EP1170510A2 - Hydraulic control arrangement for supplying pressurised fluid preferably to several hydraulic loads - Google Patents

Hydraulic control arrangement for supplying pressurised fluid preferably to several hydraulic loads Download PDF

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Publication number
EP1170510A2
EP1170510A2 EP01110563A EP01110563A EP1170510A2 EP 1170510 A2 EP1170510 A2 EP 1170510A2 EP 01110563 A EP01110563 A EP 01110563A EP 01110563 A EP01110563 A EP 01110563A EP 1170510 A2 EP1170510 A2 EP 1170510A2
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
piston
line
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP01110563A
Other languages
German (de)
French (fr)
Other versions
EP1170510A3 (en
EP1170510B1 (en
Inventor
Peter BÜTTNER
Tatu Miikkulainen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
Bosch Rexroth AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE10035575A external-priority patent/DE10035575A1/en
Application filed by Mannesmann Rexroth AG, Bosch Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP1170510A2 publication Critical patent/EP1170510A2/en
Publication of EP1170510A3 publication Critical patent/EP1170510A3/en
Application granted granted Critical
Publication of EP1170510B1 publication Critical patent/EP1170510B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/047—Preventing foaming, churning or cavitation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/51—Pressure control characterised by the positions of the valve element
    • F15B2211/513—Pressure control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—Methods of control of the load sensing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

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

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Abstract

Hydraulic control arrangement for supplying pressure medium to preferably several hydraulic consumers (22, 23) comprises valve devices (70) via which the pressure medium is fed from the inlet line (41) into a section (42) of the outlet line (43) when the pressure in this section falls below the initial stressing pressure. Preferred Features: The valve devices comprise a two-way feed valve in addition to the servo valve (60). The feed valve is a two-way pressure-reducing valve set at a pressure which is lower, preferably about 2 bar lower, than the initial stressing pressure.

Description

Die Erfindung betrifft eine hydraulische Steueranordnung, mit der vorzugsweise mehrere hydraulische Verbraucher mit Druckmittel versorgt werden und die die Merkmale aus dem Oberbegriff des Patentanspruchs 1 aufweist.The invention relates to a hydraulic control arrangement, with which preferably several hydraulic consumers are supplied with pressure medium and which the Features from the preamble of claim 1.

Bei einer hydraulische Steueranordnung gemäß dem Oberbegriff des Patentanspruchs 1 handelt es sich um eine solche nach dem lastfühlenden (load-sensing) Prinzip, bei dem eine Verstellpumpe in Abhängigkeit vom höchsten Lastdruck der betätigten hydraulischen Verbraucher jeweils so eingestellt wird, daß der Pumpendruck um eine bestimmte, vorzugsweise im Bereich zwischen 10 bar und 25 bar liegende Druckdifferenz Δp über dem höchsten Lastdruck liegt. Den hydraulischen Verbrauchern fließt das Druckmittel über verstellbare, üblicherweise durch Steuernuten an den Steuerkolben der Wegeventile realisierte Zumeßblenden zu, die zwischen einer von der Verstellpumpe abgehenden Zulaufleitung und den hydraulischen Verbrauchern angeordnet sind. Durch den Wegeventilen zugeordnete Individualdruckwaagen wird erreicht, daß bei von der Verstellpumpe ausreichend gelieferter Druckmittelmenge unabhängig von den Lastdrücken der hydraulischen Verbraucher über die Zumeßblenden eine bestimmte, gegenüber Δp kleinere Druckdifferenz besteht, so daß die einem hydraulischen Verbraucher zufließende Druckmittelmenge nur noch vom Öffnungsquerschnitt der jeweiligen Zumeßblende abhängt. Wird eine Zumeßblende weiter geöffnet, so muß mehr Druckmittelmenge über sie fließen, um die bestimmte Druckdifferenz zu erzeugen. Die Verstellpumpe wird jeweils so verstellt, daß sie die benötigte Druckmittelmenge liefert. Man spricht deshalb auch von einer Bedarfsstromregelung.In a hydraulic control arrangement according to the preamble of the claim 1 is one after the load-sensing Principle in which a variable pump depending on the highest load pressure actuated hydraulic consumer is set so that the pump pressure around a certain, preferably in the range between 10 bar and 25 bar pressure difference Δp is above the highest load pressure. The hydraulic one The pressure medium flows through consumers via adjustable, usually through Control orifices on the control pistons of the directional control valves, between an inlet line from the variable displacement pump and the hydraulic Consumers are arranged. Assigned by the directional valves Individual pressure compensators is achieved that sufficient by the variable pump delivered pressure medium quantity independent of the load pressures of the hydraulic Consumers via the metering orifices a certain one, smaller than Δp Pressure difference exists, so that the flowing to a hydraulic consumer Pressure medium quantity only from the opening cross section of the respective metering orifice depends. If a metering orifice is opened further, more pressure medium must be added flow over them to produce the determined pressure difference. The variable displacement pump is adjusted so that it delivers the required amount of pressure medium. you therefore speaks of a demand flow control.

Aus der EP 0 566 449 A1 ist eine lastfühlende hydraulische Steueranordnung bekannt, bei der die Individualdruckwaagen den Zumeßblenden nachgeschaltet sind. A load-sensing hydraulic control arrangement is known from EP 0 566 449 A1, in which the individual pressure compensators are connected downstream of the metering orifices.

Die Druckwaagen werden in Öffnungsrichtung von dem Druck nach der jeweiligen Zumeßblende und in Schließrichtung von einem in einem rückwärtigen Steuerraum anstehenden Steuerdruck beaufschlagt, der üblicherweise dem höchsten Lastdruck aller von derselben Hydropumpe versorgten hydraulischen Verbraucher entspricht. Wenn bei einer gleichzeitigen Betätigung mehrerer hydraulischer Verbraucher die Zumeßblenden so weit aufgemacht werden, daß die von der bis zum Anschlag verstellten Hydropumpe gelieferte Druckmittelmenge kleiner ist als die insgesamt geforderte Druckmittelmenge, werden die den einzelnen hydraulischen Verbrauchern zufließenden Druckmittelmengen unabhängig vom jeweiligen Lastdruck der hydraulischen Verbraucher verhältnisgleich reduziert. Man spricht deshalb von einer Steuerung mit lastunabhängiger Durchflußverteilung (LUDV-Steuerung). Derart angesteuerte hydraulische Verbraucher werden kurz LUDV-Verbraucher genannt. Weil bei einer LUDV-Steuerung auch der höchste Lastdruck abgefühlt und von der Hydropumpe durch die Variation der geförderten Druckmittelmenge ein um eine bestimmte Druckdifferenz Δp über dem höchsten Lastdruck liegender Zulaufdruck erzeugt wird, ist eine LUDV-Steuerung ein Sonderfall einer lastfühlenden oder load-sensing Steuerung (LS-Steuerung).The pressure compensators are in the opening direction by the pressure after the respective Orifice plate and in the closing direction of one in a rear control room applied control pressure, which is usually the highest Load pressure of all hydraulic consumers supplied by the same hydraulic pump equivalent. If several hydraulic consumers are operated simultaneously the metering orifices are opened so far that the from to The amount of pressure medium delivered to the adjusted hydraulic pump is smaller than that total amount of pressure medium required, the individual hydraulic Amounts of pressure medium flowing to consumers regardless of the respective Load pressure of the hydraulic consumers reduced proportionally. One speaks therefore from a control with load-independent flow distribution (LUDV control). Hydraulic consumers controlled in this way become LUDV consumers for short called. Because with a LUDV control, the highest load pressure sensed and by the hydraulic pump by varying the amount of pressure medium delivered a by a certain pressure difference Δp above the highest load pressure LUDV control is a special case of a load-sensing or load-sensing control (LS control).

Für mehrere hydraulische Verbraucher, denen Druckmittel jeweils über eine Zumeßblende mit vorgeschalteter Individualdruckwaage zufließt, die in Schließrichtung nur vom Druck vor der Zumeßblende und in Öffnungsrichtung nur vom Lastdruck des jeweiligen hydraulischen Verbrauchers und von einer Druckfeder beaufschlagt ist, erhält man keine lastunabhängige Durchflußverteilung. Man hat eine bloße LS-Steuerung und einen LS-Verbraucher. Eine solche Steuerung ist z.B. durch die DE 197 14 141 A1 bekannt. Bei einer gleichzeitigen Betätigung mehrerer hydraulischer Verbraucher und nicht ausreichend von der Verstellpumpe gelieferter Druckmittelmenge wird hier nur die dem lastdruckhöchsten hydraulischen Verbraucher zufließende Druckmittelmenge reduziert.For several hydraulic consumers, each of whom has a metering orifice with an upstream individual pressure compensator that flows in the closing direction only from the pressure in front of the metering orifice and in the opening direction only from Load pressure of the respective hydraulic consumer and from a compression spring no load-independent flow distribution is obtained. One has a mere LS control and an LS consumer. Such control is e.g. known from DE 197 14 141 A1. With simultaneous actuation several hydraulic consumers and not enough of the variable pump The quantity of pressure medium supplied is only that of the highest hydraulic pressure The amount of pressure medium flowing to the consumer is reduced.

Eine LUDV-Steueranordnung mit den Merkmalen aus dem Oberbegriff des Patentanspruchs 1 ist aus dem Datenblatt RD 64 284/05.99 der Anmelderin bekannt. An LUDV control arrangement with the features from the preamble of the claim 1 is known from the data sheet RD 64 284 / 05.99 from the applicant.

Bei dieser ist in der Ablaufleitung ein sogenanntes Vorspannventil angeordnet, durch das in dem Abschnitt der Ablaufleitung, der stromauf des Vorspannventils liegt, ein Vorspanndruck aufrechterhalten werden soll, der im Bereich von 10 bar liegen kann. Zwischen dem genannten Abschnitt der Ablaufleitung und der Verbraucherleitung, die mit dem größeren zweiten Druckraum des Differentialzylinders verbunden ist, ist ein Rückschlagventil angeordnet, das zur Verbraucherleitung hin öffnet. Das Rückschlagventil kann auch mit einem Druckbegrenzungsventil zusammengefaßt sein.In this, a so-called preload valve is arranged in the drain line, through that in the section of the drain line upstream of the bias valve , a preload pressure should be maintained that is in the range of 10 bar can lie. Between the mentioned section of the drain pipe and the consumer pipe, the one with the larger second pressure chamber of the differential cylinder is connected, a check valve is arranged leading to the consumer line opens. The check valve can also be equipped with a pressure relief valve be summarized.

Durch das Vorsehen des Vorspannventils und des Rückschlagventils wird erreicht, daß bei einer negativen am Differentialzylinder angreifenden Last, also einer Last, die am Differentialzylinder eine Kraft erzeugt, die in die durch die Stellung des Wegeventils vorgegebene Bewegungsrichtung des Differentialzylinders gerichtet ist, das aus dem ersten Druckraum verdrängte Druckmittel zusätzlich zu dem von der Pumpe geförderten und über die Zumeßblende des Wegeventils und gegebenenfalls eine Individualdruckwaage fließenden Druckmittel dem zweiten Druckraum des Differentialzylinders zugeführt wird. Auf diese Weise soll für die Bauteile schädliche und die Steuerung erschwerende Kavitation im zweiten Druckraum des Differentialzylinders vermieden werden. Es hat sich allerdings gezeigt, daß bei der bekannten Steueranordnung unter besonderen Umständen, z. B bei Kolbenstangen mit besonders großem Durchmesser im Verhältnis zum Durchmesser des Kolbens oder bei besonders schweren Lasten noch Kavitation auftreten kann.The provision of the preload valve and the check valve ensures that that with a negative load acting on the differential cylinder, i.e. a load, which generates a force on the differential cylinder, which in the by the position of the Directional valve directed direction of movement of the differential cylinder is, the pressure medium displaced from the first pressure chamber in addition to that of pumped and via the metering orifice of the directional valve and, if necessary an individual pressure compensator flowing fluid in the second pressure chamber of the differential cylinder is supplied. This is intended for the components harmful cavitation in the second pressure chamber of the controller, which complicates the control Differential cylinders can be avoided. However, it has been shown that the known control arrangement under special circumstances, e.g. B for piston rods with a particularly large diameter in relation to the diameter of the Piston or cavitation can occur with particularly heavy loads.

Der Erfindung liegt demnach die Zielsetzung zugrunde, eine hydraulische Steueranordnung, die die Merkmale aus dem Oberbegriff des Patentanspruchs 1 aufweist, so weiterzuentwickeln, daß die Gefahr von Kavitation weiter verringert wird.The invention is therefore based on the objective of a hydraulic control arrangement, which has the features from the preamble of claim 1, to develop further so that the risk of cavitation is further reduced.

Das angestrebte Ziel wird erfindungsgemäß dadurch erreicht, daß bei einer gattungsgemäßen hydraulischen Steueranordnung gemäß dem kennzeichnenden Teil des Patentanspruchs 1 Ventilmittel vorhanden sind, über die Druckmittel aus der Zulaufleitung, also von der Verstellpumpe gefördertes Druckmittel, in den Abschnitt der Ablaufleitung, in dem ein Vorspanndruck aufrechterhalten werden soll, einspeisbar ist, wenn in dem Abschnitt der Druck auf einen unterhalb des Vorspanndrucks liegenden Wert abfällt. Bei einer erfindungsgemäßen hydraulischen Steueranordnung gelangt also außer dem aus dem ersten Druckraum des Differentialzylinders verdrängten Druckmittel nicht nur eine von der Verstellpumpe geförderte zusätzliche Druckmittelmenge, die durch den Öffnungsquerschnitt der Zumeßblende und die beim Vorhandensein einer Individualdruckwaage oder mangelnder Meldung eines Lastdrucks an die Verstellpumpe auf jeden Fall niedrige Druckdifferenz über die Zumeßblende bestimmt ist, zum zweiten Druckraum. Vielmehr fließt weiteres von der Verstellpumpe gefördertes Druckmittel über die Ventilmittel zwischen der Zulaufleitung und der Ablaufleitung und über das Rückschlagventil dem zweiten Druckraum des Differentialzylinders zu. Der Öffnungsquerschnitt der Ventilmittel und des Rückschlagventils kann sehr groß gestaltet werden. Zudem steht der volle Pumpendruck ohne Abdrosselung durch eine Individualdruckwaage als Antrieb für den Druckmittelfluß zur Verfügung.The desired goal is achieved according to the invention in that with a generic hydraulic control arrangement according to the characteristic Part of claim 1 valve means are available via the pressure medium the supply line, i.e. pressure medium delivered by the variable displacement pump, into the section the drain line in which a preload pressure is to be maintained, is feedable if in the section the pressure to a below the bias pressure value falls. In a hydraulic Control arrangement thus comes from the first pressure chamber of the differential cylinder displaced pressure medium not only one promoted by the variable pump additional amount of pressure medium through the opening cross section of the Orifice plate and the presence of an individual pressure compensator or in any case low signal of a load pressure to the variable pump Pressure difference over the metering orifice is determined to the second pressure chamber. Rather, further pressure medium delivered by the variable displacement pump flows through the Valve means between the inlet line and the outlet line and via the check valve to the second pressure chamber of the differential cylinder. The opening cross section the valve means and the check valve can be made very large become. In addition, the full pump pressure is available without throttling using an individual pressure compensator available as a drive for the pressure medium flow.

Vorteilhafte Ausgestaltungen einer erfindungsgemäßen hydraulischen Steueranordnung kann man den Unteransprüchen entnehmen.Advantageous configurations of a hydraulic control arrangement according to the invention can be found in the subclaims.

Auf einfache Weise sind die Ventilmittel gemäß Patentanspruch 2 durch ein zusätzlich zum Vorspannventil vorhandenes 2-Wege-Einspeiseventil gebildet.In a simple manner, the valve means according to claim 2 by an additional existing 2-way feed valve to the preload valve.

Besonders bevorzugt ist eine Ausgestaltung gemäß Patentanspruch 3, wonach die Ventilmittel ein Druckreduzierventil mit einem Ventilkolben umfassen, der im Sinne eines Schließens der fluidischen Verbindung zwischen der Zulaufleitung und dem Abschnitt der Ablaufleitung vom Druck in diesem Abschnitt und im Sinne eines Öffnens der fluidischen Verbindung von einer Feder beaufschlagt ist. Der Aufwand für die Betätigung der Ventilmittel in Abhängigkeit von dem in der Ablaufleitung stromauf des Vorspannventils herrschenden Drucks ist dann besonders gering. An embodiment according to claim 3, according to which is particularly preferred the valve means comprise a pressure reducing valve with a valve piston which in the Meaning of closing the fluidic connection between the feed line and the section of the drain pipe from the pressure in this section and in the sense opening of the fluidic connection is acted upon by a spring. The Effort for actuating the valve means depending on that in the drain line the pressure prevailing upstream of the preload valve is then special low.

Grundsätzlich ist es denkbar, das Vorspannventil und die zwischen der Zulaufleitung und der Ablaufleitung angeordneten Ventilmittel zu einem auf einen bestimmten Vorspanndruck eingestellten 3-Wege-Druckregelventil zusammenzufassen, an dessen Regelausgang der vorzuspannende Abschnitt der Ablaufleitung, an dessen Druckanschluß die Zulaufleitung und an dessen Tankanschluß der zum Tank führende Abschnitt der Ablaufleitung angeschlossen ist. Es ist jedoch eine bessere Abstimmung auf unterschiedliche Durchflußmengen und die Verwendung eines schon in der Praxis bewährten Vorspannventils möglich, wenn, wie in Patentanspruch 2 angegeben, ein separates Einspeiseventil verwendet wird, das dann gemäß Patentanspruch 4 als 2-Wege-Druckreduzierventil ausgebildet ist. Dieses ist auf einen Druck eingestellt, der kleiner als der Vorspanndruck ist. Somit ist sichergestellt, daß nicht im normalen Betrieb Druckmittel aus der Zulaufleitung über das Druckreduzierventil in die Ablaufleitung und von dort über das Vorspannventil zum Tank strömt. Dies würde unnötige Energieverluste mit sich bringen. Eine ausreichende Sicherheit vor solchen Verlusten erscheint gewährleistet, wenn das Druckreduzierventil auf einen Druck eingestellt ist, der gemäß Patentanspruch 5 etwa 2 bar unterhalb des Vorspanndrucks liegt.In principle, it is conceivable for the preload valve and the one between the inlet line and the drain line arranged valve means to a certain one Pre-set 3-way pressure control valve, at the control outlet the section of the drain pipe to be prestressed, at its pressure connection, the inlet line and at its tank connection, the Tank leading section of the drain line is connected. However, it is one better adjustment to different flow rates and usage of a preload valve already proven in practice is possible if, as in claim 2 specified, a separate feed valve is used, the is then designed according to claim 4 as a 2-way pressure reducing valve. This is set to a pressure that is less than the preload pressure. Consequently It is ensured that pressure medium from the supply line is not in normal operation via the pressure reducing valve into the drain line and from there via the preload valve flows to the tank. This would result in unnecessary energy losses. A Sufficient security against such losses appears to be guaranteed if the pressure reducing valve is set to a pressure which according to claim 5 is approximately 2 bar below the preload pressure.

Aus dem Datenblatt RD 64 282/10.99 der Anmelderin sind Wegeventilscheiben von LS-Steuerblöcken bekannt, bei denen in zwei parallel zueinander verlaufenden Bohrungen der Scheibe der Steuerkolben des Wegeventils, mit dem die Bewegungsrichtung und die Geschwindigkeit eines hydraulischen Verbrauchers steuerbar sind, und der Regelkolben einer Individualdruckwaage untergebracht sind. Dieser Regelkolben hat einen bestimmten Außendurchmesser, ist in bestimmter Weise mit Kolbenbunden, einem Kolbenhals und einem Anschlagzapfen und mit einem von der Außenfläche des Kolbenhalses durch ihn hindurch zu einer seiner Stirnflächen führenden Fluidpfad ausgestattet und wird von einer den Anschlagzapfen umgebenden Druckfeder beaufschlagt, deren Druckäquivalent bei dem gegebenen Außendurchmesser des Regelkolbens bei etwa 10 bar liegt. Vorteilhafterweise wird nun gemäß Patentanspruch 6 für das 2-Wege-Druckreduzierventil eine Baugruppe aus Kolben und Feder verwendet, die der in der Praxis bewährten und von ihrer Auslegung hinsichtlich Durchflußmenge und Federkraft geeigneten Baugruppe entspricht.Directional valve disks are from data sheet RD 64 282 / 10.99 from the applicant known from LS control blocks, in which two parallel to each other Bores of the disc of the control piston of the directional valve, with which the direction of movement and the speed of a hydraulic consumer are controllable, and the control piston of an individual pressure compensator housed are. This control piston has a certain outside diameter and is in a certain one Way with piston collars, a piston neck and a stop pin and with one from the outer surface of the piston neck through it its end faces leading fluid path and is supported by one of the stop pins surrounding compression spring, the pressure equivalent at the given outer diameter of the control piston is about 10 bar. Advantageously, according to claim 6 for the 2-way pressure reducing valve uses a piston and spring assembly that the in proven in practice and of their design with regard to flow rate and Corresponding spring force suitable assembly.

Ein Ausführungsbeispiel einer erfindungsgemäßen hydraulischen Steueranordnung sowie die konstruktive Ausbildung eines in der Steueranordnung verwendbaren 2-Wege-Druckreduzierventils sind in den Zeichnungen dargestellt. An Hand dieser Zeichnungen wird die Erfindung nun näher erläutert.An embodiment of a hydraulic control arrangement according to the invention and the design of a usable in the control arrangement 2-way pressure reducing valve are shown in the drawings. Based these drawings, the invention will now be explained in more detail.

Es zeigenShow it

Figur 1 das Ausführungsbeispiel der hydraulischen Steueranordnung undFigure 1 shows the embodiment of the hydraulic control arrangement and

Figur 2 eine Ventilscheibe teilweise im Schnitt durch das in sie eingebaute 2-Wege-Druckreduzierventil.Figure 2 shows a valve disc partially in section through the built-in 2-way pressure reducing valve.

Bei der hydraulischen Steueranordnung nach Figur 1 beinhaltet ein Steuerblock 7 ein Eingangselement 8, eine Endplatte 9 und dazwischen zwei Wegeventilsektionen 10 und 11, von denen jede ein Wegeventil 12 bzw. 13 mit einer Zulaufkammer 14, der von einer Hydropumpe 18 gefördertes Druckmittel zufließen kann, einer Ablaufkammer 15, von der Druckmittel zu einem Tank 19 ablaufen kann, und zwei Verbraucherkammern 16 und 17 aufweist, die über Verbraucherleitungen 20, 21 mit einem doppeltwirkenden hydraulischen Verbraucher, nämlich mit einem Differentialzylinder 22 bzw. 23 verbunden sind. Diese besitzen einen stangenseitigen, ringförmigen, ersten Druckraum 24, von dem eine Verbraucherleitung 21 zu einer Verbraucherkammer 17 führt, und einen stangenabseitigen, kreiszylindrischen, zweiten Druckraum 25, von dem eine Verbraucherleitung 20 zu einer Verbraucherkammer 16 führt.In the hydraulic control arrangement according to FIG. 1, a control block 7 contains an input element 8, an end plate 9 and in between two directional valve sections 10 and 11, each of which has a directional control valve 12 or 13 with an inlet chamber 14, which can flow from a hydraulic pump 18 supplied pressure medium, one Drain chamber 15, from which pressure medium can drain to a tank 19, and two Has consumer chambers 16 and 17, the consumer lines 20, 21st with a double-acting hydraulic consumer, namely with a differential cylinder 22 and 23 are connected. These have a rod-side, annular, first pressure chamber 24, from which a consumer line 21 to a Consumer chamber 17 leads, and a rod-side, circular cylindrical, second pressure chamber 25, from which a consumer line 20 to a consumer chamber 16 leads.

Das Wegeventil 12 hat einen Steuerkolben 30 und das Wegeventil 13 einen Steuerkolben 31. Beide Steuerkolben 30 und 31sind aus einer Mittelstellung, in der die Zulaufkammer, die Ablaufkammer und die beiden Verbraucherkammern gegeneinander abgesperrt sind, in entgegengesetzte Richtungen in Arbeitsstellungen verstellbar, in der zwischen der Zulaufkammer 14 und der Verbraucherkammer 16 bzw. der Verbraucherkammer 17 eine nicht näher dargestellte, in ihrem Öffnungsquerschnitt von der Größe der Verschiebung des Steuerkolbens aus seiner Mittelstellung abhängige Zumeßblende offen ist. Bei einer Verstellung des Steuerkolbens in die eine Richtung ist bei beiden Wegeventilsektionen die Verbraucherkammer 16 über einen ebenfalls vom Verschiebeweg des Steuerkolbens abhängigen Öffnungsquerschnitt mit der Ablaufkammer 15 verbunden. Bei einer Verstellung des Steuerkolbens 30 des Wegeventils 12 in die entgegengesetzte Richtung ist die Verbraucherkammer 17 über einen vom Verschiebeweg des Steuerkolbens 30 abhängigen Öffnungsquerschnitt mit der Ablaufkammer 15 verbunden. Der Steuerkolben 31 des Wegeventils 13 dagegen ist ein sogenannter Regenerationskolben, über den bei einer Verschiebung in die entgegengesetzte Richtung die Verbraucherkammer 17 über eine Ablaufblende und die Zumeßblende mit der Verbraucherkammer 16 verbunden ist. Beim Ausfahren der Kolbenstange des Differentialzylinders 23 aus dessen Druckraum 24 verdrängtes Öl gelangt also nicht zur Ablaufkammer 15 des Wegeventils 13, sondern zur Verbraucherkammer 16 und von dort in den Druckraum 25 des Differentialzylinders 23.The directional control valve 12 has a control piston 30 and the directional control valve 13 has a control piston 31. Both control pistons 30 and 31 are from a central position in which the Inlet chamber, the outlet chamber and the two consumer chambers against each other are locked in opposite directions in working positions adjustable in the between the inlet chamber 14 and the consumer chamber 16th or the consumer chamber 17, not shown in detail, in its opening cross-section on the size of the displacement of the control piston from its central position dependent metering orifice is open. When the control piston is adjusted the consumer chamber is in one direction for both directional valve sections 16 via a likewise dependent on the displacement path of the control piston Opening cross section connected to the drain chamber 15. With an adjustment of the control piston 30 of the directional control valve 12 in the opposite direction is the consumer chamber 17 via one of the displacement of the control piston 30 dependent opening cross section connected to the drain chamber 15. The Control piston 31 of the directional control valve 13, on the other hand, is a so-called regeneration piston, over which when moving in the opposite direction Consumer chamber 17 via a drain panel and the metering panel with the Consumer chamber 16 is connected. When extending the piston rod of the Differential cylinder 23 thus displaced oil from the pressure chamber 24 passes not to the drain chamber 15 of the directional control valve 13, but to the consumer chamber 16 and from there into the pressure chamber 25 of the differential cylinder 23.

Der Zulaufkammer 14 eines jeden Wegeventils 12 und 13 vorgeschaltet ist jeweils eine Individualdruckwaage 32, an deren Regelkolben zwei Steuerräume 33 und 34 angrenzen. Der Steuerraum 33 ist mit einer Lastmeldekammer 35 des jeweiligen Wegeventils 12, 13 und der Steuerraum 34 mit der Zulaufkammer 14 verbunden. Die Lastmeldekammer 35 ist in der Mittelstellung des Steuerkolbens 30, 31 zum Tank entlastet und in einer seitlichen Arbeitsstellung jeweils mit der Verbraucherkammer verbunden, der über die Zumeßblende Öl zugeführt wird. Der Regelkolben der Druckwaage 32 wird in Öffnungsrichtung von einer Druckfeder 36 und von dem im Steuerraum 33 herrschenden Druck und in Schließrichtung von dem im Steuerraum 34 herrschenden Druck beaufschlagt.The inlet chamber 14 of each directional control valve 12 and 13 is connected upstream an individual pressure compensator 32, on the control piston of which two control rooms 33 and 34 adjoin. The control room 33 is equipped with a load reporting chamber 35 Directional control valve 12, 13 and the control chamber 34 are connected to the inlet chamber 14. The load reporting chamber 35 is in the central position of the control piston 30, 31 Tank relieved and in a side working position with the consumer chamber connected, which is supplied via the metering orifice oil. The control piston the pressure compensator 32 is in the opening direction by a compression spring 36 and the pressure prevailing in the control chamber 33 and in the closing direction from that in the Control room 34 prevailing pressure.

Über eine Wechselventilkette mit Wechselventilen 37 wird der jeweils höchste in einem Steuerraum 33 anstehende Druck, also der jeweils höchste Lastdruck, an einen Ausgang LS im Eingangselement 8 des Steuerblocks 7 gegeben und über eine Lastmeldeleitung 38 an einen LS-Pumpenregler 39 gemeldet, der die Verstellpumpe 18 jeweils so einstellt, daß sich in einem von der Verstellpumpe 18 abgehenden Abschnitt einer Zulaufleitung 40, über die den Zulaufkammern 14 der Wegeventile 12 und 13 Hydrauliköl zuführbar ist, ein Pumpendruck einstellt, der um eine bestimmte Druckdifferenz Δp über dem gemeldeten höchsten Lastdruck liegt. Die Druckdifferenz liegt üblicherweise im Bereich zwischen 10 bar und 25 bar. Vorliegend möge eine Druckdifferenz von 20 bar eingestellt sein. Wird kein Lastdruck gemeldet, stellt sich demnach in der Zulaufleitung 40 einschließlich des Zulaufkanals 41 ein Druck (Stand-by-Druck) Δp von 20 bar ein.The highest in each case is via a shuttle valve chain with shuttle valves 37 pressure present in a control chamber 33, that is to say the highest load pressure in each case given an output LS in the input element 8 of the control block 7 and over a load signaling line 38 is reported to an LS pump controller 39 which controls the variable displacement pump 18 each set so that in one outgoing from the variable displacement pump 18 Section of an inlet line 40, via which the inlet chambers 14 Directional control valves 12 and 13 hydraulic oil can be supplied, a pump pressure that by a certain pressure difference Δp above the reported highest load pressure lies. The pressure difference is usually in the range between 10 bar and 25 bar. In the present case, a pressure difference of 20 bar may be set. Will not Reported load pressure, therefore arises in the feed line 40 including the Inlet channel 41 a pressure (stand-by pressure) Δp of 20 bar.

Die Zulaufleitung 40 setzt sich von einem Eingang P des Eingangselements 8 aus innerhalb des Steuerblocks 7 als gerader Zulaufkanal 41 fort, der durch die Wegeventilsektionen 10 und 11 hindurch bis in die Endplatte 9 geht. Mit ihm sind die Eingänge der Individualdruckwaagen 32 verbunden.The inlet line 40 is exposed to an input P of the input element 8 within the control block 7 as a straight inlet channel 41, which through the directional valve sections 10 and 11 goes through into the end plate 9. With him they are Inputs of the individual pressure compensators 32 connected.

Durch die Wegeventilsektionen geht außerdem ein Ablaufkanal 42 hindurch, der in die Endplatte 9 und in das Eingangselement 8 hineinreicht und Teil eines Ablaufströmungspfades 43 ist, über den Hydrauliköl von den Ablaufkammern 15 der Wegeventile 12 und 13 zum Tank 19 zurückströmen kann und in dem auch ein Tankanschluß T des Eingangselements 8 liegt. In jeder Wegeventilsektion, insbesondere auch in die Wegeventilsektion 11 mit dem Wegeventil 13, dessen Steuerkolben ein sogenannter Regenerationskolben ist, befindet sich ein kombiniertes Druckbegrenzungs- und Einspeiseventil 45, das zwischen der Verbraucherleitung 20 und dem Ablaufkanal 42 angeordnet ist. Die Druckbegrenzungsfunktion erfüllt das Ventil 45 für die Verbraucherleitung 20, in der es den Druck auf einen um eine bestimmte Druckdifferenz über dem Druck im Ablaufkanal liegenden Wert begrenzt. Solange der Druck in der Verbraucherleitung 20 diesen Wert nicht erreicht, wirkt das Ventil 45 wie ein zur Verbraucherleitung hin öffnendes Rückschlagventil, läßt also Druckmittel von Ablaufkanal zur Verbraucherleitung strömen, wenn der Druck in der Verbraucherleitung niedriger als im Ablaufkanal ist, und sperrt, wenn der Druck in der Verbraucherleitung höher ist als im Ablaufkanal. Weitere Druckbegrenzungs- und Einspeiseventile 46 befinden sich zwischen jeder Verbraucherleitung 21 und dem Ablaufkanal 42.A flow channel 42 also passes through the directional valve sections, which in the end plate 9 and extends into the input element 8 and part of a drain flow path 43, the hydraulic oil from the drain chambers 15 of the Directional control valves 12 and 13 can flow back to the tank 19 and also in the one Tank connection T of the input element 8 is. In every directional valve section, in particular also in the directional valve section 11 with the directional valve 13, the control piston is a so-called regeneration flask, there is a combined one Pressure limiting and feed valve 45, which is between the consumer line 20 and the drain channel 42 is arranged. The pressure limiting function is fulfilled the valve 45 for the consumer line 20, in which there is pressure to one certain pressure difference above the pressure in the drain channel is limited. As long as the pressure in the consumer line 20 does not reach this value, valve 45 acts as a check valve opening towards the consumer line, So can pressure fluid flow from the drain channel to the consumer line when the Pressure in the consumer line is lower than in the drain channel, and blocks when the pressure in the consumer line is higher than in the drain channel. Further pressure limiting and feed valves 46 are located between each consumer line 21 and the drain channel 42.

Die beiden Wegeventile 12 und 13 sind jeweils elektrohydraulisch betätigbar, wozu in jede Wegeventilsektion 10 bzw. 11 zwei elektromagnetisch proportional verstellbare Vorsteuerventile 50 integriert sind. In der Ruhestellung eines Ventils 50 ist ein zugeordneter Steuerraum am Steuerkolben 30 eines Wegeventils 11, 12 zu einem Leckölkanal 51, der durch die Wegeventilsektionen 10 und 11 hindurchführt, entlastet. Durch Erregung eines Elektromagneten wird ein Steuerraum mit einer ebenfalls durch die Wegeventilsektion 10 und 11 hindurchgeführten Steuerdruckleitung 52 verbunden. Das Steueröl wird über ein Druckreduzierventil 53, das in die Endplatte 9 eingebaut ist, dem durch die beiden Wegeventilsektionen 10 und 11 hindurch- und in die Endplatte 9 hineingeführten Zulaufkanal 41 entnommen. Das Druckminderventil 53 ist z.B. auf einen Steuerdruck von 30 bar eingestellt. Der Leckölkanal 51 ist über eine an einen Anschluß Y der Endplatte 9 angeschlossene Leitung 54 direkt mit dem Tank 19 derart verbunden, daß in dem Leckölkanal derselbe Druck wie im Tank 19 herrscht.The two directional control valves 12 and 13 can each be actuated electro-hydraulically, for which purpose in each directional valve section 10 or 11 two electromagnetically proportional adjustable Pilot valves 50 are integrated. In the rest position of a valve 50 is an assigned control chamber on the control piston 30 of a directional control valve 11, 12 a leak oil channel 51, which leads through the directional valve sections 10 and 11, relieved. By excitation of an electromagnet, a control room becomes a control pressure line also passed through the directional valve section 10 and 11 52 connected. The control oil is supplied via a pressure reducing valve 53 is installed in the end plate 9, through the two directional valve sections 10 and 11 through and into the end plate 9 introduced inlet channel 41. The pressure reducing valve 53 is e.g. set to a control pressure of 30 bar. The leak oil channel 51 is connected to a connection Y of the end plate 9 Line 54 connected directly to the tank 19 such that in the Leakage oil channel the same pressure as in tank 19.

In das Eingangselement 8 ist ein Druckbegrenzungsventil 60 eingebaut, zu dessen Eingang der Ablaufkanal 42 führt und dessen Ausgang mit dem Tankanschluß T des Eingangselements verbunden ist. Da das Druckbegrenzungsventil auf eine große Durchflußmenge ausgelegt sein muß, ist es vorzugsweise ein vorgesteuertes Ventil. Der Federraum, in dem sich die die Gegenkraft zur Druckkraft erzeugende Druckfeder 61 befindet, ist über eine Verbohrung 62 des Eingangselements an den Leckölkanal 51 angeschlossen, damit gleichbleibendes Tankdruckniveau im Federraum gewährleistet ist. Das Druckbegrenzungsventil 60 hat die Funktion, in dem stromauf von ihm liegenden Ablaufkanal 42 einen nach Einstellung konstanten Druck aufrechtzuerhalten, der auch als Vorspanndruck bezeichnet wird. Deshalb kann man das Druckbegrenzungsventil auch als Vorspannventil bezeichnen. Der Vorspanndruck ist relativ klein und liegt bei sonstigen Anwendungen im Bereich von 5 bar bis 10 bar, kann aber auch auf 15 bar eingestellt sein. Als Vorspannventil kann zum Beispiel Ventil verwendet werden, das unter der Bezeichnung MHDBV im Datenblatt RD 64 642/12.97 der Anmelderin näher dargestellt ist. Vorliegend hat sich ein Vorspanndruck zwischen 8 bar und 12 bar als günstig erwiesen.In the input element 8, a pressure relief valve 60 is installed, for the latter Input of the drain channel 42 leads and its output to the tank connection T of the input element is connected. Since the pressure relief valve on a large flow rate must be designed, it is preferably a pilot controlled Valve. The spring chamber in which the counterforce to the compressive force is generated Compression spring 61 is located through a bore 62 of the input element connected to the leak oil channel 51 so that the tank pressure level remains constant is guaranteed in the spring chamber. The pressure relief valve 60 has the function in the outlet channel 42 upstream of it a constant after setting Maintain pressure, also known as preload pressure. Therefore, the pressure relief valve can also be called a preload valve. The preload pressure is relatively small and is in other applications Range from 5 bar to 10 bar, but can also be set to 15 bar. As a preload valve For example, valve can be used, which is called MHDBV in the data sheet RD 64 642 / 12.97 of the applicant is shown in more detail. In the present case, a preload pressure between 8 bar and 12 bar has proven to be favorable.

In das Eingangselement 8 ist weiterhin ein 2-Wege-Druckreduzierventil 70 eingebaut, das mit seinem Druckeingang an dem Zulaufkanal 41 liegt und mit seinem Ausgang, in dem das Ventil einen bestimmten Druck aufrechtzuerhalten sucht, stromauf des Vorspannventils 60 mit dem Ablauffluidpfad 43, also mit dem Ablaufkanal 42 verbunden ist. Das Druckreduzierventil besitzt einen Ventilkolben 71, der im Sinne einer Vergrößerung des Öffnungsquerschnitts des Ventils von einer Druckfeder 72 und im Sinne einer Verkleinerung des Öffnungsquerschnittes vom am Ausgang des Ventils, also vom im Ablaufkanal 42 herrschenden Druck beaufschlagt ist. Der am Druckreduzierventil eingestellte und am Ausgang aufrechtzuerhaltende Druck liegt etwa 2 bar unterhalb des am Vorspannventil 60 eingestellten Vorspanndrucks.A 2-way pressure reducing valve 70 is also installed in the input element 8, which is with its pressure input on the inlet channel 41 and with its Outlet in which the valve tries to maintain a certain pressure, upstream of the preload valve 60 with the drain fluid path 43, that is to say with the drain channel 42 is connected. The pressure reducing valve has a valve piston 71 which in the sense of increasing the opening cross section of the valve from one Compression spring 72 and in the sense of a reduction in the opening cross section from at the outlet of the valve, ie acted upon by the pressure prevailing in the outlet channel 42 is. The one set on the pressure reducing valve and to be maintained at the outlet Pressure is about 2 bar below that set on the preload valve 60 Biasing pressure.

Konstruktive Einzelheiten des Druckreduzierventils 70 gehen näher aus Figur 2 hervor. Danach ist in ein scheibenförmiges Gehäuse 73 des Eingangselements 8 von einer Schmalseite aus eine Sackbohrung 74 eingebracht, die durch eine Verschlußschraube 75 verschlossen ist. Die Sackbohrung 74 ist an zwei Stellen zu axial voneinander beabstandeten Ringkammern 76 und 77 erweitert, von denen die Ringkammer 76 von dem Zulaufkanal 41 durchquert und die Ringkammer 77 mit dem Ablaufkanal 42 verbunden ist. Zwischen dem Boden der Sackbohrung und der Verschlußschraube 75 ist der sich in der Sackbohrung befindliche Ventilkolben 71 axial verschiebbar. Dieser weist einen ersten Kolbenbund 78, einen zweiten Kolbenbund 79 und zwischen den beiden Kolbenbunden einen Kolbenhals 80 auf, so daß zwischen den beiden Kolbenbunden eine Ringnut 81 gebildet ist. Diese befindet sich im Bereich der beiden Ringkammern 76 und 77. An seiner der Ringnut 81 zugekehrten äußeren Kante, die als Steuerkante des Ventilkolbens 71 mit der der Ringkammer 77 nahen inneren Kante der Ringkammer 76 den Öffnungsquerschnitt des Ventils 70 steuert, ist der Kolbenbund 78 mit Feinsteuernuten 82 versehen.Structural details of the pressure reducing valve 70 are shown in more detail in FIG. 2 out. Then is in a disc-shaped housing 73 of the input element 8 a blind bore 74 is introduced from a narrow side, through a screw plug 75 is closed. The blind bore 74 is closed at two points axially spaced apart annular chambers 76 and 77, of which the annular chamber 76 passes through the inlet channel 41 and the annular chamber 77 is connected to the drain channel 42. Between the bottom of the blind hole and the screw plug 75 is the valve piston located in the blind bore 71 axially displaceable. This has a first piston collar 78, one second piston collar 79 and a piston neck between the two piston collars 80 so that an annular groove 81 is formed between the two piston collars is. This is located in the area of the two annular chambers 76 and 77 the annular groove 81 facing outer edge, which acts as the control edge of the valve piston 71 with the inner edge of the annular chamber 76 near the annular chamber 77, the opening cross section controls the valve 70, the piston collar 78 is with fine control grooves 82 provided.

Die der Verschlußschraube 75 nähere Ringkammer 76 der beiden Ringkammern 76 und 77 besitzt einen Abstand vom inneren Ende der Verschlußschraube. In diesem Bereich der Sackbohrung 74 hat der Ventilkolben 71 einen weiteren Kolbenbund 83. Dieser trennt einen Druckraum 85 zwischen der Verschlußschraube 75 und der dieser zugewandten Stirnseite 86 des Ventilkolbens. Der Kolbenbund 83 ist durch eine weitere Eindrehung 84 des Ventilkolbens zwischen ihm und dem Kolbenbund 78 entstanden. Diese Eindrehung hat nichts mit der Steuerfunktion des Ventilkolbens 71 zu tun, sondern trägt nur zu einem großen Strömungsquerschnitt für das Druckmittel im Bereich der Ringkammer 76 bei. Ohne die Eindrehung 84 wäre dann nur ein Kolbenbund zwischen dem Kolbenhals 80 und der Stirnseite 86 des Ventilkolbens 71 vorhanden.The ring chamber 76 of the two ring chambers closer to the screw plug 75 76 and 77 is at a distance from the inner end of the screw plug. In In this area of the blind bore 74, the valve piston 71 has a further piston collar 83. This separates a pressure chamber 85 between the screw plug 75 and the face 86 of the valve piston facing this. The piston collar 83 is through a further turn 84 of the valve piston between it and the Piston collar 78 was created. This twist has nothing to do with the control function of the valve piston 71, but only contributes to a large flow cross section for the pressure medium in the area of the annular chamber 76. Without the twist 84 would then only be a piston collar between the piston neck 80 and the End face 86 of the valve piston 71 is present.

Der Druckraum 85 zwischen dem Ventilkolben 71 und der Verschlußschraube 75 ist über eine Verbohrung des Ventilkolbens, die eine von der Stirnseite 86 axial eingebrachte Sackbohrung 87 und ein durchgehende Querbohrung 88 im Kolbenhals 80 umfaßt, fluidisch mit der Ringnut 81 verbunden.The pressure space 85 between the valve piston 71 and the screw plug 75 is through a bore of the valve piston, one of the end face 86 axially introduced blind bore 87 and a continuous transverse bore 88 in the piston neck 80 comprises, fluidly connected to the annular groove 81.

Von der dem Ringnut 81 abgewandten Seite des Kolbenbundes 79 steht ein Anschlagzapfen 89 ab, der einen kleineren Durchmesser als die Sackbohrung 74 hat und dessen bei an der Verschlußschraube 75 anliegendem Ventilkolben 71 vorhandener lichter Abstand vom Boden der Sackbohrung den möglichen Verschiebeweg des Ventilkolbens verdeutlicht. Der Raum 90 zwischen dem Boden der Sackbohrung 74 und dem Kolbenbund 79 wird durch diesen fluidisch von der Ringkammer 77 getrennt und ist über die auch in den Boden der Sackbohrung mündende Verbohrung 62 mit dem Leckölkanal 51 verbunden. Somit herrscht in dem Raum 90 Tankdruck. Von diesem Raum 90 ist die Druckfeder 72 aufgenommen, die sich am Boden der Sackbohrung 74 und, den Anschlagzapfen übergreifend und als Führung nutzend, an dem Kolbenbund 79 des Ventilkolbens 71 abstützt. Durch Unterlegscheiben 92 kann die Vorspannung der Druckfeder 72 variiert werden.A stop pin is located on the side of the piston collar 79 facing away from the annular groove 81 89 from which has a smaller diameter than the blind bore 74 and the valve piston 71 which is present when the valve piston 71 abuts the screw plug 75 clear distance from the bottom of the blind hole the possible displacement of the valve piston clarified. The space 90 between the floor of the The blind bore 74 and the piston collar 79 is fluidically by this from the Annular chamber 77 is separated and is also in the bottom of the blind hole opening bore 62 connected to the leak oil channel 51. So there is in the room 90 tank pressure. The compression spring 72 is received by this space 90, which is at the bottom of the blind bore 74 and, overlapping the stop pin and is used as a guide, is supported on the piston collar 79 of the valve piston 71. The preload of the compression spring 72 can be varied by means of washers 92 become.

In Figur 2 sind auch aus dem Gehäuse 73 herausragende Teile der Ventile 60 und 65 sowie der Tankanschluß T erkennbar.FIG. 2 also shows parts of the valves 60 and 60 protruding from the housing 73 65 and the tank connection T can be seen.

Bei länger ausgeschalteter Pumpe 18 steht kein Druck im Zulaufkanal 41 an. Ist der Druck im Ablaufkanal 42 kleiner als der am Druckreduzierventil eingestellte Druck, so nimmt dessen Ventilkolben 71 die in Figur 2 gezeigte Position ein. Ist der Druck im Ablaufkanal 42 dagegen höher, so ist der Ventilkolben im Vergleich zu der in Figur 2 gezeigten Position nach links verschoben und trennt die Ringkammer 76 und damit den Zulaufkanal 41 von der Ringkammer 77 und damit vom Ablaufkanal 42.When the pump 18 is switched off for a longer time, there is no pressure in the inlet channel 41. is the pressure in the outlet channel 42 is lower than that set at the pressure reducing valve Pressure, its valve piston 71 assumes the position shown in FIG. 2. is the pressure in the outlet channel 42, however, is higher, so the valve piston is compared moved to the position shown in Figure 2 to the left and separates the annular chamber 76 and thus the inlet channel 41 from the annular chamber 77 and thus from Drain channel 42.

Werden die Differentialzylinder 22 und 23 bei einer Betätigung der Wegeventile 12 oder 13 mit drückender Last im Sinne eines Ausfahrens der Kolbenstange betrieben, liegt der Druck in der im Vorlauf befindlichen Verbraucherleitung 20 über dem in der Ablaufleitung herrschenden Vorspanndruck, so daß die Rückschlagfunktion der Ventile 45 nicht anspricht und der am Ventil 60 eingestellte Vorspanndruck in der Ablaufleitung aufrechterhalten wird. Der Vorspanndruck steht über die Ringkammer 77, den Ringnut 81 und die Bohrungen 87 und 88 im Druckraum 85 an und hält den Ventilkolben in einer im Vergleich zu der in Figur 2 gezeigten Position nach links verschobenen Position, in der der Kolbenbund 78 die Steuerkante der Ringkammer 76 überfahren hat und die Ablaufleitung 42 von der Zulaufleitung 41 getrennt hält. Aufgrund der niedrigeren Druckeinstellung des Druckreduzierventils 70 gegenüber dem Vorspannventil 60 fließt kein Druckmittel von dem Zulaufkanal 41 über das Druckreduzierventil in den Ablaufkanal 42 und von dort über das Vorspannventil 60 zum Tank 19. Ein solcher Druckmittelfluß wäre mit unnötigen Energieverlusten verbunden. The differential cylinders 22 and 23 when the directional control valves 12 are actuated or 13 operated with a pushing load in the sense of extending the piston rod, is the pressure in the consumer line 20 in the flow above pre-tension pressure prevailing in the drain line, so that the non-return function the valve 45 does not respond and the preload pressure set on the valve 60 in the drain line is maintained. The preload pressure is above the ring chamber 77, the annular groove 81 and the bores 87 and 88 in the pressure chamber 85 and holds the valve piston in a position compared to the position shown in FIG to the left shifted position, in which the piston collar 78 the control edge of the Has passed over the annular chamber 76 and the outlet line 42 from the inlet line 41 keeps separate. Due to the lower pressure setting of the pressure reducing valve 70 compared to the preload valve 60, no pressure medium flows from the inlet channel 41 via the pressure reducing valve into the drain channel 42 and from there via the preload valve 60 to tank 19. Such a pressure medium flow would be unnecessary Energy losses connected.

Bei einem Betrieb der Differentialzylinder 22 und 23 mit ziehenden Lasten und im Sinne eines Ausfahrens der Kolbenstange kann es, ob nun das Wegeventil 12 mit dem Steuerkolben 30 oder das Wegeventil 13 mit dem als Regenerationskolben ausgebildeten Steuerkolben 31 betätigt wird, dazu kommen, daß der Druck in der Verbraucherleitung 20 unter den am Vorspannventil 60 eingestellten Vorspanndruck und weiter unter den am Druckreduzierventil 70 eingestellten Druck abfällt. In einem solchen Fall fließt über das oder die entsprechenden als Rückschlagventile fungierenden Ventile 45 Druckmittel aus dem Ablaufkanal 42 in die entsprechende Verbraucherleitung 20. Das Druckreduzierventil 70 macht auf und führt dem Ablaufkanal von der Verstellpumpe zumindest unter dem Stand-by-Druck gefördertes Druckmittel zu, das zusätzlich zum aus den Druckräumen 24 der Differentialzylinder verdrängten Rücköl in die Verbraucherleitungen 20 und die Druckräume 25 gelangt.When operating the differential cylinders 22 and 23 with pulling loads and in In terms of extending the piston rod, it can be determined whether the directional valve 12 is now the control piston 30 or the directional control valve 13 with the as a regeneration piston trained control piston 31 is actuated, come to the fact that the pressure in the Consumer line 20 below the preload pressure set on the preload valve 60 and further drops below the pressure set on the pressure reducing valve 70. In such a case, the corresponding one or more flows as check valves Acting valves 45 pressure medium from the drain channel 42 in the corresponding Consumer line 20. The pressure reducing valve 70 opens and leads the drain channel from the variable displacement pump at least under standby pressure conveyed pressure medium, which in addition to from the pressure chambers 24 of the differential cylinder displaced return oil into the consumer lines 20 and the pressure chambers 25 arrives.

Bei einer Betätigung des Wegeventils 12 gelangt dieses Rücköl über die Ablaufkammer 15 in den Ablaufkanal 42 und von dort je nachdem, welche hydraulischen Verbraucher unter welchen Betriebsbedingungen betrieben werden, über ein Ventil 45 in die eine, die andere oder beide Verbraucherleitungen 20. Bei einer Betätigung des Wegeventils 12 fließt außerdem über die Druckwaage 32 und die Zumeßblende eine durch deren Öffnungsquerschnitt bestimmte Druckmittelmenge aus dem Zulaufkanal 41 zum Druckraum 25 des Differentialzylinders 22.When the directional valve 12 is actuated, this return oil passes through the drain chamber 15 in the drain channel 42 and from there depending on which hydraulic Consumer under which operating conditions are operated, via a valve 45 in one, the other or both consumer lines 20. When actuated the directional control valve 12 also flows through the pressure compensator 32 and the metering orifice a pressure medium quantity determined by its opening cross section from the inlet channel 41 to the pressure chamber 25 of the differential cylinder 22.

Bei einer Betätigung des Wegeventils 13 mit Regenerationskolben kann das Rücköl aus dem Druckraum 24 des Differentialzylinders 23 nur in den Druckraum 25 dieses Zylinders gelangen. Außerdem kann es unter bestimmten Betriebsbedingungen für den Differentialzylinder 23 sein, daß wegen des Regenerationskolbens 31 die dem Wegeventil 13 zugeordnete Druckwaage schließt, so daß der Druckraum 25 des Zylinders 23 nur mit dem Rücköl aus dem Druckraum 24 des Zylinders 23 und aus dem Druckraum 24 des eventuell betätigten Zylinders 22 und mit über das Druckreduzierventil 70 dem Ablaufkanal zufließenden Druckmittel gefüllt wird.When the directional valve 13 is actuated with a regeneration piston, this can be done Return oil from the pressure chamber 24 of the differential cylinder 23 only in the pressure chamber 25 of this cylinder arrive. It can also operate under certain operating conditions for the differential cylinder 23 that because of the regeneration piston 31 closes the pressure compensator assigned to the directional control valve 13, so that the Pressure chamber 25 of the cylinder 23 only with the return oil from the pressure chamber 24 of the Cylinder 23 and from the pressure chamber 24 of the possibly actuated cylinder 22 and with pressure medium flowing to the outlet channel via the pressure reducing valve 70 is filled.

Claims (7)

Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern (22, 23) mit einer bedarfsstromgeregelten (load-sensing-geregelten) Verstellpumpe (18), deren Einstellung in Abhängigkeit vom höchsten Lastdruck der betätigten hydraulischen Verbraucher (22, 23) veränderbar ist, mit einem einen ringförmigen ersten Druckraum (24) und einen kreiszylindrischen zweiten Druckraum (25) aufweisenden Differentialzylinder (22, 23) als hydraulischen Verbraucher, mit einem proportional verstellbaren Wegeventil (12, 13), mit dem die Druckmittelwege zwischen einer von der Verstellpumpe (18) abgehenden Zulaufleitung (40), einer zu einem Tank (19) führenden Ablaufleitung (43) und einer zum ersten Druckraum (24) des Differentialzylinders (22, 23) führenden ersten Verbraucherleitung (20) und einer zum zweiten Druckraum (25) des Differentialzylinders (22, 23) führenden zweiten Verbraucherleitung (21) steuerbar sind, mit einem Vorspannventil (60) zur Erzeugung eines Vorspanndrucks in einem stromauf des Vorspannventils (60) gelegenen Abschnitt (42) der Ablaufleitung (43) und mit einem zwischen dem Abschnitt (42) der Ablaufleitung (43) und der zweiten Verbraucherleitung (21) angeordneten und zu dieser hin öffnenden Rückschlagventil (45), gekennzeichnet durch Ventilmittel (70), über die Druckmittel aus der Zulaufleitung (41) in den besagten Abschnitt (42) der Ablaufleitung (43) einspeisbar ist, wenn in diesem Abschnitt (42) der Druck auf einen unterhalb des Vorspanndrucks liegenden Wert abfällt.Hydraulic control arrangement for supplying pressure medium to preferably several hydraulic consumers (22, 23) with a demand-flow-controlled (load-sensing-regulated) variable displacement pump (18), the setting of which can be changed as a function of the highest load pressure of the actuated hydraulic consumers (22, 23), having a differential cylinder (22, 23) as an hydraulic consumer, having an annular first pressure chamber (24) and a circular cylindrical second pressure chamber (25), with a proportionally adjustable directional valve (12, 13), with which the pressure medium paths between an outgoing line from the variable pump (18) (40), an outlet line (43) leading to a tank (19) and one to the first pressure chamber (24) of the Differential cylinders (22, 23) leading first consumer line (20) and a second consumer line (21) leading to the second pressure chamber (25) of the differential cylinder (22, 23) are controllable, with a preload valve (60) for generating a preload pressure in a section (42) of the discharge line (43) located upstream of the preload valve (60) and with a between the section (42) of the discharge line (43) and the second consumer line (21) and towards this check valve (45), characterized by valve means (70) via which pressure medium from the inlet line (41) can be fed into said section (42) of the outlet line (43) if the pressure in this section (42) drops to a value below the pre-tensioning pressure. Hydraulische Steueranordnung nach Anspruch 1, dadurch gekennzeichnet, daß die Ventilmittel durch ein zusätzlich zum Vorspannventil (60) vorhandenes 2-Wege-Einspeiseventil (70) gebildet sind.Hydraulic control arrangement according to claim 1, characterized in that the valve means are formed by a 2-way feed valve (70) in addition to the preload valve (60). Hydraulische Steueranordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Ventilmittel ein Druckreduzierventil (70) mit einem Ventilkolben (71) umfassen, der im Sinne eines Schließens der fluidischen Verbindung zwischen der Zulaufleitung (40) und dem Abschnitt (42) der Ablaufleitung (43) vom Druck in diesem Abschnitt (42) und im Sinne eines Öffnens der fluidischen Verbindung von einer Feder (72) beaufschlagt ist.Hydraulic control arrangement according to Claim 1 or 2, characterized in that the valve means comprise a pressure reducing valve (70) with a valve piston (71) which, in the sense of closing the fluidic connection between the inlet line (40) and the section (42) of the outlet line ( 43) is acted upon by the pressure in this section (42) and in the sense of opening the fluidic connection by a spring (72). Hydraulische Steueranordnung nach den Ansprüchen 2 und 3, dadurch gekennzeichnet, daß das Einspeiseventil ein 2-Wege-Druckreduzierventil (70) ist, das auf einen Druck eingestellt ist, der kleiner als der Vorspanndruck ist.Hydraulic control arrangement according to claims 2 and 3, characterized in that the feed valve is a 2-way pressure reducing valve (70) which is set to a pressure which is lower than the preload pressure. Hydraulische Steueranordnung nach Anspruch 4, dadurch gekennzeichnet, daß das 2-Wege-Druckreduziervenil (70) auf einen Druck eingestellt ist, der etwa 2 bar unterhalb des Vorspanndrucks liegt.Hydraulic control arrangement according to claim 4, characterized in that the 2-way pressure reducing valve (70) is set to a pressure which is approximately 2 bar below the prestressing pressure. Hydraulische Steueranordnung nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß der Ventilkolben (71) des 2-Wege-Druckreduzierventils (70) zwei axial voneinander beabstandete Kolbenbunde (78, 79) aufweist, zwischen denen sich ein Kolbenhals (80) befindet, daß die der Ringnut (81) um den Kolbenhals (80) zugekehrte Kante des ersten Kolbenbundes (78) eine Steuerkante bildet, die mit einer Steuerkante eines Gehäuses (73) zusammenwirkt, die an einem mit der Zulaufleitung (40) verbunden Ringraum (76) des Gehäuses (73) umläuft, daß durch den Ventilkolben (71) vom Kolbenhals (80) bis zu der, vom zweiten Kolbenbund (79) aus gesehen, jenseits des ersten Kolbenbunds (78) befindlichen Stirnseite (86) des Ventilkolbens (71) ein Fluidpfad führt, und daß sich am zweiten Kolbenbund (79) auf der dem Kolbenhals (80) abgewandten Seite eine Druckfeder (72) abstützt, in die ein vom zweiten Kolbenbund (79) abstehender Anschlagzapfen (89) hineinragt.Hydraulic control arrangement according to claim 4 or 5, characterized in that the valve piston (71) of the 2-way pressure reducing valve (70) has two axially spaced piston collars (78, 79), between which there is a piston neck (80) that the the annular groove (81) around the piston neck (80) facing edge of the first piston collar (78) forms a control edge which interacts with a control edge of a housing (73) which is connected to an annular space (76) of the housing connected to the inlet line (40) (73) rotates that a fluid path leads through the valve piston (71) from the piston neck (80) to the end face (86) of the valve piston (71) located beyond the first piston collar (78), seen from the second piston collar (79) , and that a compression spring (72) is supported on the second piston collar (79) on the side facing away from the piston neck (80), into which a stop pin (89) protruding from the second piston collar (79) projects. Hydraulische Steueranordnung nach einem vorhergehenden Anspruch, dadurch gekennzeichnet, daß dem Wegeventil (12, 13) eine Zulaufdruckwaage (32) zugeordnet ist.Hydraulic control arrangement according to one of the preceding claims, characterized in that an inlet pressure compensator (32) is assigned to the directional control valve (12, 13).
EP01110563A 2000-07-08 2001-04-30 Hydraulic control arrangement for supplying pressurised fluid preferably to several hydraulic loads Expired - Lifetime EP1170510B1 (en)

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DE10033372 2000-07-08
DE10033372 2000-07-08
DE10035575 2000-07-21
DE10035575A DE10035575A1 (en) 2000-07-08 2000-07-21 Hydraulic control arrangement for supplying pressure medium to preferably several hydraulic consumers

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US8671824B2 (en) 2007-06-26 2014-03-18 Robert Bosch Gmbh Hydraulic control system
CN104564866A (en) * 2013-10-15 2015-04-29 罗伯特·博世有限公司 Valve Block having a Valve Assembly
US11841716B2 (en) 2020-12-28 2023-12-12 Danfoss Power Solutions (Zhejiang) Co. Ltd. Load-sensing multi-way valve work section

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ATE302345T1 (en) 2005-09-15
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ES2244517T3 (en) 2005-12-16

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