EP0582497B1 - Steuervorrichtung für mehrere hydraulische Verbraucher - Google Patents

Steuervorrichtung für mehrere hydraulische Verbraucher Download PDF

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Publication number
EP0582497B1
EP0582497B1 EP19930401786 EP93401786A EP0582497B1 EP 0582497 B1 EP0582497 B1 EP 0582497B1 EP 19930401786 EP19930401786 EP 19930401786 EP 93401786 A EP93401786 A EP 93401786A EP 0582497 B1 EP0582497 B1 EP 0582497B1
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EP
European Patent Office
Prior art keywords
pressure
constriction
upstream
chamber
regulation
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP19930401786
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English (en)
French (fr)
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EP0582497A1 (de
Inventor
Jean-Louis Claudinon
André Rousset
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Marrel SA
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Marrel SA
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • 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
    • F15B2211/20—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/31—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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31505—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and a return line
    • F15B2211/31511—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and a return line having a single pressure source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F15B2211/50527—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 using cross-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
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using check 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
    • F15B2211/6054—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
    • F15B2211/6058—Load sensing circuits with isolator 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust

Definitions

  • the invention relates to a control assembly for a plurality of hydraulic receivers, through which the receivers are supplied by the same generation of flow, each being connected thereto by means of a proportional distributor.
  • distributors are devices that are available between a flow generation and a receiver to control the operation of the receiver by adapting the way it is connected to the flow generation.
  • Proportional type distributors include not only a controlled drawer whose position determines the section of a constriction, but also an automatic compensating drawer to maintain constant the pressure difference between the upstream and downstream of this constriction, so that at a given position of the controlled slide corresponds to a given flow of fluid. Consequently, when a receiver is controlled with a proportional distributor, its operating speed is fixed by the position of the controlled drawer, independently of the load that the receiver supports.
  • the flow generation When the flow generation is used to supply a plurality of receivers to which each corresponds a proportional distributor, it may happen that the total flow requested by the receivers exceeds the maximum flow that the flow generation is able to supply.
  • the respective compensating drawers are no longer in able to maintain the pressure difference between the upstream and downstream of the throttle at the prefix constant in each of the distributors, so that the most loaded receivers slow down or stop while the least loaded ones can continue to operate .
  • FR-A-2.339.757 proposes to act on the actuation pressure of the slide controlled in each of the proportional distributors, by providing that the actuation valves are no longer supplied directly from a pilot pump, but with interposition between the pilot pump and the actuation valves of a maneuvering valve which varies the supply pressure of the control valves in the same way as the difference between the pressure of the flow generation and the pressure of load -sensing.
  • the supply pressure of the control valves remains constant, just as if these valves were supplied directly by the pilot pump.
  • FR-A-2.548.290 proposes to achieve the same result in the case where the proportional distributors have a compensating drawer which is located upstream of the controlled drawer, by acting on the actuating means of the compensating drawer: it continues to be used in the direction of closing by the pressure upstream of the controlled drawer and in the direction of opening by the pressure downstream of the controlled drawer, but the conventional spring is replaced by a double pressure stress, respectively in the direction of closing by the load-sensing pressure and in the opening direction by the pressure of the flow generation.
  • the pressure difference between the upstream and downstream of the throttle of the controlled slide is thus controlled by the difference between the pressure of the flow generation and the load-sensing pressure, which leads to the abovementioned result.
  • DE-A-4,036,720 proposes to take similar measures, but instead of being directly the difference between the pressure of the flow generation and the load-sensing pressure, the servo reference is obtained from these pressures through adjustment means, for example a pressure lowering valve disposed between the generation of flow and the compensating slide.
  • the invention also aims to obtain the aforementioned result, but with improved performance.
  • the assembly according to the invention differs from that described in the last prior art aforementioned by the presence of the auxiliary valve whose pressure produced is applied in place of the pressure of the flow generation.
  • the assembly according to the invention avoids this difficulty.
  • the invention also offers the advantage of being able to provide the desired result even if the generation of flow is not regulated as a function of the load supported by the receivers.
  • the assembly includes for each group an auxiliary valve adjacent to the group.
  • the distributor 70 illustrated in FIG. 1 is similar to that described in FR-A-2,562,632, with the exception of its pressure compensating device.
  • stator block 1 in the bore 2 of which slides a cylindrical controlled drawer 3.
  • switching of the hydraulic circuits is effected by displacement of the grooves of the drawer 3 in front of the lights of the stator.
  • the drawer 3 is provided with a spring return device of the type known, comprising a helical spring 4, compressed between the shoulders 5 and 6 of two rings 7 and 8, trapped between two shoulders of the end 9 of the drawer 3, around which they can slide.
  • a spring return device of the type known, comprising a helical spring 4, compressed between the shoulders 5 and 6 of two rings 7 and 8, trapped between two shoulders of the end 9 of the drawer 3, around which they can slide.
  • the drawer 3 is spontaneously returned to a neutral rest position, while it is pushed to the right (FIG. 1) when a pilot pressure is sent into an opening 10 of the fixed cap 61.
  • a pilot pressure is sent opposite, in an opening 11 of the cap 62 at its other end.
  • the three-position slide 3 is used to control a double-acting hydraulic cylinder 12.
  • one of the sections of the cylinder 12 is connected to a first channel use 13 of the stator 1, while the opposite section of the jack 12 is connected to a second use pipe 14 of the stator 1.
  • the distributor receives in an annular chamber 15, the pressure sent by a generation of flow 71.
  • the supply chamber 15 surrounds a compensating drawer 16, also called a balance, which is movable in a bore 80 of the stator 1.
  • the drawer 16 is provided with a radial bore 22 communicating with a blind axial bore 23.
  • the latter opens onto a seat capable of being closed off or unmasked by a ball 24 whose return spring 25 is compressed inside the compensating drawer 16.
  • the chamber containing the ball 24 and the spring 25 opens out through a lateral opening 26 in a chamber ring 27 surrounding the central part of the controlled drawer 3.
  • the controlled slide 3 has an axial internal housing, 28 on the left, 29 on the right.
  • the housing 28 communicates with the outside of the drawer by two radial bores referenced respectively 30 and 31. Likewise, the housing 29 opens onto two radial bores 32 and 33.
  • the bore 32 is closed at rest, by a solid part 37, located between two annular chambers 38 and 39.
  • the chamber 38 communicates with the second use pipe 14, while the chamber 39 is connected to the return circuit .
  • the stator defines, in the bore, a solid part 40, in front of which is capable of moving a groove 41 of the drawer 3.
  • annular stator chamber 42 Around the drawer 3, in the zone situated around the bore 31 when the drawer 3 is pushed to the right (FIG. 1), there is an annular stator chamber 42.
  • the drawer 3 has a groove 43 movable in front of a solid part 44 of the stator.
  • a solid part 44 of the stator Around the passage 33 when the drawer 3 is pushed to the left, there is an annular stator chamber 45.
  • the two chambers 42 and 45 are connected by a pipe 46 called the load sensing pipe.
  • a first booster valve 52 is mounted in parallel on the first use pipe 13.
  • a booster valve 53 is mounted in parallel on the second user pipe 14. Behind the valves 52 and 53, is finds a chamber 54 connected to the oil return circuit.
  • a pressure relief valve, respectively 55 and 56, is provided on the side of each of the use pipes 13, 14, which can thus flow into the return chambers, respectively 36, 39.
  • the chambers 27, 35 and 38 are closed, so that the jack 12 is immobilized while no flow passes through the distributor.
  • the pipe 46 communicates through the grooves 41 and 43 respectively with the chamber 36 and the chamber 39, that is to say that it is connected to the return circuit.
  • the slide 3 slides to the right with an amplitude determined by the value of the pilot pressure, which is balanced with the opposing thrust of the spring 4, more or less compressed.
  • the supply pressure of the chamber 27 is sent into the line 13 through the groove 49 and the chamber 35, while the line 14 communicates with the return chamber 39 through the groove 51.
  • Each of the grooves 49 and 51 determines a throttle whose section is determined by the position of the slide 3.
  • the pipe 46 communicates on the left with the pipe 13 through the passages 31, 28 and 30, while on the right it is closed. The pressure downstream of the throttle provided by the groove 49 is thus transmitted to the pipe 46.
  • the slide 3 slides to the left to a position determined by the amplitude of the pilot pressure.
  • the supply pressure of the chamber 27 is sent into the line 14 passing through the groove 50 and the chamber 38, while the line 13 communicates with the return chamber 36 through the groove 48.
  • Each of the grooves 48 and 50 determines a constriction, the section of which is determined by the position of the drawer 3.
  • the pipe 46 communicates on the right with the pipe 14 by the holes 33, 29 and 32, while on the left it is closed. The pressure downstream of the throttle provided by the groove 50 is thus transmitted to the pipe 46.
  • the circuit selector 99 (also called OR function) has one of its inputs which communicates with the pipe 46 by a channel 72, and its other input which communicates with a channel 73 connected to the output pipe of the circuit selector d '' a similar distributor.
  • the pressure in the line 46 is the highest, so that the circuit selector 99 adopts the illustrated position where it transmits by its output to the line 74 the operating pressure of the cylinder 12, which is the pressure of highest use of all the receivers supplied by the flow generation 71. More generally, as is clear from FIG. 2, it is always the pressure of the most loaded receiver which is applied to the pipe 74, this so-called "load sensing" pressure being transmitted to the generation of flow 71 which produces an operating pressure normally equal to the load sensing pressure increased by a constant.
  • the compensating slide 16 comprises around the channel 22 a groove 111 which produces, depending on the position of the slide, a more or less significant constriction upstream of the constriction provided by the slide 3 on the supply line of the jack 12, depending on the position taken by the drawer 16.
  • This comprises two active surfaces, on the left a surface 112 subjected to the pressure upstream of the throttle provided by the slide 3, and on the right a surface 301 subjected to the pressure prevailing in the pipe 46, that is to say tell the operating pressure of the jack 12.
  • a piston 114 movable coaxially, which comes into contact with the drawer compensator by a stud, and slides in a cylinder 116 screwed into the stator 1 coaxially with the bore 80, the cylinder 116 being open on the internal side and closed on the external side, and sealingly passing through the pipe 46.
  • the piston 114 has an L-shaped passage which makes it possible to communicate the chamber 115 situated between the piston and the bottom of the cylinder with the pipe 119, which is connected to the load-sensing pipe for the generation of flow, so that it is brought to the load sensing pressure.
  • the piston 114 has two opposite surfaces, a surface 121 facing the active surface 112 of the drawer 16, and subjected to the same pressure, and an active surface 123 subjected to the load sensing pressure.
  • a spring 125 applies the piston 114 against the drawer 16.
  • This comprises on the right a third active surface 302 which is subjected to the pressure produced by an auxiliary valve 303.
  • the surfaces 301 and 302 look to the right, and the pressures to which they are subjected urge the drawer 16 in the direction of opening.
  • the surface 301 is subjected to the pressure prevailing downstream of the throttle provided by the slide 3 because it is disposed in the pipe 46, and the surface 302 is subjected to the pressure produced by the valve 303 because it is disposed in a chamber 304 connected by a pipe 305 to the valve 303.
  • the surfaces 112 and 123 look to the left, the pressures to which they are subjected therefore urge the drawer 16 in the closing direction.
  • S 2 the effective value of this difference in active surfaces, which for convenience will call “dimensioning of the active surface 112”
  • S 1 the effective value of the active surface 123.
  • the effective value of the active surface 301 is also S 2 , and that of the active surface 302 is S 1 .
  • the auxiliary valve 303 comprises a stator body 306 which defines a supply chamber 307 connected to the discharge orifice of the flow generation 71; a regulation chamber 308 in which P ls prevails; an outlet chamber 309 where said pressure produced prevails; a drawer 310 whose position determines, thanks to a groove 311, the section of a constriction between the chambers 307 and 309; and a spring 312 which acts on the slide 310 in the opening direction, a screw 313 being provided to adjust the force with which the spring acts.
  • the drawer 310 comprises a first active surface 314 disposed in the chamber 308, and therefore subject in the direction of opening to P ls and a second active surface 315 disposed in the chamber 309, which means that the pressure produced acts on the surface 315 in the closing direction.
  • the pressure produced is therefore normally independent of the pressure supplied by the flow generation.
  • the proportional distributors of the control assembly are divided into several groups of a distributor or of several neighboring distributors, the groups being distant from each other, for example in the case of a public works machine, divided into a first group of two distributors which control the right and left engines for advancing the vehicle, a second group of a single distributor which controls the rotation of a turret, and a third group of several distributors which control the different arms of the vehicle, it is preferable to provide an auxiliary valve for each of the groups, not only to avoid pressure drop problems, but also to avoid having to provide a pipe between a centralized auxiliary valve and the different groups.
  • FIG. 2 shows a control assembly according to the invention, formed of a single group of two contiguous distributors, respectively the distributor 70 illustrated in FIG. 1, and an identical distributor 70 ', all the elements of the latter carrying the same reference as distributor 70, but assigned a prime index.
  • the proportional distributor 170 shown in FIG. 3 includes a compensating drawer 116, the left part of which is different from that of the drawer 16: in the position illustrated in FIG. 3, the compensating drawer 116 closes the passage between the chambers 15 and 27, but when it moves to the left it produces, depending on its position, a more or less significant constriction upstream of the constriction provided by the slide 3 on the supply line of the jack 12.
  • the drawer 116 has two surfaces 83 and 300 subjected to the pressure upstream of the throttle provided by the drawer 116, an active surface 84 subjected to the pressure upstream of the throttle provided by the drawer 3, and an active surface 85 subjected to the pressure prevailing in a chamber 86 located to the left of the drawer 116.
  • the surfaces 83 and 300 are opposite and have the same dimensioning, the slide 116 therefore does not react to the pressure upstream of the constriction which it provides.
  • the surface 84 is subjected to the pressure prevailing upstream of the constriction provided by the drawer 3 because it is disposed in a chamber 91 communicating with the room 27 via a duct 92.
  • the drawer 116 is provided with a radial bore 93 communicating with a blind axial bore 94 which opens onto a seat capable of being closed off or unmasked by a ball 95 whose return spring 96 is compressed in a chamber 98 which opens out an axial opening 100 in the chamber 86.
  • This communicates via a passage 101 with a pipe 102 closed at one end and opening into the flow generation reservoir through a restriction 104 at the other end, the pipe 102 being common to all distributors, who have their room corresponding to 86 which is connected to it.
  • the surface 84 has a similar dimension to the surface 301, that is to say S 2
  • the surface 85 has a similar dimension to the surface 302, that is to say S 1 .

Claims (10)

  1. Steuereinheit für eine Mehrzahl von hydraulischen Verbrauchern (12, 12'), durch welche hindurch die Verbraucher von derselben Druckfluidquelle (71) aus versorgt werden, indem jeder über einen Proportionalverteiler angeschlossen ist, mit
    - einem Steuerschieber (3), dessen Stellung den Querschnitt eines ersten Steuerspalts bestimmt,
    - einem Ausgleichsschieber zur Regulierung der Differenz zwischen den Drücken vor und hinter dem ersten Steuerspalt durch Bereitstellung eines zweiten Steuerspalts mit geeignetem Querschnitt in Strömungsrichtung vor dem ersten Steuerspalt, und
    - Betätigungsmitteln für den Ausgleichsschieber, um ihn automatisch eine Stellung einnehmen zu lassen, in der er den zweiten Steuerspalt mit geeignetem Querschnitt bereitstellt in Abhängigkeit von:
    dem Druck hinter dem ersten Steuerspalt und einem ersten, in Öffnungsrichtung wirkenden Druck, und
    dem Druck vor dem ersten Steuerspalt und einem zweiten, in Schließstellung wirkenden Druck;
    wobei die Steuereinheit zusätzlich ein Hilfsventil aufweist, das durch die Druckfluidquelle (71) versorgt wird und einen Druck erzeugt, welcher einen solchen ersten Druck darstellt, dadurch gekennzeichnet, daß
    - jeder zweite Druck ein Regeldruck ist, der von den Belastungsbedingungen der hydraulischen Verbraucher abhängt;
    - jeder erste Druck durch ein solches Hilfsmittel (303) erzeugt ist;
    - jedes solches Hilfsmittel, ausgehend von seiner Versorgung und dem Regeldruck, mit dem es direkt beaufschlagt ist, einen Druck erzeugt, der normalerweise gleich ist dem um eine Konstante erhöhten Regeldruck;
    - in jedem Proportionalverteiler (70, 70', 170, 170') die Betätigungsmittel des Ausgleichsschiebers so ausgebildet sind, daß er auch durch eine im wesentlichen konstante Kraft in Schließstellung belastet ist.
  2. Steuereinheit nach Anspruch 1, dadurch gekennzeichnet, daß in jedem Proportionalverteiler die Betätigungsmittel für den Ausgleichsschieber auf diesem eine erste, mit dem Druck hinter dem ersten Steuerspalt beaufschlagte erste Steuerfläche (301), eine zweite, mit dem vom Hilfsventil erzeugten Druck beaufschlagte Steuerfläche (302), eine dritte, mit dem Druck vor dem ersten Steuerspalt beaufschlagte Steuerfläche (84, 112) und eine vierte, mit dem Regeldruck beaufschlagte Steuerfläche (85, 123) aufweisen, wobei die erste und die zweite Steuerfläche (301, 302) entgegengesetzt gerichtet sind zur dritten und vierten Steuerfläche (84, 85; 112, 123), sowie eine den Ausgleichsschieber (16, 116) in Schließrichtung belastende Feder (87, 125).
  3. Steuereinheit nach einem der Anspruch 2, dadurch gekennzeichnet, daß die erste und die dritte Steuerfläche (301, 84; 301, 112) des Ausgleichsschiebers (16, 116) gleich bemessen sind, und daß die zweite und die vierte Steuerfläche (302, 85; 302, 123) des Ausgleichsschiebers dieselbe Größe haben.
  4. Steuereinheit nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß das Hilfsventil (303) aufweist:
    - eine an die Druckfluidquelle (71) angeschlossene Versorgungskammer (307),
    - eine Regelkammer (308), in welcher der Regeldruck herrscht,
    - eine Auslaßkammer (309), in der der erzeugte Druck herrscht,
    - einen Schieber (310), dessen Stellung den Querschnitt eines Steuerspalts zwischen der Versorgungskammer (307) und der Auslaßkammer (309) bestimmt und der eine erste, derart in der Regelkammer (308) gelegene Steuerfläche aufweist, daß der Regeldruck in Öffnungsrichtung wirkt, sowie eine zweite, derart in der Auslaßkammer (309) gelegene Steuerfläche (315) hat, daß der erzeugte Druck in Schließrichtung wirkt, und
    - eine Feder (312), die in öffnungsrichtung auf den Schieber (310) wirkt.
  5. Steuereinheit nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Proportionalverteiler in mehrere aus einem oder mehreren benachbarten Verteilern bestehende Gruppen aufgeteilt sind, welche mit Abstand zueinander angeordnet sind, und daß sie für jede Gruppe ein dieser benachbart angeordnetes Hilfsventil aufweist.
  6. Steuereinheit nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß sie Lastabfühlung ("load-sensing") genannte Lasterkennungsmittel (73, 74, 99, 99') für den Druck des am stärksten belasteten Verbrauchers aufweist und der Regeldruck der Druck der Lastabfühlung ist.
  7. Steuereinheit nach Anspruch 6, dadurch gekennzeichnet, daß die Lasterkennungsmittel für jeden Proportionalverteiler eine Leitung aufweisen, welche die Leitung hinter dem ersten Steuerspalt mit einem Auswahlschalter (99, 99') zur Auswahl eines Schaltkreises verbindet, und daß im Falle von mehreren Schaltkreis-Auswahlschaltern diese kaskadenartig angeordnet sind.
  8. Steuereinheit nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß sie Mittel (95, 95', 102, 104) zum Erkennen des höchsten der vor dem ersten Steuerspalt in den jeweiligen Proportionalverteilern (170, 170') herrschenden Drücke aufweist und daß der Regeldruck der höchste so erkannte Druk ist.
  9. Steuereinheit nach Anspruch 8, dadurch gekennzeichnet, daß die Proportionalverteiler (170, 170') ohne Rückschlagventile zwischen dem zweiten und dem ersten Steuerspalt ausgebildet sind.
  10. Steuereinheit nach einem der Ansprüche 8 oder 9, dadurch gekennzeichnet, daß die Mittel zum Erkennen des höchsten der vor den jeweiligen ersten Steuerspalten herrschenden Drücke eine gemeinsame, an einem ersten Ende geschlossene Leitung (102), die am anderen Ende über eine Drosselstelle (104) in das Druckfluidreservoir mündet, und für jeden Proportionalverteiler ein Rückschlagventil (95) aufweisen, welches von der Zuleitung zum ersten Steuerspalt aus zu der gemeinsamen Leitung hin zu öffnen ist.
EP19930401786 1992-08-04 1993-07-08 Steuervorrichtung für mehrere hydraulische Verbraucher Expired - Lifetime EP0582497B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9209658 1992-08-04
FR9209658A FR2694605B1 (fr) 1992-08-04 1992-08-04 Ensemble de commande d'une pluralité de récepteurs hydrauliques.

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EP0582497A1 EP0582497A1 (de) 1994-02-09
EP0582497B1 true EP0582497B1 (de) 1996-10-30

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JP (1) JPH06159310A (de)
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JP3531758B2 (ja) * 1994-06-27 2004-05-31 株式会社小松製作所 圧力補償弁を備えた方向制御弁装置
JP3549126B2 (ja) * 1994-08-05 2004-08-04 株式会社小松製作所 方向制御弁
KR100226281B1 (ko) * 1994-09-30 1999-10-15 토니헬샴 가변우선장치
US5937645A (en) * 1996-01-08 1999-08-17 Nachi-Fujikoshi Corp. Hydraulic device
US6202014B1 (en) 1999-04-23 2001-03-13 Clark Equipment Company Features of main control computer for a power machine
JP4805027B2 (ja) * 2006-05-30 2011-11-02 ナブテスコ株式会社 ローダ用油圧制御装置
US8621855B2 (en) * 2007-06-08 2014-01-07 Deere & Company Electro-hydraulic auxiliary mode control

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US3987622A (en) * 1976-02-02 1976-10-26 Caterpillar Tractor Co. Load controlled fluid system having parallel work elements
US4165613A (en) * 1978-03-27 1979-08-28 Koehring Company Control apparatus for a plurality of simultaneously actuatable fluid motors
DE3321483A1 (de) * 1983-06-14 1984-12-20 Linde Ag, 6200 Wiesbaden Hydraulische einrichtung mit einer pumpe und mindestens zwei von dieser beaufschlagten verbrauchern hydraulischer energie
FR2562632B1 (fr) * 1984-04-18 1986-12-12 Bennes Marrel Distributeur hydraulique du type proportionnel, avec prise d'informations concernant les plus fortes pressions dans les circuits d'utilisation
DE3532816A1 (de) * 1985-09-13 1987-03-26 Rexroth Mannesmann Gmbh Steueranordnung fuer mindestens zwei von mindestens einer pumpe gespeiste hydraulische verbraucher
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DE4036720C2 (de) * 1990-11-17 2001-09-13 Linde Ag Steuerschaltung für die lastunabhängige Aufteilung eines Druckmittelstromes
FR2672944A1 (fr) * 1991-02-15 1992-08-21 Bennes Marrel Distributeur proportionnel et ensemble de commande d'une pluralite de recepteurs hydrauliques comportant pour chaque recepteur un tel distributeur.

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JPH06159310A (ja) 1994-06-07
US5386697A (en) 1995-02-07
DE69305708D1 (de) 1996-12-05
EP0582497A1 (de) 1994-02-09
FR2694605A1 (fr) 1994-02-11
DE69305708T2 (de) 1997-05-28
FR2694605B1 (fr) 1994-11-10

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