WO2025197375A1 - Engin de chantier - Google Patents

Engin de chantier

Info

Publication number
WO2025197375A1
WO2025197375A1 PCT/JP2025/004824 JP2025004824W WO2025197375A1 WO 2025197375 A1 WO2025197375 A1 WO 2025197375A1 JP 2025004824 W JP2025004824 W JP 2025004824W WO 2025197375 A1 WO2025197375 A1 WO 2025197375A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
pressure
flow rate
hydraulic
accumulator
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.)
Pending
Application number
PCT/JP2025/004824
Other languages
English (en)
Japanese (ja)
Inventor
聖二 土方
剛史 山田
翔 古川
遼 八木澤
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.)
Hitachi Construction Machinery Co Ltd
Original Assignee
Hitachi Construction Machinery Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hitachi Construction Machinery Co Ltd filed Critical Hitachi Construction Machinery Co Ltd
Publication of WO2025197375A1 publication Critical patent/WO2025197375A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force

Definitions

  • the present invention relates to work machines such as hydraulic excavators.
  • Patent Document 1 is an example of a document disclosing prior art related to hydraulic drive systems mounted on work machines such as hydraulic excavators.
  • Patent Document 1 describes a hydraulic drive system equipped with a first hydraulic pump and a second hydraulic pump that are mechanically connected to an engine and driven by engine power, a boom cylinder, an arm cylinder, a bucket cylinder, and a swing motor that are actuators driven by the pressurized oil discharged from each hydraulic pump, and a first accumulator that can store pressurized oil from the first hydraulic pump and the second hydraulic pump.
  • the present invention was made in consideration of the above-mentioned problems, and its purpose is to provide a work machine that can ensure the reliability of the hydraulic pump even when the hydraulic pump capacity is increased due to a reduction in engine speed.
  • the present invention provides a work machine comprising a hydraulic pump, a pump flow rate control device that controls the flow rate of pressurized oil discharged from the hydraulic pump, a hydraulic actuator to which the pressurized oil discharged from the hydraulic pump is supplied, a pressure accumulator that accumulates the pressurized oil discharged from the hydraulic pump, a pressure accumulator flow rate control device that controls the flow rate of pressurized oil supplied from the pressure accumulator to the hydraulic actuator, a pump load detection device that detects the pump load that is the load on the hydraulic pump, and a control device that receives a signal from the pump load detection device and controls the pump flow rate control device and the pressure accumulator flow rate control device, wherein the control device controls the pressure accumulator flow rate control device so that the amount of pressurized oil supplied from the pressure accumulator to the hydraulic actuator increases as the pump load increases, and controls the pump flow rate control device so that the flow rate of pressurized oil discharged from the hydraulic pump decreases in response to an increase in the amount of press
  • FIG. 1 is a perspective view of a hydraulic excavator according to a first embodiment of the present invention.
  • FIG. 1 is a hydraulic circuit diagram of a hydraulic drive system according to a first embodiment of the present invention.
  • FIG. 2 is a block diagram showing the processing of a controller in the first embodiment of the present invention.
  • FIG. 4 is a hydraulic circuit diagram of a hydraulic drive system according to a second embodiment of the present invention.
  • FIG. 10 is a block diagram showing the processing of a controller in a second embodiment of the present invention.
  • FIG. 10 is a block diagram showing the processing of a controller in a third embodiment of the present invention.
  • FIG. 10 is a block diagram showing the processing of a controller in a fourth embodiment of the present invention.
  • FIG. 1 is a perspective view of a hydraulic excavator according to a first embodiment of the present invention.
  • the hydraulic excavator 200 comprises a lower traveling body 201, an upper rotating body 202, and a working device 203.
  • the upper rotating body 202 is driven by a traveling motor 204 (hydraulic actuator).
  • the upper rotating body 202 is rotatably mounted on the lower traveling body 201, and is driven by a swing motor (hydraulic actuator) (not shown).
  • the work device 203 has a boom 205, an arm 206, and a bucket 207.
  • the boom 205 is rotatably supported on the upper rotating body 202 and is driven by a boom cylinder 208 (hydraulic actuator).
  • the arm 206 is rotatably supported on the boom 205 and is driven by an arm cylinder 209 (hydraulic actuator).
  • the bucket 207 is rotatably supported on the arm 206 and is driven by a bucket cylinder 210 (hydraulic actuator).
  • Figure 2 is a hydraulic circuit diagram of the hydraulic drive system mounted on the hydraulic excavator 200. Note that Figure 2 only shows the parts related to driving the hydraulic cylinder 5, which is either the boom cylinder 208, arm cylinder 209, or bucket cylinder 210, and omits the parts related to driving the other actuators.
  • the hydraulic drive system 100 comprises an engine 1 as a power source, a hydraulic pump 3 driven by the engine 1 and sucking in and discharging hydraulic oil from a hydraulic oil tank 2, a pump regulator 4 (pump flow control device) that controls the flow rate of the hydraulic pump 3, a hydraulic cylinder 5 driven by pressurized oil supplied from the hydraulic pump 3, a center bypass type control valve 6 (first control valve) that controls the flow rate of pressurized oil supplied from the hydraulic pump 3 to the bottom side or rod side of the hydraulic cylinder 5 and the flow rate of pressurized oil discharged from the rod side or bottom side of the hydraulic cylinder 5 to the hydraulic oil tank 2, and an accumulator 7 (pressure accumulation device) that stores the pressurized oil discharged from the hydraulic pump 3.
  • a pump regulator 4 pump flow control device
  • first control valve first control valve
  • accumulator 7 pressure accumulation device
  • the hydraulic system includes a control valve 8 (second control valve) that controls the flow rate of pressurized oil flowing from the hydraulic pump 3 to the accumulator 7 and also controls the flow rate of pressurized oil supplied from the accumulator 7 to the hydraulic cylinder 5 via the control valve 6, a control valve 9 that controls the flow rate of pressurized oil discharged from the hydraulic pump 3 to the hydraulic oil tank 2, an operating lever 10 (operating device) that commands the operation of the hydraulic cylinder 5, a pressure sensor 11 (first pressure sensor) that detects the pressure of the hydraulic pump 3, and a control device 12 that receives signals from the operating lever 10 and pressure sensor 11 and controls the engine 1 rotation speed, the flow rate of the hydraulic pump 3, and the flow rate or opening of the control valves 6, 8, and 9.
  • a control valve 8 second control valve
  • the discharge port of the hydraulic pump 3 is connected to the hydraulic oil tank 2 via a center bypass oil passage 13 (first oil passage).
  • Control valves 6 and 9 are arranged in center bypass oil passage 13, from upstream to downstream.
  • Control valve 6 is an open-center flow control valve, and control valve 9 is a center bypass cut valve.
  • Control valve 6 is connected to the bottom side of the hydraulic cylinder 5 via oil passage 14, and to the rod side of the hydraulic cylinder 5 via oil passage 15.
  • the meter port of control valve 6 is connected to the center bypass oil passage 13 via a check valve 16.
  • Check valve 16 prevents backflow of pressurized oil from the hydraulic cylinder 5 to the center bypass oil passage 13.
  • the accumulator 7 is connected via oil passage 17 (second oil passage) to the oil passage portion of the center bypass oil passage 13 that connects the hydraulic pump 3 and the control valve 6.
  • the control valve 8 is disposed in oil passage 17.
  • the control device 12 is equipped with a calculation device such as a CPU, storage devices such as ROM and RAM, and an input/output interface that handles signal input and output between the device and external devices, and realizes the following functions by executing programs stored in the ROM, etc.
  • a calculation device such as a CPU
  • storage devices such as ROM and RAM
  • an input/output interface that handles signal input and output between the device and external devices, and realizes the following functions by executing programs stored in the ROM, etc.
  • the control device 12 When a signal is input from the operating lever 10, the control device 12 increases the flow rate of the hydraulic pump 3 according to the amount of lever operation and switches the control valve 6 in a direction corresponding to the lever operation direction. This causes pressurized oil to be supplied from the hydraulic pump 3 to one side (bottom or rod side) of the hydraulic cylinder 5, while pressure oil is discharged from the other side (rod or bottom side) of the hydraulic cylinder 5 to the hydraulic oil tank 2, causing the hydraulic cylinder 5 to extend or retract. Furthermore, when the load on the hydraulic pump 3 is high, the control device 12 opens the control valve 8 to send pressure oil from the accumulator 7 to the hydraulic cylinder 5 and reduce the flow rate of the hydraulic pump 3.
  • Lever operation signal 110 is generated by operating the operating lever 10 and is a signal that corresponds to the amount of lever operation.
  • Function generator 130 receives lever operation signal 110 as input and outputs the required flow rate of the hydraulic pump 3 that corresponds to the amount of lever operation.
  • Function generator 131 receives lever operation signal 110 as input and outputs an assist flow rate that corresponds to the amount of lever operation.
  • the assist flow rate is the flow rate supplied from the accumulator 7 to the hydraulic cylinder 5.
  • the characteristics of function generator 131 are set to be equivalent to those of function generator 130. As a result, the flow rate of pressurized oil supplied to the hydraulic cylinder 5 can be matched to the flow rate that corresponds to the amount of lever operation, regardless of the amount of assist flow rate.
  • the pressure sensor signal 111 is a signal that corresponds to the pressure of the hydraulic pump 3, and is input to the multiplier 132 together with the pump request flow rate output from the function generator 130.
  • the multiplier 132 calculates the load on the hydraulic pump 3 by multiplying the pump request flow rate by the pressure of the hydraulic pump 3.
  • the output of the multiplier 132 is input to the function generator 133.
  • the function generator 133 outputs a coefficient between 0 and 1 according to the output of the multiplier 132 (the load on the hydraulic pump 3). This coefficient is input to the multiplier 134 together with the output of the function generator 131 (the assist flow rate of the accumulator 7). With this configuration, the assist flow rate of the accumulator 7 can be increased when the load on the hydraulic pump 3 is high, and decreased when the load is low.
  • the output of the multiplier 134 (assist flow rate of the accumulator 7) and the output of the function generator 130 (required flow rate of the hydraulic pump 3) are input to the subtractor 135.
  • the subtractor 135 outputs the differential flow rate obtained by subtracting the assist flow rate from the required flow rate of the hydraulic pump 3 as the target flow rate of the hydraulic pump 3.
  • the output of the subtractor 135 (the target flow rate of the hydraulic pump 3) is input to the output conversion unit 136.
  • the output conversion unit 136 generates a tilt control signal 104 corresponding to the target flow rate of the hydraulic pump 3 and outputs it to the pump regulator 4. This allows the flow rate of the hydraulic pump 3 to match the target flow rate.
  • the output of the multiplier 134 (assist flow rate of the accumulator 7) is input to the output conversion unit 137.
  • the output conversion unit 137 generates a solenoid valve control signal 108 corresponding to the assist flow rate of the accumulator 7 and outputs it to the control valve 8. This allows the flow rate of the control valve 8 to match the assist flow rate.
  • a hydraulic excavator 200 (work machine) is provided with a hydraulic pump 3, a pump regulator 4 (pump flow rate control device) that controls the flow rate of pressurized oil discharged from the hydraulic pump 3, a hydraulic cylinder 5 (hydraulic actuator) to which the pressurized oil discharged from the hydraulic pump 3 is supplied, an accumulator 7 (pressure accumulator) that accumulates the pressurized oil discharged from the hydraulic pump 3, a control valve 8 (pressure accumulator flow rate control device) that controls the flow rate of pressurized oil supplied from the accumulator 7 to the hydraulic cylinder 5, a pressure sensor 11 (pump load detection device) that detects a pump load that is a load on the hydraulic pump 3, and a control device 12 that receives a signal from the pressure sensor 11 and controls the pump regulator 4 and the control valve 8.
  • a pump regulator 4 pump flow rate control device
  • the control device 12 controls the control valve 8 so that the amount of pressurized oil supplied from the accumulator 7 to the hydraulic cylinder 5 increases as the pump load increases, and also controls the pump regulator 4 so that the flow rate of pressurized oil discharged from the hydraulic pump 3 decreases in accordance with the increase in the pressurized oil supplied from the accumulator 7 to the hydraulic cylinder 5.
  • the first embodiment further includes an operating lever 10 (operating device) that commands the operation of the hydraulic cylinder 5 (hydraulic actuator), and the pump load detection device has a pressure sensor 11 (pump pressure detection device) that detects the pump pressure, which is the pressure of the hydraulic pump 3.
  • the control device 12 calculates the required pump flow rate, which is the required value for the flow rate of pressurized oil discharged from the hydraulic pump 3, based on the signal input from the operating lever 10, and calculates the pump load based on the required pump flow rate and the pump pressure.This makes it possible to calculate the load of the hydraulic pump 3 based on the pressure of the hydraulic pump 3.
  • the first embodiment further includes a control valve 6 (first control valve) that controls the flow rate of pressurized oil supplied from the hydraulic pump 3 to the hydraulic cylinder 5, and the pressure accumulation flow control device has a control valve 8 (second control valve) arranged in an oil line 17 (second oil line) that connects the center bypass oil line 13 (first oil line) that connects the hydraulic pump 3 and control valve 6 to the accumulator 7 (pressure accumulator).
  • first control valve controls the flow rate of pressurized oil supplied from the hydraulic pump 3 to the hydraulic cylinder 5
  • the pressure accumulation flow control device has a control valve 8 (second control valve) arranged in an oil line 17 (second oil line) that connects the center bypass oil line 13 (first oil line) that connects the hydraulic pump 3 and control valve 6 to the accumulator 7 (pressure accumulator).
  • control device 12 controls the control valve 8 (accumulator flow rate control device) so that the flow rate of pressurized oil supplied from the accumulator 7 (pressure accumulator device) to the hydraulic cylinder 5 (hydraulic actuator) continuously increases as the pump load increases, and controls the pump regulator 4 (pump flow rate control device) so that the flow rate of pressurized oil discharged from the hydraulic pump 3 continuously decreases. This makes it possible to prevent shocks caused by switching between the presence and absence of assist.
  • FIG 4 is a hydraulic circuit diagram of a hydraulic drive system 100 in a second embodiment.
  • the hydraulic drive system 100 in this embodiment further includes a pressure sensor 20 that detects the pressure in the accumulator 7, a pressure sensor 21 that detects the pressure on the bottom side of the hydraulic cylinder 5, and a control valve 22 (third control valve) that controls the flow rate of pressurized oil supplied from the accumulator 7 to the bottom side or rod side of the hydraulic cylinder 5, and the flow rate of pressurized oil discharged from the rod side or bottom side of the hydraulic cylinder 5 to the hydraulic oil tank 2.
  • Signals from the pressure sensors 20 and 21 are input to the control device 12, which controls the control valve 22.
  • the control valve 22 is located in an oil line 23 (third oil line) that connects the hydraulic cylinder 5 to the oil line portion of the oil line 17 that connects the accumulator 7 and control valve 8. Therefore, pressurized oil from the accumulator 7 can be supplied to the hydraulic cylinder 5 without passing through the control valves 6 and 8.
  • FIG. 5 is a block diagram showing the processing of the control device 12 in the second embodiment.
  • the control device 12 in this embodiment further includes a subtractor 140, a function generator 141, a multiplier 142, and a function generator 143.
  • the subtractor 140 receives as input a signal (pressure sensor signal 120) from the pressure sensor 20 that detects the pressure of the accumulator 7 and a signal (pressure sensor signal 121) from the pressure sensor 21 that detects the pressure of the hydraulic cylinder 5.
  • the subtractor 140 outputs the difference obtained by subtracting the pressure of the hydraulic cylinder 5 from the pressure of the accumulator 7. This difference is input to the function generator 141.
  • the function generator 141 outputs 1 if the difference is greater than a preset threshold P1, and outputs 0 if the difference is equal to or less than the threshold P1.
  • the output of the function generator 141 is input to the multiplier 142 together with the assist flow rate value output from the function generator 131.
  • the multiplier 142 outputs the product of the assist flow rate and the output of the function generator 141.
  • the output of the multiplier 142, together with the output of the function generator 133, is input to the multiplier 134.
  • the differential pressure output from the subtractor 140 is input to the function generator 143 along with the assist flow rate output from the multiplier 134.
  • the function generator 143 has a function that opens the control valve 22 in response to an increase in the assist flow rate, increasing the flow rate from the accumulator 7 to the hydraulic cylinder 5.
  • the differential pressure obtained by subtracting the pressure of the hydraulic cylinder 5 from the pressure of the accumulator 7 is also input to the function generator 143.
  • the function generator 143 calculates the opening of the control valve 22 so that when the differential pressure is large, the opening of the control valve 22 is reduced, and when the differential pressure is small, the opening of the control valve 22 is increased.
  • the signal from pressure sensor 21 (pressure sensor signal 121) is input to multiplier 132 instead of the signal from pressure sensor 11 (pressure sensor signal 111).
  • the load on hydraulic pump 3 was calculated using the pressure of hydraulic pump 3 (pressure sensor signal 111), but since the pressure of hydraulic pump 3 can be approximated by the pressure of hydraulic cylinder 5, in this embodiment, the load on hydraulic pump 3 is calculated using the pressure of hydraulic cylinder 5.
  • the pressure accumulation flow control device that controls the flow rate of pressurized oil supplied from the accumulator 7 to the hydraulic cylinder 5 further has a control valve 22 (third control valve) that is arranged in an oil passage 23 (third oil passage) that connects an oil passage portion that connects the accumulator 7 (pressure accumulation device) and the control valve 8 (second control valve) in the oil passage 17 (second oil passage) with the hydraulic cylinder 5 (hydraulic actuator).
  • the second embodiment configured as described above also achieves the same effects as the first embodiment. Furthermore, because the pressurized oil in the accumulator 7 can be supplied to the hydraulic cylinder 5 only through the control valve 22, without passing through the control valves 6 and 8, it is possible to reduce pressure loss when supplying the pressurized oil in the accumulator 7 to the hydraulic cylinder 5.
  • the hydraulic excavator 200 further includes an operating lever 10 (operating device) that commands the operation of the hydraulic cylinder 5 (hydraulic actuator), and the pump load detection device has a pressure sensor 21 (actuator pressure detection device) that detects the actuator pressure, which is the pressure of the hydraulic cylinder 5.
  • the control device 12 calculates the required pump flow rate, which is the required value for the flow rate of pressurized oil discharged from the hydraulic pump 3, based on the signal input from the operating lever 10, and calculates the load on the hydraulic pump 3 (pump load) based on the required pump flow rate and the actuator pressure. This makes it possible to calculate the load on the hydraulic pump 3 based on the pressure of the hydraulic cylinder 5.
  • the hydraulic excavator 200 further includes a pressure sensor 20 (accumulator pressure detection device) that detects the pressure of the accumulator 7 (accumulator), and a pressure sensor 21 (pressure detection device) that detects the pressure of the hydraulic cylinder 5 (hydraulic actuator).
  • the control device 12 controls the control valve 22 (accumulator flow control device) to increase the amount of pressurized oil supplied from the accumulator 7 to the hydraulic cylinder 5 as the pump load increases, only when the differential pressure obtained by subtracting the pressure detected by the pressure sensor 21 (hydraulic cylinder 5 pressure) from the pressure detected by the pressure sensor 20 (accumulator 7 pressure) is greater than a predetermined threshold value P1.
  • the control device 12 also controls the pump regulator 4 (pump flow control device) to decrease the flow rate of pressurized oil discharged from the hydraulic pump 3 in response to the increase in the amount of pressurized oil supplied from the accumulator 7 to the hydraulic cylinder 5. This prevents the flow rate of the hydraulic pump 3 from decreasing when the accumulator 7 is unable to assist due to insufficient pressure, thereby preventing a decrease in the speed of the hydraulic cylinder 5.
  • pump regulator 4 pump flow control device
  • FIG 6 is a block diagram showing the processing of the control device 12 in the third embodiment.
  • the difference from the second embodiment (shown in Figure 5) is that instead of the pressure sensor signal 121 indicating the pressure of the hydraulic cylinder 5, the pressure sensor signal 111 indicating the pressure of the hydraulic pump 3 is input to the multiplier 132 and the subtractor 140.
  • the hydraulic excavator 200 further includes a pressure sensor 20 (pressure accumulator pressure detection device) that detects the pressure of the accumulator 7 (pressure accumulator), and a pressure sensor 11 (pressure detection device) that detects the pressure of the hydraulic pump 3, and the control device 12 controls the control valve 22 (pressure accumulator flow rate control device) so that pressurized oil is supplied from the accumulator 7 to the hydraulic cylinder 5 in accordance with the load on the hydraulic pump 3 (pump load) only when the differential pressure obtained by subtracting the pressure detected by the pressure sensor 11 (pressure of the hydraulic pump 3) from the pressure detected by the pressure sensor 20 (pressure of the accumulator 7) is greater than a predetermined threshold value P1, and also controls the pump regulator 4 (pump flow rate control device) so that the flow rate of pressurized oil discharged from the hydraulic pump 3 is reduced.
  • a pressure sensor 20 pressure accumulator pressure detection device
  • a pressure sensor 11 pressure detection device
  • the second embodiment configured as described above also provides the same effects as the second embodiment.
  • FIG. 7 is a block diagram showing the processing of the control device 12 in the fourth embodiment.
  • the control device 12 in this embodiment has a function generator 144 instead of the function generator 133 (shown in Figure 5).
  • the function generator 144 outputs 1 when the output of the multiplier 132 (load on the hydraulic pump 3) is greater than a preset threshold L1, and outputs 0 when it is equal to or less than the threshold L1.
  • assistance by the accumulator 7 is not performed when the load on the hydraulic pump 3 is low, and assistance by the accumulator 7 is performed only when the load on the hydraulic pump 3 is high.
  • control device 12 controls the control valve 22 (pressure accumulation flow control device) so that pressurized oil is supplied from the accumulator 7 (pressure accumulation device) to the hydraulic cylinder 5 (hydraulic actuator) only when the load on the hydraulic pump 3 (pump load) is greater than a predetermined threshold value L1, and controls the pump regulator 4 (pump flow control device) so that the flow rate of pressurized oil discharged from the hydraulic pump 3 is reduced.
  • control valve 22 pressure accumulation flow control device
  • the fourth embodiment configured as described above also achieves the same effects as the second embodiment. Furthermore, because assistance by the accumulator 7 is provided only when the load on the hydraulic pump 3 is high, it is possible to reduce the consumption of pressurized oil in the accumulator 7.
  • the present invention is not limited to the above-described embodiments, and includes various modifications.
  • the above-described embodiments are presented to clearly explain the present invention, and are not necessarily limited to those including all of the configurations described.
  • it is possible to replace part of the configuration of one embodiment with the configuration of another embodiment and it is also possible to add the configuration of another embodiment to the configuration of one embodiment.
  • lever operation signal 111, 120, 121... pressure sensor signal, 130, 131... function generator, 132... multiplier, 133... function generator, 134... multiplier, 135... subtractor, 136, 137... output conversion unit, 140... subtractor, 141... function generator, 142... multiplier, 143, 144... function generator, 200... hydraulic excavator (work machine), 201... lower traveling body, 202... upper rotating body, 203... work device, 204... traveling motor (hydraulic actuator), 205... boom, 206... arm, 207... bucket, 208... boom cylinder (hydraulic actuator), 209... arm cylinder (hydraulic actuator), 210... bucket cylinder (hydraulic actuator).

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Operation Control Of Excavators (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne une pelle hydraulique comprenant : une pompe hydraulique ; un régulateur de pompe ; un vérin hydraulique alimenté en huile hydraulique évacuée de la pompe hydraulique ; un accumulateur destiné à stocker l'huile hydraulique évacuée de la pompe hydraulique ; une vanne de commande destinée à commander le débit de l'huile hydraulique fournie par l'accumulateur au vérin hydraulique ; un capteur de pression destiné à détecter une charge de pompe qui est une charge de la pompe hydraulique ; et un dispositif de commande à l'entrée duquel est appliqué un signal provenant du capteur de pression, et qui commande le régulateur de pompe et la vanne de commande. Le dispositif de commande commande la vanne de commande de sorte que l'huile hydraulique fournie par l'accumulateur au vérin hydraulique augmente à mesure que la charge de pompe augmente, et commande le régulateur de pompe de sorte que le débit de l'huile hydraulique évacuée de la pompe hydraulique diminue à mesure que l'huile hydraulique fournie par l'accumulateur au vérin hydraulique augmente.
PCT/JP2025/004824 2024-03-22 2025-02-13 Engin de chantier Pending WO2025197375A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2024047305 2024-03-22
JP2024-047305 2024-03-22

Publications (1)

Publication Number Publication Date
WO2025197375A1 true WO2025197375A1 (fr) 2025-09-25

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2025/004824 Pending WO2025197375A1 (fr) 2024-03-22 2025-02-13 Engin de chantier

Country Status (1)

Country Link
WO (1) WO2025197375A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009150462A (ja) * 2007-12-20 2009-07-09 Caterpillar Japan Ltd 作業機械における油圧制御システム
JP2010060057A (ja) * 2008-09-04 2010-03-18 Caterpillar Japan Ltd 作業機械における油圧制御システム
JP2016205494A (ja) * 2015-04-21 2016-12-08 キャタピラー エス エー アール エル 流体圧回路および作業機械
WO2018061165A1 (fr) * 2016-09-29 2018-04-05 日立建機株式会社 Dispositif d'entraînement hydraulique
JP2019049321A (ja) * 2017-09-11 2019-03-28 日立建機株式会社 建設機械
WO2019064555A1 (fr) * 2017-09-29 2019-04-04 株式会社日立建機ティエラ Dispositif d'entraînement hydraulique pour machine de travail
JP2020085194A (ja) * 2018-11-29 2020-06-04 日立建機株式会社 建設機械

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009150462A (ja) * 2007-12-20 2009-07-09 Caterpillar Japan Ltd 作業機械における油圧制御システム
JP2010060057A (ja) * 2008-09-04 2010-03-18 Caterpillar Japan Ltd 作業機械における油圧制御システム
JP2016205494A (ja) * 2015-04-21 2016-12-08 キャタピラー エス エー アール エル 流体圧回路および作業機械
WO2018061165A1 (fr) * 2016-09-29 2018-04-05 日立建機株式会社 Dispositif d'entraînement hydraulique
JP2019049321A (ja) * 2017-09-11 2019-03-28 日立建機株式会社 建設機械
WO2019064555A1 (fr) * 2017-09-29 2019-04-04 株式会社日立建機ティエラ Dispositif d'entraînement hydraulique pour machine de travail
JP2020085194A (ja) * 2018-11-29 2020-06-04 日立建機株式会社 建設機械

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