EP2287472B1 - Agencement hydraulique - Google Patents

Agencement hydraulique Download PDF

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Publication number
EP2287472B1
EP2287472B1 EP10172292.4A EP10172292A EP2287472B1 EP 2287472 B1 EP2287472 B1 EP 2287472B1 EP 10172292 A EP10172292 A EP 10172292A EP 2287472 B1 EP2287472 B1 EP 2287472B1
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EP
European Patent Office
Prior art keywords
hydraulic
consumer
line
supply
load pressure
Prior art date
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Active
Application number
EP10172292.4A
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German (de)
English (en)
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EP2287472A3 (fr
EP2287472A2 (fr
Inventor
Josef Peters
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.)
Deere and Co
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Deere and Co
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Publication date
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Publication of EP2287472A2 publication Critical patent/EP2287472A2/fr
Publication of EP2287472A3 publication Critical patent/EP2287472A3/fr
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Publication of EP2287472B1 publication Critical patent/EP2287472B1/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
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
    • 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
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority

Definitions

  • the invention relates to a hydraulic arrangement with a hydraulic pump and at least a first, second and third demand-controlled by the hydraulic pump via respective load pressure lines consumers, each consumer is connected by at least one control valve via its own supply line hydraulically parallel to the hydraulic pump and the first consumer a First level supply priority, the second consumer is assigned a first-level second-order supply priority and the third consumer is assigned a third-level supply priority to the second level.
  • hydraulic consumers with a higher priority level compared to hydraulic consumers with a lower priority level are primarily supplied hydraulically, if it comes to a hydraulic undersupply for operational reasons.
  • hydraulic consumers such as a hydraulically operated steering or hydraulically operated brake systems of a higher priority level than, for example, a hydraulically operated suspension on the vehicle.
  • This in turn may also belong to a higher priority level with respect to another hydraulic consumer, for example a hoist located on the vehicle. So often in a load pressure-dependent hydraulic system several priority levels for the different hydraulic consumers are taken into account.
  • priority control priority valves in the form of pressure compensators are used in hydraulic load-sensing systems, by which control a priority in the supply of individual hydraulic consumers in a hydraulic undersupply of the entire system.
  • the individual hydraulic consumers are each connected to at least one control valve, via which an inlet of the delivery volume flow is controlled by the hydraulic pump.
  • a priority valve In the inlet of each control valve is a priority valve, which is closed by a load pressure signal of a priority hydraulic consumer and reduces or throttles the volume flow to ensure the hydraulic supply of the priority valves.
  • a priority valve is used to implement two priority levels in the hydraulic systems or arrangements known in the art. For the realization of three priority levels, as mentioned above, thus usually two priority valves are needed.
  • a hydraulic arrangement according to the preamble of claim 1 is made DE 20 2004 010 530 U1 known.
  • the object underlying the invention is seen to provide a hydraulic arrangement of the type mentioned, by which the aforementioned problems are overcome.
  • a hydraulic arrangement of the type mentioned is designed such that for controlling the supply priority levels, the supply lines of the second and third consumers are connected via a connecting line and between the hydraulic pump and the connecting line in the supply line to the third consumer a load pressure controlled priority valve and in the supply line to second consumer volume flow reducing means are arranged, wherein further the Connecting line has means which block a volume flow from the second supply line in the direction of the third supply line.
  • a volumetric flow delivered by the hydraulic pump can be unrestricted via the first supply line to the first hydraulic consumer, via the priority valve, the connection line and the second supply line to the second hydraulic consumer and via the priority valve and the third supply line to the third reach hydraulic consumers.
  • the priority valve closes due to the connection to the load pressure lines and prevents or reduces a flowing through the priority valve to the second and third consumer flow.
  • the volume flow is passed through the second supply line via the volume flow reducing means, wherein a volume flow through the connecting line is blocked by the means arranged there.
  • the second hydraulic consumer will continue to be hydraulically powered regardless of the priority valve position, even if the priority valve should be fully closed, albeit with throttled flow.
  • a minimum supply of the second hydraulic consumer with a defined volume flow via the volume flow reducing means takes place. As a result, a pressure build-up for the second hydraulic consumer is possible and its minimum function is ensured.
  • the third hydraulic consumer is supplied with increasing closure of the priority valve with less and less volume flow, whereas the first hydraulic consumer continues to be supplied with maximum volume flow.
  • Due to the Volume flow reducing means is the first hydraulic consumer over the second hydraulic consumer to a higher supply priority.
  • the second hydraulic consumer also enjoys a higher supply priority than the third hydraulic consumer since a minimum flow rate is secured to the second supply line, even though the priority valve should be fully closed.
  • three priority levels are realized using only one priority valve.
  • the volume flow reducing means can be preset such that a minimum volume flow to the second consumer is ensured and at the same time it is ensured that in no operating condition a supply of the first hydraulic consumer can occur due to an outflowing volume flow through the second supply line.
  • a hydraulic arrangement is provided which, compared with corresponding solutions known in the prior art, has a significantly lower construction cost, a smaller overall volume and lower component costs.
  • a first shuttle valve in a first resulting load pressure line wherein a first the priority valve in the direction of a closed position controlling control pressure line connected to the first resulting load pressure line is.
  • a second control pressure line is provided, which controls the priority valve in the direction of an open position, wherein this Hydraulic pump side is connected to one of the supply lines.
  • the first resulting load pressure line and a load pressure line connected to the third consumer via a second shuttle valve is merged into a second resultant load pressure line, the second resulting load pressure line provides a control pressure, which for the control of a provided by the hydraulic pump supply pressure for the load-dependent demand-controlled Consumable consumers.
  • the volume flow reducing means in the second supply line comprise, for example, a constant throttle or orifice valve.
  • a variable or manually or electronically adjustable or controllable orifice valve or flow control valve or throttle control valve can be used. It is also possible to use other means not mentioned here for reducing the volume flow. It is essential that a minimum permitted volume flow can be presettable or regulated or controllable.
  • connection line comprise a check valve closing in the direction of the third supply line.
  • This may for example be a conventional ball valve, which opens only in a flow direction.
  • the pressure-controlled priority valve may be formed as a proportional valve, wherein the proportional valve is a pressure-controlled valve with Intermediate positions and two end positions - a closed position and an open position - represents. Depending on the load pressure state (load pressure signal or load-sensing signal) of the individual hydraulic consumers, the priority valve assumes an intermediate position which lies between a complete closing position and a complete opening position.
  • the hydraulic pump can be configured as a load-pressure-dependent variable displacement pump which supplies a variable volumetric flow via a preferably integrated volumetric flow controller as a function of the load pressure signal reported by the hydraulic consumers, wherein a load pressure supplied or signaled in accordance with the second resulting load pressure line can preferably be used to control the variable displacement pump.
  • a constant displacement pump may also be used as the hydraulic pump, in which case a proportional pressure valve which can be actuated depending on the load pressure is discharged to a hydraulic tank.
  • the required supply quantity for the hydraulic consumers is signaled via the load pressure lines and a corresponding proportion of the constant volume flow delivered by the constant displacement pump is discharged into the hydraulic tank as a function of this via the proportional valve.
  • a load pressure-dependent delivery volume can be provided to the hydraulic consumers in a comparable manner as with a variable displacement pump.
  • the first hydraulic consumer comprises a hydraulically actuated steering or hydraulically actuated brake. Further, both may be provided together in the same highest supply priority level. It is also possible to operate other hydraulic consumers as the first consumer with the highest priority level, such as a hydraulically operated transmission.
  • the second hydraulic consumer may comprise a hydraulically actuated suspension, which may be, for example, a cabin suspension or an axle suspension of the vehicle. Furthermore, other hydraulic consumers can be operated as a second consumer with a lower priority level.
  • the third hydraulic consumer may comprise, for example, a hydraulically actuated lifting mechanism, for example with a three-point hitch arranged at the front or rear of the vehicle, or a front-end loader mounted on the vehicle.
  • a hydraulic arrangement according to the invention according to the above-mentioned embodiments is suitable for use in agricultural vehicles, such as agricultural tractors or tractors, but also in harvesters, as well as construction and forestry machinery.
  • FIG. 1 shows an agricultural vehicle 10 in the form of a tractor or tractor of a hydraulic arrangement 12 according to the invention according to the FIGS. 2 and 3 includes.
  • the in the FIGS. 2 and 3 schematically illustrated hydraulic arrangements are described only as an example in connection with the tractor and can be found in the same way in other agricultural vehicles, such as harvesters, plant protection machines, planting and sowing machines but also in construction and forestry application.
  • the vehicle 10 comprises a frame 16 on which, for example, at a rear area 17 a three-point hitch (not shown) with a hoist for operating attachments or implements (not shown) is arranged.
  • the three-point hitch device can likewise be arranged at a front area of the vehicle 10.
  • the arranged on the three-point hitch hoist is considered one of several located on the vehicle 10 hydraulic Consumers powered by the hydraulic assembly 12.
  • the in the FIGS. 2 and 3 also shown hydraulically operated devices on the vehicle 10, which are not mentioned here in detail. By way of example, only a front loader or a hydraulically operated implement pulled by a pull rod is to be mentioned here.
  • the vehicle 10 further has a hydraulically operated steering and brake system (both not shown) as well as a hydraulically operated suspension system on the front axle 18, rear axle 19 and / or cab 20.
  • the hydraulic arrangement 12 shown in the hydraulic circuit diagram comprises a hydraulic pump 21 in the form of a variable displacement pump, a hydraulic reservoir 22 in the form of a hydraulic tank with hydraulic fluid.
  • the hydraulic arrangement 12 comprises a hydraulic pump 21 connected to the first, second and third hydraulic supply line 24, 26, 28 which supply a first, second and third hydraulic consumers 30, 32, 34 hydraulically, wherein the hydraulic consumers 30, 32, 34 via a first, second and third control valve 36, 38, 40 are controlled.
  • the control valves 36, 38, 40 are connected in each case via one of the supply lines 24, 26, 28 with the hydraulic pump 20 and via a plurality of different connecting lines 41 to the respective hydraulic consumers 30, 32, 34, and via tank lines 42 to the hydraulic tank 22.
  • the first hydraulic consumer 30 is thus supplied via the first supply line 24 and controlled via the control valve 36.
  • the second hydraulic consumers 32 is thus supplied via the supply line 26 and controlled by the control valve 38.
  • the third hydraulic consumer 34 is thus supplied via the supply line 28 and controlled by the control valve 40.
  • Each of the hydraulic consumers 30, 32, 34 may be more than just a hydraulic consumer so that, for example, the first hydraulic consumer 30 is a hydraulically operated steering (not shown) and / or brake system (not shown) of the vehicle 10 can.
  • the third hydraulic consumer 34 also applies that this is only representative of one or more hydraulic consumers mentioned, for example, for the lifting of a Dreipunkanitativoriques (not shown) or a front loader.
  • the hydraulic consumers 30, 32, 34 may also represent other non-mentioned hydraulic consumers and be designed in any other order.
  • the first control valve 36 has a first load pressure line 43 which is brought together in a first shuttle valve 44 with a second load pressure line 46 connected to the second control valve 38 into a first resulting load pressure line 48.
  • the first resulting load pressure line 48 is in a second shuttle valve 50 with a third control valve 40 connected to the third load pressure line 52 into a second resulting load pressure line 54 merged.
  • the shuttle valves 44, 50 are each arranged such that a pressure value signaled by the first or second load pressure line 43, 46 transfers into the first resulting load pressure line or transfers a pressure value signaled by the first or third load pressure line 48, 52 into the second resulting load pressure line becomes.
  • the second resulting load pressure line 54 leads to the variable displacement pump 21 and is used to control a volume flow regulator 56 integrated there.
  • the first supply line 24 leads directly from the hydraulic pump 21 to the first control valve 36.
  • the second supply line 26 has between the hydraulic pump 21 and the second control valve 38 arranged volume flow reducing means 58 in the form of a throttle or orifice. Between the second control valve 38 and the volume flow reducing means 58 branches off a connecting line 60, which leads to the third supply line 28 and connects to the second supply line 26.
  • the connecting line has means 62 which block a volume flow from the second supply line 26 in the direction of the third supply line 28.
  • the aforementioned means 62 are designed in particular as a check valve which permits a hydraulic flow or a volume flow coming from the third supply line 28 in the direction of the second supply line 26 or blocks in the opposite direction. Thus, no hydraulic flow or volume flow can take place from the second supply line 26 via the connecting line 60 into the third supply line 28.
  • a priority valve 66 is arranged in the form of a pressure-controlled proportional valve or a pressure compensator.
  • the priority valve 66 has a closed position 68 and an open position 70, wherein a first control pressure line 72 is arranged, which branches off from the first resulting load pressure line 48 and leads into the priority valve 66, wherein the first control pressure line 72 urges this into the closed position 68.
  • a second control pressure line 74 is arranged, which branches off from the third supply line 28 and leads into the priority valve 66, wherein the second control pressure line 74 urges this in the open position 70.
  • a load-pressure-controlled hydraulic arrangement 12 with integrated priority control is created for the various hydraulic consumers 30, 32, 34, by means of which various hydraulic consumers 30, 32, 34 with different supply priorities can be controlled as needed.
  • Priority control means in the present case that the various hydraulic consumers 30, 32, 34 are assigned to different importance levels or priority levels and are supplied with a corresponding supply priority from the hydraulic pump 21 according to their priority level. This means that with a shortage of the entire system or the hydraulic arrangement 12, which may occur due to operational reasons, the hydraulic consumers of a lower priority level are no longer or only limited hydraulically supplied to a further complete hydraulic supply of hydraulic consumers of higher priority level.
  • the first hydraulic consumer 30 has been assigned the highest supply priority
  • the second hydraulic consumer 32 a medium
  • the third hydraulic consumer 34 the lowest supply priority. This means that if it should come to an operational shortage of hydraulic suppliers 36, 38, 40, it is primarily ensured that the hydraulic consumer 30 is still adequately supplied and only then a hydraulic supply of the second and possibly even the third hydraulic Utility 32, 34 will be done. This can be achieved as follows due to the described arrangement of the load pressure lines 43, 46, 48 and the control pressure lines 72, 74 in conjunction with the shuttle valve 44 and the priority valve 66 and due to the arrangement of the volume flow reducing means 58 and arranged with the means 62 connecting line 60 become.
  • a volumetric flow conveyed by the hydraulic pump 21 can in each case unhindered via the first supply line 24 to the first hydraulic consumer 30, via the priority valve 66, the connecting line 60 and the second supply line 26 (in particular behind the volume flow reducing means 58) to the second hydraulic consumer 32 and via the priority valve 66 and the third supply line 28 to the third hydraulic consumer 34 arrive.
  • the priority valve 66 due to the connection to the first resulting load pressure line 48 and inhibits or reduces (throttles) a flowing through the priority valve 66 to the second and third consumers 32, 34 volumetric flow by full or partial closing of the priority valve 66.
  • a volume flow for the second hydraulic consumer 32 is passed through the second supply line 26 via the volume flow reducing means 58, wherein a volume flow through the connecting line 60 is blocked by the means 62 arranged there.
  • the second hydraulic consumer 32 continues to be hydraulically powered, even though the priority valve 66 should be fully closed, albeit with throttled flow rate.
  • a minimum supply of the second hydraulic consumer 32 with a volume flow defined via the volume flow reducing means 58 takes place.
  • a pressure build-up for the second hydraulic consumer 32 is generated and its minimum function secured.
  • the third hydraulic consumer 34 is supplied with increasing closure of the priority valve 66 with less and less volume flow, whereas the first hydraulic consumer 30 continues to be supplied with maximum volume flow. Due to the volume flow reducing means 58, the first hydraulic consumer 30 has a higher supply priority than the second hydraulic consumer 32. The second hydraulic consumer 32 also enjoys a higher supply priority than the third hydraulic consumer 34, since a minimum volume flow for the second hydraulic consumer 32 is secured via the second supply line 26, even if the priority valve 66 is completely closed should be. Thus, three priority levels are realized using only one priority valve 66.
  • the volume flow reducing means 58 are preset such that a minimum volume flow to the second consumer 32 is ensured and at the same time it is ensured that in no operating condition Undersupply of the first hydraulic consumer 30 may occur due to the then outflowing volume flow via the second supply line 26.
  • a hydraulic steering or braking system of the vehicle 10 which has a relation to a second hydraulic consumer designed as 32 hydraulic suspension for vehicle 10 or cabin 20 higher supply priority.
  • a hydraulic suspension designed as a second hydraulic consumer 32 for a vehicle 10 or a cab 20 also enjoys a higher supply priority compared to a lifting mechanism designed as a third hydraulic consumer 34.
  • the first hydraulic consumer 30 was designed as a steering and / or brake system, the second hydraulic consumer 32 as suspension and the third hydraulic consumer 34 as a hoist.
  • a constant displacement pump can be arranged as a hydraulic pump 21, wherein a load pressure-dependent, demand-controlled hydraulic arrangement 12 off FIG. 2 can be realized via a pressure-controlled proportional valve 76, which is pressure-controlled by the second resulting load pressure line 54 in a closed position 78 and urged by a connected to a discharge line 80 control pressure line 82 in an open position 84.
  • the discharge line 80 is connected to the delivery volume flow of the fixed pump designed as a hydraulic pump 21 and reduced by discharging excess supply liquid (hydraulic fluid delivered by the hydraulic pump 21), which is constantly conveyed by the constant pump to the supply lines 24, 26, 28, the delivery volume according to the from the second resultant load pressure line 54 supplied load pressure signal.
  • a hydraulic pump 21 designed as a fixed displacement pump an on-demand or load pressure-dependent supply of the hydraulic consumers 30, 32, 34 can take place.

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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 (12)

  1. Agencement hydraulique (12) avec une pompe hydraulique (21) et au moins un premier, un deuxième et un troisième consommateurs (30, 32, 34) alimentés en fonction des besoins par la pompe hydraulique (21) via des conduites sous pression de charge respectives (43, 46, 48, 52, 54), dans lequel chaque consommateur (30, 32, 34) est relié hydrauliquement en parallèle à la pompe hydraulique (21) par au moins une soupape de commande (36, 38, 40) via une conduite d'alimentation propre (24, 26, 28) et une priorité d'alimentation de premier niveau est associée au premier consommateur (30), une priorité d'alimentation de deuxième niveau subordonnée au premier niveau est associée au deuxième consommateur (32) et une priorité d'alimentation de troisième niveau subordonnée au deuxième niveau est associée au troisième consommateur (34), caractérisé en ce que pour la commande des niveaux de priorité d'alimentation les conduites d'alimentation (26, 28) du deuxième et du troisième consommateurs (32, 34) sont reliées par une conduite de liaison (60) et une vanne de priorité (66) commandée par la pression de charge est disposée entre la pompe hydraulique (21) et la conduite de liaison (60) dans la conduite d'alimentation (28) vers le troisième consommateur (34) et des moyens (58) réduisant le courant volumique sont disposés dans la conduite d'alimentation (26) vers le deuxième consommateur (32), caractérisé en ce que la conduite de liaison (60) présente en outre des moyens (62), qui bloquent un courant volumique de la deuxième conduite d'alimentation (26) en direction de la troisième conduite d'alimentation (28).
  2. Agencement hydraulique (12) selon la revendication 1, caractérisé en ce qu'une conduite sous pression de charge (43) reliée au premier consommateur (30) et une conduite sous pression de charge (46) reliée au deuxième consommateur (32) débouchent via une première soupape à deux voies (44) dans une première conduite sous pression de charge résultante (48), dans lequel une première conduite sous pression de commande (72) commandant la vanne de priorité (66) en direction d'une position de fermeture (68) est reliée à la première conduite sous pression de charge résultante (48), et en ce qu'une deuxième conduite sous pression de commande (74) commandant la vanne de priorité (66) dans une position d'ouverture (70) est agencée de façon à être reliée du côté de la pompe hydraulique à une des conduites d'alimentation (24, 26, 28).
  3. Agencement hydraulique (12) selon la revendication 2, caractérisé en ce que la première conduite sous pression de charge résultante (48) et une conduite sous pression de charge (52) reliée au troisième consommateur (34) débouchent dans une deuxième conduite sous pression de charge résultante (54) via une deuxième soupape à deux voies (50), dans lequel la deuxième conduite sous pression de charge résultante (54) fournit une pression de commande, qui peut être utilisée pour la commande d'une pression d'alimentation fournie par la pompe hydraulique (21) pour les consommateurs (30, 32, 34) alimentés en fonction des besoins.
  4. Agencement hydraulique (12) selon l'une quelconque des revendications précédentes, caractérisé en ce que les moyens (58) réduisant le courant volumique comprennent une vanne papillon, un diaphragme ou une soupape de réglage de courant.
  5. Agencement hydraulique (12) selon l'une quelconque des revendications précédentes, caractérisé en ce que les moyens (62) prévus dans la conduite de liaison (60) comprennent un clapet anti-retour se fermant en direction de la troisième conduite d'alimentation (28).
  6. Agencement hydraulique (12) selon l'une quelconque des revendications précédentes, caractérisé en ce que la vanne de priorité (66) commandée par la pression est constituée par une vanne proportionnelle.
  7. Agencement hydraulique (12) selon l'une quelconque des revendications précédentes, caractérisé en ce que la pompe hydraulique (21) est configurée sous la forme d'une pompe à cylindrée variable en fonction de la pression de charge.
  8. Agencement hydraulique (12) selon l'une quelconque des revendications 1 à 7, caractérisé en ce que la pompe hydraulique (21) est configurée sous la forme d'une pompe à cylindrée constante et il est prévu une vanne proportionnelle (76) pouvant être commandée en fonction de la pression de charge, qui évacue vers un réservoir hydraulique (22) du liquide d'alimentation refoulé par la pompe à cylindrée constante en fonction de la pression de charge.
  9. Agencement hydraulique (12) selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier consommateur (30) comprend une direction actionnable hydrauliquement et/ou un frein actionnable hydrauliquement.
  10. Agencement hydraulique (12) selon l'une quelconque des revendications précédentes, caractérisé en ce que le deuxième consommateur (32) comprend une suspension actionnable hydrauliquement.
  11. Agencement hydraulique (12) selon l'une quelconque des revendications précédentes, caractérisé en ce que le troisième consommateur (34) comprend un dispositif de levage actionnable hydrauliquement.
  12. Véhicule agricole (10) avec un agencement hydraulique (12) selon l'une quelconque des revendications précédentes.
EP10172292.4A 2009-08-21 2010-08-09 Agencement hydraulique Active EP2287472B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009028816A DE102009028816A1 (de) 2009-08-21 2009-08-21 Hydraulische Anordnung

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EP2287472A2 EP2287472A2 (fr) 2011-02-23
EP2287472A3 EP2287472A3 (fr) 2014-09-03
EP2287472B1 true EP2287472B1 (fr) 2016-02-17

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EP10172292.4A Active EP2287472B1 (fr) 2009-08-21 2010-08-09 Agencement hydraulique

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US (1) US20110146258A1 (fr)
EP (1) EP2287472B1 (fr)
CN (1) CN101994725A (fr)
BR (1) BRPI1002967A2 (fr)
DE (1) DE102009028816A1 (fr)
ES (1) ES2566638T3 (fr)

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CN104214150B (zh) * 2014-06-04 2016-03-23 上海中联重科桩工机械有限公司 双卷扬液压控制系统及具有其的工程机械
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CN106050768A (zh) * 2016-06-30 2016-10-26 江苏大学 一种拖拉机电液悬挂系统
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Also Published As

Publication number Publication date
BRPI1002967A2 (pt) 2012-04-17
ES2566638T3 (es) 2016-04-14
CN101994725A (zh) 2011-03-30
US20110146258A1 (en) 2011-06-23
EP2287472A3 (fr) 2014-09-03
EP2287472A2 (fr) 2011-02-23
DE102009028816A1 (de) 2011-02-24

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