EP1170510B1 - Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern - Google Patents

Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern Download PDF

Info

Publication number
EP1170510B1
EP1170510B1 EP01110563A EP01110563A EP1170510B1 EP 1170510 B1 EP1170510 B1 EP 1170510B1 EP 01110563 A EP01110563 A EP 01110563A EP 01110563 A EP01110563 A EP 01110563A EP 1170510 B1 EP1170510 B1 EP 1170510B1
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.)
Expired - Lifetime
Application number
EP01110563A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1170510A3 (de
EP1170510A2 (de
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
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 Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1170510A2 publication Critical patent/EP1170510A2/de
Publication of EP1170510A3 publication Critical patent/EP1170510A3/de
Application granted granted Critical
Publication of EP1170510B1 publication Critical patent/EP1170510B1/de
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, preferably with the several hydraulic consumers are supplied with pressure medium and the the Features from the preamble of claim 1.
  • a hydraulic control arrangement is such after the load-sensing Principle, in which a variable displacement pump depending on the highest load pressure of the actuated hydraulic consumers are each set so that the pump pressure by a certain, preferably in the range between 10 bar and 25 bar lying pressure difference .DELTA.p is above the highest load pressure.
  • the hydraulic Consumers the pressure medium flows through adjustable, usually by Control grooves realized on the control piston of the directional control valves realized metering, between an outgoing from the variable displacement supply line and the hydraulic Consumers are arranged.
  • variable displacement pump delivered pressure medium quantity independent of the load pressures of the hydraulic Consumers over the Zumeßblenden a certain, compared to ⁇ p smaller Pressure difference is such that the inflowing a hydraulic consumer Quantity of pressure medium only from the opening cross section of the respective Zumeßblende depends. If a Zumeßblende further opened, so must more pressure medium flow over them to produce the specific pressure difference.
  • the variable pump is in each case adjusted so that it supplies the required amount of pressure medium. you Therefore speaks also of a demand flow control.
  • the pressure compensators are in the opening direction of the pressure according to the respective Metering and in the closing direction of a 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.
  • control pressure which is usually the highest Load pressure of all hydraulic consumers supplied by the same hydraulic pump equivalent.
  • LHDV control Because with a LUDV control also the highest load pressure sensed and by the hydraulic pump by the variation of the conveyed pressure medium quantity one by a certain pressure difference Ap over the highest load pressure LHDV control is a special case one load-sensing or load-sensing control (LS control).
  • each pressure medium via a Zumeßbleride with upstream individual pressure compensator flows, in the closing direction only from the pressure in front of the metering aperture and in the opening direction only from Load pressure of the respective hydraulic consumer and of a compression spring is applied, you get no load-independent flow distribution.
  • Such a control is e.g. known from DE 197 14 141 A1.
  • several hydraulic consumers and not enough of the variable displacement pump supplied quantity of pressure medium is here only the last horrinen hydraulic Consumers inflowing pressure fluid reduced.
  • a LUDV control arrangement having the features of the preamble of the claim 1 is known from the data sheet RD 64 284 / 05.99 of the applicant.
  • a so-called bias valve is arranged in the drain line, through the in the section of the drain line upstream of the biasing valve is to be maintained, a bias pressure in the range of 10 bar can lie.
  • a check valve is arranged to the consumer line opens.
  • the check valve can also be equipped with a pressure relief valve be summarized.
  • the differential cylinder By the provision of the biasing valve and the check valve is achieved that at a negative load acting on the differential cylinder, ie a load, the differential cylinder generates a force in the by the position of the Directional valve predetermined direction of movement of the differential cylinder directed is the pressure medium displaced from the first pressure chamber in addition to that of funded the pump and the metering diaphragm of the directional control valve and optionally an individual pressure compensator flowing pressure medium the second pressure chamber the differential cylinder is supplied.
  • a negative load acting on the differential cylinder ie a load
  • the differential cylinder generates a force in the by the position of the Directional valve predetermined direction of movement of the differential cylinder directed is the pressure medium displaced from the first pressure chamber in addition to that of funded the pump and the metering diaphragm of the directional control valve and optionally an individual pressure compensator flowing pressure medium the second pressure chamber the differential cylinder is supplied.
  • the invention is therefore based on the object, a hydraulic control arrangement, having the features of the preamble of claim 1, develop so that the risk of cavitation is further reduced.
  • valve means are present, on the pressure medium the supply line, so promoted by the variable pressure fluid, in the section the drain line in which a bias pressure is to be maintained can be fed, if in the section the pressure on one below the prestressing pressure lying value decreases.
  • Control arrangement thus reaches out of the first pressure chamber of the differential cylinder displaced pressure fluid not only one funded by the variable displacement pump additional amount of pressure medium through the opening cross section of the Zumeßblende and the presence of a pressure compensator or Lack of reporting a load pressure to the variable pump in any case low Pressure difference over the Zumeßblende is determined to the second pressure chamber.
  • valve means between the supply line and the drain line and the check valve the second pressure chamber of the differential cylinder to.
  • the opening cross-section the valve means and the check valve can be made very large become.
  • full pump pressure is available without throttling by an individual pressure compensator as drive for the pressure medium flow available.
  • valve means according to claim 2 by an additional formed to the preload valve existing 2-way feed valve.
  • valve means comprise a pressure reducing valve with a valve piston which in Meaning a closing of the fluidic connection between the supply line and the section of the drain line from the pressure in this section and in the sense opening of the fluidic connection is acted upon by a spring.
  • the biasing valve and between the supply line and the drain line arranged valve means to a specific one Bias pressure adjusted 3-way pressure control valve summarize at whose control output the section of the drain line to be prestressed, at the pressure connection, the supply line and at the tank connection of the Tank leading section of the drain line is connected. It is, however, one better matching to different flow rates and use a proven in practice biasing valve possible if, as in claim 2, 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 bias pressure.
  • a control block 7 is included an input member 8, an end plate 9, and between them two-way 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 promoted pressure medium, a Drain chamber 15, can run from the pressure medium to a tank 19, and two Consumer combs 16 and 17, which via 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 drain chamber and the two consumer chambers against each other are shut off, in opposite directions in working positions adjustable, in between the inlet chamber 14 and the consumer chamber sixteenth or the consumer chamber 17 a non-illustrated, in its opening cross-section on the size of the displacement of the control piston from its center position dependent metering orifice is open.
  • With an adjustment of the control piston in one direction is the consumer chamber at both Wegeventilsetationen 16 via a likewise dependent on the displacement of the control piston Opening cross-section connected to the discharge chamber 15.
  • each directional control valve 12 and 13 is connected upstream in each case an individual pressure compensator 32, at the control piston two control chambers 33 and 34th adjoin.
  • the control chamber 33 is connected to a load reporting chamber 35 of the respective Directional valve 12, 13 and the control chamber 34 connected to the inlet chamber 14.
  • the load reporting chamber 35 is in the middle position of the control piston 30, 31 for Tank relieved and in a lateral working position in each case 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 of a compression spring 36 and of the prevailing in the control chamber 33 pressure and in the closing direction of the im Control chamber 34 applied pressure prevailing.
  • variable displacement pump 18 each set so that in one of the variable displacement 18 outgoing Section of a supply line 40, via the inlet chambers 14 of the Directional valves 12 and 13 hydraulic oil can be fed, a pump pressure setting, the by a certain pressure difference ⁇ p over the reported highest load pressure lies.
  • the pressure difference is usually in the range between 10 bar and 25 bar. In the present case may be set a pressure difference of 20 bar. Will not Load pressure reported, accordingly, in the supply line 40 including the Inlet channel 41 a pressure (stand-by pressure) ⁇ p of 20 bar a.
  • the supply line 40 is composed of an input P of the input element 8 within the control block 7 as a straight inlet channel 41 continues through the directional valve sections 10 and 11 passes through into the end plate 9. With him are the Inputs of the individual pressure compensators 32 connected.
  • valve section in particular also in the directional valve section 11 with the directional control valve 13, the control piston is a so-called regeneration flask, there is a combined Pressure limiting and feed valve 45, which is between the consumer line 20 and the drainage channel 42 is arranged.
  • the pressure limiting function is fulfilled the valve 45 for the consumer line 20, in which it puts pressure on one to a limited certain pressure difference above the pressure in the discharge channel value.
  • valve 45 acts like a non-return valve opening towards the consumer line, So lets pressure medium flow from the flow channel to the consumer line, if the Pressure in the consumer line is lower than in the drain channel, and locks when the pressure in the consumer line is higher than in the discharge channel.
  • Further pressure limiting and feed valves 46 are located between each consumer line 21 and the drainage channel 42.
  • the two-way valves 12 and 13 are each electro-hydraulically actuated, including in each directional valve section 10 and 11 two electromagnetically proportional adjustable Pilot valves 50 are integrated.
  • a valve 50 In the rest position of a valve 50 is an associated control chamber on the control piston 30 of a directional control valve 12, 13 to a leakage oil passage 51 passing through the directional valve sections 10 and 11, relieved.
  • By energizing an electromagnet is a control room with a likewise passed through the directional valve section 10 and 11 control pressure line 52 connected.
  • the control oil is via a pressure reducing valve 53, the is installed in the end plate 9, the through the two-way valve sections 10th and 11 passed through and guided into the end plate 9 inlet channel 41.
  • the pressure reducing valve 53 is e.g. adjusted to a control pressure of 30 bar.
  • the leakage oil passage 51 is connected to a terminal Y of the end plate 9 via a Line 54 connected directly to the tank 19 such that in the Leakage oil channel the same pressure
  • a pressure relief valve 60 is installed, to whose Entrance of the drain passage 42 leads and its output to the tank port 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-operated Valve.
  • the pressure relief valve 60 has the function in the flow channel lying upstream of him a constant after setting To maintain pressure, which is also referred to as biasing pressure. Therefore, you can call the pressure relief valve as a preload valve.
  • the preload pressure is relatively small and is in other applications in the Range from 5 bar to 10 bar, but can also be set to 15 bar.
  • the valve can be used under the name MHDBV in the data sheet RD 64 642 / 12.97 the applicant is shown in more detail. In the present case, a preload pressure between 8 bar and 12 bar has proved to be favorable.
  • a 2-way pressure reducing valve 70 is further installed, which lies with its pressure input to the inlet channel 41 and with his Output in which the valve seeks to maintain a certain pressure, upstream of the biasing valve 60 with the drain fluid path 43, so with the drain passage 42 is connected.
  • the pressure reducing valve has a valve piston 71, the in the sense of increasing the opening cross-section of the valve of a Compression spring 72 and in the sense of a reduction of the opening cross-section of at the outlet of the valve, so acted upon by the pressure prevailing in the flow passage 42 is.
  • the set at the pressure reducing valve and maintained at the output Pressure is about 2 bar below that set at the biasing valve 60 Biasing pressure.
  • the opening cross-section of the valve 70 is the piston collar 78 with fine control grooves 82 provided.
  • the closure screw 75 closer annular chamber 76 of the two annular chambers 76 and 77 has a distance from the inner end of the screw plug.
  • This area of the blind bore 74 of the valve piston 71 has another piston collar 83.
  • the piston collar 83 is by another recess 84 of the valve piston between him and the Piston collar 78 emerged.
  • This recess has nothing to do with the control function to do the valve piston 71, but only contributes to a large flow area for the pressure medium in the region of the annular chamber 76 at. Without the recess 84 would then only a piston collar between the piston neck 80 and the End face 86 of the valve piston 71 is present.
  • the pressure chamber 85 between the valve piston 71 and the screw plug 75th is via 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, fluidly connected to the annular groove 81.
  • a stop pin 89 From the annular groove 81 opposite side of the piston collar 79 is a stop pin 89, which has a smaller diameter than the blind bore 74 and whose present at the closure screw 75 valve piston 71 existing clear distance from the bottom of the blind hole the possible displacement the valve piston illustrates.
  • the compression spring 72 is added, at the bottom of the blind bore 74 and, the stop pin across and as a guide, on the piston collar 79 of the valve piston 71 is supported.
  • washers 92 By washers 92, the bias of the compression spring 72 can be varied become.
  • the differential cylinders 22 and 23 in an actuation of the directional control valves 12th or 13 operated with pressing load in the sense of extension of the piston rod is the pressure in the flow in the consumer line 20 above the prevailing in the discharge line biasing pressure, so that the check function the valves 45 is not responsive and the valve 60 set biasing pressure in the drain is maintained.
  • the preload pressure is above the annular chamber 77, the annular groove 81 and the holes 87 and 88 in the pressure chamber 85 at and holds the valve piston in a position compared to that shown in Figure 2 shifted to the left position, in which the piston collar 78, the control edge of the Has overtravelled ring chamber 76 and the drain line 42 from the feed line 41st keeps separate.
  • the directional control valve 12 with 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 Load line 20 under the bias pressure set on the biasing valve 60 and further drops below the pressure set at the pressure reducing valve 70. In such a case, it flows over the or the corresponding as check valves acting valves 45 pressure fluid from the drain passage 42 into the corresponding Consumer line 20.
  • the pressure reducing valve 70 opens and leads the drainage channel of the variable displacement pump at least under the stand-by pressure promoted pressure fluid, 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 drainage chamber 15 in the drainage channel 42 and from there depending on which hydraulic Consumers are operated under which operating conditions, 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 through the opening cross section certain amount of pressure medium from the inlet channel 41 to the pressure chamber 25 of the differential cylinder 22nd
  • the directional control valve 13 Upon actuation of the directional control valve 13 with regeneration piston can Return oil from the pressure chamber 24 of the differential cylinder 23 only in the pressure chamber 25 get this cylinder. Also, it can work under certain operating conditions be for the differential cylinder 23 that because of the regeneration piston 31, the directional control valve 13 associated pressure compensator closes, so that the Pressure chamber 25 of the cylinder 23 only with the return oil from the pressure chamber 24 of the Cylinder 23 and from the pressure chamber 24 of the possibly actuated cylinder 22 and with via the pressure reducing valve 70 the flow channel flowing pressure medium is filled.

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 Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern Expired - Lifetime EP1170510B1 (de)

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 EP1170510A2 (de) 2002-01-09
EP1170510A3 EP1170510A3 (de) 2003-10-29
EP1170510B1 true EP1170510B1 (de) 2005-08-17

Family

ID=26006326

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01110563A Expired - Lifetime EP1170510B1 (de) 2000-07-08 2001-04-30 Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern

Country Status (3)

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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013220750A1 (de) * 2013-10-15 2015-04-16 Robert Bosch Gmbh Ventilblock mit einer Ventilanordnung
DE102015203404A1 (de) * 2015-02-26 2016-09-01 Robert Bosch Gmbh Hydraulische Steueranordnung zur Druckmittelversorgung eines hydraulischen Aktuators

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006018706A1 (de) * 2006-04-21 2007-10-25 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102006061305B3 (de) 2006-12-22 2008-07-10 Hydac Filtertechnik Gmbh Ansteuereinrichtung für hydraulische Verbraucher
US8789553B2 (en) * 2007-02-16 2014-07-29 Robert Bosch Gmbh Control block comprising an oil channel for temperature control
DE102007029358A1 (de) 2007-06-26 2009-01-02 Robert Bosch Gmbh Verfahren und hydraulische Steueranordnung zur Druckmittelversorgung zumindest eines hydraulischen Verbrauchers
DE102007029355A1 (de) 2007-06-26 2009-01-02 Robert Bosch Gmbh Hydraulische Steueranordnung
DK4019786T3 (da) 2020-12-28 2024-02-05 Danfoss Power Solutions Zhejiang Co Ltd Flervejsbelastningsventilarbejdssektion

Family Cites Families (9)

* 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
FR2689575B1 (fr) 1992-04-06 1994-07-08 Rexroth Sigma Distributeur hydraulique a compensation de pression et une selection de pression maximale pour piloter une pompe et commande hydraulique multiple incluant de tels distributeurs.
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
DE19714141A1 (de) 1997-04-05 1998-10-08 Mannesmann Rexroth Ag Hydraulische Steueranordnung
US6422804B1 (en) * 2000-02-18 2002-07-23 Deere & Company Inertia load dampening hydraulic system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013220750A1 (de) * 2013-10-15 2015-04-16 Robert Bosch Gmbh Ventilblock mit einer Ventilanordnung
US9874884B2 (en) 2013-10-15 2018-01-23 Robert Bosch Gmbh Valve block having a valve assembly
DE102015203404A1 (de) * 2015-02-26 2016-09-01 Robert Bosch Gmbh Hydraulische Steueranordnung zur Druckmittelversorgung eines hydraulischen Aktuators

Also Published As

Publication number Publication date
ATE302345T1 (de) 2005-09-15
ES2244517T3 (es) 2005-12-16
EP1170510A3 (de) 2003-10-29
EP1170510A2 (de) 2002-01-09

Similar Documents

Publication Publication Date Title
EP0760908B1 (de) Steueranordnung für wenigstens zwei hydraulische verbraucher
EP1149246B1 (de) Steueranordnung für wenigstens zwei hydraulische verbraucher und druckdifferenzventil dafür
EP1701042B1 (de) Hydraulische Steueranordnung
EP2013487B1 (de) Hydraulische steueranordnung
EP1996821B1 (de) Ludv-ventilanordnung
EP2636908A2 (de) Steueranordnung
EP2059683B1 (de) Ls-steueranordnung
EP1200743B1 (de) Hydraulische steueranordnung zur bedarfstromgeregelten (load-sensing-geregelten) druckmittelversorgung von vorzugsweise mehreren, hydraulischen verbrauchern
EP1170510B1 (de) Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern
WO2001002736A1 (de) Hydraulische steueranordnung zur druckmittelversorgung von vorzugsweise mehreren hydraulischen verbrauchern
DE102007028864A1 (de) Hydraulische Steueranordnung
WO2003087585A1 (de) Hydraulische steueranordnung in load-sensing technik
WO2016091528A1 (de) Hydraulische ventilanordnung, hydraulischer ventilblock mit einer derartigen ventilanordnung, und hydraulischer antrieb mit einem derartigen ventilblock
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
EP1386084B1 (de) Hydraulische steueranordnung mit wegeventil zur steuerung eines einfachwirkenden hydraulischen verbrauchers hinsichtlich richtung und geschwindigkeit
DE19503943C2 (de) Bremsventilanordnung für einen reversierbaren hydraulischen Verbraucher
EP2891805A2 (de) Steueranordnung und Steuerventil für eine derartige Steueranordnung
EP1069317A2 (de) Wegeventilscheibe, insbesondere für ein mobiles Arbeitsgerät
DE10119276A1 (de) Hydraulischer Steuerkreis
DE102007026676A1 (de) Hydraulische Steueranordnung zur bedarfstromgeregelten (load-sensing-geregelten) Druckmittelversorgung von mehreren hydraulischen Verbrauchern
DE19646449A1 (de) Steuereinrichtung für einen hydraulischen Verbraucher, insbesondere für das Hubwerk eines Traktors
WO2008031483A1 (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