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EP1736671A2 - Système de commande à détection de charge et valve directionnelle à détection de charge - Google Patents

Système de commande à détection de charge et valve directionnelle à détection de charge Download PDF

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Publication number
EP1736671A2
EP1736671A2 EP06010425A EP06010425A EP1736671A2 EP 1736671 A2 EP1736671 A2 EP 1736671A2 EP 06010425 A EP06010425 A EP 06010425A EP 06010425 A EP06010425 A EP 06010425A EP 1736671 A2 EP1736671 A2 EP 1736671A2
Authority
EP
European Patent Office
Prior art keywords
pressure
control
chamber
valve
channel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06010425A
Other languages
German (de)
English (en)
Other versions
EP1736671A3 (fr
EP1736671B1 (fr
Inventor
Armin Stellwagen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1736671A2 publication Critical patent/EP1736671A2/fr
Publication of EP1736671A3 publication Critical patent/EP1736671A3/fr
Application granted granted Critical
Publication of EP1736671B1 publication Critical patent/EP1736671B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation 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
    • F15B2211/305—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
    • F15B2211/365—Directional control combined with flow control and pressure 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
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a 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
    • F15B2211/50—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
    • F15B2211/50—Pressure control
    • F15B2211/575—Pilot pressure control
    • F15B2211/5753—Pilot pressure control for closing a valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—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
    • F15B2211/654—Methods of control of the load sensing pressure the load sensing pressure being lower than the load pressure

Definitions

  • the invention relates to a LS control arrangement according to the preamble of patent claim 1 and a suitable for such a control arrangement LS-way valve.
  • Such LS control arrangements are for example from the DE 197 15 020 A1 or from the published by the applicant data sheet RD 64 282 (control block M4) and are used, for example, in mobile work equipment to provide their consumers with pressure medium.
  • Each of the consumers is assigned an LS directional control valve, via which the speed and the direction of the pressure medium volume flow conveyed by a pump are controlled.
  • the pump pressure is adjusted in LS systems so that it is above the maximum load pressure of the consumer by a certain control ⁇ p, for example 20 bar.
  • the pressure medium volume flow over a set by an inlet control edge of the LS-way valve inlet orifice is kept constant independent of the load in the mentioned known solutions by a LS or individual pressure compensator.
  • a pressure compensator piston of the individual pressure compensator is biased by a spring in the opening direction, in addition to the force of the spring acts downstream of the inlet orifice metered load pressure also in the opening direction.
  • In the closing direction of the pressure compensator piston acts upstream of the inlet orifice and downstream of the individual pressure compensated tapped inlet pressure.
  • the individual pressure compensator upstream of the inlet orifice plate in principle, the individual pressure compensator also as in one of the US Pat. No. 4,787,294 known Embodiment be arranged downstream of the inlet orifice.
  • the individual pressure compensator responds to changes in load pressure and is displaced in the closing direction at a load pressure increase in the opening direction and at a load pressure reduction.
  • the pressure in the inlet to the inlet orifice plate is regulated by the individual pressure compensator in such a way that the force acting in the closing direction by this inlet pressure is in equilibrium with the force of the spring acting on the opening direction and the force equivalent of the load pressure. Accordingly, the pressure in the inlet is always adjusted by the constant, the spring force corresponding amount higher than the load pressure, so that above the inlet orifice a constant pressure drop and thus a constant flow exists (load pressure independent flow control).
  • the load pressure at the two load ports of a piston axis each by a pressure relief valve can be individually limited to protect the consumer-side machine equipment, the load pressure at the two load ports of a piston axis each by a pressure relief valve.
  • this pressure relief valve responds, the actual load pressure is forfeited to the individual pressure compensator, so that the above-described volume flow control can be disabled for the consumer connection.
  • the pressure medium volume flow set via the inlet metering orifice can be reduced, for example, if the consumer is driven against a high resistance, which would actually require an inlet pressure above the set maximum pressure. In this case, however, the inlet pressure will not exceed the value set on the pressure relief valve by more than the spring force. Because every consumer connection has a pressure relief valve is assigned, different pressure settings can be set for each consumer connection.
  • operating conditions may occur in which different maximum pressures must be achieved in a direction of movement of the consumer at different operating speeds. For example, it may be necessary to run the consumer at a higher speed with only a low pressure, but at a lower speed with a higher pressure.
  • z. B. causes the speed of a lowering movement of a crane jib by a so-called flow rate control.
  • a lowering brake valve is opened by the inlet pressure in the hydraulic cylinder determining the movement of the crane jib. Since the opening pressure of the lowering brake valve has an influence on the lowering speed of the crane jib, this opening pressure must be kept as constant as possible in order to avoid possible vibrations.
  • the above-described pressure relief valve can be set to limit the load pressure, so that the inlet volume flow control is ineffective when the pressure relief valve is triggered. By the kinematics of the crane boom, however, this can be moved when lowering into positions in which a higher pressure is required than the set opening pressure.
  • the present invention seeks to provide an LS control arrangement and a suitable LS-way valve, which allow a multi-stage supply pressure limitation.
  • a LS control oil flow path for tapping the load pressure is successively or overlapping connected to two pressure limiting chambers when adjusting a valve spool of the LS-way valve in one direction, each of which a pressure relief valve is assigned to LS-pressure limitation.
  • the load pressure can be limited to different values in different stroke ranges of the valve slide so that a supply pressure limitation in the manner described above is made possible.
  • the maximum pressure in the pressure limiting chamber connected to the LS control oil flow path during a first partial lift is set to a higher pressure than that in the second pressure limiting chamber, which is effective during a subsequent partial stroke.
  • the valve spool has a pressure limiting channel which forms part of the LS control oil flow path.
  • This pressure limiting channel opens on the one hand during the adjustment of the valve spool in one direction in a connected to the associated load port working control chamber and on the other hand during the first partial stroke of the valve spool in the first pressure limiting chamber during the second partial stroke in the second pressure limiting chamber.
  • a Lastabgriffsdüse is formed in the pressure limiting channel between the load tap and the pressure relief valve.
  • the valve spool is of particularly simple construction if two spaced peripheral recesses are formed on its outer circumference, in each of which a nozzle channel passing through the pressure limiting passage communicates with the valve spool, ie the pressure limiting channel is during the first partial stroke via the first peripheral recess and the associated first nozzle channel the first pressure-limiting chamber and during the further partial stroke via the second circumferential recess and the second nozzle channel is connected to the second pressure-limiting chamber.
  • the start of operation and the functional range of the second pressure relief valve can then be determined by the position and length of the peripheral recesses in the valve spool.
  • This very simple Construction makes it possible to realize the LS directional control valve with the exception of the control piston with series components.
  • peripheral recesses are preferably designed as pockets for minimizing leaks.
  • the LS control chamber In the neutral position of the LS-way valve, the LS control chamber is connected to a drain chamber via one of the pressure-limiting chambers and a tank groove on the valve slide.
  • the load pressure is picked up via an LS channel and reported to the LS control chamber.
  • peripheral recesses are designed such that they shut off the connection between the LS control chamber and the pressure limiting chambers when adjusting the valve spool in the second adjustment direction, wherein during a relatively small stroke, a connection may still be approved.
  • valve spool is particularly simple when the LS channel and the pressure limiting channel open on the one hand in the same piston collar.
  • This piston collar can be designed with a control edge over which the first pressure limiting chamber is connected to a drain chamber in the second partial stroke of the valve slide.
  • the individual pressure compensator of LS control arrangement of the metering orifice may be connected upstream, wherein a pressure compensator piston in the opening direction of a pressure compensator spring and the limited Load pressure and in the closing direction of the pressure in the area between the individual pressure compensator and the metering orifice is acted upon.
  • FIG. 1 shows a schematic circuit diagram of a valve disk of a mobile control block, by means of which a piston axis is formed to supply the pressure medium to a consumer, for example an actuating cylinder of a crane jib.
  • a mobile control block has an input member, an end member, and a plurality of directional control elements each associated with a consumer of the mobile implement.
  • the illustrated in Figure 1, a LS control arrangement 1 forming the directional control valve element valve block has a pressure port P, two consumer ports A, B, a drain port T and a control oil drain Y.
  • a LS connection forming the directional control valve element valve block has a pressure port P, two consumer ports A, B, a drain port T and a control oil drain Y.
  • a LS connection connections to Tapping of the individual load pressure at the load connections and with control connections.
  • the LS control arrangement 1 has a continuously adjustable directional control valve 2, an individual pressure compensator 4 and two adjustable pressure relief valves 6, 8 for limiting the load pressure.
  • the basic structure of such a LS control arrangement is already known from the prior art described above (RD 64 282), so that only the components essential for understanding the invention are described here.
  • the continuously adjustable directional control valve 2 has a valve slide 10 which is biased by a centering spring, not shown, in its basic position shown in Figure 1 0.
  • the valve spool 10 can be moved electrically or hydraulically from its illustrated basic position to the left (working positions A) or to the right (working positions B).
  • a hydraulic pilot control pressure reducing valves can be used, for example, to pressurize the valve spool 2 for adjusting with a control pressure difference.
  • the valve spool 10 is guided in a valve bore 12 of the valve disc.
  • the valve spool 10 is executed with four control circuits, wherein the right in Figure 1 control collar as tank collar 30, the two central piston collars as Control collar 32 and control collar 34 and the left in Figure 1, slightly longer piston collar is referred to as end collar 38.
  • the aforementioned bundles are spaced from each other by piston necks.
  • the tank collar 30 closes the valve bore 12 to the right frontally to a spring or control chamber, not shown.
  • a control control edge 40 designed with fine control notches and an inlet control edge 42 are formed on the other annular end face. Accordingly, a further feed control edge 44 and a further flow control edge 46 are provided on the second control collar 34.
  • the inlet control edges 44, 42 block the pressure medium connection from the inlet chamber 18 to the two adjacent working chambers 16 , 20 off. Their connection to the outer drainage chambers 14, 22 is locked in the basic position 0 by the two flow control edges 40, 46.
  • the tank control edge 48 is located within the second discharge chamber 22, which is connected via a circumferential tank groove 50 on the outer circumference of the end collar 38 with the adjacent pressure-limiting chamber 24.
  • On the outer circumference of the end collar 38 are further provided two pocket-shaped or flattened circumferential recesses 52, 54, the circumferential recess 52 having a greater axial length than the further circumferential recess 54.
  • the illustrated basic position opens the smaller circumferential recess 54 in the LS control chamber 26, the larger circumferential recess 52 connects the pressure limiting chamber 24 with the LS control chamber 26th
  • the valve spool 10 is penetrated by a pressure limiting channel 56 which is drilled in the illustrated embodiment of the left end face of the end collar 38 ago as axially parallel bore and closed by a sealing plug 58.
  • the pressure limiting channel 56 extends in the axial direction of the basic position 0 to beyond the working chamber 20 and then flows through a Lastabgriffsdüse 60 in the outer periphery of the control collar 34.
  • the Lastabgriffsdüse 60 is covered by the annular web between the chambers 18, 20 and thus closed ,
  • the pressure-limiting channel 56 also opens out via a first radial nozzle channel 62 in the larger circumferential recess 52 and via a second radial nozzle channel 64 in the smaller circumferential recess 54 (nozzle channels radially). Accordingly, in the home position, the LS control chamber 26 and the right pressure limiting chamber 24 and the pressure limiting channel 56 are connected to the drain chamber 22 and thus pressure relieved.
  • This Lastabgriffsbohrung 70 is covered by the web between the inlet chamber 18 and the working chamber 16 in the basic position 0.
  • the inlet chamber 18 is connected via an inlet channel 72 to an outlet port A of the individual pressure compensator 4, the input port P is connected via a pump channel 74 with a LS-pump 76, which as Variable or can be designed as a constant pump with bypass pressure compensator.
  • the control of this LS pump 76 is carried out - as stated - depending on the highest load pressure of the driven loads, the pump pressure is adjusted so that it is above the control ⁇ p above this highest load pressure.
  • the individual pressure compensator 4 is designed in the version shown with a load-holding function. This is achieved by blocking the connection between P and A in its spring-biased basic position as long as no pump pressure is built up. Such an individual pressure compensator 4 thus operates in the load holding function similar to a check valve.
  • the pump pressure in the pump channel 74 is tapped via a control line 78 and acts on the pressure compensator piston in the direction of its closing position indicated by (c) in FIG. In the opening direction, d.
  • the two working chambers 16, 20 are connected via a feed channel 82 and a return passage 84 to the load ports A, B.
  • the return passage 84 can also act as a flow channel and then correspondingly the flow channel 82 are in the pressure medium return.
  • the pressure limiting valve 6 is connected via a load pressure limiting channel 86 to the pressure limiting chamber 24, accordingly, the other pressure limiting chamber 28 via a further load pressure limiting channel 88 with the further pressure relief valve 8 connected.
  • This maximum pressure is executed in both pressure relief valves 6, 8 mechanically or electrically / hydraulically changeable.
  • the drain port T is connected via a drain passage 90 with the two drain chambers 14, 22.
  • valve spool 10 is moved to the left according to Figure 1, being traversed when passing through the total stroke, the positions A1, A2 and A3 shown in Figure 2.
  • connection of the pressure limiting channel 56 is opened with the working chamber 20 via the Lastabgriffsdüse 60 before the Zulaufberichtkante 44 opens the connection between the inlet chamber 18 and the working chamber 20 and the flow control edge 40, the pressure medium connection between the drain chamber 14 and connected to the load port B working chamber 16 opens.
  • the Lastabgriffsbohrung 70 remains covered by the bridge between the chambers 16, 18.
  • the connection between the drainage chamber 22 and the first pressure-limiting chamber 24 which is opened by the tank groove 50 in the basic position is also shut off.
  • the LS control chamber 26 is over the larger circumferential recess 52 with the Pressure limiting chamber 24 connected and thus also the pressure limiting channel 56 connected to the LS control chamber 26 - ie, in the LS control chamber 26 and in the pressure limiting chamber 24, the pressure in the working chamber 20 is reported with the pressure relief valve closed.
  • an inlet orifice plate between the inlet chamber 18 and the working chamber 20 is opened via the inlet control edge 44 and conveyed in accordance with pressure medium to the consumer port A.
  • the flowing away from the consumer pressure fluid flows through the consumer port B, the return passage 84, the up-regulated by the flow control edge 40 drain cross section between the working chamber 16 and the drain chamber 14 to the tank T out.
  • the load pressure building up downstream of the inlet orifice plate is then reported via the load tap nozzle 60, the pressure limiting channel 56, the first nozzle channel 62 and the longer circumferential recess 52 to both the LS control chamber 26 and the pressure limiting chamber 24 until the A2 position is reached.
  • the maximum load pressure building up in the pressure limiting chamber is limited by the pressure limiting valve 6, which is set to a higher pressure than the other pressure relief valve 8.
  • the load pressure applied in the LS control chamber 26 is applied via the LS control line 80 to the pressure compensator piston of the individual pressure compensator 4 in the opening direction.
  • the individual pressure compensator 4 operates in the manner described in the introduction and regulates a pressure in the inlet channel 72 which is always higher by a value corresponding to the constant amount of the force of the pressure compensator spring 80 than the individual one Load pressure, so that the pressure drop across the inlet orifice kept constant independent of the load pressure can be and thus depends only on the opening cross-section.
  • the load pressure effective in the opening direction on the individual pressure compensator can not exceed this preset maximum value, so that the inlet pressure in the inlet channel 72 is correspondingly limited.
  • the pressure relief valve 6 is effective, so that the inlet pressure is limited to a relatively high value at low pressure medium flow rate.
  • the connection between the pressure limiting chamber 24 and the LS control chamber 26 is shut off via the longer recess 52 and via the smaller circumferential recess 54 the connection of the pressure limiting channel 56 to the left pressure limiting chamber 28 via the further nozzle channel 64 turned on.
  • the tapped via the Lastabgriffsdüse 60 load pressure is also reported via the first nozzle channel 62 in the LS control chamber 26, but since this is not connected to the pressure limiting chambers 24, 28 in the positions A2, A3, flows from the LS control chamber 26 virtually no Control oil, so that no pressure drop over the first nozzle channel 62.
  • the maximum load pressure in the pressure limiting channel 56 and thus in the LS control chamber 26 is limited in the positions A2, A3 by the set to a lower pressure relief valve 8, whose input is connected via the load pressure limiting channel 88 to the pressure limiting chamber 28.
  • the Lastabgriffsdüse 60 ensures that even when the pressure relief valve 8 is open via the first nozzle channel 62 is not directly the load pressure is reported, since the control oil flow through the open pressure relief valve 8 at the Lastabgriffsdüse 60, a pressure drop.
  • the actual pressure in the pressure limiting channel 56 and thus in the LS control chamber 26 is thus somewhat above the maximum pressure set at the pressure limiting valve 8 - its set value is adjusted until the desired maximum load pressure is reached. Accordingly, when the pressure limiting valve 8 responds, the inlet pressure is set to a lower value at a higher pressure medium volume flow.
  • the connection between the drain chamber 22 and the pressure-limiting chamber 24 is opened via the tank control edge 48, so that the latter is pressure-relieved. Furthermore, in the above-described positions A1, A2, A3, the load tap hole 70 remains covered by the web between the inlet chamber 18 and the working chamber 16.
  • the function start and the functional range of the second pressure limiting valve are determined by the geometry of the circumferential recesses 52, 54.
  • the pressure limiting channel 56 is connected successively with the pressure limiting chamber 24 and the pressure limiting chamber 28 - it is also possible to connect the pressure limiting channel 56 with two pressure limiting chambers 24, 28 in a transition region - the pressure is then in any case limited to the lower, predetermined by the pressure relief valve 8 value.
  • the valve slide will move from its basic position 0 shown in FIG. 1 to the right in the direction of the positions B1, B2 Figure 3 moved.
  • the Lastabgriffsbohrung 70 opens to the with the consumer port B
  • the inlet orifice plate 42 is opened via the inlet control edge 42 between the inlet chamber 18 and the working chamber 16 and opened according to the flow control edge 46, a flow area between the working chamber 20 and the drain chamber 22.
  • the downstream of the inlet orifice in the working chamber 16 applied pressure is reported via the Lastabgriffsbohrung 70, the LS channel 66 and the radial bore 68 in the LS control chamber 26.
  • This load pressure is not limited, so that the individual pressure compensator 4 is always acted upon by the actual load pressure in the opening direction.
  • the load tap nozzle 60 remains covered by the web between the inlet chamber 18 and the working chamber 20, so that no load pressure can be tapped over it.
  • the individual pressure compensator can also be connected downstream of the metering orifice.
  • circumferential annular grooves can also be selected - although this variant can be produced more easily, it has the disadvantage that the leakage is increased.
  • an LS control arrangement and an LS directional control valve, via which the load pressure in an adjustment direction of the LS directional control valve can be limited to two different maximum values.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Servomotors (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Multiple-Way Valves (AREA)
  • Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)
  • Fluid-Driven Valves (AREA)
EP06010425A 2005-06-21 2006-05-19 Système de commande à détection de charge et valve directionnelle à détection de charge Not-in-force EP1736671B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005029028 2005-06-21
DE102005050169A DE102005050169A1 (de) 2005-06-21 2005-10-19 LS-Steueranordnung und LS-Wegeventil

Publications (3)

Publication Number Publication Date
EP1736671A2 true EP1736671A2 (fr) 2006-12-27
EP1736671A3 EP1736671A3 (fr) 2007-11-21
EP1736671B1 EP1736671B1 (fr) 2011-01-12

Family

ID=36992828

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06010425A Not-in-force EP1736671B1 (fr) 2005-06-21 2006-05-19 Système de commande à détection de charge et valve directionnelle à détection de charge

Country Status (4)

Country Link
EP (1) EP1736671B1 (fr)
AT (1) ATE495371T1 (fr)
DE (2) DE102005050169A1 (fr)
DK (1) DK1736671T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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DE102007054138A1 (de) 2007-11-14 2009-05-28 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102007054137A1 (de) 2007-11-14 2009-05-28 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102009041859A1 (de) * 2009-09-16 2011-03-24 Robert Bosch Gmbh Steuerschieber eines Hydraulikventils

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EP1069317A2 (fr) 1999-07-10 2001-01-17 Mannesmann Rexroth AG Tranche de distributeur hydraulique, surtout pour un véhicule automobile
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EP1069317A2 (fr) 1999-07-10 2001-01-17 Mannesmann Rexroth AG Tranche de distributeur hydraulique, surtout pour un véhicule automobile
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DE102005050169A1 (de) 2006-12-28
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ATE495371T1 (de) 2011-01-15
EP1736671A3 (fr) 2007-11-21
EP1736671B1 (fr) 2011-01-12

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