EP3236085B1 - Vanne amplificatrice pour un circuit hydraulique de travail conçu comme circuit à centre fermé d'un engin de travail utilisable dans l'agriculture ou les travaux publics - Google Patents

Vanne amplificatrice pour un circuit hydraulique de travail conçu comme circuit à centre fermé d'un engin de travail utilisable dans l'agriculture ou les travaux publics Download PDF

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Publication number
EP3236085B1
EP3236085B1 EP17160538.9A EP17160538A EP3236085B1 EP 3236085 B1 EP3236085 B1 EP 3236085B1 EP 17160538 A EP17160538 A EP 17160538A EP 3236085 B1 EP3236085 B1 EP 3236085B1
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EP
European Patent Office
Prior art keywords
valve
line
signal line
pressure
control
Prior art date
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Active
Application number
EP17160538.9A
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German (de)
English (en)
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EP3236085A1 (fr
Inventor
Thomas Fedde
Manfred Kirchhoff
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Claas Industrietechnik GmbH
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Claas Industrietechnik GmbH
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Publication of EP3236085A1 publication Critical patent/EP3236085A1/fr
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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
    • 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
    • F15B2211/6057—Load sensing circuits having valve means between output member and the load sensing circuit using directional control 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/653—Methods of control of the load sensing pressure the load sensing pressure being higher than the 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups

Definitions

  • the invention relates to one which generates an amplified secondary load pressure signal by means of a pump pressure of a pressure line due to a primary load pressure signal generated by one or more controllers in a primary load signal line, the amplifier valve having a primary load pressure signal and a booster spring on the one hand and the amplified secondary load pressure signal on the other hand having controllable control valve, the input side is connected to the pressure line and the output side with a shut-off valve.
  • the invention also relates to a working hydraulics of a land or building usable vehicle to which vehicle in its rear and / or front area a hydraulic adjusting and / or drive system having attachments are coupled, wherein a hydraulic system of the respective attachment by means of a hydraulic coupling system the working hydraulics can be connected and both within the work hydraulics and within the hydraulic system each control units are assigned functionally, wherein in the working hydraulics, a variable is provided whose delivery volume in response to a load pressure of the hydraulic load of the working hydraulics and the implement associated hydraulic system adjustable is, is provided as part of the regulation of the variable displacement pump at least one hydraulic load signal line which is connected to the control units, and wherein between a secondary Lastsig naltechnisch, which is connected to the arranged within the working hydraulics control units, and a primary load signal line which is connected to the control units of the hydraulic system, a consisting of a control valve and a shut-off valve amplifier valve is arranged, which due to a generated by one of the control units of the hydraulic system primary Loa
  • variable-displacement pumps which in the meantime only supply a volume flow and pressure which is appropriate to the demand.
  • the variable displacement pump is controlled by a so-called load-sensing system, which consists of a load signal line and a pressure compensator associated with the adjustment of the variable displacement pump.
  • load signal line is from each of the control valves, which are assigned to the individual consumers of the working hydraulics, the highest load pressure reported to the pressure compensator and the variable only builds the load pressure plus a small pressure surplus.
  • variable displacement pump is pivoted back into a stand-by state, as soon as the control valves are in their neutral position and demand no flow.
  • the pump pressure settles so that the pressure difference ⁇ p LS between the load pressure p LS of the pressure compensator and the delivery pressure of the pump p p always remains the same. If one or more valves are actuated, the pressure is passed on via the load signal line to the pressure compensator, which determines the energy requirement of the system by comparing the load pressure p LS and the pump pressure p p . Pump pressure and pump flow are always automatically adapted to the respective requirements.
  • the respective highest load pressure p LS is reported by the corresponding control valve to the variable displacement pump, whereupon the variable displacement pump only builds up the load pressure plus a low pressure surplus (rule - ⁇ p).
  • the pump flow is divided by the use of so-called section pressure compensators regardless of the various load pressures on the consumer, as it corresponds to the ratio of the opening cross-sections of the control valves.
  • the hydraulic coupling system for the implements can also be designed as a power beyond connection, in which case the pressure line is connected via a corresponding remote coupling with the implement and there is a corresponding switching valve for controlling the hydraulic functions on the implement.
  • power beyond connections can be provided in their front and rear areas, in which there is also a three-point power lift for receiving the respective implement.
  • the power beyond connection system When this power beyond connection is combined with a load sensing system, the power beyond connection system is expanded to include a connector for a primary load signal line leading to the implement controllers.
  • This ensures that the variable displacement pump of the agricultural vehicle supplies the control valves of the attachment only with pressure medium when the corresponding hydraulic power is needed. Therefore, this system regulates the flow rate and pressure to meet the needs.
  • the load pressure In the primary load signal line, the load pressure increases as the operator of the implement retrieves one of its hydraulic functions.
  • considerable pressure losses can occur in the connection elements between the pump and the attachment so that the control variable for the hydraulic pump ⁇ p LS collapses. This has the consequence that the variable displacement pump can not provide sufficient volume flow.
  • such pressure losses can also occur in the working hydraulics of the agricultural or construction-economical vehicle, since many hydraulic functions are activated at the same time during working operations.
  • An intensifier valve for a trained as a closed-center system working hydraulics of a land or building economics usable machine of the type specified in the preamble of claim 1 is known from the EP 1-843-047-A2 or from the DE 11 2004 002 768 B4 known.
  • FIGS. 3 to 8 This document discloses a hydraulic control system in which an implement is operated via power beyond ports.
  • the respective load pressure of the load can be reported as a load-sensing signal via a load signal line to the control system.
  • the control system has means to influence at least one of the load-sensing signals.
  • a compensating valve and a shut-off valve existing compensator In order to change the load-sensing signal such that the consumer or consumers receive a larger flow of oil, resulting in a rapid action of the consumer or the consumer should result, a compensating valve and a shut-off valve existing compensator is provided.
  • the compensation valve should lift a load sensing pressure applied to it by a fixed amount .DELTA.p, the sum of the load-sensing pressure and the fixed amount .DELTA.p representing the corrected load-sensing pressure.
  • the shut-off valve should shut off the compensator when the load-sensing pressure applied to the compensation valve goes against a tank pressure.
  • FIGS. 7 and 8 of FIG DE 11 2004 002 768 B4 show an embodiment of the compensator, in which the shut-off valve shown in its two switching positions is connected downstream of the compensation valve.
  • the shut-off valve receives on the input side a corrected by the compensation valve pressure.
  • the shut-off valve does not control the compensation valve in the sense of its shutdown.
  • the compensation valve should always generate the increase of the pressure in the load-sensing line LS 1 or LS 40 by the amount ⁇ p, ie not only when the consumer is in operation and the pressure in the load-sensing line LS 1 or LS 40 represents the load of the consumer.
  • the booster valve amplifies a load pressure signal (p LS ) generated by one or more controllers in a primary load signal line by means of a pressure increase from a pressure line.
  • the booster valve has a controllable on the one hand via the load pressure signal and an amplifier spring and on the other hand via an amplified load pressure signal control valve, said control valve is connected on the input side to the pressure line and the output side with a shut-off valve.
  • the primary load signal line, the secondary load signal line, leading to a control of the control valve signal line and a return to the tank should be connected to one another in a designed as a blocking position first working position of the shut-off valve.
  • the relief according to the invention integrated in the shut-off valve via the return has the advantage that the amounts of oil that are permanently withdrawn from the primary and the secondary load signal line, are very low. Consequently, it is achieved that the volume of oil withdrawn from the volume flow is very low and a delay-free control, both of the booster valve and an adjustment of a closed-center system operated variable pump is possible.
  • the relief member after the DE 11 2004 002 768 B4 arranged directly in a branch of the primary load signal line wherein the relief member may be formed as a diaphragm or flow control valve.
  • An orifice would dissipate a large amount of oil at a high load-sensing pressure while the amount of oil drained from the flow regulator would be constant regardless of the load-sensing pressure. Accordingly, the document teaches that when the consumer is not driven, the load-sensing pressure in the primary load signal line corresponds to the pressure pT in the tank line due to the relief member. In the process, a considerable volume of oil flows into the tank via the tank line.
  • the shut-off valve is designed as a 5/2-way valve, which blocks an output side of the control valve provided connecting line in its first switching position and the secondary load signal line with both the primary load signal line and serving to control the control valve signal line and a return connects and which connects in its second switching position, the connecting line to the secondary load signal line and the primary load signal line with both the signal line and the return.
  • the amplified load pressure signal is supplied, which is locked in the first switching position relative to the secondary load signal line.
  • the amplified load pressure signal is forwarded to the secondary load signal line.
  • the primary load signal line is always connected to the control valve controlling the signal line and the return line in combination.
  • control valve is pilot-controlled via the shut-off valve, wherein the primary load pressure signal is transmitted via the shut-off valve in the two switching positions on the signal line.
  • an end face of a spool of the control valve in each switching position of the shut-off valve via the signal line with the load pressure signal is applied, this being connected in a flow position of the shut-off additionally with a controlled return and in a blocking position of the shut-off valve with a controlled return and with the secondary load pressure line is.
  • the control pressure of the signal line acts on the front side of the spool of the control valve, wherein the spool at this first end face is acted upon by the force of an amplifier spring whose spring preload is variable.
  • shut-off valve is acted upon exclusively with the delivery pressure p p of the variable. Consequently, the control valve on the input side, that is not supplied via a working port, a load pressure and this transmitted together with the pump pressure to the shut-off valve.
  • control valve is designed as a 3/3-way valve having a blocking position and two working positions, wherein in the first working position, the pressure line is connected to the connecting line leading to the shutdown valve and wherein in the second working position, the connecting line and between the control valve and the shut-off valve extending signal line are interconnected.
  • From the connecting line branches off a control line via which the spool of the control valve is acted upon at a second end face, ie in the first working position of the control valve with the amplified load pressure signal.
  • the increased load pressure is thus adjusted via the spring bias of the spool by means of the booster spring. In the second operating position of the control valve, this connects the signal line to the control line, so that the primary load pressure acts on both sides of the control slide.
  • a diaphragm and an oil filter can be arranged, these, starting from the consumer, the shut-off valve, ie its control and its corresponding working port are connected upstream.
  • control valve and the shut-off valve may be arranged within a common valve housing, which is preferably designed as a plate-like way valve block.
  • a corresponding directional valve block may be sandwiched together with further directional control valve blocks, this arrangement being ultimately closed by a cover plate.
  • a spool of this control valve has a blind bore extending in the axial direction and two transverse to this control bores, wherein the spool on the front side a trained as a coil spring booster spring is acted upon, whose spring preload is adjustable via a trained as a set screw actuator.
  • the shut-off valve should be designed such that its valve slide is formed as a hollow piston and is provided in its outer circumferential surface with a control groove, via which the connecting line to the secondary load signal line is connectable, and that via an interior of the valve spool and provided in this transverse holes in both switching positions of Valve spool the primary load pressure line is connected to both the control line and the return line.
  • the design of the valve spool provided in the shut-off valve makes it possible for the primary load-pressure line to be connected to the secondary load-pressure line at the same time as the front-end pressurization of the valve spool via its interior and at least one transverse bore in its blocking position.
  • a hydraulic control system for a working hydraulics of a land or building economy usable vehicle should be provided, to the vehicle in its rear and / or front area attachments can be coupled, which have a hydraulic actuator and / or drive system.
  • a hydraulic system of the respective attachment by means of a hydraulic coupling system with a hydraulic circuit of the working hydraulics can be connected, both within the hydraulic circuit and within the hydraulic system hydraulic consumers each control devices are assigned functionally.
  • a variable displacement pump is provided in the hydraulic circuit, the delivery volume in response to a load pressure of the hydraulic load of the hydraulic circuit and the implement associated hydraulic system is regulated, wherein at least one hydraulic load signal line is provided as part of the regulation of the variable, which is connected to the control units.
  • an amplifier valve is to be arranged, which is generated due to one of the control units of the hydraulic system primary load pressure signal from a pump pressure of a pressure line generates a secondary load pressure signal.
  • This booster valve should, as stated above, be arranged and constructed within the hydraulic control system.
  • FIG. 1 denotes a working hydraulics, which is provided for example for an agricultural tractor or an agricultural system vehicle.
  • This working group 1 is designed as a closed-center system, in which the pressure medium from a tank 2 via a variable displacement pump 3, preferably as an axial piston unit is designed according to the bent axis principle, two as a double-acting hydraulic cylinders 4 and 5 trained consumers 6 and 7 supplies.
  • the hydraulic cylinders 4 and 5 are associated with control devices 8 and 9, which are designed as electromagnetically operated, provided with spring centering 4/4-way valves.
  • the hydraulic cylinders 4 and 5 may be provided, for example, each for lifting devices of a front and a rear linkage.
  • the pressure medium is conveyed by the variable displacement pump 3 via a pressure line 10 to the control units 8 and 9, where it can get into corresponding positions of these control units 8 and 9 in a return line 11 and thus back into the tank 2. In this position, the respective control units 8 and 9 whose working lines 12, 13, 14 and 15 are shut off.
  • the delivery volume of the variable displacement pump 3 can be adjusted, for which purpose a single-acting adjusting cylinder 16 is provided.
  • this adjusting cylinder 16 is connected to a secondary load signal line 17 via a pressure compensator 18 and a pressure regulator 19.
  • the secondary load signal line 17 is connected to each of the control units 8 and 9 in such a way that a pressure on the pressure compensator 18 can be passed through it, if via the respective control unit 8 or 9, a pressure medium applied to the hydraulic cylinder 4 or 5 takes place.
  • FIG. 1 is the variable displacement pump 3 in its standby mode, ie, in a variable displacement pump according to the bent axis principle, the corresponding axial piston unit is in a state with a small swing angle and thus low displacement volume.
  • the variable displacement pump 3 promotes only a very small amount of hydraulic oil and only builds up a low pressure.
  • the pump pressure p p settles in such a way that the pressure difference ⁇ p LS between the load pressure p LS of the pressure compensator 18 and the delivery pressure p p of the variable displacement pump 3 always remains the same.
  • variable displacement pump 3 is permanently adapted to the needs.
  • the efficiency is considerably greater, especially in the fine control range, than in a so-called open center system.
  • the actuating speeds of the consumers 6 and 7 is not influenced by changing load pressures, so that a countersteering is not required.
  • FIG. 1 Furthermore, a so-called power beyond connection system 24 is provided, which for the hydraulic connection of the working hydraulics 1 with a in the FIG. 2 shown hydraulic system 25 of an attachment is used.
  • the pressure line 10 has a remote port 26 labeled P, a primary load signal line 17 'having a remote port 27 labeled LS, and the return line 11 having a remote port 28 labeled T.
  • the in FIG. 2 shown hydraulic system 25 of the attachment corresponding lines with the aforementioned lines 10, 17, 11 are connected.
  • These are in the FIG. 2 correspondingly denoted by 10 ', 17 “and 11' and lead to control devices 29 and 30, which are associated with consumers 31 and 32.
  • the consumer 31 is a double-acting hydraulic cylinder 33, while the consumer 32 as a hydraulic motor 34th is trained.
  • a booster valve 37 which, in the event of actuation of the control devices 29 and / or 30 of the working device, increases a load pressure pSsecondary in the secondary load signal line 17 connected to the pressure compensator 18 should.
  • This pressure increase is necessary because the pressure losses between the variable displacement pump 3 and the hydraulic system 25 of the attachment due to the hydraulic couplings, hose lines, etc. may be greater than the control variable ⁇ p LS , so that a maximum flow for the supply of the load 31 and 32 not more can be provided.
  • the booster valve 37 consists of a control valve 38 and a shut-off 39th
  • booster valve 37 may also be used when it is necessary to increase the primary load pressure for consumers who are part of the working hydraulics, as if no attachment hydraulically powered is coupled to the agricultural or construction vehicle.
  • booster valve 37 and its function is on the following FIGS. 3 and 4 directed.
  • FIGS. 3 and 4 each show an enlarged view of the hydraulic scheme of the booster valve 37 and its connection to the working hydraulics 1 and with the primary load signal line 17'.
  • FIGS. 3 and 4 characterized in that the shut-off valve 39 in the FIG. 3 in its second working position, namely a flow position, and in the FIG. 4 in its first working position, which corresponds to a blocking position is located.
  • the control valve 38 is designed as a 3/3-way valve, which is actuated hydraulically and in addition on a front side by spring force.
  • the corresponding switching positions of the control valve are in the FIGS. 3 and 4 with a middle position 0 and working positions a and b, wherein in the switching position a, which corresponds to a first working position, the pressure line 10 is connected to a leading from the control valve 38 to the shut-off valve 39 connecting line 40.
  • This switching position a takes the control valve 38 in both FIGS. 3 and 4 on. From the connecting line 40 branches off a control line 41, which acts on the control valve 38 at a first end face 42. At a second end face 43 of the control valve 38, this is acted upon via an amplifier spring 44, whose spring bias is variable, and via a signal line 45.
  • the signal line 45 is also connected via a line branch 45a to a working port of the control valve 38.
  • lines are formed as extending in a valve housing bores, cross sections, annular grooves, etc., which are therefore shown only in the hydraulic scheme as lines or line sections.
  • a diaphragm 46th located at the inlet of the pressure medium from the pressure line 10 in the control valve 38, a diaphragm 46th
  • the shut-off valve 39 is connected downstream of the control valve 38.
  • This shut-off valve 39 is designed as a 5/2-way valve and thus has two switching positions a and b.
  • the secondary load signal line 17 ', the primary load signal line 17, the signal line 45 and the return line 11 are connected to each other in this switching position a, ie the first working position.
  • the shut-off valve 39 in its switching position b, which represents a flow position. In this only the pressure fluid from the pressure line 10 into the secondary load signal line 17 passes.
  • the primary load signal line 17 ', the return line 11 and the signal line 45 are also connected to each other.
  • a throttle 47 is arranged in the switching position a.
  • FIGS. 3 and 4 shows that the shut-off valve is acted upon at one end face of the primary load pressure of the load signal line 17 'and thus is shifted at an increased primary load pressure in its switching position b.
  • a valve spring 49 and a pressure p T of the return line 11 act.
  • an aperture 50 and an oil filter 51 are arranged in the primary load signal line 17 '.
  • the booster valve 37 goes out of the FIG. 5 which shows this booster valve 37 in a longitudinal section.
  • the control valve 38 and the shut-off valve 39 each take a switching position, which with the FIG. 4 matches.
  • the booster valve 37 has a valve housing 52 which is designed as a plate-like way valve block.
  • receiving bores 53 and 54 are provided, wherein the receiving bore 53 receives a slidably guided in this control spool 55 of the control valve 38.
  • This spool 55 has a concentric blind bore 56 extending from the transverse control bores 57 and 58.
  • the pressure medium of the pressure line 10 passes through a connecting piece 59, the control bore 57 and the blind bore 56 in the connecting line 40.
  • the spool 55 is the end face, so applied to the end face 42 with the pressure of the connecting line 40 , On the side facing away from this end face other end face 43 of the spool 55 is acted upon by a spring plate 60 with the force of the booster spring 44.
  • This is arranged in a spring housing 61, wherein the spring preload can be changed via a trained as a set screw actuator 62.
  • the connecting line 40 communicates with the receiving bore 54, wherein in this receiving bore 54, a valve spool 63 of the shut-off valve 39 is slidably disposed.
  • a connecting piece 64 At the end of the receiving bore 54 is in this a connecting piece 64, to which the primary load signal line 17 'is connected, screwed.
  • the valve spool 63 is designed as a hollow piston and provided on its outer circumferential surface with a control groove 65.
  • FIG. 5 takes the valve spool 63 a position in which this shuts off the connecting line 40.
  • a connecting piece 66 for the return line 11 is screwed into this.
  • Transverse to the receiving bore 54 extends the secondary load signal line 17 which is inserted via a further connecting piece 67 in the valve housing.
  • this primary load signal line 17 via a transverse control bore 68 with a spring chamber 69 and thus the end face of the valve spool 63 as well as a longitudinal bore 70 of the valve spool 63 and the throttle 48 with the primary load signal line 17 'in connection.

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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)

Claims (13)

  1. Valve d'amplification (37) pour un moyen hydraulique de travail (1), conformé en système à centre fermé, d'une machine de travail utilisable en agriculture ou dans les travaux publics, laquelle, sur la base d'un signal de pression de charge primaire produit par un ou plusieurs appareils de commande (8, 9, 39, 30) sur une ligne de signal de charge primaire (17'), produit, au moyen d'une pression de pompe (pp) d'une ligne de pression (10), un signal de pression de charge secondaire amplifié, la valve d'amplification (37) comportant une valve de régulation (38) qui est commandable, d'une part, par l'intermédiaire du signal de pression de charge primaire et d'un ressort d'amplification (44) ainsi que, d'autre part, par l'intermédiaire du signal de pression de charge secondaire amplifié et qui est reliée, côté entrée, à la ligne de pression (10) ainsi que, côté sortie, à une valve de coupure (39), caractérisée en ce que, dans une première position de travail (a), conformée en position de fermeture, de la valve de coupure (39), sont reliés entre eux, à travers celle-ci, la ligne de signal de charge primaire (17'), une ligne de signal de charge secondaire (17), une ligne de signal (45) provoquant un actionnement de la valve de régulation (38) et un moyen de retour (11) dans un réservoir (2).
  2. Valve d'amplification selon la revendication 1, caractérisée en ce que la valve de coupure (39) est conformée en valve directionnelle à 5 voies/2 positions qui, dans sa première position de commutation (a), ferme une ligne de liaison (40) prévue côté sortie de la valve de régulation (38) et relie la ligne de signal de charge primaire (17') aussi bien à la ligne de signal de charge secondaire (17) qu'à une ligne de signal (45) servant à commander la valve de régulation (38) et à un moyen de retour (11) et qui, dans sa seconde position de commutation (b), relie la ligne de liaison (40) à la ligne de signal de charge secondaire (17) ainsi que la ligne de signal de charge primaire (17') aussi bien à la ligne de signal (45) qu'au moyen de retour (11).
  3. Valve d'amplification selon la revendication 2, caractérisée en ce que, dans la première position de commutation (a) de la valve de coupure (39), une liaison de la ligne de signal de charge primaire (17') à la ligne de signal de charge secondaire (17) et au moyen de retour (11) ainsi que, dans la seconde position de commutation (b) de celle-ci, une liaison de la ligne de signal de charge primaire (17') et de la ligne de signal (45) au moyen de retour (11) est restreinte.
  4. Valve d'amplification selon la revendication 1, caractérisée en ce que la valve de régulation (38) est précommandée par l'intermédiaire de la valve de coupure (39), le signal de pression de charge primaire étant transmis à la ligne de signal (45) par l'intermédiaire de la valve de coupure (39) dans les deux positions de commutation (a et b) de celle-ci.
  5. Valve d'amplification selon la revendication 1, caractérisée en ce que, dans chaque position de commutation (a et b) de la valve de coupure (39), un côté frontal (43) d'un tiroir de commande (55) de la valve de régulation (38) est soumis, par l'intermédiaire de la ligne de signal (45), au signal de pression de charge primaire, celui-ci étant en outre relié, dans une position de passage (b) de la valve de coupure (39), au moyen de retour commandé (11) et, dans une position de fermeture (a) de la valve de coupure (39), à un moyen de retour commandé (11) ainsi qu'à la ligne de pression de charge secondaire (17).
  6. Valve d'amplification selon la revendication 1, caractérisée en ce que, dans la position de commutation (a) de la valve de régulation (38) pour une élévation de pression de charge dans la ligne de signal de charge secondaire (17), la valve de coupure (39) est soumise exclusivement à la pression de refoulement pp de la pompe de réglage (3).
  7. Valve d'amplification selon la revendication 1, caractérisée en ce que la valve de régulation (38) est conformée en valve directionnelle à 3 voies/3 positions qui comporte une position de fermeture (0) et deux positions de travail (a et b), dans sa première position de travail (a) la ligne de pression (10) étant reliée à une ligne de liaison (40) conduisant à la valve de coupure (39), et dans sa seconde position de travail (b) la ligne de liaison (40) et une ligne de signal (45) s'étendant entre la valve de régulation (38) et la valve de coupure (39) étant reliées entre elles.
  8. Valve d'amplification selon la revendication 1 caractérisée en ce que sur la ligne de signal de charge primaire (17') est disposé un étrangleur (50) et un filtre à huile (51).
  9. Valve d'amplification selon la revendication 1, caractérisée en ce que la valve de régulation (38) et la valve de coupure (39) sont disposées dans un boîtier de valves commun (52) qui est conformé, de préférence, en bloc de valves directionnelles.
  10. Valve d'amplification selon la revendication 7, caractérisée en ce qu'un tiroir de commande (55) de la valve de régulation (38) comporte un perçage borgne (56) s'étendant dans la direction axiale et deux perçages de commande (57 et 58) s'étendant transversalement à celui-ci, le tiroir de commande (55) étant sollicité côté frontal par l'intermédiaire d'un ressort d'amplification (44) qui est conformé en ressort hélicoïdal et dont la précontrainte élastique est modifiable par l'intermédiaire d'un élément de réglage (62) conformé en vis de réglage.
  11. Valve d'amplification selon la revendication 2, caractérisée en ce qu'un tiroir de valve (63) de la valve de coupure (39) est conformé en piston creux et est pourvu, dans sa surface d'enveloppe extérieure, d'une rainure de commande (65) par l'intermédiaire de laquelle la ligne de liaison (40) peut être reliée à la ligne de signal de charge secondaire (17), et en ce que, par l'intermédiaire d'un espace intérieur du tiroir de valve (63) et par l'intermédiaire de perçages transversaux (68) ménagés dans celui-ci, la ligne de pression de charge primaire (17') est reliée aussi bien à la ligne de signal (45) qu'au moyen de retour (11) dans les deux positions de commutation du tiroir de valve (63).
  12. Valve d'amplification selon la revendication 11, caractérisée en ce que, dans la position de fermeture (a) du tiroir de valve (63), la ligne de pression de charge primaire (17') est reliée à la ligne de pression de charge secondaire (17) en présence d'une mise en pression frontale simultanée du tiroir de valve (63) par l'intermédiaire de son espace intérieur (70) et d'au moins un perçage transversal (68).
  13. Moyen hydraulique de travail (1) pour un véhicule utilisable en agriculture ou dans les travaux publics, audit véhicule pouvant être accouplé, dans sa zone arrière et/ou avant, un outil porté comportant des systèmes de réglage et/ou d'entraînement hydrauliques, un système hydraulique (25) de l'outil porté concerné pouvant être relié à un circuit hydraulique du moyen hydraulique de travail (1) à l'aide d'un système de couplage hydraulique (24), et des appareils de commande (8, 9, 29, 30) étant associés de manière fonctionnelle à des organes utilisateurs hydrauliques (6, 7, 31, 32) aussi bien à l'intérieur du circuit hydraulique qu'à l'intérieur du système hydraulique (25), dans le moyen hydraulique de travail (1) étant prévue une pompe de réglage (3) dont le volume refoulé est régulable en fonction d'une pression de charge (pLS) des organes utilisateurs hydrauliques du moyen hydraulique de travail (1) et du système hydraulique (25) associé à l'outil porté, dans le cadre de la régulation de la pompe de réglage (3) étant prévue au moins une ligne de signal de charge hydraulique (17, 17') qui est reliée aux appareils de commande (8, 9, 29, 30), et entre une ligne de signal de charge secondaire (17), qui est reliée aux appareils de commande (8 et 9) disposés à l'intérieur du moyen hydraulique de travail (1), et une ligne de signal de charge primaire (17'), qui est reliée aux appareils de commande (29 et 30) du système hydraulique (25), étant disposée une valve d'amplification qui, sur la base d'un signal de pression de charge primaire (pLSprimär) produit par un des appareils de commande (29 et 30) du système hydraulique (25), produit, au moyen d'une pression de pompe d'une ligne de pression (10), un signal de pression de charge secondaire, caractérisé par un agencement de la valve d'amplification à l'intérieur du circuit hydraulique du moyen hydraulique de travail et par sa conception selon une des revendications 1 à 12.
EP17160538.9A 2016-04-22 2017-03-13 Vanne amplificatrice pour un circuit hydraulique de travail conçu comme circuit à centre fermé d'un engin de travail utilisable dans l'agriculture ou les travaux publics Active EP3236085B1 (fr)

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DE102016107526.4A DE102016107526A1 (de) 2016-04-22 2016-04-22 Verstärkerventil für eine als Closed-Center-System ausgebildete Arbeitshydraulik einer land- oder bauwirtschaftlich nutzbaren Arbeitsmaschine

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Cited By (1)

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EP4173459A1 (fr) * 2021-10-29 2023-05-03 Deere & Company Système hydraulique pour véhicule agricole

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DE102018114495A1 (de) * 2018-06-18 2019-12-19 Claas Industrietechnik Gmbh Lastsignalsteuerung einer Arbeitshydraulik eines Anbaugeräts

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DE2159766A1 (de) * 1971-12-02 1973-06-07 Rexroth Gmbh G L Druckregelung mit verstellpumpe
WO2005093263A1 (fr) 2004-03-09 2005-10-06 Bucher Hydraulics Gmbh Systeme de commande hydraulique
GB2436856A (en) * 2006-04-07 2007-10-10 Agco Gmbh Pressure control for system with primary and secondary consumers

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Publication number Priority date Publication date Assignee Title
EP4173459A1 (fr) * 2021-10-29 2023-05-03 Deere & Company Système hydraulique pour véhicule agricole

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