EP1170510B1 - 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
EP1170510B1
EP1170510B1 EP01110563A EP01110563A EP1170510B1 EP 1170510 B1 EP1170510 B1 EP 1170510B1 EP 01110563 A EP01110563 A EP 01110563A EP 01110563 A EP01110563 A EP 01110563A EP 1170510 B1 EP1170510 B1 EP 1170510B1
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EP
European Patent Office
Prior art keywords
pressure
valve
piston
line
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP01110563A
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German (de)
French (fr)
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EP1170510A3 (en
EP1170510A2 (en
Inventor
Peter BÜTTNER
Tatu Miikkulainen
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Bosch Rexroth AG
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Bosch Rexroth AG
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Priority claimed from DE10035575A external-priority patent/DE10035575A1/en
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1170510A2 publication Critical patent/EP1170510A2/en
Publication of EP1170510A3 publication Critical patent/EP1170510A3/en
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Publication of EP1170510B1 publication Critical patent/EP1170510B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/047—Preventing foaming, churning or cavitation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/51—Pressure control characterised by the positions of the valve element
    • F15B2211/513—Pressure control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—Methods of control of the load sensing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the invention relates to a hydraulic control arrangement, preferably with the several hydraulic consumers are supplied with pressure medium and the the Features from the preamble of claim 1.
  • a hydraulic control arrangement is such after the load-sensing Principle, in which a variable displacement pump depending on the highest load pressure of the actuated hydraulic consumers are each set so that the pump pressure by a certain, preferably in the range between 10 bar and 25 bar lying pressure difference .DELTA.p is above the highest load pressure.
  • the hydraulic Consumers the pressure medium flows through adjustable, usually by Control grooves realized on the control piston of the directional control valves realized metering, between an outgoing from the variable displacement supply line and the hydraulic Consumers are arranged.
  • variable displacement pump delivered pressure medium quantity independent of the load pressures of the hydraulic Consumers over the Zumeßblenden a certain, compared to ⁇ p smaller Pressure difference is such that the inflowing a hydraulic consumer Quantity of pressure medium only from the opening cross section of the respective Zumeßblende depends. If a Zumeßblende further opened, so must more pressure medium flow over them to produce the specific pressure difference.
  • the variable pump is in each case adjusted so that it supplies the required amount of pressure medium. you Therefore speaks also of a demand flow control.
  • the pressure compensators are in the opening direction of the pressure according to the respective Metering and in the closing direction of a in a rear control room applied control pressure, which is usually the highest Load pressure of all hydraulic consumers supplied by the same hydraulic pump equivalent.
  • control pressure which is usually the highest Load pressure of all hydraulic consumers supplied by the same hydraulic pump equivalent.
  • LHDV control Because with a LUDV control also the highest load pressure sensed and by the hydraulic pump by the variation of the conveyed pressure medium quantity one by a certain pressure difference Ap over the highest load pressure LHDV control is a special case one load-sensing or load-sensing control (LS control).
  • each pressure medium via a Zumeßbleride with upstream individual pressure compensator flows, in the closing direction only from the pressure in front of the metering aperture and in the opening direction only from Load pressure of the respective hydraulic consumer and of a compression spring is applied, you get no load-independent flow distribution.
  • Such a control is e.g. known from DE 197 14 141 A1.
  • several hydraulic consumers and not enough of the variable displacement pump supplied quantity of pressure medium is here only the last horrinen hydraulic Consumers inflowing pressure fluid reduced.
  • a LUDV control arrangement having the features of the preamble of the claim 1 is known from the data sheet RD 64 284 / 05.99 of the applicant.
  • a so-called bias valve is arranged in the drain line, through the in the section of the drain line upstream of the biasing valve is to be maintained, a bias pressure in the range of 10 bar can lie.
  • a check valve is arranged to the consumer line opens.
  • the check valve can also be equipped with a pressure relief valve be summarized.
  • the differential cylinder By the provision of the biasing valve and the check valve is achieved that at a negative load acting on the differential cylinder, ie a load, the differential cylinder generates a force in the by the position of the Directional valve predetermined direction of movement of the differential cylinder directed is the pressure medium displaced from the first pressure chamber in addition to that of funded the pump and the metering diaphragm of the directional control valve and optionally an individual pressure compensator flowing pressure medium the second pressure chamber the differential cylinder is supplied.
  • a negative load acting on the differential cylinder ie a load
  • the differential cylinder generates a force in the by the position of the Directional valve predetermined direction of movement of the differential cylinder directed is the pressure medium displaced from the first pressure chamber in addition to that of funded the pump and the metering diaphragm of the directional control valve and optionally an individual pressure compensator flowing pressure medium the second pressure chamber the differential cylinder is supplied.
  • the invention is therefore based on the object, a hydraulic control arrangement, having the features of the preamble of claim 1, develop so that the risk of cavitation is further reduced.
  • valve means are present, on the pressure medium the supply line, so promoted by the variable pressure fluid, in the section the drain line in which a bias pressure is to be maintained can be fed, if in the section the pressure on one below the prestressing pressure lying value decreases.
  • Control arrangement thus reaches out of the first pressure chamber of the differential cylinder displaced pressure fluid not only one funded by the variable displacement pump additional amount of pressure medium through the opening cross section of the Zumeßblende and the presence of a pressure compensator or Lack of reporting a load pressure to the variable pump in any case low Pressure difference over the Zumeßblende is determined to the second pressure chamber.
  • valve means between the supply line and the drain line and the check valve the second pressure chamber of the differential cylinder to.
  • the opening cross-section the valve means and the check valve can be made very large become.
  • full pump pressure is available without throttling by an individual pressure compensator as drive for the pressure medium flow available.
  • valve means according to claim 2 by an additional formed to the preload valve existing 2-way feed valve.
  • valve means comprise a pressure reducing valve with a valve piston which in Meaning a closing of the fluidic connection between the supply line and the section of the drain line from the pressure in this section and in the sense opening of the fluidic connection is acted upon by a spring.
  • the biasing valve and between the supply line and the drain line arranged valve means to a specific one Bias pressure adjusted 3-way pressure control valve summarize at whose control output the section of the drain line to be prestressed, at the pressure connection, the supply line and at the tank connection of the Tank leading section of the drain line is connected. It is, however, one better matching to different flow rates and use a proven in practice biasing valve possible if, as in claim 2, a separate feed valve is used, the is then designed according to claim 4 as a 2-way pressure reducing valve. This is set to a pressure that is less than the bias pressure.
  • a control block 7 is included an input member 8, an end plate 9, and between them two-way valve sections 10 and 11, each of which has a directional control valve 12 or 13 with an inlet chamber 14, which can flow from a hydraulic pump 18 promoted pressure medium, a Drain chamber 15, can run from the pressure medium to a tank 19, and two Consumer combs 16 and 17, which via consumer lines 20, 21st with a double-acting hydraulic consumer, namely with a differential cylinder 22 and 23 are connected.
  • These have a rod-side, annular, first pressure chamber 24, from which a consumer line 21 to a Consumer chamber 17 leads, and a rod-side, circular cylindrical, second pressure chamber 25, from which a consumer line 20 to a consumer chamber 16 leads.
  • the directional control valve 12 has a control piston 30 and the directional control valve 13 has a control piston 31.
  • Both control pistons 30 and 31 are from a central position in which the Inlet chamber, the drain chamber and the two consumer chambers against each other are shut off, in opposite directions in working positions adjustable, in between the inlet chamber 14 and the consumer chamber sixteenth or the consumer chamber 17 a non-illustrated, in its opening cross-section on the size of the displacement of the control piston from its center position dependent metering orifice is open.
  • With an adjustment of the control piston in one direction is the consumer chamber at both Wegeventilsetationen 16 via a likewise dependent on the displacement of the control piston Opening cross-section connected to the discharge chamber 15.
  • each directional control valve 12 and 13 is connected upstream in each case an individual pressure compensator 32, at the control piston two control chambers 33 and 34th adjoin.
  • the control chamber 33 is connected to a load reporting chamber 35 of the respective Directional valve 12, 13 and the control chamber 34 connected to the inlet chamber 14.
  • the load reporting chamber 35 is in the middle position of the control piston 30, 31 for Tank relieved and in a lateral working position in each case with the consumer chamber connected, which is supplied via the metering orifice oil.
  • the control piston the pressure compensator 32 is in the opening direction of a compression spring 36 and of the prevailing in the control chamber 33 pressure and in the closing direction of the im Control chamber 34 applied pressure prevailing.
  • variable displacement pump 18 each set so that in one of the variable displacement 18 outgoing Section of a supply line 40, via the inlet chambers 14 of the Directional valves 12 and 13 hydraulic oil can be fed, a pump pressure setting, the by a certain pressure difference ⁇ p over the reported highest load pressure lies.
  • the pressure difference is usually in the range between 10 bar and 25 bar. In the present case may be set a pressure difference of 20 bar. Will not Load pressure reported, accordingly, in the supply line 40 including the Inlet channel 41 a pressure (stand-by pressure) ⁇ p of 20 bar a.
  • the supply line 40 is composed of an input P of the input element 8 within the control block 7 as a straight inlet channel 41 continues through the directional valve sections 10 and 11 passes through into the end plate 9. With him are the Inputs of the individual pressure compensators 32 connected.
  • valve section in particular also in the directional valve section 11 with the directional control valve 13, the control piston is a so-called regeneration flask, there is a combined Pressure limiting and feed valve 45, which is between the consumer line 20 and the drainage channel 42 is arranged.
  • the pressure limiting function is fulfilled the valve 45 for the consumer line 20, in which it puts pressure on one to a limited certain pressure difference above the pressure in the discharge channel value.
  • valve 45 acts like a non-return valve opening towards the consumer line, So lets pressure medium flow from the flow channel to the consumer line, if the Pressure in the consumer line is lower than in the drain channel, and locks when the pressure in the consumer line is higher than in the discharge channel.
  • Further pressure limiting and feed valves 46 are located between each consumer line 21 and the drainage channel 42.
  • the two-way valves 12 and 13 are each electro-hydraulically actuated, including in each directional valve section 10 and 11 two electromagnetically proportional adjustable Pilot valves 50 are integrated.
  • a valve 50 In the rest position of a valve 50 is an associated control chamber on the control piston 30 of a directional control valve 12, 13 to a leakage oil passage 51 passing through the directional valve sections 10 and 11, relieved.
  • By energizing an electromagnet is a control room with a likewise passed through the directional valve section 10 and 11 control pressure line 52 connected.
  • the control oil is via a pressure reducing valve 53, the is installed in the end plate 9, the through the two-way valve sections 10th and 11 passed through and guided into the end plate 9 inlet channel 41.
  • the pressure reducing valve 53 is e.g. adjusted to a control pressure of 30 bar.
  • the leakage oil passage 51 is connected to a terminal Y of the end plate 9 via a Line 54 connected directly to the tank 19 such that in the Leakage oil channel the same pressure
  • a pressure relief valve 60 is installed, to whose Entrance of the drain passage 42 leads and its output to the tank port T of the input element is connected. Since the pressure relief valve on a large flow rate must be designed, it is preferably a pilot-operated Valve.
  • the pressure relief valve 60 has the function in the flow channel lying upstream of him a constant after setting To maintain pressure, which is also referred to as biasing pressure. Therefore, you can call the pressure relief valve as a preload valve.
  • the preload pressure is relatively small and is in other applications in the Range from 5 bar to 10 bar, but can also be set to 15 bar.
  • the valve can be used under the name MHDBV in the data sheet RD 64 642 / 12.97 the applicant is shown in more detail. In the present case, a preload pressure between 8 bar and 12 bar has proved to be favorable.
  • a 2-way pressure reducing valve 70 is further installed, which lies with its pressure input to the inlet channel 41 and with his Output in which the valve seeks to maintain a certain pressure, upstream of the biasing valve 60 with the drain fluid path 43, so with the drain passage 42 is connected.
  • the pressure reducing valve has a valve piston 71, the in the sense of increasing the opening cross-section of the valve of a Compression spring 72 and in the sense of a reduction of the opening cross-section of at the outlet of the valve, so acted upon by the pressure prevailing in the flow passage 42 is.
  • the set at the pressure reducing valve and maintained at the output Pressure is about 2 bar below that set at the biasing valve 60 Biasing pressure.
  • the opening cross-section of the valve 70 is the piston collar 78 with fine control grooves 82 provided.
  • the closure screw 75 closer annular chamber 76 of the two annular chambers 76 and 77 has a distance from the inner end of the screw plug.
  • This area of the blind bore 74 of the valve piston 71 has another piston collar 83.
  • the piston collar 83 is by another recess 84 of the valve piston between him and the Piston collar 78 emerged.
  • This recess has nothing to do with the control function to do the valve piston 71, but only contributes to a large flow area for the pressure medium in the region of the annular chamber 76 at. Without the recess 84 would then only a piston collar between the piston neck 80 and the End face 86 of the valve piston 71 is present.
  • the pressure chamber 85 between the valve piston 71 and the screw plug 75th is via a bore of the valve piston, one of the end face 86 axially introduced blind bore 87 and a continuous transverse bore 88 in the piston neck 80, fluidly connected to the annular groove 81.
  • a stop pin 89 From the annular groove 81 opposite side of the piston collar 79 is a stop pin 89, which has a smaller diameter than the blind bore 74 and whose present at the closure screw 75 valve piston 71 existing clear distance from the bottom of the blind hole the possible displacement the valve piston illustrates.
  • the compression spring 72 is added, at the bottom of the blind bore 74 and, the stop pin across and as a guide, on the piston collar 79 of the valve piston 71 is supported.
  • washers 92 By washers 92, the bias of the compression spring 72 can be varied become.
  • the differential cylinders 22 and 23 in an actuation of the directional control valves 12th or 13 operated with pressing load in the sense of extension of the piston rod is the pressure in the flow in the consumer line 20 above the prevailing in the discharge line biasing pressure, so that the check function the valves 45 is not responsive and the valve 60 set biasing pressure in the drain is maintained.
  • the preload pressure is above the annular chamber 77, the annular groove 81 and the holes 87 and 88 in the pressure chamber 85 at and holds the valve piston in a position compared to that shown in Figure 2 shifted to the left position, in which the piston collar 78, the control edge of the Has overtravelled ring chamber 76 and the drain line 42 from the feed line 41st keeps separate.
  • the directional control valve 12 with the control piston 30 or the directional control valve 13 with the as a regeneration piston trained control piston 31 is actuated come to the fact that the pressure in the Load line 20 under the bias pressure set on the biasing valve 60 and further drops below the pressure set at the pressure reducing valve 70. In such a case, it flows over the or the corresponding as check valves acting valves 45 pressure fluid from the drain passage 42 into the corresponding Consumer line 20.
  • the pressure reducing valve 70 opens and leads the drainage channel of the variable displacement pump at least under the stand-by pressure promoted pressure fluid, in addition to from the pressure chambers 24 of the differential cylinder displaced return oil into the consumer lines 20 and the pressure chambers 25 arrives.
  • this return oil passes through the drainage chamber 15 in the drainage channel 42 and from there depending on which hydraulic Consumers are operated under which operating conditions, via a valve 45 in one, the other or both consumer lines 20.
  • the directional control valve 12 also flows through the pressure compensator 32 and the metering orifice a through the opening cross section certain amount of pressure medium from the inlet channel 41 to the pressure chamber 25 of the differential cylinder 22nd
  • the directional control valve 13 Upon actuation of the directional control valve 13 with regeneration piston can Return oil from the pressure chamber 24 of the differential cylinder 23 only in the pressure chamber 25 get this cylinder. Also, it can work under certain operating conditions be for the differential cylinder 23 that because of the regeneration piston 31, the directional control valve 13 associated pressure compensator closes, so that the Pressure chamber 25 of the cylinder 23 only with the return oil from the pressure chamber 24 of the Cylinder 23 and from the pressure chamber 24 of the possibly actuated cylinder 22 and with via the pressure reducing valve 70 the flow channel flowing pressure medium is filled.

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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, preferably with the several hydraulic consumers are supplied with pressure medium and the 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 such after the load-sensing Principle, in which a variable displacement pump depending on the highest load pressure of the actuated hydraulic consumers are each set so that the pump pressure by a certain, preferably in the range between 10 bar and 25 bar lying pressure difference .DELTA.p is above the highest load pressure. The hydraulic Consumers, the pressure medium flows through adjustable, usually by Control grooves realized on the control piston of the directional control valves realized metering, between an outgoing from the variable displacement supply line and the hydraulic Consumers are arranged. By the directional valves assigned Individual pressure compensators is achieved that sufficient by the variable displacement pump delivered pressure medium quantity independent of the load pressures of the hydraulic Consumers over the Zumeßblenden a certain, compared to Δp smaller Pressure difference is such that the inflowing a hydraulic consumer Quantity of pressure medium only from the opening cross section of the respective Zumeßblende depends. If a Zumeßblende further opened, so must more pressure medium flow over them to produce the specific pressure difference. The variable pump is in each case adjusted so that it supplies the required amount of pressure medium. you Therefore speaks also of a demand flow control.

Aus der EP 0 566 449 A1 ist eine lastfühlende hydraulische Steueranordnung bekannt, bei der die Individualdruckwaagen den Zumeßblenden nachgeschaltet sind. From EP 0 566 449 A1 a load-sensing hydraulic control arrangement is known, 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 of the pressure according to the respective Metering and in the closing direction of a in a rear control room applied control pressure, which is usually the highest Load pressure of all hydraulic consumers supplied by the same hydraulic pump equivalent. When simultaneous operation of several hydraulic consumers the metering orifices are opened so far that the from the to the Stop adjusted hydraulic pump delivered pressure medium quantity is smaller than that total required pressure medium quantity, which are the individual hydraulic Consumers flowing pressure fluid quantities regardless of the respective Load pressure of the hydraulic consumer proportionally reduced. One speaks Therefore, from a controller with load-independent flow distribution (LUDV control). Such controlled hydraulic consumers are short LUDV consumers called. Because with a LUDV control also the highest load pressure sensed and by the hydraulic pump by the variation of the conveyed pressure medium quantity one by a certain pressure difference Ap over the highest load pressure LHDV control is a special case one load-sensing or load-sensing control (LS control).

Für mehrere hydraulische Verbraucher, denen Druckmittel jeweils über eine Zumeßbleride 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 pressure medium via a Zumeßbleride with upstream individual pressure compensator flows, in the closing direction only from the pressure in front of the metering aperture and in the opening direction only from Load pressure of the respective hydraulic consumer and of a compression spring is applied, you get no load-independent flow distribution. One has a mere LS control and a LS consumer. Such a control is e.g. known from DE 197 14 141 A1. In a simultaneous operation several hydraulic consumers and not enough of the variable displacement pump supplied quantity of pressure medium is here only the lastdruckhöchsten hydraulic Consumers inflowing pressure fluid 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. A LUDV control arrangement having the features of the preamble of the claim 1 is known from the data sheet RD 64 284 / 05.99 of the applicant.

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 bias valve is arranged in the drain line, through the in the section of the drain line upstream of the biasing valve is to be maintained, a bias pressure in the range of 10 bar can lie. Between the said section of the drainage line and the consumer line, with the larger second pressure chamber of the differential cylinder is connected, a check valve is arranged 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.By the provision of the biasing valve and the check valve is achieved that at a negative load acting on the differential cylinder, ie a load, the differential cylinder generates a force in the by the position of the Directional valve predetermined direction of movement of the differential cylinder directed is the pressure medium displaced from the first pressure chamber in addition to that of funded the pump and the metering diaphragm of the directional control valve and optionally an individual pressure compensator flowing pressure medium the second pressure chamber the differential cylinder is supplied. In this way, intended for the components harmful and difficult control of the cavitation in the second pressure chamber of Differential cylinder can be avoided. However, it has been shown that in the known control arrangement under special circumstances, for. B for piston rods with a particularly large diameter in relation to the diameter of the Piston or cavitation may occur at 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 object, a hydraulic control arrangement, having the features of the preamble of claim 1, develop 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 inventively achieved in that in a generic hydraulic control arrangement according to the characterizing Part of claim 1 valve means are present, on the pressure medium the supply line, so promoted by the variable pressure fluid, in the section the drain line in which a bias pressure is to be maintained can be fed, if in the section the pressure on one below the prestressing pressure lying value decreases. In a hydraulic according to the invention Control arrangement thus reaches out of the first pressure chamber of the differential cylinder displaced pressure fluid not only one funded by the variable displacement pump additional amount of pressure medium through the opening cross section of the Zumeßblende and the presence of a pressure compensator or Lack of reporting a load pressure to the variable pump in any case low Pressure difference over the Zumeßblende is determined to the second pressure chamber. Rather, more of the variable displacement pumped pressure fluid flows through the Valve means between the supply line and the drain line and the check valve the second pressure chamber of the differential cylinder to. The opening cross-section the valve means and the check valve can be made very large become. In addition, the full pump pressure is available without throttling by an individual pressure compensator as drive for the pressure medium flow available.

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

Auf einfache Weise sind die Ventilmittel gemäß Patentanspruch 2 durch ein zusätzlich zum Vorspannventil vorhandenes 2-Wege-Einspeiseventil gebildet.In a simple way, the valve means according to claim 2 by an additional formed to the preload valve existing 2-way feed 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. Particularly preferred is an embodiment according to claim 3, which the valve means comprise a pressure reducing valve with a valve piston which in Meaning a closing of the fluidic connection between the supply line and the section of the drain line from the pressure in this section and in the sense opening of the fluidic connection is acted upon by a spring. Of the Effort for the actuation of the valve means in dependence on the in the drain line The pressure prevailing upstream of the biasing valve is then particularly high 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 that the biasing valve and between the supply line and the drain line arranged valve means to a specific one Bias pressure adjusted 3-way pressure control valve summarize at whose control output the section of the drain line to be prestressed, at the pressure connection, the supply line and at the tank connection of the Tank leading section of the drain line is connected. It is, however, one better matching to different flow rates and use a proven in practice biasing valve possible if, as in claim 2, a separate feed valve is used, the is then designed according to claim 4 as a 2-way pressure reducing valve. This is set to a pressure that is less than the bias pressure. Consequently is ensured that not in normal operation pressure medium from the supply line via the pressure reducing valve in the drain line and from there via the preload valve flows to the tank. This would involve unnecessary energy losses. A adequate security against such losses appears guaranteed when the pressure reducing valve is set to a pressure according to claim 5 is about 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.From the data sheet RD 64 282 / 10.99 the applicant are directional control valves LS control blocks known in which two parallel Holes of the disc of the control piston of the directional control valve, with which the direction of movement and the speed of a hydraulic consumer are controllable, and housed the control piston of an individual pressure compensator are. This control piston has a certain outer diameter, is in certain Way with piston collars, a piston neck and a stop pin and with one of the outer surface of the piston neck through it to a its end faces leading fluid path and is provided by a stop pin pressurized surrounding spring, whose pressure equivalent at the given outer diameter of the control piston is about 10 bar. Advantageously, now according to claim 6 for the 2-way pressure reducing valve used an assembly of piston and spring, the in proven in practice and by their interpretation in terms of flow rate and Spring force suitable assembly corresponds.

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 structural design of a usable in the control arrangement 2-way pressure reducing valve are shown in the drawings. Based of these drawings, the invention will now be explained in more detail.

Es zeigen

  • Figur 1 das Ausführungsbeispiel der hydraulischen Steueranordnung und
  • Figur 2 eine Ventilscheibe teilweise im Schnitt durch das in sie eingebaute 2-Wege-Druckreduzierventil.
    • Show it
  • Figure 1 shows the embodiment of the hydraulic control arrangement and
  • Figure 2 is 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 Verbraucherkammem 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 is included an input member 8, an end plate 9, and between them two-way valve sections 10 and 11, each of which has a directional control valve 12 or 13 with an inlet chamber 14, which can flow from a hydraulic pump 18 promoted pressure medium, a Drain chamber 15, can run from the pressure medium to a tank 19, and two Consumer combs 16 and 17, which via consumer lines 20, 21st with a double-acting hydraulic consumer, namely with a differential cylinder 22 and 23 are connected. These have a rod-side, annular, first pressure chamber 24, from which a consumer line 21 to a Consumer chamber 17 leads, and a rod-side, circular cylindrical, second pressure chamber 25, from which a consumer line 20 to a consumer chamber 16 leads.

    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 drain chamber and the two consumer chambers against each other are shut off, in opposite directions in working positions adjustable, in between the inlet chamber 14 and the consumer chamber sixteenth or the consumer chamber 17 a non-illustrated, in its opening cross-section on the size of the displacement of the control piston from its center position dependent metering orifice is open. With an adjustment of the control piston in one direction is the consumer chamber at both Wegeventilsektionen 16 via a likewise dependent on the displacement of the control piston Opening cross-section connected to the discharge chamber 15. In an adjustment of the control piston 30 of the directional control valve 12 in the opposite direction is the consumer chamber 17 via a displacement of the control piston 30 dependent opening cross-section connected to the discharge chamber 15. Of the Control piston 31 of the directional control valve 13, however, is a so-called regeneration piston, about the case of a shift in the opposite direction the Consumer chamber 17 via a drain plate and the metering with the Consumer chamber 16 is connected. When extending the piston rod of the Differential cylinder 23 from the pressure chamber 24 displaced oil thus passes not to the discharge 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 23rd

    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 in each case an individual pressure compensator 32, at the control piston two control chambers 33 and 34th adjoin. The control chamber 33 is connected to a load reporting chamber 35 of the respective Directional valve 12, 13 and the control chamber 34 connected to the inlet chamber 14. The load reporting chamber 35 is in the middle position of the control piston 30, 31 for Tank relieved and in a lateral working position in each case with the consumer chamber connected, which is supplied via the metering orifice oil. The control piston the pressure compensator 32 is in the opening direction of a compression spring 36 and of the prevailing in the control chamber 33 pressure and in the closing direction of the im Control chamber 34 applied pressure prevailing.

    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.About a shuttle valve chain with shuttle valves 37 is the highest in a control chamber 33 pending pressure, so the highest load pressure, to an output LS in the input element 8 of the control block 7 and over a Lastmeldeleitung 38 to a LS pump controller 39 reported that the variable displacement pump 18 each set so that in one of the variable displacement 18 outgoing Section of a supply line 40, via the inlet chambers 14 of the Directional valves 12 and 13 hydraulic oil can be fed, a pump pressure setting, the by a certain pressure difference Δp over the reported highest load pressure lies. The pressure difference is usually in the range between 10 bar and 25 bar. In the present case may be set a pressure difference of 20 bar. Will not Load pressure reported, accordingly, in the supply line 40 including the Inlet channel 41 a pressure (stand-by pressure) Δp of 20 bar a.

    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 supply line 40 is composed of an input P of the input element 8 within the control block 7 as a straight inlet channel 41 continues through the directional valve sections 10 and 11 passes through into the end plate 9. With him are the Inputs of the individual pressure compensators 32 connected.

    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.Through the directional control valve sections also passes through a drain passage 42, the in the end plate 9 and extends into the input member 8 and part of a drain flow path 43 is, via the hydraulic oil from the drain chambers 15 of the Directional valves 12 and 13 can flow back to the tank 19 and in which also a Tank connection T of the input element 8 is located. In every way valve section, in particular also in the directional valve section 11 with the directional control valve 13, the control piston is a so-called regeneration flask, there is a combined Pressure limiting and feed valve 45, which is between the consumer line 20 and the drainage channel 42 is arranged. The pressure limiting function is fulfilled the valve 45 for the consumer line 20, in which it puts pressure on one to a limited certain pressure difference above the pressure in the discharge channel value. As long as the pressure in the consumer line 20 does not reach this value, the valve 45 acts like a non-return valve opening towards the consumer line, So lets pressure medium flow from the flow channel to the consumer line, if the Pressure in the consumer line is lower than in the drain channel, and locks when the pressure in the consumer line is higher than in the discharge channel. Further pressure limiting and feed valves 46 are located between each consumer line 21 and the drainage channel 42.

    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 12, 13 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-way valves 12 and 13 are each electro-hydraulically actuated, including in each directional valve section 10 and 11 two electromagnetically proportional adjustable Pilot valves 50 are integrated. In the rest position of a valve 50 is an associated control chamber on the control piston 30 of a directional control valve 12, 13 to a leakage oil passage 51 passing through the directional valve sections 10 and 11, relieved. By energizing an electromagnet is a control room with a likewise passed through the directional valve section 10 and 11 control pressure line 52 connected. The control oil is via a pressure reducing valve 53, the is installed in the end plate 9, the through the two-way valve sections 10th and 11 passed through and guided into the end plate 9 inlet channel 41. The pressure reducing valve 53 is e.g. adjusted to a control pressure of 30 bar. The leakage oil passage 51 is connected to a terminal Y of the end plate 9 via a Line 54 connected directly to the tank 19 such that in the Leakage oil channel the same pressure as in the tank 19 prevails.

    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 das 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 member 8, a pressure relief valve 60 is installed, to whose Entrance of the drain passage 42 leads and its output to the tank port T of the input element is connected. Since the pressure relief valve on a large flow rate must be designed, it is preferably a pilot-operated Valve. The spring chamber in which the counterforce to the pressure generating Compression spring 61 is located above a bore 62 of the input member connected to the leak oil passage 51, thus constant tank pressure level is ensured in the spring chamber. The pressure relief valve 60 has the function in the flow channel lying upstream of him a constant after setting To maintain pressure, which is also referred to as biasing pressure. Therefore, you can call the pressure relief valve as a preload valve. The preload pressure is relatively small and is in other applications in the Range from 5 bar to 10 bar, but can also be set to 15 bar. As a preload valve For example, the valve can be used under the name MHDBV in the data sheet RD 64 642 / 12.97 the applicant is shown in more detail. In the present case, a preload pressure between 8 bar and 12 bar has proved to be favorable.

    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.In the input element 8, a 2-way pressure reducing valve 70 is further installed, which lies with its pressure input to the inlet channel 41 and with his Output in which the valve seeks to maintain a certain pressure, upstream of the biasing valve 60 with the drain fluid path 43, so with the drain passage 42 is connected. The pressure reducing valve has a valve piston 71, the in the sense of increasing the opening cross-section of the valve of a Compression spring 72 and in the sense of a reduction of the opening cross-section of at the outlet of the valve, so acted upon by the pressure prevailing in the flow passage 42 is. The set at the pressure reducing valve and maintained at the output Pressure is about 2 bar below that set at the biasing valve 60 Biasing pressure.

    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.Constructive details of the pressure reducing valve 70 are closer to FIG. 2 out. Thereafter, in a disc-shaped housing 73 of the input member. 8 from a narrow side of a blind bore 74 introduced by a screw plug 75 is closed. The blind bore 74 is in two places axially spaced apart annular chambers 76 and 77 extends, of which the annular chamber 76 passes from the inlet channel 41 and the annular chamber 77th is connected to the drainage channel 42. Between the bottom of the blind hole and the closure screw 75 is located in the blind bore valve piston 71 axially displaceable. This has a first piston collar 78, a second piston collar 79 and between the two piston collars a piston neck 80, so that formed between the two piston collars an annular groove 81 is. This is located in the area of the two annular chambers 76 and 77. At his the annular groove 81 facing outer edge, as the control edge of the valve piston 71 with the annular chamber 77 near inner edge of the annular chamber 76, the opening cross-section of the valve 70 is the piston collar 78 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 closure screw 75 closer annular chamber 76 of the two annular chambers 76 and 77 has a distance from the inner end of the screw plug. In This area of the blind bore 74 of the valve piston 71 has another piston collar 83. This separates a pressure chamber 85 between the screw plug 75 and the facing this end face 86 of the valve piston. The piston collar 83 is by another recess 84 of the valve piston between him and the Piston collar 78 emerged. This recess has nothing to do with the control function to do the valve piston 71, but only contributes to a large flow area for the pressure medium in the region of the annular chamber 76 at. Without the recess 84 would then only a piston collar between the piston neck 80 and the End face 86 of the valve piston 71 is present.

    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 chamber 85 between the valve piston 71 and the screw plug 75th is via a bore of the valve piston, one of the end face 86 axially introduced blind bore 87 and a continuous transverse bore 88 in the piston neck 80, fluidly connected to the annular groove 81.

    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.From the annular groove 81 opposite side of the piston collar 79 is a stop pin 89, which has a smaller diameter than the blind bore 74 and whose present at the closure screw 75 valve piston 71 existing clear distance from the bottom of the blind hole the possible displacement the valve piston illustrates. The room 90 between the floor of Blind bore 74 and the piston collar 79 is fluidly through this of the Ring chamber 77 is separated and is also in the bottom of the blind hole opening Verbohrung 62 connected to the leakage oil passage 51. Thus prevails in the room 90 tank pressure. From this space 90, the compression spring 72 is added, at the bottom of the blind bore 74 and, the stop pin across and as a guide, on the piston collar 79 of the valve piston 71 is supported. By washers 92, the bias of the compression spring 72 can be varied become.

    In Figur 2 sind auch aus dem Gehäuse 73 herausragende Teile der Ventile 60 und 65 sowie der Tankanschluß T erkennbar.In Figure 2 are also from the housing 73 outstanding parts of the valves 60 and 65 and the tank connection T recognizable.

    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 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 smaller than that set at the pressure reducing valve Pressure, so takes its valve piston 71, the position shown in Figure 2 a. is the pressure in the outlet channel 42, however, higher, so the valve piston in comparison shifted to the position shown in Figure 2 to the left and separates the annular chamber 76 and thus the inlet channel 41 of the annular chamber 77 and thus from Outflow 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. If the differential cylinders 22 and 23 in an actuation of the directional control valves 12th or 13 operated with pressing load in the sense of extension of the piston rod, is the pressure in the flow in the consumer line 20 above the prevailing in the discharge line biasing pressure, so that the check function the valves 45 is not responsive and the valve 60 set biasing pressure in the drain is maintained. The preload pressure is above the annular chamber 77, the annular groove 81 and the holes 87 and 88 in the pressure chamber 85 at and holds the valve piston in a position compared to that shown in Figure 2 shifted to the left position, in which the piston collar 78, the control edge of the Has overtravelled ring chamber 76 and the drain line 42 from the feed line 41st keeps separate. Due to the lower pressure setting of the pressure reducing valve 70 against the biasing valve 60 no pressure fluid flows from the inlet channel 41 via the pressure reducing valve in the drain passage 42 and from there via the biasing valve 60 to the tank 19. Such a pressure medium flow would be unnecessary Energy losses associated.

    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.In an operation of the differential cylinder 22 and 23 with pulling loads and in The sense of extending the piston rod, it may, whether now the directional control valve 12 with the control piston 30 or the directional control valve 13 with the as a regeneration piston trained control piston 31 is actuated, come to the fact that the pressure in the Load line 20 under the bias pressure set on the biasing valve 60 and further drops below the pressure set at the pressure reducing valve 70. In such a case, it flows over the or the corresponding as check valves acting valves 45 pressure fluid from the drain passage 42 into the corresponding Consumer line 20. The pressure reducing valve 70 opens and leads the drainage channel of the variable displacement pump at least under the stand-by pressure promoted pressure fluid, in addition to from the pressure chambers 24 of the differential cylinder displaced return oil into the consumer lines 20 and the pressure chambers 25 arrives.

    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.Upon actuation of the directional control valve 12, this return oil passes through the drainage chamber 15 in the drainage channel 42 and from there depending on which hydraulic Consumers are operated under which operating conditions, via a valve 45 in one, the other or both consumer lines 20. When actuated the directional control valve 12 also flows through the pressure compensator 32 and the metering orifice a through the opening cross section certain amount of pressure medium from the inlet channel 41 to the pressure chamber 25 of the differential cylinder 22nd

    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.Upon actuation of the directional control valve 13 with regeneration piston can Return oil from the pressure chamber 24 of the differential cylinder 23 only in the pressure chamber 25 get this cylinder. Also, it can work under certain operating conditions be for the differential cylinder 23 that because of the regeneration piston 31, the directional control valve 13 associated pressure compensator closes, so that the Pressure chamber 25 of the cylinder 23 only with the return oil from the pressure chamber 24 of the Cylinder 23 and from the pressure chamber 24 of the possibly actuated cylinder 22 and with via the pressure reducing valve 70 the flow channel flowing pressure medium is filled.

    Claims (7)

    1. A hydraulic control arrangement for the pressure medium supply of preferably a plurality of hydraulic consumers (22, 23),
      having a demand-feed regulated (load-sensing controlled) variable-displacement pump (18), the setting of which can be adjusted as a function of the highest load pressure of the actuated hydraulic consumers (22, 23),
      having a differential cylinder (22, 23) with an annular first pressure chamber (24) and a circular-cylindrical second pressure chamber (25) as hydraulic consumer,
      having a proportionally adjustable directional control valve (12, 13) with which the pressure fluid paths between an inflow line (40) emanating from the variable-displacement pump (18), an outflow line (43) leading to a tank (19), and a first consumer line (21) leading to the first pressure chamber (24) of the differential cylinder (22, 23) and a second consumer line (20) leading to the second pressure chamber (25) of the differential cylinder (22, 23) can be controlled,
      having a biasing valve (60) for the generation of a biasing pressure in a portion (42) of the outflow line (43) lying upstream of the biasing valve (60) and having arranged, between the portion (42) of the outflow line (43) and the second consumer line (20), a nonreturn valve (45) opening towards the latter,
      characterized by valve means (70) via which pressure medium can be fed from the inflow line (41) into the said portion (42) of the outflow line (43) when in this portion (42) the pressure falls to a value below that of the biasing pressure.
    2. A hydraulic control arrangement according to claim 1, characterized by the fact that the valve means are formed by a 2-way feed valve (70) that is present in addition to the biasing valve (60).
    3. A hydraulic control arrangement according to claim 1 or 2, characterized by the fact that the valve means comprise a pressure-reducing valve (70) with a valve piston (71) which is acted upon with the effect of closing the fluidic connection between the inflow line (40) and the portion (42) of the outflow line (43) by the pressure in this portion (42) and with the effect of opening the fluidic connection by a spring (72).
    4. A hydraulic control arrangement according to claims 2 and 3, characterized by the fact that the feed valve is a 2-way pressure-reducing valve (70) which is set to a pressure that is lower than the biasing pressure.
    5. A hydraulic control arrangement according to claim 4, characterized by the fact that the 2-way pressure-reducing valve (70) is set to a pressure that lies about 2 bar below the biasing pressure.
    6. A hydraulic control arrangement according to claim 4 or 5, characterized by the fact that the valve piston (71) of the 2-way pressure-reducing valve (70) has two piston collars (78, 79) axially spaced at a distance from each other, between which is located a piston neck (80), by the fact that the edge of the first piston collar (78) facing the annular groove (81) around the piston neck (80) forms a control edge which co-operates with a control edge of a housing (73) running circumferentially around an annular space (76) of the housing (73) which is connected to the inflow line (40), by the fact that a fluid path leads through the valve piston (71) from the piston neck (80) to the end face (88) of the valve piston (71) located beyond the first piston collar (78), as seen from the second piston collar (79), and that on the side of the second piston collar (79) remote from the piston neck (80) there rests a compression spring (72) into which extends a stop pin projecting from the second piston collar (79).
    7. A hydraulic control arrangement according to any of the preceding claims, characterized by the fact that a 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)

    Applications Claiming Priority (4)

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

    Publications (3)

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

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    ID=26006326

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP01110563A Expired - Lifetime EP1170510B1 (en) 2000-07-08 2001-04-30 Hydraulic control arrangement for supplying pressurised fluid preferably to several hydraulic loads

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    EP (1) EP1170510B1 (en)
    AT (1) ATE302345T1 (en)
    ES (1) ES2244517T3 (en)

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    DE102013220750A1 (en) * 2013-10-15 2015-04-16 Robert Bosch Gmbh Valve block with a valve assembly
    DE102015203404A1 (en) * 2015-02-26 2016-09-01 Robert Bosch Gmbh Hydraulic control arrangement for pressure medium supply of a hydraulic actuator

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    DE102006018706A1 (en) 2006-04-21 2007-10-25 Robert Bosch Gmbh Hydraulic control arrangement
    DE102006061305B3 (en) * 2006-12-22 2008-07-10 Hydac Filtertechnik Gmbh Control device for hydraulic consumers
    WO2008098559A1 (en) * 2007-02-16 2008-08-21 Robert Bosch Gmbh Control block comprising an oil channel for temperature control
    DE102007029358A1 (en) 2007-06-26 2009-01-02 Robert Bosch Gmbh Method and hydraulic control arrangement for pressure medium supply at least one hydraulic consumer
    DE102007029355A1 (en) 2007-06-26 2009-01-02 Robert Bosch Gmbh Hydraulic control arrangement
    EP4019786B1 (en) 2020-12-28 2023-11-22 Danfoss Power Solutions (Zhejiang) Co. Ltd Load-sensing multi-way valve work section

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    JPS61165432A (en) * 1985-01-17 1986-07-26 Hitachi Constr Mach Co Ltd Hydraulic circuit for inertial mass drive of construction machine
    JP2600009B2 (en) * 1990-04-25 1997-04-16 株式会社神戸製鋼所 Crane turning control device
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    DE102013220750A1 (en) * 2013-10-15 2015-04-16 Robert Bosch Gmbh Valve block with a valve assembly
    US9874884B2 (en) 2013-10-15 2018-01-23 Robert Bosch Gmbh Valve block having a valve assembly
    DE102015203404A1 (en) * 2015-02-26 2016-09-01 Robert Bosch Gmbh Hydraulic control arrangement for pressure medium supply of a hydraulic actuator

    Also Published As

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

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