EP2287472B1 - Hydraulic assembly - Google Patents

Hydraulic assembly 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)
French (fr)
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EP2287472A2 (en
EP2287472A3 (en
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 of EP2287472A2 publication Critical patent/EP2287472A2/en
Publication of EP2287472A3 publication Critical patent/EP2287472A3/en
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Publication of EP2287472B1 publication Critical patent/EP2287472B1/en
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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)

Description

Die Erfindung betrifft eine hydraulische Anordnung mit einer Hydraulikpumpe und wenigstens einem ersten, zweiten und dritten von der Hydraulikpumpe über jeweilige Lastdruckleitungen bedarfsgesteuert versorgten Verbraucher, wobei jeder Verbraucher durch wenigstens ein Steuerventil über eine eigene Versorgungsleitung hydraulisch parallel mit der Hydraulikpumpe verbunden ist und dem ersten Verbraucher eine Versorgungspriorität erster Stufe, dem zweiten Verbraucher eine der ersten Stufe untergeordnete Versorgungspriorität zweiter Stufe und dem dritten Verbraucher eine der zweiten Stufe untergeordnete Versorgungspriorität dritter Stufe zugeordnet ist.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.

Bei hydraulischen Systemen in landwirtschaftlichen Fahrzeugen, wie z.B. in landwirtschaftlichen Schleppern oder Traktoren, aber auch in Erntemaschinen, sowie Bau- und Forstmaschinen ist es bekannt, lastdruckabhängige Versorgungen für die einzelnen hydraulischen Verbraucher vorzusehen. Derartige Systeme, auch als Load-Sensing-Systeme bekannt, können sowohl mit Konstantpumpen als auch mit Fördervolumenstrom geregelten Verstellpumpen betrieben werden. Bei der Verwendung von Konstantpumpen wird eine lastdruckabhängige Versorgung dadurch realisiert, dass ein konstanter Fördervolumenstrom über eine Abführleitung lastdruckabhängig abgeführt wird. Verstellpumpen hingegen können direkt lastdruckabhängig betrieben werden. Es ist ferner bekannt, die hydraulischen Verbraucher an den genannten Fahrzeugen prioritätsgesteuert zu versorgen, so dass hydraulische Verbraucher mit einer höheren Prioritätsstufe gegenüber hydraulischen Verbrauchern mit eine geringeren Prioritätsstufe vorrangig hydraulisch versorgt werden, falls es betriebsbedingt zu einer hydraulischen Unterversorgung kommt. So gehören hydraulische Verbraucher, wie z.B. eine hydraulisch betriebene Lenkung oder hydraulisch betriebene Bremsanlagen einer höheren Prioritätsstufe an als beispielsweise eine hydraulisch betriebene Federung am Fahrzeug. Diese kann wiederum gegenüber einem weiteren hydraulischen Verbraucher, beispielsweise einem am Fahrzeug befindlichen Hubwerk, ebenfalls einer höheren Prioritätsstufe angehören. So sind oftmals in einem lastdruckabhängigen hydraulischen System mehrere Prioritätsstufen für die unterschiedlichen hydraulischen Verbraucher zu berücksichtigen.In hydraulic systems in agricultural vehicles, such as in agricultural tractors or tractors, but also in harvesters, and construction and forestry machines, it is known to provide load pressure-dependent supplies for the individual hydraulic consumers. Systems of this type, also known as load-sensing systems, can be operated both with constant-displacement pumps and with variable-displacement pumps controlled by volume flow. When constant-displacement pumps are used, a load-pressure-dependent supply is realized by discharging a constant delivery volume flow via a discharge line depending on the load pressure. On the other hand, variable displacement pumps can be operated directly depending on the load pressure. It is also known to provide priority control of the hydraulic consumers on the said vehicles, so that 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. So include 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.

Um eine zuverlässige Prioritätssteuerung zu realisieren werden in hydraulischen Load-Sensing-Systemen Prioritätsventile in Form von Druckwaagen verwendet, durch die eine Vorrangigkeit in der Versorgung einzelner hydraulischer Verbraucher bei einer hydraulischen Unterversorgung des Gesamtsystems steuern. In der Regel sind die einzelnen hydraulischen Verbraucher mit jeweils wenigstens einem Steuerventil verbunden, über das ein Zulauf des Fördervolumenstroms seitens der Hydraulikpumpe gesteuert wird. Im Zulauf jedes Steuerventils befindet sich ein Prioritätsventil, das von einem Lastdrucksignal eines vorrangigen hydraulischen Verbrauchers geschlossen wird und den Volumenstrom reduziert bzw. androsselt, um die hydraulische Versorgung der vorrangigen Ventile zu gewährleisten. So wird zur Realisierung von zwei Prioritätsstufen in dem im Stand der Technik bekannten hydraulischen Systemen oder Anordnungen ein Prioritätsventil eingesetzt. Für die Realisierung von drei Prioritätsstufen, wie oben erwähnt, werden somit üblicherweise zwei Prioritätsventile benötigt. Dies ist in der Regel mit einem erhöhten Bauaufwand und Bauvolumen verbunden. Will man diesen verhindern, so muss man auf entsprechende Prioritätsstufen verzichten, so dass oftmals die verschiedenen unterrangigen hydraulischen Verbraucher in eine Prioritätsstufe zusammengelegt werden, um ein weiteres mit Bauaufwand und Bauvolumen verbundenes Prioritätsventil einzusparen. Dies kann jedoch bei einer Unterversorgung des Gesamtsystems dazu führen, dass einer der zusammengelegten hydraulischen Verbraucher keine ausreichende Volumenstromversorgung erfährt und somit ausfällt. Besonders nachteilig ist dies, wenn es sich um einen hydraulischen Verbraucher handelt, der gegenüber einem in der gleichen Prioritätsstufe zusammengelegten hydraulischen Verbraucher eine eigentlich höhere Versorgungspriorität genießen sollte. Eine hydraulische Anordnung nach dem Oberbegriff von Anspruch 1 ist aus DE 20 2004 010 530 U1 bekannt.In order to realize a reliable 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. In general, 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. 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. Thus, 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. This is usually associated with increased construction costs and overall volume. If you want to prevent this, you have to go to appropriate priority levels dispense, so often the various subordinate hydraulic consumers are merged into a priority level to save another associated with construction costs and volume priority valve. However, this can lead to a shortage of the entire system that one of the hydraulic hydraulic consumer does not receive sufficient volume power supply and thus fails. This is particularly disadvantageous if it is a hydraulic consumer who should enjoy a higher supply priority than a hydraulic consumer that has been assembled in the same priority level. A hydraulic arrangement according to the preamble of claim 1 is made DE 20 2004 010 530 U1 known.

Die der Erfindung zugrunde liegende Aufgabe wird darin gesehen, eine hydraulische Anordnung der eingangs genannten Art anzugeben, durch welches die vorgenannten Probleme überwunden werden.The object underlying the invention is seen to provide a hydraulic arrangement of the type mentioned, by which the aforementioned problems are overcome.

Die Aufgabe wird erfindungsgemäß durch die Lehre des Patentanspruchs 1 gelöst. Weitere vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindung gehen aus den Unteransprüchen hervor.The object is achieved by the teaching of claim 1. Further advantageous embodiments and modifications of the invention will become apparent from the dependent claims.

Erfindungsgemäß wird eine hydraulische Anordnung der eingangs genannten Art derart ausgebildet, dass zur Steuerung der Versorgungsprioritätsstufen die Versorgungsleitungen des zweiten und dritten Verbrauchers über eine Verbindungsleitung verbunden sind und zwischen der Hydraulikpumpe und der Verbindungsleitung in der Versorgungsleitung zum dritten Verbraucher ein lastdruckgesteuertes Prioritätsventil und in der Versorgungsleitung zum zweiten Verbraucher Volumenstrom reduzierende Mittel angeordnet sind, wobei ferner die Verbindungsleitung Mittel aufweist, die einen Volumenstrom von der zweiten Versorgungsleitung in Richtung der dritten Versorgungsleitung sperren. Unter normalen Versorgungsbedingungen des Gesamtsystems kann ein von der Hydraulikpumpe geförderter Volumenstrom jeweils ungehindert bzw. ungedrosselt über die erste Versorgungsleitung zum ersten hydraulischen Verbraucher, über das Prioritätsventil, die Verbindungsleitung und die zweite Versorgungsleitung zum zweiten hydraulischen Verbraucher und über das Prioritätsventil und die dritte Versorgungsleitung zum dritten hydraulischen Verbraucher gelangen. Im Falle einer Unterversorgung des Gesamtsystems schließt sich das Prioritätsventil aufgrund der Verbindung zu den Lastdruckleitungen und unterbindet bzw. reduziert einen durch das Prioritätsventil zu dem zweiten und dritten Verbraucher strömenden Volumenstrom. Gleichzeitig wird der Volumenstrom durch die zweite Versorgungsleitung über die den Volumenstrom reduzierende Mittel geleitet, wobei ein Volumenstrom über die Verbindungsleitung durch die dort angeordneten Mittel gesperrt ist. Der zweite hydraulische Verbraucher wird somit unabhängig von der Stellung des Prioritätsventils weiterhin hydraulisch versorgt, selbst wenn das Prioritätsventil vollständig geschlossen sein sollte, wenn auch mit gedrosseltem Volumenstrom. Es findet also bei einer Unterversorgung des Gesamtsystems eine Mindestversorgung des zweiten hydraulischen Verbrauchers mit einem definierten Volumenstrom über die Volumenstrom reduzierenden Mittel statt. Hierdurch wird ein Druckaufbau für den zweiten hydraulischen Verbraucher möglich und seine Mindestfunktion ist gesichert. Der dritte hydraulische Verbraucher wird mit zunehmender Schließung des Prioritätsventils mit immer weniger Volumenstrom versorgt, hingegen der erste hydraulische Verbraucher weiterhin mit maximalem Volumenstrom versorgt wird. Aufgrund der Volumenstrom reduzierenden Mittel kommt dem ersten hydraulischen Verbraucher gegenüber dem zweiten hydraulischen Verbraucher eine höhere Versorgungspriorität zu. Der zweite hydraulische Verbraucher genießt zudem eine gegenüber dem dritten hydraulischen Verbraucher höhere Versorgungspriorität, da ein minimaler Volumenstrom für die zweite Versorgungsleitung gesichert ist, auch wenn das Prioritätsventil vollständig geschlossen sein sollte. Es werden somit drei Prioritätsstufen realisiert unter Verwendung von nur einem Prioritätsventil. Zur Auslegung der hydraulischen Anordnung können die den Volumenstrom reduzierenden Mittel derart voreingestellt werden, dass ein minimaler Volumenstrom zum zweiten Verbraucher gewährleistet wird und gleichzeitig sichergestellt ist, dass in keinem Betriebszustand eine Unterversorgung des ersten hydraulischen Verbrauchers aufgrund eines abfließenden Volumenstroms über die zweite Versorgungsleitung eintreten kann. Dadurch wird eine hydraulische Anordnung geschaffen die, gegenüber entsprechenden im Stand der Technik bekannten Lösungen, einen deutlich geringeren Bauaufwand, ein geringeres Bauvolumen und geringere Bauteilkosten aufweist.According to the invention, 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. Under normal supply conditions of the entire system, 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. In the case of a shortage of the overall system, 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. At the same time, 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. Thus, 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. Thus, in the case of a shortage of the overall system, 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. Thus, three priority levels are realized using only one priority valve. For the design of the hydraulic arrangement, 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. As a result, 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.

Zur lastdruckabhängigen Steuerung der hydraulischen Anordnung ist eine mit dem ersten Verbraucher verbundene Lastdruckleitung und eine mit dem zweiten Verbraucher verbundene Lastdruckleitung über ein erstes Wechselventil in eine erste resultierende Lastdruckleitung überführt, wobei eine erste das Prioritätsventil in Richtung einer Schließstellung ansteuernde Steuerdruckleitung mit der ersten resultierenden Lastdruckleitung verbunden ist. Ferner ist eine zweite Steuerdruckleitung vorgesehen, die das Prioritätsventil in Richtung einer Öffnungsstellung ansteuert, wobei diese hydraulikpumpenseitig mit einer der Versorgungsleitungen verbunden ist.For load pressure-dependent control of the hydraulic arrangement connected to the first load load pressure line and connected to the second load load pressure line is transferred via 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. Furthermore, 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.

Des Weiteren ist die erste resultierende Lastdruckleitung und eine mit dem dritten Verbraucher verbundene Lastdruckleitung über ein zweites Wechselventil in eine zweite resultierende Lastdruckleitung zusammengeführt, wobei die zweite resultierende Lastdruckleitung einen Steuerdruck liefert, der für die Steuerung eines durch die Hydraulikpumpe bereitgestellten Versorgungsdrucks für die lastabhängig bedarfsgesteuert versorgten Verbraucher heranziehbar ist.Furthermore, 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.

Die Volumenstrom reduzierenden Mittel in der zweiten Versorgungsleitung umfassen beispielsweise eine konstante Drossel oder Blende bzw. ein Blendenventil. Hierbei kann auch ein variables bzw. manuell oder elektronisch verstellbares oder ansteuerbares Blendenventil bzw. Stromregelventil oder Drosselregelventil zum Einsatz kommen. Es können auch andere hier nicht genannte Mittel zur Reduzierung des Volumenstroms eingesetzt werden. Wesentlich ist, dass ein minimal zugelassener Volumenstrom voreinstellbar oder regelbar bzw. steuerbar vorgegeben werden kann.The volume flow reducing means in the second supply line comprise, for example, a constant throttle or orifice valve. In this case, 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.

Die in der Verbindungsleitung vorgesehenen Mittel umfassen ein in Richtung der dritten Versorgungsleitung schließendes Rückschlagventil. Dies kann beispielsweise ein herkömmliches Kugelventil sein, welches nur in eine Durchflussrichtung öffnet.The means provided in the 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.

Das druckgesteuerte Prioritätsventil kann als Proportionalventil ausgebildet sein, wobei das Proportionalventil ein druckgesteuertes Ventil mit Zwischenstellungen und zwei Endstellungen - einer Schließstellung und einer Öffnungsstellung - darstellt. In Abhängigkeit von dem Lastdruckzustand (Lastdrucksignal bzw. Load-Sensing-Signal) der einzelnen hydraulischen Verbraucher nimmt das Prioritätsventil eine Zwischenstellung ein, die zwischen einer vollständigen Schließ- und einer vollständigen Öffnungsstellung liegt.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.

Die Hydraulikpumpe kann als lastdruckabhängige Verstellpumpe ausgebildet sein, die über einen vorzugsweise integrierten Fördervolumenstromregler in Abhängigkeit des von den hydraulischen Verbrauchern gemeldeten Lastdrucksignals einen variablen Volumenstrom liefert, wobei vorzugsweise ein entsprechend der zweiten resultierenden Lastdruckleitung gelieferter bzw. signalisierter Lastdruck zur Regelung der Verstellpumpe heranziehbar ist.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.

In einer alternativen Ausführungsform kann an Stelle der Verstellpumpe auch eine Konstantpumpe als Hydraulikpumpe verwendet werden, wobei dann ein lastdruckabhängig ansteuerbares Proportionalventil vorgesehen ist, welches lastdruckabhängig von der Konstantpumpe geförderte Versorgungsflüssigkeit zu einem Hydrauliktank abführt. Über die Lastdruckleitungen wird die erforderliche Versorgungsmenge für die hydraulischen Verbraucher signalisiert und in Abhängigkeit dessen über das Proportionalventil ein entsprechender Anteil des von der Konstantpumpe geförderten konstanten Volumenstroms in den Hydrauliktank abgeführt. Dadurch kann den hydraulischen Verbrauchern ein lastdruckabhängiges Fördervolumen auf vergleichbare Weise wie mit einer Verstellpumpe bereitgestellt werden.In an alternative embodiment, instead of 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. As a result, a load pressure-dependent delivery volume can be provided to the hydraulic consumers in a comparable manner as with a variable displacement pump.

Der erste hydraulische Verbraucher umfasst eine hydraulisch betätigbare Lenkung oder hydraulisch betätigbare Bremse. Ferner kann auch beides zusammen in der gleichen höchsten Versorgungsprioritätsstufe vorgesehen sein. Es ist ferner auch möglich noch andere hydraulische Verbraucher als ersten Verbraucher mit höchster Prioritätsstufe zu betreiben, beispielsweise ein hydraulisch betätigtes Getriebe.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.

Der zweite hydraulische Verbraucher kann eine hydraulisch betätigbare Federung umfassen, wobei diese beispielsweise eine Kabinenfederung oder aber auch eine Achsfederung des Fahrzeugs sein kann. Ferner können auch andere hydraulische Verbraucher als zweiter Verbraucher mit untergeordneter Prioritätsstufe betrieben werden.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.

Der dritte hydraulische Verbraucher kann beispielsweise ein hydraulisch betätigbares Hubwerk umfassen, beispielsweise mit einer vorn oder hinten am Fahrzeug angeordneten Dreipunktanhängevorrichtung, oder einem am Fahrzeug montierten Frontlader.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.

Eine erfindungsgemäße hydraulische Anordnung gemäß den oben angeführten Ausgestaltungen eignet sich für den Einsatz in landwirtschaftlichen Fahrzeugen, beispielsweise landwirtschaftlichen Schleppern oder Traktoren, aber auch in Erntemaschinen, sowie Bau- und Forstmaschinen.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.

Anhand der Zeichnung, die ein Ausführungsbeispiel der Erfindung zeigt, werden nachfolgend die Erfindung sowie weitere Vorteile und vorteilhafte Weiterbildungen und Ausgestaltungen der Erfindung näher beschrieben und erläutert.Reference to the drawing, which shows an embodiment of the invention, the invention and further advantages and advantageous developments and refinements of the invention are described and explained in more detail below.

Es zeigt:

Fig. 1
die schematische Seitenansicht eines landwirtschaftlichen Fahrzeugs mit einer erfindungsgemäßen hydraulischen Anordnung,
Fig. 2
einen schematischen Hydraulikschaltplan einer erfindungsgemäßen hydraulischen Anordnung mit einer variablen Verstellpumpe und
Fig. 3
einen schematischen Hydraulikschaltplan einer erfindungsgemäßen hydraulischen Anordnung mit einer Konstantpumpe.
It shows:
Fig. 1
the schematic side view of an agricultural vehicle with a hydraulic arrangement according to the invention,
Fig. 2
a schematic hydraulic circuit diagram of a hydraulic arrangement according to the invention with a variable displacement pump and
Fig. 3
a schematic hydraulic circuit diagram of a hydraulic arrangement according to the invention with a constant pump.

Figur 1 zeigt ein landwirtschaftliches Fahrzeug 10 in Form eines Traktors oder Schleppers der eine erfindungsgemäße hydraulische Anordnung 12 gemäß den Figuren 2 und 3 umfasst. Die in den Figuren 2 und 3 schematisch dargestellten hydraulischen Anordnungen sind nur beispielhaft in Verbindung mit dem Traktor beschrieben und können in gleicher Weise auch in anderen landwirtschaftlichen Fahrzeugen, wie Erntemaschinen, Pflanzenschutzmaschinen, Pflanz- und Sämaschinen aber auch in Bau- und Forstmaschinen Anwendung finden. 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.

Das Fahrzeug 10 umfasst einen Rahmen 16, an dem beispielsweise an einem hinteren Bereich 17 eine Dreipunktanhängevorrichtung (nicht gezeigt) mit Hubwerk zum Betreiben von Anbau- oder Arbeitsgeräten (nicht gezeigt) angeordnet ist. Die Dreipunktanhängevorrichtung kann in gleicher Weise auch an einem vorderen Bereich des Fahrzeugs 10 angeordnet sein. Das an der Dreipunktanhängevorrichtung angeordnete Hubwerk wird als ein von mehreren am Fahrzeug 10 befindlichen hydraulischen Verbrauchern über die hydraulische Anordnung 12 versorgt. Die in den Figuren 2 und 3 dargestellte hydraulische Anordnung 12 kann ferner auch hydraulisch betriebene Geräte am Fahrzeug 10 versorgen, die hier nicht im Einzelnen genannte werden. Beispielhaft soll hier nur ein Frontlader oder ein mittels Zugstange gezogenes hydraulisch betriebenes Arbeitsgerät genannt werden.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.

Das Fahrzeug 10 verfügt ferner über eine hydraulische betriebene Lenkung und Bremsanlage (beides nicht gezeigt) sowie über ein hydraulisch betriebenes Federungssystem an Vorderachse 18, Hinterachse 19 und/oder Kabine 20.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.

Gemäß Figur 2 umfasst die im Hydraulikschaltplan dargestellte hydraulische Anordnung 12 eine Hydraulikpumpe 21 in Form einer variablen Verstellpumpe, ein Hydraulikreservoir 22 in Form eines Hydrauliktanks mit Hydraulikflüssigkeit.According to FIG. 2 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.

Die hydraulische Anordnung 12 umfasst eine mit der Hydraulikpumpe 21 verbundene erste, zweite und dritte hydraulische Versorgungsleitung 24, 26, 28 die einen ersten, zweiten und dritten hydraulischen Verbraucher 30, 32, 34 hydraulisch versorgen, wobei die hydraulischen Verbraucher 30, 32, 34 über ein erstes, zweites und drittes Steuerventil 36, 38, 40 angesteuert werden. Die Steuerventile 36, 38, 40 sind jeweils über eine der Versorgungsleitungen 24, 26, 28 mit der Hydraulikpumpe 20 und über mehrere verschiedene Verbindungsleitungen 41 mit dem jeweiligen hydraulischen Verbraucher 30, 32, 34, sowie über Tankleitungen 42 mit dem Hydrauliktank 22 verbunden. Der erste hydraulische Verbraucher 30 wird demnach über die erste Versorgungsleitung 24 versorgt und über das Steuerventil 36 angesteuert. Der zweite hydraulische Verbraucher 32 wird demnach über die Versorgungsleitung 26 versorgt und über das Steuerventil 38 angesteuert. Der dritte hydraulische Verbraucher 34 wird demnach über die Versorgungsleitung 28 versorgt und über das Steuerventil 40 angesteuert.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.

Bei jedem der hydraulischen Verbraucher 30, 32, 34 kann es sich um mehr als nur einen hydraulischen Verbraucher handeln, so dass beispielsweise der erste hydraulische Verbraucher 30 eine hydraulisch betriebene Lenkung (nicht gezeigt) und/oder Bremsanlage (nicht gezeigt) des Fahrzeugs 10 darstellen kann. Das gleiche gilt für den zweiten hydraulischen Verbraucher 32, der beispielsweise eine hydraulisch betriebene Federung (nicht gezeigt) des Fahrzeugrahmens 16 and der Vorderachse 18 und/oder an der Hinterachse 19 und/oder auch eine hydraulische Federung (nicht gezeigt) der Kabine 20 darstellen kann. Für den dritten hydraulischen Verbraucher 34 gilt ebenfalls, dass dieser hier nur repräsentativ für einen oder mehrere hydraulische Verbraucher genannt ist, beispielsweise für das Hubwerk einer Dreipunkanhängevorrichtung (nicht gezeigt) oder eines Frontladers. Hierbei können die hydraulischen Verbraucher 30, 32, 34 auch andere nicht genannte hydraulische Verbraucher darstellen sowie in anderer beliebiger Reihenfolge ausgebildet sein.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 same applies to the second hydraulic consumer 32, which may represent, for example, a hydraulically operated suspension (not shown) of the vehicle frame 16 on the front axle 18 and / or on the rear axle 19 and / or also a hydraulic suspension (not shown) of the cab 20 , For 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 Dreipunkanhängevorrichtung (not shown) or a front loader. In this case, the hydraulic consumers 30, 32, 34 may also represent other non-mentioned hydraulic consumers and be designed in any other order.

Das erste Steuerventil 36 weist eine erste Lastdruckleitung 43 auf, die in einem ersten Wechselventil 44 mit einer mit dem zweiten Steuerventil 38 verbundenen zweiten Lastdruckleitung 46 in eine erste resultierende Lastdruckleitung 48 zusammengeführt wird. Die erste resultierende Lastdruckleitung 48 wird in einem zweiten Wechselventil 50 mit einer mit dem dritten Steuerventil 40 verbundenen dritten Lastdruckleitung 52 in eine zweite resultierende Lastdruckleitung 54 zusammengeführt. Die Wechselventile 44, 50 sind jeweils so angeordnet, dass ein von der ersten oder zweiten Lastdruckleitung 43, 46 signalisierter Druckwert in die erste resultierende Lastdruckleitung überführt bzw. ein von der ersten resultierenden oder dritten Lastdruckleitung 48, 52 signalisierter Druckwert in die zweite resultierende Lastdruckleitung überführt wird.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.

Die zweite resultierende Lastdruckleitung 54 führt zur variablen Verstellpumpe 21 und wird zur Steuerung eines dort integrierten Volumenstromreglers 56 herangezogen.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.

Die erste Versorgungsleitung 24 führt direkt von der Hydraulikpumpe 21 zum ersten Steuerventil 36. Die zweite Versorgungsleitung 26 weist zwischen der Hydraulikpumpe 21 und dem zweiten Steuerventil 38 angeordnete Volumenstrom reduzierende Mittel 58 in Forme einer Drossel oder Blende auf. Zwischen dem zweiten Steuerventil 38 und den Volumenstrom reduzierenden Mitteln 58 zweigt eine Verbindungsleitung 60 ab, die zur dritten Versorgungsleitung 28 führt und diese mit der zweiten Versorgungsleitung 26 verbindet. Die Verbindungsleitung weist Mittel 62 auf, die einen Volumenstrom von der zweiten Versorgungsleitung 26 in Richtung der dritten Versorgungsleitung 28 sperren. Die genannten Mittel 62 sind insbesondere als Rückschlagventil ausgebildet, welches einen Hydraulikfluss bzw. einen Volumenstrom von der dritten Versorgungsleitung 28 kommend in Richtung der zweiten Versorgungsleitung 26 zulässt bzw. in entgegen gesetzter Richtung sperrt. Es kann also kein Hydraulikfluss bzw. Volumenstrom von der zweiten Versorgungsleitung 26 über die Verbindungsleitung 60 in die dritte Versorgungsleitung 28 erfolgen.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.

Zwischen einer Verbindungsstelle 64 der Verbindungsleitung 60 mit der dritten Versorgungsleitung 28 und der Hydraulikpumpe 21 ist ein Prioritätsventil 66 in Form eines druckgesteuerten Proportionalventils oder einer Druckwaage angeordnet. Das Prioritätsventil 66 weist eine Schließstellung 68 und eine Öffnungsstellung 70 auf, wobei eine erste Steuerdruckleitung 72 angeordnet ist, die von der ersten resultierenden Lastdruckleitung 48 abzweigt und in das Prioritätsventil 66 führt, wobei die erste Steuerdruckleitung 72 dieses in die Schließstellung 68 drängt. Auf der entgegen gelegenen Seite des Prioritätsventils 66 ist eine zweite Steuerdruckleitung 74 angeordnet, die von der dritten Versorgungsleitung 28 abzweigt und in das Prioritätsventil 66 führt, wobei die zweite Steuerdruckleitung 74 dieses in die Öffnungsstellung 70 drängt.Between a junction 64 of the connecting line 60 with the third supply line 28 and the hydraulic pump 21, 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. On the opposite side of the priority valve 66, 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.

Durch die beschriebene hydraulische Anordnung gemäß Figur 2 wird eine lastdruckgesteuerte hydraulische Anordnung 12 mit integrierter Prioritätssteuerung für die verschiedenen hydraulischen Verbraucher 30, 32, 34 geschaffen, durch die verschiedene hydraulische Verbraucher 30, 32, 34 mit unterschiedlichen Versorgungsprioritäten bedarfsgerecht ansteuerbar sind. Prioritätssteuerung heißt im vorliegenden Fall, dass die verschiedenen hydraulischen Verbraucher 30, 32, 34 unterschiedlichen Wichtigkeitsstufen bzw. Prioritätsstufen zugeordnet sind und entsprechend ihrer Prioritätsstufe mit einer entsprechenden Versorgungspriorität von der Hydraulikpumpe 21 versorgt werden. Dies bedeutet, dass bei einer Unterversorgung des Gesamtsystems bzw. der hydraulischen Anordnung 12, was betriebsbedingt eintreten kann, die hydraulischen Verbraucher einer geringeren Prioritätsstufe nicht mehr oder nur noch begrenzt hydraulisch versorgt werden, um eine weiterhin vollständige hydraulische Versorgung von hydraulischen Verbrauchern höherer Prioritätsstufe zu gewährleisten.By the described hydraulic arrangement according to FIG. 2 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.

Im vorliegenden Ausführungsbeispiel gemäß Figur 2 wurde dem ersten hydraulischen Verbraucher 30 eine oberste, dem zweiten hydraulischen Verbraucher 32 eine mittlere und dem dritten hydraulischen Verbraucher 34 die niedrigste Versorgungspriorität zugesprochen. Das heißt, dass wenn es zu einer betriebsbedingten Unterversorgung der hydraulischen Versorger 36, 38, 40 kommen sollte, in erster Linie gewährleistet wird, dass der hydraulische Verbraucher 30 weiterhin ausreichend versorgt wird und erst dann eine hydraulische Versorgung des zweiten und gegebenenfalls noch des dritten hydraulischen Versorgers 32, 34 erfolgen wird. Dies kann wie folgt aufgrund der beschriebenen Anordnung der Lastdruckleitungen 43, 46, 48 und der Steuerdruckleitungen 72, 74 in Verbindung mit dem Wechselventil 44 und dem Prioritätsventil 66 sowie aufgrund der Anordnung der Volumenstrom reduzierenden Mittel 58 und der mit den Mitteln 62 angeordneten Verbindungsleitung 60 erzielt werden.In the present embodiment according to FIG. 2 For example, the first hydraulic consumer 30 has been assigned the highest supply priority, the second hydraulic consumer 32 a medium and 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.

Unter normalen Versorgungsbedingungen des Gesamtsystems bzw. der hydraulischen Anordnung 12 kann ein von der Hydraulikpumpe 21 geförderter Volumenstrom jeweils ungehindert bzw. ungedrosselt über die erste Versorgungsleitung 24 zum ersten hydraulischen Verbraucher 30, über das Prioritätsventil 66, die Verbindungsleitung 60 und die zweite Versorgungsleitung 26 (insbesondere hinter den Volumenstrom reduzierenden Mitteln 58) zum zweiten hydraulischen Verbraucher 32 und über das Prioritätsventil 66 und die dritte Versorgungsleitung 28 zum dritten hydraulischen Verbraucher 34 gelangen. Im Falle einer Unterversorgung des Gesamtsystems schließt sich das Prioritätsventil 66 aufgrund der Verbindung zu der ersten resultierenden Lastdruckleitung 48 und unterbindet bzw. reduziert (drosselt) einen durch das Prioritätsventil 66 zu dem zweiten und dritten Verbraucher 32, 34 strömenden Volumenstrom durch vollständiges bzw. teilweises Schließen des Prioritätsventils 66. Gleichzeitig wird ein Volumenstrom für den zweiten hydraulischen Verbraucher 32 durch die zweite Versorgungsleitung 26 über die den Volumenstrom reduzierende Mittel 58 geleitet, wobei ein Volumenstrom über die Verbindungsleitung 60 durch die dort angeordneten Mittel 62 gesperrt ist. Der zweite hydraulische Verbraucher 32 wird somit unabhängig von der Stellung des Prioritätsventils 66 weiterhin hydraulisch versorgt, selbst wenn das Prioritätsventil 66 vollständig geschlossen sein sollte, wenn auch mit gedrosseltem Volumenstrom. Es findet also bei einer Unterversorgung des Gesamtsystems eine Mindestversorgung des zweiten hydraulischen Verbrauchers 32 mit einem über die Volumenstrom reduzierenden Mittel 58 definierten Volumenstrom statt. Ein Druckaufbau für den zweiten hydraulischen Verbraucher 32 wird erzeugt und seine Mindestfunktion gesichert. Der dritte hydraulische Verbraucher 34 wird mit zunehmender Schließung des Prioritätsventils 66 mit immer weniger Volumenstrom versorgt, hingegen der erste hydraulische Verbraucher 30 weiterhin mit maximalem Volumenstrom versorgt wird. Aufgrund der Volumenstrom reduzierenden Mittel 58 kommt dem ersten hydraulischen Verbraucher 30 gegenüber dem zweiten hydraulischen Verbraucher 32 eine höhere Versorgungspriorität zu. Der zweite hydraulische Verbraucher 32 genießt zudem eine gegenüber dem dritten hydraulischen Verbraucher 34 höhere Versorgungspriorität, da ein minimaler Volumenstrom für den zweiten hydraulischen Verbraucher 32 über die zweite Versorgungsleitung 26 gesichert ist, auch wenn das Prioritätsventil 66 vollständig geschlossen sein sollte. Es werden somit drei Prioritätsstufen realisiert unter Verwendung von nur einem Prioritätsventil 66. Zur Auslegung der hydraulischen Anordnung 12 werden die den Volumenstrom reduzierenden Mittel 58 derart voreingestellt, dass ein minimaler Volumenstrom zum zweiten Verbraucher 32 gewährleistet wird und gleichzeitig sichergestellt ist, dass in keinem Betriebszustand eine Unterversorgung des ersten hydraulischen Verbrauchers 30 aufgrund des dann abfließenden Volumenstroms über die zweite Versorgungsleitung 26 eintreten kann. Als erster Verbraucher 30 wäre beispielsweise eine hydraulische Lenkung oder Bremsanlage des Fahrzeugs 10 zu nennen, die eine gegenüber einer als zweiten hydraulischen Verbraucher 32 ausgebildeten hydraulischen Federung für Fahrzeug 10 oder Kabine 20 höhere Versorgungspriorität aufweist. Ferner genießt in der Regel eine als zweiter hydraulischer Verbraucher 32 ausgebildete hydraulische Federung für ein Fahrzeug 10 oder eine Kabine 20 auch gegenüber einem als dritter hydraulischer Verbraucher 34 ausgebildetes Hubwerk eine höhere Versorgungspriorität. Im vorliegendem Ausführungsbeispiel wurde demnach der erste hydraulische Verbraucher 30 als Lenkung und/oder Bremsanlage, der zweite hydraulische Verbraucher 32 als Federung und der dritte hydraulische Verbraucher 34 als Hubwerk ausgebildet.Under normal supply conditions of the overall system or the hydraulic arrangement 12, 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. In the case of a shortage of the overall system that closes 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. At the same time, 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. Thus, regardless of the position of the priority valve 66, 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. Thus, if the overall system is undersupplied, 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. For the design of the hydraulic arrangement 12, 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. As the first load 30 would be mentioned, for example, 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. Furthermore, as a rule, 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. In the present embodiment, therefore, 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.

Auch wenn die Erfindung lediglich anhand nur eines Ausführungsbeispiels beschrieben wurde, erschließen sich für den Fachmann im Lichte der vorstehenden Beschreibung sowie der Zeichnungen viele verschiedenartige Alternativen, Modifikationen und Varianten, die unter die vorliegende Erfindung fallen. So kann beispielsweise gemäß Figur 3 an Stelle der variablen Verstellpumpe eine Konstantpumpe als Hydraulikpumpe 21 angeordnet werden, wobei eine lastdruckabhängige, bedarfsgesteuerte hydraulische Anordnung 12 aus Figur 2 über ein druckgesteuertes Proportionalventil 76 realisierbar ist, welches von der zweiten resultierenden Lastdruckleitung 54 druckgesteuert in eine Schließstellung 78 und durch eine mit einer Abführleitung 80 verbundene Steuerdruckleitung 82 in eine Öffnungsstellung 84 gedrängt wird. Die Abführleitung 80 ist mit dem Fördervolumenstrom der als Hydraulikpumpe 21 ausgebildeten Konstantpumpe verbunden und reduziert durch Abführen von überschüssiger Versorgungsflüssigkeit (von der Hydraulikpumpe 21 geförderte Hydraulikflüssigkeit), die durch die Konstantpumpe konstant an die Versorgungsleitungen 24, 26, 28 gefördert wird, das Fördervolumen entsprechend dem von der zweiten resultierenden Lastdruckleitung 54 gelieferten Lastdrucksignal. Somit kann auch mittels einer als Konstantpumpe ausgebildeten Hydraulikpumpe 21 eine bedarfsgesteuerte bzw. lastdruckabhängige Versorgung der hydraulischen Verbraucher 30, 32, 34 erfolgen.Although the invention has been described by way of example only, in the light of the above description and the drawings, many different alternatives, modifications and variants falling within the scope of the present invention will become apparent to those skilled in the art. For example, according to FIG. 3 Instead of the variable displacement pump 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. Thus, by means of 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.

Claims (12)

  1. Hydraulic assembly (12) having a hydraulic pump (21) and at least a first, second and third consumer (30, 32, 34), supplied on demand by the hydraulic pump (21) via respective load pressure lines (43, 46, 48, 52, 54), each consumer (30, 32, 34) being connected hydraulically in parallel to the hydraulic pump (21) by at least one control valve (36, 38, 40) via its own supply line (24, 26, 28), and a first-level supply priority being assigned to the first consumer (30), a second-level supply priority subordinate to the first level being assigned to the second consumer (32) and a third-level supply priority subordinate to the second level being assigned to the third consumer (34), characterized in that for controlling the supply priority levels the supply lines (26, 28) of the second and third consumers (32,34) are connected via a connecting line (60) and a load pressure-controlled priority valve (66) is arranged between the hydraulic pump (21) and the connecting line (60) in the supply line (28) to the third consumer (34) and volumetric flow-reducing means (58) are arranged in the supply line (26) to the second consumer (32), characterized in that the connecting line (60) furthermore comprises means (62), which prohibit a volumetric flow from the second supply line (26) in the direction of the third supply line (28).
  2. Hydraulic assembly (12) according to Claim 1, characterized in that a load pressure line (46) connected to the first consumer (30) and a load pressure line (46) connected to the second consumer (32) open via a first shuttle valve (44) into a first resulting load pressure line (48), a first control pressure line (72) driving the priority valve (66) in the direction of a closed position (68) being connected to the first resulting load pressure line (48), and that a second control pressure line (74), which drives the priority valve (66) in the direction of an open position (70), is provided, said line being connected on the hydraulic pump side to one of the supply lines (24, 26, 28).
  3. Hydraulic assembly (12) according to Claim 2, characterized in that the first resulting load pressure line (48) and a load pressure line (52) connected to the third consumer (34) open via a second shuttle valve (50) into a second resulting load pressure line (54), the second resulting load pressure line (54) delivering a control pressure, which can be used to control a supply pressure provided by the hydraulic pump (21) for the consumers (30, 32, 34) supplied on demand.
  4. Hydraulic assembly (12) according to one of the preceding claims, characterized in that the volumetric flow-reducing means (58) comprise a restrictor, orifice plate or flow control valve.
  5. Hydraulic assembly (12) according to one of the preceding claims, characterized in that the means (62) provided in the connecting line (60) comprise a non-return valve closing in the direction of the third supply line (28).
  6. Hydraulic assembly (12) according to one of the preceding claims, characterized in that the pressure-controlled priority valve (66) is embodied as a proportional valve.
  7. Hydraulic assembly (12) according to one of the preceding claims, characterized in that the hydraulic pump (21) is embodied as a load pressure-dependent variable-delivery pump.
  8. Hydraulic assembly (12) according to one of Claims 1 to 7, characterized in that the hydraulic pump (21) is embodied as a constant-delivery pump and a proportional valve (76) controllable as a function of the load pressure is provided, which as a function of the load pressure evacuates supply fluid delivered by the constant-delivery pump to a hydraulic tank (22).
  9. Hydraulic assembly (12) according to one of the preceding claims, characterized in that the first consumer (30) comprises a hydraulically operated steering and/or a hydraulically operated brake.
  10. Hydraulic assembly (12) according to one of the preceding claims, characterized in that the second consumer (32) comprises a hydraulically operated suspension.
  11. Hydraulic assembly (12) according to one of the preceding claims, characterized in that the third consumer (34) comprises a hydraulically operated lifting gear.
  12. Agricultural vehicle (10) having a hydraulic assembly (12) according to one of the preceding claims.
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Also Published As

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

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