EP1781952B1 - Ensemble de commande hydraulique - Google Patents

Ensemble de commande hydraulique Download PDF

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Publication number
EP1781952B1
EP1781952B1 EP05755620A EP05755620A EP1781952B1 EP 1781952 B1 EP1781952 B1 EP 1781952B1 EP 05755620 A EP05755620 A EP 05755620A EP 05755620 A EP05755620 A EP 05755620A EP 1781952 B1 EP1781952 B1 EP 1781952B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
pilot
valve
chamber
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.)
Not-in-force
Application number
EP05755620A
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German (de)
English (en)
Other versions
EP1781952A1 (fr
Inventor
Alfred Breunig
Karl Krug-Kussius
Jörn PETERSEN
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Bosch Rexroth AG
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Bosch Rexroth AG
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Publication of EP1781952A1 publication Critical patent/EP1781952A1/fr
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    • 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
    • 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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • 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
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/024—Pressure relief 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
    • 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
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the 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
    • F15B2211/3133—Regenerative position connecting the working ports or connecting the working ports to the pump, e.g. for high-speed approach stroke
    • 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
    • F15B2211/329—Directional 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
    • F15B2211/50—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
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/5159—Pressure control characterised by the connections of the pressure 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
    • F15B2211/50—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
    • F15B2211/60—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
    • 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
    • F15B2211/75—Control of speed of the 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8609—Control during or prevention of abnormal conditions the abnormal condition being cavitation

Definitions

  • the invention relates to a hydraulic control arrangement with a differential cylinder according to the preamble of patent claim 1 and suitable for such a control arrangement pilot-operated pressure relief valve.
  • Such control arrangements are used in particular in mobile work equipment, for example, to pivot a blade of a wheel loader.
  • the blade is pivoted down to empty, for example, material received therein.
  • the piston rod of the differential cylinder is retracted so that the blade is pivoted upwards, ie, away from the ground.
  • a control valve which is followed by a boost valve.
  • the control valve and the boost valve are brought into a position in which a pump of the control arrangement with a piston rod-side annulus and a bottom-side cylinder chamber are connected to a tank.
  • a pump of the control arrangement with a piston rod-side annulus and a bottom-side cylinder chamber are connected to a tank.
  • the control valve and the boost valve are adjusted so that the cylinder chamber is connected to the pump and the piston rod side annulus is also in communication with the cylinder chamber, so that the displaced from this pressure medium is additionally guided into the cylinder chamber and so the extension movement of the differential cylinder is faster than in control arrangements without differential circuit.
  • the DE 38 13 020 A1 shows a device for feed control of a double-acting hydraulic cylinder with means for setting a counter-pressure.
  • control arrangement for actuating the blade and the boom of a wheel loader, bulldozer or the like is disclosed.
  • the control arrangement is designed with a pressure relief valve, via which the load pressure is limited to the two hydraulic cylinders.
  • the pressure limiting valve is designed with a pressure switching stage, which makes it possible to limit the load pressure to a higher pressure when operating the blade alone, as it is the case when operating the boom or actuation of both hydraulic cylinders.
  • the invention has for its object to provide a hydraulic control arrangement and a pressure relief valve, by which damage to a differential cylinder of the control arrangement can be prevented.
  • the hydraulic control arrangement is designed with a differential cylinder. Its pressure chambers can be connected via a control valve arrangement with a pump or a tank, so that a piston rod of the differential cylinder extends or retracts.
  • the pressure in the effective pressure in the supporting pressure chamber is limited in the inventive solution via a pilot-operated pressure relief valve.
  • Its pilot stage is designed with a pressure changeover stage, via which the pressure set at the lower pressure in the other pressure chamber of the pressure limiting valve is lowered to the extent that overloading of the piston rod is reliably prevented.
  • a control surface of the pilot stage is acted upon by the pressure in the other pressure chamber, so that the limit pressure at which the pressure relief valve opens, in response to this pressure is variable.
  • the differential cylinder can be controlled via the control valve arrangement in differential circuit, in which the annular space is connected to the cylinder space when the piston rod is extended.
  • the pressure switching stage preferably has a control spring of the pilot stage of the pressure relief valve acting on the clamping piston, which is acted upon in the direction of increasing the spring preload pressure in the piston rod side annulus and in the direction of lowering the spring preload pressure in the other, effective in the support pressure chamber (cylinder chamber), wherein in this Direction effective control surface of the tensioning piston is smaller than the effective in the direction of increasing the spring bias control surface.
  • the basic structure of a pressure relief valve used in the control arrangement according to the invention is per se from the DE 100 62 428 A1 the applicant known. Different from this solution is in a preferred embodiment, that the clamping piston of the pressure switching stage is acted upon in the direction of increasing the bias of a pilot valve cone acting on the control spring from a control pressure corresponding to the pressure in the other pressure chamber, which drops when exposed to an external force when he not already tank pressure. An effective in the direction of a reduction of the control spring bias smaller control surface is acted upon by the pressure in the effective in the support direction pressure chamber.
  • the clamping piston of the pressure changeover stage is acted upon in the direction of increasing the bias of the pressure at the inlet of the pressure relief valve, which corresponds to the pressure in the effective pressure in the support direction.
  • the tensioning piston is acted upon in the known solution by an external control pressure - this known pilot operated pressure relief valve could not be used without changes in the inventive solution.
  • clamping piston is dispensed with the smaller control surface.
  • the area ratio between the control surface of the tensioning piston and the pilot valve seat surface is ⁇ 1.5 in one embodiment.
  • the control arrangement can be made particularly compact if a pilot piston of the pressure limiting valve is provided with a longitudinal channel, is passed over the control oil from a spring chamber of a main stage of the pressure relief valve to the smaller control surface.
  • pilot piston is preferably carried out with a projection which dips sealing into a recess of the clamping piston.
  • the end face of this recess then forms the smaller control surface, wherein the effective size of this surface is equal to the cross-sectional area of the projection.
  • the two control surfaces are formed on a pilot piston, wherein a smaller control surface from the pressure in the other pressure chamber (for example, piston rod side) and the larger control surface from the pressure in the other pressure chamber of the consumer (for example cylinder chamber) is acted upon - the tensioning piston then be waived. -
  • the pressure limiting valve is designed with an emergency opening, via which the input connection can be connected directly to the tank connection.
  • control valve arrangement used in the control arrangement has a metering orifice formed by a continuously adjustable directional valve, which is followed by a LUDV pressure compensator. It is particularly preferred if the pressure medium supply takes place via a pump whose flow rate is adjustable in dependence on the highest load pressure of the entire system - the control arrangement then represents a LUDV system.
  • FIG. 1 is a circuit diagram of a directional control valve element 1 of a mobile control block, via which several consumers of a mobile implement, such as a wheel loader can be controlled.
  • This in FIG. 1 illustrated directional control valve element 1 of the mobile control block is used to control an actuating cylinder 2, via which a blade mounted on a boom is pivotable.
  • the disk-type directional control valve element 1 has a pressure port P, a tank port T, two working ports A1, B1, and two control ports a1, b1, another control port x and a LS port LS.
  • the control block is designed as a LUDV system, via which a load pressure-independent flow distribution is possible.
  • a pump with variable delivery volume for example, a variable displacement pump depending on the highest load pressure of the consumer is controlled.
  • the LUDV directional control valve element 1 has a continuously adjustable directional control valve 4 whose valve spool can be acted upon by a control pressure via the two control ports a1, b1 and is thus displaceable from a spring-biased central locking position into a multiplicity of control positions identified by (a) or (b).
  • the directional control valve 4 has at least one pressure connection P, a tank connection T, two working connections A, B as well as two further connections D and D '.
  • the directional control valve 4 forms a directional part, which is indicated by the two intersecting or branching arrows, and a speed part, which is formed by a variable metering orifice 5, which lies between the connections D and D '.
  • the two working ports A, B of the directional control valve 4 are connected via working lines, referred to below as feed line 6 and return line 8, to the working port A1 or to the working port B1.
  • a so-called low-leakage valve 10 is arranged in the return line 8, which consists in principle of a logic valve 12 and a pilot control valve 14.
  • the logic valve has a stepped valve body which is loaded by a spring accommodated in a spring chamber in the closing direction.
  • the spring chamber is connected via a throttle to the working port B1 of the directional control valve element.
  • the pilot valve 14 is biased into a blocking position and can be switched by means of an actuating piston 16 from this blocking position into a passage position in which the spring chamber of the logic valve 12 is connected via a tank control channel 17 with a tank port T connected to the tank channel 18, so that the spring chamber of the logic valve 12 is depressurized.
  • the graduated valve body of the logic valve 12 can thus be lifted at a pressure fluid flow in the return line 8 to the actuating cylinder 2 already due to a non-return function and at a flow of pressure medium from the actuating cylinder 2 to port B of the directional control valve with relief of the spring chamber of its valve seat.
  • the actuating piston 16 is acted upon via a control branch passage 20 with the pressure at the control port a1, wherein due to a large area of the actuating piston 16, a comparatively large force is applied to the pilot control valve 14. Since the construction of such a low-leakage valve 10 is known, further relevant embodiments are unnecessary.
  • the two working ports A1, B1 of the directional control valve element 1 are via working lines 24, 26 with a bottom-side cylinder chamber 28 and a piston rod-side annular space 30 of the actuating cylinder 2 designed as a differential cylinder connected.
  • the directional control valve element 1 is further penetrated by a connected to the pressure port P pump channel 32. From this branches off an inlet channel 34, which leads to the connection D of the directional control valve 4.
  • the port D 'of the directional control valve is connected via a connecting channel 36 to an input port P of a LUDV pressure compensator 38, the pressure compensator piston is acted upon in the opening direction by the pressure in the connecting channel 36 and in the closing direction by the force of a spring and the highest load pressure of the operated consumer , which is tapped via a connected to the LS port LS LS channel 40.
  • the pressure compensator is thus acted upon in the opening direction by the pressure downstream of the metering orifice 5.
  • An output port A of the pressure compensator 38 is connected via a pressure compensator channel 42 and a check valve 44 to the input port P of the directional control valve 4.
  • the tank connection T is connected to the tank channel 18 by means of a drainage channel 46.
  • the pressure in the return line 8 connected to the annular space 30 is limited by a secondary pressure limiting valve 48, which is arranged in a discharge channel 50 which branches off in the region of the pressure medium flow path between the logic valve 12 and the associated working port B1 of the return line 8 and with the tank channel 18 is connected.
  • the pressure protection of the associated with the cylinder chamber 28 feed line 6 via a pilot-operated pressure relief valve 52 which is arranged in a likewise connected to the tank channel 18 channel 54, in the area branches off from the flow line 6 between the directional control valve 4 and the working port A1.
  • the pilot-operated pressure limiting valve 52 and the pressure limiting valve 48 are each designed with a Nachsaugfunktion, so that pressure medium can be sucked from the tank channel 18 to avoid cavitation in a pulling load.
  • the pilot-operated pressure relief valve 52 is, as described below in more detail with reference to Figures 2 and 3 is explained, from a main stage, a pilot stage and a pressure changeover stage 56.
  • the latter makes it possible to change the set pressure on the pilot operated pressure relief valve 52.
  • This schematic in FIG. 1 illustrated pressure changeover stage 56 has a clamping piston 58, on which a control spring 60 of the pilot stage is supported.
  • a larger control surface of the clamping piston 58 is acted upon by the pressure in a pilot channel 62, which leads to the control terminal X of the directional control valve element 1, which in turn is connected via a line 64 with the leading to the annulus 30 working line 26.
  • the pressure acts in the flow line 6, which is tapped off via the channel 54 and via a tapping channel 66.
  • the directional control valve 4 is brought into one of its (a) marked positions by the control port a1 is acted upon by a control pressure.
  • This control pressure can be adjusted for example via pressure reducing valves, which reduce the pressure in a control circuit to a suitable control pressure.
  • the pressure medium then flows from the variable displacement pump via a pump line, not shown, to the pressure port P and from there via the pump channel 32, the inlet channel 34 to port D of the directional control valve, from there via the metering orifice 5 corresponding to the control pressure to the port D 'of the directional control valve 4 and via the connecting channel 36 to the connection P of the LUDV pressure compensator 38.
  • This LUDV pressure compensator 38 arranged downstream of the metering orifice 5 throttles the pressure medium volume flow so strongly that the pressure after all metering orifices of the system is the same and preferably corresponds to the highest load pressure or slightly above this is. D. h., With a shortage of several consumers changes to the pressure downstream of the orifices nothing.
  • the pump pressure is applied in the same way to all metering orifices of the system, so that the pressure difference at all metering orifices alters in the same way if the pump pressure decreases in the event of an undersupply - the flow distribution between the metering orifices is maintained (load pressure-independent flow distribution).
  • the thus throttled pressure medium flow then flows through the pressure balance channel 42, the input port P and the working port A of the directional control valve 4 and the flow line 6 and the working line 24 to the cylinder chamber 28.
  • the piston rod 68 extends, wherein the pressure medium displaced from the annular space 30 via the working line 26 and the working port B1 flows.
  • the pilot control valve 14 is brought from its spring-biased locking position to its passage position, so that the spring chamber of the logic valve 12 relieved and this is opened by the pressure in the drain line 8, so that the pressure fluid continues to the working port B of the directional control valve 4th flows and there to that of the pump subsidized pressure medium flow is summed.
  • Tank connection T is shut off in positions (a).
  • the pilot operated pressure relief valve 52 remains set to a comparatively high pressure, which should be, for example, 380 bar. As will be explained in more detail below, this higher pressure is adjusted by acting on the larger control surface of the clamping piston 58, the pressure in the annular space 30, which is at least as large as the pressure in the cylinder chamber 28, which is the smaller control surface of the differential circuit Tensioning piston 58 acted upon.
  • the directional control valve 4 is displaced by applying a control pressure to the control port b1 in one of its (b) marked positions, in which case the cylinder chamber 28 is connected to the tank channel 18 and the annular space 30 with the pump channel 32, so that Pressure medium is conveyed into the annular space 30 and flows back from the cylinder chamber 28 displaced pressure fluid to the tank T.
  • FIG. 2 As already mentioned, this has a main stage 70, a pilot stage 72 and the pressure changeover stage 56.
  • the basic structure of the main stage 70 and the pilot stage 72 is essentially made of DE 100 62 426 A1 known, so that only the components required for understanding the invention are described and reference is otherwise made to this pre-published document.
  • the pilot-operated pressure relief valve 52 is designed in cartridge construction and has a housing 74, on which an end-side pressure port P and a radial, formed for example by a bore star tank port T is formed.
  • a valve slide 76 designed with a sliding seat is guided in a valve bore 78, which is prestressed against a seat edge 82 via a weak compression spring 80.
  • the valve spool 76 is hollow, wherein in an axially projecting end face a nozzle bore 84 is formed, which extends inwardly toward a spring chamber 110 extended for the compression spring 80.
  • a radial collar 86 is formed at the in FIG. 2 arranged on the right rear side of the valve spool 76 . This forms a stop for a Nachsaugring 88 which is sealingly guided in an annular space between a radially enlarged portion of the valve bore 78 and the outer periphery of the valve spool 76.
  • left end face of the Nachsaugrings 88 is acted upon via a throttle gap 90 with the pressure at the tank port T.
  • a sealing edge 92 is formed in the radially widened region of the valve bore 78, against which a seat body 94 inserted in a further enlarged region of the valve bore 78 rests. This is biased by means of a screwed into the housing 70 pilot housing 96 against the sealing edge 92.
  • a pilot valve seat 98 is formed, against which a pilot valve cone 100 is biased by the control spring 60.
  • the pilot valve cone 100 has a collar 102, the outer circumference is guided in a provided with two longitudinal grooves guide bore 104 of the seat body 94.
  • FIG. 2 Left end face of the seat body 94 is formed an axial projection in which a closed blind hole 106 is provided to the left, which widens to the pilot valve seat 98 and which is connected via radial bores 108 with the spring chamber 110 for the compression spring 80.
  • the in FIG. 2 the space 93 formed on the right of the seat 92 is connected to the tank connection T via a sloping channel 95. This space 93 is also connected via connecting holes 97 with the space encompassed by the seat body 94.
  • About the longitudinal grooves in the guide bore 104 of the seat body 94 and the control spring 60 receiving space is connected to the tank.
  • the control spring 60 is on the in FIG. 2 supported on the left end face of the clamping piston 58, so that this rests in its illustrated basic position on a screwed into the through hole 114 stop screw 122.
  • the through hole 114 opens at the right end face of the pilot housing and forms a port X1 of the pilot operated pressure relief valve 52, to which the in FIG. 1 shown control channel 62 is connected.
  • the stop screw 122 is annular, so that the pressure at the control terminal X1 also acts on the back of the clamping piston 58, which forms a substantially larger compared to the control surface 120 control surface 124.
  • a radial shoulder acting as a stop 126 is formed on the through-bore 114, which moves the axial travel of the tensioning piston 58 to the left (FIG. FIG. 2 ) limited.
  • FIG. 3 The symbol of the in FIG. 2 illustrated pressure relief valve 52 is in FIG. 3 strongly schematized shown. Shown are the main stage 70, the pilot stage 72 and the pressure switching stage 56 with the clamping piston 58 and the pilot housing 96. The larger control surface 124 of the clamping piston 58 is acted upon by the pressure in the control channel 62 and the smaller control surface 120 with pressure at the input terminal P over the longitudinal channel 116 and the spring chamber 110 and the nozzle bore 84 is tapped (see FIG. 2 ). In FIG. 3 only the reference numeral for the longitudinal channel 116 is shown.
  • the clamping piston 58 acts on the control spring 60, which acts on the valve spool 76 of the main stage 72 in the closing direction. In the opening direction acts on the valve spool 76, the pressure at the input port P, which also rests in the channel 54 and in the flow line 6.
  • the pressure port P of the pressure relief valve 52 can be connected by hand to the tank port T. This is in FIG. 3 indicated with the manually operable switching valve 128. When switching this switching valve 128 in its passage position of the input port P of the pressure relief valve 52 is relieved to the tank channel 18 out. At the in FIG. 2 shown concrete Aus sinceungsbeispiel this emergency opening is formed by the interaction of the seat body 94 with the sealing edge 92.
  • pilot housing 96 of the seat body 94 sits firmly on the sealing edge 92 - this corresponds to the closed position of the switching valve 128 (see FIG. 3 ).
  • the manually accessible pilot housing 96 is unscrewed somewhat out of the housing 74, so that the seat body 94 lifts off from the sealing edge 92 and the spring chamber 110, in which the pressure is usually applied to the input terminal P.
  • the slant channel 95 is connected to the tank port T or more precisely the tank channel 18 - the valve spool 76 can then be moved by the pressure at the input port P against the force of the comparatively weak compression spring 80 to the right, so that the connection to the tank port T is opened.
  • the Nachsaugring 88 is moved by the higher tank pressure to the right and runs on the Radial collar 86, so that the valve spool 76 is taken and the connection from the tank port T to the input port P is opened, so that pressure fluid can be sucked from the tank.
  • the force acting in one direction on the tensioning piston is the sum of the force of the control spring 60 plus the pressure force generated on the control surface 120, which is equal to the cross-sectional area of the projection 111 within the recess 112, by the pressure prevailing in the spring space 110 becomes.
  • the spring force is equal to a compressive force generated by the boundary pressure on a surface containing the differential area between the cross-sectional area of the pilot valve cone 100 at the seat 98 and the control surface 120 is.
  • the force acting on the tensioning piston in the one direction when the higher limit pressure is reached corresponds to a compressive force produced by the higher limit pressure on the cross-sectional area of the pilot valve cone on the seat 98.
  • the highest limit pressure is given by contact of the clamping piston on the stop 126 and the then existing bias of the control spring 60.
  • the tensioning piston 58 is moved from the position in FIG FIG. 2 shifted to the left until it runs onto the stop 126.
  • the control spring 60 is tensioned - at the pilot operated pressure relief valve 52, the higher pressure is set. For example, to set 390 bar, 65 bar in connection X1 is sufficient.
  • the pressure in the annular space 30 decreases, if he was not already tank pressure, while the pressure in the cylinder chamber 28 increases.
  • the geometry of the clamping piston 58 is selected so that from a certain pressure difference between the pressure chambers 28, 30 of the clamping piston 58 lifts by the relief of the control surface 124 from the stop 126 and is moved against the stop screw 122. This return movement is assisted by the pressure acting on the smaller control surface 120 - the bias of the control spring 60 is reduced and corresponding to the release pressure of pilot operated pressure relief valve 52 set to a lower pressure (100 bar). This pressure is chosen so that damage to the piston rod 68 can be reliably avoided. Below a certain pressure in the terminal X1 of the clamping piston 58 is also at tank pressure in the cylinder chamber 28 on the stop screw 122, namely, when the pressure force is less than the force of the relaxed spring 60.
  • the small control surface 120 of the clamping piston 58 causes, when the pressure limiting valve 52 responds, the tensioning piston 58 is acted upon in the direction of relaxing the control spring 60 by a force which is as great as the force generated by the inlet pressure (P) on the entire seating surface of the pilot valve seat 98 is.
  • P inlet pressure
  • FIG. 4 an embodiment is explained in which the pressure relief valve 52 already responds at a much smaller pressure drop in the annular space 30 of the actuating cylinder 2.
  • This will be at the in FIG. 4 illustrated embodiment essentially achieved in that the additional smaller control surface 120 is omitted and the area ratio between the effective diameter of the clamping piston 58 and the pilot valve seat diameter is chosen substantially smaller than in the above-described embodiment.
  • This area ratio is at the in FIG. 4 illustrated embodiment, about 1.12, ie, the pilot valve seat area A 2 is 1.12 times greater than the effective area A 1 of the clamping piston 58th
  • FIG. 4 illustrated embodiment corresponds to that of FIG. 2 , Accordingly, this is also in FIG. 4 illustrated embodiment with a main stage 70, a pilot stage 72 and a pressure switching stage 56 executed.
  • the main stage 70 with the valve spool 76, the pressure spring 80 arranged in the spring chamber 110, the cartridge-shaped housing 74 and the Nachsaugring 88 corresponds to the main stage 70 of the above-described embodiment, so that the simplicity is referred to the relevant embodiments.
  • the pilot stage 72 and the switching stage 56 are substantially integrated into the pilot housing 96, which is screwed into the cartridge-shaped housing 74 and presses the seat body 94 against the sealing edge 92 (in the illustrated basic position).
  • the sealing body 94 is designed with an axial projection 130, in which the blind hole 106 is formed, which opens via the radial bores 108 in the spring chamber 110.
  • a damping piston 132 is guided axially displaceable, which via damping gaps (in FIG. 4 not shown in detail) a pressure medium connection in the direction of the pilot valve seat 98 allows.
  • a spherical pilot valve body is biased in this embodiment, which is also referred to as a pilot valve cone 100 for simplicity.
  • This is supported by a mushroom-shaped spring plate 134 on which the control spring 60 engages, which in turn is supported by a further spring plate 136 on the clamping piston 58.
  • the outer circumference of the mushroom-shaped spring plate 134 is guided within the seat body 94.
  • the control spring 60 receiving space 93 is - as in the above embodiment - connected to the tank port T.
  • the pilot stage 72 opens when the effective pressure at the pilot valve seat 98 is sufficient to lift the pilot valve cone 100 from the pilot valve seat 98.
  • In the opening direction acts on the pilot valve seat 98 with the cross-sectional area A 2, the pressure at the pressure port P of the nozzle bore 84, the spring chamber 110, the radial bores 108 and limited by the damping oil 106 damping gap is tapped.
  • the area ratio A 1 / A 2 is relatively small (for example, 1.12) executed, so that even at a much higher pressure in the annulus 30 than in the above embodiment, the pilot stage 72 is open.
  • the pressure relief valve would correspondingly at a pressure of about 340 bar - ie much earlier than in the FIG. 2 illustrated embodiment - open.
  • This early opening is further supported by the fact that in FIG. 4 illustrated embodiment, an effective in the direction of relaxation of the control spring 60 control surface (120 in FIG. 2 ) is missing.
  • the pressure in the annular space 30 further, for example, to 110 bar, so the stopper head 138 comes into contact with the stop screw 122, so that the lower limit pressure (minimum bias of the control spring 60) is set.
  • This minimum limit pressure corresponds to in the embodiment according to FIG. 4 corresponding to the area ratio A 1 / A 2 then about 123 bar.
  • the boundary pressure increases linearly in accordance with this area ratio.
  • FIG. 4 illustrated embodiment is in FIG. 5 shown. This symbol is essentially the same as that FIG. 3 wherein the pressure switching stage 56 has no effective in the direction of relaxation of the control spring 60 control surface 120.
  • the illustrated control oil nozzle is as in the embodiment according to the Figures 2 and 3 formed by the nozzle bore 84.
  • FIG. 6 shows a further simplified embodiment of a pressure relief valve according to the invention, in which dispensed with the use of a clamping piston.
  • the basic structure of the valve is identical to that with reference to the guide and the structure of the pilot valve cone 100 FIG. 2 described embodiment, so that in terms of the description of the main stage 70 with the valve spool 76, the compression spring 80 and the Nachsaugring 88 and with respect to the seat body 94 and screwed into the housing 74 of the main stage 70 pilot housing 96 to the comments on FIG. 2 is referenced.
  • the outer contour of the pilot valve cone 100 also corresponds to the in FIG.
  • the two limit pressures are determined by the ratio of the areas A 1 / A 2 .
  • the pressure at the control port X1 and thus also the pressure in the control chamber 148 is approximately zero, so that the end face 146 is not subjected to a control oil pressure - the pilot valve cone 100 becomes thus biased solely by the force of the control spring 60 against its pilot valve seat 98, so that the lower limit pressure is set.
  • both the end face 146 and the limited by the pilot valve seat 98 face area of the pilot valve piston 100 are subjected to the same pressure, so that this pressure at the Area difference A 2 -A 1 is effective and the upper limit pressure is set.
  • FIG. 7 The symbol of the in FIG. 6 shown pressure relief valve 52 is in FIG. 7 shown. Accordingly, in this embodiment, the bias of the control spring 60 is not changed, but only the pressure acting on the pilot control in the opening and closing direction, a change in the pressure at the control terminal X1 always results in a change of the set limit pressure. If this limiting pressure p G set at the pressure limiting valve 52 is applied as a function of the pressure p X1 present at the control port X1 (pressure in the annular space 30), the result is in FIG. 8 continuous line characteristic. Accordingly, in an embodiment according to FIG FIG. 6 (solid line in FIG.
  • the hydraulic control assembly has a differential cylinder with a piston rod side pressure chamber and a bottom pressure chamber, which are connectable via a control valve assembly for actuating the differential cylinder with a pump or a tank.
  • the pressure in a pressure chamber is limited by a pilot-operated pressure relief valve, which is designed with a pressure changeover stage, via which the pressure set on the pressure limiting valve can be lowered in dependence on the pressure in the other of the pressure chambers.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Operation Control Of Excavators (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (16)

  1. Ensemble de commande hydraulique avec un cylindre différentiel (2) présentant un premier espace de pression (28) et un second espace de pression (30) qui peuvent être reliés par un ensemble de soupape de commande (4, 38), pour l'actionnement du cylindre différentiel (2), à une pompe ou un réservoir, sachant que l'ensemble de soupape de commande (4, 38) possède une soupape à voie (4) réglable en permanence, réalisant un obturateur de dosage (5) variable, caractérisé par une soupape de limitation de pression (52) précommandée disposée sur une conduite montante (6) entre la soupape à voie (4) réglable en permanence et le cylindre différentiel (2) pour limiter la pression dans l'un des espaces de pression (28), sachant qu'une surface de commande (124, 146 ; A1) est présente dans un gradin de précommande (72) de la soupape de limitation de pression (52), laquelle est sollicitée par la pression de l'autre espace de pression (30), et sachant que la sortie de la soupape de limitation de pression (52) précommandée est reliée à un canal de réservoir (T).
  2. Ensemble de commande hydraulique selon la revendication 1, sachant que l'espace de pression cité en premier est un espace cylindrique (28) côté fond et l'autre espace de pression est un espace annulaire (30) côté tige de piston.
  3. Ensemble de commande hydraulique selon la revendication 2, sachant que les deux espaces de pression (28, 30) peuvent être reliés l'un à l'autre en couplage différentiel par l'ensemble de soupape de commande (4, 38) pour la sortie du cylindre différentiel (2).
  4. Ensemble de commande hydraulique selon l'une quelconque des revendications précédentes, sachant que le gradin de précommande possède un piston de serrage (58) sollicité par un ressort de commande (60), lequel est sollicité par la pression de l'autre espace de pression (30) en vue de l'augmentation de la précontrainte de ressort.
  5. Ensemble de commande hydraulique selon la revendication 4, sachant qu'une surface de commande (120) relativement plus petite du piston de serrage (58) est sollicitée par la pression de l'espace de pression cité en premier (28) en vue de la décharge du ressort de commande (60).
  6. Ensemble de commande hydraulique selon la revendication 5, sachant que le rapport de surface (A1/A2) entre la surface de commande (124, 146) du piston de serrage (58) et la surface active du siège de soupape de précommande (98) est inférieur à 4, de préférence inférieur à 1,5.
  7. Ensemble de commande hydraulique selon la revendication 5 ou 6, sachant qu'un piston de précommande (100) de la soupape de limitation de pression (52) est pourvu d'un canal longitudinal (116) qui guide de l'huile de commande d'un espace de ressort (110) d'un gradin principal (70) à une surface de commande plus petite (120).
  8. Ensemble de commande hydraulique selon la revendication 7, sachant que le piston de précommande (100) présente une saillie (111) qui plonge de manière étanche dans un évidement (112) du piston de serrage (58), dont la surface frontale réalise la surface de commande plus petite (120).
  9. Ensemble de commande hydraulique selon l'une quelconque des revendications 1 à 3, sachant que la surface de commande (146) est réalisée sur une saillie (111) d'un piston de précommande (100) de telle manière que la pression de l'autre espace de pression (30) agisse dans le sens de fermeture sur le piston de précommande (100).
  10. Ensemble de commande hydraulique selon la revendication 9, sachant que la saillie (111) traverse un espace de ressort (93) du gradin de précommande et plonge dans un espace de commande (148) sollicité par la pression de l'autre espace de pression (30).
  11. Ensemble de commande hydraulique selon l'une quelconque des revendications précédentes, sachant que la soupape de limitation de pression (52) précommandée possède une ouverture de secours pouvant être actionnée à la main.
  12. Ensemble de commande hydraulique selon l'une quelconque des revendications précédentes, sachant qu'une balance de pression (38) appartenant à l'ensemble de commande hydraulique est montée en aval de l'obturateur de dosage (5) variable, laquelle est sollicitée dans le sens d'ouverture par la pression après l'obturateur de dosage (5) et dans le sens de fermeture par la pression de charge maximale.
  13. Ensemble de commande hydraulique selon la revendication 12, avec une pompe, dont le débit de refoulement peut être réglé en fonction de la pression de charge maximale de sorte qu'une pression de pompage soit supérieure à la pression de charge maximale d'une certaine différence de pression.
  14. Soupape de limitation de pression pour un ensemble de commande selon l'une quelconque des revendications précédentes, avec un raccord d'entrée (P) et un raccord de sortie (T) ainsi qu'un gradin principal (70), un gradin de précommande (72) possédant un piston de serrage (58) qui agit sur un ressort de commande (60) d'un cône de soupape de précommande (100), caractérisée en ce que le piston de serrage (58) présente une surface de commande plus grande (124) qui peut être sollicitée par une pression de commande en vue de l'augmentation de la précontrainte de ressort par un raccord de commande (X1), et sachant qu'une surface de commande plus petite (120) du piston de serrage (58) est sollicitée par la pression sur le raccord d'entrée (P) en vue de la réduction de la précontrainte de ressort de commande.
  15. Soupape de limitation de pression pour un ensemble de commande selon l'une quelconque des revendications précédentes 1 à 13, avec un raccord d'entrée (P) et un raccord de sortie (T) ainsi qu'un gradin principal (70), un gradin de précommande (72), caractérisée en ce qu'un cône de soupape de précommande (100) précontraint par ressort du gradin de précommande (72) présente une surface de commande A1 sollicitée par une pression de commande (X1) dans le sens de fermeture et une surface de commande A2 active dans le sens d'ouverture, sollicitée par la pression sur le raccord d'entrée (P), laquelle est plus grande que la surface de commande A1 sollicitée dans le sens de fermeture.
  16. Soupape de limitation de pression selon la revendication 15, sachant que le rapport A1/A2 de la surface de commande est ≤ 4, de préférence 1 < A1/A2 < 1,5.
EP05755620A 2004-07-22 2005-06-23 Ensemble de commande hydraulique Not-in-force EP1781952B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004035632 2004-07-22
DE102005022275A DE102005022275A1 (de) 2004-07-22 2005-05-10 Hydraulische Steueranordnung
PCT/EP2005/006826 WO2006010419A1 (fr) 2004-07-22 2005-06-23 Ensemble de commande hydraulique

Publications (2)

Publication Number Publication Date
EP1781952A1 EP1781952A1 (fr) 2007-05-09
EP1781952B1 true EP1781952B1 (fr) 2011-09-07

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Family Applications (1)

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EP05755620A Not-in-force EP1781952B1 (fr) 2004-07-22 2005-06-23 Ensemble de commande hydraulique

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US (1) US20070245889A1 (fr)
EP (1) EP1781952B1 (fr)
AT (1) ATE523697T1 (fr)
DE (1) DE102005022275A1 (fr)
WO (1) WO2006010419A1 (fr)

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SE534272C2 (sv) * 2009-06-18 2011-06-28 Kurt Palmloef Säkerhetsventil
ITTO20100190A1 (it) * 2010-03-12 2011-09-13 Cnh Italia Spa Sistema idraulico
US9127437B2 (en) 2010-12-15 2015-09-08 Caterpillar Inc. Flow regeneration hydraulic circuit
CN102182715B (zh) * 2011-05-20 2012-11-14 中联重科股份有限公司 液压控制系统及其液压控制模块及具有该系统的工程机械
CH705123A1 (de) * 2011-06-15 2012-12-31 Liebherr Machines Bulle Sa Druckbegrenzungsventil.
CN103547811B (zh) 2012-04-03 2016-08-17 博世力士乐株式会社 液压回路
US9790964B2 (en) 2014-09-25 2017-10-17 Cnh Industrial America Llc Hydraulic system
US9708796B2 (en) 2014-09-25 2017-07-18 Cnh Industrial America Llc Hydraulic valve
EP3354905B1 (fr) * 2015-09-25 2020-09-02 KYB Corporation Dispositif de commande de pression de fluide
AU2016277732B2 (en) * 2016-12-23 2023-11-02 Draeger Australia Pty Ltd Breathing apparatus filling device
US11583455B2 (en) 2019-10-28 2023-02-21 Stryker Corporation Hydraulic valve and system
CN111577698B (zh) * 2020-05-27 2022-06-17 三一汽车起重机械有限公司 缓冲阀、回转液压系统及起重机
JP2023104377A (ja) 2022-01-17 2023-07-28 川崎重工業株式会社 リリーフ弁

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US3160076A (en) 1961-12-14 1964-12-08 Parker Hannifin Corp Fluid system and relief valve assembly therefor
JPS5730483Y2 (fr) 1976-06-10 1982-07-05
DE3813020C2 (de) * 1988-04-19 1996-12-19 Bosch Gmbh Robert Vorrichtung zur Vorschubsteuerung einer hydraulischen Stelleinrichtung
DE19524900C2 (de) * 1995-07-08 2000-12-28 Mannesmann Rexroth Ag Vorgesteuertes Druckbegrenzungsventil
US6318079B1 (en) * 2000-08-08 2001-11-20 Husco International, Inc. Hydraulic control valve system with pressure compensated flow control
DE10062428A1 (de) 2000-12-14 2002-06-20 Mannesmann Rexroth Ag Vorgesteuertes Druck-Einspeiseventil
JP2003185042A (ja) * 2001-12-17 2003-07-03 Shin Caterpillar Mitsubishi Ltd ラインリリーフ弁

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DE102005022275A1 (de) 2006-02-16
WO2006010419A1 (fr) 2006-02-02
ATE523697T1 (de) 2011-09-15
EP1781952A1 (fr) 2007-05-09
US20070245889A1 (en) 2007-10-25

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