EP1812715B1 - Hydraulic control arrangement - Google Patents

Hydraulic control arrangement Download PDF

Info

Publication number
EP1812715B1
EP1812715B1 EP05799204A EP05799204A EP1812715B1 EP 1812715 B1 EP1812715 B1 EP 1812715B1 EP 05799204 A EP05799204 A EP 05799204A EP 05799204 A EP05799204 A EP 05799204A EP 1812715 B1 EP1812715 B1 EP 1812715B1
Authority
EP
European Patent Office
Prior art keywords
pressure
pressure compensator
power
control arrangement
beyond
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP05799204A
Other languages
German (de)
French (fr)
Other versions
EP1812715A2 (en
Inventor
Gerhard Keuper
Peter Stachnik
Heinrich Lödige
Sönke Jessen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1812715A2 publication Critical patent/EP1812715A2/en
Application granted granted Critical
Publication of EP1812715B1 publication Critical patent/EP1812715B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/634—Electronic controllers using input signals representing a state of a 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6656—Closed loop control, i.e. control using feedback

Definitions

  • the invention relates to a hydraulic control arrangement for controlling a plurality of consumers according to the preamble of patent claim 1 and a control method for such a hydraulic control arrangement.
  • Such hydraulic control arrangements are used in particular in mobile work equipment, such as wheel loaders or tractors to provide their consumers, such as the working hydraulics, the steering or traction drives and accessories with pressure medium.
  • a closed-center system is known in which the pressure medium supply via an electrically controlled variable displacement pump.
  • the variable displacement pump is assigned a bypass valve, via which a connection to a tank can be opened.
  • the adjustment of the variable displacement pump, the bypass valve and the closed-center valves connected upstream of the consumer is carried out electrically via control devices, inter alia as a function of the pump pressure and of the path of one of the valve slides of the closed-center valves.
  • control devices inter alia as a function of the pump pressure and of the path of one of the valve slides of the closed-center valves.
  • a so-called power beyond connection which may have a pressure line, a return line and an LS line.
  • This power-beyond connection makes the load-sensing system of the implement also usable for the attachment.
  • Such solutions are for example from the DE 102 14 850 A1 and the DE 42 39 109 C1 known. From the EP1 245 834 A1 a control arrangement according to the preamble of claim 1 is known.
  • the invention has the object to provide a control method and a hydraulic control arrangement in which at least one power beyond consumer to a power beyond connection a pressure medium supply of all consumers is improved over the known solutions.
  • the hydraulic control arrangement has a pump whose flow rate is adjustable and over which at least one consumer can be supplied with pressure medium.
  • the consumer is connected upstream of a metering orifice, via which the pressure medium volume flow to the consumer is set.
  • the pump is followed by an inlet pressure compensator, via which a connection can be opened to a tank line leading to a tank.
  • the control arrangement further has a power beyond connection to which a power beyond consumer is connected.
  • the control of the inlet pressure compensator in dependence on the largest of those load pressures applied to the consumers of Steueranordung and the power beyond consumers. D.
  • the load pressure of the power beyond consumer is used to adjust the pressure in a pump or supply line determining incoming pressure compensator, so that by their appropriate setting disturbance by the power beyond consumer is almost impossible.
  • Such disorders occur at the beginning of the described Technology especially at low load pressure and high pressure medium volume flow.
  • the pump and / or the metering orifices of the consumers are controlled in such a way that, when the power beyond consumer is supplied via the inlet pressure compensator, a predetermined residual volume flow to the tank is established in order to avoid undersupply.
  • the pump is adjusted depending on the setting of the inlet pressure compensator. This can be done for example by measuring the residual volume flow or by position sensing a slider of the inlet pressure compensator.
  • the pressure medium supply of the power beyond consumers takes place either via the inlet pressure compensator or via power beyond individual pressure compensators.
  • the inlet pressure compensator is preferably acted upon by the largest of the load pressures in the closing direction.
  • the inlet pressure compensator is then designed in a preferred embodiment, that in a spring-biased position the connection to the priority consumer and the tank is shut off and when adjusting the inlet pressure compensator in the opening direction, the connection to the priority consumer and then to the tank is aufêtbar. A sufficient supply of the priority consumer is ensured when the said residual volume flow flows to the tank.
  • a second or more power beyond consumers can be supplied with pressure medium either simultaneously or in a predetermined order of priority via the inlet pressure compensator.
  • a priority for example, the second power beyond consumers a power beyond pressure scale be upstream, in the closing direction of the force of a spring and the same control pressure as the inlet pressure compensator and in the opening direction of the at the entrance of the power beyond Pressure compensator applied pressure applied.
  • This power beyond pressure compensator opens only when the pressure medium supply of the former power beyond consumer is secured.
  • the inlet pressure compensator and the power beyond pressure compensator in the closing direction of the largest of the load pressures applied.
  • the inlet pressure compensator and the power beyond pressure compensator are loaded in the opening direction by the highest of the load pressures.
  • the inlet pressure compensator can also be acted upon in the opening direction by the highest of the load pressures, in which case the pressure downstream of the diaphragm also acts in the opening direction on the power beyond pressure compensator.
  • the pump can be designed as an electrically controllable variable displacement pump or as a variable speed fixed displacement pump.
  • the hydraulic control arrangement is embodied as an LS system, wherein each of the metering orifices assigned to a consumer is preceded by an individual pressure compensator.
  • the springs of the individual pressure compensators assigned to the consumers, the power beyond pressure compensators associated with the power beyond consumers, and the inlet pressure compensator are matched to one another such that either consumers or power beyond consumers are prioritized.
  • the opening pressure difference of the inlet pressure compensator is set to be greater than the opening pressure differential of the individual pressure compensators and the power beyond pressure compensators, wherein the opening pressure difference across the power beyond pressure compensators may be greater or smaller than that via the individual pressure compensators, depending on prioritization.
  • the adjustment of the metering orifices can be done electrically, hydraulically or mechanically.
  • the tapping of the highest of the load pressures is preferably carried out via a shuttle valve, at one input of the highest load pressure of the consumer and at the other input, the highest load pressure of the power beyond consumer is applied, so that at the output of the larger of these load pressures tapped and fed to the inlet pressure compensator can be.
  • FIG. 1 shows a hydraulic control arrangement 1 of a mobile implement, such as a tractor.
  • This control arrangement can be formed for example by a mobile control block, via which the hydraulic consumers of the working hydraulics of the working device, in the present case two double-acting cylinders 2, 4 are supplied with pressure medium, which is supplied by a pump 6 and returned by the consumers to a tank T.
  • the pump 6 is in the illustrated embodiment as electrically controllable variable displacement pump whose pivot angle is adjustable via a pump regulator 8.
  • a variable speed fixed displacement pump or the like can be used.
  • the sucked by the pump 6 from the tank T pressure fluid is conveyed into a pump line 10, which branches into two supply lines 12, 14, wherein the supply line 12 to the cylinder 2 and the supply line 14 is assigned to the cylinder 4.
  • the pressure medium volume flow Q VW delivered by the pump 6 is branched into partial pressure medium volume flows Q VW1 and Q VW2 .
  • the supply lines 12, 14 are each connected to an input port P of a continuously variable directional control valve 16 or 18, through which the pressure medium flow direction to or from the consumer and the pressure medium volume flow can be adjusted.
  • the actuation of the two-way valves 16, 18 via one or more pilot control devices 36, via the control spaces of the directional control valves 16, 18 are acted upon with a control pressure to the valve spool from its illustrated locking position (closed center) in the indicated positions (a) or ( b) to adjust, in which either the cylinder chamber 28, 30 or the annulus 32, 34 is supplied with pressure medium, while the pressure medium is then displaced from the respective other pressure chamber.
  • a Zulaufmeßblende is controlled via an inlet control edge, whose opening cross-section determines the pressure medium volume flow to the cylinder 2, 4.
  • the pressure medium flowing back from the cylinder 2, 4 is returned to the tank T via a tank connection T and a tank line 38 connected thereto.
  • FIG. 1 is characterized by the flow lines 20, 22 inflowing pressure medium flow with Q A1 , Q A2 and the outflowing pressure medium flow with Q B1 and Q B2 .
  • the indicated pressures p A1 , p B1 , p A2 and p B2 are then in each case in the lines.
  • each directional control valve 16, 18 Upstream of each directional control valve 16, 18 is in the corresponding flow line 12 and 14, a LS or individual pressure compensator 40, 42 is provided, which is acted upon in the opening direction respectively by the force of a pressure compensator spring 44 and 46 and the load applied to the respective load 2, 4 , In the closing direction acts on the pressure compensator slide of the individual pressure compensators 40, 42 respectively, the pressure in the pressure medium flow path between the output of the respective individual pressure compensator 40, 42 and the input of the downstream directional control valve 16, 18.
  • a flow regulator is formed over which the pressure drop across the orifice can be kept constant independent of the load.
  • the control arrangement further has an inlet pressure compensator 52, which is arranged in a branch line 54 branching off from the pump line 10. Via the inlet pressure compensator 52, a connection to the tank T can be opened.
  • control arrangement 1 substantially corresponds to the structure as described in the aforementioned prior art.
  • power beyond consumer 50 To connect a device with an additional hydraulic consumer to the mobile implement, such as a loading wagon or a potato harvester, the system is provided with a power beyond port to which this additional consumer, hereinafter referred to as power beyond consumer 50, can be connected.
  • the inlet pressure compensator 52 is designed as a 3/3-way pressure balance, the slide in the closing direction of the force of a spring 56 and the pressure applied to the output of a pressure compensating valve 58 pressure and in the closing direction of the pressure in the branch line 54 and thus the pressure in the pump line 10 is applied.
  • the pressure compensator exchange valve 58 At the inputs of the pressure compensator exchange valve 58, on the one hand, the highest load pressure of the two consumers 2, 4, which is tapped via a shuttle valve 48 and corresponding load reporting lines from the directional control valves 16, 18.
  • the load pressure of the power beyond consumer 50 is applied, which is tapped via a power-beyond-Lastmelde effet 68.
  • the pressure slide of the inlet pressure compensator 52 is acted upon in the closing direction of the highest of the load pressures at the consumers 2, 4 and the power beyond consumer 50 abut.
  • the power beyond consumer 50 is connected via an inlet channel 60 to a working port A of the 3/3-way pressure compensator.
  • the flowing away from the power beyond consumer 50 pressure medium is passed through a drain passage 64 in the tank line 38.
  • a tank channel 62 leading to the tank T is connected.
  • the opening pressure difference ⁇ PEDW which must be applied to fully open the inlet pressure compensator 52, is determined by the force of the spring 56.
  • the path of the valve spool of the input pressure compensator 52 is detected via a displacement sensor 66 and converted into a signal which is applied to a signal input of the pump controller 8, so that the adjustment of the pump in response to the path of the pressure compensator slide of the inlet pressure compensator 52 takes place.
  • the inlet pressure compensator 52 When the power beyond consumer 50 is not actuated or not connected, the inlet pressure compensator 52 is closed and the working hydraulics of the tractor (cylinders 2, 4) are supplied with pressure medium. Upon actuation of the power beyond consumer 3, the inlet pressure compensator 52 is adjusted in the opening direction, so that it can be supplied with pressure medium. The pump 6 is adjusted in response to the path of the pressure compensator slide of the inlet pressure compensator 52 so that a small residual volume flow flows through the tank port T - (the inlet pressure compensator 52 is then open to the power beyond consumer 50 and the tank T out). This ensures that all consumers 2, 4 and the power beyond consumer 50 are adequately supplied with pressure medium.
  • control of the pump 6 takes place in dependence on the path of the Pressure compensator valve of the inlet pressure compensator 52, alternatively, the residual volume flow flowing out to the tank T could also be detected and used to set the pump 6.
  • the actual path of the pressure compensator valve corresponding signal Y EDWist is compared with a stored in a data storage setpoint - the adjustment of the pump 6 then takes place in response to this control difference via a control algorithm.
  • the opening pressure difference of the input pressure compensator 52 will generally be greater than the opening pressure difference of the individual pressure compensators 40, 42, d. h.,
  • the spring 56 is stronger than the pressure compensator springs 44, 46th
  • FIG. 2 illustrated embodiment corresponds in principle to in Fig. 1 illustrated solution, but instead of a single consumer two power beyond consumers 50, 70 are driven.
  • the inlet pressure compensator 52 is designed as a 4/4-way pressure compensator, wherein the input terminal P of the inlet pressure compensator 52 is connected to the branch line 54, while the pressure medium supply of the two power beyond consumers 50, 70 via the Inlet passage 60 and a further inlet channel 72 takes place, which are connected to two output terminals A, B of the pressure compensator 52.
  • the inlet pressure compensator 52 is again acted upon in the closing direction by the force of the spring 56 and the highest load pressure of the consumers 2, 4 and the two power beyond consumers 50, 70, wherein the greater of the load pressures of the two power beyond consumers 50, 70 is tapped via a power beyond shuttle valve 73. In the opening direction, the inlet pressure compensator 52 in turn is acted upon by the pressure at the inlet port P.
  • the inlet pressure compensator 52 is designed so that when inoperative or disconnected power beyond consumers 50, 70, the inlet pressure compensator 52 is shut off. Upon actuation of both power beyond consumers 50, 70, the power beyond consumer 50 is first supplied with pressure medium and on a further displacement of the pressure compensator slide the connection to the other power beyond consumer 70 aufteil.
  • the power beyond consumer 50 is prioritized over the power beyond consumer 70.
  • the inlet pressure compensator 52 is completely open, a residual volume flow flows via the tank channel 62 to the tank T.
  • the path of the pressure compensator slide is detected as in the above embodiment via the transducer 66 and guided via a signal line 74 to a signal port of the pump controller 8 and processed in the manner described above - the adjustment of the pump 6 is again such that a predetermined residual flow to the tank T. flows out, so that a sufficient supply of all consumers and the power beyond consumers 50, 70 is ensured.
  • dargestellen embodiment is the same inlet pressure compensator 52 as in Embodiment according to Fig. 1 used, but over which two power beyond consumers 50, 70 can be supplied with pressure medium.
  • the connected to the output terminal A inlet channel 60 branches into two Zulaufzweigkanäle 76, 78, via which the pressure medium to the power beyond consumer 50 or 70 is performed.
  • a power beyond pressure compensator 80 is provided, which is acted upon in the closing direction by the force of a pressure compensator spring 82 and the highest of the occurring load pressures, which is tapped from the output of the pressure compensator shuttle valve 58.
  • In the opening direction of the power beyond pressure compensator 80 is acted upon by the pressure at its input terminal P.
  • This power beyond pressure compensator 80 is smaller than that of the inlet pressure compensator 52 and the individual pressure compensators 40, 42 chosen.
  • the pressure medium supply of the power beyond consumer 50, 70 always via the inlet pressure compensator 52, which is located in the pressure fluid flow path between the pump line 10 and the associated load 50, 70.
  • the pressure medium supply to the consumer takes place directly, d. h., When bypassing the inlet pressure compensator 52 via associated power beyond pressure compensators.
  • Fig. 4 shows a variant of the control arrangement 1, in which the inlet pressure compensator 52 is designed as a 2/2-way pressure compensator, wherein the input terminal P as in the above-described embodiments is connected to the branch line 54 and the tank port T opens via the tank passage 62 into the tank.
  • the inlet pressure compensator 52 is acted upon by the pressure at the inlet port P in the opening direction and by the force of the spring 56 and the highest applied to the output of the pressure compensating valve 58, the load pressures in the closing direction.
  • the path of the pressure compensator valve spool is in turn detected by a displacement sensor 66 and used to control the pump 6.
  • the pressure medium supply of the power beyond consumer 50 takes place according to Fig. 4 via the power beyond pressure compensator 80, which is acted upon in the opening direction by the pressure in the pump line 10 and in the closing direction by the force of the pressure balance spring 82 and the highest of the load pressures tapped at the outlet of the pressure balance changeover valve 58.
  • the power beyond pressure compensator 80 is arranged in a power beyond feed 84 branching off from the pump line 10.
  • the inlet pressure compensator 52 and the power beyond pressure compensator 80 are arranged in parallel and each designed as a 2/2-way pressure compensator.
  • the opening pressure ⁇ p EDW of the inlet pressure compensator is greater than that of the power beyond pressure compensator 80 ( ⁇ p IDW3 ) and the two individual pressure compensators 40, 42 ( ⁇ p IDW1 , 2), whereby either the opening pressure of the two individual pressure compensators 40, 42 or that of the power Beyond-Druckwaage 80 can be selected larger to set a prioritization. That is, it can first the power beyond consumer 50 or the working hydraulics of the tractor (cylinder 2, 4) are supplied with pressure medium. Also in this embodiment, a supply of all consumers 2, 4, 50 is ensured when the pump 6 is set so that a residual volume flow flows through the inlet pressure compensator 52 to the tank T out.
  • Fig. 5 is a variant of in Fig. 4 shown embodiment, wherein the inlet pressure compensator 52 is not - as in Fig. 4 - parallel, but in series with the power beyond pressure scale 80 is connected. That is, the branch line 54 leading to the input port P of the input pressure compensator 52 does not branch from the pump line 10 but from the inlet port 60 connecting the output port A of the power beyond pressure compensator 80 and the power beyond consumer 50.
  • the input pressure compensator 52 is thus supplied with pressure medium only after the control of the power beyond pressure compensator 80.
  • Both pressure compensators 52, 80 are designed as a 2/2-way pressure compensator and are biased over the highest of the load pressures in the closed position and by the pressure applied in each case at the input P in the open position.
  • the power beyond consumer 50 or the consumers 2, 4 can be prioritized.
  • the opening pressure difference of the inlet pressure compensator 52 is again greater than the opening pressure difference of the individual pressure compensators 40, 42 and the power beyond pressure compensator 80 selected. Otherwise, the function corresponds to that of the embodiment Fig. 4 ,
  • FIG. 6 an embodiment is shown in which two power beyond consumers 50, 70 to be supplied with pressure medium. These are each associated with a power beyond pressure compensator 80 or 86, which are each connected via branching off from the pump line 10 power beyond supply lines 84, 88 with the associated power beyond consumers 50, 70.
  • the two Power Beyond pressure compensators 80, 86 and the inlet pressure compensator 52 are each designed as 2/2-way pressure compensators.
  • the input pressure compensator 52 is biased in this embodiment by the tapped via the pressure compensating valve 58 highest of the load pressures in the opening direction, while in the closing direction, only the spring 56 acts.
  • the output port of the inlet pressure compensator 52 is connected via the tank channel 62 to the tank T.
  • the two power beyond pressure scales 80, 86 are biased only by the force of a pressure compensator spring 82 and 90 in the closing direction, while in the opening direction in this embodiment, the highest of the load pressures acts, which is tapped at the output of the pressure compensator shuttle valve 58.
  • This embodiment allows a variety of functional processes, since depending on the spring selection of the individual pressure compensators 40, 42 and the power beyond pressure scales 80, 86 either the working hydraulics of the tractor (consumers 2, 4) and then the power beyond consumers 50, 70 or vice versa or initially only one of the power beyond consumers, then the working hydraulics and then the other power beyond consumers 70, 50 can be supplied with pressure medium.
  • a residual volume flow will occur when the inlet pressure compensator 52 is open and the pump 6 is actuated in dependence on this residual volume flow or on the position of the pressure compensator piston of the inlet pressure compensator 52 in order to avoid undersupply.
  • Fig. 7 an embodiment is shown with the connection of a power beyond consumer 50, that in the basic structure of that Fig. 4 equivalent.
  • the power beyond consumer 50 is supplied with pressure medium via a power beyond pressure compensator 80 arranged in the power beyond supply line 84.
  • the inlet pressure compensator 52 is arranged in the branch line 54 and acted upon in the opening direction by the pressure in this branch line 54, while in the closing direction, the force of the spring 56 and the tapped on the pressure compensating valve 58 highest load pressure act.
  • the residual volume flow through the inlet pressure compensator 52 to avoid undesirable high pressure drops at the aperture 92 via a parallel to the aperture 92 switched bias valve to the tank.
  • the opening pressure of the individual pressure compensators 40, 42 of Working hydraulics set greater than the opening pressure of the power beyond pressure compensator 80 and the opening pressure of the inlet pressure compensator 52 is - as in all embodiments - preferably greater than that of the individual or power beyond pressure scales selected.
  • Fig. 8 shows an embodiment in which the basis Fig. 7 explained principle for controlling a plurality of power beyond consumers 50, 70 is used.
  • Each of the two power beyond consumers 50, 70 is in each case assigned a power beyond pressure compensator 80, 86, which are arranged in branching off from the pump line 10 power beyond supply lines 84 and 88 and over which the two power Beyond Consumers 50, 70 are supplied with pressure medium.
  • the inlet pressure compensator 52 is formed and interconnected as in the above-described embodiment, wherein the aperture 92 is again provided in the tank channel 62, which generates a control pressure for controlling the two power beyond pressure compensators 80, 86.
  • a pressure medium supply of the two power beyond consumers 50, 70 takes place only when a sufficient control pressure is built up before the aperture 92.
  • the two power beyond consumers 50, 70 can be prioritized by a suitable choice of the pressure balance springs 82, 90 with each other.
  • the concept according to the invention makes it possible to easily connect power beyond consumers and to ensure a desired pressure medium supply of all consumers even under unfavorable operating conditions (for example low load pressure, high pressure medium volume flow).
  • DW pressure compensator
  • PB power beyond consumer
  • ⁇ p the respective opening pressure of the pressure compensators
  • Pressure compensators 52, 80, 86 1P B 2PB Opening pressure ratios of the EDW (52) and IDWs (40, 42, 80, 86) 1 1x3 / 3 DW x ⁇ p EDW > ⁇ p IDW1,2 2 1x4 / 4 DW x ⁇ p EDW > ⁇ p IDW1,2 3 1x3 / 3 12/2 DW x ⁇ p EDW > ⁇ p IW1,2 > ⁇ p IDW3 4 2x2 / 2 DW parallel x ⁇ p EDW > ⁇ p IDW3 > ⁇ p IDW1,2 ⁇ p EDW> ⁇ p IDW1,2 > ⁇ p IDW> ⁇ p IDW1,2 > ⁇ p IDW3 5 2x2 / 2 DW row x ⁇ p EDW> ⁇ p IDW3 ⁇ p IDW1,2 ⁇ p EDW > ⁇ p IDW1,2 > ⁇ p IDW3 6 3x2 / 2 DW parallel x ⁇ p EDW >
  • the use of the invention is possible with the use of electrically adjustable control pumps and variable speed constant displacement pumps, in particular in conjunction with open center and LS valves, which are operated mechanically, electrically or electro-hydraulically.
  • the invention is suitable for all working hydraulic applications of mobile hydraulics whose consumers are not fixed from the outset.
  • a hydraulic control arrangement for controlling a plurality of consumers, in particular a mobile working device, wherein in addition to the consumers of the control arrangement, a power beyond consumer should be connectable to a power beyond port. All consumers and power beyond consumers are supplied by a pump with pressure medium, downstream of the pump, an inlet pressure compensator is provided at the control terminal of the greater of the load pressures of the consumer or the at least one power beyond consumer is present.

Abstract

The invention discloses a hydraulic control arrangement (1) for controlling a number of consumers (2, 4), particularly of a mobile working machine. In addition to the consumers of the control arrangement, an additional consumer (50) should be able to be connected to a power beyond connection. All consumers and power beyond consumers are supplied with hydraulic fluid by a pump (6). An input pressure scale (52) is provided downstream from the pump, and the greater of the load pressures of the consumers or of the at least one power beyond consumer is present on the control connection of said input pressure scale.

Description

Die Erfindung betrifft eine hydraulische Steueranordnung zur Ansteuerung mehrerer Verbraucher gemäß dem oberbegriff des Patentanspruchs 1 sowie ein Regelverfahren für eine derartige hydraulische Steueranordnung.The invention relates to a hydraulic control arrangement for controlling a plurality of consumers according to the preamble of patent claim 1 and a control method for such a hydraulic control arrangement.

Derartige hydraulische Steueranordnungen werden insbesondere bei mobilen Arbeitsgeräten, beispielsweise Radlader oder Schlepper verwendet, um deren Verbraucher, beispielsweise die Arbeitshydraulik, die Lenkung oder Fahrantriebe sowie Zusatzgeräte mit Druckmittel zu versorgen.Such hydraulic control arrangements are used in particular in mobile work equipment, such as wheel loaders or tractors to provide their consumers, such as the working hydraulics, the steering or traction drives and accessories with pressure medium.

Aus der US 5,540,049 ist ein Closed-Center-System bekannt, bei dem die Druckmittelversorgung über eine elektrisch angesteuerte Verstellpumpe erfolgt. Der Verstellpumpe ist ein Bypassventil zugeordnet, über das eine Verbindung zu einem Tank aufsteuerbar ist. Die Ansteuerung der Verstellpumpe, des Bypassventils und von dem Verbraucher vorgeschalteten Closed-Center-Ventilen erfolgt elektrisch über Steuergeräte unter anderem in Abhängigkeit von dem Pumpendruck und von dem Weg eines der Ventilschieber der Closed-Center-Ventile. Bei dieser bekannten Lösung erfolgt somit eine elektronische Geschwindigkeits- oder Kraftregelung/-steuerung der Verbraucher.From the US 5,540,049 is a closed-center system is known in which the pressure medium supply via an electrically controlled variable displacement pump. The variable displacement pump is assigned a bypass valve, via which a connection to a tank can be opened. The adjustment of the variable displacement pump, the bypass valve and the closed-center valves connected upstream of the consumer is carried out electrically via control devices, inter alia as a function of the pump pressure and of the path of one of the valve slides of the closed-center valves. In this known solution thus takes place an electronic speed or force control / control of consumers.

Aus der EP 0 462 589 B1 , der EP 0 432 266 B2 und der DE 41 27 342 C2 sind hydraulische Steueranordnungen bekannt, die als LS-System ausgeführt sind. Bei derartigen LS-Systemen wird die Fördermenge der Pumpe so geregelt, dass in der Pumpenleitung ein um eine bestimmte Druckdifferenz Δp über dem höchsten Lastdruck der Verbraucher liegender Pumpendruck anliegt. Bei den bekannten Systemen.sind jedem Verbraucher eine einstellbare Zumessblende und eine Individualdruckwaage zugeordnet, über die der Druckmittelvolumenstrom zum Verbraucher in Abhängigkeit von der Einstellung der Zumessblende lastunabhängig konstant gehalten werden kann. Bei diesen LS-Systemen kann stromabwärts der Pumpe eine Eingangsdruckwaage vorgesehen werden, über die eine Verbindung zum Tank aufsteuerbar ist. Diese Eingangsdurckwaagen sind in Schließrichtung von einem dem höchsten Lastdruck entsprechenden Steuerdruck beaufschlagt. Die Druckdifferenz, bei der die Eingangsdruckwaage öffnet ist in der Regel geringfügig größer als das über die Pumpe eingestellte Δp.From the EP 0 462 589 B1 , of the EP 0 432 266 B2 and the DE 41 27 342 C2 Hydraulic control arrangements are known, which are designed as LS system. In such LS systems, the flow rate of the pump is so regulated that in the pump line to a by a certain pressure difference .DELTA.p above the highest load pressure of the consumer lying pump pressure is applied. In the known systems, each consumer is assigned an adjustable metering orifice and an individual pressure compensator via which the pressure medium volume flow to the load can be kept constant as a function of the setting of the metering orifice irrespective of the load. In these LS systems downstream of the pump, an inlet pressure compensator can be provided, via which a connection to the tank can be opened. These input weighers are acted upon in the closing direction by a control pressure corresponding to the highest load pressure. The pressure difference at which the inlet pressure compensator opens is usually slightly larger than the Δp set by the pump.

Zum Anschluss von Anbaugeräten oder Zusatzgeräten ohne eigene Druckmittelversorgung ist ein sogenannter Power-Beyond-Anschluss vorgesehen, der eine Druckleitung, eine Rücklaufleitung und eine LS-Leitung aufweisen kann. Dieser Power-Beyond-Anschluss macht das Load-Sensing-System des Arbeitsgerätes auch für das Anbaugerät nutzbar. Derartige Lösungen sind beispielsweise aus der DE 102 14 850 A1 und der DE 42 39 109 C1 bekannt. Aus der EP1 245 834 A1 ist eine Steueranordnung nach dem Oberbegriff von Anspruch 1 bekannt.To connect attachments or attachments without their own pressure medium supply a so-called power beyond connection is provided, which may have a pressure line, a return line and an LS line. This power-beyond connection makes the load-sensing system of the implement also usable for the attachment. Such solutions are for example from the DE 102 14 850 A1 and the DE 42 39 109 C1 known. From the EP1 245 834 A1 a control arrangement according to the preamble of claim 1 is known.

Problematisch bei mit Power-Beyond-Anschlüssen versehenen hydraulischen Steueranordnungen ist, dass keine Informationen über den Druckmittelvolumenstrombedarf des oder der an den Power-Beyond-Anschluss angeschlossenen Verbraucher (Power-Beyond-Verbraucher) vorliegen. Im Fall einer Unterversorgung im System kann es je nach Lastdruck zu einem unkontrollierten Verhalten eines oder mehrerer Verbraucher kommen. Dabei ist es in der Regel nicht möglich, einzelne Verbraucher des Sytems gezielt zurückzufahren, um andere, priorisierte Verbraucher in einer gewünschten Weise zu betreiben.The problem with provided with power beyond ports hydraulic control arrangements is that there is no information about the pressure medium volume flow demand of or connected to the power beyond terminal consumers (power beyond consumers). In the case of an undersupply in the system, depending on the load pressure, uncontrolled behavior of one or more consumers may occur. It is usually not possible to target individual consumers of the system backtrack to operate other, prioritized consumers in a desired manner.

Dem gegenüber liegt der Erfindung die Aufgabe zugrunde, ein Regelverfahren und eine hydraulische Steueranordnung zu schaffen, bei der bei Anschluss zumindest eines Power-Beyond-Verbrauchers an einen Power-Beyond-Anschluss eine Druckmittelversorgung aller Verbraucher gegenüber den bekannten Lösungen verbessert ist.In contrast, the invention has the object to provide a control method and a hydraulic control arrangement in which at least one power beyond consumer to a power beyond connection a pressure medium supply of all consumers is improved over the known solutions.

Diese Aufgabe wird durch eine hydraulische Steueranordung mit den Merkmalen des Patentanspruchs 1 und ein Regelverfahren nach Patentanspruch 19 gelöst.This object is achieved by a hydraulic Steueranordung with the features of claim 1 and a control method according to claim 19.

Erfindungsgemäß hat die hydraulische Steueranordnung eine Pumpe, deren Fördermenge einstellbar ist und über die zumindest ein Verbraucher mit Druckmittel versorgbar ist. Dem Verbraucher ist eine Zumessblende vorgeschaltet, über die der Druckmittelvolumenstrom zum Verbraucher eingestellt wird. Der Pumpe ist eine Eingangsdruckwaage nachgeschaltet, über die eine Verbindung zu einer zu einem Tank führenden Tankleitung aufsteuerbar ist. Die Steueranordnung hat des Weiteren einen Power-Beyond-Anschluss, an den ein Power-Beyond-Verbraucher angeschlossen ist. Erfindungsgemäß erfolgt die Ansteuerung der Eingangsdruckwaage in Abhängigkeit vom größten derjenigen Lastdrücke, die an den Verbrauchern der Steueranordung und den Power-Beyond-Verbrauchern anliegen. D. h., der Lastdruck des Power-Beyond-Verbrauchers wird zur Einstellung der den Druck in einer Pumpen- oder Vorlaufleitung bestimmenden Eingangsdruckwaage verwendet, so dass durch deren geeignete Einstellung eine Störung durch den Power-Beyond-Verbraucher nahezu ausgeschlossen ist. Derartige Störungen treten beim eingangs beschriebenen Stand der Technik insbesondere bei niedrigem Lastdruck und großem Druckmittelvolumenstrom auf.According to the invention, the hydraulic control arrangement has a pump whose flow rate is adjustable and over which at least one consumer can be supplied with pressure medium. The consumer is connected upstream of a metering orifice, via which the pressure medium volume flow to the consumer is set. The pump is followed by an inlet pressure compensator, via which a connection can be opened to a tank line leading to a tank. The control arrangement further has a power beyond connection to which a power beyond consumer is connected. According to the invention, the control of the inlet pressure compensator in dependence on the largest of those load pressures applied to the consumers of Steueranordung and the power beyond consumers. D. h., The load pressure of the power beyond consumer is used to adjust the pressure in a pump or supply line determining incoming pressure compensator, so that by their appropriate setting disturbance by the power beyond consumer is almost impossible. Such disorders occur at the beginning of the described Technology especially at low load pressure and high pressure medium volume flow.

Nach dem erfindungsgemäßen Regelkonzept wird zur Vermeidung einer Unterversorgung die Pumpe und/oder die Zumessblenden der Verbraucher derart angesteuert, dass sich bei Versorgung des Power-Beyond-Verbrauchers über die Eingangsdruckwaage ein vorbestimmter Restvolumenstrom zum Tank hin einstellt. Dabei wird die Pumpe in Abhängigkeit von der Einstellung der Eingangsdruckwaage eingestellt. Dies kann beispielsweise durch Messung des Restvolumenstroms oder durch Lagesensierung eines Schiebers der Eingangsdruckwaage erfolgen.According to the control concept according to the invention, the pump and / or the metering orifices of the consumers are controlled in such a way that, when the power beyond consumer is supplied via the inlet pressure compensator, a predetermined residual volume flow to the tank is established in order to avoid undersupply. The pump is adjusted depending on the setting of the inlet pressure compensator. This can be done for example by measuring the residual volume flow or by position sensing a slider of the inlet pressure compensator.

Erfindungsgemäß erfolgt die Druckmittelversorgung der Power-Beyond-Verbraucher entweder über die Eingangsdruckwaage oder über Power-Beyond-Individualdruckwaagen.According to the invention, the pressure medium supply of the power beyond consumers takes place either via the inlet pressure compensator or via power beyond individual pressure compensators.

Bei der erstgenannten Alternative wird die Eingangsdruckwaage vorzugsweise vom größten der Lastdrücke in Schließrichtung beaufschlagt.In the former alternative, the inlet pressure compensator is preferably acted upon by the largest of the load pressures in the closing direction.

Die Eingangsdruckwaage ist dann bei einem bevorzugten Ausführungsbeispiel so ausgelegt, dass in einer federvorgespannten Grundposition die Verbindung zum Prioritätsverbraucher und zum Tank abgesperrt ist und bei Verstellen der Eingangsdruckwaage in Öffnungsrichtung zunächst die Verbindung zum Prioritätsverbraucher und dann zum Tank aufsteuerbar ist. Eine hinreichende Versorgung des Prioritätsverbrauchers ist dann gewährleistet, wenn der genannte Restvolumenstrom zum Tank abströmt.The inlet pressure compensator is then designed in a preferred embodiment, that in a spring-biased position the connection to the priority consumer and the tank is shut off and when adjusting the inlet pressure compensator in the opening direction, the connection to the priority consumer and then to the tank is aufsteuerbar. A sufficient supply of the priority consumer is ensured when the said residual volume flow flows to the tank.

Für den Fall, dass ein zweiter oder mehrere Power-Beyond-Verbraucher angeschlossen werden, können diese entweder gleichzeitig oder in einer vorbestimmten Prioritätsreihenfolge über die Eingangsdruckwaage mit Druckmittel versorgt werden. Zur Einstellung einer Priorität kann dann beispielsweise dem zweiten Power-Beyond-Verbraucher eine Power-Beyond-Druckwaage vorgeschaltet sein, die in Schließrichtung von der Kraft einer Feder und vom gleichen Steuerdruck wie die Eingangsdruckwaage und in Öffnungsrichtung von dem am Eingang der Power-Beyond-Druckwaage anliegenden Druck beaufschlagt werden. D. h., diese Power-Beyond-Druckwaage öffnet erst, wenn die Druckmittelversorgung des erstgenannten Power-Beyond-Verbrauchers gesichert ist.In the event that a second or more power beyond consumers are connected, they can be supplied with pressure medium either simultaneously or in a predetermined order of priority via the inlet pressure compensator. To set a priority then, for example, the second power beyond consumers a power beyond pressure scale be upstream, in the closing direction of the force of a spring and the same control pressure as the inlet pressure compensator and in the opening direction of the at the entrance of the power beyond Pressure compensator applied pressure applied. D. h., This power beyond pressure compensator opens only when the pressure medium supply of the former power beyond consumer is secured.

Beim zweiten erfindungsgemäßen Konzept, gemäß dem die Power-Beyond-Verbraucher nicht über die Eingangsdruckwaage, sondern über Power-Beyond-Druckwaagen mit Druckmittel versorgbar sind, werden bei einer erfindungsgemäßen Variante die Eingangsdruckwaage und die Power-Beyond-Druckwaage in Schließrichtung vom größten der Lastdrücke beaufschlagt.In the second inventive concept, according to which the power beyond consumers can not be supplied via the inlet pressure balance, but via power beyond pressure scales with pressure medium, in a variant of the invention, the inlet pressure compensator and the power beyond pressure compensator in the closing direction of the largest of the load pressures applied.

Dabei kann es vorteilhaft sein, die Eingangsdruckwaage der Power-Beyond-Druckwaage nachzuschalten, so dass dann die Eingangsdruckwaage praktisch parallel zum Power-Beyond-Verbraucher an den Ausgang der Power-Beyond-Druckwaage angeschlossen ist.It may be advantageous to connect the input pressure balance of the power beyond pressure compensator, so that then the inlet pressure compensator is connected in parallel to the power beyond consumer to the output of the power beyond pressure compensator.

Bei einer alternativen Lösungsvariante sind die Eingangsdruckwaage und die Power-Beyond-Druckwaage in Öffnungsrichtung vom höchsten der Lastdrücke beaufschlagt.In an alternative solution variant, the inlet pressure compensator and the power beyond pressure compensator are loaded in the opening direction by the highest of the load pressures.

Weitere Lösungsmöglichkeiten bestehen darin, wenn die Eingangsdruckwaage in Schließrichtung vom höchsten der Lastdrücke beaufschlagt ist und zwischen dem Ausgang der Eingangsdruckwaage und dem Tank eine Blende vorgesehen ist, wobei der Druck stromaufwärts dieser Blende in Öffnungsrichtung auf die Power-Beyond-Druckwaage wirkt, über die der oder die Power-Beyond-Verbraucher mit Druckmittel versorgt werden.Other possible solutions are when the inlet pressure compensator in the closing direction is acted upon by the highest of the load pressures and provided between the output of the inlet pressure compensator and the tank, a diaphragm is, wherein the pressure upstream of this aperture in the opening direction acts on the power beyond pressure compensator over which the power or beyond consumers are supplied with pressure medium.

Alternativ kann die Eingangsdruckwaage auch in Öffnungsrichtung vom Höchsten der Lastdrücke beaufschlagt werden, wobei dann der Druck stromabwärts der Blende ebenfalls in Öffnungsrichtung auf die Power-Beyond-Druckwaage wirkt.Alternatively, the inlet pressure compensator can also be acted upon in the opening direction by the highest of the load pressures, in which case the pressure downstream of the diaphragm also acts in the opening direction on the power beyond pressure compensator.

Die Pumpe kann als elektrisch steuerbare Verstellpumpe oder als drehzahlgeregelte Konstantpumpe ausgeführt sein.The pump can be designed as an electrically controllable variable displacement pump or as a variable speed fixed displacement pump.

Erfindungsgemäß wird es bevorzugt, wenn die hydraulische Steueranordnung als LS-System ausgeführt ist, wobei jeder der einem Verbraucher zugeordneten Zumessblenden eine Individualdruckwaage vorgeschaltet ist.According to the invention, it is preferred if the hydraulic control arrangement is embodied as an LS system, wherein each of the metering orifices assigned to a consumer is preceded by an individual pressure compensator.

Die Federn der den Verbrauchern zugeordneten Individualdruckwaagen, der den Power-Beyond-Verbrauchern zugeordneten Power-Beyond-Druckwaagen und der Eingangsdruckwaage sind derart aufeinander abgestimmt, dass entweder Verbraucher oder Power-Beyond-Verbraucher priorisiert sind.The springs of the individual pressure compensators assigned to the consumers, the power beyond pressure compensators associated with the power beyond consumers, and the inlet pressure compensator are matched to one another such that either consumers or power beyond consumers are prioritized.

Erfindungsgemäß wird die Öffnungsdruckdifferenz der Eingangsdruckwaage größer als die Öffnungsdruckdifferenz der Individualdruckwaagen und der Power-Beyond-Druckwaagen eingestellt, wobei die Öffnungsdruckdifferenz über den Power-Beyond-Druckwaagen je nach Priorisierung größer oder kleiner als diejenige über den Individualdruckwaagen gewählt sein kann.According to the invention, the opening pressure difference of the inlet pressure compensator is set to be greater than the opening pressure differential of the individual pressure compensators and the power beyond pressure compensators, wherein the opening pressure difference across the power beyond pressure compensators may be greater or smaller than that via the individual pressure compensators, depending on prioritization.

Die Verstellung der Zumessblenden kann elektrisch, hydraulisch oder mechanisch erfolgen.The adjustment of the metering orifices can be done electrically, hydraulically or mechanically.

Das Abgreifen des Höchsten der Lastdrücke erfolgt vorzugsweise über ein Wechselventil, an dessen einem Eingang der höchste Lastdruck der Verbraucher und an dessen anderem Eingang der höchste Lastdruck der Power-Beyond-Verbraucher anliegt, so dass am Ausgang der größere dieser Lastdrücke abgegriffen und zur Eingangsdruckwaage geführt werden kann.The tapping of the highest of the load pressures is preferably carried out via a shuttle valve, at one input of the highest load pressure of the consumer and at the other input, the highest load pressure of the power beyond consumer is applied, so that at the output of the larger of these load pressures tapped and fed to the inlet pressure compensator can be.

Sonstige vorteilhafte Weiterbildungen der Erfindung sind Gegenstand weiterer Unteransprüche.Other advantageous developments of the invention are the subject of further subclaims.

Im Folgenden werden bevorzugte Ausführungsbeispiele der Erfindung anhand schematischer Zeichnungen näher erläutert. Es zeigen:

  • Figuren 1, 2 und 3 Ausführungsbeispiele von erfindungsgemäßen Steueranordnungen, bei denen Power-Beyond-Verbraucher über eine Eingangsdruckwaage mit Druckmittel versorgbar sind und
  • Figuren 4 bis 8 Ausführungsbeispiele, bei denen die Druckmittelversorgung der oder des Power-Beyond-Verbrauchers jeweils über eine Power-Beyond-Druckwaage erfolgt.
In the following preferred embodiments of the invention will be explained in more detail with reference to schematic drawings. Show it:
  • FIGS. 1 . 2 and 3 Embodiments of control arrangements according to the invention, in which power beyond consumers can be supplied via an inlet pressure compensator with pressure medium and
  • FIGS. 4 to 8 Embodiments in which the pressure medium supply of the or the power beyond consumer takes place in each case via a power beyond pressure compensator.

Figur 1 zeigt eine hydraulische Steueranordnung 1 eines mobilen Arbeitsgerätes, beispielsweise eines Ackerschleppers. Diese Steueranordnung kann beispielsweise durch einen Mobilsteuerblock gebildet sein, über den die hydraulischen Verbraucher der Arbeitshydraulik des Arbeitsgerätes, im vorliegenden Fall zwei doppeltwirkende Zylinder 2, 4 mit Druckmittel versorgbar sind, das von einer Pumpe 6 geliefert und von den Verbrauchern zu einem Tank T zurückgeführt wird. Die Pumpe 6 ist beim dargestellten Ausführungsbeispiel als elektrisch steuerbare Verstellpumpe ausgebildet, deren Schwenkwinkel über einen Pumpenregler 8 verstellbar ist. Anstelle einer elektrisch steuerbaren Verstellpumpe kann auch eine drehzahlgeregelte Konstantpumpe oder dergleichen eingesetzt werden. FIG. 1 shows a hydraulic control arrangement 1 of a mobile implement, such as a tractor. This control arrangement can be formed for example by a mobile control block, via which the hydraulic consumers of the working hydraulics of the working device, in the present case two double-acting cylinders 2, 4 are supplied with pressure medium, which is supplied by a pump 6 and returned by the consumers to a tank T. , The pump 6 is in the illustrated embodiment as electrically controllable variable displacement pump whose pivot angle is adjustable via a pump regulator 8. Instead of an electrically controllable variable displacement pump, a variable speed fixed displacement pump or the like can be used.

Das von der Pumpe 6 aus dem Tank T angesaugte Druckmittel wird in eine Pumpenleitung 10 gefördert, die in zwei Zulaufleitungen 12, 14 verzweigt, wobei die Zulaufleitung 12 dem Zylinder 2 und die Zulaufleitung 14 dem Zylinder 4 zugeordnet ist. D. h., der von der Pumpe 6 gelieferte Druckmittelvolumenstrom QVW wird in Teildruckmittelvolumenströme QVW1 und QVW2 verzweigt. Die Zulaufleitungen 12, 14 sind jeweils an einen Eingangsanschluss P eines stetig verstellbaren Wegeventils 16 bzw. 18 angeschlossen, durch das die Druckmittelströmungsrichtung zum bzw. vom Verbraucher und der Druckmittelvolumenstrom einstellbar sind. An Arbeitsanschlüsse A, B der Wegeventile 16, 18 sind Zulaufleitungen 20 bzw. 22 und Rücklaufleitungen 24 bzw. 26 angeschlossen, wobei die Vorlaufleitungen 20, 22 mit einem bodenseitigen Zylinderraum 28 bzw. 30 und die Rücklaufleitungen 24, 26 mit einem kolbenstangenseitigen Ringraum 32 bzw. 34 der Zylinder 2, 4 verbunden sind. Bei entsprechender Betätigung des Wegeventils 16, 18 kann selbstverständlich die als Vor- bzw. Rücklaufleitung bezeichnete Leitung auch als Rück- bzw. Vorlaufleitung wirken.The sucked by the pump 6 from the tank T pressure fluid is conveyed into a pump line 10, which branches into two supply lines 12, 14, wherein the supply line 12 to the cylinder 2 and the supply line 14 is assigned to the cylinder 4. In other words , the pressure medium volume flow Q VW delivered by the pump 6 is branched into partial pressure medium volume flows Q VW1 and Q VW2 . The supply lines 12, 14 are each connected to an input port P of a continuously variable directional control valve 16 or 18, through which the pressure medium flow direction to or from the consumer and the pressure medium volume flow can be adjusted. To working ports A, B of the directional control valves 16, 18 supply lines 20 and 22 and return lines 24 and 26 are connected, wherein the flow lines 20, 22 with a bottom-side cylinder chamber 28 and 30 and the return lines 24, 26 with a piston rod side annular space 32 and 34 of the cylinders 2, 4 are connected. With appropriate operation of the directional control valve 16, 18 can of course be referred to as a forward or return line line also act as a return or flow line.

Die Betätigung der beiden Wegeventile 16, 18 erfolgt über ein oder mehrere Vorsteuergeräte 36, über die Steuerräume der Wegeventile 16, 18 mit einem Steuerdruck beaufschlagbar sind, um den Ventilschieber aus seiner dargestellten Sperrposition (Closed Center) in die angedeuteten Positionen (a) oder (b) zu verstellen, in denen entweder der Zylinderraum 28, 30 oder der Ringraum 32, 34 mit Druckmittel versorgt wird, während das Druckmittel dann aus dem jeweils anderen Druckraum verdrängt wird. Dabei wird über eine Zulaufsteuerkante eine Zulaufmeßblende aufgesteuert, deren Öffnungsquerschnitt den Druckmittelvolumenstrom zum Zylinder 2, 4 bestimmt. Das vom Zylinder 2, 4 zurückströmende Druckmittel wird über einen Tankanschluss T und eine daran angeschlossene Tankleitung 38 zum Tank T zurückgeführt.The actuation of the two-way valves 16, 18 via one or more pilot control devices 36, via the control spaces of the directional control valves 16, 18 are acted upon with a control pressure to the valve spool from its illustrated locking position (closed center) in the indicated positions (a) or ( b) to adjust, in which either the cylinder chamber 28, 30 or the annulus 32, 34 is supplied with pressure medium, while the pressure medium is then displaced from the respective other pressure chamber. In this case, a Zulaufmeßblende is controlled via an inlet control edge, whose opening cross-section determines the pressure medium volume flow to the cylinder 2, 4. The pressure medium flowing back from the cylinder 2, 4 is returned to the tank T via a tank connection T and a tank line 38 connected thereto.

Über die beiden Zylinder 2, 4 wird beim dargestellten Ausführungsbeispiel jeweils eine Last m1 bzw. m2 bewegt. In Figur 1 ist der über die Vorlaufleitungen 20, 22 zuströmende Druckmittelvolumenstrom mit QA1, QA2 und der abströmende Druckmittelvolumenstrom mit QB1 bzw. QB2 gekennzeichnet. In den Leitungen liegen dann jeweils die eingezeichneten Drücke pA1, pB1, pA2 und pB2 an.In the illustrated embodiment, in each case one load m1 or m2 is moved over the two cylinders 2, 4. In FIG. 1 is characterized by the flow lines 20, 22 inflowing pressure medium flow with Q A1 , Q A2 and the outflowing pressure medium flow with Q B1 and Q B2 . The indicated pressures p A1 , p B1 , p A2 and p B2 are then in each case in the lines.

Stromaufwärts jedes Wegeventils 16, 18 ist in der entsprechenden Vorlaufleitung 12 bzw. 14 eine LS- oder Individualdruckwaage 40, 42 vorgesehen, die in Öffnungsrichtung jeweils von der Kraft einer Druckwaagenfeder 44 bzw. 46 sowie dem am jeweiligen Verbraucher 2, 4 anliegenden Lastdruck beaufschlagt ist. In Schließrichtung wirkt auf die Druckwaagenschieber der Individualdruckwaagen 40, 42 jeweils der Druck im Druckmittelströmungspfad zwischen dem Ausgang der jeweiligen Individualdruckwaage 40, 42 und dem Eingang des nachgeschalteten Wegeventils 16, 18. Durch die jeweilige Individualdruckwaage 40, 42 und die zugeordnete, durch das Wegeventil 16, 18 ausgebildete Zumessblende wird ein Stromregler gebildet, über den der Druckabfall über der Messblende lastunabhängig konstant gehalten werden kann.Upstream of each directional control valve 16, 18 is in the corresponding flow line 12 and 14, a LS or individual pressure compensator 40, 42 is provided, which is acted upon in the opening direction respectively by the force of a pressure compensator spring 44 and 46 and the load applied to the respective load 2, 4 , In the closing direction acts on the pressure compensator slide of the individual pressure compensators 40, 42 respectively, the pressure in the pressure medium flow path between the output of the respective individual pressure compensator 40, 42 and the input of the downstream directional control valve 16, 18. By the respective individual pressure compensator 40, 42 and the associated, through the directional control valve 16 , 18 formed metering orifice, a flow regulator is formed over which the pressure drop across the orifice can be kept constant independent of the load.

Die Steueranordnung hat des Weiteren noch eine Eingangsdruckwaage 52, die in einer von der Pumpenleitung 10 abzweigenden Zweigleitung 54 angeordnet ist. Über die Eingangsdruckwaage 52 kann eine Verbindung zum Tank T aufgesteuert werden.The control arrangement further has an inlet pressure compensator 52, which is arranged in a branch line 54 branching off from the pump line 10. Via the inlet pressure compensator 52, a connection to the tank T can be opened.

Bis hier entspricht die erfindungsgemäße Steueranordnung 1 im Wesentlichen dem Aufbau, wie er im eingangs genannten Stand der Technik beschrieben wurde.Up to here, the control arrangement 1 according to the invention substantially corresponds to the structure as described in the aforementioned prior art.

Zum Anschluss eines Geräts mit einem zusätzlichen hydraulischen Verbrauchers an das mobile Arbeitsgerät, beispielsweise eines Ladewagens oder eines Kartoffel-Vollernters, ist das System mit einem Power-Beyond-Anschluss versehen, an den dieser Zusatzverbraucher, im folgenden Power-Beyond-Verbraucher 50 genannt, angeschlossen werden kann.To connect a device with an additional hydraulic consumer to the mobile implement, such as a loading wagon or a potato harvester, the system is provided with a power beyond port to which this additional consumer, hereinafter referred to as power beyond consumer 50, can be connected.

Beim dargestellten Ausführungsbeispiel ist die Eingangsdruckwaage 52 als 3/3-Wegedruckwaage ausgeführt, deren Schieber in Schließrichtung von der Kraft einer Feder 56 sowie dem am Ausgang eines Druckwaagenwechselventils 58 anliegenden Druck und in Schließrichtung vom Druck in der Zweigleitung 54 und somit dem Druck in der Pumpenleitung 10 beaufschlagt ist. An den Eingängen des Druckwaagenwechselventils 58 liegt einerseits der höchste Lastdruck der beiden Verbraucher 2, 4 an, der über ein Wechselventil 48 und entsprechende Lastmeldeleitungen von den Wegeventilen 16, 18 abgegriffen wird. Am anderen Eingang des Druckwaagenwechselventils 58 liegt der Lastdruck des Power-Beyond-Verbrauchers 50 an, der über eine Power-Beyond-Lastmeldeleitung 68 abgegriffen wird. Der Druckwagenschieber der Eingangsdruckwaage 52 wird in Schließrichtung vom höchsten der Lastdrücke beaufschlagt, die an den Verbrauchern 2, 4 und am Power-Beyond-Verbraucher 50 anliegen. Der Power-Beyond-Verbraucher 50 ist über einen Zulaufkanal 60 an einen Arbeitsanschluss A der 3/3-Wege-Druckwaage angeschlossen. Das vom Power-Beyond-Verbraucher 50 abströmende Druckmittel wird über einen Ablaufkanal 64 in die Tankleitung 38 geleitet. Am Tankanschluss T der Eingangsdruckwaage 52 wird ein zum Tank T führender Tankkanal 62 angeschlossen.In the illustrated embodiment, the inlet pressure compensator 52 is designed as a 3/3-way pressure balance, the slide in the closing direction of the force of a spring 56 and the pressure applied to the output of a pressure compensating valve 58 pressure and in the closing direction of the pressure in the branch line 54 and thus the pressure in the pump line 10 is applied. At the inputs of the pressure compensator exchange valve 58, on the one hand, the highest load pressure of the two consumers 2, 4, which is tapped via a shuttle valve 48 and corresponding load reporting lines from the directional control valves 16, 18. At the other input of the pressure compensator exchange valve 58, the load pressure of the power beyond consumer 50 is applied, which is tapped via a power-beyond-Lastmeldeleitung 68. The pressure slide of the inlet pressure compensator 52 is acted upon in the closing direction of the highest of the load pressures at the consumers 2, 4 and the power beyond consumer 50 abut. The power beyond consumer 50 is connected via an inlet channel 60 to a working port A of the 3/3-way pressure compensator. The flowing away from the power beyond consumer 50 pressure medium is passed through a drain passage 64 in the tank line 38. At the tank connection T of the inlet pressure compensator 52, a tank channel 62 leading to the tank T is connected.

Die Öffnungsdruckdifferenz ΔPEDW, die zum vollständigen Aufsteuern der Eingangsdruckwaage 52 aufgebracht werden muss, ist durch die Kraft der Feder 56 bestimmt. Bei dem dargestellten Ausführungsbeispiel wird der Weg des Ventilschiebers der Eingangsdruckwaage 52 über einen Wegaufnehmer 66 erfasst und in ein Signal umgewandelt, das an einem Signaleingang des Pumpenreglers 8 anliegt, so dass die Einstellung der Pumpe in Abhängigkeit von dem Weg des Druckwaagenschiebers der Eingangsdruckwaage 52 erfolgt.The opening pressure difference Δ PEDW , which must be applied to fully open the inlet pressure compensator 52, is determined by the force of the spring 56. In the illustrated embodiment, the path of the valve spool of the input pressure compensator 52 is detected via a displacement sensor 66 and converted into a signal which is applied to a signal input of the pump controller 8, so that the adjustment of the pump in response to the path of the pressure compensator slide of the inlet pressure compensator 52 takes place.

Bei nicht betätigtem oder nicht angeschlossenem Power-Beyond-Verbraucher 50 ist die Eingangsdruckwaage 52 geschlossen und die Arbeitshydraulik des Schleppers (Zylinder 2, 4) wird mit Druckmittel versorgt. Bei Betätigung des Power-Beyond-Verbrauchers 3 wird die Eingangsdruckwaage 52 in Öffnungsrichtung verstellt, so dass dieser mit Druckmittel versorgt werden kann. Die Pumpe 6 wird in Abhängigkeit vom Weg des Druckwaagenschiebers der Eingangsdruckwaage 52 so eingestellt, dass ein geringer Restvolumenstrom über den Tankanschluss T abströmt - (die Eingangsdruckwaage 52 ist dann zum Power-Beyond-Verbraucher 50 und zum Tank T hin geöffnet). Dadurch ist gewährleistet, dass sämtliche Verbraucher 2, 4 und der Power-Beyond-Verbraucher 50 hinreichend mit Druckmittel versorgt werden. Bei dem dargestellten Ausführungsbeispiel erfolgt die Ansteuerung der Pumpe 6 in Abhängigkeit vom Weg des Druckwaagenschiebers der Eingangsdruckwaage 52, alternativ könnte auch der zum Tank T hin abströmende Restvolumenstrom erfasst und zur Einstellung der Pumpe 6 verwendet werden. Im Pumpenregler 8 wird das dem Istweg des Druckwaagenschiebers entsprechende Signal YEDWist mit einem in einem Datenspeicher abgelegtem Sollwert verglichen - die Einstellung der Pumpe 6 erfolgt dann in Abhängigkeit von dieser Regeldifferenz über einen Regelalgorithmus 9..When the power beyond consumer 50 is not actuated or not connected, the inlet pressure compensator 52 is closed and the working hydraulics of the tractor (cylinders 2, 4) are supplied with pressure medium. Upon actuation of the power beyond consumer 3, the inlet pressure compensator 52 is adjusted in the opening direction, so that it can be supplied with pressure medium. The pump 6 is adjusted in response to the path of the pressure compensator slide of the inlet pressure compensator 52 so that a small residual volume flow flows through the tank port T - (the inlet pressure compensator 52 is then open to the power beyond consumer 50 and the tank T out). This ensures that all consumers 2, 4 and the power beyond consumer 50 are adequately supplied with pressure medium. In the illustrated embodiment, the control of the pump 6 takes place in dependence on the path of the Pressure compensator valve of the inlet pressure compensator 52, alternatively, the residual volume flow flowing out to the tank T could also be detected and used to set the pump 6. In the pump controller 8, the actual path of the pressure compensator valve corresponding signal Y EDWist is compared with a stored in a data storage setpoint - the adjustment of the pump 6 then takes place in response to this control difference via a control algorithm. 9

Bei diesem Ausführungsbeispiel wird in der Regel die Öffnungsdruckdifferenz der Eingangsdruckwaage 52 größer als die Öffnungsdruckdifferenz der Individualdruckwaagen 40, 42 sein, d. h., die Feder 56 ist stärker als die Druckwaagenfedern 44, 46.In this embodiment, the opening pressure difference of the input pressure compensator 52 will generally be greater than the opening pressure difference of the individual pressure compensators 40, 42, d. h., The spring 56 is stronger than the pressure compensator springs 44, 46th

Die folgenden beschriebenen Ausführungsbeispiele unterscheiden sich vom vorbeschriebenen Ausführungsbeispiel lediglich in der Art und Weise, wie die Eingangsdruckwaage 52 ausgeführt ist und wie der oder die Power-Beyond-Verbraucher angesteuert werden. Es kann daher auf die Darstellung der Verbraucher 2, 4, der zugeordneten Wegeventile 16, 18 und der Individualdruckwaagen 40, 42 verzichtet werden, diese sind bei den folgenden Ausführungsbeispielen genauso wie beim vorbeschriebenen Ausführungsbeispiel ausgeführt.The following described embodiments differ from the above-described embodiment only in the manner in which the inlet pressure compensator 52 is designed and how the power beyond consumer (s) are driven. It can therefore be dispensed with the representation of the consumer 2, 4, the associated directional control valves 16, 18 and the individual pressure compensators 40, 42, these are the same in the following embodiments as in the embodiment described above.

Das in Fig. 2 dargestellte Ausführungsbeispiel entspricht im Prinzip der in Fig. 1 dargestellten Lösung, wobei jedoch anstelle eines einzigen Verbrauchers zwei Power-Beyond-Verbraucher 50, 70 angesteuert werden. Die Eingangsdruckwaage 52 ist als 4/4-Wege-Druckwaage ausgeführt, wobei der Eingangsanschluss P der Eingangsdruckwaage 52 an die Zweigleitung 54 angeschlossen ist, während die Druckmittelversorgung der beiden Power-Beyond-Verbraucher 50, 70 über den Zulaufkanal 60 bzw. einen weiteren Zulaufkanal 72 erfolgt, die an zwei Ausgangsanschlüsse A, B der Druckwaage 52 angeschlossen sind. Die Eingangsdruckwaage 52 ist wiederum in Schließrichtung von der Kraft der Feder 56 und dem höchsten Lastdruck der Verbraucher 2, 4 und der beiden Power-Beyond-Verbraucher 50, 70 beaufschlagt, wobei der größere der Lastdrücke der beiden Power-Beyond-Verbraucher 50, 70 über ein Power-Beyond-Wechselventil 73 abgegriffen wird. In Öffnungsrichtung ist die Eingangsdruckwaage 52 wiederum von dem Druck am Eingangsanschluss P beaufschlagt. Die Eingangsdruckwaage 52 ist so ausgelegt, dass bei Nichtbetätigung oder nicht angeschlossenen Power-Beyond-Verbrauchern 50, 70 die Eingangsdruckwaage 52 abgesperrt ist. Bei Betätigung beider Power-Beyond-Verbraucher 50, 70 wird zunächst der Power-Beyond-Verbraucher 50 mit Druckmittel versorgt und bei einer weiteren Verschiebung des Druckwaagenschiebers die Verbindung zum weiteren Power-Beyond-Verbraucher 70 aufgesteuert. Das heißt, bei dieser in Fig. 2 dargestellten Lösung ist der Power-Beyond-Verbraucher 50 gegenüber dem Power-Beyond-Verbraucher 70 priorisiert. Bei vollständig geöffneter Eingangsdruckwaage 52 strömt ein Restvolumenstrom über den Tankkanal 62 zum Tank T ab. Der Weg des Druckwaagenschiebers wird wie beim vorbeschriebenen Ausführungsbeispiel über den Wegaufnehmer 66 erfasst und über eine Signalleitung 74 an einen Signalanschluss des Pumpenreglers 8 geführt und in der eingangs beschriebenen Weise verarbeitet - die Einstellung der Pumpe 6 erfolgt wiederum so, dass ein vorbestimmter Restvolumenstrom zum Tank T hin abströmt, so dass eine hinreichende Versorgung sämtlicher Verbraucher und der Power-Beyond-Verbraucher 50, 70 gewährleistet ist.This in Fig. 2 illustrated embodiment corresponds in principle to in Fig. 1 illustrated solution, but instead of a single consumer two power beyond consumers 50, 70 are driven. The inlet pressure compensator 52 is designed as a 4/4-way pressure compensator, wherein the input terminal P of the inlet pressure compensator 52 is connected to the branch line 54, while the pressure medium supply of the two power beyond consumers 50, 70 via the Inlet passage 60 and a further inlet channel 72 takes place, which are connected to two output terminals A, B of the pressure compensator 52. The inlet pressure compensator 52 is again acted upon in the closing direction by the force of the spring 56 and the highest load pressure of the consumers 2, 4 and the two power beyond consumers 50, 70, wherein the greater of the load pressures of the two power beyond consumers 50, 70 is tapped via a power beyond shuttle valve 73. In the opening direction, the inlet pressure compensator 52 in turn is acted upon by the pressure at the inlet port P. The inlet pressure compensator 52 is designed so that when inoperative or disconnected power beyond consumers 50, 70, the inlet pressure compensator 52 is shut off. Upon actuation of both power beyond consumers 50, 70, the power beyond consumer 50 is first supplied with pressure medium and on a further displacement of the pressure compensator slide the connection to the other power beyond consumer 70 aufgesteuert. That is, at this in Fig. 2 As illustrated, the power beyond consumer 50 is prioritized over the power beyond consumer 70. When the inlet pressure compensator 52 is completely open, a residual volume flow flows via the tank channel 62 to the tank T. The path of the pressure compensator slide is detected as in the above embodiment via the transducer 66 and guided via a signal line 74 to a signal port of the pump controller 8 and processed in the manner described above - the adjustment of the pump 6 is again such that a predetermined residual flow to the tank T. flows out, so that a sufficient supply of all consumers and the power beyond consumers 50, 70 is ensured.

Bei dem in Fig. 3 dargestellen Ausführungsbeispiel ist die gleiche Eingangsdruckwaage 52 wie beim Ausführungsbeispiel gemäß Fig. 1 verwendet, über die aber zwei Power-Beyond-Verbraucher 50, 70 mit Druckmittel versorgt werden können. Dazu verzweigt sich der an den Ausgangsanschluss A angeschlossene Zulaufkanal 60 in zwei Zulaufzweigkanäle 76, 78, über die das Druckmittel zum Power-Beyond-Verbraucher 50 bzw. 70 geführt wird. In dem Zulaufzweigkanal 78 ist eine Power-Beyond-Druckwaage 80 vorgesehen, die in Schließrichtung von der Kraft einer Druckwaagenfeder 82 und dem höchsten der auftretenden Lastdrücke beaufschlagt ist, der vom Ausgang des Druckwaagenwechselventils 58 abgegriffen wird. In Öffnungsrichtung ist die Power-Beyond-Druckwaage 80 vom Druck an ihrem Eingangsanschluss P beaufschlagt. Der Öffnungsdruck dieser Power-Beyond-Druckwaage 80 ist kleiner als derjenige der Eingangsdruckwaage 52 und der Individualdruckwaagen 40, 42 gewählt. Durch Zusammenwirken der Eingangsdruckwaage 52 und der Power-Beyond-Druckwaage 80 erfolgt bei diesem Ausführungsbeispiel eine Priorisierung des Power-Beyond-Verbrauchers 50 gegenüber dem Power-Beyond-Verbraucher 70.At the in Fig. 3 dargestellen embodiment is the same inlet pressure compensator 52 as in Embodiment according to Fig. 1 used, but over which two power beyond consumers 50, 70 can be supplied with pressure medium. For this purpose, the connected to the output terminal A inlet channel 60 branches into two Zulaufzweigkanäle 76, 78, via which the pressure medium to the power beyond consumer 50 or 70 is performed. In the inlet branch channel 78, a power beyond pressure compensator 80 is provided, which is acted upon in the closing direction by the force of a pressure compensator spring 82 and the highest of the occurring load pressures, which is tapped from the output of the pressure compensator shuttle valve 58. In the opening direction of the power beyond pressure compensator 80 is acted upon by the pressure at its input terminal P. The opening pressure of this power beyond pressure compensator 80 is smaller than that of the inlet pressure compensator 52 and the individual pressure compensators 40, 42 chosen. By interaction of the inlet pressure compensator 52 and the power beyond pressure compensator 80, a prioritization of the power beyond consumer 50 with respect to the power beyond consumer 70 occurs in this exemplary embodiment.

Bei den drei vorbeschriebenen Ausführungsbeispielen erfolgt die Druckmittelversorgung des oder der Power-Beyond-Verbraucher 50, 70 stets über die Eingangsdruckwaage 52, die im Druckmittelströmungspfad zwischen der Pumpenleitung 10 und dem zugeordneten Verbraucher 50, 70 liegt. Bei den im Folgenden beschriebenen Ausführungsbeispielen erfolgt die Druckmittelversorgung der Verbraucher direkt, d. h., bei Umgehung der Eingangsdruckwaage 52 über zugeordnete Power-Beyond-Druckwaagen.In the three embodiments described above, the pressure medium supply of the power beyond consumer 50, 70 always via the inlet pressure compensator 52, which is located in the pressure fluid flow path between the pump line 10 and the associated load 50, 70. In the embodiments described below, the pressure medium supply to the consumer takes place directly, d. h., When bypassing the inlet pressure compensator 52 via associated power beyond pressure compensators.

Fig. 4 zeigt eine Variante der Steueranordnung 1, bei der die Eingangsdruckwaage 52 als 2/2-Wege-Druckwaage ausgeführt ist, wobei der Eingangsanschluss P wie bei den vorbeschriebenen Ausführungsbeispielen an die Zweigleitung 54 angeschlossen ist und der Tankanschluss T über den Tankkanal 62 in den Tank mündet. Die Eingangsdruckwaage 52 ist durch den Druck am Eingangsanschluss P in Öffnungsrichtung und durch die Kraft der Feder 56 sowie den am Ausgang des Druckwaagenwechselventils 58 anliegenden höchsten der Lastdrücke in Schließrichtung beaufschlagt. Der Weg des Druckwaagenventilschiebers wird wiederum über einen Wegaufnehmer 66 erfasst und zur Ansteuerung der Pumpe 6 verwendet. Fig. 4 shows a variant of the control arrangement 1, in which the inlet pressure compensator 52 is designed as a 2/2-way pressure compensator, wherein the input terminal P as in the above-described embodiments is connected to the branch line 54 and the tank port T opens via the tank passage 62 into the tank. The inlet pressure compensator 52 is acted upon by the pressure at the inlet port P in the opening direction and by the force of the spring 56 and the highest applied to the output of the pressure compensating valve 58, the load pressures in the closing direction. The path of the pressure compensator valve spool is in turn detected by a displacement sensor 66 and used to control the pump 6.

Die Druckmittelversorgung des Power-Beyond-Verbrauchers 50 erfolgt gemäß Fig. 4 über die Power-Beyond-Druckwaage 80, die in Öffnungsrichtung von dem Druck in der Pumpenleitung 10 und in Schließrichtung von der Kraft der Druckwaagenfeder 82 sowie dem höchsten der Lastdrücke beaufschlagt ist, der am Ausgang des Druckwaagenwechselventils 58 abgegriffen wird. Die Power-Beyond-Druckwaage 80 ist in einem von der Pumpenleitung 10 abzweigenden Power-Beyond-Zulauf 84 angeordnet.The pressure medium supply of the power beyond consumer 50 takes place according to Fig. 4 via the power beyond pressure compensator 80, which is acted upon in the opening direction by the pressure in the pump line 10 and in the closing direction by the force of the pressure balance spring 82 and the highest of the load pressures tapped at the outlet of the pressure balance changeover valve 58. The power beyond pressure compensator 80 is arranged in a power beyond feed 84 branching off from the pump line 10.

Bei dieser Variante sind die Eingangsdruckwaage 52 und die Power-Beyond-Druckwaage 80 parallel angeordnet und jeweils als 2/2-Wege-Druckwaage ausgeführt. Der Öffnungsdruck ΔpEDW der Eingangsdruckwaage ist größer als derjenige der Power-Beyond-Druckwaage 80 (ΔpIDW3) und der beiden Individualdruckwaagen 40, 42 (ΔpIDW1, 2), wobei entweder der Öffnungsdruck der beiden Individualdruckwaagen 40, 42 oder derjenige der Power-Beyond-Druckwaage 80 größer gewählt werden kann, um eine Priorisierung festzulegen. Das heißt, es kann zuerst der Power-Beyond-Verbraucher 50 oder die Arbeitshydraulik des Schleppers (Zylinder 2, 4) mit Druckmittel versorgt werden. Auch bei diesem Ausführungsbeispiel ist eine Versorgung sämtlicher Verbraucher 2, 4, 50 gewährleistet, wenn die Pumpe 6 so eingestellt ist, dass ein Restvolumenstrom über die Eingangsdruckwaage 52 zum Tank T hin abströmt.In this variant, the inlet pressure compensator 52 and the power beyond pressure compensator 80 are arranged in parallel and each designed as a 2/2-way pressure compensator. The opening pressure Δp EDW of the inlet pressure compensator is greater than that of the power beyond pressure compensator 80 (Δp IDW3 ) and the two individual pressure compensators 40, 42 (Δp IDW1 , 2), whereby either the opening pressure of the two individual pressure compensators 40, 42 or that of the power Beyond-Druckwaage 80 can be selected larger to set a prioritization. That is, it can first the power beyond consumer 50 or the working hydraulics of the tractor (cylinder 2, 4) are supplied with pressure medium. Also in this embodiment, a supply of all consumers 2, 4, 50 is ensured when the pump 6 is set so that a residual volume flow flows through the inlet pressure compensator 52 to the tank T out.

In Fig. 5 ist eine Variante des in Fig. 4 dargestellten Ausführungsbeispiels gezeigt, wobei die Eingangsdruckwaage 52 nicht - wie in Fig. 4 - parallel, sondern in Reihe zur Power-Beyond-Druckwaage 80 geschaltet ist. Das heißt, die zum Eingangsanschluss P der Eingangsdruckwaage 52 führende Zweigleitung 54 zweigt nicht von der Pumpenleitung 10, sondern von dem den Ausgangsanschluss A der Power-Beyond-Druckwaage 80 und den Power-Beyond-Verbraucher 50 verbindenden Zulaufkanal 60 ab. Die Eingangsdruckwaage 52 wird somit erst nach dem Aufsteuern der Power-Beyond-Druckwaage 80 mit Druckmittel versorgt. Beide Druckwaagen 52, 80 sind als 2/2-Wege-Druckwaage ausgeführt und sind über den höchsten der Lastdrücke in Schließstellung und durch den jeweils am Eingang P anliegenden Druck in Öffnungsstellung vorgespannt. Je nach Wahl der Druckwaagenfedern 44, 46, 82 und der Feder 56 der Eingangsdruckwaage kann entweder der Power-Beyond-Verbraucher 50 oder die Verbraucher 2, 4 priorisiert werden. Die Öffnungsdruckdifferenz der Eingangsdruckwaage 52 ist wieder größer als die Öffnungsdruckdifferenz der Individualdruckwaagen 40, 42 und der Power-Beyond-Druckwaage 80 gewählt. Im übrigen entspricht die Funktion derjenigen des Ausführungsbeispiels aus Fig. 4.In Fig. 5 is a variant of in Fig. 4 shown embodiment, wherein the inlet pressure compensator 52 is not - as in Fig. 4 - parallel, but in series with the power beyond pressure scale 80 is connected. That is, the branch line 54 leading to the input port P of the input pressure compensator 52 does not branch from the pump line 10 but from the inlet port 60 connecting the output port A of the power beyond pressure compensator 80 and the power beyond consumer 50. The input pressure compensator 52 is thus supplied with pressure medium only after the control of the power beyond pressure compensator 80. Both pressure compensators 52, 80 are designed as a 2/2-way pressure compensator and are biased over the highest of the load pressures in the closed position and by the pressure applied in each case at the input P in the open position. Depending on the choice of pressure compensator springs 44, 46, 82 and the spring 56 of the input pressure compensator, either the power beyond consumer 50 or the consumers 2, 4 can be prioritized. The opening pressure difference of the inlet pressure compensator 52 is again greater than the opening pressure difference of the individual pressure compensators 40, 42 and the power beyond pressure compensator 80 selected. Otherwise, the function corresponds to that of the embodiment Fig. 4 ,

In Fig. 6 ist ein Ausführungsbeispiel dargestellt, bei dem zwei Power-Beyond-Verbraucher 50, 70 mit Druckmittel versorgt werden sollen. Diesen ist jeweils eine Power-Beyond-Druckwaage 80 bzw. 86 zugeordnet, die jeweils über von der Pumpenleitung 10 abzweigende Power-Beyond-Zulaufleitungen 84, 88 mit den zugeordneten Power-Beyond-Verbrauchern 50, 70 verbunden sind.In Fig. 6 an embodiment is shown in which two power beyond consumers 50, 70 to be supplied with pressure medium. These are each associated with a power beyond pressure compensator 80 or 86, which are each connected via branching off from the pump line 10 power beyond supply lines 84, 88 with the associated power beyond consumers 50, 70.

Die beiden Power-Beyond-Druckwaagen 80, 86 und die Eingangsdruckwaage 52 sind jeweils als 2/2-Wege-Druckwaagen ausgeführt. Die Eingangsdruckwaage 52 ist bei diesem Ausführungsbeispiel durch den über das Druckwaagenwechselventil 58 abgegriffenen höchsten der Lastdrücke in Öffnungsrichtung vorgespannt, während in Schließrichtung lediglich die Feder 56 wirkt. Der Ausgangsanschluss der Eingangsdruckwaage 52 ist über den Tankkanal 62 mit dem Tank T verbunden. Auch die beiden Power-Beyond-Druckwaagen 80, 86 werden lediglich von der Kraft einer Druckwaagenfeder 82 bzw. 90 in Schließrichtung vorgespannt, während in Öffnungsrichtung bei diesem Ausführungsbeispiel der höchste der Lastdrücke wirkt, der am Ausgang des Druckwaagenwechselventils 58 abgegriffen wird.The two Power Beyond pressure compensators 80, 86 and the inlet pressure compensator 52 are each designed as 2/2-way pressure compensators. The input pressure compensator 52 is biased in this embodiment by the tapped via the pressure compensating valve 58 highest of the load pressures in the opening direction, while in the closing direction, only the spring 56 acts. The output port of the inlet pressure compensator 52 is connected via the tank channel 62 to the tank T. The two power beyond pressure scales 80, 86 are biased only by the force of a pressure compensator spring 82 and 90 in the closing direction, while in the opening direction in this embodiment, the highest of the load pressures acts, which is tapped at the output of the pressure compensator shuttle valve 58.

Dieses Ausführungsbeispiel ermöglicht eine Vielzahl von Funktionsabläufen, da je nach Federauswahl der Individualdruckwaagen 40, 42 und der Power-Beyond-Druckwaagen 80, 86 entweder die Arbeitshydraulik des Schleppers (Verbraucher 2, 4) und dann die Power-Beyond-Verbraucher 50, 70 oder umgekehrt oder auch zunächst nur einer der Power-Beyond-Verbraucher, dann die Arbeitshydraulik und dann der andere Power-Beyond-Verbraucher 70, 50 mit Druckmittel versorgbar ist.This embodiment allows a variety of functional processes, since depending on the spring selection of the individual pressure compensators 40, 42 and the power beyond pressure scales 80, 86 either the working hydraulics of the tractor (consumers 2, 4) and then the power beyond consumers 50, 70 or vice versa or initially only one of the power beyond consumers, then the working hydraulics and then the other power beyond consumers 70, 50 can be supplied with pressure medium.

Entsprechend der Pumpenansteuerung und des Druckmittelbedarfs wird bei geöffneter Eingangsdruckwaage 52 ein Restvolumenstrom auftreten und in Abhängigkeit von diesem Restvolumenstrom oder von der Stellung des Druckwaagenkolbens der Eingangsdruckwaage 52 die Pumpe 6 angesteuert, um eine Unterversorgung zu vermeiden.Corresponding to the pump control and the pressure medium requirement, a residual volume flow will occur when the inlet pressure compensator 52 is open and the pump 6 is actuated in dependence on this residual volume flow or on the position of the pressure compensator piston of the inlet pressure compensator 52 in order to avoid undersupply.

In Fig. 7 ist ein Ausführungsbeispiel mit dem Anschluss eines Power-Beyond-Verbrauchers 50 dargestellt, das im Grundaufbau demjenigen aus Fig. 4 entspricht. Auch bei dieser Lösung wird der Power-Beyond-Verbraucher 50 über eine in der Power-Beyond-Zulaufleitung 84 angeordnete Power-Beyond-Druckwaage 80 mit Druckmittel versorgt. Die Eingangsdruckwaage 52 ist in der Zweigleitung 54 angeordnet und in Öffnungsrichtung vom Druck in dieser Zweigleitung 54 beaufschlagt, während in Schließrichtung die Kraft der Feder 56 und der am Druckwaagenwechselventil 58 abgegriffene höchste Lastdruck wirken. Im Unterschied zum Ausführungsbeispiel gemäß Fig. 4 ist in dem an den Ausgangsanschluss T der der Eingangsdruckwaage 52 angeschlossenen Tankkanal 62 eine Blende 92 vorgesehen, über die bei zum Tank T abströmendem Restvolumenstrom ein Steuerdruck erzeugt wird, der über eine Steuerleitung 94 abgegriffen und zu der in Öffnungsrichtung wirksamen Steuerfläche der Power-Beyond-Druckwaage 80 geführt ist. Diese ist in Schließrichtung von der Kraft der Feder 82 beaufschlagt. Bei dieser Variante werden zunächst die Verbraucher 2, 4 der Arbeitshydraulik mit Druckmittel versorgt und erst nach Ansteigen des Restvolumenstroms und entsprechendem Druckabfall im Tankkanal 62 die Power-Beyond-Druckwaage 80 aufgesteuert, so dass dann der Power-Beyond-Verbraucher 50 mit Druckmittel versorgt wird. Wie bei allen vorbeschriebenen Ausführungsbeispielen wird dann, wenn der Restvolumenstrom zum Tank T hin eine bestimmte Grösse überschreitet, dieser zur Pumpensteuerung benützt.In Fig. 7 an embodiment is shown with the connection of a power beyond consumer 50, that in the basic structure of that Fig. 4 equivalent. In this solution too, the power beyond consumer 50 is supplied with pressure medium via a power beyond pressure compensator 80 arranged in the power beyond supply line 84. The inlet pressure compensator 52 is arranged in the branch line 54 and acted upon in the opening direction by the pressure in this branch line 54, while in the closing direction, the force of the spring 56 and the tapped on the pressure compensating valve 58 highest load pressure act. In contrast to the embodiment according to Fig. 4 in the tank port 62 connected to the outlet port T of the inlet pressure compensator 52, an orifice 92 is provided, via which a control pressure is produced at the residual volume flow flowing to the tank T, which is picked off via a control line 94 and fed to the control surface of the power beyond. Pressure compensator 80 is guided. This is acted upon in the closing direction by the force of the spring 82. In this variant, first the consumers 2, 4 of the working hydraulics are supplied with pressure medium and only after increasing the residual volume flow and corresponding pressure drop in the tank channel 62, the power beyond pressure compensator 80 opened, so that then the power beyond consumer 50 is supplied with pressure medium , As with all embodiments described above, when the residual volume flow to the tank T exceeds a certain size, it is used for pump control.

Im Fail-Safe-Fall wird der Restvolumenstrom über die Eingangsdruckwaage 52 zur Vermeidung unerwünschter hoher Druckabfälle an der Blende 92 über ein parallel zur Blende 92 geschaltetes Vorspannventil zum Tank abgeleitet.In the fail-safe case, the residual volume flow through the inlet pressure compensator 52 to avoid undesirable high pressure drops at the aperture 92 via a parallel to the aperture 92 switched bias valve to the tank.

Auch bei diesem Ausführungsbeispiel wird der Öffnungsdruck der Individualdruckwaagen 40, 42 der Arbeitshydraulik größer als der Öffnungsdruck der Power-Beyond-Druckwaage 80 eingestellt und der Öffnungsdruck der Eingangsdruckwaage 52 ist - wie bei allen Ausführungsbeispielen - vorzugsweise größer als derjenige der Individual- oder Power-Beyond-Druckwaagen gewählt.Also in this embodiment, the opening pressure of the individual pressure compensators 40, 42 of Working hydraulics set greater than the opening pressure of the power beyond pressure compensator 80 and the opening pressure of the inlet pressure compensator 52 is - as in all embodiments - preferably greater than that of the individual or power beyond pressure scales selected.

Fig. 8 zeigt schließlich ein Ausführungsbeispiel, bei dem das anhand Fig. 7 erläuterte Prinzip zur Ansteuerung mehrerer Power-Beyond-Verbraucher 50, 70 verwendet wird. Jedem der beiden Power-Beyond-Verbraucher 50, 70 ist jeweils eine Power-Beyond-Druckwaage 80, 86 zugeordnet, die in von der Pumpenleitung 10 abzweigenden Power-Beyond-Zulaufleitungen 84 bzw. 88 angeordnet sind und über die die beiden Power-Beyond-Verbraucher 50, 70 mit Druckmittel versorgt werden. Die Eingangsdruckwaage 52 ist wie beim vorbeschriebenen Ausführungsbeispiel ausgebildet und verschaltet, wobei wiederum im Tankkanal 62 die Blende 92 vorgesehen ist, die einen Steuerdruck zur Ansteuerung der beiden Power-Beyond-Druckwaagen 80, 86 erzeugt. Auch bei diesem Ausführungsbeispiel werden zunächst die Verbraucher 2, 4 der Arbeitshydraulik des Schleppers mit Druckmittel versorgt, eine Druckmittelversorgung der beiden Power-Beyond-Verbraucher 50, 70 erfolgt erst dann, wenn vor der Blende 92 ein hinreichender Steuerdruck aufgebaut ist. Die beiden Power-Beyond-Verbraucher 50, 70 können jedoch durch geeignete Wahl der Druckwaagenfedern 82, 90 untereinander priorisiert werden. Fig. 8 Finally, shows an embodiment in which the basis Fig. 7 explained principle for controlling a plurality of power beyond consumers 50, 70 is used. Each of the two power beyond consumers 50, 70 is in each case assigned a power beyond pressure compensator 80, 86, which are arranged in branching off from the pump line 10 power beyond supply lines 84 and 88 and over which the two power Beyond Consumers 50, 70 are supplied with pressure medium. The inlet pressure compensator 52 is formed and interconnected as in the above-described embodiment, wherein the aperture 92 is again provided in the tank channel 62, which generates a control pressure for controlling the two power beyond pressure compensators 80, 86. Also in this embodiment, first the consumers 2, 4 of the working hydraulics of the tractor are supplied with pressure medium, a pressure medium supply of the two power beyond consumers 50, 70 takes place only when a sufficient control pressure is built up before the aperture 92. However, the two power beyond consumers 50, 70 can be prioritized by a suitable choice of the pressure balance springs 82, 90 with each other.

Das erfindungsgemäße Konzept ermöglicht es, auf einfache Weise Power-Beyond-Verbraucher anzuschließen und auch bei ungünstigen Betriebsbedingungen (beispielsweise geringer Lastdruck, hoher Druckmittelvolumenstrom) eine gewünschte Druckmittelversorgung sämtlicher Verbraucher zu gewährleisten.The concept according to the invention makes it possible to easily connect power beyond consumers and to ensure a desired pressure medium supply of all consumers even under unfavorable operating conditions (for example low load pressure, high pressure medium volume flow).

Der Power-Beyond-Anschluss lässt sich mit vergleichweise wenigen Bauelementen realisieren, wobei bei den Ausführungsbeispielen gemäß den Fig. 1 - 8, die in der folgenden Tabelle aufgelisteten Druckwaagenbauarten (DW) verwendet werden. In dieser Tabelle bedeutet DW: Druckwaage, PB: Power-Beyond-Verbraucher sowie Δp: der jeweilige Öffnungsdruck der Druckwaagen, wobei die Indizes EDW die Eingangsdruckwaage, IDW 1, 2 die Individualdruckwaagen der Arbeitshydraulik und IDW 3, 4 die Power-Beyond-Druckwaagen kennzeichnen.The power beyond connection can be realized with comparatively few components, wherein in the embodiments according to the Fig. 1 - 8 , the pressure compensator types (DW) listed in the following table are used. In this table, DW means: pressure compensator, PB: power beyond consumer and Δp: the respective opening pressure of the pressure compensators, whereby the indices EDW the input pressure balance, IDW 1, 2 the individual pressure compensators of the working hydraulics and IDW 3, 4 the Power Beyond pressure compensators mark.

Bei der Auslegung der Bauelemente gemäß der Tabelle ist die Wahl der Federkräfte bzw. der Öffnungsdruckdifferenzen der einzelnen Druckwaagen mit den Indizes 1 und 2 und ggf. 3 und 4 untereinander austauschbar, was im Einzelfall zu unterschiedlichen Priorisierungen der Verbraucher 2, 4 und der Power-Beyond-Verbraucher 50, 70 führen kann.In the design of the components according to the table, the choice of spring forces or the opening pressure differences of the individual pressure compensators with the indices 1 and 2 and possibly 3 and 4 interchangeable, which in individual cases to different prioritizations of consumers 2, 4 and the power Beyond consumers 50, 70 can lead.

Prinzipiell ist in Verbindung mit elektrischen Wegeventilen 16, 18 auch eine direkte Steuerung eines Power-Beyond-Verbrauchers 50, 70 ohne eigenes Ventil möglich. Dabei ergibt sich der Druckmittelvolumenstrom zum Power-Beyond-Verbraucher 50, 70 aus der Differenz des eingestellten Pumpenvolumenstroms und der an den Arbeitsanschlüssen der Wegeventile 16, 18 eingestellten Druckmittelvolumenströme im Normalbetrieb, d. h. bei entsprechend der Eingangsdruckwaage 52 richtig eingestellter Pumpe. TABELLE Fi g. Druckwaagen 52, 80, 86 1P B 2PB Öffnungsdruckverhältnisse der EDW (52) und IDWs (40, 42, 80, 86) 1 1x3/3 DW x ΔpEDW>ΔpIDW1,2 2 1x4/4 DW x ΔpEDW>ΔpIDW1,2 3 1x3/3 12/2 DW x ΔpEDW>ΔpIW1,2>ΔpIDW3 4 2x2/2 DW parallel x ΔpEDW>ΔpIDW3>ΔpIDW1,2 ΔpEDW>ΔpIDW1,2>ΔpIDW3 5 2x2/2 DW reihe x ΔpEDW>ΔpIDW3ΔpIDW1,2 ΔpEDW>ΔpIDW1,2>ΔpIDW3 6 3x2/2 DW parallel x ΔpEDW>ΔpIDW3,4>ΔpIDW1,2 ΔpEDW>ΔpIDW1,2>ΔpIDW3,4 ΔpEDW>ΔpIDW3>ΔpIDW1,2>ΔpIDW4 ΔpEDW>ΔpIDW1>ΔpIDW3,4>ΔpIDW2 ΔpPEDW>ΔpIDW1>ΔpIDW3>ΔpIDW2>ΔpIDW4 ΔpEDW>ΔpIDW3>ΔpIDW1>ΔpIDW4>ΔpIDW2 7 Blende und 1x2/2 DW x ΔpEDW>ΔpIDW1,2>ΔpIDW3 8 Blende und 1x2/2 DW x ΔpEDW>ΔpIDW1,2;ΔpIDW3/4 unabhängig von ΔpIDW1,2 In principle, a direct control of a power beyond consumer 50, 70 without its own valve is possible in conjunction with electrical directional control valves 16, 18. In this case, the pressure medium volume flow to the power beyond consumer 50, 70 results from the difference of the set pump volume flow and set at the working ports of the directional control valves 16, 18 pressure medium flow rates in normal operation, ie in accordance with the input pressure compensator 52 correctly adjusted pump. TABLE Fi g. Pressure compensators 52, 80, 86 1P B 2PB Opening pressure ratios of the EDW (52) and IDWs (40, 42, 80, 86) 1 1x3 / 3 DW x Δp EDW > Δp IDW1,2 2 1x4 / 4 DW x Δp EDW > Δp IDW1,2 3 1x3 / 3 12/2 DW x Δp EDW > Δp IW1,2 > Δp IDW3 4 2x2 / 2 DW parallel x Δp EDW > Δp IDW3 > Δp IDW1,2 Δp EDW> Δp IDW1,2 > Δp IDW3 5 2x2 / 2 DW row x Δp EDW> Δp IDW3 Δp IDW1,2 Δp EDW > Δp IDW1,2 > Δp IDW3 6 3x2 / 2 DW parallel x Δp EDW > Δp IDW3,4 > Δp IDW1,2 Δp EDW > Δp IDW1,2 > Δp IDW3,4 Δp EDW > Δp IDW3 > Δp IDW1,2 > Δp IDW4 Δp EDW > Δp IDW1 > Δp IDW3,4 > Δp IDW2 Δp PEDW > Δp IDW1 > Δp IDW3 > Δp IDW2 > Δp IDW4 Δp EDW > Δp IDW3 > Δp IDW1 > Δp IDW4 > Δp IDW2 7 Aperture and 1x2 / 2 DW x Δp EDW > Δp IDW1,2 > Δp IDW3 8th Aperture and 1x2 / 2 DW x Δp EDW > Δp IDW1,2 ; Δp IDW3 / 4 independent of Δp IDW1,2

Des Weiteren ist insbesondere bei einer Unterversorgung mit elektrisch gesteuerten Ventilen ein Flow-Management möglich. So können z. B. bei Priorisierung der Power-Beyond-Verbraucher die anderen Verbraucher ggf. soweit zurückgenommen werden, dass der Power-Beyond-Verbraucher stets optimal versorgt wird. Dies ist an dem Lagesignal bzw. dem Restvolumenstrom über die Eingangsdruckwaage 52 erkennbar.Furthermore, a flow management is possible in particular in the case of an undersupply with electrically controlled valves. So z. B. prioritization of the power beyond consumers, the other consumers if necessary be taken back so far that the power beyond consumer is always optimally supplied. This can be recognized by the position signal or the residual volume flow via the inlet pressure compensator 52.

Die Verwendung der Erfindung ist möglich bei Einsatz elektrisch verstellbarer Steuerpumpen sowie drehzahlgeregelter Konstantpumpen insbesondere in Verbindung mit Open-Center und LS-Ventilen, die mechanisch, elektrisch oder elektrohydraulisch betätigt werden. Prinzipiell ist die Erfindung für alle Arbeitshydraulikanwendungen der Mobilhydraulik geeignet, deren Verbraucher nicht von vornherein festgeschrieben sind.The use of the invention is possible with the use of electrically adjustable control pumps and variable speed constant displacement pumps, in particular in conjunction with open center and LS valves, which are operated mechanically, electrically or electro-hydraulically. In principle, the invention is suitable for all working hydraulic applications of mobile hydraulics whose consumers are not fixed from the outset.

Offenbart ist eine hydraulische Steueranordnung zur Ansteuerung mehrerer Verbraucher, insbesondere eines mobilen Arbeitsgerätes, wobei zusätzlich zu den Verbrauchern der Steueranordnung ein Power-Beyond-Verbraucher an einen Power-Beyond-Anschluss anschließbar sein soll. Sämtliche Verbraucher und Power-Beyond-Verbraucher werden von einer Pumpe mit Druckmittel versorgt, wobei stromabwärts der Pumpe eine Eingangsdruckwaage vorgesehen ist, an deren Steueranschluss der größere der Lastdrücke der Verbraucher oder des zumindest einen Power-Beyond-Verbrauchers anliegt.Disclosed is a hydraulic control arrangement for controlling a plurality of consumers, in particular a mobile working device, wherein in addition to the consumers of the control arrangement, a power beyond consumer should be connectable to a power beyond port. All consumers and power beyond consumers are supplied by a pump with pressure medium, downstream of the pump, an inlet pressure compensator is provided at the control terminal of the greater of the load pressures of the consumer or the at least one power beyond consumer is present.

Bezugszeichenliste:LIST OF REFERENCE NUMBERS

11
Steueranordnungcontrol arrangement
22
Zylindercylinder
44
Zylindercylinder
66
Pumpepump
88th
Pumpenreglerpump regulator
99
Regelalgorithmuscontrol algorithm
1010
Pumpenleitungpump line
1212
Zulaufleitungsupply line
1414
Zulaufleitungsupply line
1616
Wegeventilway valve
1818
Wegeventilway valve
2020
Vorlaufleitungsupply line
2222
Vorlaufleitungsupply line
2424
RücklaufleitungReturn line
2626
RücklaufleitungReturn line
2828
Zylinderraumcylinder space
3030
Zylinderraumcylinder space
3232
Ringraumannulus
3434
Ringraumannulus
3636
Vorsteuergerätpilot control unit
3838
Tankleitungtank line
4040
IndividualdruckwaageIndividual pressure compensator
4242
IndividualdruckwaageIndividual pressure compensator
4444
DruckwaagenfederCompensator spring
4646
DruckwaagenfederCompensator spring
4848
Wechselventilshuttle valve
5050
Power-Beyond-VerbraucherPower beyond consumer
5252
EingangsdruckwaageInlet pressure
5454
Zweigleitungbranch line
5656
Federfeather
5858
DruckwaagenwechselventilPressure scale shuttle valve
6060
Zulaufkanalinlet channel
6262
Tankkanaltank channel
6464
Ablaufkanaldrain channel
6666
Wegaufnehmertransducer
6868
Power-Beyond-LastmeldeleitungPower beyond load-sensing line
7070
Power-Beyond-VerbraucherPower beyond consumer
7272
Zulaufkanalinlet channel
7373
Power-Beyond-WechselventilPower beyond shuttle valve
7474
Signalleitungsignal line
7676
ZulaufzweigkanalInlet branch channel
7878
ZulaufzweigkanalInlet branch channel
8080
Power-Beyond-DruckwaagePower beyond pressure scale
8282
DruckwaagenfederCompensator spring
8484
Power-Beyond-ZulaufleitungPower beyond supply line
8686
Power-Beyond-DruckwaagePower beyond pressure scale
8888
Power-Beyond-ZulaufleitungPower beyond supply line
9090
DruckwaagenfederCompensator spring
9292
Blendecover
9494
Steuerleitungcontrol line

Claims (20)

  1. A hydraulic control arrangement for controlling a plurality of consumers (2, 4), particularly of a mobile working machine, said hydraulic control arrangement comprising a pump (6) whereby said plurality of consumers (2, 4) may be supplied with pressure medium, wherein an input pressure compensator (52) belonging to the hydraulic control arrangement allowing to open a connection to a tank (T) is arranged downstream of said pump (6), wherein an adjustable metering orifice (16, 18) belonging to the hydraulic control arrangement is allocated to each consumer (2, 4), and wherein said control arrangement includes a power-beyond port (50, 70) to which at least one power-beyond consumer can be connected, with the adjustment of the input pressure compensator (52) being effected as a function of the highest one of the load pressures of the consumers (2, 4) and the at least one power-beyond consumer (50, 70), characterized in that the pump (6) is a variable-adjustment pump which is adapted to be controlled as a function of the setting of the input pressure compensator (52).
  2. The control arrangement according to claim 1, wherein the power-beyond consumer (50, 70) can be supplied with pressure medium via the input pressure compensator (52), and the highest one of the load pressures is applied to the input pressure compensator (52) in the closing direction.
  3. The control arrangement according to claim 2, wherein the input pressure compensator (52) blocks the connection to the power-beyond consumer (50, 70) and to the tank (T) in a spring-biased home position and, when displaced in the opening direction, first opens the connection to the power-beyond consumer (50, 70) and then to the tank (T).
  4. The control arrangement according to claim 3, wherein a second power-beyond consumer (70) may be connected which can be supplied with pressure medium via the input pressure compensator (52) simultaneously with or after the first power-beyond consumer (50).
  5. The hydraulic control arrangement according to claim 4, wherein a power-beyond pressure compensator (80) belonging to the hydraulic control arrangement to which the force of a spring (82) and the same control pressure as to the input pressure compensator (52) are applied in the closing direction and the pressure prevailing at its input port (P) is applied in the opening direction is arranged upstream of the second power-beyond pressure compensator (80).
  6. The hydraulic control arrangement according to claim 1, wherein at least one power-beyond consumer (50, 70) may be supplied with pressure medium via a power-beyond pressure compensator (80, 86) while bypassing the input pressure compensator (52).
  7. The control arrangement according to claim 6, wherein the highest one of the load pressures and the force of a spring (56) are applied to the input pressure compensator (52) in the closing direction and the pressure prevailing at the input (P) thereof is applied to the same in the opening direction.
  8. The control arrangement according to claim 7, wherein the highest one of the load pressures and the force of a spring (82) are applied to the power-beyond pressure compensator in the closing direction.
  9. The control arrangement according to claim 8, wherein the input pressure compensator (52) is connected in series downstream of the power-beyond pressure compensator (80).
  10. The control arrangement according to claim 6, wherein the highest one of the load pressures is applied to the input pressure compensator (52) in the opening direction.
  11. The control arrangement according to claim 10, wherein the highest one of the load pressures is applied in the opening direction and the force of a spring (82, 90) is applied in the closing direction to the at least one power-beyond pressure compensator (80, 86).
  12. The control arrangement according to claim 7 or 10, wherein a diaphragm (92) is disposed downstream of the input pressure compensator (52) in a tank line (62) leading to the tank (T), and the pressure acting in the opening direction upon the at least one power-beyond pressure compensator (80, 86) is tapped between the diaphragm (92) and the input pressure compensator (52), wherein the force of a spring (82, 90) is applied to the power-beyond pressure compensator (80, 86) in the closing direction.
  13. The control arrangement according to any one of the preceding claims, wherein the pump (6) is an electrically controllable variable displacement pump or a speed-controlled constant displacement pump.
  14. The control arrangement according to any one of the preceding claims, wherein an individual pressure compensator (40, 42) to which a pressure compensator spring (44) and the highest load pressure of the consumers (2, 4) are applied in the opening direction and the pressure prevailing at the output of the individual pressure compensator (40, 42) is applied in the closing direction is disposed upstream of each metering orifice (16, 18).
  15. The control arrangement according to claim 14, wherein the pressure compensator springs (44, 46) of the individual pressure compensators (40, 42) and of the power-beyond pressure compensators (80, 86) or of the input pressure compensator (52) are adapted to each other in such a manner that priority is given either to consumers (2, 4) or to power-beyond consumers (50, 70).
  16. The control arrangement according to claim 15, wherein the opening pressure difference of the input pressure compensator (52) is selected to be greater than the opening pressure difference of the individual pressure compensators (40, 42) or power-beyond pressure compensators (80, 86).
  17. The control arrangement according to any one of the preceding claims, wherein the metering orifices are formed by electrically, hydraulically, or mechanically adjustable directional control valves (16, 18).
  18. The control arrangement according to any one of the preceding claims, comprising a pressure compensator shuttle valve (58) to the input of which the highest load pressure of the consumers (2, 4)on the one hand and the highest load pressure of the power-beyond consumer(s) (50) on the other hand is applied, and the output of which is connected to a control chamber of the input pressure compensator (52).
  19. A control method for a hydraulic control arrangement according to claim 1, characterized in that the pump (6) and/or the metering orifices (16, 18) of the consumers (2, 4) are controlled such that a predetermined residual volume flow to the tank (T) results when the at least one power-beyond consumer (50, 70) is supplied with pressure medium via the input pressure compensator (52).
  20. The control method according to claim 19, wherein the pump (6) is adjusted in response to the residual volume flow or the position of a pressure compensator slide of the input pressure compensator (52).
EP05799204A 2004-10-06 2005-10-06 Hydraulic control arrangement Not-in-force EP1812715B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004048684A DE102004048684A1 (en) 2004-10-06 2004-10-06 Hydraulic control arrangement
PCT/DE2005/001792 WO2006037318A1 (en) 2004-10-06 2005-10-06 Hydraulic control arrangement

Publications (2)

Publication Number Publication Date
EP1812715A2 EP1812715A2 (en) 2007-08-01
EP1812715B1 true EP1812715B1 (en) 2012-07-04

Family

ID=35601823

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05799204A Not-in-force EP1812715B1 (en) 2004-10-06 2005-10-06 Hydraulic control arrangement

Country Status (4)

Country Link
US (1) US7870728B2 (en)
EP (1) EP1812715B1 (en)
DE (1) DE102004048684A1 (en)
WO (1) WO2006037318A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019092206A1 (en) 2017-11-10 2019-05-16 Syn Trac Gmbh Hydraulic system for a vehicle and a vehicle having such a hydraulic system

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006008940A1 (en) 2006-02-23 2007-08-30 Robert Bosch Gmbh Hydraulic control arrangement for actuating multiple consumers, has input pressure balance provided in pressure medium flow path between pump and one of two consumers
DE102007045802A1 (en) * 2007-08-16 2009-02-19 Robert Bosch Gmbh Hydraulic control arrangement
EP2025948A3 (en) * 2007-08-16 2013-03-27 Robert Bosch GmbH Hydraulic control device
EP2028376B1 (en) * 2007-08-22 2013-11-27 Robert Bosch GmbH Hydraulic control device
DE102007045803A1 (en) * 2007-08-22 2009-02-26 Robert Bosch Gmbh Hydraulic control arrangement
WO2009114407A1 (en) * 2008-03-10 2009-09-17 Parker-Hannifin Corporation Hydraulic system having multiple actuators and an associated control method
DE102009028816A1 (en) * 2009-08-21 2011-02-24 Deere & Company, Moline Hydraulic arrangement
DE102010027964A1 (en) * 2010-04-20 2011-10-20 Deere & Company Hydraulic arrangement
SE1350633A1 (en) * 2013-05-24 2014-11-25 BAE Systems Hägglunds Aktiebolag Method and system for controlling hydraulic device
DE102013214734A1 (en) * 2013-07-29 2015-01-29 Robert Bosch Gmbh Hydraulic control arrangement and method for supplying multiple consumers with it
CA2926228C (en) 2013-10-03 2022-05-17 Transocean Innovation Labs, Ltd. Hydraulic devices and methods of actuating same
DE102013223288A1 (en) * 2013-11-15 2015-05-21 Robert Bosch Gmbh Hydraulic control arrangement
IT201800020131A1 (en) * 2018-12-18 2020-06-18 Cnh Ind Italia Spa HYDRAULIC ARRANGEMENT FOR WORK VEHICLES INCLUDING A PRIORITY VALVE

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4335577A (en) * 1980-06-19 1982-06-22 Deere & Company Hydraulic system having variable displacement pumps controlled by power beyond flow
US4400937A (en) * 1982-09-29 1983-08-30 Deere & Company Control for quickly effecting displacement changes in a pump supplying fluid to primary and secondary function control valves
DE3629471A1 (en) * 1986-08-29 1988-03-03 Bosch Gmbh Robert Hydraulic control arrangement
JPH02107802A (en) * 1988-08-31 1990-04-19 Hitachi Constr Mach Co Ltd Hydraulic driving device
DE69004789T3 (en) 1989-01-18 1997-12-18 Hitachi Construction Machinery HYDRAULIC DRIVE UNIT FOR CONSTRUCTION MACHINERY.
US4977928A (en) * 1990-05-07 1990-12-18 Caterpillar Inc. Load sensing hydraulic system
JP2828490B2 (en) 1990-06-19 1998-11-25 日立建機株式会社 Load sensing hydraulic drive circuit controller
DE4127342C2 (en) 1991-08-19 1995-02-16 Danfoss As Hydraulic system with a pump
DE4239109C1 (en) * 1992-11-20 1994-06-30 Danfoss As Hydraulic system
DE4433633C1 (en) * 1994-09-21 1995-12-07 Wessel Hydraulik Hydraulic switching unit for operation of exchangeable additional device on hydraulic excavators
US5540049A (en) 1995-08-01 1996-07-30 Caterpillar Inc. Control system and method for a hydraulic actuator with velocity and force modulation control
GB2352275B (en) * 1999-07-17 2004-02-18 Agco Gmbh & Co Hydraulic system for utility vehicles
DE10115650A1 (en) * 2001-03-29 2002-10-02 Bosch Gmbh Robert Hydraulic control device
DE10214850A1 (en) * 2002-04-04 2003-10-30 Cnh Oesterreich Gmbh Hydraulic system of a tractor with an attachment
JP4081487B2 (en) * 2004-12-28 2008-04-23 東芝機械株式会社 Hydraulic control valve

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019092206A1 (en) 2017-11-10 2019-05-16 Syn Trac Gmbh Hydraulic system for a vehicle and a vehicle having such a hydraulic system
DE102017126505B4 (en) 2017-11-10 2023-06-15 Syn Trac Gmbh Hydraulic system for a vehicle and a vehicle with such a hydraulic system

Also Published As

Publication number Publication date
US7870728B2 (en) 2011-01-18
US20080202110A1 (en) 2008-08-28
WO2006037318A1 (en) 2006-04-13
EP1812715A2 (en) 2007-08-01
DE102004048684A1 (en) 2006-04-13

Similar Documents

Publication Publication Date Title
EP1812715B1 (en) Hydraulic control arrangement
EP1664551B1 (en) Control system and method for supplying pressure means to at least two hydraulic consumers
EP1588057B1 (en) Hydraulic system for linear drives controlled by a displacer element
EP1644643B1 (en) Method and arrangement for controlling at least two hydraulic consumers
EP1710446B1 (en) Hydraulic control device and control block
EP1989450B1 (en) Hydraulic control arrangement
DE102010009704A1 (en) Hydraulic drive and method for controlling such a drive
DE102006060326A1 (en) Hydraulic valve arrangement
EP2142808B1 (en) Hydraulic control arrangement
DE102012001874A1 (en) Hydraulic control arrangement
EP2171289A1 (en) Control device for at least two hydraulic drives
EP1565658B1 (en) Hydraulic dual circuit system
EP1497559B1 (en) Hydraulic control system using load-sensing technology
DE112004002768B4 (en) Hydraulic control system
EP1954949B1 (en) Hydraulic control device
EP2028376B1 (en) Hydraulic control device
DE102008008102A1 (en) Method for supplying pressure medium to e.g. hydraulic cylinders of hydraulic excavator, involves attaching consumer similar with respect to load pressure or required stream to one pump
EP1253327B1 (en) Hydraulic control circuit
WO2016091528A1 (en) Hydraulic valve arrangement, hydraulic valve block with such a valve arrangement, and hydraulic drive comprising such a valve block
DE102007045802A1 (en) Hydraulic control arrangement
DE10114042A1 (en) Hydraulic system for two constant pumps
WO2023241843A1 (en) Volume flow supply
EP2303614B1 (en) Circuit configuration and stabilization device using the circuit configuration
EP3415769A1 (en) Valve assembly for a traction drive
EP2025948A2 (en) Hydraulic control device

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: 20070504

AK Designated contracting states

Kind code of ref document: A2

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 NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

RIN1 Information on inventor provided before grant (corrected)

Inventor name: KEUPER, GERHARD

Inventor name: LOEDIGE, HEINRICH

Inventor name: STACHNIK, PETER

Inventor name: JESSEN, SOENKE

DAX Request for extension of the european patent (deleted)
R17D Deferred search report published (corrected)

Effective date: 20060413

RIN1 Information on inventor provided before grant (corrected)

Inventor name: LOEDIGE, HEINRICH

Inventor name: STACHNIK, PETER

Inventor name: KEUPER, GERHARD

Inventor name: JESSEN, SOENKE

17Q First examination report despatched

Effective date: 20090827

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

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

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 565285

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120715

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: 502005012885

Country of ref document: DE

Effective date: 20120830

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20120704

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

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: 20120704

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

Effective date: 20120704

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

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: 20120704

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: 20120704

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: 20120704

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: 20121104

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

Ref country code: FR

Payment date: 20121113

Year of fee payment: 8

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: 20120704

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: 20121005

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: 20121105

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: 20120704

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: 20120704

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

Ref country code: IT

Payment date: 20121025

Year of fee payment: 8

Ref country code: GB

Payment date: 20121023

Year of fee payment: 8

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: 20120704

BERE Be: lapsed

Owner name: BOSCH REXROTH A.G.

Effective date: 20121031

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

Ref country code: DK

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

Effective date: 20120704

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: 20120704

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: 20120704

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: 20120704

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: 20121015

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

Ref country code: DE

Payment date: 20121217

Year of fee payment: 8

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

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 NON-PAYMENT OF DUE FEES

Effective date: 20121031

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: 20120704

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26N No opposition filed

Effective date: 20130405

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: IE

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

Effective date: 20121006

Ref country code: CH

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

Effective date: 20121031

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: 20121004

Ref country code: LI

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

Effective date: 20121031

Ref country code: BE

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

Effective date: 20121031

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502005012885

Country of ref document: DE

Effective date: 20130405

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 565285

Country of ref document: AT

Kind code of ref document: T

Effective date: 20121031

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: 20121031

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: 20120704

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: 20121006

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

Effective date: 20131006

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

Ref country code: GB

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

Effective date: 20131006

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

Effective date: 20051006

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005012885

Country of ref document: DE

Effective date: 20140501

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20140630

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

Ref country code: FR

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

Effective date: 20131031

Ref country code: IT

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

Effective date: 20131006

Ref country code: DE

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

Effective date: 20140501