EP3625457B1 - Dispositif de contrôle de l'approvisionnement d'au moins un consommateur hydraulique avec fluide - Google Patents

Dispositif de contrôle de l'approvisionnement d'au moins un consommateur hydraulique avec fluide Download PDF

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Publication number
EP3625457B1
EP3625457B1 EP18722442.3A EP18722442A EP3625457B1 EP 3625457 B1 EP3625457 B1 EP 3625457B1 EP 18722442 A EP18722442 A EP 18722442A EP 3625457 B1 EP3625457 B1 EP 3625457B1
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EP
European Patent Office
Prior art keywords
valve
control
control device
displacement pump
pressure
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Active
Application number
EP18722442.3A
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German (de)
English (en)
Other versions
EP3625457C0 (fr
EP3625457A1 (fr
Inventor
Heinz-Peter Huth
Marc Anton
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.)
Hydac Systems and Services GmbH
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Hydac Systems and Services GmbH
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Publication date
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Publication of EP3625457A1 publication Critical patent/EP3625457A1/fr
Application granted granted Critical
Publication of EP3625457C0 publication Critical patent/EP3625457C0/fr
Publication of EP3625457B1 publication Critical patent/EP3625457B1/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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/10—Other safety measures
    • F04B49/106—Responsive to pumped volume
    • 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
    • F15B2211/20538—Type of pump constant 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
    • F15B2211/205—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
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/265—Control of multiple pressure sources
    • F15B2211/2654—Control of multiple pressure sources one or more pressure sources having priority
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line

Definitions

  • the invention relates to a control device for supplying at least one hydraulic consumer with fluid with the features in the preamble of claim 1.
  • LS systems can be designed as a so-called open center system with constant pumps or as a so-called closed center system with variable pumps, as is the case with the control device mentioned above, which forms the subject of the application. Because of their energy-saving operation, LS systems are advantageously used to control components of the working hydraulics of mobile work equipment.
  • Such equipment such as agricultural tractors or soil cultivation devices, usually have several hydraulic consumers, such as travel drives, hydraulic steering, lifting drives and the like.
  • variable pump intended as a swivel pump must be designed for a maximum volume flow. If special or extreme work situations occur, for example when using a tractor for field cultivation, an undersupply may possibly occur during maneuvers at the end of the field, in which, in addition to the travel drive, the steering and processing devices with lifting drive simultaneously request the maximum volume flow.
  • the DE 10 2012 209 142 A1 describes a control device with the features in the preamble of claim 1 for supplying at least one hydraulic consumer with fluid with a variable pump that can be controlled by means of a load sensing pressure, whereby for a case-by-case increase in the volume flow in the inlet of the hydraulic consumer, the load sensing pressure is sent via a control line to a Control device is forwarded, which increases the inlet by switching on a constant pump as soon as an operator initiates the relevant function by actuating the control device, the control device having a first and a second control valve, of which the second control valve can be controlled by the operator.
  • the invention sets itself the task of providing a control device of the type mentioned at the outset, which enables a particularly functionally reliable supply of hydraulic consumers.
  • an essential special feature of the invention is that the first control valve can be controlled by the load sensing pressure in the control line.
  • the load sensing pressure is forwarded via a control line to a control device, which increases the inlet by switching on a fixed pump as soon as an operator activates the relevant amount by actuating the control device Function triggered.
  • This not only provides a type of boost function for extreme work situations, but at the same time provides protection against a possible threat to occupational safety, such as can be caused by an abrupt change in operating behavior when the constant pump is switched on.
  • the boost function is only activated by the operator can be initiated by the operator.
  • the first valve is a proportional valve, in particular a 2/2-way proportional valve, which is acted upon on one control side in addition to a spring preload with the load sensing pressure and on its other control side with the inlet pressure in the inlet of the respective hydraulic consumer.
  • the second valve to be actuated by the operator is advantageously an electromagnetically actuated switching valve, in particular a 2/2-way switching valve, which in its unactuated position releases a fluid path from the constant pump to a storage tank and in its actuated position triggered by the operator the corresponding one Fluid path blocks, so that in this activated state the volume flow of the fixed pump is available to increase the inlet.
  • the second valve can form a bypass to the first valve in that the inlet and the outlet of the first valve are connected to the inlet and the outlet of the second valve in a fluid-carrying manner.
  • the output of the constant pump can be connected via a branch point to the input of the first and second valves.
  • the inlet of the constant pump can be connected to the output of the variable pump via a connecting line into which a check valve is connected, in particular in the form of a spring-loaded check valve, which opens in the direction of the variable pump and in the direction of the constant pump closes.
  • the connecting line with the check valve and then a control line can be connected, which applies the inlet pressure to the first valve.
  • a pressure relief valve is connected in parallel to the second control valve in a bypass line, when the volume flow of the constant pump responds and is forwarded to the storage tank, bypassing the first and second valves.
  • control device can be designed as a control block which contains the first and second valves, the check valve and the pressure relief valve and which has connections for the fluid-carrying connection of the swivel angle pump serving as a variable displacement pump, the constant pump, the respective consumer, the storage tank and the load sensing control line.
  • the control device has a control device designated 2 in the figures, the components of which are combined to form a control block 4.
  • the control block 4 has a first input connection 6, which is connected to the output 8 of a variable displacement pump in the form of a swivel pump 10, which is connected to a storage tank 12 on the input side.
  • a second input connection 13 of the control block 4 is connected to the output 14 of a fixed displacement pump 16, which, like the swivel pump 10, can be driven by a motor and is connected to the storage tank 12 on the input side.
  • the constant pump 16 is present Example formed by a gear pump.
  • a demand-reporting LS signal can be fed to a third input connection 18 of the control block 4; more precisely, if there are several consumers to be supplied, the highest LS signal that occurs is fed via shuttle valves.
  • a first output connection 20 on the control block 4 leads to the consumer inlet 22, and a second output connection 24 leads to the storage tank 12.
  • the swivel pump 10 is part of a closed center system, which is otherwise not shown, so that the swivel angle is set via a pressure regulator DR in accordance with the LS signal.
  • a supply line is designated 26, which leads from the first input connection 6 to the first output connection 20 and thus to the inlet 22.
  • a control line that supplies the LS pressure from the third input port 18 to the control device 2 is designated 28.
  • the control block 4 contains a first control valve 30 and a second control valve 32, of which the first valve 30 is a 2/2-way proportional valve and the second valve 32 is a 2/2-way switching valve.
  • the latter can be actuated electromagnetically when triggered by an operator, and can be brought against the force of a return spring 34 from an unactuated switching position, which corresponds to the flow position, into an actuated switching position in which the valve 32 is blocked.
  • the first valve 30 is acted upon on the one hand by a compression spring 36 and with the respective LS pressure supplied via the control line 28 and on the other hand is acted upon by the inlet pressure prevailing in the supply line 26 via a further control line 38.
  • the output 14 of the fixed pump 16 is connected to the input 42 of the first valve 30 and to the input 44 of the second valve 32 via the second input connection 13 and via a branch point 40.
  • the second valve 32 is in the non-actuated switching position, the volume flow of the constant pump 16 is therefore diverted to the tank without being throttled.
  • the output 14 of the constant pump 16 is also connected via a connecting line 46 to the supply line 26 leading from the swivel pump 10 to the inlet 22, a check valve 48 being inserted into the connecting line 46, which opens in the direction of the supply line 26.
  • This connecting line 46 is connected to the supply line 26 in front of the control line 38, viewed in the direction of flow.
  • the first valve 30, like the second valve 32, is connected on the output side to the second output connection 24 of the control block 4 and thus to the storage tank 12.
  • the control block 4 is completed by a pressure relief valve 50, which secures the constant pump 16 to the storage tank 12 and is inserted as a bypass to the second valve 32 between its inlet 44 and its outlet 52 connected to the tank.
  • the Fig. 2 shows an operating state in which the constant pump 16 also makes no contribution to increasing the inflow quantity because the second valve 32 is again inactive, so that the volume flow of the constant pump 16 is diverted to the tank.
  • an LS pressure is effective at the first valve 30, which signals the need for additional supply to the inlet 22. Together with the effect of the compression spring 36, the first valve 30 is therefore controlled into the blocking state.
  • no volume of the pivot pump 16 flows out via the valve 30, since the second valve 32 is not actuated, a diversion takes place via this valve, so that the fixed pump 16 in turn makes no contribution to the supply.
  • an LS pressure is effective on the first valve 30 via the control line 28, which signals an additional supply, so that the first valve 30 is controlled into the blocking position.
  • the boost function is triggered by the operator by pressing the second valve 32 into the blocking position. In these valve positions, the entire volume flow of the constant pump 16 is fed into the supply line 26 via the branch point 40, the first check valve 48 and the connecting line 46 and increases the volume flow in the inlet 22. Since the boost function also increases when the LS pressure and the additional supply are requested thereby blocked first valve 30, as shown in Fig. 2 is shown, can only be triggered if the operator, as in Fig. 4 shown, the second Valve 32 is actuated, the invention provides a safety-enhancing hydraulic locking of the boost function.

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

Claims (9)

  1. Installation de commande pour alimenter en fluide au moins un consommateur hydraulique par une pompe (10) à cylindrée variable pouvant être commandée au moyen d'une pression loadsensing (LS), dans laquelle, pour une augmentation cas par cas du courant en volume dans l'arrivée (22) du consommateur hydraulique, la pression loadsensing (LS) est acheminée par un conduit (28) de commande à un dispositif (2) de commande qui, par mise en circuit d'une pompe (16) à cylindrée constante, effectue l'augmentation dans l'arrivée (22), dès qu'une personne provoque par actionnement du dispositif (2) de commande la fonction en question, dans laquelle le dispositif (2) de commande a une première (30) et une deuxième soupapes (32) pilotes, dont la deuxième soupape (32) pilote peut être commandée par la personne de service, caractérisée en ce que la première soupape (30) pilote peut être commandée par la pression loadsensing (LS) dans le conduit (28) de commande.
  2. Installation de commande suivant la revendication 1, caractérisée en ce que la première soupape est une soupape proportionnelle, en particulier une soupape (30) proportionnelle à 2/2 voies, qui est soumise sur l'un de ses côtés de commande, outre à une précontrainte (36) par un ressort, à la pression loadsensing (LS) et sur son autre côté de commande à la pression d'arrivée dans l'arrivée (22) du consommateur hydraulique respectif.
  3. Installation de commande suivant la revendication 1 ou 2, caractérisé en ce que la deuxième soupape est une soupape de commande pouvant être actionnée électromagnétiquement, en particulier une soupape (32) de commande à 2/2 voies qui, dans sa position non actionnée, dégage un chemin de fluide de la pompe (16) à cylindrée constante à un réservoir (12, T) et, dans sa position actionnée déclenchée par la personne de service, obture le chemin de fluide en question.
  4. Installation de commande suivant l'une des revendications précédentes, caractérisée en ce que la deuxième soupape (32) est montée en dérivation par rapport à la première soupape (30), par le fait que l'entrée (42) et la sortie (54) de la première soupape (30) sont raccordées fluidiquement à l'entrée (44) et respectivement à la sortie (52) de la deuxième soupape (32).
  5. Installation de commande suivant l'une des revendications précédentes, caractérisée en ce que la sortie (14) de la pompe (16) à cylindrée constante est raccordée par un point (40) de dérivation à l'entrée (42) et respectivement (44) de la première (30) et de la deuxième soupapes (32).
  6. Installation de commande suivant l'une des revendications précédentes, caractérisée en ce que la sortie (14) de la pompe (16) à cylindrée constante est raccordée à la sortie (8) de la pompe (10) à cylindrée variable par un conduit (46) de liaison, dans lequel est montée une soupape (48) d'arrêt, en particulier sous la forme d'un clapet antiretour soumis à l'action d'un ressort, qui ouvre dans la direction de la pompe (10) à cylindrée variable et ferme dans la direction de la pompe (16) à cylindrée constante.
  7. Installation de commande suivant la revendication 6, caractérisée en ce que, dans la liaison (26) entre la pompe (10) à cylindrée variable et le consommateur hydraulique respectif, sont raccordés d'abord le conduit (46) de liaison ayant la soupape (48) d'arrêt, et ensuite un conduit (38) de commande, qui alimente la première soupape (30) en la pression d'arrivée.
  8. Installation de commande suivant l'une des revendications précédentes, caractérisée en ce que, en parallèle à la deuxième soupape (32) pilote, est montée dans un conduit de dérivation une soupape (50) de limitation de la pression, dont le fonctionnement achemine le courant en volume de la pompe (16) à cylindrée constante au réservoir (12, T) en contournant la première (30) et la deuxième soupapes (32).
  9. Installation de commande suivant l'une des revendications précédentes, caractérisé en ce qu'elle est constituée sous la forme d'un bloc (4) de commande, qui comporte
    - la première (30) et la deuxième soupapes (32),
    - la soupape (48) d'arrêt et
    - la soupape (50) de limitation de la pression
    et qui a des raccords (6, 13, 20 ,24, 18) pour le raccordement fluidique de la pompe (10) à angle de pivotement prévue comme pompe à cylindrée variable, à la pompe (16) à cylindrée constante, au consommateur respectif, au réservoir (12, T) et au conduit (28) de commande loadsensing.
EP18722442.3A 2017-05-15 2018-04-27 Dispositif de contrôle de l'approvisionnement d'au moins un consommateur hydraulique avec fluide Active EP3625457B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017004634.4A DE102017004634A1 (de) 2017-05-15 2017-05-15 Steuervorrichtung zum Versorgen mindestens eines hydraulischen Verbrauchers
PCT/EP2018/060866 WO2018210550A1 (fr) 2017-05-15 2018-04-27 Dispositif de commande servant à alimenter au moins un consommateur hydraulique en fluide

Publications (3)

Publication Number Publication Date
EP3625457A1 EP3625457A1 (fr) 2020-03-25
EP3625457C0 EP3625457C0 (fr) 2023-12-06
EP3625457B1 true EP3625457B1 (fr) 2023-12-06

Family

ID=62116405

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18722442.3A Active EP3625457B1 (fr) 2017-05-15 2018-04-27 Dispositif de contrôle de l'approvisionnement d'au moins un consommateur hydraulique avec fluide

Country Status (6)

Country Link
US (1) US11168710B2 (fr)
EP (1) EP3625457B1 (fr)
JP (1) JP7130662B2 (fr)
CN (1) CN211448991U (fr)
DE (1) DE102017004634A1 (fr)
WO (1) WO2018210550A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3633188B1 (fr) * 2018-10-02 2021-07-14 Siemens Gamesa Renewable Energy A/S Circuit hydraulique à débit variable pour une éolienne
CN113266615B (zh) * 2021-06-23 2024-12-03 安百拓（南京）建筑矿山设备有限公司 集成控制阀及牙轮钻机钢丝绳张紧液压系统
DE102021130272A1 (de) * 2021-11-19 2023-05-25 Still Gesellschaft Mit Beschränkter Haftung Hydrauliksystem für ein Flurförderzeug
CN116104824A (zh) * 2023-01-29 2023-05-12 佛山市恒力泰机械有限公司 一种用于挤压设备的供油系统

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4559965A (en) * 1984-01-09 1985-12-24 J. I. Case Company Multiple compensating unloading valve circuit
DE4129508C2 (de) * 1991-09-05 1994-12-15 Rexroth Mannesmann Gmbh Ventilanordnung zur Versorgung eines Verbrauchers aus zwei Druckmittelquellen
JPH10266274A (ja) * 1997-03-27 1998-10-06 Hitachi Constr Mach Co Ltd 建設機械の油圧回路装置
JPH11115780A (ja) * 1997-10-15 1999-04-27 Komatsu Ltd 作業車両用ステアリングポンプの容量制御方法および装置
DE19906689A1 (de) * 1999-02-18 2000-08-24 Krupp Foerdertechnik Gmbh Hydraulikantrieb für Schwimmbagger
US6901754B2 (en) * 2003-10-01 2005-06-07 Husco International, Inc. Power conserving hydraulic pump bypass compensator circuit
JP2013044398A (ja) * 2011-08-24 2013-03-04 Komatsu Ltd 油圧駆動システム
GB201209109D0 (en) * 2012-05-24 2012-07-04 Agco Int Gmbh Pilot pressure supply system
DE102012209142A1 (de) 2012-05-31 2013-12-05 Putzmeister Engineering Gmbh Hydrauliksystem
DE102012011400A1 (de) * 2012-06-08 2013-12-12 Hydac System Gmbh Hydrauliksystem zur sicheren Druckversorgung mindestens eines Verbrauchers
DE102014004932B3 (de) * 2014-04-05 2015-05-13 Hydac Fluidtechnik Gmbh Schaltungsanordnung

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Publication number Publication date
DE102017004634A1 (de) 2018-11-15
JP7130662B2 (ja) 2022-09-05
EP3625457C0 (fr) 2023-12-06
CN211448991U (zh) 2020-09-08
US11168710B2 (en) 2021-11-09
JP2020519815A (ja) 2020-07-02
US20200095987A1 (en) 2020-03-26
EP3625457A1 (fr) 2020-03-25
WO2018210550A1 (fr) 2018-11-22

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