083578A1 (fr) * 2018-07-09 2020-01-10 Safran Landing Systems Circuit hydraulique d'alimentation d'un verin, notamment utilise pour manœuvrer une porte de soute d'aeronef
EP3594508A1 (fr) * 2018-07-09 2020-01-15 Safran Landing Systems Circuit hydraulique d'alimentation d'un verin, notamment utilise pour manoeuvrer une porte de soute d'aeronef
US10907660B2 (en) 2018-07-09 2021-02-02 Safran Landing Systems Hydraulic circuit for feeding an actuator, in particular for use in moving a door of an aircraft bay
DE102020212201A1 (de) 2020-09-28 2022-03-31 Hawe Hydraulik Se Separates hydraulisches Dämpfungsmodul und Lasthalteventil mit separatem hydraulischen Dämpfungsmodul
DE102020212201B4 (de) 2020-09-28 2022-12-01 Hawe Hydraulik Se Separates hydraulisches Dämpfungsmodul und Lasthalteventil mit separatem hydraulischen Dämpfungsmodul

Also Published As

Publication number Publication date
US5263400A (en) 1993-11-23
GR3017881T3 (en) 1996-01-31
JPH0565904A (ja) 1993-03-19
JP3276166B2 (ja) 2002-04-22
DE59203935D1 (de) 1995-11-16
EP0503266B1 (fr) 1995-10-11
DE4107776A1 (de) 1992-09-17
DE4107776C2 (fr) 1992-12-24
ATE129050T1 (de) 1995-10-15
DK0503266T3 (da) 1996-01-22
ES2080350T3 (es) 1996-02-01

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