EP1170510A2 - Agencement de contrôle hydraulique pour alimenter en fluide sous pression de préférence plusieurs utilisateurs hydrauliques - Google Patents

Agencement de contrôle hydraulique pour alimenter en fluide sous pression de préférence plusieurs utilisateurs hydrauliques Download PDF

Info

Publication number
EP1170510A2
EP1170510A2 EP01110563A EP01110563A EP1170510A2 EP 1170510 A2 EP1170510 A2 EP 1170510A2 EP 01110563 A EP01110563 A EP 01110563A EP 01110563 A EP01110563 A EP 01110563A EP 1170510 A2 EP1170510 A2 EP 1170510A2
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
piston
line
hydraulic
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
EP01110563A
Other languages
German (de)
English (en)
Other versions
EP1170510A3 (fr
EP1170510B1 (fr
Inventor
Peter BÜTTNER
Tatu Miikkulainen
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
Bosch Rexroth AG
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
Priority claimed from DE10035575A external-priority patent/DE10035575A1/de
Application filed by Mannesmann Rexroth AG, Bosch Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP1170510A2 publication Critical patent/EP1170510A2/fr
Publication of EP1170510A3 publication Critical patent/EP1170510A3/fr
Application granted granted Critical
Publication of EP1170510B1 publication Critical patent/EP1170510B1/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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/047—Preventing foaming, churning or cavitation
    • 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
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • 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
    • F15B2211/329—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
    • F15B2211/51—Pressure control characterised by the positions of the valve element
    • F15B2211/513—Pressure control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source 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
    • F15B2211/515—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
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means
    • 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
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • 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
    • F15B2211/65—Methods of control of the load sensing 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
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the invention relates to a hydraulic control arrangement, with which preferably several hydraulic consumers are supplied with pressure medium and which the Features from the preamble of claim 1.
  • a hydraulic control arrangement is one after the load-sensing Principle in which a variable pump depending on the highest load pressure actuated hydraulic consumer is set so that the pump pressure around a certain, preferably in the range between 10 bar and 25 bar pressure difference ⁇ p is above the highest load pressure.
  • the hydraulic one The pressure medium flows through consumers via adjustable, usually through Control orifices on the control pistons of the directional control valves, between an inlet line from the variable displacement pump and the hydraulic Consumers are arranged.
  • variable pump delivered pressure medium quantity independent of the load pressures of the hydraulic Consumers via the metering orifices a certain one, smaller than ⁇ p Pressure difference exists, so that the flowing to a hydraulic consumer Pressure medium quantity only from the opening cross section of the respective metering orifice depends. If a metering orifice is opened further, more pressure medium must be added flow over them to produce the determined pressure difference.
  • the variable displacement pump is adjusted so that it delivers the required amount of pressure medium. you therefore speaks of a demand flow control.
  • a load-sensing hydraulic control arrangement is known from EP 0 566 449 A1, in which the individual pressure compensators are connected downstream of the metering orifices.
  • the pressure compensators are in the opening direction by the pressure after the respective Orifice plate and in the closing direction of one in a rear control room applied control pressure, which is usually the highest Load pressure of all hydraulic consumers supplied by the same hydraulic pump equivalent. If several hydraulic consumers are operated simultaneously the metering orifices are opened so far that the from to The amount of pressure medium delivered to the adjusted hydraulic pump is smaller than that total amount of pressure medium required, the individual hydraulic Amounts of pressure medium flowing to consumers regardless of the respective Load pressure of the hydraulic consumers reduced proportionally.
  • LUDV control load-independent flow distribution
  • the highest load pressure sensed and by the hydraulic pump by varying the amount of pressure medium delivered a by a certain pressure difference ⁇ p above the highest load pressure LUDV control is a special case of a load-sensing or load-sensing control (LS control).
  • a so-called preload valve is arranged in the drain line, through that in the section of the drain line upstream of the bias valve , a preload pressure should be maintained that is in the range of 10 bar can lie.
  • a check valve is arranged leading to the consumer line opens.
  • the check valve can also be equipped with a pressure relief valve be summarized.
  • the provision of the preload valve and the check valve ensures that that with a negative load acting on the differential cylinder, i.e. a load, which generates a force on the differential cylinder, which in the by the position of the Directional valve directed direction of movement of the differential cylinder is, the pressure medium displaced from the first pressure chamber in addition to that of pumped and via the metering orifice of the directional valve and, if necessary an individual pressure compensator flowing fluid in the second pressure chamber of the differential cylinder is supplied.
  • This is intended for the components harmful cavitation in the second pressure chamber of the controller, which complicates the control Differential cylinders can be avoided.
  • the known control arrangement under special circumstances, e.g. B for piston rods with a particularly large diameter in relation to the diameter of the Piston or cavitation can occur with particularly heavy loads.
  • the invention is therefore based on the objective of a hydraulic control arrangement, which has the features from the preamble of claim 1, to develop further so that the risk of cavitation is further reduced.
  • valve means are available via the pressure medium the supply line, i.e. pressure medium delivered by the variable displacement pump, into the section the drain line in which a preload pressure is to be maintained, is feedable if in the section the pressure to a below the bias pressure value falls.
  • a hydraulic Control arrangement thus comes from the first pressure chamber of the differential cylinder displaced pressure medium not only one promoted by the variable pump additional amount of pressure medium through the opening cross section of the Orifice plate and the presence of an individual pressure compensator or in any case low signal of a load pressure to the variable pump Pressure difference over the metering orifice is determined to the second pressure chamber.
  • valve means between the inlet line and the outlet line and via the check valve to the second pressure chamber of the differential cylinder.
  • the opening cross section the valve means and the check valve can be made very large become.
  • the full pump pressure is available without throttling using an individual pressure compensator available as a drive for the pressure medium flow.
  • valve means according to claim 2 by an additional existing 2-way feed valve to the preload valve.
  • valve means comprise a pressure reducing valve with a valve piston which in the Meaning of closing the fluidic connection between the feed line and the section of the drain pipe from the pressure in this section and in the sense opening of the fluidic connection is acted upon by a spring.
  • valve means in principle, it is conceivable for the preload valve and the one between the inlet line and the drain line arranged valve means to a certain one Pre-set 3-way pressure control valve, at the control outlet the section of the drain pipe to be prestressed, at its pressure connection, the inlet line and at its tank connection, the Tank leading section of the drain line is connected.
  • a preload valve already proven in practice is possible if, as in claim 2 specified, a separate feed valve is used, the is then designed according to claim 4 as a 2-way pressure reducing valve. This is set to a pressure that is less than the preload pressure.
  • Directional valve disks are from data sheet RD 64 282 / 10.99 from the applicant known from LS control blocks, in which two parallel to each other Bores of the disc of the control piston of the directional valve, with which the direction of movement and the speed of a hydraulic consumer are controllable, and the control piston of an individual pressure compensator housed are.
  • This control piston has a certain outside diameter and is in a certain one Way with piston collars, a piston neck and a stop pin and with one from the outer surface of the piston neck through it its end faces leading fluid path and is supported by one of the stop pins surrounding compression spring, the pressure equivalent at the given outer diameter of the control piston is about 10 bar.
  • the 2-way pressure reducing valve uses a piston and spring assembly that the in proven in practice and of their design with regard to flow rate and Corresponding spring force suitable assembly.
  • Figure 1 shows the embodiment of the hydraulic control arrangement
  • Figure 2 shows a valve disc partially in section through the built-in 2-way pressure reducing valve.
  • a control block 7 contains an input element 8, an end plate 9 and in between two directional valve sections 10 and 11, each of which has a directional control valve 12 or 13 with an inlet chamber 14, which can flow from a hydraulic pump 18 supplied pressure medium, one Drain chamber 15, from which pressure medium can drain to a tank 19, and two Has consumer chambers 16 and 17, the consumer lines 20, 21st with a double-acting hydraulic consumer, namely with a differential cylinder 22 and 23 are connected.
  • These have a rod-side, annular, first pressure chamber 24, from which a consumer line 21 to a Consumer chamber 17 leads, and a rod-side, circular cylindrical, second pressure chamber 25, from which a consumer line 20 to a consumer chamber 16 leads.
  • the directional control valve 12 has a control piston 30 and the directional control valve 13 has a control piston 31.
  • Both control pistons 30 and 31 are from a central position in which the Inlet chamber, the outlet chamber and the two consumer chambers against each other are locked in opposite directions in working positions adjustable in the between the inlet chamber 14 and the consumer chamber 16th or the consumer chamber 17, not shown in detail, in its opening cross-section on the size of the displacement of the control piston from its central position dependent metering orifice is open.
  • the control piston is adjusted the consumer chamber is in one direction for both directional valve sections 16 via a likewise dependent on the displacement path of the control piston Opening cross section connected to the drain chamber 15.
  • the Control piston 31 of the directional control valve 13 is a so-called regeneration piston, over which when moving in the opposite direction Consumer chamber 17 via a drain panel and the metering panel with the Consumer chamber 16 is connected.
  • each directional control valve 12 and 13 is connected upstream an individual pressure compensator 32, on the control piston of which two control rooms 33 and 34 adjoin.
  • the control room 33 is equipped with a load reporting chamber 35
  • Directional control valve 12, 13 and the control chamber 34 are connected to the inlet chamber 14.
  • the load reporting chamber 35 is in the central position of the control piston 30, 31 Tank relieved and in a side working position with the consumer chamber connected, which is supplied via the metering orifice oil.
  • the control piston the pressure compensator 32 is in the opening direction by a compression spring 36 and the pressure prevailing in the control chamber 33 and in the closing direction from that in the Control room 34 prevailing pressure.
  • the highest in each case is via a shuttle valve chain with shuttle valves 37 pressure present in a control chamber 33, that is to say the highest load pressure in each case given an output LS in the input element 8 of the control block 7 and over a load signaling line 38 is reported to an LS pump controller 39 which controls the variable displacement pump 18 each set so that in one outgoing from the variable displacement pump 18 Section of an inlet line 40, via which the inlet chambers 14 Directional control valves 12 and 13 hydraulic oil can be supplied, a pump pressure that by a certain pressure difference ⁇ p above the reported highest load pressure lies.
  • the pressure difference is usually in the range between 10 bar and 25 bar. In the present case, a pressure difference of 20 bar may be set. Will not Reported load pressure, therefore arises in the feed line 40 including the Inlet channel 41 a pressure (stand-by pressure) ⁇ p of 20 bar.
  • the inlet line 40 is exposed to an input P of the input element 8 within the control block 7 as a straight inlet channel 41, which through the directional valve sections 10 and 11 goes through into the end plate 9. With him they are Inputs of the individual pressure compensators 32 connected.
  • a flow channel 42 also passes through the directional valve sections, which in the end plate 9 and extends into the input element 8 and part of a drain flow path 43, the hydraulic oil from the drain chambers 15 of the Directional control valves 12 and 13 can flow back to the tank 19 and also in the one Tank connection T of the input element 8 is.
  • the control piston is a so-called regeneration flask
  • the pressure limiting function is fulfilled the valve 45 for the consumer line 20, in which there is pressure to one certain pressure difference above the pressure in the drain channel is limited.
  • valve 45 acts as a check valve opening towards the consumer line, So can pressure fluid flow from the drain channel to the consumer line when the Pressure in the consumer line is lower than in the drain channel, and blocks when the pressure in the consumer line is higher than in the drain channel.
  • Further pressure limiting and feed valves 46 are located between each consumer line 21 and the drain channel 42.
  • the two directional control valves 12 and 13 can each be actuated electro-hydraulically, for which purpose in each directional valve section 10 or 11 two electromagnetically proportional adjustable Pilot valves 50 are integrated.
  • a valve 50 In the rest position of a valve 50 is an assigned control chamber on the control piston 30 of a directional control valve 11, 12 a leak oil channel 51, which leads through the directional valve sections 10 and 11, relieved.
  • a control room becomes a control pressure line also passed through the directional valve section 10 and 11 52 connected.
  • the control oil is supplied via a pressure reducing valve 53 is installed in the end plate 9, through the two directional valve sections 10 and 11 through and into the end plate 9 introduced inlet channel 41.
  • the pressure reducing valve 53 is e.g. set to a control pressure of 30 bar.
  • the leak oil channel 51 is connected to a connection Y of the end plate 9 Line 54 connected directly to the tank 19 such that in the Leakage oil channel the same pressure as in tank 19.
  • a pressure relief valve 60 is installed, for the latter Input of the drain channel 42 leads and its output to the tank connection T of the input element is connected. Since the pressure relief valve on a large flow rate must be designed, it is preferably a pilot controlled Valve.
  • the spring chamber in which the counterforce to the compressive force is generated Compression spring 61 is located through a bore 62 of the input element connected to the leak oil channel 51 so that the tank pressure level remains constant is guaranteed in the spring chamber.
  • the pressure relief valve 60 has the function in the outlet channel 42 upstream of it a constant after setting Maintain pressure, also known as preload pressure. Therefore, the pressure relief valve can also be called a preload valve.
  • the preload pressure is relatively small and is in other applications Range from 5 bar to 10 bar, but can also be set to 15 bar.
  • valve can be used, which is called MHDBV in the data sheet RD 64 642 / 12.97 of the applicant is shown in more detail. In the present case, a preload pressure between 8 bar and 12 bar has proven to be favorable.
  • a 2-way pressure reducing valve 70 is also installed in the input element 8, which is with its pressure input on the inlet channel 41 and with its Outlet in which the valve tries to maintain a certain pressure, upstream of the preload valve 60 with the drain fluid path 43, that is to say with the drain channel 42 is connected.
  • the pressure reducing valve has a valve piston 71 which in the sense of increasing the opening cross section of the valve from one Compression spring 72 and in the sense of a reduction in the opening cross section from at the outlet of the valve, ie acted upon by the pressure prevailing in the outlet channel 42 is.
  • the one set on the pressure reducing valve and to be maintained at the outlet Pressure is about 2 bar below that set on the preload valve 60 Biasing pressure.
  • FIG. 2 out Structural details of the pressure reducing valve 70 are shown in more detail in FIG. 2 out. Then is in a disc-shaped housing 73 of the input element 8 a blind bore 74 is introduced from a narrow side, through a screw plug 75 is closed. The blind bore 74 is closed at two points axially spaced apart annular chambers 76 and 77, of which the annular chamber 76 passes through the inlet channel 41 and the annular chamber 77 is connected to the drain channel 42. Between the bottom of the blind hole and the screw plug 75 is the valve piston located in the blind bore 71 axially displaceable.
  • the ring chamber 76 of the two ring chambers closer to the screw plug 75 76 and 77 is at a distance from the inner end of the screw plug.
  • the valve piston 71 has a further piston collar 83. This separates a pressure chamber 85 between the screw plug 75 and the face 86 of the valve piston facing this.
  • the piston collar 83 is through a further turn 84 of the valve piston between it and the Piston collar 78 was created.
  • This twist has nothing to do with the control function of the valve piston 71, but only contributes to a large flow cross section for the pressure medium in the area of the annular chamber 76. Without the twist 84 would then only be a piston collar between the piston neck 80 and the End face 86 of the valve piston 71 is present.
  • the pressure space 85 between the valve piston 71 and the screw plug 75 is through a bore of the valve piston, one of the end face 86 axially introduced blind bore 87 and a continuous transverse bore 88 in the piston neck 80 comprises, fluidly connected to the annular groove 81.
  • a stop pin is located on the side of the piston collar 79 facing away from the annular groove 81 89 from which has a smaller diameter than the blind bore 74 and the valve piston 71 which is present when the valve piston 71 abuts the screw plug 75 clear distance from the bottom of the blind hole the possible displacement of the valve piston clarified.
  • the space 90 between the floor of the The blind bore 74 and the piston collar 79 is fluidically by this from the Annular chamber 77 is separated and is also in the bottom of the blind hole opening bore 62 connected to the leak oil channel 51. So there is in the room 90 tank pressure.
  • the compression spring 72 is received by this space 90, which is at the bottom of the blind bore 74 and, overlapping the stop pin and is used as a guide, is supported on the piston collar 79 of the valve piston 71.
  • the preload of the compression spring 72 can be varied by means of washers 92 become.
  • FIG. 2 also shows parts of the valves 60 and 60 protruding from the housing 73 65 and the tank connection T can be seen.
  • the differential cylinders 22 and 23 when the directional control valves 12 are actuated or 13 operated with a pushing load in the sense of extending the piston rod, is the pressure in the consumer line 20 in the flow above pre-tension pressure prevailing in the drain line, so that the non-return function the valve 45 does not respond and the preload pressure set on the valve 60 in the drain line is maintained.
  • the preload pressure is above the ring chamber 77, the annular groove 81 and the bores 87 and 88 in the pressure chamber 85 and holds the valve piston in a position compared to the position shown in FIG to the left shifted position, in which the piston collar 78 the control edge of the Has passed over the annular chamber 76 and the outlet line 42 from the inlet line 41 keeps separate.
  • the directional valve 12 When operating the differential cylinders 22 and 23 with pulling loads and in terms of extending the piston rod, it can be determined whether the directional valve 12 is now the control piston 30 or the directional control valve 13 with the as a regeneration piston trained control piston 31 is actuated, come to the fact that the pressure in the Consumer line 20 below the preload pressure set on the preload valve 60 and further drops below the pressure set on the pressure reducing valve 70. In such a case, the corresponding one or more flows as check valves Acting valves 45 pressure medium from the drain channel 42 in the corresponding Consumer line 20.
  • the pressure reducing valve 70 opens and leads the drain channel from the variable displacement pump at least under standby pressure conveyed pressure medium, which in addition to from the pressure chambers 24 of the differential cylinder displaced return oil into the consumer lines 20 and the pressure chambers 25 arrives.
  • this return oil passes through the drain chamber 15 in the drain channel 42 and from there depending on which hydraulic Consumer under which operating conditions are operated, via a valve 45 in one, the other or both consumer lines 20.
  • the directional control valve 12 also flows through the pressure compensator 32 and the metering orifice a pressure medium quantity determined by its opening cross section from the inlet channel 41 to the pressure chamber 25 of the differential cylinder 22.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
EP01110563A 2000-07-08 2001-04-30 Agencement de contrôle hydraulique pour alimenter en fluide sous pression de préférence plusieurs utilisateurs hydrauliques Expired - Lifetime EP1170510B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10033372 2000-07-08
DE10033372 2000-07-08
DE10035575 2000-07-21
DE10035575A DE10035575A1 (de) 2000-07-08 2000-07-21 Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern

Publications (3)

Publication Number Publication Date
EP1170510A2 true EP1170510A2 (fr) 2002-01-09
EP1170510A3 EP1170510A3 (fr) 2003-10-29
EP1170510B1 EP1170510B1 (fr) 2005-08-17

Family

ID=26006326

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01110563A Expired - Lifetime EP1170510B1 (fr) 2000-07-08 2001-04-30 Agencement de contrôle hydraulique pour alimenter en fluide sous pression de préférence plusieurs utilisateurs hydrauliques

Country Status (3)

Country Link
EP (1) EP1170510B1 (fr)
AT (1) ATE302345T1 (fr)
ES (1) ES2244517T3 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007121873A1 (fr) * 2006-04-21 2007-11-01 Robert Bosch Gmbh Dispositif de commande hydraulique
WO2008083772A1 (fr) * 2006-12-22 2008-07-17 Hydac Filtertechnik Gmbh Dispositif de commande pour des consommateurs hydrauliques
CN101646874B (zh) * 2007-02-16 2013-07-24 罗伯特博世有限公司 包括用于温度控制油槽的控制块
US8499552B2 (en) 2007-06-26 2013-08-06 Robert Bosch Gmbh Method and hydraulic control system for supplying pressure medium to at least one hydraulic consumer
US8671824B2 (en) 2007-06-26 2014-03-18 Robert Bosch Gmbh Hydraulic control system
CN104564866A (zh) * 2013-10-15 2015-04-29 罗伯特·博世有限公司 具有阀装置的阀组
US11841716B2 (en) 2020-12-28 2023-12-12 Danfoss Power Solutions (Zhejiang) Co. Ltd. Load-sensing multi-way valve work section

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015203404A1 (de) * 2015-02-26 2016-09-01 Robert Bosch Gmbh Hydraulische Steueranordnung zur Druckmittelversorgung eines hydraulischen Aktuators

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0566449A1 (fr) 1992-04-06 1993-10-20 Rexroth-Sigma Distributeur hydraulique combinant la compensation de pression et la sélection de pression maximale
DE19714141A1 (de) 1997-04-05 1998-10-08 Mannesmann Rexroth Ag Hydraulische Steueranordnung

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3323363A1 (de) * 1983-06-29 1985-01-10 Mannesmann Rexroth GmbH, 8770 Lohr Vorgesteuertes druckreduzierventil
JPS61165432A (ja) * 1985-01-17 1986-07-26 Hitachi Constr Mach Co Ltd 建設機械の慣性質量駆動用油圧回路
JP2600009B2 (ja) * 1990-04-25 1997-04-16 株式会社神戸製鋼所 クレーンの旋回制御装置
FR2744497B1 (fr) * 1996-02-07 1998-04-03 Rexroth Sigma Dispositif de distribution hydraulique multiple
JPH09317879A (ja) * 1996-05-27 1997-12-12 Komatsu Ltd 油圧駆動装置の背圧制御回路
DE19640100B4 (de) * 1996-09-28 2005-07-14 Sauer-Danfoss Holding Aps Hydraulisches System
US6422804B1 (en) * 2000-02-18 2002-07-23 Deere & Company Inertia load dampening hydraulic system

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0566449A1 (fr) 1992-04-06 1993-10-20 Rexroth-Sigma Distributeur hydraulique combinant la compensation de pression et la sélection de pression maximale
DE19714141A1 (de) 1997-04-05 1998-10-08 Mannesmann Rexroth Ag Hydraulische Steueranordnung

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007121873A1 (fr) * 2006-04-21 2007-11-01 Robert Bosch Gmbh Dispositif de commande hydraulique
US8281583B2 (en) 2006-04-21 2012-10-09 Robert Bosch Gmbh Hydraulic control assembly
WO2008083772A1 (fr) * 2006-12-22 2008-07-17 Hydac Filtertechnik Gmbh Dispositif de commande pour des consommateurs hydrauliques
EP2441967A1 (fr) * 2006-12-22 2012-04-18 Hydac Filtertechnik GmbH Dispositif de commande pour consommateurs hydrauliques
EP2441966A1 (fr) * 2006-12-22 2012-04-18 Hydac Filtertechnik GmbH Dispositif de commande pour consommateurs hydrauliques
US8443827B2 (en) 2006-12-22 2013-05-21 Hydac Filtertechnik Gmbh Controlling device for hydraulic consumers
CN101646874B (zh) * 2007-02-16 2013-07-24 罗伯特博世有限公司 包括用于温度控制油槽的控制块
US8499552B2 (en) 2007-06-26 2013-08-06 Robert Bosch Gmbh Method and hydraulic control system for supplying pressure medium to at least one hydraulic consumer
US8671824B2 (en) 2007-06-26 2014-03-18 Robert Bosch Gmbh Hydraulic control system
CN104564866A (zh) * 2013-10-15 2015-04-29 罗伯特·博世有限公司 具有阀装置的阀组
US11841716B2 (en) 2020-12-28 2023-12-12 Danfoss Power Solutions (Zhejiang) Co. Ltd. Load-sensing multi-way valve work section

Also Published As

Publication number Publication date
EP1170510A3 (fr) 2003-10-29
ATE302345T1 (de) 2005-09-15
EP1170510B1 (fr) 2005-08-17
ES2244517T3 (es) 2005-12-16

Similar Documents

Publication Publication Date Title
EP0760908B1 (fr) Systeme de commande pour au moins deux consommateurs hydrauliques
DE60105849T2 (de) Hydraulisches wegeventilsystem mit druckwaagen
EP2013487B1 (fr) Dispositif de commande hydraulique
EP1701042B1 (fr) Commande hydraulique
EP1710446B1 (fr) Commande hydraulique et bloc de commande
WO2000046513A1 (fr) Dispositif de commande pour au moins deux consommateurs hydrauliques, et soupape a pression differentielle correspondante
DE102012220863A1 (de) Steueranordnung
DE19855187A1 (de) Verfahren und Steueranordnung zur Ansteuerung eines hydraulischen Verbrauchers
EP2636908A2 (fr) Agencement de commande
EP2059683B1 (fr) Système de commande ls
EP1200743B1 (fr) Dispositif de commande hydraulique destine a l'alimentation en agent de pression, reglee par detection de charge, de preference de plusieurs consommateurs hydrauliques
WO2001002736A1 (fr) Dispositif de commande hydraulique destine a alimenter, de preference, plusieurs consommateurs hydrauliques en agent de pression
DE102007028864A1 (de) Hydraulische Steueranordnung
EP1170510B1 (fr) Agencement de contrôle hydraulique pour alimenter en fluide sous pression de préférence plusieurs utilisateurs hydrauliques
WO2003087585A1 (fr) Systeme de commande hydraulique faisant appel au principe de la sensibilite de charge
WO2016091528A1 (fr) Agencement de soupapes hydraulique, bloc de soupapes hydraulique ayant un tel agencement de soupapes, et mécanisme d'entraînement hydraulique ayant un tel bloc de soupapes hydraulique
EP1629209A1 (fr) Ensemble commande hydraulique
DE19802430A1 (de) Hydraulisches System zum Betreiben eines reversierbaren hydraulischen Verbrauchers
DE10035575A1 (de) Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern
DE19603899A1 (de) Hydraulische Steuervorrichtung zur Druckmittelversorgung mehrerer hydraulischer Verbraucher
EP2891805A2 (fr) Système de commande et soupape de commande pour un tel système de commande
DE19715021A1 (de) Hydraulische Steueranordnung zur Druckmittelversorgung eines ersten und eines zweiten hydraulischen Verbrauchers
DE10119276A1 (de) Hydraulischer Steuerkreis
WO2019134832A1 (fr) Agencement de soupape hydraulique
DE102007026676A1 (de) Hydraulische Steueranordnung zur bedarfstromgeregelten (load-sensing-geregelten) Druckmittelversorgung von mehreren hydraulischen Verbrauchern

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: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: BOSCH REXROTH AG

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

17P Request for examination filed

Effective date: 20040408

17Q First examination report despatched

Effective date: 20040513

AKX Designation fees paid

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

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): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

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

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20050817

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20050817

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20050817

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 50107098

Country of ref document: DE

Date of ref document: 20050922

Kind code of ref document: P

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

Effective date: 20050921

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

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20051117

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20051117

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2244517

Country of ref document: ES

Kind code of ref document: T3

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

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060117

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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

Ref country code: CH

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

Effective date: 20060430

Ref country code: MC

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

Effective date: 20060430

Ref country code: BE

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

Effective date: 20060430

Ref country code: LI

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

Effective date: 20060430

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: 20060518

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

BERE Be: lapsed

Owner name: BOSCH REXROTH A.G.

Effective date: 20060430

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

Ref country code: LU

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

Effective date: 20060430

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

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20050817

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

Ref country code: FR

Payment date: 20120511

Year of fee payment: 12

Ref country code: GB

Payment date: 20120423

Year of fee payment: 12

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

Ref country code: IT

Payment date: 20120426

Year of fee payment: 12

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

Ref country code: ES

Payment date: 20120423

Year of fee payment: 12

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

Ref country code: AT

Payment date: 20120420

Year of fee payment: 12

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 302345

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130430

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

Effective date: 20130430

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: 20130430

Ref country code: AT

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

Effective date: 20130430

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20131231

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: 20130430

Ref country code: IT

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

Effective date: 20130430

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20140609

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: 20130501

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

Ref country code: SE

Payment date: 20150423

Year of fee payment: 15

Ref country code: FI

Payment date: 20150422

Year of fee payment: 15

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

Ref country code: DE

Payment date: 20160628

Year of fee payment: 16

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

Ref country code: FI

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

Effective date: 20160430

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

Ref country code: SE

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

Effective date: 20160501

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50107098

Country of ref document: DE

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

Ref country code: DE

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

Effective date: 20171103