WO2001002736A1 - Dispositif de commande hydraulique destine a alimenter, de preference, plusieurs consommateurs hydrauliques en agent de pression - Google Patents

Dispositif de commande hydraulique destine a alimenter, de preference, plusieurs consommateurs hydrauliques en agent de pression Download PDF

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Publication number
WO2001002736A1
WO2001002736A1 PCT/EP2000/005988 EP0005988W WO0102736A1 WO 2001002736 A1 WO2001002736 A1 WO 2001002736A1 EP 0005988 W EP0005988 W EP 0005988W WO 0102736 A1 WO0102736 A1 WO 0102736A1
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Prior art keywords
pressure
valve
load
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.)
Ceased
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PCT/EP2000/005988
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German (de)
English (en)
Inventor
Wolfgang Kauss
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Bosch Rexroth AG
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Mannesmann Rexroth AG
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Publication of WO2001002736A1 publication Critical patent/WO2001002736A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/05—Pressure after the pump outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/06—Pressure in a (hydraulic) circuit
    • F04B2205/061—Pressure in a (hydraulic) circuit after a throttle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/15—By-passing over the pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B2211/255—Flow control functions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • 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
    • F15B2211/515—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
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—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
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • Hydraulic control arrangement for the pressure medium supply of preferably several hydraulic consumers
  • the invention relates to a hydraulic control arrangement with which a plurality of hydraulic consumers are preferably provided with pressure medium and which has the features from the preamble of patent claim 1.
  • a hydraulic control arrangement is known for example from EP 0 566 449 A1. It is a hydraulic control arrangement based on the load-sensing principle, in which a variable pump is adjusted depending on the highest load pressure of the hydraulic consumers actuated so that the pump pressure is a certain pressure difference above the highest load pressure.
  • the hydraulic fluid flows to the hydraulic consumers via adjustable metering orifices which are arranged between an inlet line leading from the variable displacement pump and the hydraulic consumer.
  • downstream pressure balances ensure that there is a certain pressure difference across the metering orifices when the amount of pressure medium supplied by the variable displacement pump is independent of the load pressures of the hydraulic consumers, so that the amount of pressure medium flowing to a hydraulic consumer only depends on the opening cross section of the respective metering orifice. If a metering orifice is opened further, more pressure medium has to flow over it in order to generate the specific pressure difference. The variable pump is adjusted so that it delivers the required amount of pressure medium.
  • the pressure compensators downstream of the metering orifices are acted upon in the opening direction by the pressure after the respective metering orifice and in the closing direction by a control pressure present in a rear control chamber, which usually corresponds to the highest load pressure of all hydraulic consumers supplied by the same hydraulic pump. If, with simultaneous actuation of several hydraulic consumers, the metering orifices are opened to such an extent that the pressure medium delivered by the hydraulic pump adjusted to the stop is smaller than the total quantity of pressure medium required, the pressure medium quantities flowing to the individual hydraulic consumers become independent of the respective load pressure of the hydraulic Consumers reduced proportionately.
  • LUDV control Hydraulic consumers controlled in this way are called LUDV consumers for short.
  • LUDV control is a special case of load-sensing or load-sensing control (LS control).
  • I5 see consumers of moving devices or parts of devices noticeably. This is disadvantageous, in particular if rapid changes in the direction of movement, for example the shaking of an excavator bucket or the operation of a hammer, are desired.
  • the invention is based on the objective of further developing a hydraulic control arrangement which has the features from the preamble of claim 1 so that the variable displacement pump can continue to be operated in an energy-saving manner with the usual LS behavior, but if desired , operation with higher dynamics is also possible.
  • the desired aim is achieved according to the invention in that, in a generic hydraulic control arrangement according to the characterizing part of patent claim 1, there are arbitrarily switchable valve means which can be brought into a switching state in which the valve means of a pressure can be built up in the load signaling line from the feed line.
  • the switching state of the valve means mentioned there is therefore a high pressure regardless of the position of the directional valves in the load-signaling line, so that the LS pump control valve reacts quickly.
  • the pressure build-up in the feed line is preceded by the pressure build-up in the load signaling line, so that pressure is already present in the feed line at the start of the adjustment of a directional valve. This also contributes to a quick adjustment of the variable pump. Overall, we get a high dynamic of the system.
  • valve means comprise a switching valve which blocks a fluid connection from the supply line to the load signal line in a first switching position and opens in a second switching position.
  • a configuration according to claim 4 is particularly preferred, according to which the input connection of a load simulation valve which has a large hydraulic resistance and is connected to an outlet connection to a drain line can be connected to the supply line via a switchable nozzle and the load signaling line can be acted upon by the pressure present at the input connection of the valve , With this configuration, a load pressure that is lower than the pressure in the feed line can be simulated in the load signaling line.
  • the hydraulic control arrangement according to the invention can thus also be designed as an LUDV control with the pressure compensators connected downstream of the metering orifices, in which, for the inflow of pressure medium to a hydraulic consumer, a pressure difference between the pressure prevailing in the rear control chamber of the pressure compensators and the pressure prevailing in the feed line Pressure must be present.
  • the training according to claim 4 is of course also possible with an LS control.
  • the load simulation valve can be a second nozzle.
  • the hydraulic resistance of a nozzle is heavily dependent on viscosity.
  • the load simulation valve is preferably a pressure relief valve.
  • the load simulation valve lies with its input connection on the load signaling line and limits the pressure that can be built up therein to a highest value.
  • the pressure limiting valve by means of which the pressure in the load signaling line is also limited in the LUDV controls known today, is used for load simulation, so that the design of a LUDV control according to the invention requires very little additional effort.
  • the training according to claim 7 is of course also advantageous for LS controls, since a pressure control valve directly connected to the load signaling line can also be present in these controls even if a pressure control valve is provided in addition to the LS pump control valve for controlling the variable displacement pump Safety valve causes the variable displacement pump to swing back when the pressure in the supply line reaches a maximum value set on the pressure control valve.
  • a load simulation valve is preferably provided according to claim 8, which can be fluidly connected to the load signaling line with its input connection via pressure selection valve means. It is therefore treated like hydraulic consumers.
  • the control arrangement is an LS control arrangement, the design according to claim 9 appears to be associated with particularly little effort, since there is no load simulation valve. Rather, the function of an existing pump pressure control valve is used, which causes the variable displacement pump to pivot back and to limit the pressure in the feed line, even when the LS pump control valve is in a "swing out pump" position.
  • FIG. 1 shows a first exemplary embodiment working according to the LUDV principle, in which a pressure limiting valve connected directly to the load signaling line is used as the load simulation valve,
  • FIG. 2 shows a second exemplary embodiment working according to the LUDV principle, in which, in addition to the pressure limiting valve directly connected to the load signaling line, there is a second, lower set pressure limiting valve as a load simulation valve,
  • FIG. 3 shows a first embodiment working according to the LS principle, in which a pressure limiting valve directly connected to the load-reducing line is used as the load simulation valve,
  • Figure 4 shows a second embodiment based on the LS principle, in which the input connection of a pressure relief valve serving as a load simulation valve can be connected to the load signaling line via a shuttle valve
  • Figure 5 shows a third embodiment based on the LS principle, in which there is no pressure relief valve connected to the load signaling line or connectable to the load signaling line and the load signaling line can be short-circuited with the supply line.
  • variable displacement pump 10 for example an axial piston pump based on the swashplate principle, is used as the pressure medium source, which sucks pressure medium from a tank 11 and into it
  • I O delivers an inlet line 12 and the one indicated by a double arrow
  • Swashplate 13 can be pivoted in the interaction of two Steli cylinders 14 and 15. Both Steli cylinders are differential cylinders, which have a piston 16 or 17 and each have a piston rod 18 with which they engage on the swash plate 13. Pressure is only applied to the piston rod
  • the piston area of the piston 17 of the actuating cylinder 15 is smaller than the piston area of the piston 16 of the other actuating cylinder 14. Extending the piston rod 18 of the actuating cylinder 14 causes a reduction in size and extending the piston rod 18 of the actuating cylinder 15 increases the pivoting angle of the Swashplate and thus the lifting volume
  • a compression spring 19 exerts a force on the swash plate in the direction of increasing the swivel angle.
  • the pressure chamber of the actuating cylinder 15 is permanently connected to the inlet line 12.
  • the pressure in this pressure chamber is the same as in the feed line.
  • the inflow and outflow of pressure medium to and from the pressure chamber of the actuating cylinder 14 is controlled by a pump control unit 25, which is built on the variable pump 10, which has an external connection LS, to which a load signaling line 26 is connected, and which essentially two 3/2 - Proportional directional control valves, one of which represents the LS pump control valve 27 and the other the pressure control valve 28, which is set to a pressure above the normally occurring load pressures.
  • the pressure control valve 28 has a first connection, which is connected via a relief line 29 the tank 11 can be connected A second connection of the pressure control valve 28 is connected to the inlet line 12.
  • the third connection which can be connected to the first or the second connection, is connected to the pressure chamber of the actuating cylinder 14.
  • a first connection of the LS pump control valve 27 is connected to the Discharge line 29, a second connection to the inlet line 12.
  • the third connection of the valve 27 can be connected to its first or second connection and is permanently connected to the first connection of the valve 28.
  • a slide valve 28, not shown, is actuated by a compression spring 30 in the sense of a Enlargement of the swivel angle and from the inlet pressure in the sense of a reduction in the swivel angle of the pump 10
  • a slide of the LS pump control valve 27, not shown in more detail, is finally used in the sense of an increase in the swivel angle of the pump 10 by a compression spring 31 and by the pressure prevailing in the load signaling line 26 and in the sense of a reduction in the Swivel angle acted upon by the inlet pressure
  • There is a force equilibrium on the slide of the valve 27 if there is a difference between the inlet pressure and the pressure in the load signaling line 26 which corresponds to the force of the spring 31 28 prevails when the inlet pressure generates a force which corresponds to the force of the spring 30.
  • the inlet pressure is in the range of 350 bar
  • FIGS. 1 and 2 show two examples Sections shown, which are constructed completely the same. Of course, there may be other sections.
  • the control block 35 has an inlet connection P, a tank connection T, a load reporting connection LS and various consumer connections A and B.
  • An inlet channel 36 begins at the inlet connection P as part of the inlet line 12 and a tank channel 37 of the control block at the tank connection T.
  • Two LUDV directional control valves 38 with a closed center are formed in the control block, with which two hydraulic consumers, for example two differential cylinders, can be controlled.
  • a speed control part and a direction control part are formed separately from one another on the same control slide.
  • pressure medium coming from the inlet channel 36 flows from an inlet chamber 39 via a measuring orifice 40 into a first intermediate chamber 41, from there via the opening cross section of a pressure compensator 42 into a second one Intermediate chamber 43 and then via the directional part of the directional control valve into a consumer chamber 44 or 45. From there, pressure medium reaches consumer port A or B.
  • the regulating piston of the pressure compensators 42 becomes open in the opening direction by the pressure in the intermediate chamber 41, that is, the pressure after the orifice plate 40 and acted upon in the closing direction by the pressure in a load signaling channel 46 running as part of the load signaling line in the control block and by a weak compression spring 47.
  • the control piston of the pressure compensators 42 is designed such that, when the pressure compensator is completely open, it creates a throttled connection between the intermediate chamber 41 and the load-sensing channel 46. This is the case if the respective hydraulic consumer is operated alone or if the hydraulic consumer assigned to the respective pressure compensator has the highest load pressure when a plurality of hydraulic consumers are operated simultaneously.
  • the external connections P, T and LS of the control block 35 are located on an input section 48, through which the channels 36, 37 and 46 lead to the directional valve sections.
  • a pressure relief valve 50 is connected with its inlet connection 51 to the load signaling channel 46 and with its outlet connection 52 to the tank channel 37.
  • Valve 50 limits the pressure that can be built up in the load reporting line to a maximum value, for example to 230 bar.
  • a small flow control valve 53 is located in the input section 48 between the load-signaling channel 46 and the tank channel 37.
  • a 2/2 way switching valve 60 which can be actuated by an electromagnet 59 and is designed as a seat valve, and a nozzle 61 located in series with it.
  • the switching valve is connected between the control block 35 and the variable displacement pump 10 with an input to the inlet line 12. It locks in the rest position. After actuation, it connects one side of the nozzle 61 to the feed line 12.
  • the other side of the nozzle 61 is connected directly to the load reporting line 26.
  • the other side of the nozzle 61 is connected to the inlet connection 51 of a further pressure relief valve 62 which is present in addition to the pressure relief valve 50 and which is set to a lower value than the pressure relief valve 50, for example to 200 bar.
  • the pressure relief valve 62 With its outlet connection 52, the pressure relief valve 62 is connected to a tank line 63 leading from the tank connection T of the control block 35 to the tank 11.
  • the inlet connection 51 of the pressure relief valve 62 and thus one side of the nozzle 61 can be connected via a check valve 64 to the load signaling line 26, towards which the check valve opens.
  • the two control arrangements according to FIGS. 1 and 2 can be operated like conventional LUDV controls. Their mode of operation is generally known, so that there is no need to go into this here.
  • control oil flows from the feed line 12 via the nozzle 61 to the load-signaling line 26.
  • the flow cross-section of the nozzle 61 is selected such that, given the pressure difference via the nozzle 61, which is predetermined by the setting of the LS pump control valve 27, the quantity of pressure medium flowing to the load signaling line is greater than the regulated quantity of pressure medium flowing out of the load signaling line via the flow control valve 53 ,
  • a pressure builds up in the load-signaling line until the pressure relief valve 50 responds in the embodiment according to FIG. 1 and the pressure relief valve 62 responds in the embodiment according to FIG.
  • the pressure in the inlet line is higher by the pressure difference set at valve 27 than the pressure set at pressure relief valve 50 or 62. Since the pressure in the load signaling line also prevails in the rear control rooms of the pressure compensators 42, the hydraulic consumers can be operated with the same pressure difference via the orifice plates 40 as in normal LUDV operation. The greater difference between the pressure in the feed line and the load pressures is compensated for by increased throttling at the control edges of the pressure compensators, whereby with a gain in dynamics, however, higher energy losses occur than in normal LUDV operation.
  • the check valve 64 in the embodiment according to FIG. 2 prevents the pressure limiting valve 62 from responding in normal LUDV operation.
  • LS control arrangements are given to the exemplary embodiments 5 according to FIGS. 3, 4 and 5 by the type of the existing control block 65, which is composed of LS directional control valve disks and, like the control block from FIGS has a load signaling connection LS.
  • the existing control block 65 which is composed of LS directional control valve disks and, like the control block from FIGS has a load signaling connection LS.
  • two way valve disks 66 are shown, which are constructed completely identically. Of course I O there may be more disks.
  • Each directional valve disk 66 serves as a housing for a directional valve 67. Both directional valve disks 66 are completely identical to one another and contain the same components and channels.
  • Each directional control valve 67 includes a control spool 68, 15 which is axially displaceable in a valve bore (not specified in any more detail) and which assumes a neutral position under the mere effect of two centering springs 69. In this position, a consumer channel 70, which leads to a consumer connection B, a consumer channel 71, which leads to a consumer connection A, the inlet channel 36 and the outlet channel 37 are separated from one another.
  • the spool 68 of a directional control valve By pressurizing a control pressure chamber 72, the spool 68 of a directional control valve is displaced out of the neutral position in one direction and by pressurizing a control pressure chamber 73 in the other direction. Depending on the direction of displacement, either the consumer channel 70 becomes 25 or the consumer channel 71 with the inlet channel 36 and the other
  • the control slide opens a metering orifice between an inlet inlet on the directional control valve and a consumer channel, the opening cross section of which determines the amount of pressure medium that flows to the hydraulic consumer.
  • a pressure compensator 75 is arranged in the part of the inlet channel 36 leading to the inlet inlet of the directional valve, which is acted upon in the closing direction by the pressure in front of the measuring orifice and in the opening direction by the pressure behind the measuring orifice and by a compression spring 76.
  • the pressure drop across the orifice plate is equivalent to the force of the compression spring 76 and is set to a value between 10 bar and 20 bar.
  • the pressure after the metering orifice corresponds to the load pressure of the respective hydraulic consumer.
  • This pressure is also present at an inlet of a shuttle valve 77, the other inlet of shuttle valve 77 of one directional valve disc being connected to the outlet of shuttle valve 77 of the other directional valve disc.
  • the other inlet of the shuttle valve 77 from the latter directional control valve disk is connected to the outlet channel 37 via an end plate 78.
  • a channel leads from the outlet of the shuttle valve 77 of the former directional control valve disk to the load signaling connection LS of this disk.
  • the highest load pressure of the hydraulic consumers that can be actuated with the two directional control valves is present at this connection LS.
  • the pressure in the inlet channel 36 is around a predetermined pressure difference of e.g. 15 bar above the highest load pressure.
  • Pressure equivalent to the force of the compression spring 76 of a pressure compensator 75 can also be 15 bar, so that regardless of whether a hydraulic consumer generates the highest load pressure or not, the pressure drop across the measuring orifice of the respective directional control valve is the same.
  • a small flow control valve 53 and a pressure relief valve 50 lie parallel to one another between a load signaling line 26 leading from the connection LS of the control block 65 to the connection LS of the control unit 25 and a tank line 63.
  • the series connection of the 2/2-way switching valve 60 and the nozzle 61 between the feed line 12 and the load signaling line 26 is also identical to the embodiment according to FIG. 1.
  • the pressure limiting valve 52 and the flow control valve 53 to the load signaling line 26 and the connection LS of the control block 65 there is also a check valve 79 which blocks the connection LS so that the pressure compensators 75 are also acted upon on one side by the individual load pressure when the valve 60 is switched, and the hydraulic one
  • the amount of pressure medium flowing to the consumer depends solely on the flow cross-section of the respective metering orifice.
  • the control arrangement shows the usual LS behavior.
  • the pressure in the section of the load signal line between the check valve 79 and the connection LS of the control unit 25 rises to the value set on the pressure limiting valve 50 due to the inflow of control oil via the nozzle 61.
  • the pressure in the supply line is then, regardless of the load pressures of the hydraulic consumers operated, higher by the pressure difference set on the pump control valve 27 than the pressure at the inlet connection of the pressure relief valve 50 and at the connection LS of the control unit 25.
  • the flow cross section of the nozzle 61 is also here large that the amount of pressure medium flowing through the nozzle at the set pressure difference is greater than the controlled amount of the flow control valve 53.
  • the maximum pressure in the load signaling line 26 is determined by the same pressure relief valve in the usual LUDV or LS operation and in operation with increased dynamics.
  • the embodiment according to FIG. 4 is similar to the embodiment according to FIG. 2 in that there is that for the operating mode with the higher dynamic in the Load signaling line 26 provided pressure is lower than the maximum pressure possible in the load signaling line.
  • the outlet of the nozzle 61 is connected to the inlet connection of a pressure relief valve 62.
  • a shuttle valve 80 is connected to the connection channel with one of its two inputs, to the other input of which a first section of the load-signaling line 26 leads from the shuttle valve 77 of the control block 65.
  • a second section of the load signal line leads from the outlet of the shuttle valve 80 to the connection LS of the control unit 25.
  • the switching valve 60 assumes the position shown in FIG. 4.
  • the highest load pressure that occurs at the actuated hydraulic consumers is then reported to the control unit 25 via the shuttle valves 77 and 80.
  • a higher inlet pressure is set in the inlet line by the pressure difference set on the LS pump control valve. If the load pressure of a hydraulic consumer and with it the pressure in the feed line 12 increases, for example because the hydraulic consumer has hit a stop, to the value set on the pressure control valve 28, this valve responds and the variable displacement pump 10 swings back.
  • the pressure in the load signaling line rises up to the pressure in the supply line.
  • the pressure set on the pressure relief valve 62 is reported via the shuttle valve 80 via the shuttle valve 80 to the section of the load reporting line leading to the control unit 25, as long as the load pressures of the actuated hydraulic consumers are below the set value lie.
  • the flow through the nozzle 61 is also greater than the flow through the flow control valve 53, which is arranged between the said section of the load signaling line and the tank line. If a load pressure exceeds the pressure set on the pressure limiting valve 62, this higher load pressure is supplied via the shuttle valve 80 Control unit 25. A further increase in the highest load pressure finally allows the pressure control valve 28 to respond as in the normal LS operation.
  • a check valve 79 which blocks from the connection LS of the control unit 25 to the connection LS of the control block 65, is inserted between two sections of the load signal line 26, similar to that according to FIG.
  • the switching valve 60 is arranged between the connection LS of the control unit 25 and the inlet line 12 and the flow control valve 53 between the connection LS of the control unit 25 and the outlet line 63.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un dispositif de commande destiné à alimenter, de préférence, plusieurs consommateurs hydrauliques en agent de pression. Ce dispositif comprend une pompe à cylindrée variable (10) à réglage par détection de charge et dont le réglage peut être modifié par une soupape de réglage de pompe à détection de charge (27) en fonction d'une pression de charge maximale du consommateur hydraulique actionné; des tiroirs (38) à réglable proportionnel placés entre une conduite d'alimentation (12) partant de la pompe à cylindrée variable, une conduite d'évacuation (63) conduisant à un réservoir (11) et les consommateurs hydrauliques ; et enfin une conduite de signalisation de charge (26) par laquelle la soupape de réglage de pompe à détection de charge (27) est alimentée avec la pression de charge maximale des consommateurs hydrauliques actionnés simultanément. Parfois, un tel dispositif de commande n'a pas la dynamique souhaitée. L'objectif est donc d'améliorer ce dispositif de telle façon que la pompe à cylindrée variable puisse continuer à fonctionner avec le comportement détection de charge usuel en étant économique en énergie mais qu'il puisse aussi, si besoin, fonctionner avec une plus grande dynamique. A cet effet, des moyens soupapes (60, 61) couplables de façon arbitraire peuvent être amenés en mode couplé dans lequel une pression peut être établie dans la conduite de signalisation de charge à partir de la conduite d'alimentation par les moyens soupapes.
PCT/EP2000/005988 1999-07-02 2000-06-28 Dispositif de commande hydraulique destine a alimenter, de preference, plusieurs consommateurs hydrauliques en agent de pression Ceased WO2001002736A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19930618A DE19930618A1 (de) 1999-07-02 1999-07-02 Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern
DE19930618.4 1999-07-02

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EP1253327A1 (fr) * 2001-04-28 2002-10-30 Robert Bosch Gmbh Circuit de commande hydraulique
US8006490B2 (en) * 2005-11-21 2011-08-30 Bosch Rexroth Ag Hydraulic control device
CN105041732A (zh) * 2015-09-18 2015-11-11 上海中联重科桩工机械有限公司 带有自动抖土功能的控制系统及旋挖钻机
CN110304137A (zh) * 2019-08-13 2019-10-08 徐州重型机械有限公司 液压系统以及起重机
WO2021227452A1 (fr) * 2020-05-12 2021-11-18 徐州徐工基础工程机械有限公司 Système de treuil principal d'appareil de forage rotatif et son procédé de commande

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DE102004061555A1 (de) 2004-12-21 2006-06-22 Bosch Rexroth Aktiengesellschaft Hydraulische Steueranordnung
DE102007055377A1 (de) 2007-11-19 2009-05-20 Robert Bosch Gmbh Hydraulische Steueranordnung und Wegeventilsektion
DE102010009705A1 (de) 2010-03-01 2011-09-01 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102012015286A1 (de) * 2012-03-01 2013-09-05 Robert Bosch Gmbh Hydraulische Load-Sensing Steueranordnung
CN102927086A (zh) * 2012-11-16 2013-02-13 无锡汇虹机械制造有限公司 一种液压系统负载敏感变量泵流量控制方法
CN102927089A (zh) * 2012-11-16 2013-02-13 无锡汇虹机械制造有限公司 一种液压系统负载敏感技术节能控制方法
DE102014215549A1 (de) * 2014-08-06 2016-02-11 Robert Bosch Gmbh Hydrostatischer Antrieb
DE102021108081B4 (de) 2021-03-30 2023-02-02 Andreas Lupold Hydrotechnik Gmbh Vorrichtung zum Regeln einer Hydraulikpumpe oder eines Hydraulikmotors

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1253327A1 (fr) * 2001-04-28 2002-10-30 Robert Bosch Gmbh Circuit de commande hydraulique
US8006490B2 (en) * 2005-11-21 2011-08-30 Bosch Rexroth Ag Hydraulic control device
CN105041732A (zh) * 2015-09-18 2015-11-11 上海中联重科桩工机械有限公司 带有自动抖土功能的控制系统及旋挖钻机
CN110304137A (zh) * 2019-08-13 2019-10-08 徐州重型机械有限公司 液压系统以及起重机
WO2021227452A1 (fr) * 2020-05-12 2021-11-18 徐州徐工基础工程机械有限公司 Système de treuil principal d'appareil de forage rotatif et son procédé de commande
US12091293B2 (en) 2020-05-12 2024-09-17 Xuzhou Xugong Foundation Construction Machinery Co., Ltd. Main hoist system of rotary drilling rig, and control method therefor

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