EP2677180B1 - Dispositif d'entraînement hydraulique d'un engin de chantier - Google Patents

Dispositif d'entraînement hydraulique d'un engin de chantier Download PDF

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Publication number
EP2677180B1
EP2677180B1 EP12747270.2A EP12747270A EP2677180B1 EP 2677180 B1 EP2677180 B1 EP 2677180B1 EP 12747270 A EP12747270 A EP 12747270A EP 2677180 B1 EP2677180 B1 EP 2677180B1
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EP
European Patent Office
Prior art keywords
control device
control
boom
arm
center bypass
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.)
Active
Application number
EP12747270.2A
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German (de)
English (en)
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EP2677180A1 (fr
EP2677180A4 (fr
Inventor
Masahiro Kayane
Kazuhiro Ichimura
Katsuaki Kodaka
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Hitachi Construction Machinery Co Ltd
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Hitachi Construction Machinery Co Ltd
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Publication date
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Publication of EP2677180A1 publication Critical patent/EP2677180A1/fr
Publication of EP2677180A4 publication Critical patent/EP2677180A4/fr
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    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2282—Systems using center bypass type changeover valves
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2285—Pilot-operated systems
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of 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
    • 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

Definitions

  • This invention relates to a working machine as known from JP H 06280810 , such as a hydraulic excavator, having working equipment that includes working elements such as a boom and arm and can perform normal operation and precision operation which.is performed by a smaller manipulation stroke at a slower manipulation speed than the normal operation.
  • the hydraulic drive system is provided with an open-center directional control valve, and positively controls a variable displacement hydraulic pump.
  • JP-11-82416 A As a conventional technology including an open- center positive control system of this type, there is one disclosed in JP-11-82416 A .
  • This conventional technology includes an open-center boom directional control valve, arm directional control valve and the like, which are arranged in a center bypass line communicating a variable displacement hydraulic pump and a reservoir with each other, and variably controls the displacement of the variable displacement hydraulic pump according to manipulation strokes of control devices that switchingly control the boom directional control valve, arm directional control device and the like, respectively.
  • JPH 06280810 A describes a working machine with a hydraulic drive system capable of controlling the displacement volume of a variable displacement hydraulic pump according to the operation mode of the operating device.
  • a control of the opening of a center bypass valve by the load pressure of an actuator is not disclosed.
  • an extra pump flowvolume is facilitated to flow to the reservoir via the directional control valves and center bypass line in precision operation, which is performed by making, for example, the manipulation strokes or manipulation speeds of the control devices smaller or slower, when the system is set with a view to assuring good controllability in normal work such as digging work. Therefore, substantial energy is drained without effective use in work so that energy loss tends to occur.
  • the system is set with a view to reducing an extra flowvolume to be flowed to the reservoir in precision operation as described above, the operability in normal work deteriorates conversely. With the conventional technology, it has hence been difficult to achieve both of a reduction in energy loss in precision work and the assurance of good operability in normal work.
  • the present invention has as an object thereof the provision of a working machine with a hydraulic drive system, which can realize the assurance of good operability in normal operation and precision operation and a reduction in energy loss in the precision operation.
  • a control signal is outputted from the pump delivery rate control unit of the controller to the displacement control device to control the variable displacement hydraulic pump at a relatively large displacement corresponding to the normal operation.
  • a large flow volume is fed from the variable displacement hydraulic pump to the working element actuator via the directional control valve for the working element.
  • a control signal is outputted from the center bypass valve control unit of the controller to the center bypass valve control device to open or close the center bypass valve.
  • a large flow volume can be returned from the working element actuator to the reservoir via the center bypass line and center bypass valve .
  • a control signal is outputted from the pump delivery rate control unit of the controller to the displacement control device to make the displacement of the variable displacement hydraulic pump smaller than the displacement corresponding to normal operation.
  • a flow volume which is smaller compared with that at the time of the normal operation is fed from the variable displacement hydraulic pump to the working element actuator via the directional control valve for the working element.
  • a control signal is outputted from the center bypass valve control unit of the controller to the center bypass valve control device to control the center bypass valve in a switched state between the fully open position and the fully closed position.
  • a control signal is outputted, even at the time of precision operation, from the center bypass valve control unit of the controller to the center bypass valve control device to make the opening amount of the center bypass valve still smaller in a predetermined switched state between the fully open position and the fully closed position.
  • a control signal is outputted, even at the time of precision operation, from the center bypass valve control unit of the controller to the center bypass valve control device to make the opening amount of the center bypass valve greater compared with the above-mentioned opening amount at the time of the heavy load in a predetermined switched state between the fully open position and the fully closedposition.
  • the delivery pressure of the variable displacement hydraulic pump is kept low, thereby assuring good operability upon work that relies upon the precision and light load operation. It is also possible to limit the output of the variable displacement hydraulic pump at this time and hence to reduce energy loss.
  • the controller may perform, based on the manipulation stroke, the manipulation speed or a manipulation acceleration of the working element control device, processing to compute that the working element control device is in the manipulation mode considered to correspond to the precision operation.
  • the working machine may be a hydraulic excavator
  • the working element may comprise a boom and an arm
  • the working element actuator may comprise a boom cylinder for actuating the boom and an arm cylinder for actuating the arm
  • the directional control valve for the working element may comprise a boom directional control valve for controlling the boom cylinder and an arm directional control valve for controlling the arm cylinder
  • the working element control device may comprise a boom control device for switchingly controlling the boom directional control valve, and an arm control device for switchingly controlling the arm directional control valve.
  • the hydraulic drive system may be further provided with a delivery pressure sensor for detecting a delivery pressure of the variable displacement hydraulic pump, or a bottom pressure sensor for detecting a bottom pressure of the boom cylinder and a rod pressure sensor for detecting a rod pressure of the arm cylinder
  • the center bypass valve control unit of the controller may perform, according to at least one of a manipulation stroke of the boom control device and a manipulation stroke of the arm control device and the delivery pressure detected at the delivery pressure sensor or according to at least one of the manipulation stroke of the boom control device and the manipulation stroke of the arm control device, the bottom pressure detected at the bottom pressure sensor and the rod pressure detected at the rod pressure sensor, control processing to output a control signal to control the center bypass valve at a relatively large opening amount when the working element control device is in the manipulation mode considered to correspond to the precision operation and the load pressure on the working element actuator is in the low state.
  • the controller is provided with the pump delivery rate control unit and the center bypass valve control unit.
  • the pump delivery rate control unit outputs, to the displacement control device that controls the displacement of the variable displacement hydraulic pump, a control signal to control the variable displacement hydraulic pump at corresponding one of mutually-different displacements according to normal operation or precision operation, while the center bypass valve control unit outputs, to the center bypass valve control device that controls the center bypass valve, a control signal to control the center bypass valve at corresponding one of mutually-different center bypass opening amounts according to the normal operation or precision operation, and outputs, to a control terminal of the above-mentioned proportional solenoid valve, a control signal to control the proportional solenoid valve at corresponding one of mutually-different center bypass opening amounts according to the level of a load pressure on the working element actuator at the time of the precision operation.
  • FIG. 1 is a side view showing a hydraulic excavator exemplified as a working machine.
  • the hydraulic drive system according to the first embodiment is arranged, for example, on a hydraulic excavator, which is provided with a travel base 1, an upperstructure 2 mounted on the travel base 1, and working equipment 3 attached tiltably in an up-and-down direction to the upperstructure 2.
  • the working equipment 3 includes, together with a boom 4, arm 5 and bucket 6 that make up a working element, working element actuators, for example, a boom cylinder 7 for actuating the boom 4, an arm cylinder 8 for actuating the arm 5, and a bucket cylinder 9 for actuating the bucket 6.
  • FIG. 2 is an electrical and hydraulic circuit diagram illustrating a hydraulic drive system according to a first embodiment, which is arranged on the hydraulic excavator shown in FIG. 1
  • FIG. 3 is a block diagram illustrating the configuration of a pump delivery rate control unit included in a controller arranged in the hydraulic drive system according to the first embodiment illustrated in FIG. 2
  • FIG. 4 is a block diagram illustrating the configuration of a center bypass valve control unit included in the controller arranged in the hydraulic drive system according to the first embodiment illustrated in FIG. 2 .
  • the hydraulic drive system is provided with a variable displacement hydraulic pump 10, a servo valve 20 and control actuator 20a included in a regulator for the variable displacement hydraulic pump 10, and a control device for controlling the servo valve 20, specifically a displacement control device, for example, a solenoid-operated proportional reducing valve 21 for controlling the displacement of the variable displacement hydraulic pump 10.
  • This embodiment is also provided, in addition to the above-mentioned boom cylinder 7 and arm cylinder 8 that are operated by pressure oil delivered from the variable displacement hydraulic pump 10 and make up the working element actuators, with open-center directional control valves for the working elements, specifically a boom directional control valve 14 and arm directional control valve 15, which are arranged in a center bypass line 60 communicating the variable displacement hydraulic pump 10 and a reservoir 34 with each other and control flows of pressure oil to be fed from the variable displacement hydraulic pump 10 to the boom cylinder 7 and arm cylinder 8. Also provided are working element control devices for switchingly controlling the boom directional control valve 14 and arm directional control valve 15, specifically a boom control device 12 and arm control device 13.
  • the first embodiment is also provided with a center bypass valve 22, which is arranged in a part of the center bypass line 60, said part being located downstream of the boom directional control valve 14, and can control a flow volume to be returned to the reservoir 34 via the center bypass line 60, and a center bypass valve control device, for example, a proportional solenoid valve 23 for controlling the center bypass valve 22.
  • the first embodiment is further provided with a controller 31, which controls the solenoid-operated proportional reducing valve 21 via a signal line 32 and also the proportional solenoid valve 23 via a signal line 33.
  • This controller 31 is provided with a below-described pump delivery rate control unit 40 for performing control processing to output a control signal to a control terminal of the solenoid-operated proportional reducing valve 21 via the signal line 32 to control the variable displacement hydraulic pump 10 at a displacement corresponding to normal operation when the boom control device 12 and arm control device 13 are in manipulation modes considered to correspond to the normal operation or to output a control signal to the control terminal of the solenoid-operated proportional reducing valve 21 via the signal line 32 to make the displacement of the variable displacement hydraulic pump 10 smaller than the displacement corresponding to the normal operation when the boom control device 12 and arm control device 13 are in manipulation modes considered to correspond to the precision operation.
  • the controller 31 is also provided with a below-described center bypass valve control unit 50 for performing control processing to output, to a control terminal of the proportional solenoid valve 23 via the signal line 33, a control signal to open or close the center bypass valve 22 when the boom control device 12 and arm control device 13 are in the manipulation modes considered to correspond to the normal operation or a control signal to control the center bypass valve 22 in a predetermined switched state (a state that the center bypass line 60 is restricted by the center bypass valve 22) between the fully open position and the fully closed position.
  • a predetermined switched state a state that the center bypass line 60 is restricted by the center bypass valve 22
  • This center bypass valve control unit 50 also performs control processing to output, to the control terminal of the proportional solenoid valve 23 via the signal line 33, a control signal to make the opening amount of the center bypass valve 22 still smaller in a predetermined switched state between the fully open position and the fully closed position when the boom control device 12 and arm control device 13 are in the operation modes considered to correspond to the precision operation or a control signal to make the opening amount of the center bypass valve 22 greater compared with that at the time of the above-mentioned high load pressure despite the center bypass valve 22 is in a predetermined switched position between the fully open position and the fully closed position when the boom control device 12 and arm control device 13 are in the manipulation modes considered to correspond to the precision operation and the load pressures on the boom cylinder 7 and arm cylinder 8 are in low states.
  • the first embodiment is also provided with a pilot pump 11 for feeding a pilot pressure to the boom control device 12 and arm control device 13, and a delivery pressure sensor 24 for detecting a delivery pressure of the variable displacement hydraulic pump 10. Also provided are a boom-raising pressure sensor 25 for detecting a pilot pressure to be produced upon boom-raising operation by the boom control device 12, a boom-lowering pressure sensor 26 for detecting a pilot pressure to be produced upon boom-lowering operation by the boom control device 12, an arm-dumping pressure sensor 27 for detecting a pilot pressure to be produced upon arm-dumping operation by the arm control device 13, and an arm-crowding pressure sensor 28 for detecting a pilot pressure to be produced upon arm-crowding operation by the arm control device 13.
  • the first embodiment is also provided with a bottom pressure sensor 29 for detecting a bottom pressure of the boom cylinder 7 and a rod pressure sensor 30 for detecting a rod pressure of the arm cylinder 8.
  • the above-mentioned pump delivery rate control unit 40 of the controller 31 is provided with a function generating unit 40a for the boom, which includes a boom-raising function generating unit 40a1 and a boom-lowering function generating unit 40a2.
  • the boom-raising function generating unit 40a1 computes a displacement of the variable displacement hydraulic pump 10, which corresponds to a signal outputted from the boom-raising pressure sensor 25 in commensurate with a boom-raising manipulation stroke of the boom control device 12.
  • the boom-lowering function generating unit 40a2 computes a displacement of the variable displacement hydraulic pump 10, which corresponds to a signal outputted from the boom-lowering pressure sensor 26 in commensurate with a boom-lowering manipulation stroke of the boom control device 12.
  • the function generating unit 40a for the boom is configured to produce a displacement such that it takes a greater value as the lever manipulation stroke of the boom control device 12 becomes greater.
  • the pump delivery rate control unit 40 is also provided with a function generating unit 40b for the arm, which includes an arm-crowding function generating unit 40b1 and an arm-dumping function generating unit 40b2.
  • the arm-crowding function generating unit 40b1 computes a displacement of the variable displacement hydraulic pump 10, which corresponds to a signal outputted from the arm-crowding pressure sensor 28 in commensurate with an arm-crowding manipulation stroke of the arm control device 13.
  • the arm-dumping function generating unit 40b2 computes a displacement of the variable displacement hydraulic pump 10, which corresponds to a signal outputted from the arm-dumping pressure sensor 27 in commensurate with an arm-dumping manipulation stroke of the arm control device 13.
  • This function generating unit 40b for the arm is also configured to produce a displacement such that it takes a greater value as the lever manipulation stroke of the arm control device 13 becomes greater.
  • the pump delivery rate control unit 40 is also provided with a maximum selection unit 40c, which selects one having a maximum value from a displacement outputted from the boom-raising function generating unit 40a1 and a displacement outputted from the boom-lowering function generating unit 40a2 in the function generating unit 40a for the boom.
  • the pump delivery rate control unit 40 is also provided with a maximum selection unit 40d, which selects one having a maximum value from a displacement outputted from the arm-crowding function generating unit 40b1 and a displacement outputted from the arm-dumping function generating unit 40b2 in the function generating unit 40b for the arm.
  • the pump delivery rate control unit 40 also includes an addition unit 40e and a control function generating unit 40f.
  • the addition unit 40e adds the displacement outputted from the maximum selection unit 40c and the displacement outputted from the maximum selection unit 40d.
  • the control function generating unit 40f outputs, to the control terminal of the solenoid-operated proportional reducing valve 21, a control signal corresponding to a displacement outputted from the addition unit 40e.
  • the control function generating unit 40f is configured to output, to the control terminal of the solenoid-operated proportional reducing valve 21, the control signal such that it takes a smaller value as the value of the displacement outputted from the addition unit 40e becomes greater.
  • the above-mentioned center bypass valve control unit 50 of the controller 31 is provided with a first differential pressure generating unit 50a that outputs a target differential pressure, which is a target value for a differential pressure between a pump delivery pressure and a boom bottom pressure, corresponding to a boom-raising manipulation stroke of the boom control device 12.
  • This first differential pressure generating unit 50a is configured to output a greater target differential pressure as the pressure outputted from the boom-raising pressure sensor 25 becomes higher.
  • the center bypass valve control unit 50 is provided with a first subtraction unit 50b and a second subtraction unit 50c.
  • the first subtraction unit 50b subtracts a pressure, which is outputted by the bottom pressure sensor 29 of the boom cylinder 7, from a pressure, which is outputted by the delivery pressure sensor 24, to compute an actual differential pressure as the differential pressure between the actual pump delivery pressure and the actual boom bottom pressure.
  • the second subtraction unit 50c subtracts the actual differential pressure, which is outputted by the first subtraction unit 50b, from the target differential pressure outputted by the first differential pressure generating unit 50a.
  • the center bypass valve control unit 50 is also provided with a second differential pressure generating unit 50b that outputs a target differential pressure, which is a target value for a differential pressure between a pump delivery pressure and an arm rod pressure, corresponding to an arm-dumping manipulation stroke of the arm control device 13.
  • This second differential pressure generating unit 50d is also configured to output a greater target differential pressure as the pressure outputted from the arm-dumping pressure sensor 27 becomes higher.
  • the center bypass valve control unit 50 is provided with a third subtraction unit 50e and a fourth subtraction unit 50f.
  • the third subtraction unit 50e subtracts a pressure, which is outputted by the rod pressure sensor 30 of the arm cylinder 8, from a pressure, which is outputted by the delivery pressure sensor 24, to compute an actual differential pressure as the differential pressure between the actual pump delivery pressure and the actual arm rod pressure.
  • the fourth subtraction unit 50f subtracts the actual differential pressure, which is outputted by the third subtraction unit 50e, from the target differential pressure outputted by the second differential pressure generating unit 50d.
  • the center bypass valve control unit 50 also includes a maximum selection unit 50g, a control signal computing unit 50h, and an addition unit 50i.
  • the maximum selection unit 50g selects one having a maximum value from the difference between the target differential pressure and the actual differential pressure as outputted from the second subtraction unit 50c and the difference between the target differential pressure and the actual differential pressure as outputted from the fourth subtraction unit 50f.
  • the control signal computing unit 50h converts, to a control signal, the difference outputted from the maximum selection unit 50g.
  • the addition unit 50i adds the current control signal, which has been converted at the control signal computing unit 50h, to the preceding control value to produce a new control signal.
  • control signal computing unit 50 performs computing processing to output, for example, a control signal of a smaller value as the difference outputted from the maximum selection unit 50g becomes greater. Owing to such a configuration as described above, the pump delivery pressure is controlled to become higher than the load pressure on the actuator by the difference between the target differential pressure selected at the maximum selection unit 50g and the actual differential pressure.
  • the large manipulation stroke of the boom control device 12 is detected at the boom-raising pressure sensor 25 and is inputted to the boom-raising function generating unit 40a1 included in the pump delivery rate control unit 40 of the controller 31, as illustrated in FIG. 3 .
  • the large manipulation stroke of the arm control device 13 is detected at the arm-dumping pressure sensor 27 and is inputted to the arm-dumping function generating unit 40b2 included in the pump delivery rate control unit 40.
  • displacements of large values are outputted from the boom-raising function generating unit 40a1 and arm-dumping function generating unit 40b2 to the maximum selection units 40c,40d, respectively, and these values are added at the addition unit 40e, from which the thus-added value is outputted to the control function generating unit 40f.
  • a control signal of a small value is outputted from the control function generating unit 40f to the solenoid-operated proportional reducing valve 21 illustrated in FIG. 2 .
  • the solenoid-operated proportional reducing valve 21 tends to be switched under its spring force to a side of an upper valve chamber as viewed in FIG. 2 , so that a control port of the servo valve 20 tends to be connected to the boom control device 12 and arm control device 13 via the solenoid-operated proportional reducing valve 21, and under a pilot pressure outputted corresponding to the manipulation strokes of the boom control device 12 and arm control device 13, the servo valve 20 tends to be switched to a side of a left position as viewed in FIG. 2 .
  • variable displacement hydraulic pump 10 is controlled to have a large displacement so that a large flow volume is delivered from the variable displacement hydraulic pump 10.
  • the boom directional control valve 14 is switched to a left position in FIG. 2
  • the arm directional control valve 15 is switched to a right position inFIG. 2. Therefore, the pressure oil of the large flow volume delivered from the hydraulic pump 10 is fed to a rod chamber of the arm cylinder 8 via the arm directional control valve 15, and is also fed to a bottom chamber of the boom cylinder 7 via the boom directional control valve 14.
  • the boom cylinder 7 extends to perform boom-raising operation, while the arm cylinder 8 retracts to perform arm-dumping operation.
  • pressures for example, high pressures are detected from the bottom pressure sensor 29 for detecting the bottom pressure of the boom cylinder 7 and the rod pressure sensor 30 for detecting the rod pressure of the arm cylinder 8, respectively.
  • the pressure detected at the bottom pressure sensor 29 is, therefore, subtracted from the pressure detected at the delivery pressure sensor 24 to compute a small actual differential pressure between the pump delivery pressure and the boom bottom pressure, and the small actual differential pressure is outputted to the subtraction unit 50c.
  • the first differential pressure generating unit 50a outputs a large target differential pressure to the subtraction unit 50c.
  • the actual differential pressure outputted by the subtraction unit 50b is subtracted from the target differential pressure outputted by the first differential pressure generating unit 50a, and the difference between the target differential pressure and the actual differential pressure, said difference having a relatively large value, is outputted to the maximum selection unit 50g.
  • the pressure detected at the rod pressure sensor 30 is subtracted from the pressure detected at the delivery pressure sensor 24 to compute a small actual differential pressure between the pump delivery pressure and the arm rod pressure, and the small actual differential pressure is outputted to the subtraction unit 50f.
  • the second differential pressure generating unit 50d outputs a large target differential pressure to the subtraction unit 50f.
  • the actual differential pressure outputted by the subtraction unit 50e is subtracted from the target differential pressure outputted by the second differential pressure generating unit 50d, and the difference between the target differential pressure and the actual differential pressure, said difference being relatively large, is outputted to the maximum selection unit 50g.
  • the maximum selection unit 50g selects the larger difference from the difference between the target differential pressure and the actual differential pressure as outputted from the subtraction unit 50c and the difference between the target differential pressure and the actual differential pressure as outputted from the subtraction unit 50f, and the thus-selected relatively large difference is outputted to the control signal computing unit 50h.
  • the relatively large difference outputted from the maximum selection unit 50g is converted to a relatively small control signal of a value corresponding to the difference, and this relatively small control signal is outputted to the addition unit 50i.
  • this control signal so converted is added to the preceding control value to perform corrective computation for the production of a new control signal, and the thus-computed value is outputted to the control terminal of the proportional solenoid valve 23 illustrated in FIG. 2 .
  • the proportional solenoid valve 23 tends to be switched under its spring force to a side of a lower valve chamber as viewed in FIG. 2 so that the pilot pump 11 and the control port of the center bypass valve 22 are connected with each other.
  • the pilot pressure of the pilot pump 11 is delivered to the control port of the center bypass valve 22 via the proportional solenoid valve 23, and the center bypass valve 22 operates to assume a predetermined switched state between the fully open position and the fully closed position.
  • the small manipulation stroke of the boom control device 12 is detected at the boom-raising pressure sensor 25 and is inputted to the boom-raising function generating unit 40a1 included in the pump delivery rate control unit 40 of the controller 31, as illustrated in FIG. 3 .
  • the small manipulation stroke of the arm control device 13 is detected at the arm-dumping pressure sensor 27 and is inputted to the arm-dumping function generating unit 40b2 included in the pump delivery rate control unit 40, as illustrated in FIG. 3 .
  • displacements of smaller values compared with those at the time of the above-mentioned earth or sand digging work are outputted from the boom-raising function generating unit 40a1 and arm-dumping function generating unit 40b2 to the maximum selection units 40c, 40d, respectively, and these values are added together at the addition unit 40e, from which the thus-added value is outputted to the control function generating unit 40f.
  • a control signal of a large value is outputted from the control function generating unit 40f to the solenoid-operated proportional reducing valve 21 illustrated in FIG. 2 .
  • the solenoid-operated proportional reducing valve 21 tends to be switched against its spring force to a side of a lower valve chamber as viewed in FIG. 2 , so that the control port of the servo valve 20 and the reservoir 34 tend to be communicated with each other, and the servo valve 20 tends to be switched under its spring force to a side of a right position as viewed in FIG. 2 .
  • the pilot pressure from the pilot pump 11 is also fed to the large-diameter chamber of the control piston 20a, and for the difference in area between the large-diameter chamber and the small-diameter chamber, the control piston 20a moves in a right direction in FIG. 2 .
  • the variable displacement hydraulic pump 10 is controlled to have a small displacement so that a small flow volume is delivered from the variable displacement hydraulic pump 10.
  • the boom directional control valve 14 is switched slightly toward the left position in FIG. 2 , and responsive to the arm-dumping manipulation of the arm control device 13 over the small stroke, the arm directional control valve 15 is switched slightly toward the right position in FIG. 2 . Therefore, the pressure oil of the small flow volume delivered from the hydraulic pump 10 is fed to the rod chamber of the arm cylinder 8 via the arm directional control valve 15, and is also fed to the bottom chamber of the boom cylinder 7 via the boom directional control valve 14.
  • the first differential pressure generating unit 50a outputs a small target differential pressure to the subtraction unit 50c.
  • the actual differential pressure outputted by the subtraction unit 50b is subtracted from the target differential pressure outputted by the first differential pressure generating unit 50a, and the difference between the target differential pressure and the actual differential pressure, said difference having a relatively large value, is outputted to the maximum selection unit 50g.
  • the high pressure detected at the rod pressure sensor 30 is subtracted from the pressure detected at the delivery pressure sensor 24 to compute a small actual differential pressure, and this small actual differential pressure is outputted to the subtraction unit 50f.
  • the second differential pressure generating unit 50d outputs a small target differential pressure to the subtraction unit 50f.
  • the actual differential pressure outputted by the subtraction unit 50e is subtracted from the target differential pressure outputted by the second differential pressure generating unit 50d, and the difference between the target differential pressure and the actual differential pressure, said difference having a relatively large value, is outputted to the maximum selection unit 50g.
  • the maximum selection unit 50g selects the larger difference from the difference between the target differential pressure and the actual differential pressure as outputted from the subtraction unit 50c and the difference between the target differential pressure and the actual differential pressure as outputted from the subtraction unit 50f, and the thus-selected relatively large difference is outputted to the control signal computing unit 50h.
  • the relatively large difference outputted from the maximum selection unit 50g is converted to a small control signal of a value corresponding to the difference, and this small control signal is outputted to the addition unit 50i.
  • this control signal so converted is added to the preceding control value to perform corrective computation for the production of a new control signal, and the thus-computed value is outputted to the control terminal of the proportional solenoid valve 23 illustrated in FIG. 2 .
  • the proportional solenoid valve 23 tends to be switched under its spring force to the side of the lower valve chamber as viewed in FIG. 2 so that the pilot pump 11 and the control port of the center bypass valve 22 are connected with each other.
  • the pilot pressure of the pilot pump 11 is delivered to the control port of the center bypass valve 22, and the center bypass valve 22 assumes a predetermined switched state between the fully open position and the fully closed position and its opening amount becomes still smaller.
  • the center bypass line 60 tends to be closed. It is, therefore, possible to perform combined boom-raising and arm-dumping operation, which is precision operation of slow operation speed and becomes high in the load pressures on the actuators, and hence to perform the desired crane work.
  • control at the pump delivery rate control unit 40 of the controller 31 is similar to that in the above-described crane operation, but control different from that at the time of the crane work is performed at the center bypass valve control unit 50.
  • the low pressure detected at the bottom pressure sensor 29 is, therefore, subtracted from the pressure detected at the delivery pressure sensor 24 to compute a large actual differential pressure, and this large actual differential pressure is outputted to the subtraction unit 50c.
  • the first differential pressure generating unit 50a outputs a small target differential pressure to the subtraction unit 50c.
  • the actual differential pressure outputted by the subtraction unit 50b is subtracted from the target differential pressure outputted by the first differential pressure generating unit 50a, and the difference between the target differential pressure and the actual differential pressure, said difference having a relatively small value, is outputted to the maximum selection unit 50g.
  • the low pressure detected at the rod pressure sensor 30 is subtracted from the pressure detected at the delivery pressure sensor 24 to compute a large actual differential pressure, and this large actual differential pressure is outputted to the subtraction unit 50f .
  • the second differential pressure generating unit 50d outputs a small target differential pressure to the subtraction unit 50f.
  • the actual differential pressure outputted by the subtraction unit 50e is subtracted from the target differential pressure outputted by the second differential pressure generating unit 50d, and the difference between the target differential pressure and the actual differential pressure, said difference being of a relatively small value, is outputted to the maximum selection unit 50g.
  • the maximum selection unit 50g selects the larger but small difference from the difference between the target differential pressure and the actual differential pressure as outputted from the subtraction unit 50c and the difference between the target differential pressure and the actual differential pressure as outputted from the subtraction unit 50f, and the thus-selected difference is outputted to the control signal computing unit 50h.
  • the small difference outputted from the maximum selection unit 50g is converted to a control signal, and this control signal is outputted to the addition unit 50i.
  • this control signal so selected is added to the preceding control value to perform corrective computation for the production of a new control signal the value of which is slightly greater, and the thus-computed value is outputted to the control terminal of the proportional solenoid valve 23 illustrated in FIG. 2 .
  • the proportional solenoid valve 23 tends to be switched against its spring force to a side of an upper valve chamber as viewed in FIG. 2 , so that the pilot pump 11 and the control port of the center bypass valve 22 tend to be cut off from each other, and on the other hand, the control port of the center bypass valve 22 and the reservoir 34 tend to be connected with each other. Therefore, the center bypass valve 22 assumes, under its spring force, a predetermined switched state between the fully open position and the fully closed position and has a slightly larger opening amount, so that the center bypass line 60 tends to be more opened than at the time of the precision and heavy load operation.
  • FIG. 5 is a diagram depicting control to be performed by the hydraulic drive system according to the first embodiment.
  • the abscissa indicates the lever manipulation stroke, for example, the lever manipulation stroke of the boom control device 12 or the lever manipulation stroke of the arm control device 13, and the ordinate indicates the load pressure on an actuator such as the boom cylinder 7 or arm cylinder 8.
  • the first embodiment can perform control in a normal operation range A with the hydraulic pump 10 being set at a high delivery rate, for example, can perform normal work such as earth or sand digging work can be performed as mentioned above when the manipulation strokes of the boom control device 12 or the manipulation stroke of the arm control device are increased.
  • normal work such as earth or sand digging work
  • the above description is made about the case in which the bottom pressure of the boom cylinder 7 and the rod pressure of the arm cylinder 8 become high but in this normal operation range A, no limitation is fundamentally imposed on the levels of load pressures on the actuators, in other words, the loads on the actuators can fundamentally be either light or heavy.
  • the delivery rate of the hydraulic pump 10 is reduced, so that the speeds of the actuators become slow and precision operation can be performed.
  • the first embodiment configured as described above, it is possible to assure good normal operability that enables to drive working elements such as the boom 4 and arm 5 at fast operation speeds by making greater the manipulation strokes of the boom control device 12 and arm control device 13. In addition, it is also possible to assure good precision operability that enables to drive the working element such as the boom 4 and arm 5 at slow operation speeds by making smaller the manipulation strokes of the boom control device 12 and arm control device 13. It is also possible to limit the output of the variable displacement hydraulic pump 10 at this time, and hence, to realize a reduction in energy loss.
  • the first embodiment raises the delivery pressure of the variable displacement hydraulic pump 10 at the time of heavy load that the load pressures on the boom cylinder 7 and arm cylinder 8 become high, thereby enabling to assure good operability upon work that relies upon this precision and heavy load operation. Even at the time of precision operation, the first embodiment lowers the delivery pressure of the variable displacement hydraulic pump 10 at the time of light load that the load pressures on the boom cylinder 7 and arm cylinder 8 become low, thereby also enabling to assure good operability upon work that relies upon this precision and light load operation. It is also possible to limit the output of the variable displacement hydraulic pump 10 at this time, and hence, to reduce energy loss. Therefore, this embodiment can realize a hydraulic drive system, which can realize the assurance of high-precision operability and is economical, excellent in practicality and high in reliability.
  • the embodiment may also be provided with a configuration which is similar to that in the above-described embodiment but relates to boom-lowering operation and arm-crowding operation. Further, the above-described embodiment may also be provided, as needed, with a configuration which is similar to that in the embodiment but relates to swinging, the operation of the bucket 6, or the operation of an attachment arranged in place of the bucket 6.
  • the first embodiment can perform not only combined operation of the boom 4 and arm 5 but also single operation of the boom 4 and single operation of the arm 5 by the above-described configuration without problem.
  • the above-described first embodiment is configured to perform control corresponding to the manipulation stroke of the boom control device 12 and the manipulation stroke of the arm control device 13.
  • the first embodiment may, however, be configured to compute, at the controller 31, the lever manipulation speed of the boom control device 12 or the lever manipulation speed of the arm control device based on a signal outputted from the bottom pressure sensor 29 arranged on the boom cylinder 7 or a signal outputted from the rod pressure sensor 30 arranged on the arm cylinder 8, and to perform control corresponding to the thus-computed manipulation speed.
  • FIG. 6 depicts control to be performed based on such manipulation speeds by a second embodiment.
  • sign A1 indicates a normal operation range
  • sign B1 indicates an operation range for precision and heavy load operation
  • sign C1 indicates an operation range for precision and light load operation.
  • the manipulation speeds of the boom control device 12 and arm control device 13 are normally made slow by the operator. High-precision control that corresponds more to actual operation conditions can, therefore, be realized if the control is performed based on such manipulation speeds in place of manipulation strokes.
  • computation may be performed at the controller 31 to determine operation accelerations and control may be performed corresponding to the thus-computed operation accelerations.
  • FIG. 7 is a block diagram illustrating the configuration of an essential part of a pump delivery rate control unit included in a controller arranged in a hydraulic drive system according to a third embodiment of the present invention
  • FIG. 8 is a block diagram illustrating the configuration of an essential part of a center bypass valve control unit included in the controller arranged in the hydraulic drive system according to the third embodiment of the present invention.
  • the third embodiment determines whether the work, which is being performed by the working equipment 3, is heavy load work or light load work.
  • a pump delivery rate control unit 40 nor a center bypass valve control unit 70 of a controller 31 said pump delivery rate control unit 40 and center bypass valve control unit 70 being illustrated in FIGS. 7 and 8 , functions, and normal control is performed.
  • the pump delivery rate control unit 40 in the third embodiment is provided with a switch unit 40g connected to the addition unit 40e.
  • the switch unit 40g is turned ON when the signal outputted from the delivery pressure sensor 24 or the signals outputted from the bottom pressure sensor 29 for detecting the bottom pressure of the boom cylinder 7 and the rod pressure sensor 30 for detecting the rod pressure of the arm cylinder 8 is a signal or are signals that corresponds or correspond to light load, but is turned OFF when the signal or signals is a signal or are signals that corresponds or correspond to heavy load.
  • the switch unit 40g is turned ON, an added value from the addition unit 40e is converted to a control signal, which is then outputted to the control function generating unit 40f that controls the solenoid-operated proportional reducing valve 21 for adjusting the displacement of the variable displacement hydraulic pump 10.
  • the third embodiment is also different from the first embodiment in the configuration of the center bypass valve control unit 70 in the controller 31.
  • the center bypass valve control unit 70 in the third embodiment is provided with a boom function generating unit 70a for outputting an opening area of the center bypass valve 22, which corresponds to a manipulation stroke of the boom control device 12, and an arm function generating unit 70b for outputting an opening area of the center bypass valve 22, which corresponds to a manipulation stroke of the arm control device 13.
  • the boom function generating unit 70a includes a boom-raising function generating unit 70a1 and a boom-lowering function generating unit 70a2.
  • the boom-raising function generating unit 70a1 outputs a larger opening amount as the opening amount of the center bypass valve 22 as the boom-raising manipulation stroke becomes smaller, in other words, as the load becomes lighter in precision operation
  • the boom-lowering function generating unit 70a2 outputs a larger opening amount as the opening amount of the center bypass valve 22 as the boom-lowering manipulation stroke becomes smaller, in other words, as the load becomes lighter in precision operation.
  • the relationship between the boom-raising manipulation stroke and the opening amount of the center bypass valve 22 in the boom-raising function generating unit 70a1 and the relationship between the boom-lowering manipulation stroke and the opening amount of the center bypass valve 22 in the boom-lowering function generating unit 70a2 have been set beforehand. It is to be noted that a boom tends to apply a smaller load pressure in its lowering direction under the influence of its dead load, and therefore, compared with the opening amount in the precision operation range set, for example, in the boom-raising function generating unit 70a1, the opening amount in the same precision operation range, said opening amount being to be set in the boom-lowering function generating unit 70a2, can be set greater.
  • the arm function generating unit 70b includes an arm-crowding function generating unit 70b1 and an arm-dumping function generating unit 70b2.
  • the arm-crowding function generating unit 70b1 outputs a larger opening amount as the opening amount of the center bypass valve 22 as the arm-crowding manipulation stroke becomes smaller, in other words, as the load becomes lighter in precision operation
  • the arm-dumping function generating unit 70b2 outputs a larger opening amount as the opening amount of the center bypass valve 22 as the arm-dumping manipulation stroke becomes smaller, in other words, as the load becomes lighter in precision operation.
  • the center bypass valve control unit 70 also includes a maximum selection unit 70c and another maximum selection unit 70d.
  • the maximum selection unit 70c selects greater one of the opening amount of the center bypass valve 22 as outputted from the boom-raising function generating unit 70a1 and the opening amount of the center bypass valve 22 as outputted from the boom-lowering function generating unit 70a2.
  • the maximum selection unit 70d selects greater one of the opening amount of the center bypass valve 22 as outputted from the arm-crowding function generating unit 70b1 and the opening amount of the center bypass valve 22 as outputted from the arm-dumping function generating unit 70b2.
  • the center bypass valve control unit 70 is also provided with an addition unit 70e for adding the opening amount of the center bypass valve 22 as outputted from the above-mentioned maximum selection unit 70c and the opening amount of the center bypass valve 22 as outputted from the above-mentioned maximum selection unit 70d.
  • the center bypass valve control unit 70 is also provided with a switch unit 70f connected to the addition unit 70e.
  • the switch unit 70 is turned ON when the signal outputted from the delivery pressure sensor 24 or the signals outputted from the bottom pressure sensor 29 for detecting the bottom pressure of the boom cylinder 7 and the rodpressure sensor 30 for detecting the rod pressure of the arm cylinder 8 is a signal or are signals that corresponds or correspond to light load but is turned OFF when the signal or signals is a signal or are signals that corresponds or correspond to heavy load.
  • This center bypass valve control unit 70 is also provided with a control function generating unit 70g.
  • the control function generating unit 70g converts the added value, which relates to the opening amount of the center bypass valve 22 and has been obtained at the addition unit 70e, to a control signal and outputs this control signal to the proportional solenoid valve 23 that controls the center bypass valve 22.
  • this control function generating unit 70g a relationship that the value of the control signal increases with the added value obtained at the addition unit 70e has been set beforehand.
  • the remaining configuration in this third embodiment is equivalent to that in the above-described first embodiment.
  • the switch unit 40g is turned OFF so that the output of the added value, which has been obtained at the addition unit 40e, to the control function generating unit 40f is cut off. In this state, processing operation corresponding to heavy load work in a state of normal precision operation is performed.
  • the switch unit 40g When a pressure value detected by the delivery pressure sensor 24 is (or pressure values detected by the bottom pressure sensor 29 and rod pressure sensor 30 are) low at the time of the precision operation and the condition of light load is detected in the precision operation, the switch unit 40g is turned ON so that the added value obtained at the addition unit 40e is outputted to the control function generating unit 40f.
  • the control function generating unit 40f outputs, to the solenoid-operated proportional reducing valve 21, a control signal of large value corresponding to the relatively small value obtained at the addition unit 40e.
  • the proportional solenoid valve 21 therefore, tends to be switched to the side of the lower position in FIG. 2 .
  • the displacement of the variable displacement hydraulic pump 10 is controlled to become small as mentioned above, and from this variable displacement hydraulic pump 10, a small flow volume is delivered.
  • the switch unit 70f of the center bypass valve control unit 70 in this third embodiment is turned OFF so that the output of the added value, which has been obtained at the addition unit 70e, to the control function generating unit 70g is cut off.
  • processing operation corresponding to heavy load work in a state of normal precision operation is performed.
  • the proportional solenoid valve 23 tends to be held at the side of the lower position in FIG. 2 such that the pilot pressure from the pilot pump 11 is guided to the control port of the center bypass valve 22.
  • the center bypass valve 22 is controlled such that it assumes a predetermined switched state between the fully closed position and the fully open position and its opening amount becomes relatively small. A pressure, therefore, arises in the center bypass line 60, thereby making it possible to perform the desired heavy load work by precision operation.
  • the switch unit 70f in the center bypass valve control unit 70 is turned ON so that the added value obtained at the addition unit 70e is outputted to the control function generating unit 70g.
  • the control function generating unit 70g outputs, to the proportional solenoid valve 23, a large control signal value corresponding to the large added value.
  • the proportional solenoid valve 23, therefore, tends to be switched to the side of the upper position in FIG. 2 .
  • the center bypass valve 22 is controlled such that it assumes a predetermined switched state between the fully closed position and the fully open position and its opening amount becomes greater compared with that at the time of the above-described precision operation under heavy load. Therefore, the flow volume that flows to the reservoir 34 via the center bypass line 60 increases, thereby making it possible to perform the desired light load work by precision operation.
  • the third embodiment configured as described above, similar advantageous effects as those available from the first embodiment can be obtained, and moreover, it is necessary to arrange, as pressure sensors for detecting load pressures on the actuators, only either the delivery pressure sensor 24 or the bottom pressure sensor 29 and rod pressure sensor 30. Therefore, the third embodiment can reduce the number of pressure sensors compared with the first embodiment, and can simplify the configuration of the system.

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  • Civil Engineering (AREA)
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Claims (4)

  1. Machine de chantier comprenant :
    un équipement de travail (3) capable d'exécuter un fonctionnement normal et un fonctionnement de précision qui est exécuté par une course de manipulation plus petite ou à une vitesse de manipulation plus lente que le fonctionnement normal ; et
    un système d'entraînement hydraulique étant doté de :
    i. une pompe hydraulique à déplacement variable (10),
    ii. un actionneur d'élément de travail (7, 8) pouvant fonctionner via de l'huile sous pression, qui est distribuée depuis la pompe hydraulique à déplacement variable (10), pour entraîner un élément de travail (4, 5) inclus dans l'équipement de travail (3),
    iii. une vanne de commande directionnelle à centre ouvert (14, 15) pour l'élément de travail, ladite vanne de commande directionnelle à centre ouvert (14, 15) étant agencée dans un conduit de bypass central (60), qui fait communiquer la pompe hydraulique à déplacement variable (10) et un réservoir (34) l'une avec l'autre, pour commander un écoulement d'huile sous pression qu'il s'agit d'alimenter depuis la pompe hydraulique à déplacement variable (10) jusqu'à l'actionneur d'élément de travail (7, 8),
    iv. un dispositif de commande d'élément de travail (12, 13) pour commander de manière commutable la vanne de commande directionnelle (14, 15) pour l'élément de travail,
    v. un dispositif de commande de déplacement (21) pour commander un déplacement de la pompe hydraulique à déplacement variable (10),
    vi. une vanne de bypass centrale (22) agencée dans une partie du conduit de bypass central (60), ladite partie étant située en aval de la vanne de commande directionnelle (14, 15) pour l'élément de travail, et capable de commander un volume d'écoulement qu'il s'agit de renvoyer jusqu'au réservoir (34) via le conduit de bypass central (60),
    vii. un dispositif de commande de vanne de bypass centrale (23) pour commander la vanne de bypass centrale (22), et
    viii. un contrôleur (31) pour commander le dispositif de commande de déplacement (21) et le dispositif de commande de vanne de bypass centrale (23),
    caractérisé en ce que
    le contrôleur (31) inclut :
    une unité de commande de débit de distribution de pompe (40) pour exécuter un traitement de commande pour sortir un signal de commande vers le dispositif de commande de déplacement (21),
    i. pour commander la pompe hydraulique à déplacement variable (10) à un déplacement correspondant au fonctionnement normal dans un cas où le dispositif de commande d'élément de travail (12, 13) est dans un mode de manipulation considéré comme correspondant au fonctionnement normal, et
    ii. pour rendre le déplacement de la pompe hydraulique à déplacement variable (10) plus petit que le déplacement correspondant au fonctionnement normal dans un cas où le dispositif de commande d'élément de travail (12, 13) est dans un mode de manipulation considéré comme correspondant au fonctionnement de précision,
    et
    une unité de commande de vanne de bypass centrale (50, 70) pour exécuter un traitement de commande pour sortir, vers le dispositif de commande de vanne de bypass centrale (23),
    i. un signal de commande (A, A1) pour ouvrir ou fermer la vanne de bypass centrale (22) dans un cas où le dispositif de commande d'élément de travail (12, 13) est dans le mode de manipulation considéré comme correspondant au fonctionnement normal,
    ii. un signal de commande pour commander la vanne de bypass centrale (23) dans un état commuté entre une position entièrement ouverte et une position entièrement fermée dans un cas où le dispositif de commande d'élément de travail (12, 13) est dans le mode de manipulation considéré comme correspondant au fonctionnement de précision,
    iii. un signal de commande (B, B1) pour amener la vanne de bypass centrale (22) à avoir une petite amplitude d'ouverture dans un état commuté entre la position entièrement ouverte et la position entièrement fermée dans un cas où le dispositif de commande d'élément de travail (12, 13) est dans le mode de manipulation considéré comme correspondant au fonctionnement de précision et qu'une pression de charge sur l'actionneur d'élément de travail (7, 8) est dans un état élevé, et
    iv. un signal de commande (C, C1) pour amener la vanne de bypass centrale (22) à avoir une amplitude d'ouverture plus grande que la petite amplitude d'ouverture dans un cas où le dispositif de commande d'élément de travail (12, 13) est dans le mode de manipulation considéré comme correspondant au fonctionnement de précision et que la pression de charge sur l'actionneur d'élément de travail (7, 8) est dans un état bas.
  2. Machine de chantier selon la revendication 1, dans laquelle :
    le contrôleur (31) exécute, sur la base de la course de manipulation, de la vitesse de manipulation ou d'une accélération de manipulation du dispositif de commande d'élément de travail (12, 13), un traitement pour calculer que le dispositif de commande d'élément de travail (12, 13) est dans le mode de manipulation considéré comme correspondant au fonctionnement de précision.
  3. Machine de chantier selon la revendication 2, dans laquelle :
    la machine de chantier est un excavateur hydraulique,
    l'élément de travail (4, 5) comprend une flèche (4) et un bras (5),
    l'actionneur d'élément de travail (7, 8) comprend un vérin de flèche (7) pour actionner la flèche (4) et un vérin de bras (8) pour actionner le bras (5),
    la vanne de commande directionnelle (14, 15) pour l'élément de travail comprend une vanne de commande directionnelle de flèche (14) pour commander le vérin de flèche (7) et une vanne de commande directionnelle de bras (15) pour commander le vérin de bras (8), et
    le dispositif de commande d'élément de travail (12, 13) comprend un dispositif de commande de flèche (12) pour commander de manière commutable la vanne de commande directionnelle de flèche (14), et un dispositif de commande de bras (13) pour commander de manière commutable la vanne de commande directionnelle de bras (15).
  4. Machine de chantier selon la revendication 3, dans laquelle :
    le système d'entraînement hydraulique est en outre doté d'un capteur de pression de distribution (24) pour détecter une pression de distribution de la pompe hydraulique à déplacement variable (10), ou d'un capteur de pression de fond (29) pour détecter une pression de fond du vérin de flèche (7) et d'un capteur de pression de tige (30) pour détecter une pression de tige du vérin de bras (8), et
    l'unité de commande de vanne de bypass centrale (50, 70) du contrôleur (31) est configurée pour exécuter, en accord avec au moins une course parmi une course de manipulation du dispositif de commande de flèche (12) et une course de manipulation du dispositif de commande de bras (13) et la pression de distribution détectée au niveau du capteur de pression de distribution (24), ou en accord avec au moins une course parmi la course de manipulation du dispositif de commande de flèche (12) et la course de manipulation du dispositif de commande de bras (13), la pression de fond détectée au niveau du capteur de pression de fond (29) et la pression de tige détectée au niveau du capteur de pression de tige (30), un traitement de commande pour sortir un signal de commande pour commander la vanne de bypass centrale (22) à une amplitude d'ouverture relativement grande quand le dispositif de commande d'élément de travail (12, 13) est dans le mode de manipulation considéré comme correspondant au fonctionnement de précision et que la pression de charge sur l'actionneur d'élément de travail (7, 8) est dans l'état bas.
EP12747270.2A 2011-02-14 2012-02-09 Dispositif d'entraînement hydraulique d'un engin de chantier Active EP2677180B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011028940A JP5481408B2 (ja) 2011-02-14 2011-02-14 作業機械の油圧駆動装置
PCT/JP2012/052977 WO2012111525A1 (fr) 2011-02-14 2012-02-09 Dispositif d'entraînement hydraulique d'engin de chantier

Publications (3)

Publication Number Publication Date
EP2677180A1 EP2677180A1 (fr) 2013-12-25
EP2677180A4 EP2677180A4 (fr) 2018-02-14
EP2677180B1 true EP2677180B1 (fr) 2021-09-22

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EP (1) EP2677180B1 (fr)
JP (1) JP5481408B2 (fr)
KR (1) KR101913309B1 (fr)
CN (1) CN103380303B (fr)
WO (1) WO2012111525A1 (fr)

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JP5996778B2 (ja) * 2013-03-22 2016-09-21 日立建機株式会社 建設機械の油圧駆動装置
JP6279856B2 (ja) * 2013-08-27 2018-02-14 住友建機株式会社 ショベル用表示装置
KR102425743B1 (ko) * 2015-08-21 2022-07-28 현대두산인프라코어(주) 건설기계 및 건설기계의 제어 방법
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KR101913309B1 (ko) 2018-10-30
WO2012111525A1 (fr) 2012-08-23
EP2677180A1 (fr) 2013-12-25
CN103380303B (zh) 2015-10-14
JP5481408B2 (ja) 2014-04-23
CN103380303A (zh) 2013-10-30
JP2012167735A (ja) 2012-09-06
EP2677180A4 (fr) 2018-02-14
KR20140010066A (ko) 2014-01-23

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