EP4407156A2 - Système hydraulique pour machine de travail agricole - Google Patents

Système hydraulique pour machine de travail agricole Download PDF

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Publication number
EP4407156A2
EP4407156A2 EP23212658.1A EP23212658A EP4407156A2 EP 4407156 A2 EP4407156 A2 EP 4407156A2 EP 23212658 A EP23212658 A EP 23212658A EP 4407156 A2 EP4407156 A2 EP 4407156A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic system
pump
valve arrangement
fan
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP23212658.1A
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German (de)
English (en)
Other versions
EP4407156B1 (fr
EP4407156A3 (fr
Inventor
Norbert Strieker
George Danatzis
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.)
Claas Selbstfahrende Erntemaschinen GmbH
Original Assignee
Claas Selbstfahrende Erntemaschinen GmbH
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Publication of EP4407156A2 publication Critical patent/EP4407156A2/fr
Publication of EP4407156A3 publication Critical patent/EP4407156A3/fr
Application granted granted Critical
Publication of EP4407156B1 publication Critical patent/EP4407156B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/02—Controlling of coolant flow the coolant being cooling-air
    • F01P7/04—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio
    • F01P7/044—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio using hydraulic drives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/14—Indicating devices; Other safety devices
    • F01P11/16—Indicating devices; Other safety devices concerning coolant temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
    • F01P5/04—Pump-driving arrangements
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • F15B21/0423—Cooling
    • 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
    • F15B2211/20507—Type of prime mover
    • F15B2211/20523—Internal combustion engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low 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
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a return line
    • 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
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/611—Diverting circuits, e.g. for cooling or filtering
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/62—Cooling or heating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators

Definitions

  • the present invention relates to a hydraulic system according to the preamble of claim 1. Furthermore, the present invention relates to an agricultural working machine, in particular a self-propelled harvesting machine, according to the preamble of claim 14.
  • EP 2 636 907 B1 A hydraulic system of the type mentioned above is known from EP 2 636 907 B1 known. It describes a hydraulic system for an agricultural machine such as a combine harvester, which serves, among other things, to drive a hydraulic motor of a fan.
  • the hydraulic motor is supplied with hydraulic fluid by means of a variable displacement pump.
  • the variable displacement pump supplies a working hydraulic system of the agricultural machine.
  • temporary operating situations can occur in which the pressure medium supply provided by the variable displacement pump is not sufficient to supply all the components of the hydraulic system to be driven with sufficient pressure medium.
  • the EP 2 636 907 B1 suggests that the performance of the fan is temporarily reduced in the event of an operationally induced pressure drop in the hydraulic system.
  • the duration of the temporary reduction in the fan speed by appropriate control of the The performance of a hydraulic motor is limited by the ambient conditions prevailing during operation. During normal harvest periods in particular, the influence of ambient temperatures on the required cooling capacity is high, so that compensation for an operationally induced pressure drop in the hydraulic system is only possible to a limited extent.
  • a hydraulic system for an agricultural work machine in particular a self-propelled harvester, wherein the hydraulic system comprises a variable displacement pump which is designed and configured to supply a working hydraulic system of the work machine and a hydraulic motor which is connected to a fan for driving purposes with a pressure medium which is essentially under constant pressure.
  • the hydraulic system comprises a connection pump which is controlled by a valve arrangement having a first switching position and a second switching position, wherein the connection pump is fluidically connected to a heat exchanger of the hydraulic system by a supply line in the first switching position of the valve arrangement, and wherein the connection pump is fluidically connected to the hydraulic motor by a pressure line in the second switching position of the valve arrangement.
  • the invention is based on the idea of integrating a switchable pump into the hydraulic system instead of a more powerful variable displacement pump, which can be switched on as needed by the valve arrangement or is switched on when an operationally induced pressure drop occurs in the hydraulic system.
  • a variable displacement pump that is adapted or designed to the power requirement that is regularly required during operation can be used, i.e. essentially without taking operationally induced load peaks into account.
  • the additional pump is switched on using the valve arrangement. Accordingly, the variable displacement pump can be dimensioned smaller so that it is better utilized by driving the fan and operating the working hydraulics and thus has a better efficiency than a larger variable displacement pump.
  • An operationally induced pressure drop in the hydraulic system can occur due to the automatic control of the working hydraulics, for example when reaching or driving through a headland.
  • the heat exchanger of the hydraulic system is responsible for cooling the pressure medium flowing back from the working hydraulics and the hydraulic motor of the fan.
  • the hydraulic system is designed as a constant pressure system.
  • the activation pump is preferably designed as a constant pump.
  • the activation pump can also be designed as a variable pump.
  • the design of the activation pump as a constant pump has the advantage that the volume flow provided by the variable pump of the hydraulic system can be reduced for the duration of the activation of the activation pump.
  • the volume flow provided by the variable pump can be reduced essentially by the volume flow provided by the activation pump, which is designed here and preferably as a constant pump.
  • a further advantage of the smaller dimensioned variable displacement pump is that it can be operated at a higher drive speed than the drive speed provided by a drive motor, in particular an internal combustion engine, of the agricultural machine.
  • An operationally induced pressure drop in the hydraulic system can also occur in a drive motor designed as an internal combustion engine due to engine pressure during ongoing harvesting operations and during road travel.
  • the agricultural work machine is preferably a self-propelled harvesting machine, in particular a combine harvester or a forage harvester.
  • the pressure line is branched into a first line branch leading to the working hydraulics and a second line branch leading to the hydraulic motor.
  • the branching of the pressure line has the advantage that in the second switching position of the valve arrangement, both the working hydraulics and the hydraulic motor are supplied with pressure medium by the additional pump in addition to the variable displacement pump.
  • the use of an additional pump designed as a constant pump enables a large power spread over the entire speed range of the drive motor of the working machine in the second switching position of the valve arrangement, in which the additional pump works together with the variable displacement pump.
  • the heat exchanger can be connected to a cooler pump to supply pressure medium.
  • the cooler pump which is preferably designed as a constant pump, maintains a continuous volume flow to supply the heat exchanger in order to ensure the cooling of the returning pressure medium regardless of the respective switching position of the valve arrangement. In the first switching position of the valve arrangement, the cooler pump can be supported by the additional pump.
  • the working hydraulics can comprise a hydraulic steering system and/or a lifting device.
  • the working hydraulics can also comprise further hydraulic consumers.
  • the valve arrangement can be assigned a control device which is designed to control the valve arrangement depending on at least one detected operating parameter of the hydraulic system and/or the working hydraulics supplied by the hydraulic system and/or the fan supplied by the hydraulic system.
  • the control device has the task of determining the occurrence of operationally induced load peaks and controlling the valve arrangement depending on this.
  • the control device can be connected to at least one sensor arrangement of the hydraulic system and/or the working hydraulics, in particular the lifting device and the steering system, in order to be able to detect at least one Sensor arrangement to receive signals for evaluating the operating parameters to be detected.
  • control device is designed to control the valve arrangement depending on the performance of the variable displacement pump and depending on a specific drive speed of the fan.
  • control device can be designed to control the variable displacement pump.
  • control device can comprise a storage unit in which at least one characteristic curve or a characteristic curve field for the performance of the variable displacement pump and at least one characteristic curve for the performance of the fan is stored, as well as a computing unit which evaluates the at least one characteristic curve or the at least one characteristic curve field of the variable displacement pump and the fan for controlling the valve arrangement.
  • control device can be set up to use the at least one characteristic curve for the power of the variable displacement pump and for the power of the fan to determine a difference value for the output power of the variable displacement pump and the speed-dependent power consumption of the fan and to compare it with limit values stored in the memory unit and, if a first limit value is undershot, to operate the activation pump by controlling the valve arrangement in the first switching position to supply the heat exchanger and, if a second limit value is exceeded, to operate it in the second switching position to drive the fan and the working hydraulics.
  • the first limit value can represent a power reserve available to the working hydraulics, which results from the difference between the output power of the variable displacement pump and the power taken off by the fan.
  • the second limit value can represent a lower limit of the power reserve, when this is reached, the valve arrangement is controlled in order to switch on the activation pump by changing from the first switching position to the second switching position. If the first limit value is exceeded again, the valve arrangement is controlled again in order to switch back to the first switching position.
  • This design has the advantage that a smaller power reserve has to be provided by the variable displacement pump.
  • the variable displacement pump can thus be better utilized and is a range with a good level of efficiency. Peak loads in the hydraulic system are cushioned by switching on the additional pump.
  • control device can be designed to control the valve arrangement as a function of the passing of a threshold value for a steering angle.
  • the control device can preferably be set up to control the valve arrangement depending on a threshold value for a control current of a steering valve of the hydraulic steering system.
  • the work machine can comprise a control unit that is set up for automatic steering of the work machine.
  • the control unit can be set up to control the hydraulic steering system. While the required compensating steering movement when driving on a field to be worked requires a low control current, steering movements such as cornering on the headland require a larger control current for the steering valve.
  • the value for the control current generated by the control unit of the steering system can preferably be transmitted to the control device for evaluation essentially in real time by a bus system, for example a CAN bus system, of the work machine.
  • the control device can be set up to control the valve arrangement depending on a threshold value for a control current of a control valve of the lifting device.
  • the work machine can comprise a control unit that is set up to automatically control the lifting device.
  • the automatic actuation of the lifting device for example when reaching a headland, serves to lift the attachment, which leads to a higher demand for pressure medium than a compensating movement when guiding the attachment above an area that is being driven on or is to be worked on during a work process, in particular a harvesting process.
  • the control unit of the lifting device can also transmit the value it generates for the control current, preferably via a bus system, for example a CAN bus system, of the work machine, essentially in real time to the control device for evaluation.
  • Further preferred operating parameters can be sensor-determined temperatures of cooling media that are cooled directly or indirectly by the hydraulic system.
  • a cooling pump is provided for direct cooling of a cooling medium, here the pressure medium circulating in the hydraulic system.
  • the cooling pump can be part of the hydraulic system.
  • the fan which cools a cooling package, is provided for indirect cooling.
  • the cooling package can include a charge air pressure cooler and/or an engine cooling water cooler. Further cooling media used can be the air from a charge air cooler or the engine oil and/or the cooling water of a drive motor designed as an internal combustion engine, which are indirectly cooled by the fan of the hydraulic system.
  • variable displacement pump and at least the activation pump can be driven or actuated by a common drive shaft.
  • the radiator pump can also be driven or actuated by the common drive shaft.
  • One advantage of this arrangement is the space efficiency.
  • the variable displacement pump and at least the activation pump can be driven or actuated spatially separately from one another by two drive shafts.
  • the radiator pump can be driven on a common drive shaft of the activation pump or by means of a further drive shaft that only drives the radiator pump.
  • valve arrangement can comprise a directional valve and a check valve, with the directional valve being connected upstream of the heat exchanger and the check valve being connected upstream of the working hydraulics and the fan.
  • the pressure line that connects the variable displacement pump to the fan and the working hydraulics comprises a pressure accumulator that, when an operationally induced load peak occurs, bridges the period within which the valve arrangement is controlled in order to switch on the activation pump to drive the fan and the working hydraulics and to cover the reaction time of the activation pump.
  • an agricultural working machine in particular a self-propelled harvesting machine, which comprises a working hydraulic system, a hydraulic motor connected to a fan and a hydraulic system which is used to supply the working hydraulic system and the hydraulic motor with a Pressure medium is designed and arranged according to independent patent claim 14.
  • a self-propelled harvesting machine which comprises a working hydraulic system, a hydraulic motor connected to a fan and a hydraulic system which is used to supply the working hydraulic system and the hydraulic motor with a Pressure medium is designed and arranged according to independent patent claim 14.
  • FIG.1 an agricultural working machine 1 is shown schematically in side view.
  • the agricultural working machine 1 is designed as a self-propelled harvesting machine, here and preferably as a combine harvester.
  • the working machine 1 has an attachment 2, in the illustrated embodiment an attachment for a combine harvester, which can be changed in height by means of a hydraulically operated lifting device 3.
  • the lifting device 3 is part of a working hydraulics 7 of the working machine 1.
  • the working hydraulics 7 can also include a hydraulic steering system 6, which serves to actuate a steering axle 8 of the working machine 1.
  • the drive motor 4 is equipped with a cooling device 5, which serves to cool the cooling media used, the air of a charge air cooler or the engine oil and/or the cooling water of the drive motor 4 designed as an internal combustion engine.
  • the cooling device 5 comprises a hydraulically driven fan 15.
  • the reference number 9 designates a hydraulic system for the work machine 1.
  • the representation according to Fig. 2 shows an example of a simplified circuit diagram of the hydraulic system 9 of the agricultural work machine 1.
  • the hydraulic system 9 comprises a variable displacement pump 10.
  • the hydraulic system 9 is designed as a constant pressure system.
  • the variable displacement pump 10 is designed and configured to supply the working hydraulics 7 of the work machine 1 and the hydraulic motor 14, which is connected to the fan 15 of the cooling device 5, with a pressure medium that is essentially under constant pressure. To do this, the variable displacement pump 10 sucks in the pressure medium from a pressure medium reservoir T through a suction line 20.
  • a pressure relief valve 16 is provided in the line branch 12, which serves to protect the working hydraulics 7.
  • the pressure medium flows through a common return line 17 to a heat exchanger 18 for cooling.
  • the heat exchanger 18 is followed by a filter 19 through which the pressure medium is passed before it reaches the pressure medium reservoir T.
  • the filter 19 is intended in particular to separate impurities in the pressure medium that can be introduced by the working hydraulics 7.
  • the hydraulic system 9 comprises a cooling pump 22.
  • the cooling pump 22 is connected to the heat exchanger 18 by a supply line 23.
  • the cooling pump 22 sucks pressure medium from the pressure medium reservoir T through a suction line 21. and feeds this to the heat exchanger 18 for cooling the pressure medium flowing back from the working hydraulics 7 and the hydraulic motor 14.
  • the hydraulic system 9 comprises a switching pump 24.
  • the switching pump 24 is connected to a valve arrangement 27 by a supply line 25.
  • the valve arrangement 27 has at least two switching positions, a first switching position and a second switching position.
  • the switching pump 24 is either connected by a supply line 26 to the supply line 23 leading to the heat exchanger 18 or to the pressure line 11 or the line branches 12, 13.
  • the valve arrangement 27 comprises a directional valve 28, in particular a 2/2-way valve, which in the illustrated first switching position of the valve arrangement 27 connects the activation pump 24 to the supply line 26 in a fluid-conducting manner. According to this first switching position, the cooling pump 22 and the activation pump 24 jointly convey pressure medium to the heat exchanger 18.
  • a check valve 29 is arranged between the supply line 25 and the second line branch 13 of the pressure line 11 leading to the hydraulic motor 14, which blocks in the direction of the activation pump 24.
  • the pressure medium conveyed by the activation pump 24 flows out via the directional valve 28 and passes through the supply line 26 into the supply line 23 and from there to the heat exchanger 18.
  • the working hydraulics 7 and the hydraulic motor 14 for driving the fan 15 are supplied exclusively by the variable displacement pump 10.
  • the pressure line 11, which connects the variable displacement pump 10 through the line branch 13 to the fan 15 and the line branch 12 to the working hydraulics 7, comprises a pressure accumulator 30 which provides pressure medium.
  • the pressure accumulator 30 serves to cushion a drop in pressure in the hydraulic system 9.
  • Fig.3 shows an example of the circuit diagram according to Fig. 2 with the valve arrangement 27 in the second switching position.
  • the fluid-conducting connection between the feed line 25 and the supply line 26 are interrupted.
  • the pressure medium delivered by the activation pump 24 flows via the check valve 29 into the two line branches 12, 13. This serves to compensate for an operationally induced pressure drop in the hydraulic system 9, which can occur in response to activation of the working hydraulics 7.
  • Such a situation occurs, among other things, when the lifting device 3 is automatically activated as part of the working hydraulics 7 in order to lift the attachment 2 by means of the lifting device 3, for example when reaching the headland. Actuating the lifting device 3 to lift the attachment 2 leads to an increased need for pressure medium.
  • the valve arrangement 27 is assigned a control device 31 which is designed to control the valve arrangement 27 depending on at least one detected operating parameter of the hydraulic system 9 and/or the working hydraulics 7 supplied by the hydraulic system 9 and/or the fan 15 supplied by the hydraulic system 9.
  • the control device 31 comprises a memory unit 32 and a computing unit 33. Furthermore, the control device 31 is connected to at least one sensor arrangement 34 of the hydraulic system 9 and/or the working hydraulics 7. Signals received from the at least one sensor arrangement 34 are evaluated by the computing unit 33 to determine operating parameters.
  • Operating parameters are the power consumption of the variable displacement pump 10 and the drive speed of the fan 15.
  • An operating parameter of the hydraulic steering system 6 is the control current of a steering valve of the hydraulic steering system 6.
  • An operating parameter of the lifting device 3 is the control current of a control valve of the Lifting device 3.
  • a further operating parameter is the sensor-determined temperature of cooling media which is cooled directly or indirectly by the hydraulic system 9.
  • At least one characteristic curve 36 or a characteristic curve field for the performance of the variable displacement pump 10 and at least one characteristic curve 35 for the performance of the fan 15 can be stored in the memory unit 32 of the control device 31.
  • the computing unit 33 is set up to evaluate the at least one characteristic curve 35, 36 or the at least one characteristic curve field in order to control the valve arrangement 27.
  • the control device 31 is set up to use the at least one characteristic curve 35 for the power of the variable displacement pump 10 and for the power of the fan 15 to determine a difference value for the output power of the variable displacement pump 10 and the speed-dependent power consumption of the fan 15.
  • the difference value is compared with limit values stored in the memory unit 32. If a first limit value G1 is undershot, the activation pump 24 is operated by controlling the valve arrangement 27 in the first switching position to supply the heat exchanger 18 via the activation pump 24. If a second limit value G2 is exceeded, the valve arrangement is operated in the second switching position to drive the fan 15 and the working hydraulics 7 via the activation pump 24.
  • the first limit value G1 can represent a power reserve available to the working hydraulics 7, which results from the difference between the output power of the variable displacement pump 10 and the power consumed by the fan 15.
  • the second limit value G2 can represent a lower limit of the power reserve, upon reaching which the valve arrangement 27 is controlled in order to switch on the activation pump 24 to operate the fan 15 by changing from the first switching position to the second switching position. If the first limit value G1 is again undershot, the valve arrangement 27 is controlled again in order to switch back to the first switching position.
  • Fig.4 shows an exemplary course of the characteristic curve 35 of the fan 15 of the working machine 1
  • Fig.5 shows an example of a performance characteristic curve 36 of the variable displacement pump 10 and a performance characteristic curve 37 of the variable displacement pump 10 and the activation pump 24 of the hydraulic system 9 switched on in the second switching position.
  • the power requirement of the fan 15 is shown as a function of the speed and increases disproportionately with increasing fan speed.
  • the characteristic curve 35 of the fan 15 depends, among other things, on the geometry of the fan 15, the air resistance of a cooler package and its surroundings, as well as the air density, which in turn depends on the ambient temperature and the air humidity.
  • the cooler package can include a charge air pressure cooler and/or an engine cooling water cooler. Another component of the cooler package can be an evaporator of an air conditioning system.
  • variable displacement pump 10 depends on the drive motor speed of the drive motor 4, which in turn is subject to fluctuations depending on the operating situation of the work machine 1, in particular when driving in the field and on the road. In both operating situations, engine suppression, i.e. a drop in the drive motor speed, can occur, which can lead to the variable displacement pump 10 not providing sufficient pumping capacity for the operation of the fan 15 and/or other hydraulic consumers.
  • the control of the valve arrangement 27 can also be based on the control current of the steering valve as an operating parameter of the hydraulic steering system 6 and/or the control current of the control valve of the lifting device 3 as an operating parameter of the lifting device 3.
  • the control device 31 can be set up to control the valve arrangement 27 depending on a threshold value for the control current of the steering valve of the hydraulic steering system 6.
  • the work machine 1 can comprise a control unit that is set up for automatic steering of the work machine 1.
  • the control unit can be set up for automatic control of the hydraulic steering system 6. While the required compensating steering movement when driving on a field to be worked requires a small control current, steering movements such as cornering on the headland require a larger control current for the steering valve.
  • the value for the control current generated by the control unit can preferably be transmitted by a bus system, for example a CAN bus system, of the work machine 1 essentially in real time to the control device 31 for evaluation.
  • control device 31 can be set up to control the valve arrangement 27 depending on the threshold value for the control current of the control valve of the lifting device 3.
  • the work machine 1 can comprise a control unit that is set up to automatically control the lifting device 3.
  • the automatic actuation of the lifting device 3, for example when reaching a headland, serves to lift the attachment 2, which leads to a higher demand for pressure medium than a compensating movement when guiding the attachment 2 above an area being driven on or to be worked on during a work process, in particular a harvesting process.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
EP23212658.1A 2023-01-24 2023-11-28 Système hydraulique pour machine de travail agricole Active EP4407156B1 (fr)

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DE102023101659.8A DE102023101659A1 (de) 2023-01-24 2023-01-24 Hydrauliksystem für eine landwirtschaftliche Arbeitsmaschine

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DE102024204879B3 (de) * 2024-05-27 2025-10-16 Hawe Hydraulik Se Hydrauliksystem mit Kühlkreislauf sowie Werkzeugmaschine
CN120140302B (zh) * 2025-05-15 2025-07-22 太原理工大学 具有主动散热与冗余驱动的液压系统及控制方法

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EP2636907B1 (fr) 2012-03-05 2020-03-25 CLAAS Selbstfahrende Erntemaschinen GmbH Système hydraulique pour une machine de travail automobile

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JP2006090156A (ja) * 2004-09-21 2006-04-06 Shin Caterpillar Mitsubishi Ltd 廃熱エネルギ再生方法および廃熱エネルギ再生装置
WO2012030003A1 (fr) * 2010-09-02 2012-03-08 볼보 컨스트럭션 이큅먼트 에이비 Circuit hydraulique pour équipement de construction
DE102012003320A1 (de) * 2012-02-18 2013-08-22 Robert Bosch Gmbh Mobile Arbeitsmaschine mit Energierückgewinnung zum Antrieb der Motorkühlung
EP2855784A4 (fr) * 2012-05-30 2016-06-01 Volvo Constr Equip Ab Procédé pour récupérer de l'énergie et système hydraulique

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2636907B1 (fr) 2012-03-05 2020-03-25 CLAAS Selbstfahrende Erntemaschinen GmbH Système hydraulique pour une machine de travail automobile

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