[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

EP1450048A1 - Agencement de vanne - Google Patents

Agencement de vanne Download PDF

Info

Publication number
EP1450048A1
EP1450048A1 EP04100627A EP04100627A EP1450048A1 EP 1450048 A1 EP1450048 A1 EP 1450048A1 EP 04100627 A EP04100627 A EP 04100627A EP 04100627 A EP04100627 A EP 04100627A EP 1450048 A1 EP1450048 A1 EP 1450048A1
Authority
EP
European Patent Office
Prior art keywords
valve
chamber
hydraulic
flow
arrangement according
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
EP04100627A
Other languages
German (de)
English (en)
Other versions
EP1450048B1 (fr
Inventor
Marcus Bitter
David Price
Marlin Onnen
Steffen Schlemmer
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.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Publication of EP1450048A1 publication Critical patent/EP1450048A1/fr
Application granted granted Critical
Publication of EP1450048B1 publication Critical patent/EP1450048B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/065—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks non-masted
    • B66F9/0655—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks non-masted with a telescopic boom
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems
    • 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
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/3144—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
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/46—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
    • F15B2211/40—Flow control
    • F15B2211/47—Flow control in one direction only
    • F15B2211/473—Flow control in one direction only without restriction in the reverse direction
    • 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
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance 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
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/5154—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an output member
    • 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
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/77—Control of direction of movement of the output member
    • F15B2211/7741—Control of direction of movement of the output member with floating mode, e.g. using a direct connection between both lines of a double-acting cylinder

Definitions

  • the invention relates to a valve arrangement for a Hydraulic cylinder with a control valve, which at least a first chamber of the hydraulic cylinder over a first Supply line optionally with a hydraulic pressure source or connects a container. Furthermore, a first one Switch valve included, which the flow in a extending between the first chamber and the container controls first hydraulic line, and which due to a Switching signal opens, making a floating position adjustable is.
  • Valve arrangements with implemented floating positions, thereby free movement of a hydraulic consumer are made possible are known in the prior art. there both connection sides of the hydraulic consumer with each other as well as with or without pressure with one Tank or hydraulic tank connected. Such Valve arrangements are found in construction and loader vehicles Use where a boom with a lifting cylinder or a loader arm can be raised or lowered.
  • the Function of the floating position is required, for example, to regardless of the position and location of the vehicle allow a tool on the boom or loader arm of the Can follow the contour of the ground true to the contour. The tool will be there just pressed to the ground by gravity.
  • Valve arrangements of this type do not contain any load holding valves, the for safety reasons when a leak occurs in the Connection between cylinder and control valve on unintentional lowering of the boom or loader arm prevent or slow down strongly. Since it can be opened or Bypassing the load holding valve requires a control pressure a solution for combining a load holding valve with a Floating position, in the depressurized state of the hydraulic consumer and therefore no control pressure is buildable, not known.
  • DE 101 49 787 A1 discloses a valve arrangement with Floating position to control a double acting Consumer, where a control valve in a Flow position is acted upon and by a pressure-switched valve arrangement a floating position is feasible.
  • a control valve in a Flow position is acted upon and by a pressure-switched valve arrangement a floating position is feasible.
  • changes in the Movement speed of the consumer during the transition to the Floating position should be avoided effectively. adversely this has an effect that the throttling over a complex constructed pressure control of the Control valve takes place, which gives a high tax inertia and it is at high load when switching to one Floating position despite throttling to unwanted or uncontrolled lowering movements can occur.
  • the valve arrangement does not contain a load holding valve Protection of the hydraulic operation of the consumer.
  • DE 100 06 908 A1 discloses a hydraulic one Piston cylinder unit for agricultural machines with a load holding valve in the one working position is achieved in which a constant pressure in the piston chamber side cylinder space is adjustable. This can a boom or a tool attached to it always Lie on the floor with the selected contact force.
  • This Working position is achieved by the pressure chambers of the Piston-cylinder unit are connected to each other and a pressure compensation valve between the both pressure chambers. If the pressure drops below one Preselected value, the pressure control valve closes.
  • a Floating position is only possible if the preselected one Value is set to zero, so no pressure control he follows. The disadvantage is that when switching the load or the tool is uncontrolled under load would sink.
  • DD 205 471 discloses a hydraulic circuit arrangement, with which a floating position is created at the driver's request can be made by the chambers of a cylinder by means of a 3/2 valve can be connected to a container.
  • About one Throttle check valve is a throttled drain on the Pressure side of the cylinder both in the operating position and in Floating position guaranteed.
  • the disadvantage is that at Switch to the floating position under load on the Operation designed constant cross section of the throttle Lowering the pressure side is not controllable.
  • such a throttle check valve does not Load holding valve, which is in the operating position can prevent unwanted sinking.
  • the object underlying the invention is seen in specify a valve arrangement of the type mentioned at the outset, by which the aforementioned problems are overcome.
  • a valve arrangement is to be proposed with which a floating position can be realized and at Switch from operating position to floating position controlled sinking or holding the pressure side can.
  • Another object of the task is the Valve arrangement effective with a load holding valve for one Combine operating position.
  • a flow-dependent control has the Advantage that regardless of the hydraulic pressure in the Hydraulic line the volume flow is controllable so that with both low and high hydraulic loads only a certain flow rate through the hydraulic line reached and thus a safety function is offered.
  • the valve assembly brought into floating position by the switching signal Switching valve is switched to the flow position, then ensures the valve device that controls the volume flow, that regardless of the level of pressure, the flow rate can only change within certain limits or a certain value will not exceed.
  • the Valve device changing the flow opening Adjustment means for example a slide or Closing elements, on the one hand a pressure of the first chamber and on the other hand a pressure of the container as well possibly exposed to a spring force.
  • the Valve device changing the flow opening Adjustment means for example a slide or Closing elements, on the one hand a pressure of the first chamber and on the other hand a pressure of the container as well possibly exposed to a spring force.
  • valve device means that with increasing (falling) pressure drop across the valve device Reduce (widen) the flow cross-section.
  • the valve device contains a flow control valve, which the volume flow changes depending on the flow and to one specifiable maximum value limited.
  • flow control valves are for example from the company "HYDAC International" offered. A precise description can be found in DIN-ISO 1219 be removed.
  • a flow control valve has one Differential pressure regulator, which depends on the flow rate Control piston, a compression spring, a control orifice and one Set screw to adjust the control pressure difference Flow controls. With increasing volume flow or increasing flow d. H. increasing pressure drop the cross section of the control orifice is increased accordingly Pressure drop reduced until on again There is a balance of forces.
  • the control direction preferably the outflow direction of the hydraulic fluid the chamber of the Hydraulic cylinder, preferably the stroke side of the Hydraulic cylinder, corresponds to the direction of the container.
  • the valve can be flowed through uncontrolled in the opposite direction.
  • Such a valve has the advantage that even with extreme high pressure loads always a the control pressure difference sets the appropriate volume flow, with the Control pressure difference can be specified via the adjusting screw. This has the consequence that when switching from operating position to Floating position under load a controlled decrease in pressure, largely independent of the prevailing level Pressure, takes place and thus a safety precaution with the Switching to the floating position is given.
  • valve device contains a parallel to the Flow control valve arranged check valve, which in Direction of the first chamber opens. This ensures that the flowing towards the container Hydraulic fluid is forced through the flow control valve to flow and accordingly controlled from the high Pressurized chamber flows away, whereas an inflow can take place unhindered from the opposite direction.
  • valve device means that when exceeded of a preselectable pressure drop reduce the volume flow or interrupt. This ensures that at Reaching a volume flow that corresponds to the predeterminable pressure drop causes the connection to be broken so that the Pressure in the first chamber under high pressure or is held in the first hydraulic line. The pressure drops again, the connection will be re-established as soon as that Predeterminable pressure drop is reached or a Sets the volume flow, which causes a pressure drop, which is less than or equal to the specifiable pressure drop.
  • the Valve device a raw break protection valve, which at Reaching or exceeding a predeterminable pressure drop closes or when the pressure drop falls below the predefinable pressure drop opens.
  • raw breakage protection valves are for example offered by the company "HYDAC International” and are detailed in a company catalog “HYDAC INTERNATIONAL - FLUTEC pipe burst safety devices RBE ".
  • "Flutec" pipe burst safety devices are dependent on the volume flow switching flat seat valves, the impermissible and uncontrolled movements of a person under load Prevent consumers.
  • Has a pipe rupture safety valve a closing element, for example a locking piston in the form a poppet valve, which in normal operating condition has open switch position.
  • the closing element is preferably held in the open state by a spring, as long as the spring force is greater than that by the Flow resistance caused by flow through the closing element or on the plate surface of the Poppet valve.
  • the valve remains open and is in both Directions flowable. If the prevailing Volume flow when flowing through the valve in a predeterminable Direction of the pressure drop defined by the maximum permissible value is determined by the Flow resistance increase overcomes the spring force and that Closing element suddenly pressed onto the valve seat, see above that the flow is interrupted.
  • the valve opens automatically as soon as pressure equalization takes place and the Pressure force in front of the valve resulting from spring force and Compressive force behind the valve below.
  • the Valve device one parallel to the pipe rupture safety valve arranged choke or orifice, which when closed Pipe burst safety valve a reduced volume flow allowed. This ensures that there is always a certain Share of the volume flow is forwarded so that the Can not build up pressure in front of the valve device.
  • the throttle or orifice can be parallel in a bypass line be arranged to the raw break protection valve or for example in the form of a hole directly on Pipe rupture safety valve, especially directly on the poppet valve be trained. At high volume flows ensures that by closing the Pipe rupture valve a large part of the volume flow is intercepted and only a small part of the Hydraulic fluid passes through the throttle so that overall a controlled decrease in pressure when switching over to the floating position is reached.
  • this connects Control valve over a second chamber of the hydraulic cylinder a second supply line optionally with the Hydraulic pressure source or the container. So both can Chambers of a double-acting hydraulic cylinder with pressure be acted upon, which accelerated emptying of the Enables chambers and thus the extension and retraction of one Hydraulic cylinder piston is made possible at shorter intervals.
  • a second switching valve is preferably included, which the flow in a between the second chamber and the Container-extending second hydraulic line controls, and which is parallel to the first due to the switching signal Switch valve opens, making a floating position adjustable is in which the first chamber and the second chamber directly or communicate indirectly through the container.
  • the hydraulic cylinder can be used in any way Operating position are brought into a floating position or after accidentally switching to a floating position without significant pressure loss immediately back into a Operating position.
  • the first contains and / or the second supply line a load holding valve arrangement.
  • Load holding valve arrangements are state of the art and are considered in most modern valve arrangements Safety precautions introduced in supply lines to an unwanted pressure drop in the consumer or To prevent hydraulic cylinders. If leaks occur, be it on the control valve, on the connecting lines or on Seals etc., especially under load, can be too fast Pressure losses in the hydraulic chambers of the hydraulic cylinder come, which in turn poses a security risk. Around Preventing pressure drops under load will be such Load holding valve arrangements as close as possible to the Hydraulic cylinder positioned so that between Hydraulic cylinder and load holding valve arrangement as little as possible Components are included that could have leaks.
  • load holding valve arrangements are usually located directly on the hydraulic cylinder and are part of it Assembly, so that no easily damaged components, such as z. B. hoses must be used. Also allow Load holding valve assemblies have a tightness under load even the smallest pressure drops over a longer period of time prevent. An intended pressure change is achieved by such load holding valve arrangements by hydraulic Circuits are bypassed or opened.
  • the load holding valve assembly includes a check valve, for example a hydraulically unlockable check valve, which is in a closed position and in Dependence on the pressure of the first and / or the second Supply line opens. Furthermore, is parallel to Check valve included an additional check valve, where the additional check valve towards the Hydraulic cylinder opens.
  • the load holding valve assembly will preferably arranged on the stroke side of the hydraulic cylinder, d. H. on the usually safety-relevant pressure side of the Lift cylinder on which there is a high operating pressure a load will set.
  • About the corresponding one Supply line can be the first chamber of the hydraulic cylinder be filled by the pump.
  • the check valve prevents an effective escape of the hydraulic fluid this filled chamber.
  • a first pressure line connects the second supply line with the shut-off valve. Should now Chamber is emptied, the second chamber over the second Supply line filled, which creates a pressure in the second supply line that builds the check valve the first pressure line from the closed position to a Pass position moved. The hydraulic fluid can now run out the first chamber into the container. As soon as the Relieves pressure in the second supply line, for example by switching to another operating position, that takes Check valve back to its closed position. Furthermore is on the hydraulic cylinder side in the first supply line second pressure line provided as overload protection, which at excessive pressure conditions on the stroke side of the Hydraulic cylinder, regardless of the switching position of the Control valve that opens the shut-off valve.
  • the first and second switching valve as electromagnetic switchable seat valves. This allows through The switching valves generate an electrical switching signal controlled and switched to a floating position at any time become.
  • Switching valves for example pneumatic, hydraulic or are also mechanically controlled switchable.
  • valve arrangements for use for a Hydraulic cylinder for lifting and lowering a boom on one Loader or construction vehicle especially on a telescopic loader used.
  • a Hydraulic cylinder for lifting and lowering a boom on one Loader or construction vehicle, especially on a telescopic loader used.
  • a Floating position without described volume flow control would cause that with increasing load the boom more or would shutdown less uncontrollably, which is an increased Represents security risk.
  • the Use floating position when working on the ground surface.
  • the hydraulic cylinder with the boom raised by appropriate control via the control valve to apply pressure on the vertical side so that a accelerated boom shutdown entry. In all Operating positions is a secure switchover to one Given floating position.
  • the inventive Refinements a floating position for a telescopic loader while maintaining a security-relevant Load holding valve arrangement (pipe rupture protection) is given.
  • a floating position which dispenses with complex construction methods, so that the Mostly lifting sections already present on a telescopic loader the main valve blocks do not need to be changed.
  • the number of valve blocks can be kept low and also the possibility of retrofitting or upgrading Use of the same lifting cylinder with different Options.
  • a floating position function for example combine a hydraulic suspension version so that starting from a basic version with load holding valve arrangement a modular extension with floating position function and in addition a modular extension with suspension function is possible.
  • the circuit diagram shown in Fig. 1 shows a Embodiment for a valve assembly 10 for Realization of a floating position.
  • the valve assembly 10 contains a switchable control valve 12, for example a Slider valve, which with hydraulic lines 14, 16 with a pump 18 and a hydraulic tank 20 is connected, the control valve 12 in three operating positions, lifting, Neutral and lower position, is switchable. Switching the Control valve 12 is preferably manually controlled, but can also done electrically, hydraulically or pneumatically.
  • first and second supply line 22, 24 Control valve 12 connected to a hydraulic cylinder 26, wherein the first supply line 22 into a first chamber 28 of the Hydraulic cylinder 26 and the second supply line 24 in a second chamber 30 of the hydraulic cylinder 26 leads.
  • the first chamber 28 of the hydraulic cylinder 26 provides the piston chamber side or stroke side chamber, whereas the second chamber 30 the piston rod side or lower side Represents chamber of the hydraulic cylinder.
  • Load holding valve assembly 32 is provided.
  • the load holding valve assembly 32 contains a pressure and spring controlled Blocking valve 34, as well as one opening to the hydraulic cylinder side Check valve 36, which via a bypass line 38 is arranged parallel to the check valve 34.
  • About a first Pressure line 40 is a pressure connection from the check valve 34 to Hydraulic cylinder-side section of the first supply line 22 manufactured.
  • Via a second pressure line 42 a further pressure connection from the check valve 34 to the second Supply line 24 manufactured.
  • one Spring 44 the check valve 34 in the closed position.
  • a first hydraulic line 46 connects the first chamber 28 or the first supply line 22 with the hydraulic tank 20, which is not connected to the hydraulic tank 20 End 48 of the first hydraulic line 46 between the first Chamber 28 and the load holding valve assembly 32 is arranged.
  • a first switching valve is located in the first hydraulic line 46 50 and one in the direction of the hydraulic container 20 in series switched valve device 52 arranged.
  • the first Switch valve 50 represents an electrically switchable seat valve represents which via an adjusting spring 54 in the closed position is held and opened via a magnetic coil 56 Open position can be brought.
  • the switching valve 50 seals in one or both directions without leakage from.
  • the valve device 52 contains a flow control valve 58, which is connected in parallel to a check valve 60 is arranged, the check valve 60 in Hydraulic cylinder direction opens. It is also possible here the valve device 52 in the direction of the hydraulic container 20 to be arranged before the switching valve 50.
  • a second hydraulic line 62 is also provided, which connects the second supply line 24 to the first Hydraulic line 46 connects, the connection point 64 with the first hydraulic line 46 between the Hydraulic container 20 and the valve device 52 are arranged is.
  • the second hydraulic line 62 also contains a second one Switching valve 66, which is the first switching valve 50 in construction and function is the same.
  • the individual operating states can now be done as follows via the Control valve 12 and the switching valves 50 and 66 can be controlled.
  • the Control valve 12 by the actuating springs 68, 70 in the neutral position held.
  • the switching valves 50 and 66 are in one Closed position.
  • the control valve 12 is controlled by a control signal by means of an actuating device 72 from the neutral position brought out into the lifting or lowering position. It can manual, electrical, hydraulic or act pneumatic actuator 72.
  • the load holding valve arrangement 32 thus ensures that the Hydraulic cylinder 26 in its neutral position maintains or no oil from the pressurized first chamber 28 escape and that in Lowering the oil from the first chamber 28 over the open Check valve 34 can flow.
  • the lifting side being the side of the Hydraulic cylinder 26 is in which a pressure for lifting a load is built up.
  • the stroke side is the first chamber 28 of the hydraulic cylinder 26, by turning the hydraulic cylinder 26 also the second Chamber 30 could serve as the lifting side.
  • the first pressure line 40 represents an overload protection, so that if the Operating pressures in the first chamber 28 of the hydraulic cylinder 26, which arise, for example, from excessive loads can reach a limit pressure in the first pressure line 40 that opens the shut-off valve 34 for pressure reduction.
  • the switching valves 50 and 66 can be used in any Operating position can be switched to the floating position. To are the switching valves 50 and 66 by means of a switching signal driven in parallel so that the solenoids 56 of the Counteract the spring force of the springs 54 and the switching valves 50, 66 essentially from the closed position brought into flow position at the same time. This has to Consequence that the first chamber 28 and the second chamber 30 to one with the other and the other with the hydraulic reservoir 20 be related, so that an exchange of Hydraulic fluid or oil take place and the piston 74th can be moved freely. Finds a toggle an operating position under load, the oil flows under increased pressure from the pressurized first chamber 28 out, which leads to accelerated piston movement.
  • the flow control valve 58 enters into force Volume flow limited or controls the flow of the oil or regulates. If the volume flow exceeds an approved value, the passage cross section of the flow control valve 58 narrows, so that the volume flow does not continue to increase. hereby become uncontrolled movements of the hydraulic cylinder piston 74 effectively avoided. With an opposite pressure effect in the direction of the first chamber 28 enables this Check valve 60 bypassing the flow control valve 58 and thus an unregulated flow in the direction of the first Chamber 28. A switch from the floating position to one Operating position is at any time by switching the switching valves 50, 66 possible in a closed position.
  • FIG. 2 shows a second exemplary embodiment described. The same will be the same for similar components Reference numerals as used in Fig. 1. 2 is for the valve device 52 in place of the flow control valve 58 and the check valve 60 a pipe rupture valve 76 in Combination with a choke 78 connected in parallel used. Instead of the throttle 78 can also equivalent aperture are used. Is by switching of the switching valves 50, 66 switched to the floating position the pipe rupture safety valve 76 also one flow-dependent reduction or limitation of the Volume flow.
  • FIG. 3 shows a mobile telescopic loader 82 with a on a housing 84 or frame of the telescopic loader 82 pivotally hinged, extendable boom 86, between boom 86 and housing 84 is a hydraulic cylinder 26 for lifting and Lowering the boom 86 is arranged.
  • the hydraulic cylinder 26 is at a first and a second bearing point 88, 90 pivoted, the piston rod side 92 on the second bearing 90 on the boom 86 and the piston crown side 94 is hinged to the housing 84 at the first bearing 88.
  • the hydraulic tank 20, the pump 18 and the valve assembly 10 positioned on or in the housing 84 and connected to one another via hydraulic lines 14, 16, 46, 96. Furthermore, the supply lines 22, 24 are between Valve arrangement 10 and hydraulic cylinder 26 can be seen in FIG. 3. Control or not, control or Switch signals generated with which the control valve 12 and the switching valves 50, 66 (see FIGS. 1 and 2) controlled or be switched. According to the previous one described operating positions, the hydraulic cylinder 26th are operated in such a way that the boom 86 is raised, can be held or lowered. It is also possible in Switch floating position so that the piston can move freely and the boom 86 is floating.
  • valve arrangement 10 Realized with this by the valve arrangement 10 Safety precaution for a floating position can be taken from anyone Operating position switched out into a floating position be without causing uncontrolled changes in movement on the Boom 86 is coming. Furthermore, a Valve arrangement 10 with integrated floating position in Realized connection with a load holding device 32 with which also involves a pressurized lowering of the boom 86 by switching the control valve 12 in the lowered position closed switching valves 50, 66 is possible.
  • valve arrangement on others Vehicles are used, for example on excavators or Cranes that have hydraulically actuated components, which have to be raised or how to be lowered and where a floating position seems reasonable.

Landscapes

  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
EP04100627A 2003-02-21 2004-02-17 Agencement de vanne Expired - Lifetime EP1450048B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10307346 2003-02-21
DE10307346A DE10307346A1 (de) 2003-02-21 2003-02-21 Ventilanordnung

Publications (2)

Publication Number Publication Date
EP1450048A1 true EP1450048A1 (fr) 2004-08-25
EP1450048B1 EP1450048B1 (fr) 2006-06-14

Family

ID=32731084

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04100627A Expired - Lifetime EP1450048B1 (fr) 2003-02-21 2004-02-17 Agencement de vanne

Country Status (5)

Country Link
US (1) US7104181B2 (fr)
EP (1) EP1450048B1 (fr)
CA (1) CA2457980C (fr)
DE (2) DE10307346A1 (fr)
ES (1) ES2262091T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1762535A2 (fr) 2005-09-13 2007-03-14 Deere & Company Engin roulant du type muni d'un bras et procédé pour celui-ci
CN102583173A (zh) * 2011-12-19 2012-07-18 徐州重型机械有限公司 吊臂伸缩液控系统及具有液控系统的起重机

Families Citing this family (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004012382B4 (de) 2004-03-13 2014-03-13 Deere & Company Hydraulische Anordnung
US7207164B2 (en) * 2005-05-10 2007-04-24 Deere & Company Header hydraulic float suspension
US7430846B2 (en) * 2005-05-10 2008-10-07 Deere & Company Floating header with integrated float system for use with an agricultural windrower or combine
DE102006010696B4 (de) * 2006-03-08 2009-01-22 Sauer-Danfoss Aps Hydraulische Lenkung
DE102006010695B4 (de) * 2006-03-08 2009-05-14 Sauer-Danfoss Aps Hydraulische Lenkung
DE102006010697B4 (de) 2006-03-08 2009-01-22 Sauer-Danfoss Aps Hydraulische Lenkung
DE102006051541B4 (de) * 2006-11-02 2009-06-04 Sauer-Danfoss Aps Hydraulische Lenkeinrichtung
ES2332382T3 (es) * 2007-04-27 2010-02-03 Hawe Hydraulik Se Dispositivo de regulacion electrohidraulico para un soporte de panel solar.
US7827787B2 (en) 2007-12-27 2010-11-09 Deere & Company Hydraulic system
US8028613B2 (en) * 2009-04-29 2011-10-04 Longyear Tm, Inc. Valve system for drilling systems
US8858151B2 (en) * 2011-08-16 2014-10-14 Caterpillar Inc. Machine having hydraulically actuated implement system with down force control, and method
EP2570301B1 (fr) * 2011-09-16 2015-11-11 Cargotec Finland Oy Agencement hydraulique et procédé de réduction d'un cadre de culbuteur d'un levage à crochet
US9085873B2 (en) * 2011-12-23 2015-07-21 Caterpillar Inc. Hydraulic system for controlling a work implement
CN102900731B (zh) * 2012-10-31 2014-12-31 长沙中联消防机械有限公司 臂架应急收回的液压控制系统
EP2937472A4 (fr) * 2012-12-20 2016-09-07 Volvo Constr Equip Ab Engin de chantier à fonction flottante
CN103836021A (zh) * 2014-03-24 2014-06-04 徐州重型机械有限公司 一种平衡组阀、举升液压系统及消防车
US9708796B2 (en) 2014-09-25 2017-07-18 Cnh Industrial America Llc Hydraulic valve
US9790964B2 (en) 2014-09-25 2017-10-17 Cnh Industrial America Llc Hydraulic system
JP6502076B2 (ja) * 2014-12-11 2019-04-17 古河ユニック株式会社 増速弁およびこれを備える折り曲げ式クレーン
CN105443464B (zh) * 2015-12-01 2017-08-08 湖北江山重工有限责任公司 差动液压缸控制回路
US10550863B1 (en) 2016-05-19 2020-02-04 Steven H. Marquardt Direct link circuit
US11015624B2 (en) 2016-05-19 2021-05-25 Steven H. Marquardt Methods and devices for conserving energy in fluid power production
US10914322B1 (en) 2016-05-19 2021-02-09 Steven H. Marquardt Energy saving accumulator circuit
KR20190095287A (ko) 2016-12-16 2019-08-14 클라크 이큅먼트 컴파니 접이식 리프트 아암을 갖는 로더
USD832552S1 (en) 2017-10-12 2018-10-30 Clark Equipment Company Lift arm for loader
USD832551S1 (en) 2017-10-12 2018-10-30 Clark Equipment Company Loader
CN111519677B (zh) * 2020-04-28 2022-03-01 三一重机有限公司 浮动液压系统及工程机械
DE102020207104B4 (de) 2020-06-05 2023-08-10 Hawe Hydraulik Se Hydraulische Powertrimm-Lift-Vorrichtung für einen Bootantrieb und Bootantrieb
US12085099B1 (en) * 2020-06-18 2024-09-10 Vacuworx Global, LLC Flow control block for use with a vacuum material handler
CN112922915A (zh) * 2021-02-08 2021-06-08 徐工消防安全装备有限公司 一种平台重力下降控制系统和方法
US11976675B2 (en) * 2021-02-11 2024-05-07 Xtreme Manufacturing, Llc Systems and methods for bleed down and retraction of a construction machine boom
CN215058526U (zh) * 2021-03-19 2021-12-07 湖南星邦智能装备股份有限公司 双作用浮动油缸控制回路
CN114109946A (zh) * 2021-12-03 2022-03-01 中船重工重庆液压机电有限公司 一种千斤顶多点同步定位液压装置及控制方法
DE102022126009A1 (de) 2022-10-07 2024-04-18 Kramer-Werke Gmbh Hydraulikmaschine mit einem um eine Schwenkachse verschwenkbaren Ausleger

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5415076A (en) * 1994-04-18 1995-05-16 Caterpillar Inc. Hydraulic system having a combined meter-out and regeneration valve assembly
JPH09317706A (ja) * 1996-05-27 1997-12-09 Hitachi Constr Mach Co Ltd 再生機能付き落下防止弁装置
JPH10168949A (ja) * 1996-12-06 1998-06-23 Kobelco Kenki Eng Kk 油圧シリンダのフローティング装置
DE19932948A1 (de) * 1998-07-23 2000-02-10 Caterpillar Inc Gesteuerte Schwebeschaltung für eine Betätigungsvorrichtung

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3472127A (en) * 1967-12-12 1969-10-14 Caterpillar Tractor Co Control circuit for bulldozers used in pushing
US4024796A (en) * 1975-09-24 1977-05-24 Caterpillar Tractor Co. Float control electrical circuit for a blade
DE3216580A1 (de) * 1981-05-07 1983-02-24 Hiab-Foco AB, 82401 Hudiksvall Lasthalte- und senkbremsventil
DD205471A1 (de) 1982-06-24 1983-12-28 Peter Prusseit Hydraulische schaltungsanordnung zur erreichung einer schwimmstellung eines auslegerzylinders
DE3840246A1 (de) * 1988-06-22 1990-01-04 Edelhoff Polytechnik Muellsammelfahrzeug mit als wechselbehaelter ausgebildeten, auf einem kipprahmen hin- und herverschieblich gefuehrten containern
DE4129509C2 (de) * 1991-09-05 1994-06-16 Rexroth Mannesmann Gmbh Hydraulische Steueranordnung für Baumaschinen
DE10006908A1 (de) * 2000-02-16 2001-08-23 Caterpillar Sarl Genf Geneva Hydraulische Kolbenzylindereinheit für landwirtschaftliche Arbeitsmaschinen
DE10149787B4 (de) 2000-10-23 2012-06-06 Linde Material Handling Gmbh Ventilanordnung mit Schwimmstellung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5415076A (en) * 1994-04-18 1995-05-16 Caterpillar Inc. Hydraulic system having a combined meter-out and regeneration valve assembly
JPH09317706A (ja) * 1996-05-27 1997-12-09 Hitachi Constr Mach Co Ltd 再生機能付き落下防止弁装置
JPH10168949A (ja) * 1996-12-06 1998-06-23 Kobelco Kenki Eng Kk 油圧シリンダのフローティング装置
DE19932948A1 (de) * 1998-07-23 2000-02-10 Caterpillar Inc Gesteuerte Schwebeschaltung für eine Betätigungsvorrichtung

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 04 31 March 1998 (1998-03-31) *
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 11 30 September 1998 (1998-09-30) *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1762535A2 (fr) 2005-09-13 2007-03-14 Deere & Company Engin roulant du type muni d'un bras et procédé pour celui-ci
DE102005043447A1 (de) * 2005-09-13 2007-03-15 Deere & Company, Moline Ladegerät sowie Verfahren für ein Ladegerät
US7430953B2 (en) 2005-09-13 2008-10-07 Deere & Company Loading implement and process for loading implement
EP1762535A3 (fr) * 2005-09-13 2009-01-07 Deere & Company Engin roulant du type muni d'un bras et procédé pour celui-ci
CN102583173A (zh) * 2011-12-19 2012-07-18 徐州重型机械有限公司 吊臂伸缩液控系统及具有液控系统的起重机

Also Published As

Publication number Publication date
CA2457980A1 (fr) 2004-08-21
US7104181B2 (en) 2006-09-12
US20040221714A1 (en) 2004-11-11
DE10307346A1 (de) 2004-09-02
DE502004000729D1 (de) 2006-07-27
EP1450048B1 (fr) 2006-06-14
ES2262091T3 (es) 2006-11-16
CA2457980C (fr) 2007-08-28

Similar Documents

Publication Publication Date Title
EP1450048B1 (fr) Agencement de vanne
DE102004012382B4 (de) Hydraulische Anordnung
DE19956717B4 (de) Hydrauliksteuergerät
DE2352742C2 (de) Hydraulisches Senkbrems-Sperrventil
EP1496009B1 (fr) Suspension hydraulique
EP1915538B1 (fr) Montage pour commander un cylindre d'entrainement hydraulique a double effet
EP1766146B1 (fr) Systeme de soupapes de mecanisme de levage
EP1355065B1 (fr) Commande hydraulique
DE102006060333B3 (de) Hydraulische Ventilanordnung
EP1743981A1 (fr) Agencement hydraulique
DE10330869A1 (de) Hydraulisches System
DE4106845C2 (fr)
EP2142808B1 (fr) Ensemble de commande hydraulique
EP1781952B1 (fr) Ensemble de commande hydraulique
WO2009015502A1 (fr) Dispositif de commande pour au moins deux commandes hydrauliques
EP3527833B1 (fr) Circuit d'alimentation à commande à pression réglable
DE69610922T2 (de) Hydraulisches sicherheitsbremsventil
DE10340505B4 (de) Ventilanordnung zur Steuerung eines Hydraulikantriebs
DE19653810A1 (de) Hydraulische Einrichtung zur Steuerung des Druckmittelflusses
EP2157320B1 (fr) Commande hydraulique pour un moteur hydraulique
DE19548943B4 (de) Ventilanordnung
DE4135013A1 (de) Hydraulisches antriebssystem
DE102010026453A1 (de) Hubwerk
EP0735275B1 (fr) Dispositif à crans
EP3464908B1 (fr) Système de vannes

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK

17P Request for examination filed

Effective date: 20050225

AKX Designation fees paid

Designated state(s): DE ES FR GB IT

17Q First examination report despatched

Effective date: 20050407

RBV Designated contracting states (corrected)

Designated state(s): DE ES FR GB IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20060614

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 502004000729

Country of ref document: DE

Date of ref document: 20060727

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20060830

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2262091

Country of ref document: ES

Kind code of ref document: T3

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20070315

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20140121

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20140220

Year of fee payment: 11

Ref country code: ES

Payment date: 20140226

Year of fee payment: 11

Ref country code: IT

Payment date: 20140224

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20140227

Year of fee payment: 11

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004000729

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20150217

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20151030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150217

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150217

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150901

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150302

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20160928

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150218