EP2013487B1 - Hydraulic control arrangement - Google Patents
Hydraulic control arrangement Download PDFInfo
- Publication number
- EP2013487B1 EP2013487B1 EP07724220A EP07724220A EP2013487B1 EP 2013487 B1 EP2013487 B1 EP 2013487B1 EP 07724220 A EP07724220 A EP 07724220A EP 07724220 A EP07724220 A EP 07724220A EP 2013487 B1 EP2013487 B1 EP 2013487B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- valve
- control
- hydraulic
- pilot
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
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
- F15B11/166—Controlling a pilot pressure in response to the load, i.e. supply to at least one user is regulated by adjusting either the system pilot pressure or one or more of the individual pilot command pressures
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2285—Pilot-operated systems
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2296—Systems with a variable displacement pump
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
-
- 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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30505—Non-return valves, i.e. check valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
- F15B2211/30535—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
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
- F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3144—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
- F15B2211/60—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
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit 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
- F15B2211/60—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
- F15B2211/6057—Load sensing circuits having valve means between output member and the load sensing circuit using directional control 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
- F15B2211/65—Methods of control of the load sensing pressure
- F15B2211/654—Methods of control of the load sensing pressure the load sensing pressure being lower than the 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
- F15B2211/70—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, which is used in particular for controlling hydraulic consumers on mobile machines and having the features of the preamble of claim 1.
- Such a hydraulic control arrangement is for example from the EP 0 566 449 A1 known.
- This is a hydraulic control arrangement according to the load-sensing principle, in which a variable displacement pump is adjusted in each case depending on the highest load pressure of the actuated hydraulic consumers so that the pump pressure is above the highest load pressure by a certain pressure difference.
- the hydraulic consumers, the pressure medium flows through adjustable metering orifices, which are arranged between an outgoing from the variable flow pump inlet line and the hydraulic consumers and are usually integrated into an also the direction control of a hydraulic consumer serving main control valve.
- variable displacement pump By the metering orifices downstream pressure compensators is achieved that at a sufficiently supplied by the variable pressure fluid independent of the load pressures of the hydraulic consumers a certain pressure difference across the metering orifices, so that the inflowing hydraulic pressure consumer fluid quantity depends only on the opening cross section of the respective metering orifice. If a metering orifice is opened further, more pressure medium must flow over it in order to generate the specific pressure difference.
- the variable displacement pump is adjusted in such a way that it supplies the required amount of pressure medium. Therefore, one speaks of a demand flow control.
- the variable displacement pump has a pump regulator, which can be acted upon by a load-sensing line with the highest load pressure of the simultaneously actuated hydraulic consumers.
- a fixed pressure relief valve is connected to the end section of the load signaling line connected to the pump regulator connected, which limits the reported to the pump regulator pressure and thus also the pump pressure in cooperation with a decoupling the end portion of the remaining load sensing line throttle.
- the pressure compensators downstream of the metering orifices are acted upon in the opening direction by the pressure downstream of the respective metering orifice and in the closing direction by a control pressure prevailing in a rearward control chamber, which usually corresponds to the highest load pressure of all the hydraulic consumers supplied by the same hydraulic pump. If, in a simultaneous operation of several hydraulic consumers, the metering orifices are opened so far that the pressure medium supplied by the stoppered hydraulic pump is less than the total required pressure medium, the individual hydraulic consumers inflowing pressure medium quantities regardless of the respective load pressure of the hydraulic consumers proportionally reduced. This is why we speak of a controller with load-independent flow distribution (LUDV control).
- LUDV control load-independent flow distribution
- a LUDV control is a special case of a load-sensing or load-sensing control ( LS control).
- a LUDV control in which also individually for a hydraulic consumer, the pressure is limited. It is necessary that the rear control chamber of a LUDV pressure compensator is structurally separated from the load-sensing line. And it is a directional valve necessary, depending on the switching position of the rear control chamber is connected to the load-sensing line or is acted upon by pump pressure. The directional valve is switched depending on the load pressure. A change in the switching pressure during operation is not provided.
- the invention has for its object to develop a hydraulic control arrangement with the features of the preamble of claim 1 so that with pilot signals for the main control valves in a simple and cost-effective manner, a pressure control for several hydraulic consumers is possible.
- the desired aim is achieved in a hydraulic control arrangement with the features of the preamble of claim 1 according to the invention that according to the characterizing part of claim 1, the pressure relief valve is adjustable in dependence on the height of a control of a main control valve pilot signal.
- the pressure limiting valve is adjustable, with which the pressure reported to the pump regulator can be limited.
- the invention is based on the idea that there are mobile machines on which in a pressure control of a hydraulic consumer is rarely still another hydraulic consumer to operate.
- a pressure control of a hydraulic consumer is also possible in a LUDV control arrangement with very simple means and without changes to the individual pressure compensators associated with the metering orifices.
- the pressure relief valve is adjustable in dependence on the height of a plurality of pilot signals, it is advantageously adjusted when queuing several pilot signals in response to the largest pilot signal. It is assumed that the higher the pre-control signal, the higher the pressure set at the pressure relief valve.
- the pressure relief valve is adjustable in response to a pilot signal only to a set value, which is below the maximum set value, it is possible for the machine operator, the adjustable with a pilot signal maximum consumer pressure depending on the type of machine or to specify the type of work to be done individually.
- the pressure control can be turned off by a design according to claim 4, the pressure control. It then has a demand flow control with a limitation of the load pressure to a high value.
- the pressure relief valve is hydraulically adjustable and has an adjacent to a pressure chamber connected to the control chamber actuating piston.
- the pressure relief valve may also be one which is electrically or electro-hydraulically adjustable.
- adjustability of the pressure relief valve may be beneficial.
- a hydraulic actuation of the main control valve however, the use of a purely hydraulically adjustable pressure limiting valve appears more advantageous.
- a pilot pressure is usually generated with the aid of an adjustable pressure reducing valve, which has a pressure connection, at which a substantially constant supply pressure is preferably present at a height of 30 to 35 bar, a tank connection and a control connection, at which the pilot pressure is adjusted.
- the pressure relief valve can now be easily adjusted to its maximum setting if, according to claim 6, an arbitrarily operable directional control valve is present, depending on the switching position, the pressure chamber of the pressure relief valve with the pilot pressure or the supply pressure can be acted upon.
- the directional control valve alternately either a line in which the supply pressure is present, or a line in which the pilot pressure is present to connect with the pressure chamber of the pressure relief valve.
- the directional control valve may be of simpler construction if according to claim 7 between the pilot line and the pressure chamber at the pressure relief valve is a check valve opening to the pressure chamber. This prevents the high supply pressure from entering the pilot control line and influencing the control of the main control valve.
- check valves which are arranged according to claim 8, can be easily select the highest hydraulic pilot signal and einêtn in the pressure chamber of the pressure relief valve.
- a second pressure relief valve is present.
- the directional control valve is used, via which the supply pressure is switched through into the pressure chamber.
- the pressure relief of the pressure chamber on the pressure relief valve is advantageously carried out via a flow control valve, which may be realized by a simple nozzle, but preferably is a flow control valve.
- a variable displacement pump 10 for example an axial piston pump according to the swashplate principle, is used as the pressure medium source, which draws in pressure medium from a tank 11 and discharges it into a supply line 12 and its swash plate 13 indicated by a double arrow in the interaction of two actuating cylinders 14 and 15 can be pivoted.
- Both actuating cylinders are differential cylinders, which have a piston 16 or 17 and in each case a piston rod 18, with which they engage the swash plate 13.
- the piston surface of the piston 17 of the adjusting cylinder 15 is smaller than the piston surface of the piston 16 of the other actuating cylinder 14.
- An extension of the piston rod 18 of the actuating cylinder 14 causes a reduction and extension of the piston rod 18 of the actuating cylinder 15, an increase in the swivel angle of the swash plate and thus the Hubvolumens the variable displacement 10.
- a compression spring 19 on the swash plate a force in the direction of increasing the pivot angle.
- the pressure chamber of the actuating cylinder 15 is permanently connected to the supply line 12. In this pressure chamber so there is always the same pressure as in the supply line.
- the inflow and outflow of pressure fluid to and from the pressure chamber of the actuating cylinder 14 is controlled by a pump control unit 25 which is constructed on the variable displacement pump 10 having an outer terminal LS, to which an end portion 26a of a load reporting line 26 is connected, and the two substantially 3/2-way proportional valves comprises, one of which is a LS-pump control valve 27 and the other a pressure control valve 28, the is set to a pressure above the usually occurring load pressures.
- the pressure control valve 28 has a first port which is connectable via a discharge line 29 to the tank 11.
- a second connection of the pressure regulating valve 28 is located on the supply line 12.
- the third connection which can be connected to the first or the second connection, is connected to the pressure chamber of the adjusting cylinder 14.
- a first connection of the LS pump control valve 27 is located on the discharge line 29, a second connection on the supply line 12.
- the third connection of the valve 27 can be connected to its first or second connection and permanently connected to the first connection of the valve 28.
- a non-illustrated slide of the valve 28 is acted upon by a compression spring 30 in the sense of increasing the pivot angle and the inlet pressure in the sense of a reduction of the pivot angle of the pump 10.
- a slider (not shown in detail) of the LS pump control valve 27 is acted upon by a pressure spring 31 and by the pressure prevailing in the end portion 26a of the load-sensing line 26 in the sense of increasing the pivoting angle of the pump 10 and in the sense of reducing the pivoting angle by the inlet pressure.
- a slider (not shown in detail) of the LS pump control valve 27 is acted upon by a pressure spring 31 and by the pressure prevailing in the end portion 26a of the load-sensing line 26 in the sense of increasing the pivoting angle of the pump 10 and in the sense of reducing the pivoting angle by the inlet pressure.
- the difference is between 10 bar and 20 bar. Balance prevails on the spool of the valve 28 when the supply pressure produces a force corresponding to the force of the spring 30.
- the equilibrium of the inlet pressure in the range of 350 bar.
- the characteristic as LUDV control arrangement receives the embodiment FIG. 1 by the nature of the existing control block 35, which includes LUDV directional control valve sections.
- FIG. 1 For example, two sections are shown, which are constructed completely the same. Of course, there may be more sections.
- the control block 35 has an inlet connection P, a tank connection T, a load-signaling connection LS and various consumer connections A and B.
- At the inlet port P begins as part of the inlet line 12, an inlet channel 36 and the tank port T, a tank channel 37 of the control block.
- two LUDV directional control valves 38 are formed with a closed center, with which two hydraulic consumers, for example two differential cylinders are controllable.
- the directional valves 38 are hydraulically actuated. In them, a speed control part and a direction control part are formed separately from each other on the same spool.
- pressure medium coming from inlet channel 36 flows from an inlet chamber 39 via a metering orifice 40 into a first intermediate chamber 41, from there via the opening cross section of a pressure balance 42 into a second intermediate chamber 43 From there, pressure fluid to the consumer port A or B.
- the control piston of the pressure compensators 42 is in the opening direction of the pressure in the intermediate chamber 41, ie from the pressure to the metering orifice 40 and in the closing direction of the Pressure is applied in a load-side channel running as part of the load-sensing line in the control block.
- the control piston of the pressure compensators 42 is designed so that, when the pressure compensator is completely open, it establishes a fluidic connection between the intermediate chamber 41 and the load-signaling channel. This is the case when the respective hydraulic consumer is operated alone or when a simultaneous actuation of several hydraulic consumers that consumer, which is associated with the pressure balance, has the highest load pressure.
- the outer terminals P, T and LS of the control block 35 are located at an input section 48, through which pass the channels 36, 37 and the Lastmelde effet 26 to the directional control valve sections.
- the end portion 26a of the load-sensing line 26 is hydraulically decoupled from its remaining parts by a nozzle 54. With a pressure medium flow through the nozzle 54, a pressure difference occurs at this, so that the pressure in the end portion 26a of the load reporting line 26 is lower than in the other parts thereof.
- a pressure relief valve 50 Within the input section is also a pressure relief valve 50 with its input terminal 51 to the end portion 26 a of the load reporting line 26 and its output port 52 connected to the tank channel 37.
- valve 50 and the nozzle 54 of the build-up in the end portion 26a of the load reporting line pressure can be limited.
- a small flow control valve 53 located in the inlet section 48 connects the load detection channel 26 and the tank channel 37.
- the characteristic as LS control arrangement receives the embodiment FIG. 2 by the nature of the existing control block 55, which is composed of LS-way valve discs and how the control block from the FIG. 1 an inlet port P, a drain port T and a load reporting port LS.
- FIG. 2 By way of example, two directional control valves 56 are shown. Of course, more discs may be present.
- Each directional valve disc 56 serves as a housing for a directional control valve 57, which is hydraulically actuated. Both directional valve discs 56 are completely identical to each other and contain the same components and channels.
- To each directional control valve 57 includes a spool 58 which is axially displaceable in a valve bore unspecified and occupies a middle neutral position under the mere effect of two centering springs 59. In this position, a consumer channel 60, which leads to a consumer connection B, a consumer channel 61, which leads to a consumer connection A, the inlet channel 36 and the outlet channel 37 are separated from each other.
- the spool 58 of a directional control valve By pressurizing a control pressure chamber 62, the spool 58 of a directional control valve is displaced out of the neutral position in one direction and by pressurizing a control pressure space 63 in the other direction.
- either the consumer channel 60 or the consumer channel 61 is connected to the inlet channel 36 and the respective other consumer channel to the outlet channel 37.
- a shift from the neutral position of the spool opens a metering orifice between an inlet inlet to the directional control valve and a consumer channel whose opening cross-section determines the amount of pressure medium flowing to the hydraulic consumer.
- the pressure difference across the metering orifice is kept constant, so that the amount of pressure medium flowing through the metering orifice depends solely on the opening cross section.
- a pressure compensator 65 is arranged in the leading to the inlet inlet of the directional control valve part part 36, which is acted upon in the closing direction by the pressure before the metering orifice and in the opening direction by the pressure to the metering orifice and by a compression spring 66.
- the pressure drop across the metering orifice is equivalent to the force of the compression spring 66 and set to a value between 10 bar and 20 bar.
- the pressure after the metering orifice corresponds to the load pressure of the respective hydraulic consumer.
- This pressure is also applied to an input of a shuttle valve 67, wherein the other input of the shuttle valve 67 of a directional control valve disc is connected to the output of the shuttle valve 67 of the other directional control valve disc.
- the other input of the shuttle valve 67 of the latter directional valve disc is connected via an end plate 68 to the drain passage 37.
- a channel leads to the load reporting LS of this disc.
- LS is the highest load pressure of actuatable with the two-way valves hydraulic consumers.
- the pressure in the inlet channel 36 is a predetermined pressure difference of z. B.
- the pressure equivalent to the force of the compression spring 66 of a pressure compensator 65 may also be 15 bar, so that regardless of whether a hydraulic load generates the highest load pressure or not, the pressure drop across the metering orifice of the respective directional control valve is the same.
- FIG. 2 is the same as in the embodiment FIG. 1 the end portion 26a of the load-sensing line 26 is hydraulically decoupled from the other parts thereof by a nozzle 54.
- a pressure limiting valve 50 is connected with its input terminal 51 to the load-signaling line 26 and with its output terminal 52 to the tank channel 37.
- a small flow control valve 53 connects the load reporting channel 46 and the tank channel 37.
- the pressure limiting valve 50 is hydraulically adjustable and has an actuating piston 73, which adjoins a pressure chamber 74 and a by the distance between two stops from each other and its length predetermined distance is movable.
- a control spring 75 of the pressure relief valve 50 is minimally biased when the actuator piston is applied to a stop, and maximum biased when the actuator piston rests against the other stop.
- the pressure at which the pressure limiting valve 50 responds can therefore be set between a minimum and a maximum value. In what way the pressure relief valve 50 is adjustable, goes closer FIG. 3 out.
- each pilot unit has a total of four pilot valves 79 and correspondingly four control outputs 80.
- each pilot unit has a tank port T and a pressure port P, at which a substantially constant supply pressure is present at a level between 30 and 35 bar.
- a pilot control lever 81 Via a pilot control lever 81, which can be deflected from a central position in which there is tank pressure at all control outputs 80, the pilot valves 79 can be adjusted. Depending on the lever deflection, they regulate a specific pilot pressure at the corresponding control output 80.
- pilot lines 82 From the control outputs 80 lead pilot lines 82 to the control pressure chambers 62 and 63 of the directional control valves 38 ( FIG. 1 ) or 57 ( FIG. 2 ).
- the pilot pressure jumps after a small pivot angle of a lever 81 to an initial value and then increases continuously with the swivel angle. At a certain tilt angle, the pilot pressure then jumps to the supply pressure.
- each pilot line 82 From each pilot line 82 is a branch line 83 from, in which a nozzle 84 and a blocking the pilot line back check valve 85 are in succession. Downstream of the check valves 85, all branch lines 83 open into a common control line 86, which leads to the pressure chamber 74 of the pressure limiting valve 50. All pilot control lines 82 are thus connected in parallel to each other via a respective nozzle 84 and a check valve 85 with the pressure chamber 74 of the pressure relief valve 50.
- the control line 86 is also still connected to a first port of a 3/2 way valve 87, of which a second port is connected to the supply pressure leading line and of which a third port to the input of a second pressure relief valve 88.
- a rest position which occupies the directional control valve 87 under the action of a compression spring 89, the control line 86 is connected to the pressure relief valve 88.
- the second connection is blocked.
- the directional control valve 87 can be brought by means of an electromagnet 90 in a switching position in which the control line 86 is connected to the second terminal and the third terminal is shut off.
- the solenoid 90 is connected via an electrical line to an electrical switch housed in the one pilot control lever 81, which can be actuated by a push button 91.
- the pressure relief valve 88 is manually adjustable. It is used together with the nozzles 84 to be able to limit the pressure in the control line 86 to a value in the rest position of the directional control valve 87, which is lower than the maximum controllable by a pressure reducing valve 79 pilot pressure. Via a flow control valve 92, the control line 86 can be relieved to the tank 11.
- variable displacement pump 10 delivers as much pressure fluid quantity that the pressure in the supply line 12 by 20 bar above the reported load pressure lies.
- the hydraulic consumer is moved at a speed which is determined by the opening cross-section of the metering orifice.
- the load pressure is higher than 165 bar, a pressure medium supply to the hydraulic consumer is only possible after further deflection of the pilot control lever.
- the pilot control lever must be deflected so far that the pressure in the control line 86 becomes 20 bar.
- the pressure limiting valve 88 responds.
- the pressure in the control line 86 remains at 20 bar, so that the pressure in the end portion 26a at 200 bar and thus the inlet pressure at 220 bar. This pressure of 220 bar is in the consumer, so that a corresponding force can be exercised.
- a hydraulic load with a load pressure up to 250 bar is to be controlled solely by the degree of opening of the metering orifice and the full stroke of a main control valve, the button 91 is pressed on a pilot control lever and thus the directional control valve is switched. Now the supply pressure of 30 bar is in the control line 86.
- the check valves 85 ensure that the pre-control pressure predetermined by the pilot control device prevails in the respective pilot control line.
- the pressure relief valve 50 is on set its highest value of 250 bar.
- the pressure in the end portion 26a of the load-sensing line is now equal to the load pressure up to a load pressure of 250 bar.
- the pressure in the feed line 12 is 20 bar higher than the load pressure.
- a load of up to 250 bar can be moved with a speed determined solely by the opening cross section of the associated metering orifice.
- a load pressure of 270 bar Up to a load pressure of 270 bar, a slower movement is possible because of the reduced pressure difference across the metering orifice. With a load pressure of more than 270 bar, the load can no longer be moved.
- Each pilot line 82 is connected via a nozzle 84 and a check valve 85 to the control line 86. It is therefore possible for each of the two pilot control devices 78 controllable hydraulic consumers and for each direction of pressure control. With a simultaneous actuation of a plurality of hydraulic consumers, the check valves 85 ensure that the highest pilot pressure is present in the control line 86 and that the pilot pressures in the pilot lines 82 do not influence each other.
- branch line 83 is present between the corresponding pilot control line 82 and the control line 86.
- a branch line may also be present only between a single pilot control line 82 and the control line 86
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Abstract
Description
Die Erfindung betrifft eine hydraulische Steueranordnung, die insbesondere zur Steuerung von hydraulischen Verbrauchern an mobilen Arbeitsmaschinen verwendet wird und die die Merkmale aus dem Oberbegriff des Patentanspruchs 1 aufweist.The invention relates to a hydraulic control arrangement, which is used in particular for controlling hydraulic consumers on mobile machines and having the features of the preamble of claim 1.
Eine solche hydraulische Steueranordnung ist z.B. aus der
Die den Zumessblenden nachgeschalteten Druckwaagen werden in Öffnungsrichtung von dem Druck nach der jeweiligen Zumessblende und in Schließrichtung von einem in einem rückwärtigen Steuerraum anstehenden Steuerdruck beaufschlagt, der üblicherweise dem höchsten Lastdruck aller von derselben Hydropumpe versorgten hydraulischen Verbraucher entspricht. Wenn bei einer gleichzeitigen Betätigung mehrerer hydraulischer Verbraucher die Zumessblenden so weit aufgemacht werden, dass die von der bis zum Anschlag verstellten Hydropumpe gelieferte Druckmittelmenge kleiner ist als die insgesamt geforderte Druckmittelmenge, werden die den einzelnen hydraulischen Verbrauchern zufließenden Druckmittelmengen unabhängig vom jeweiligen Lastdruck der hydraulischen Verbraucher verhältnisgleich reduziert. Man spricht deshalb von einer Steuerung mit lastunabhängiger Durchflussverteilung (LUDV-Steuerung). Weil bei einer LUDV-Steuerung auch der höchste Lastdruck abgefühlt und von der Hydropumpe durch die Variation der geförderten Druckmittelmenge ein um eine bestimmte Druckdifferenz über dem höchsten Lastdruck liegender Zulaufdruck erzeugt wird, ist eine LUDV-Steuerung ein Sonderfall einer lastfühlenden oder load-sensing Steuerung (LS-Steuerung).The pressure compensators downstream of the metering orifices are acted upon in the opening direction by the pressure downstream of the respective metering orifice and in the closing direction by a control pressure prevailing in a rearward control chamber, which usually corresponds to the highest load pressure of all the hydraulic consumers supplied by the same hydraulic pump. If, in a simultaneous operation of several hydraulic consumers, the metering orifices are opened so far that the pressure medium supplied by the stoppered hydraulic pump is less than the total required pressure medium, the individual hydraulic consumers inflowing pressure medium quantities regardless of the respective load pressure of the hydraulic consumers proportionally reduced. This is why we speak of a controller with load-independent flow distribution (LUDV control). Because in a LUDV control even the highest load pressure is sensed and by the hydraulic pump by the variation of the conveyed pressure medium amount to a certain pressure difference above the highest load pressure lying inlet pressure is generated, a LUDV control is a special case of a load-sensing or load-sensing control ( LS control).
Für mehrere hydraulische Verbraucher, denen Druckmittel jeweils über eine Zumessblende mit vorgeschalteter Druckwaage zufließt, die in Schließrichtung nur vom Druck vor der Zumessblende und in Öffnungsrichtung über eine individuelle Lastmeldeleitung nur vom Lastdruck des jeweiligen hydraulischen Verbrauchers und von einer Druckfeder beaufschlagt ist, erhält man keine lastunabhängige Durchflussverteilung. Man hat eine bloße LS-Steuerung und LS-Verbraucher. Eine solche Steuerung ist z.B. durch die
Bei der hydraulischen Steueranordnung nach der
In der
Der Erfindung liegt die Aufgabe zugrunde, eine hydraulische Steueranordnung mit den Merkmalen aus dem Oberbegriff des Patentanspruchs 1 so weiter zu entwickeln, dass mit Vorsteuersignalen für die Hauptsteuerventile auf einfache und kostengünstige Weise eine Drucksteuerung auch für mehrere hydraulische Verbraucher möglich ist.The invention has for its object to develop a hydraulic control arrangement with the features of the preamble of claim 1 so that with pilot signals for the main control valves in a simple and cost-effective manner, a pressure control for several hydraulic consumers is possible.
Das angestrebte Ziel wird bei einer hydraulischen Steueranordnung mit den Merkmalen aus dem Oberbegriff des Patentanspruchs 1 erfindungsgemäß dadurch erreicht, dass gemäß dem kennzeichnenden Teil des Patentanspruchs 1 das Druckbegrenzungsventil in Abhängigkeit von der Höhe eines der Ansteuerung eines Hauptsteuerventils dienenden Vorsteuersignals verstellbar ist. Gemäß der Erfindung ist also das Druckbegrenzungsventil verstellbar, mit dem der an den Pumpenregler gemeldete Druck begrenzbar ist. Der Erfindung liegt dabei der Gedanke zugrunde, dass es mobile Arbeitsmaschinen gibt, an denen bei einer Drucksteuerung eines hydraulischen Verbrauchers nur selten noch ein weiterer hydraulischer Verbraucher zu betätigen ist. Insbesondere ist gemäß der Erfindung auch bei einer LUDV-Steueranordnung mit sehr einfachen Mitteln und ohne Veränderungen an den den Zumessblenden zugeordneten Individualdruckwaagen eine Drucksteuerung eines hydraulischen Verbrauchers möglich.The desired aim is achieved in a hydraulic control arrangement with the features of the preamble of claim 1 according to the invention that according to the characterizing part of claim 1, the pressure relief valve is adjustable in dependence on the height of a control of a main control valve pilot signal. According to the invention, therefore, the pressure limiting valve is adjustable, with which the pressure reported to the pump regulator can be limited. The invention is based on the idea that there are mobile machines on which in a pressure control of a hydraulic consumer is rarely still another hydraulic consumer to operate. In particular, according to the invention, a pressure control of a hydraulic consumer is also possible in a LUDV control arrangement with very simple means and without changes to the individual pressure compensators associated with the metering orifices.
Vorteilhafte Ausgestaltungen einer erfindungsgemäßen hydraulischen Steueranordnung kann man den Unteransprüchen entnehmen.Advantageous embodiments of a hydraulic control arrangement according to the invention can be found in the dependent claims.
Wenn das Druckbegrenzungsventil in Abhängigkeit von der Höhe mehrerer Vorsteuersignale verstellbar ist, so wird es beim Anstehen mehrerer Vorsteuersignale vorteilhafterweise in Abhängigkeit vom größten Vorsteuersignal verstellt. Dabei wird davon ausgegangen, dass der am Druckbegrenzungsventil eingestellte Druck umso höher ist je größer das Vorsteuersignal ist.If the pressure relief valve is adjustable in dependence on the height of a plurality of pilot signals, it is advantageously adjusted when queuing several pilot signals in response to the largest pilot signal. It is assumed that the higher the pre-control signal, the higher the pressure set at the pressure relief valve.
Bei einer Ausbildung gemäß Patentanspruch 3, nach der das Druckbegrenzungsventil in Abhängigkeit von einem Vorsteuersignal nur bis auf einen Einstellwert verstellbar ist, der unterhalb des maximalen Einstellwerts liegt, ist es für den Maschinenbetreiber möglich, den mit einem Vorsteuersignal einstellbaren maximalen Verbraucherdruck je nach Art der Maschine oder nach Art der zu bewältigenden Arbeit individuell vorzugeben.In an embodiment according to claim 3, according to which the pressure relief valve is adjustable in response to a pilot signal only to a set value, which is below the maximum set value, it is possible for the machine operator, the adjustable with a pilot signal maximum consumer pressure depending on the type of machine or to specify the type of work to be done individually.
Vorteilhafterweise kann durch eine Ausbildung nach Patentanspruch 4 die Drucksteuerung ausgeschaltet werden. Man hat dann eine Bedarfsstromregelung mit einer Begrenzung des Lastdrucks auf einen hohen Wert.Advantageously, can be turned off by a design according to claim 4, the pressure control. It then has a demand flow control with a limitation of the load pressure to a high value.
Gemäß Patentanspruch 5 ist das Druckbegrenzungsventil hydraulisch verstellbar und weist einen an eine mit der Steuerleitung verbundene Druckkammer angrenzenden Stellkolben auf. Grundsätzlich kann das Druckbegrenzungsventil auch ein solches sein, das elektrisch oder elektrohydraulisch verstellbar ist. Insbesondere wenn das Hauptsteuerventil elektrisch betätigt wird, kann eine solche Verstellbarkeit des Druckbegrenzungsventils günstig sein. Bei einer hydraulischen Betätigung des Hauptsteuerventils dagegen erscheint die Verwendung eines rein hydraulisch verstellbaren Druckbegrenzungsventils vorteilhafter.According to claim 5, the pressure relief valve is hydraulically adjustable and has an adjacent to a pressure chamber connected to the control chamber actuating piston. In principle, the pressure relief valve may also be one which is electrically or electro-hydraulically adjustable. In particular, when the main control valve is electrically operated, such adjustability of the pressure relief valve may be beneficial. In a hydraulic actuation of the main control valve, however, the use of a purely hydraulically adjustable pressure limiting valve appears more advantageous.
Ist das Hauptsteuerventil hydraulisch betätigbar, so wird ein Vorsteuerdruck üblicherweise mit Hilfe eines verstellbaren Druckreduzierventils erzeugt, das einen Druckanschluss, an dem ein weitgehend konstanter Versorgungsdruck vorzugsweise in einer Höhe von 30 bis 35 bar ansteht, einen Tankanschluss und einen Regelanschluss besitzt, an dem der Vorsteuerdruck eingeregelt wird. Das Druckbegrenzungsventil kann nun auf einfache Weise auf seinen maximalen Einstellwert verstellt werden, wenn gemäß Patentanspruch 6 ein willkürlich betätigbares Wegeventil vorhanden ist, in Abhängigkeit von dessen Schaltstellung die Druckkammer des Druckbegrenzungsventil mit dem Vorsteuerdruck oder mit dem Versorgungsdruck beaufschlagbar ist.If the main control valve can be actuated hydraulically, then a pilot pressure is usually generated with the aid of an adjustable pressure reducing valve, which has a pressure connection, at which a substantially constant supply pressure is preferably present at a height of 30 to 35 bar, a tank connection and a control connection, at which the pilot pressure is adjusted. The pressure relief valve can now be easily adjusted to its maximum setting if, according to claim 6, an arbitrarily operable directional control valve is present, depending on the switching position, the pressure chamber of the pressure relief valve with the pilot pressure or the supply pressure can be acted upon.
Es ist möglich, mit dem Wegeventil wechselweise entweder eine Leitung, in der der Versorgungsdruck ansteht, oder eine Leitung, in der der Vorsteuerdruck ansteht mit der Druckkammer des Druckbegrenzungsventils zu verbinden. Das Wegeventil kann jedoch einfacher aufgebaut sein, wenn sich gemäß Patentanspruch 7 zwischen der Vorsteuerleitung und der Druckkammer am Druckbegrenzungsventil ein zur Druckkammer hin öffnendes Rückschlagventil befindet. Dieses verhindert, dass der hohe Versorgungsdruck auch in die Vorsteuerleitung gelangt und die Ansteuerung des Hauptsteuerventils beeinflusst.It is possible, with the directional control valve alternately either a line in which the supply pressure is present, or a line in which the pilot pressure is present to connect with the pressure chamber of the pressure relief valve. However, the directional control valve may be of simpler construction if according to claim 7 between the pilot line and the pressure chamber at the pressure relief valve is a check valve opening to the pressure chamber. This prevents the high supply pressure from entering the pilot control line and influencing the control of the main control valve.
Mit Rückschlagventilen, die gemäß Patentanspruch 8 angeordnet sind, lässt sich auf einfache Weise das höchste hydraulische Vorsteuersignal auswählen und in die Druckkammer des Druckbegrenzungsventils einsteuern.With check valves, which are arranged according to claim 8, can be easily select the highest hydraulic pilot signal and einsteuern in the pressure chamber of the pressure relief valve.
Um eine Drucksteuerung über ein Vorsteuersignal auf einen unterhalb des maximalen Einstellwerts des Druckbegrenzungsventils liegenden Druckwert zu beschränken, ist gemäß Patentanspruch ein zweites Druckbegrenzungsventil vorhanden. Dieses soll natürlich auf jeden Fall dann nicht wirksam sein, wenn eine Verstellung des ersten Druckbegrenzungsventils auf den maximalen Einstellwert durch Beaufschlagung der Druckkammer mit dem Versorgungsdruck gewünscht ist. Für diese Funktionsweise wird gemäß Patentanspruch 11 vorteilhafterweise das Wegeventil herangezogen, über das der Versorgungsdruck in die Druckkammer durchgeschaltet wird.In order to limit a pressure control via a pilot control signal to a below the maximum set value of the pressure relief valve pressure value, according to claim a second pressure relief valve is present. Of course, this should not be effective in any case when an adjustment of the first pressure relief valve to the maximum setting value is desired by acting on the pressure chamber with the supply pressure. For this operation, according to claim 11 advantageously the directional control valve is used, via which the supply pressure is switched through into the pressure chamber.
Die Druckentlastung der Druckkammer am Druckbegrenzungsventil geschieht zweckmäßigerweise über ein Stromventil, das durch eine einfache Düse realisiert sein kann, bevorzugt jedoch ein Stromregelventil ist.The pressure relief of the pressure chamber on the pressure relief valve is advantageously carried out via a flow control valve, which may be realized by a simple nozzle, but preferably is a flow control valve.
Mehrere Ausführungsbeispiele einer erfindungsgemäßen hydraulischen Steueranordnung sind in der Zeichnung dargestellt. Anhand dieser Ausführungsbeispiele wird die Erfindung nun näher erläutert.Several embodiments of a hydraulic control arrangement according to the invention are shown in the drawing. On the basis of these embodiments, the invention will now be explained in more detail.
Es zeigen
-
Figur 1 ein erstes, nach dem LUDV-Prinzip arbeitendes Ausführungsbeispiel mit dem an einen Endabschnitt der Lastmeldeleitung angeschlossenen, in Abhängigkeit von einem hydraulischen Vorsteuersignal hydraulisch verstellbaren Druckbegrenzungsventil, -
Figur 2 ein zweites, nach dem LS-Prinzip arbeitendes Ausführungsbeispiel mit dem an einen Endabschnitt der Lastmeldeleitung angeschlossenen, in Abhängigkeit von einem hydraulischen Vorsteuersignal hydraulisch verstellbaren Druckbegrenzungsventil und -
Figur 3 die für beide Ausführungsbeispiele verwendbare Anordnung von Vorsteuerventilen zur Betätigung der Hauptsteuerventile und zur Verstellung des Druckbegrenzungsventils.
-
FIG. 1 a first, working according to the LUDV principle embodiment with the connected to an end portion of the load-sensing line, in response to a hydraulic pilot signal hydraulically adjustable pressure relief valve, -
FIG. 2 a second, working according to the LS principle embodiment with the connected to an end portion of the load-sensing line, in dependence from a hydraulic pilot signal hydraulically adjustable pressure relief valve and -
FIG. 3 the usable for both embodiments arrangement of pilot valves for actuating the main control valves and for adjusting the pressure relief valve.
In den beiden gezeigten hydraulischen Steueranordnungen wird als Druckmittelquelle eine Verstellpumpe 10, zum Beispiel eine Axialkolbenpumpe nach dem Schrägscheibenprinzip, verwendet, die Druckmittel aus einem Tank 11 ansaugt und in eine Zulaufleitung 12 abgibt und deren durch einen Doppelpfeil angedeutete Schrägscheibe 13 im Zusammenspiel zweier Stellzylinder 14 und 15 verschwenkt werden kann. Beide Stellzylinder sind Differentialzylinder, die einen Kolben 16 bzw. 17 und jeweils eine Kolbenstange 18 haben, mit der sie an der Schrägscheibe 13 angreifen. Von Druck beaufschlagt wird jeweils nur der kolbenstangenabseitige Druckraum der Stellzylinder. Die Kolbenfläche des Kolbens 17 des Stellzylinders 15 ist kleiner als die Kolbenfläche des Kolbens 16 des anderen Stellzylinders 14. Ein Ausfahren der Kolbenstange 18 des Stellzylinders 14 bewirkt eine Verkleinerung und ein Ausfahren der Kolbenstange 18 des Stellzylinders 15 eine Vergrößerung des Schwenkwinkels der Schrägscheibe und damit des Hubvolumens der Verstellpumpe 10. Zusätzlich zu dem Druck im Stellzylinder 15 übt eine Druckfeder 19 auf die Schrägscheibe eine Kraft in Richtung Vergrößerung des Schwenkwinkels aus.In the two hydraulic control arrangements shown, a
Der Druckraum des Stellzylinders 15 ist dauernd mit der Zulaufleitung 12 verbunden. In diesem Druckraum herrscht also jeweils derselbe Druck wie in der Zulaufleitung. Der Zufluss und Abfluss von Druckmittel zum und vom Druckraum des Stellzylinders 14 wird von einer Pumpenregeleinheit 25 gesteuert, die auf die Verstellpumpe 10 aufgebaut ist, die einen Außenanschluss LS aufweist, an den ein Endabschnitt 26a einer Lastmeldeleitung 26 angeschlossen ist, und die im wesentlichen zwei 3/2-Proportional-Wegeventile umfasst, von denen das eine ein LS-Pumpenregelventil 27 und das andere ein Druckregelventil 28 darstellt, das auf einen über den üblicherweise auftretenden Lastdrücken liegenden Druck eingestellt ist. Das Druckregelventil 28 besitzt einen ersten Anschluss, der über eine Entlastungsleitung 29 mit dem Tank 11 verbindbar ist. Ein zweiter Anschluss des Druckregelventils 28 liegt an der Zulaufleitung 12. Der dritte Anschluss, der mit dem ersten oder dem zweiten Anschluss verbindbar ist, ist mit dem Druckraum des Stellzylinders 14 verbunden. Ein erster Anschluss des LS-Pumpenregelventils 27 liegt an der Entlastungsleitung 29, ein zweiter Anschluss an der Zulaufleitung 12. Der dritte Anschluss des Ventils 27 ist mit dessen ersten oder zweiten Anschluss verbindbar und dauernd mit dem ersten Anschluss des Ventils 28 verbunden. Ein nicht näher dargestellter Schieber des Ventils 28 wird von einer Druckfeder 30 im Sinne einer Vergrößerung des Schwenkwinkels und vom Zulaufdruck im Sinne einer Verkleinerung des Schwenkwinkels der Pumpe 10 beaufschlagt. Ein nicht näher dargestellter Schieber des LS-Pumpenregelventils 27 schließlich wird in Sinne einer Vergrößerung des Schwenkwinkels der Pumpe 10 von einer Druckfeder 31 und vom im Endabschnitt 26a der Lastmeldeleitung 26 herrschenden Druck und im Sinne einer Verkleinerung des Schwenkwinkels vom Zulaufdruck beaufschlagt. Am Schieber des Ventils 27 herrscht ein Kräftegleichgewicht, wenn zwischen dem Zulaufdruck und dem Druck im Endabschnitt 26a der Lastmeldeleitung 26 eine Differenz besteht, die der Kraft der Feder 31 entspricht. Üblicherweise liegt die Differenz zwischen 10 bar und 20 bar. Gleichgewicht am Schieber des Ventils 28 herrscht, wenn der Zulaufdruck eine Kraft erzeugt, die der Kraft der Feder 30 entspricht. Üblicherweise liegt bei einem Gleichgewicht der Zulaufdruck im Bereich von 350 bar.The pressure chamber of the
Die Charakteristik als LUDV-Steueranordnung erhält das Ausführungsbeispiel nach
Der Steuerblock 35 weist einen Zulaufanschluss P, einen Tankanschluss T, einen Lastmeldeanschluss LS und verschiedenen Verbraucheranschlüsse A und B auf. Am Zulaufanschluss P beginnt als Teil der Zulaufleitung 12 ein Zulaufkanal 36 und am Tankanschluss T ein Tankkanal 37 des Steuerblocks. Im Steuerblock sind zwei LUDV-Wegeventile 38 mit geschlossener Mitte ausgebildet, mit denen zwei hydraulische Verbraucher, zum Beispiel zwei Differentialzylinder steuerbar sind. Die Wegeventile 38 sind hydraulisch betätigbar. In ihnen sind ein Geschwindigkeitssteuerteil und ein Richtungssteuerteil voneinander getrennt am selben Steuerschieber ausgebildet. Wenn ein Wegeventil 38 aus seiner Mittelstellung in eine seiner beiden seitlichen Arbeitsstellungen gebracht worden ist, strömt vom Zulaufkanal 36 kommendes Druckmittel von einer Zulaufkammer 39 über eine Zumessblende 40 in eine erste Zwischenkammer 41, von dort über den Öffnungsquerschnitt einer Druckwaage 42 in eine zweite Zwischenkammer 43 und dann über den Richtungsteil des Wegeventils in eine Verbraucherkammer 44 oder 45. Von dort gelangt Druckmittel zum Verbraucheranschluss A oder B. Der Regelkolben der Druckwaagen 42 wird in Öffnungsrichtung vom Druck in der Zwischenkammer 41, also vom Druck nach der Zumessblende 40 und in Schließrichtung vom Druck in einem als Teil der Lastmeldeleitung im Steuerblock verlaufenden Lastmeidekanal beaufschlagt. Der Regelkolben der Druckwaagen 42 ist so ausgebildet, dass er, wenn die Druckwaage ganz offen ist, eine fluidische Verbindung zwischen der Zwischenkammer 41 und dem Lastmeldekanal herstellt. Dies ist der Fall, wenn der jeweilige hydraulische Verbraucher allein betätigt wird oder wenn bei einer gleichzeitigen Betätigung mehrerer hydraulischer Verbraucher derjenige Verbraucher, dem die Druckwaage zugeordnet ist, den höchsten Lastdruck hat.The
Die Außenanschlüsse P, T und LS des Steuerblocks 35 befinden sich an einer Eingangssektion 48, durch die hindurch die Kanäle 36, 37 und die Lastmeldeleitung 26 zu den Wegeventilsektionen führen. Innerhalb der Eingangssektion ist der Endabschnitt 26a der Lastmeldeleitung 26 von deren übrigen Teilen durch eine Düse 54 hydraulisch entkoppelt. Bei einem Druckmittelfluss durch die Düse 54 hindurch tritt an dieser eine Druckdifferenz auf, so dass der Druck im Endabschnitt 26a der Lastmeldeleitung 26 niedriger wird als in deren anderen Teilen. Innerhalb der Eingangssektion ist außerdem ein Druckbegrenzungsventil 50 mit seinem Eingangsanschluss 51 an den Endabschnitt 26a der Lastmeldeleitung 26 und mit seinem Ausgangsanschluss 52 an den Tankkanal 37 angeschlossen. Durch das Ventil 50 und die Düse 54 ist der im Endabschnitt 26a der Lastmeldeleitung aufbaubare Druck begrenzbar. Stromauf der Düse 54 verbindet ein in der Eingangssektion 48 befindliches kleines Stromregelventil 53 den Lastmeldekanal 26 und den Tankkanal 37.The outer terminals P, T and LS of the
Die Charakteristik als LS-Steueranordnung erhält das Ausführungsbeispiel nach
Jede Wegeventilscheibe 56 dient als Gehäuse für ein Wegeventil 57, das hydraulisch betätigbar ist. Beide Wegeventilscheiben 56 sind völlig identisch zueinander und enthalten dieselben Komponenten und Kanäle. Zu jedem Wegeventil 57 gehört ein Steuerschieber 58, der in einer nicht näher bezeichneten Ventilbohrung axial verschiebbar ist und unter der bloßen Wirkung zweier Zentrierfedern 59 eine mittlere Neutrallage einnimmt. In dieser Lage sind ein Verbraucherkanal 60, der zu einem Verbraucheranschluss B führt, ein Verbraucherkanal 61, der zu einem Verbraucheranschluss A führt, der Zulaufkanal 36 sowie der Ablaufkanal 37 voneinander getrennt.Each
Durch Druckbeaufschlagung eines Steuerdruckraums 62 wird der Steuerschieber 58 eines Wegeventils aus der Neutrallage heraus in die eine Richtung und durch Druckbeaufschlagung eines Steuerdruckraums 63 in die andere Richtung verschoben. Je nach Verschieberichtung wird entweder der Verbraucherkanal 60 oder der Verbraucherkanal 61 mit dem Zulaufkanal 36 und der jeweils andere Verbraucherkanal mit dem Ablaufkanal 37 verbunden. Bei einer Verschiebung aus der Neutrallage öffnet der Steuerschieber eine Zumessblende zwischen einem Zulaufeingang am Wegeventil und einem Verbraucherkanal, deren Öffnungsquerschnitt die Druckmittelmenge bestimmt, die zum hydraulischen Verbraucher fließt.By pressurizing a
Es wird nämlich die Druckdifferenz über die Zumessblende konstant gehalten, so dass die über die Zumessblende strömende Druckmittelmenge allein vom Öffnungsquerschnitt abhängt. Dazu ist in dem zum Zulaufeingang des Wegeventils führenden Teil des Zulaufkanals 36 eine Druckwaage 65 angeordnet, die in Schließrichtung vom Druck vor der Zumessblende und in Öffnungsrichtung vom Druck nach der Zumessblende und von einer Druckfeder 66 beaufschlagt wird. Der Druckabfall über die Zumessblende ist der Kraft der Druckfeder 66 äquivalent und auf einen Wert zwischen 10 bar und 20 bar eingestellt.Namely, the pressure difference across the metering orifice is kept constant, so that the amount of pressure medium flowing through the metering orifice depends solely on the opening cross section. For this purpose, a
Der Druck nach der Zumessblende entspricht dem Lastdruck des jeweiligen hydraulischen Verbrauchers. Dieser Druck steht außerdem auch an einem Eingang eines Wechselventils 67 an, wobei der andere Eingang des Wechselventils 67 der einen Wegeventilscheibe mit dem Ausgang des Wechselventils 67 der anderen Wegeventilscheibe verbunden ist. Der andere Eingang des Wechselventils 67 von letzterer Wegeventilscheibe ist über eine Endplatte 68 mit dem Ablaufkanal 37 verbunden. Vom Ausgang des Wechselventils 67 der ersteren Wegeventilscheibe führt ein Kanal zum Lastmeldeanschluss LS dieser Scheibe. An diesem Anschluss LS steht der höchste Lastdruck der mit den beiden Wegeventilen betätigbaren hydraulischen Verbraucher an. Der Druck im Zulaufkanal 36 liegt um eine vorgegebene Druckdifferenz von z. B. 15 bar über dem höchsten Lastdruck. Das Druckäquivalent zur Kraft der Druckfeder 66 einer Druckwaage 65 kann ebenfalls 15 bar betragen, so dass unabhängig davon, ob nun ein hydraulischer Verbraucher den höchsten Lastdruck erzeugt oder nicht, der Druckabfall über die Zumessblende des jeweiligen Wegeventils derselbe ist.The pressure after the metering orifice corresponds to the load pressure of the respective hydraulic consumer. This pressure is also applied to an input of a
Bei dem Ausführungsbeispiel nach
Das Druckbegrenzungsventil 50 nach beiden Ausführungsbeispielen ist hydraulisch verstellbar und besitzt dazu einen Stellkolben 73, der an eine Druckkammer 74 angrenzt und eine durch den Abstand zweier Anschläge voneinander und seine Länge vorgegebene Wegstrecke bewegbar ist. Eine Regelfeder 75 des Druckbegrenzungsventils 50 ist minimal vorgespannt, wenn der Stellkolben am einen Anschlag anliegt, und maximal vorgespannt, wenn der Stellkolben am anderen Anschlag anliegt. Der Druck, bei dem das Druckbegrenzungsventil 50 anspricht, kann also zwischen einem minimalen und einem maximalen Wert eingestellt werden. Auf welche Weise das Druckbegrenzungsventil 50 verstellbar ist, geht näher aus
Dort sind zwei hydraulische Vorsteuergeräte 78 erkennbar, die beide in allgemein bekannter Weise auf der Basis von direktgesteuerten Druckreduzierventilen 79 arbeiten, von denen eines symbolhaft in jedes Vorsteuergerät eingezeichnet ist. Jedes Vorsteuergerät besitzt insgesamt vier Vorsteuerventile 79 und entsprechend vier Steuerausgänge 80. Außerdem besitzt jedes Vorsteuergerät einen Tankanschluss T und einen Druckanschluss P, an dem ein weitgehend konstanter Versorgungsdruck in einer Höhe zwischen 30 und 35 bar ansteht. Über einen Vorsteuerhebel 81, der aus einer Mittelstellung heraus, in der an allen Steuerausgängen 80 Tankdruck ansteht, nach vier Richtungen ausgelenkt werden kann, können die Vorsteuerventile 79 verstellt werden. Je nach Hebelauslenkung regeln sie am entsprechenden Steuerausgang 80 einen bestimmten Vorsteuerdruck ein. Von den Steuerausgängen 80 führen Vorsteuerleitungen 82 zu den Steuerdruckräumen 62 und 63 der Wegeventile 38 (
Von jeder Vorsteuerleitung 82 geht eine Zweigleitung 83 ab, in der sich hintereinander eine Düse 84 und ein zu der Vorsteuerleitung hin sperrendes Rückschlagventil 85 befinden. Stromab der Rückschlagventile 85 münden alle Zweigleitungen 83 in eine gemeinsame Steuerleitung 86, die zu der Druckkammer 74 des Druckbegrenzungsventils 50 führt. Alle Vorsteuerleitungen 82 sind also parallel zueinander über jeweils eine Düse 84 und ein Rückschlagventil 85 mit der Druckkammer 74 des Druckbegrenzungsventils 50 verbunden.From each
Die Steuerleitung 86 ist außerdem noch an einen ersten Anschluss eines 3/2 Wegeventil 87 angeschlossen, von dem ein zweiter Anschluss mit der den Versorgungsdruck führenden Leitung und von dem ein dritter Anschluss mit dem Eingang eines zweiten Druckbegrenzungsventils 88 verbunden ist. In einer Ruhestellung, die das Wegeventil 87 unter der Wirkung einer Druckfeder 89 einnimmt, ist die Steuerleitung 86 mit dem Druckbegrenzungsventil 88 verbunden. Der zweite Anschluss ist abgesperrt. Das Wegeventil 87 kann mit Hilfe eines Elektromagneten 90 in eine Schaltstellung gebracht werden, in der die Steuerleitung 86 mit dem zweiten Anschluss verbunden und der dritte Anschluss abgesperrt ist. Der Elektromagnet 90 ist über eine elektrische Leitung mit einem in dem einen Vorsteuerhebel 81 untergebrachten elektrischen Schalter verbunden, der über einen Druckknopf 91 betätigt werden kann. Über den Druckknopf 91 kann also der Elektromagnet 90 angesteuert und abgeschaltet werden. Das Druckbegrenzungsventil 88 ist manuell verstellbar. Es dient zusammen mit den Düsen 84 dazu, in der Ruhestellung des Wegeventils 87 den Druck in der Steuerleitung 86 auf einen Wert begrenzen zu können, der niedriger ist als der maximale durch ein Druckreduzierventil 79 einregelbare Vorsteuerdruck. Über ein Stromregelventil 92 kann die Steuerleitung 86 zum Tank 11 entlastet werden.The
Für die Betrachtung der Funktionsweise der Steueranordnung seien folgende Annahmen gemacht:
- Der Versorgungsdruck für die
Vorsteuergeräte beträgt 30 bar.Mit den Druckreduzierventilen 79 können Vorsteuerdrücke bis zu 25 bar proportional eingeregelt werden, wobei dieVerstellung der Hauptsteuerventile 38 bzw. 57 bei 5 bar beginnt und deren voller Hub bei 25 bar erreicht wird.Das Druckbegrenzungsventil 50 begrenzt bei einem in der Steuerleitung anstehenden Druck bis zu 5 bar wegen einer Anfangsvorspannung derFeder 75 den Druck indem Endabschnitt 26a der Lastmeldeleitung auf 50 bar. Der Einstellwert des Druckbegrenzungsventils 50 steigt linear mit dem Druck inder Steuerleitung 86 an und erreicht bei einemDruck von 25 bar in der Steuerleitung einen Maximalwert von 250 bar.Das Druckbegrenzungsventil 88 ist auf 20 bar eingestellt. Das Pumpen-Apalso die Differenz zwischen demDruck im Endabschnitt 26a der Lastmeldeleitung und dem Druck inder Zulaufleitung 12 beträgt 20 bar.
- The supply pressure for the pilot control units is 30 bar. With the
pressure reducing valves 79 pilot pressures up to 25 bar can be adjusted proportionally, the adjustment of themain control valves 38 and 57 starts at 5 bar and whose full stroke is achieved at 25 bar. Thepressure relief valve 50 limits at a pending in the control line pressure up to 5 bar because of an initial bias of thespring 75, the pressure in theend portion 26a of the load sensing line to 50 bar. The set value of thepressure relief valve 50 increases linearly with the pressure in thecontrol line 86 and reaches a maximum value of 250 bar at a pressure of 25 bar in the control line. Thepressure relief valve 88 is set to 20 bar. The pump Apalso the difference between the pressure in theend portion 26a of the load reporting line and the pressure in thesupply line 12 is 20 bar.
Damit ergibt sich in der gezeigten Ruhestellung des Wegeventils 87 folgende Funktionsweise:
- Wenn ein Vorsteuerhebel ausgelenkt und
ein Druckreduzierventil 79 verstellt wird, baut sich in einerVorsteuerleitung 82 ein Vorsteuerdruck auf. Bis zu einem Vorsteuerdruck von 5 bar tut sich zunächst nichts. Danach beginnt die Bewegung des des Steuerschiebers des angesteuerten Hauptsteuerventils. Nach einem geringen Anfangshub wird die entsprechende Zumessblende immer weiter geöffnet. Der Druck inder Steuerleitung 86 und damit der inder Druckkammer 74 desDruckbegrenzungsventils 50 anstehende Druck ist geringfügig kleiner als der Vorsteuerdruck, nämlich um die Druckdifferenz, die dieüber den Stromregler 92 fließende Druckmittelmenge aneiner Düse 84 erzeugt. Die Druckdifferenz mag zum Beispiel bei 0,5 bar liegen. Somit ist derDruck im Endabschnitt 26a der Lastmeldeleitung bis zu einem Vorsteuerdruck von 5,5bar auf 50 bar begrenzt und steigt mit zunehmendem Vorsteuerdruck an. Ist der Vorsteuerdruck zum Beispiel 15 bar, so ist der Druck inder Steuerleitung 86 14,5 bar und der Druck indem Endabschnitt 26a der Lastmeldeleitung ist auf 145 bar begrenzt.
- When a pilot control lever is deflected and a
pressure reducing valve 79 is displaced, a pilot pressure builds up in apilot line 82. Up to a pilot pressure of 5 bar initially nothing works. Thereafter, the movement of the spool of the controlled main control valve begins. After a small initial stroke, the corresponding metering orifice is opened more and more. The pressure in thecontrol line 86 and thus the pressure in thepressure chamber 74 of thepressure relief valve 50 is slightly smaller than the pilot pressure, namely the pressure difference that generates the current flowing through theflow regulator 92 pressure medium at anozzle 84. The pressure difference may be, for example, 0.5 bar. Thus, the pressure in theend portion 26a of the load-sensing line is limited to 50 bar to a pilot pressure of 5.5 bar and increases with increasing pilot pressure. If the pilot pressure is, for example, 15 bar, then the pressure in thecontrol line 86 is 14.5 bar and the pressure in theend section 26a of the load reporting line is limited to 145 bar.
Ist der Lastdruck des angesteuerten hydraulischen Verbrauchers kleiner als oder gleich 145 bar, so ist die Druckbegrenzung im Endabschnitt 26a ohne Belang. Es steht dort der Lastdruck an. Die Verstellpumpe 10 fördert soviel Druckmittelmenge, dass der Druck in der Zulaufleitung 12 um 20 bar über dem gemeldeten Lastdruck liegt. Der hydraulische Verbraucher wird mit einer Geschwindigkeit bewegt, die durch den Öffnungsquerschnitt der Zumessblende bestimmt ist.If the load pressure of the controlled hydraulic consumer is less than or equal to 145 bar, then the pressure limit in the
Ist der Lastdruck größer als 145 bar, so wird an die Verstellpumpe 10 ein Druck von 145 bar gemeldet, weil nun das Druckbegrenzungsventil 50 den Druck im Endabschnitt 26a nicht höher werden lässt. Der Druck in der Zulaufleitung ist dann 165 bar. Ist der Lastdruck kleiner als 165 bar, so fließt bei offener Druckwaage dem hydraulischen Verbraucher über die Zumessblende weitgehend ungedrosselt eine Druckmittelmenge zu, die sich durch den Öffnungsquerschnitt der Zumessblende und durch die Differenz zwischen dem Zulaufdruck in Höhe von 165 bar und dem Lastdruck ergibt. Es ist damit sowohl bei einer LUDV- Steuerung nach
Ist der Lastdruck höher als 165 bar, so ist nur nach weiterer Auslenkung des Vorsteuerhebels noch eine Druckmittelzufuhr zum hydraulischen Verbraucher möglisch. Ist allerdings der Lastdruck größer als 220 bar, dann muss der Vorsteuerhebel soweit ausgelenkt werden, dass der Druck in der Steuerleitung 86 20 bar wird. Dann spricht das Druckbegrenzungsventil 88 an. Trotz weitere Hebelauslenkung verbleibt der Druck in der Steuerleitung 86 bei 20 bar, damit der Druck im Endabschnitt 26a bei 200 bar und damit der Zulaufdruck bei 220 bar. Dieser Druck von 220 bar steht im Verbraucher an, so dass eine entsprechende Kraft ausgeübt werden kann.If the load pressure is higher than 165 bar, a pressure medium supply to the hydraulic consumer is only possible after further deflection of the pilot control lever. However, if the load pressure is greater than 220 bar, then the pilot control lever must be deflected so far that the pressure in the
Wenn ein hydraulischer Verbraucher mit einem Lastdruck bis zu 250 bar allein durch den Grad der Öffnung der Zumessblende und über den vollen Hub eines Hauptsteuerventils gesteuert werden soll, so wird der Knopf 91 am einen Vorsteuerhebel gedrückt und damit das Wegeventil umgeschaltet. Nun steht der Versorgungsdruck von 30 bar in der Steuerleitung 86 an. Die Rückschlagventile 85 gewährleisten, dass in der jeweiligen Vorsteuerleitung der durch das Vorsteuergerät vorgegebene Vorsteuerdruck herrscht. Das Druckbegrenzungsventil 50 ist auf seinen höchsten Wert von 250 bar eingestellt. Der Druck im Endabschnitt 26a der Lastmeldeleitung ist nun bis zu einem Lastdruck von 250 bar gleich dem Lastdruck. Der Druck in der Zulaufleitung 12 ist 20 bar höher als der Lastdruck. Somit lässt sich eine Last bis zu 250 bar mit einer allein durch den Öffnungsquerschnitt der zugehörigen Zumessblende bestimmten Geschwindigkeit bewegen. Bis zu einem Lastdruck von 270 bar ist wegen der verringerten Druckdifferenz über die Zumessblende eine verlangsamte Bewegung möglich. Bei einem Lastdruck über 270 bar kann die Last nicht mehr bewegt werden.If a hydraulic load with a load pressure up to 250 bar is to be controlled solely by the degree of opening of the metering orifice and the full stroke of a main control valve, the
Bei dem Ausführungsbeispiel nach
Natürlich kann für einzelne Verbraucher oder für eine Bewegungsrichtung auch von der Möglichkeit einer Drucksteuerung abgesehen sein. Dann ist zwischen der entsprechenden Vorsteuerleitung 82 und der Steuerleitung 86 keine Zweigleitung 83 vorhanden. Letztendlich kann eine Zweigleitung auch nur zwischen einer einzigen Vorsteuerleitung 82 und der Steuerleitung 86 vorhanden seinOf course, for individual consumers or for a direction of movement to be apart from the possibility of pressure control. Then, no
Claims (14)
- Hydraulic control arrangement, in particular for controlling hydraulic consumers of a mobile work machine, with a load message line (26) which can be acted upon by the highest load pressure of a plurality of hydraulic consumers activated simultaneously in each case via a main control valve (38, 57) and which can be connected with an end portion (26a) to a pump controller (25), and with a pressure-limiting valve (50), by means of which the control pressure in the end portion (26a) of the load message line (26) can be limited, characterized in that the pressure-limiting valve (50) can be adjusted as a function of the height of a pilot control signal serving for activating a main control valve (38, 57).
- Hydraulic control arrangement according to Claim 1, characterized in that the pressure-limiting valve (50) can be adjusted as a function of the height of a plurality of pilot control signals, and in that, when a plurality of pilot control signals are present, the pressure-limiting valve (50) can be adjusted as a function of the highest pilot control signal.
- Hydraulic control arrangement according to Claim 1 or 2, characterized in that the pressure-limiting valve (50) can be adjusted as a function of a pilot control signal to only a set value which lies below the maximum set value.
- Hydraulic control arrangement according to Claim 1, 2 or 3, characterized in that the pressure-limiting valve (50) can be adjusted to its maximum set value independently of the pilot control signal just present for the main control valve (38, 57).
- Hydraulic control arrangement according to one of the preceding claims, characterized in that the pressure-limiting valve (50) can be adjusted hydraulically and has an actuating piston (73) adjacent to a pressure chamber (74) connected to a control line (86).
- Hydraulic control arrangement according to Claim 5, characterized in that the pilot control signal is a pilot control pressure which is generated by an adjustable pilot control valve (79) from a supply pressure and is present in a pilot control line (82) of a main control valve (38, 57), and in that the pressure chamber (74) of the pressure-limiting valve (50) can be acted upon with the pilot control pressure or with the supply pressure as a function of the switching position of an arbitrarily actuable directional valve (87).
- Hydraulic control arrangement according to Claim 6, characterized in that the pilot control line (82) is connected, via a non-return valve (85) shutting off towards it, to the pressure chamber (74) on the pressure-limiting valve (50).
- Hydraulic control arrangement according to one of Claims 5 to 7, characterized in that a plurality of pilot control lines (82) capable of being acted upon by a pilot control pressure lead to one or more main control valves (38, 57), and in that a plurality of pilot control lines (82) are connected parallel to one another, in each case via a non-return valve (85), to the pressure chamber (74) on the pressure-limiting valve (50).
- Hydraulic control arrangement according to one of Claims 6 to 8, characterized in that a second pressure-limiting valve (88) is present, by means of which the pressure in the pressure chamber (74) of the first pressure-limiting valve (50) can be limited, which pressure-limiting valve is set at a limit pressure lying below the maximum pilot control pressure and can be actively switched when the pressure chamber (74) of the first pressure-limiting valve (50) can be acted upon by a pilot control pressure.
- Hydraulic control arrangement according to Claim 9, characterized in that the second pressure-limiting valve (88) can be set manually.
- Hydraulic control arrangement according to one of Claims 6 to 10, characterized in that the directional valve (87) has a first switching position, in which the second pressure-limiting valve (88) is connected to the pressure chamber (74) of the first pressure-limiting valve (50) and the pressure chamber (74) is separated from the supply pressure, and a second switching position, in which the second pressure-limiting valve (88) is separated from the pressure chamber (74) of the first pressure-limiting valve (50) and the pressure chamber (74) can be acted upon by supply pressure.
- Hydraulic control arrangement according to Claim 11, characterized in that the first switching position is the position of rest of the directional valve (87).
- Hydraulic control arrangement according to one of Claims 5 to 12, characterized in that a flow control valve (92), via which pressure fluid can be drained out of the control line (86) to a reservoir (T) in order to lower the pressure, is connected to the control line (86).
- Hydraulic control arrangement according to Claim 13, characterized in that the flow control valve (92) is a flow-regulating valve.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006018706A DE102006018706A1 (en) | 2006-04-21 | 2006-04-21 | Hydraulic control arrangement |
PCT/EP2007/003280 WO2007121873A1 (en) | 2006-04-21 | 2007-04-13 | Hydraulic control arrangement |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2013487A1 EP2013487A1 (en) | 2009-01-14 |
EP2013487B1 true EP2013487B1 (en) | 2012-08-15 |
Family
ID=38372345
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07724220A Not-in-force EP2013487B1 (en) | 2006-04-21 | 2007-04-13 | Hydraulic control arrangement |
Country Status (5)
Country | Link |
---|---|
US (1) | US8281583B2 (en) |
EP (1) | EP2013487B1 (en) |
JP (1) | JP5174804B2 (en) |
DE (1) | DE102006018706A1 (en) |
WO (1) | WO2007121873A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014004337B4 (en) | 2013-03-28 | 2023-04-27 | Aebi Schmidt Deutschland Gmbh | Municipal vehicle and method for adjusting pump outlet pressures of a variable displacement pump |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008061350A1 (en) * | 2008-12-10 | 2010-06-17 | Robert Bosch Gmbh | Hydrostatic system with a hydropneumatic accumulator |
DE102013220750A1 (en) * | 2013-10-15 | 2015-04-16 | Robert Bosch Gmbh | Valve block with a valve assembly |
JP6619163B2 (en) * | 2015-06-17 | 2019-12-11 | 日立建機株式会社 | Work machine |
DE102015218832A1 (en) * | 2015-09-30 | 2017-03-30 | Robert Bosch Gmbh | Pump-controller combination with power limitation |
JP7095589B2 (en) * | 2018-12-26 | 2022-07-05 | 株式会社豊田自動織機 | Hydraulic drive for industrial vehicles |
DE102020205365A1 (en) | 2020-04-28 | 2021-10-28 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hydrostatic linear drive |
US11608616B2 (en) | 2020-09-30 | 2023-03-21 | Kubota Corporation | Hydraulic system for working machine |
CN112594240B (en) * | 2020-12-24 | 2023-02-03 | 山推工程机械股份有限公司 | Hydraulic system of working device, control method and electric loader |
US11680381B2 (en) * | 2021-01-07 | 2023-06-20 | Caterpillar Underground Mining Pty. Ltd. | Variable system pressure based on implement position |
CN113152575B (en) * | 2021-05-19 | 2022-11-25 | 徐州徐工挖掘机械有限公司 | Hydraulic bridge circuit based set pilot positive flow control system |
US11834811B2 (en) * | 2021-10-25 | 2023-12-05 | Cnh Industrial America Llc | System and method for controlling hydraulic pump operation within a work vehicle |
Family Cites Families (38)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2946347A (en) * | 1959-04-22 | 1960-07-26 | New York Air Brake Co | Control valve having a movable member containing combination check and relief valve unit |
US4083382A (en) * | 1976-06-03 | 1978-04-11 | J. I. Case Company | Regulating valve with hydraulic detent |
FR2376978A1 (en) | 1977-01-06 | 1978-08-04 | Rexroth Sigma | IMPROVEMENTS TO FLUID DISTRIBUTOR DEVICES, ESPECIALLY FOR HYDRAULIC REMOTE CONTROL |
JPS5410734A (en) * | 1977-06-27 | 1979-01-26 | Sharp Corp | Ink supply device for ink jet printer |
US4355660A (en) * | 1980-04-15 | 1982-10-26 | General Signal Corporation | Pneumatically controlled, four position hydraulic valve |
DE3422978C2 (en) | 1984-06-22 | 1995-07-20 | Bosch Gmbh Robert | Device for controlling a hydraulic actuating device |
DE3513452A1 (en) * | 1985-04-15 | 1986-10-16 | Mannesmann Rexroth GmbH, 8770 Lohr | HYDRAULIC SYSTEM FOR SUPPLYING A HYDROSTATIC STEERING |
DE3709504C2 (en) | 1987-03-23 | 1995-02-02 | Rexroth Mannesmann Gmbh | Valve device |
WO1990010795A1 (en) | 1989-03-13 | 1990-09-20 | Hitachi Construction Machinery Co., Ltd. | Hydraulic driving unit for working machine |
JPH0351201A (en) | 1989-07-18 | 1991-03-05 | Daiken Iki Kk | Waste collecting bag |
JPH0351201U (en) * | 1989-09-26 | 1991-05-17 | ||
JP2557000B2 (en) * | 1990-05-15 | 1996-11-27 | 株式会社小松製作所 | Control valve device |
JPH04136507A (en) * | 1990-09-28 | 1992-05-11 | Komatsu Ltd | Hydraulic circuit |
US5138838A (en) * | 1991-02-15 | 1992-08-18 | Caterpillar Inc. | Hydraulic circuit and control system therefor |
DE4308004C2 (en) | 1992-04-04 | 2000-10-12 | Mannesmann Rexroth Ag | Hydraulic control device for multiple consumers |
FR2689575B1 (en) * | 1992-04-06 | 1994-07-08 | Rexroth Sigma | HYDRAULIC DISTRIBUTOR WITH PRESSURE COMPENSATION AND A MAXIMUM PRESSURE SELECTION FOR DRIVING A PUMP AND MULTIPLE HYDRAULIC CONTROL INCLUDING SUCH DISTRIBUTORS. |
SE503750C2 (en) * | 1995-05-15 | 1996-08-19 | Nordwin Ab | Hydraulic directional valve |
FI955172A0 (en) | 1995-10-30 | 1995-10-30 | Sakari Pinomaeki | Foerfarande i ett tryckmediumsystem och ett tryckmediumsystem |
FR2744497B1 (en) * | 1996-02-07 | 1998-04-03 | Rexroth Sigma | MULTIPLE HYDRAULIC DISTRIBUTION DEVICE |
DE19608801C2 (en) | 1996-03-07 | 2000-06-08 | Oil Control Gmbh | Hydraulic load holding or lowering brake valve |
KR100208732B1 (en) * | 1996-05-21 | 1999-07-15 | 토니헬샴 | Control valve for a heavy equipment |
US6334308B1 (en) * | 1998-03-04 | 2002-01-01 | Komatsu Ltd. | Pressure compensating valve, unloading pressure control valve and hydraulically operated device |
CA2297040C (en) * | 1998-05-28 | 2005-08-09 | Plustech Oy | Method for adjusting supply pressure |
DE19828963A1 (en) * | 1998-06-29 | 1999-12-30 | Mannesmann Rexroth Ag | Hydraulic switch system for the operation of low- and high-load units |
US6349543B1 (en) * | 1998-06-30 | 2002-02-26 | Robert Moshe Lisniansky | Regenerative adaptive fluid motor control |
DE19831595B4 (en) | 1998-07-14 | 2007-02-01 | Bosch Rexroth Aktiengesellschaft | Hydraulic circuit |
JP2000170707A (en) * | 1998-12-02 | 2000-06-20 | Hitachi Constr Mach Co Ltd | Directional control valve |
DE19948232A1 (en) | 1999-07-10 | 2001-01-11 | Mannesmann Rexroth Ag | Directional valve disc, especially for a mobile working device |
DE19949802A1 (en) | 1999-10-15 | 2001-04-19 | Mannesmann Rexroth Ag | Manual input control of hydraulic and electrohydraulic valves through joystick movement and operation of switches |
DE19958257B4 (en) | 1999-12-03 | 2008-04-24 | Bosch Rexroth Aktiengesellschaft | Semi-open hydraulic circuit |
EP1170510B1 (en) | 2000-07-08 | 2005-08-17 | Bosch Rexroth AG | Hydraulic control arrangement for supplying pressurised fluid preferably to several hydraulic loads |
US6581639B2 (en) * | 2000-10-20 | 2003-06-24 | Case Corporation | Low leak boom control check valve |
US6694860B2 (en) * | 2001-12-10 | 2004-02-24 | Caterpillar Inc | Hydraulic control system with regeneration |
DE10325294A1 (en) * | 2003-06-04 | 2004-12-23 | Bosch Rexroth Ag | Hydraulic control arrangement |
JP2006125627A (en) | 2004-09-29 | 2006-05-18 | Kobelco Contstruction Machinery Ltd | Hydraulic circuit of construction machinery |
KR100611713B1 (en) * | 2004-10-14 | 2006-08-11 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | Hydraulic control valve with regeneration function |
DE102005005928A1 (en) | 2004-12-10 | 2006-06-14 | Bosch Rexroth Aktiengesellschaft | Control arrangement e.g. for controlling hydraulic directional valve, has two pilot valves connected over control pressure pipe where actuating pressure adjusts selector valve |
DE102005005927A1 (en) | 2005-02-09 | 2006-08-17 | Bosch Rexroth Aktiengesellschaft | Hydraulic control arrangement |
-
2006
- 2006-04-21 DE DE102006018706A patent/DE102006018706A1/en not_active Withdrawn
-
2007
- 2007-04-13 WO PCT/EP2007/003280 patent/WO2007121873A1/en active Application Filing
- 2007-04-13 US US12/297,410 patent/US8281583B2/en not_active Expired - Fee Related
- 2007-04-13 EP EP07724220A patent/EP2013487B1/en not_active Not-in-force
- 2007-04-13 JP JP2009505756A patent/JP5174804B2/en not_active Expired - Fee Related
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014004337B4 (en) | 2013-03-28 | 2023-04-27 | Aebi Schmidt Deutschland Gmbh | Municipal vehicle and method for adjusting pump outlet pressures of a variable displacement pump |
Also Published As
Publication number | Publication date |
---|---|
DE102006018706A1 (en) | 2007-10-25 |
JP2009534596A (en) | 2009-09-24 |
WO2007121873A1 (en) | 2007-11-01 |
US20090094972A1 (en) | 2009-04-16 |
JP5174804B2 (en) | 2013-04-03 |
EP2013487A1 (en) | 2009-01-14 |
US8281583B2 (en) | 2012-10-09 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2013487B1 (en) | Hydraulic control arrangement | |
EP0760908B1 (en) | Control arrangement for at least two hydraulic consumers | |
EP1149246B1 (en) | Control arrangement for at least two hydraulic consumers and pressure differential valve for said control arrangement | |
DE4036720C2 (en) | Control circuit for the load-independent distribution of a pressure medium flow | |
DE4027047C2 (en) | ||
EP1200743B1 (en) | Hydraulic control system for load-sensing controlled supply of hydraulic fluid for preferably several hydraulic consumers | |
WO2001002736A1 (en) | Hydraulic control device for supplying a pressure means to preferably, several hydraulic consumers | |
DE102006040234A1 (en) | LS control arrangement | |
EP1170510B1 (en) | Hydraulic control arrangement for supplying pressurised fluid preferably to several hydraulic loads | |
EP1497559B1 (en) | Hydraulic control system using load-sensing technology | |
DE4210252C1 (en) | ||
WO2007039249A1 (en) | Hydraulic control device | |
WO2016091528A1 (en) | Hydraulic valve arrangement, hydraulic valve block with such a valve arrangement, and hydraulic drive comprising such a valve block | |
DE19646427A1 (en) | Valve arrangement for control of hydraulic equipment of e.g. lifting gear of land cultivator | |
EP0746690B1 (en) | Hydraulic pump control system | |
DE19603899A1 (en) | Hydraulic control device for supplying pressure medium to several hydraulic consumers | |
WO1999037929A1 (en) | Hydraulic system for operating a reversible hydraulic consumer | |
DE19530234C2 (en) | Actuating device for a sliding roof on a machine, in particular on a machine tool or plastic processing machine | |
EP2176556A1 (en) | Control arrangement and method for controlling at least two hydraulic consumers | |
DE10035575A1 (en) | Hydraulic control arrangement for supplying pressure medium to preferably several hydraulic consumers | |
DE102023205767B3 (en) | Hydraulic valve assembly and mobile hydraulics | |
DE10119276A1 (en) | Hydraulic control circuit for primary and secondary hydraulic loads where the primary load is the priority load and the control circuit ensures it has an adequate pressure supply | |
WO2003074883A1 (en) | Valve arrangement | |
DE19520451C1 (en) | Hydraulic system | |
DE10353049A1 (en) | Load sensing control system to control consumers of working machine has two tank passage sections interconnected via adjustable counterbalance valve unit for balance of hydraulic medium feed between pressure chambers of consumers |
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 |
|
17P | Request for examination filed |
Effective date: 20081121 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA HR MK RS |
|
17Q | First examination report despatched |
Effective date: 20101112 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
DAX | Request for extension of the european patent (deleted) | ||
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 BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 570995 Country of ref document: AT Kind code of ref document: T Effective date: 20120815 Ref country code: CH Ref legal event code: EP Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502007010388 Country of ref document: DE Effective date: 20121011 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: VDEP Effective date: 20120815 |
|
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: 20120815 Ref country code: IS 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: 20121215 Ref country code: FI 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: 20120815 Ref country code: LT 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: 20120815 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV 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: 20120815 Ref country code: SI 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: 20120815 Ref country code: PL 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: 20120815 Ref country code: SE 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: 20120815 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: 20121116 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: 20121217 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20120815 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: EE 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: 20120815 Ref country code: CZ 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: 20120815 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: 20120815 Ref country code: RO 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: 20120815 Ref country code: ES 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: 20121126 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK 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: 20120815 |
|
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: 20130516 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG 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: 20121115 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20130627 Year of fee payment: 7 Ref country code: GB Payment date: 20130422 Year of fee payment: 7 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20130429 Year of fee payment: 7 Ref country code: FR Payment date: 20130523 Year of fee payment: 7 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502007010388 Country of ref document: DE Effective date: 20130516 |
|
BERE | Be: lapsed |
Owner name: ROBERT BOSCH G.M.B.H. Effective date: 20130430 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC 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: 20120815 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20130430 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20130430 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20130430 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20130413 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 570995 Country of ref document: AT Kind code of ref document: T Effective date: 20130413 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20130413 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502007010388 Country of ref document: DE |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20140413 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502007010388 Country of ref document: DE Effective date: 20141101 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20141231 |
|
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: 20141101 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20140413 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT 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: 20120815 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20140430 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20140413 |
|
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: 20120815 |
|
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: 20130413 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20070413 |