EP1149246B1 - Dispositif de commande pour au moins deux consommateurs hydrauliques, et soupape a pression differentielle correspondante - Google Patents

Dispositif de commande pour au moins deux consommateurs hydrauliques, et soupape a pression differentielle correspondante Download PDF

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Publication number
EP1149246B1
EP1149246B1 EP00906203A EP00906203A EP1149246B1 EP 1149246 B1 EP1149246 B1 EP 1149246B1 EP 00906203 A EP00906203 A EP 00906203A EP 00906203 A EP00906203 A EP 00906203A EP 1149246 B1 EP1149246 B1 EP 1149246B1
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EP
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Prior art keywords
pressure
control
valve
fact
acted
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EP00906203A
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German (de)
English (en)
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EP1149246A1 (fr
Inventor
Martin OBERHÄUSSER
Thomas Weickert
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Bosch Rexroth AG
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Bosch Rexroth AG
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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
    • F15B11/163—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
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/421—Flow control characterised by the type of actuation mechanically
    • F15B2211/423—Flow control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of a differential 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
    • F15B2211/67—Methods for controlling pilot 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
    • 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
    • F15B2211/78—Control of multiple output members

Definitions

  • the invention relates to a control arrangement, with the at least two hydraulic Consumers are supplied with pressure medium and the characteristics of the Preamble of claim 1 has.
  • the invention also relates to a Pressure differential valve used in particular in said control arrangement becomes.
  • a hydraulic control arrangement is e.g. from EP 0 566 449 A1. It is a hydraulic one Control arrangement according to the load-sensing principle, at a variable displacement pump depending on the highest load pressure actuated hydraulic consumers are each set so that the inlet pressure to a certain pressure difference is above the highest load pressure.
  • the two hydraulic For consumers the pressure medium flows through two adjustable metering orifices to, of which a first between one outgoing from the variable displacement Pump line and a first hydraulic consumer and the second between the pump line and the second hydraulic consumer is arranged.
  • variable displacement is adjusted in each case so that they the required amount of pressure medium supplies. This is why one speaks of a demand current regulation.
  • the metering orifices downstream pressure compensators are in the opening direction from the pressure after the respective metering diaphragm and in the closing direction of applied to a pending in a rear control chamber control pressure, usually the highest load pressure of all supplied by the same hydraulic pump hydraulic consumer corresponds. If at a simultaneous actuation several hydraulic consumers the metering orifices opened so far be that supplied by the up to the stop adjusted hydraulic pump Pressure medium quantity is smaller than the total required pressure medium quantity, Be the individual hydraulic consumers inflowing pressure fluid quantities regardless of the load pressure of the hydraulic consumers proportionally reduced. This is why we speak of a controller with load-independent Flow distribution (LUDV control). Such controlled hydraulic Consumers are called LUDV consumers for short.
  • LUDV control load-independent Flow distribution
  • a LUDV control is a special case of a load-sensing or load-sensing control (LS control).
  • a Steberan angel with the features of the preamble of the claim 1 is also known from DE 38 44 400 A1.
  • a pressure is reported to the variable displacement pump, and the Junction between a metering and the downstream of this Pressure compensator inserted in each case one to Lastmelde effet opening check valve.
  • the rear control chamber of a pressure compensator is via a shuttle valve with the pressure in the load-sensing line or with the load pressure the associated hydraulic consumer acted upon. It also works in Closing direction on the pressure balance a spring slightly weaker than the Spring of the check valve is.
  • DE 296 17 735 U1 shows a hydraulic control arrangement, the one LUDV control according to the preamble of claim 1 is.
  • the rear control chamber of the pressure compensator also via a shuttle valve either with a channel downstream of the pressure compensator or connectable to the load signaling line leading to a pump regulator.
  • the junction between a metering and the This downstream pressure compensator each have a nozzle and a to Lastmelde effet inserted opening check valve. Between the nozzle and the Check valve is connected to another check valve, which leads to the Channel downstream of the pressure compensator opens.
  • the pressure in the rear control chambers of the pressure compensators not higher than the highest Load pressure.
  • each pressure medium via a metering orifice with upstream pressure compensator flows, in the closing direction only from the pressure in front of the metering orifice and in the opening direction only from the load pressure of the respective hydraulic consumer and is acted upon by a compression spring, you get no load-independent flow distribution.
  • Such control is e.g. through the DE 197 14 141 A1 known.
  • An advantage of a LS control with the metering orifices upstream pressure compensators downstream of a LS control with the metering orifices downstream Pressure compensators is that for a short time at one of the variable supplied excess quantity and an associated increase in Zulaufdrukkes the upstream pressure compensators by reducing their opening cross section do not allow increasing the pressure difference across the orifices, so that over the Zumeßblenden not more pressure medium flow and the speed the hydraulic consumer is not changed.
  • the superset flows back to a tank via a pressure relief valve.
  • the invention is the objective of a hydraulic Control arrangement comprising the features of the preamble of claim 1 has, so in particular the pressure compensators downstream of the metering orifices are to be designed so that the influx of excess quantities to the hydraulic Consumers is prevented.
  • the desired goal is inventively achieved in that in a generic hydraulic control arrangement according to the characterizing Part of claim 1, the control piston of the pressure compensators in the closing direction acted upon by a pending in a rear control chamber control pressure are, with the help of a valve device prevailing in the supply line Inlet pressure is derived and changes with the inlet pressure. While in the known hydraulic control arrangement with the metering orifices Downstream pressure compensators in the rear control room with the highest load pressure to be applied to the flow of the variable displacement pump has no influence is in a control arrangement according to the invention the in the rear control chamber pending control pressure derived from the inlet pressure and changes with this. So if the inlet pressure for one over the need outgoing flow rate of the variable displacement increases, and the increases Control pressure on.
  • Consistent Pressure difference over a Zumeßblende means, however, at the same Opening cross section of the metering diaphragm also consistent over the Zumeßblende flowing pressure medium quantity.
  • the difference between the inlet pressure and the control pressure with not yet adjusted to the stop variable So with a sufficient amount of pressure medium not greater than between the Inlet pressure and the highest load pressure. If the pressure difference were greater, so Namely, would the hydraulic fluid consumer influent pressure medium depend on whether the load pressure of this hydraulic consumer higher or lower than the control pressure.
  • the control pressure is small higher than the highest load pressure, so that on the one hand no unnecessary throttle losses on the pressure compensators arise, on the other hand, but also the one associated with respective hydraulic consumers with the highest load pressure Pressure compensator is still in the control range.
  • the pressure difference between the supply line and a rearward control room on a pressure compensator thereby produce that between the feed line and the control chamber a nozzle and between the Control room and a tank, a flow control valve are connected.
  • About the Flow control valve would each have a certain amount of control oil from the control room drain to the tank. This amount of control oil would pass through the nozzle to the control room accrue. Over the nozzle would thus be a constant pressure gradient. Indeed For example, the amount of pressure fluid flowing through a nozzle is highly dependent on the viscosity the pressure medium dependent.
  • a pressure differential valve which with a Input to the supply line and with an output to the rear control room a pressure compensator is connected.
  • the pressure difference valve is preferably set according to claim 4 to a fixed pressure difference and has a movable valve member, in the sense of opening the fluidic connection between the supply line and the control room on the pressure compensator from Inlet pressure and in the sense of closing this connection from the control pressure and acted upon by a spring.
  • a particularly preferred embodiment also contains the patent claim 5, after the backward control rooms of several pressure compensators directly with each other are connected, so that in these control rooms the same control pressure prevails.
  • these pressure compensators is thus only a valve device for the derivation the control pressure from the inlet pressure necessary.
  • the control arrangement has a load signal line, in the over selector valves, the highest load pressure of each actuated hydraulic consumer is given, and a valve that is a fluidic Connection from the load signal line to the rear control room at least a pressure compensator opens when the difference between the inlet pressure and the highest load pressure falls below a certain value. In this way receives in the case of supersaturation, ie inadequate pressure medium delivery the variable displacement pump, a load independent flow distribution between the hydraulic consumers whose pressure compensators with their control room with the Load signal line to be connected.
  • the priority valve according to claim 9 a connected to the supply line first port and one with the back control rooms of the non-privileged one hydraulic consumers associated pressure compensators connected second Connection on and possesses a valve member, which opens towards the connection between the first terminal and the second terminal of in one Line section downstream of the privileged hydraulic consumer associated metering orifice prevailing pressure and an additional force and in Direction closing the connection between the first port and the second port of the inlet pressure can be acted upon.
  • Downstream of the metering orifice may a control chamber of the priority valve upstream or downstream of the pressure compensator be connected to the line section, since the priority valve then in Function occurs when the pressure balance is completely open and because then before and behind the pressure balance of the same pressure, namely the load pressure of the privileged hydraulic consumer prevails.
  • An object of the invention is also to provide a pressure differential valve, in particular is used to in a control arrangement according to one of the claims 1 to 9 from the inlet pressure a control pressure for a pressure balance derive and that builds particularly small, so it easily into one Control block can be used.
  • Figure 1 sucks a variable displacement pump 10 with an adjustment 11 pressure medium from a tank and it is in a system of supply lines 13 from.
  • the Supply lines are in the exemplary embodiment three hydraulic consumers 14, 15 and 16, which are all designed as differential cylinders, supplied with pressure medium.
  • To control the speed and the direction of movement are each Differential cylinder 14, 15 and 16, a metering orifice 17, 18 and 19 and a 4/3-way valve 20, 21 and 22 assigned.
  • a metering and a directional control valve each integrated into one another such that by the operation of a in a central position spring-centered valve slide in a certain direction from the middle position out the direction of movement of the differential cylinder specified and by the way, the valve spool is moved, the opening cross-section the metering aperture is determined.
  • the metering apertures 17, 18 and 19 are connected to the system of the supply lines 13.
  • a pressure compensator 23, 24 and 25 respectively, whose not shown Regulating piston in the opening direction of the pressure downstream of the respective Metering and in the closing direction of a in a rear control room 26 prevailing control pressure is applied.
  • the directional valves 20, 21 and 22 each have two connected to pressure chambers of the respective differential cylinder Load ports 30 and 31, an inlet port 32, with the Output of the respective pressure compensator is connected, and a return port 33, from which a return line to the tank 12 leads. In the middle position of a Directional valve, the two consumer connections are shut off and the inlet connection is connected to the tank connection.
  • the line section between the output of the pressure compensator and the inlet connection is therefore of pressure relieved.
  • a lateral working position of a directional valve flows the one Pressure chamber of a hydraulic cylinder pressure medium too, while from the other Pressure chamber pressure fluid can flow away to the tank.
  • control pistons of the pressure compensators 23, 24 and 25 are in the direction of closing except by a control pressure and a weak compression spring 34 applied, which is a pressure of e.g. is only 0.5 bar equivalent.
  • a control pressure and a weak compression spring 34 applied which is a pressure of e.g. is only 0.5 bar equivalent.
  • the Control chambers 26 and 27 of the two pressure compensators 23 and 24 via a channel 35th interconnected so that in the two control rooms 26 and 27 always the same control pressure is pending.
  • shuttle valves 36 To the outputs of the pressure compensators 23, 24 and 25 or to the inlet connections 32 of the directional valves are connected shuttle valves 36, which in such a way are concatenated that in a load reporting line 37, the adjustment 11 of the pump 10 leads, which is present in each case the highest load pressure of all actuated differential cylinder.
  • the load-signaling line 37 leads to it a control valve 39 with three ports, one of which with a control cylinder 40 of the variable displacement pump 10 is connected.
  • Another connection of the control valve 39 is connected to a supply line 13 and the third connection to tank 12.
  • the control piston of the control valve 39 is in the direction of a connection of the first Connection with the second connection from the pressure in the supply line 13 and in Direction of a connection of the first terminal to the third terminal of Pressure in the load-sensing line 37 and acted upon by a control spring 41.
  • Variable and control valves according to the circuit diagram of Figure 2 are general known and readily available on the market. It is therefore unnecessary, closer to respond to it. It should only be noted that the shown Load-sensing or load-sensing pump control causes in the supply line 13 sets a pressure equivalent to one of the force of the control spring 41 Pressure difference is above the pressure in the load-sensing line 37.
  • a pressure differential valve 45 arranged between the system of the supply lines 13 and the channel 35 between the two control chambers 26 of the pressure compensators 23 and 24. This is with an inlet opening 46 to the inlet pipes 13th and connected to the output port 47 to the channel 35.
  • piston valve 48 of the pressure difference valve 45 are the input port 46 and shut off the output port 47 against each other or over a more or less large opening cross-section fluidly interconnected.
  • the piston valve 48 is in the direction of reduction of the opening cross-section between the inlet opening and the outlet opening in the channel 35 and in the control chambers 26 of the pressure compensator pressure prevailing and of a Compression spring 49 and in the direction of enlargement of the opening cross-section of in supplied to the supply lines 13 prevailing inlet pressure.
  • the effective surfaces on the piston valve for the attack of the control pressure and the inlet pressure are the same size, so that the pressure differential valve 45 ensures that in the channel 35 pending control pressure a rising inlet pressure in each case at a distance one of the force of the compression spring 49 equivalent differential pressure follows.
  • the pressure differential valve 45 is set so that the control pressure 20 bar lower than the inlet pressure.
  • the channel 35 is via a small current regulator 50th connected to tank 12, so that the control pressure in the channel 35 by outflow of Pressure medium via the small flow regulator 50 and a decreasing inlet pressure can follow.
  • the control the spool of the differential pressure valve 52 is the same as the controller the spool of the differential pressure valve 45. Both valves are on the same pressure difference of e.g. 20 bar set. With sufficient flow the variable displacement pump 10 is thus the control pressure in the control chambers 26 by 20 bar lower than the inlet pressure and, since this example by 25 bar higher than the highest load pressure should be 5 bar higher than the highest load pressure.
  • the Pressure balances 23, 24 and 25 are therefore all inclusive, including those which is assigned to the consumer with the highest load pressure, in control position. Furthermore, the control chamber 26 of the pressure compensator 25 via a second Small current regulator 50 connected to tank 12.
  • the differential cylinder 16 should, when the variable displacement pump 10 maximum flow brings and does not meet the needs, above all the other two Hydraulic cylinders 14 and 15 are supplied with pressure medium.
  • a priority valve for this 55 provided as a proportional shutter with an input 56 and with an output 57 is formed. The latter is fluidically connected to the channel 35.
  • the input 56 is connected upstream of the metering orifice 19 with a supply line 13.
  • the not shown movable valve member of the priority valve will be in the direction of closing the connection between the input and the output from the pressure in the inlet, ie from the inlet pressure and in the direction of opening the Connection from the pressure downstream of Zumeßblende 19 and the force of a control spring 58 charged.
  • the control spring 58 is e.g.
  • He is capable of the priority valve 55 to open against the inlet pressure, whereby the pressure in the channel 35 and thus in the control chambers 26 of the pressure compensator 23 and 24 on the highest load pressure is raised.
  • the pressure compensators 23 and 24 are therefore in the closing direction adjusted until by an increase in the pressure downstream of the metering orifices 17 and 18 again an equilibrium of forces is reached at its control piston. Now, however reduces the pressure difference across the metering orifices 17 and 18. The to the Consumers 14 and 15 flowing pressure medium flows have become smaller.
  • the priority valve 55 provides by raising the pressure in the Control spaces 26 of the pressure compensators 23 and 24 that by an increase in the Control pressure in the channel 35, the pressure difference across the metering orifices 17 and 18th and thus the flowing to the hydraulic consumers 14 and 15 pressure medium flows each be reduced so far that the metering diaphragm 19 a Pressure medium amount flows, which generates a pressure difference, which is approximately equal to the Pressure difference in normal operation is.
  • the Priority valve can now be set to the same pressure difference, too in normal operation on the Zumeßblende 19 prevails, since in normal operation the Pressure difference between the load pressure of the priority hydraulic consumer 16 and the inlet pressure is higher than the pressure difference across the Zumeßblende 19 and therefore the priority valve 55 certainly does not respond.
  • This pressure which is slightly elevated above the highest load pressure, is downstream of both Metering 17 and 18 at. Upstream of both metering orifices 17 and 18 prevails Inlet pressure. Thus, the pressure difference across the metering orifice 17 is equal to Pressure difference across the metering orifice 18.
  • the pressure medium flows to the hydraulic Consumers 14 and 15 therefore become independent in the case of undersaturation of whether the preferential consumer 16 is actuated, proportional reduced. Consumers 14 and 15 are therefore LUDV consumers.
  • variable displacement 10 of the pressure medium demand all simultaneously actuated hydraulic consumer is covered by the differential pressure valves 45 and 52 together with the current regulators 50 for the control pressures in the Control chambers 26 of the pressure compensators follow the inlet pressure at a fixed distance.
  • variable displacement 10 for a short time beyond the requirement Quantity, because e.g. a wide open metering orifice is completely closed, the inlet pressure rises sharply for a short time.
  • the control pressures follow this Rise, so that the control piston of the pressure compensator in the closing direction with a increased control pressure can be applied, in the closing direction of the pressure compensators move and thereby raise the pressure downstream of the metering orifices, so that the pressure difference across the Zumeßblenden 17, 18 and 19 remains the same or only slightly increased. So does not increase the speed of one hydraulic consumer.
  • the oversize flows via a pressure relief valve 60 to the tank.
  • the pressure difference valves 45 used in the control arrangement according to FIG and 52 are, as has already been pointed out, the same and as shown in FIG designed as built-in cartridges. They have a cartridge housing 70, passes through the axially a stepped valve bore 71. From one end is in the valve bore 71, an adjusting screw 72 screwed through which the Valve bore 71 is closed and the support of the control spring 49th serves. This control spring is located in the portion of the valve bore 71 with the larger diameter, in which also the adjusting screw 72 is screwed is. The control spring 49 is supported with its adjusting screw 72 facing away from End of the spool 48 from the axially movable guided in the valve bore 71 is.
  • the free space in the valve bore between the adjusting screw 72nd and the spool 48 may be referred to as a spring chamber 75.
  • a spring chamber 75 In these opens free a star of radial bores 76, the output 47 of the pressure differential valve form.
  • Radial holes 76 separated At an axial distance to the radial bores 76 and after installation in a block by a sealing arrangement 77 fluidly from the Radial holes 76 separated go through the cartridge housing 70 more radial bores 78 therethrough, which form the input of the pressure difference valve.
  • Outside on the cartridge housing 70 is also after installation in a Block a free fluidic connection between the radial bores 78 and the End face 79 of the cartridge housing 70, at which the smaller diameter portion the valve bore 71 comes to the outside.
  • the spool 48 is in the latter portion of the valve bore 71st guided axially and has there outside an annular groove 80 through which an annular space between he and the wall of the valve bore 71 is created. From the adjusting screw 72 facing end face is in the spool 48 a axial blind bore 81 introduced, which extends into the region of the annular groove 80 and there is connected via individual radial bores 82 with the annular groove 80. Additional radial bores 83 provide for an open fluidic connection between the bore 81 and the spring chamber 75 and thus the output 47 also when the spool 48 with its one end to a stop the adjusting screw 72 is applied.
  • the spool 48 has an outer shoulder 84, with which he from the control spring 49 against the inner shoulder of the valve bore 71 can be pressed.
  • the annular groove 80 is located between the bore star of the radial bores 78 and the end face 79 of the cartridge housing 70. There is no opening cross-section between the radial bores 78 and the annular groove 80.
  • the spool 48 is sealingly sliding in the valve bore 71 out, so that the radial bores 78 from the spring chamber 75 and the annular groove 80th are fluidly separated from the space in front of the end face 79 of the valve housing. So there is no fluid connection between the input 46 and the Output 47 of the valve.
  • the spool 48 is from the front side 79 of the valve housing 70 ago acted upon by the inlet pressure.
  • the compression spring 49 and on an equal area as the inlet pressure the output pressure in the output 47.
  • Balance on Piston 48 prevails when the output pressure to one of the force of Compression spring 49 equivalent pressure difference is less than the inlet pressure.

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

Claims (13)

  1. Un dispositif de commande pour l'alimentation en fluide de pression d'au moins deux récepteurs (14, 15, 16) hydrauliques à l'aide d'une pompe (10) à cylindrée variable à régulation du débit en fonction du besoin (à régulation load-sensing), dont le calibrage peut être modifié par un régulateur (11) de pompe en fonction de la pression en charge la plus élevée des récepteurs (14, 15, 16) hydrauliques actionnés,
    doté de deux orifices (17, 18, 19) d'étranglement réglables, desquels un premier est disposé entre une conduite (13) d'alimentation partant de la pompe (10) à cylindrée variable et un premier récepteur (14, 15, 16) hydraulique et le deuxième est disposé entre la conduite (13) d'alimentation et un deuxième récepteur (14, 15, 16) hydraulique, et doté de deux balances (23, 24, 25) de pression, desquelles une première est branchée en aval du premier orifice (17, 18, 19) d'étranglement et la deuxième est branchée en aval du deuxième orifice (17, 18, 19) d'étranglement et dont les tiroirs de régulation peuvent être soumis, sur une face avant et dans le sens de l'ouverture, à la pression régnant en aval de l'orifice (17, 18, 19) d'étranglement correspondant,
    caractérisé en ce que
    les tiroirs de régulation des balances (23, 24, 25) de pression peuvent être soumis, dans le sens de la fermeture, à une pression de commande, qui règne dans une chambre (26) de commande arrière, qui est dérivée de la pression d'alimentation régnant dans la conduite (13) d'alimentation à l'aide d'un dispositif (45, 52) de valves et qui varie en fonction de la pression d'alimentation.
  2. Un dispositif de commande selon la revendication n° 1, caractérisé en ce que la différence entre la pression d'alimentatiori et la pression de commande n'est pas supérieure à la différence entre la pression d'alimentation et la pression en charge la plus élevée, tant que la pompe (10) à cylindrée variable n'est pas encore déplacée jusqu'en butée (cas de saturation).
  3. Un dispositif de commande selon la revendication n° 1 ou n° 2, caractérisé en ce que le dispositif de valves est constitué d'une valve (45, 52) à différence de pression, qui est raccordée par une entrée (46) à la conduite (13) d'alimentation et par une sortie (47) à la chambre (26) de commande arrière d'une balance (23, 24, 25) de pression.
  4. Un dispositif de commande selon la revendication n° 3, caractérisé en ce que la valve (45, 52) à différence de pression est calibrée sur une différence de pression fixe et présente un élément (48) de valve mobile, qui est soumis à la pression d'alimentation dans le sens d'une ouverture de la connexion fluide entre la conduite (13) d'alimentation et la chambre (26) de commande au niveau de la balance (23, 24, 25) de pression et qui est sollicité par la pression de commande et par un ressort (49) dans le sens d'une fermeture de cette connexion.
  5. Un dispositif de commande selon une revendication précédente, caractérisé en ce que les chambres (26) de commande arrière de plusieurs balances (23, 24) de pression communiquent directement les unes avec les autres, de façon à ce que la même pression de commande règne dans les chambres (26) de commande arrière de ces balances (23, 24) de pression.
  6. Un dispositif de commande selon une revendication précédente, caractérisé par une conduite (37) de signalisation de charge, dans laquelle règne, au moyen de valves (36) de sélection, la pression en charge la plus élevée des récepteurs (14, 15, 16) hydrauliques actionnés à un instant donné, et par une valve (51), qui ouvre une connexion fluide de la conduite (37) de signalisation de charge vers la chambre (26) de commande arrière d'au moins une balance (23, 24) de pression, lorsque la différence entre la pression d'alimentation et la pression en charge la plus élevée est inférieure à une valeur donnée.
  7. Un dispositif de commande selon la revendication n° 6, caractérisé en ce que la valve entre la conduite (37) de signalisation de charge et la chambre (26) de commande arrière est un clapet (51) anti-retour, qui ouvre dans le sens de cette chambre (26) de commande arrière.
  8. Un dispositif de commande selon une revendication précédente, caractérisé en ce qu'un premier dispositif (45) de valves permet d'établir, à partir de la pression de la pompe, une pression de commande pour la chambre (26) de commande arrière de la première balance (23, 24) de pression et un second dispositif (52) de valves permet d'établir, à partir de la pression de la pompe, une pression de commande pour la chambre (26) de commande arrière d'une autre balance (25) de pression et qu'est prévue une valve (55) de priorité, qui permet d'élever la pression de commande dans la chambre (26) de commande arrière de la première balance (23, 24) de pression au-dessus de la pression de commande en cas de saturation, afin de maintenir une différence de pression souhaitée au niveau de l'orifice (19) d'étranglement disposé en amont de l'autre balance (25) de pression, et donc une alimentation en fluide de pression suffisante du récepteur (16) hydraulique correspondant, prioritaire, lorsque le débit refoulé par la pompe (10) à cylindrée variable ne correspond pas au besoin (en cas de sous-saturation).
  9. Un dispositif de commande selon la revendication n° 8, caractérisé en ce que la valve (55) de priorité présente un premier raccord (56) relié à la conduite (13) d'alimentation et un second raccord (57) relié à la chambre (26) de commande arrière de la première balance (23, 24) de pression et possède un élément de valve, qui, dans le sens de l'ouverture de la connexion entre le premier raccord (56) et le second raccord (57), peut être soumis à la pression régnant dans un segment de conduite en aval de l'orifice (19) d'étranglement dédié au récepteur (16) hydraulique prioritaire et à une force additionnelle et, dans le sens de la fermeture de la connexion entre le premier raccord (56) et le second raccord (57), peut être soumis à la pression d'alimentation.
  10. Une valve de différence de pression, en particulier pour utilisation dans un dispositif de commande selon une des revendications précédentes, caractérisée par les caractères distinctifs suivants :
    a) un corps (70) de valve présente un alésage (71) de valve, à l'intérieur duquel débouchent, dans la direction radiale, un canal (46) d'entrée et, à une certaine distance axiale de celui-ci, un canal (47) de sortie ;
    b) à l'intérieur de l'alésage (71) de valve, dans la direction axiale, peut coulisser un tiroir (48) distributeur, qui permet de commander une section d'ouverture au niveau du canal (46) d'entrée et qui, sur une première face, peut être soumis à la pression régnant dans le canal (46) d'entrée et, sur sa seconde face, peut être soumis à la pression régnant dans le canal (47) de sortie ;
    c) une chambre (75) de ressort, qui est située entre l'une des faces du tiroir (48) distributeur et une fermeture (72) de l'alésage (71) de valve, héberge un ressort (49) de pression, qui sollicite le tiroir (48) distributeur dans le sens d'une réduction de la section d'ouverture ;
    d) le canal (47) de sortie débouche librement dans la chambre (75) de ressort ;
    e) le tiroir (48) distributeur est un tiroir creux doté d'alésages (81, 82, 83), qui relient par voie fluide une chambre (80) annulaire, formée entre le tiroir (48) distributeur et le corps (70) de valve et présentant une arête de commande périphérique pour la commande de la section d'ouverture au niveau du canal (46) d'entrée, à la chambre (75) de ressort, et doté de deux segments d'étanchéité, qui sont guidés dans l'alésage (71) de valve de façon à faire étanchéité à chaque instant, desquels l'un des segments d'étanchéité isole le canal (46) d'entrée de la chambre (75) de ressort et l'autre segment d'étanchéité isole le cheminement (80, 82, 81, 83) du fluide traversant le tiroir (48) distributeur de la première face du tiroir (48) distributeur.
  11. Une valve de différence de pression selon la revendication n° 10, caractérisée en ce que le ressort (49) de pression vient s'étayer contre une vis (72) de fermeture, qui est vissée dans l'alésage (71) de valve et qui referme l'alésage (71) de valve.
  12. Une valve de différence de pression selon la revendication n° 10 ou n° 11, caractérisée en ce que l'alésage (71) de valve présente un diamètre plus grand dans la zone de la chambre (75) de ressort que dans la zone située de part et d'autre du canal (46) d'entrée.
  13. Une valve de différence de pression selon la revendication n° 12, caractérisée en ce que le corps (70) de valve est une cartouche, dotée d'un alésage (71) de valve ouvert au niveau de la première face du tiroir (48) distributeur, et que le tiroir (48) distributeur est conçu sous forme de tiroir étagé, dont le segment de diamètre supérieur peut solliciter une épaule intérieure de l'alésage (71) de valve, dans le sens du côté ouvert de l'alésage (71) de valve.
EP00906203A 1999-02-05 2000-01-15 Dispositif de commande pour au moins deux consommateurs hydrauliques, et soupape a pression differentielle correspondante Expired - Lifetime EP1149246B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19904616 1999-02-05
DE19904616A DE19904616A1 (de) 1999-02-05 1999-02-05 Steueranordnung für wenigstens zwei hydraulische Verbraucher und Druckdifferenzventil dafür
PCT/EP2000/000294 WO2000046513A1 (fr) 1999-02-05 2000-01-15 Dispositif de commande pour au moins deux consommateurs hydrauliques, et soupape a pression differentielle correspondante

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EP1149246A1 EP1149246A1 (fr) 2001-10-31
EP1149246B1 true EP1149246B1 (fr) 2005-01-05

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US (1) US6644025B1 (fr)
EP (1) EP1149246B1 (fr)
JP (1) JP4739529B2 (fr)
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WO (1) WO2000046513A1 (fr)

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Publication number Publication date
WO2000046513A1 (fr) 2000-08-10
US6644025B1 (en) 2003-11-11
EP1149246A1 (fr) 2001-10-31
JP2002536599A (ja) 2002-10-29
JP4739529B2 (ja) 2011-08-03
DE19904616A1 (de) 2000-08-10
DE50009158D1 (de) 2005-02-10

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