EP1598560A1 - Dispositif de soupape hydraulique - Google Patents

Dispositif de soupape hydraulique Download PDF

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Publication number
EP1598560A1
EP1598560A1 EP05009870A EP05009870A EP1598560A1 EP 1598560 A1 EP1598560 A1 EP 1598560A1 EP 05009870 A EP05009870 A EP 05009870A EP 05009870 A EP05009870 A EP 05009870A EP 1598560 A1 EP1598560 A1 EP 1598560A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
control
control valve
working
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
EP05009870A
Other languages
German (de)
English (en)
Other versions
EP1598560B1 (fr
Inventor
Knud Meldgaard Jensen
Carl Christian Dixen
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.)
Danfoss Power Solutions ApS
Original Assignee
Sauer Danfoss ApS
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 Sauer Danfoss ApS filed Critical Sauer Danfoss ApS
Publication of EP1598560A1 publication Critical patent/EP1598560A1/fr
Application granted granted Critical
Publication of EP1598560B1 publication Critical patent/EP1598560B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and 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
    • 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
    • F15B2211/3144—Directional 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
    • F15B2211/50—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
    • F15B2211/50—Pressure control
    • F15B2211/565—Control of a downstream 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves

Definitions

  • the invention relates to a hydraulic valve arrangement with a control valve module having a supply connection arrangement with a high pressure connection and a Low pressure connection and a working connection arrangement with two working connections and a control valve between the supply connection arrangement and the work connection arrangement having.
  • valve assembly serves to provide a hydraulic Consumer, for example, a motor, the the working connections are connected with hydraulic fluid to supply under pressure.
  • Return flow compensation valves are provided for this purpose ensure that the consumer then too; when he is in Sliding operation works exclusively from the control valve is controlled.
  • DE 198 00 721 shows a control device for a hydraulic engine acting as a hydraulic cylinder is trained.
  • a compensation valve and a load-holding valve provided, which connected to a work connection is.
  • the load-holding valve is thereby by a pressure turned on at the other work connection.
  • the invention is based on the object, the control behavior to improve the valve assembly.
  • This object is achieved in a valve arrangement of the above mentioned type achieved in that the control valve module between the control valve and at least one Working connection has a return compensation valve.
  • the return compensation valve is immediate connected to an output of the control valve. This keeps a pressure drop at the lowest, practically achievable value. The consumer is then controlled exclusively via the control valve.
  • the return compensation valve has two Control inputs, of which a first with a Load-sensing line and a second one point between the control valve and the return compensation valve is connected, wherein the first control input connected via a suction valve to the low pressure port is.
  • the return compensation valve by the Pressure at the second control input closes or increases throttles when the pressure between the return compensation valve and the control valve rises.
  • the return compensation valve in the opening direction or towards a reduced throttling acted upon when the pressure in the load sensing line increases. This behavior is from a return compensation valve known in itself.
  • the return compensation valve has a valve element that through Controlled the pressures at the two control inputs becomes.
  • This valve element is often as a slide educated.
  • the return compensation valve can namely vacuum hydraulic fluid, if necessary should be.
  • the suction valve is preferably designed as a check valve, the first Control input opens, so that the pressure in the Load sensing line not readily to low pressure connection can drain off, a Nachsaugen too small Pressure is possible.
  • the first control input via a check valve disposed in the spool of the control valve connectable to the low pressure connection is.
  • This provides a mobility of the valve element the return compensation valve in both directions for sure.
  • From the second control input is a Supply of hydraulic fluid uncritical, because here always a sufficient liquid supply available is.
  • the return compensation valve either hydraulic fluid can suck in through the suction valve or deliver can through the check valve, that with the low pressure connection is connectable.
  • a discharge of hydraulic fluid over the first control input anyway only required when the slide in a corresponding position.
  • the check valve opens into a path in the slide, which can be connected to the low-pressure connection is.
  • This is a structurally relatively simple solution the construction costs for the control valve low holds.
  • a load-holding valve arranged, with the help of a pressure at the other working connection is alsêtbar.
  • the return compensation valve can that from a working connection to the control valve flowing stream of hydraulic fluid though curb. It is usually not easy able to prevent this liquid flow. If you now have a load-holding valve between the consumer and the work connection orders, then is the Consumer secured, i. you can actually put it in a locked position, namely even if an external load on the consumer acts.
  • the first control input is at least the Return compensation valve, which with the load-holding valve connected in series via a back pressure valve connected to the low pressure port. That's it possible, in the load-sensing cable during trouble-free operation always to maintain a pressure to Opening the load-holding valve is required. At long last must be generated by the back pressure valve pressure only be so great that he kept open the load-holding valve allows.
  • the back pressure valve is electrically activated
  • the control valve is electrically activated
  • the back pressure valve and the control valve respond to the same electrical signal.
  • a electrical activation can also be a hydraulic, a mechanical or other auxiliary force Use activation. So you can with the Deflection of the control valve at the same time the back pressure valve activate, so that it is ensured that the load-holding valve opens as soon as necessary is. Without a corresponding activation of the control valve but this is not required, so that the Back pressure valve can remain inactive.
  • Control valve module It is also advantageous if the back pressure valve in Control valve module is arranged. This is at the Use of multiple control valve modules to each control valve and thus every connected consumer assigned its own backpressure valve. Leave it Each consumer is individually approached.
  • each working port is a return compensation valve assigned.
  • the burden of the consumer So it can be done in both directions. In each The consumer will then still be the only direction controlled by the control valve.
  • each first control input connected via a throttle with a pressure control valve is, wherein the pressure control valves to different Pressures are adjustable. That's easy Way the consumer is in different ways To operate directions in different ways.
  • a tap between the Throttle and the pressure control valve of each return compensation valve connected to a shuttle valve, its output with an input of the control valve connected upstream flow compensation valve is.
  • the flow compensation valve can then with the Control valve together form a proportional valve.
  • the flow compensation valve ensures that over the control valve is always at a constant pressure, so that the amount of liquid controlled by the control valve depends solely on the opening cross-section, the is released from the control valve.
  • the pressure at the flow compensation valve will then be of the most Pressure controlled in the load-sensing lines.
  • the control valve has a slide, the in two working positions and a neutral position is displaceable, being between the neutral position and each working position provided a blocking position is.
  • the two working positions serve the consumer to drive in one direction or the other.
  • In the neutral position both outputs are the Control valve connected to tank, so no "false" signals may be generated, possibly the Open the load-holding valve.
  • To a defined transition between the neutral position and the drive in the one or to cause other direction is between the Neutral position and the two working positions one Blocking provided in the the path from the supply connection arrangement to the work connection arrangement is actually interrupted.
  • a hydraulic valve arrangement 1 has a control valve module 2, which has a high pressure port P and has a low pressure port T.
  • the high pressure connection P and the low pressure port T together a supply connection arrangement.
  • the Control valve module 2 two working ports A, B on, which together form a working connection arrangement.
  • the control valve module 2 is shown here as a box. It is realized in a coherent housing.
  • the Control valve 3 is arranged, which is designed as a slide valve.
  • the Control valve 3 has a slide 4, which by shifted a drive 5 in different positions can be.
  • the drive 5 can on the one hand via a pilot line 6 are hydraulically controlled. on the other hand is also an electrical control via a control line 7 possible.
  • the slider In the position shown, the slider is located 4 in a so-called neutral position s, in the the two working connections A, B with a tank line 8 are connected, which leads to the low pressure port T.
  • In the neutral position is one at the working ports A, B Connected consumers based on below blocked valves described.
  • the slider 4 is in a first working position. 1 and in a second working position r movable.
  • In the Working position r will be the working connection A with the High pressure port P connected.
  • In the working position 1 is the working port B to the high pressure port P connected.
  • a blocking position u1, u2 provided in which a connection between the working ports A, B and the high pressure port P is interrupted.
  • the two working positions 1, r are, as with Slide valves is common, not as discrete positions to understand. In every working position 1, r can the slider 4 can still be moved to different large flow cross sections for the hydraulic fluid from the high pressure port P to one of the two working ports A, B and other of the two working ports B, A to tank connection T (meter-out) release.
  • a flow compensation valve 9 is arranged between the high pressure port P and the control valve 3rd.
  • the Flow compensation valve 9 is in the opening direction from the force of a spring 10 and the pressure in one Control line 11 and in the closing direction of a pressure to a point 12 between the flow compensation valve 9 and the control valve 3 acted upon.
  • the flow compensation valve 9 and the control valve 3 thus together form a load-independent Valve, which may also be called Proportional valve can denote.
  • the working connection A is via a working line 13 and the work connection B is via a work line 14 connected to the control valve.
  • a return compensation valve 15 is arranged in the working line 14 in the working line 14 .
  • a return compensation valve 16 arranged in the working line 14 .
  • Both return compensation valves 15, 16 have in principle the same structure. They are therefore explained together.
  • Both return compensation valves 15, 16 are inside the control valve module 2 arranged and that the control valve. 3 relatively close together. With other words close the two return compensation valves 15, 16 directly to the control valve 3, so that between the Return compensation valves 15, 16 and the control valve 3 practically no or only a very small Pressure loss is observed.
  • Each control valve 15, 16 has a first control input 17a, 17b.
  • the letter a becomes reference numerals used to the return compensation valve 15th assigned.
  • the letter b is for reference numerals used associated with the return compensation valve 16 are.
  • the control input 17a, 17b is connected to a Load sensing line 18a, 18b in connection.
  • the load-sensing line 18a, 18b is at a corresponding deflection of the slide 4, which connects to the pressure port P causes, provided with the same pressure as the section of the working line 13, 14 between the Return compensation valve 15, 16 and the control valve Third
  • the force of a spring 19a, 19b acts in the same direction as the pressure at the first control input 17a, 17b.
  • the pressure at the first control input 17a, 17b and the Force of the spring 19a, 19b act in one direction, in which open the return compensation valves 15, 16, i.e. increase their flow cross-section.
  • a pressure acts on one second control input 20a, 20b, with a section the working line 13, 14 between the return compensation valve 15, 16 and the control valve 3rd connected is.
  • the control valve 3 is in each working position 1, r of the slider 4 a supply path 21 a, 21 b, the one connection between the output of the flow compensation valve 9 and the corresponding work management 13, 14 forms. From the supply path 21a, 21b branches off a control path 22a, 22b, which in the corresponding Load sensing line 18a, 18b opens.
  • the slider 4 depends on his position for each job 1, r one Return path 23a, 23b, through which the not with the Flow compensation valve 9 connected working line 13, 14 is connected to the tank line 8.
  • the Return path 23a, 23b opens a discharge path 24a, 24b, in which a to the tank line 8 opening check valve 25a, 25b is arranged.
  • the discharge path 24a, 24b in connection with the load-sensing line 18a, 18b.
  • the two load-sensing lines 18a, 18b are connected by a Shuttle valve 26 connected to each other, whose output is connected to another shuttle valve 27, the the highest in a hydraulic system in which too the valve assembly 1 is arranged, prevailing Pressure to a load sensing connection LS passes.
  • a throttle 28a, 28b provided between the shuttle valve 26 and the control valve 3rd is for each load-sensing line 18a, 18b a throttle 28a, 28b provided. Between the throttle 28a, 28b and the Shuttle valve 26 branches a line with a pressure control valve 29a, 29b.
  • the two pressure control valves 29a, 29b are shown with one only schematically Counter-pressure valve 30 is connected, which in the illustrated Design via an electric drive 31 activated is. But it can also work automatically, in another embodiment.
  • the drive 31 is connected to the Control line 7 connected so that the control valve. 3 and the back pressure valve 30 together with the same Control signal can be activated.
  • the back pressure valve 30 is connected to the low pressure port T. It ensures that in the respective load-sensing line 18a, 18b each have a predetermined minimum pressure prevails.
  • B is a hydraulic Consumer in the form of a hydraulic cylinder 32 connected. On the cylinder acts one through a Arrow 33 shown external force.
  • a load-holding valve 34 arranged in the opening direction through the Pressure at working port A and pressure at its inlet and in the closing direction by the force of a spring 35 is acted upon.
  • a check valve 36 is arranged to the cylinder 32 opens.
  • the load holding valve 34 is capable of the line between the cylinder 32 and the control valve module 2 completely close.
  • the return compensation valves 15, 16 are not necessarily capable of one complete interruption of the working pipes 13, 14 to effect.
  • the two load-sensing lines 18a, 18b are each over a suction valve 37a, 37b connected to the tank line.
  • the Nachsaugventile 37a, 37b are as check valves formed to the first control input 17a, 17b open.
  • valve assembly now works as follows:
  • the pressure regulating valves 29a, 29b in each case ensure that that the pressure in the load sensing lines 18a, 18b does not exceed a predetermined value. Should this be the case, then hydraulic fluid to the low pressure port T out through the backpressure valve 30. The back pressure valve 30 is stopped In any case, ensure that there is sufficient pressure to operate the load-holding valve 34 is present.
  • the highest pressure from the two load-sensing lines 18a, 18b is connected via the control line 11 to the Given flow compensation valve 9, which accordingly just as far as it opens, as it in the load-sensing lines 18a, 18b pending pressure requires.
  • the load-holding valve 34 relieves in the present embodiment, with the help of the back pressure valve done, to the environment. But one has with other configurations also the possibility of this Load holding valve to the working line 14 to relieve, to hermetically close or close the load-holding valve a connected proportional valve or to the tank towards relieve.
  • the slider of the control valve 3 may instead of the illustrated Pressure control also a flow control or cause a mixed pressure-flow control.
  • the arrangement of the two return compensation valves 15, 16 in the immediate vicinity of the control valve 3 within the control valve module 2 has the advantage that the Danger of leakage is significantly reduced compared with an external unit or a flanged one Unit comprising the return compensation valves 15, 16 contains.
  • At a greater distance from the control valve there can always be one in the routing Giving pressure loss corrected by the spring 19a, 19b would have to be. But you do not usually know exactly how big the loss is. If you, however, the Return compensation valves 15, 16 so close to the control valve 3 arranges, as in the present embodiment, then you have virtually no pressure loss, so that you have complete control over the tolerances has and always achieved a consistent performance.
  • the aftercare valves 37a, 37b and the return valves 25a, 25b allow the slider (or another Valve element) in the return compensation valves 15, 16 can react extremely fast. Of the Slider can suck or displace oil, without him overcoming any significant resistance here got to.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Multiple-Way Valves (AREA)
EP05009870A 2004-05-19 2005-05-06 Dispositif de soupape hydraulique Not-in-force EP1598560B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004025322 2004-05-19
DE102004025322A DE102004025322A1 (de) 2004-05-19 2004-05-19 Hydraulische Ventilanordnung

Publications (2)

Publication Number Publication Date
EP1598560A1 true EP1598560A1 (fr) 2005-11-23
EP1598560B1 EP1598560B1 (fr) 2008-05-21

Family

ID=34936198

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05009870A Not-in-force EP1598560B1 (fr) 2004-05-19 2005-05-06 Dispositif de soupape hydraulique

Country Status (5)

Country Link
US (1) US7328646B2 (fr)
EP (1) EP1598560B1 (fr)
CN (1) CN100354533C (fr)
AT (1) ATE396340T1 (fr)
DE (2) DE102004025322A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1953431A3 (fr) * 2007-02-02 2010-07-14 Paul John Brooks Ensemble de sélecteur de circuit
EP3135924A1 (fr) * 2015-08-24 2017-03-01 HAWE Hydraulik SE Commande hydraulique

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004025322A1 (de) 2004-05-19 2005-12-15 Sauer-Danfoss Aps Hydraulische Ventilanordnung
DE102006060333B3 (de) 2006-12-20 2008-08-21 Sauer-Danfoss Aps Hydraulische Ventilanordnung
DE102006060326B4 (de) * 2006-12-20 2008-11-27 Sauer-Danfoss Aps Hydraulische Ventilanordnung
DE102007017472B4 (de) * 2007-04-13 2018-05-30 Franz Xaver Meiller Fahrzeug- Und Maschinenfabrik - Gmbh & Co Kg Entlastung eines hydraulischen Kippsystems
US8925439B2 (en) * 2011-01-13 2015-01-06 Husco International, Inc. Valve control valve circuit for operating a single acting hydraulic cylinder
CN104154057B (zh) * 2014-08-14 2016-07-06 北京首钢股份有限公司 一种液压平衡回路
US20180319634A1 (en) * 2014-10-30 2018-11-08 Xuzhou Heavy Machinery Co., Ltd. Crane hydraulic system and controlling method of the system
WO2019219491A1 (fr) 2018-05-18 2019-11-21 Hydac Systems & Services Gmbh Soupape
DE102018207928A1 (de) * 2018-05-18 2019-11-21 Hydac Systems & Services Gmbh Ventil
DE102020123331A1 (de) * 2020-09-07 2022-03-10 Rheinisch-Westfälische Technische Hochschule (RWTH) Aachen, Körperschaft des öffentlichen Rechts Gasbetriebenes Antriebssystem und Verfahren zum Betrieb
DE102021202207B4 (de) * 2021-03-08 2022-12-01 Hawe Hydraulik Se Vorwahlventil, Hydraulikventilverband und Hydrauliksteuervorrichtung

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US3589387A (en) * 1969-08-22 1971-06-29 Int Basic Economy Corp Integrated manifold circuits and method of assembly
US4569272A (en) * 1982-03-22 1986-02-11 Vickers, Incorporated Power transmission
EP0197467A2 (fr) 1985-04-11 1986-10-15 Beringer-Hydraulik AG Soupape de descente freinée et maintenu sans fuites.
EP0515692A1 (fr) * 1990-11-30 1992-12-02 Kabushiki Kaisha Komatsu Seisakusho Systeme de circuit hydraulique
DE19800721A1 (de) 1998-01-12 1999-07-15 Danfoss As Steuervorrichtung für einen hydraulischen Motor
DE10216958B3 (de) 2002-04-17 2004-01-08 Sauer-Danfoss (Nordborg) A/S Hydraulische Steuerung

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Publication number Priority date Publication date Assignee Title
US4364304A (en) * 1976-01-21 1982-12-21 Danfoss A/S Arrangement for influencing the operating quantity of a servomotor
US4418612A (en) * 1981-05-28 1983-12-06 Vickers, Incorporated Power transmission
DE3800188A1 (de) * 1988-01-07 1989-07-20 Danfoss As Hydraulische sicherheitsbremsventilanordnung
DE102004025322A1 (de) 2004-05-19 2005-12-15 Sauer-Danfoss Aps Hydraulische Ventilanordnung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3589387A (en) * 1969-08-22 1971-06-29 Int Basic Economy Corp Integrated manifold circuits and method of assembly
US4569272A (en) * 1982-03-22 1986-02-11 Vickers, Incorporated Power transmission
EP0197467A2 (fr) 1985-04-11 1986-10-15 Beringer-Hydraulik AG Soupape de descente freinée et maintenu sans fuites.
EP0515692A1 (fr) * 1990-11-30 1992-12-02 Kabushiki Kaisha Komatsu Seisakusho Systeme de circuit hydraulique
DE19800721A1 (de) 1998-01-12 1999-07-15 Danfoss As Steuervorrichtung für einen hydraulischen Motor
DE10216958B3 (de) 2002-04-17 2004-01-08 Sauer-Danfoss (Nordborg) A/S Hydraulische Steuerung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1953431A3 (fr) * 2007-02-02 2010-07-14 Paul John Brooks Ensemble de sélecteur de circuit
EP3135924A1 (fr) * 2015-08-24 2017-03-01 HAWE Hydraulik SE Commande hydraulique

Also Published As

Publication number Publication date
EP1598560B1 (fr) 2008-05-21
US7328646B2 (en) 2008-02-12
DE102004025322A1 (de) 2005-12-15
CN1699762A (zh) 2005-11-23
CN100354533C (zh) 2007-12-12
ATE396340T1 (de) 2008-06-15
DE502005004165D1 (de) 2008-07-03
US20050257519A1 (en) 2005-11-24

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