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WO2018178961A1 - Système hydraulique - Google Patents

Système hydraulique Download PDF

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Publication number
WO2018178961A1
WO2018178961A1 PCT/IB2018/053503 IB2018053503W WO2018178961A1 WO 2018178961 A1 WO2018178961 A1 WO 2018178961A1 IB 2018053503 W IB2018053503 W IB 2018053503W WO 2018178961 A1 WO2018178961 A1 WO 2018178961A1
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WO
WIPO (PCT)
Prior art keywords
proportional valve
electromagnetic proportional
valve
secondary pressure
flow path
Prior art date
Application number
PCT/IB2018/053503
Other languages
English (en)
Japanese (ja)
Inventor
近藤哲弘
Original Assignee
川崎重工業株式会社
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 川崎重工業株式会社 filed Critical 川崎重工業株式会社
Priority to CN201880019230.9A priority Critical patent/CN110741169A/zh
Publication of WO2018178961A1 publication Critical patent/WO2018178961A1/fr

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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
    • E02F9/22—Hydraulic or pneumatic drives
    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems

Definitions

  • the present invention relates to an electric positive control hydraulic system.
  • Patent Document 1 discloses a hydraulic system 100 for a construction machine as shown in FIG.
  • hydraulic oil is supplied from the variable displacement pump 110 to each hydraulic actuator 130 via the control valve 120.
  • the control valve 120 increases the opening area of the passage for supplying the hydraulic oil to the hydraulic actuator 130 as the operation amount with respect to the operation unit (operation lever in FIG. 4) of the corresponding operation device 140 increases.
  • the tilt angle of the pump 110 is adjusted by the regulator 111.
  • the regulator 111 is connected to the electromagnetic proportional valve 112.
  • the electromagnetic proportional valve 112 outputs a higher secondary pressure as the operation amount with respect to the operation unit of the operation device 140 increases. Thereby, the discharge flow rate of the pump 110 increases as the operation amount with respect to the operation unit of the operation device 140 increases.
  • the electromagnetic proportional valve 112 when the electromagnetic proportional valve 112 does not function normally due to a failure or the like, the secondary pressure of the electromagnetic proportional valve 112 may become zero. In this case, since the discharge flow rate of the pump 110 is maintained at the minimum discharge flow rate even when the operation unit of the operation device 140 is operated, the hydraulic actuator 130 cannot be operated at a sufficient speed. In order to solve this problem, for example, it is conceivable to install a spare electromagnetic proportional valve.
  • some hydraulic systems include a plurality of pumps for supplying hydraulic oil to hydraulic actuators.
  • a hydraulic system for example, when a separate electromagnetic proportional valve is installed for each pump, the cost increases.
  • an object of the present invention is to make it possible to cope with a failure of an electromagnetic proportional valve with an inexpensive configuration in a hydraulic system including a variable displacement type first pump and a second pump.
  • the present invention provides, from one aspect, a first operating device and a second operating device that output an operation signal corresponding to an operation amount with respect to an operating unit, and a first control valve to a first hydraulic actuator.
  • a variable displacement first pump that supplies hydraulic oil via a first pressure regulator, a first regulator that increases a tilt angle of the first pump as the control pressure increases, and a second hydraulic actuator via a second control valve
  • a variable displacement second pump that supplies hydraulic oil, a second regulator that increases the tilt angle of the second pump as the control pressure increases, and a higher operation signal output from the first operating device.
  • the first electromagnetic proportional valve when the first electromagnetic proportional valve is normal, the secondary pressure of the first electromagnetic proportional valve is guided to the first regulator, so that the first electromagnetic proportional valve tilts the first pump.
  • the angle discharge flow rate
  • the first regulator has a third electromagnetic proportional to the operation signal output from the first operating device.
  • the secondary pressure of the valve is led. Therefore, the tilt angle of the first pump increases as the operation signal increases. As a result, the first hydraulic actuator can be operated at a sufficient speed.
  • the second electromagnetic proportional valve when the second electromagnetic proportional valve is normal, the secondary pressure of the second electromagnetic proportional valve is guided to the second regulator, and therefore the tilt angle (discharge flow rate) of the second pump by the second electromagnetic proportional valve. ) Can be controlled.
  • the second electromagnetic proportional valve when the second electromagnetic proportional valve does not function normally and its secondary pressure becomes zero, the second regulator has a third electromagnetic proportional to the operation signal output from the second operating device. The secondary pressure of the valve is led. Therefore, the tilt angle of the second pump increases as the operation signal increases. As a result, the second hydraulic actuator can be operated at a sufficient speed.
  • the 3rd electromagnetic proportional valve becomes a reserve of both the 1st electromagnetic proportional valve and the 2nd electromagnetic proportional valve, it should respond to failure etc. of the 1st electromagnetic proportional valve and the 2nd electromagnetic proportional valve with an inexpensive structure. Can do.
  • the hydraulic system further includes a control device that supplies a drive current to the first electromagnetic proportional valve, the second electromagnetic proportional valve, and the third electromagnetic proportional valve, and the control device includes the first electromagnetic proportional valve.
  • the control device includes the first electromagnetic proportional valve.
  • the third electromagnetic proportional valve Drive to the valve Current may be used as the zero.
  • hydraulic oil is supplied to the first hydraulic actuator and the first hydraulic actuator via the first control valve, and the first hydraulic actuator and the second operational device that output an operation signal corresponding to the operation amount with respect to the operation unit.
  • the first operating device connected to the first regulator by a displacement type second pump, a second regulator that increases a tilt angle of the second pump as the control pressure increases, and a first secondary pressure line
  • the higher the operation signal output from the first the higher the secondary pressure is output to the first regulator as the control pressure
  • the second regulator is connected to the second regulator by a second secondary pressure line.
  • a second electromagnetic proportional valve that outputs a higher secondary pressure to the second regulator as the control pressure, and the first secondary pressure line as the first electromagnetic signal.
  • a first switching valve provided so as to be divided into a first upstream flow path on the proportional valve side and a first downstream flow path on the first regulator side; and the second secondary pressure line is connected to the second electromagnetic proportional valve.
  • a second switching valve provided so as to be divided into a second upstream flow path on the side and a second downstream flow path on the second regulator side, and an operation signal output from the first operating device, A drive current is supplied to the first electromagnetic proportional valve so that the first electromagnetic proportional valve outputs a secondary pressure between a minimum value and a maximum value larger than one set value, and the second operating device. A minimum value larger than the second set value according to the operation signal output from And a control device for supplying a drive current to the second electromagnetic proportional valve so that the second electromagnetic proportional valve outputs a secondary pressure between a large value.
  • the second switching valve is connected to the first upstream flow path by a second relay flow path, blocks the second upstream flow path in the neutral position, and connects the second relay flow path to the second relay flow path.
  • the secondary pressure of the second electromagnetic proportional valve exceeded the second set value
  • the secondary pressure causes the second upstream flow path to communicate with the second downstream flow path and is switched to an operating position that blocks the second relay flow path.
  • a higher secondary pressure is applied as the operation signal output from the first operating device increases.
  • the second solenoid proportional valve is controlled so that the solenoid proportional valve outputs, and the second solenoid proportional valve is determined not to function normally from monitoring of the drive current supplied to the second solenoid proportional valve.
  • a hydraulic system is provided that controls the first electromagnetic proportional valve so that the first electromagnetic proportional valve outputs a higher secondary pressure as the operation signal output from the second operating device increases.
  • the tilt angle (discharge flow rate) of the first pump can be controlled by the first electromagnetic proportional valve.
  • the first electromagnetic proportional valve does not function normally and the secondary pressure becomes zero
  • the first switching valve is switched to the neutral position, and the first regulator outputs the first regulator.
  • the secondary pressure of the second electromagnetic proportional valve according to the operation signal is derived. Therefore, the tilt angle of the first pump increases as the operation signal increases. As a result, the first hydraulic actuator can be operated at a sufficient speed.
  • the second switching valve when the second electromagnetic proportional valve is normal, the second switching valve is located at the operating position, so that the secondary pressure of the second electromagnetic proportional valve is guided to the second regulator. Therefore, the tilt angle (discharge flow rate) of the second pump can be controlled by the second electromagnetic proportional valve.
  • the second electromagnetic proportional valve when the second electromagnetic proportional valve does not function normally and its secondary pressure becomes zero, the second switching valve is switched to the neutral position, and is output from the second operating device to the second regulator.
  • the secondary pressure of the first electromagnetic proportional valve corresponding to the operation signal is derived. Therefore, the tilt angle of the second pump increases as the operation signal increases. As a result, the second hydraulic actuator can be operated at a sufficient speed.
  • the first electromagnetic proportional valve and the second electromagnetic valve have an inexpensive configuration. It can cope with the failure of the proportional valve.
  • FIG. 1 is a schematic configuration diagram of a hydraulic system according to a first embodiment of the present invention. It is a schematic block diagram of the hydraulic system which concerns on 2nd Embodiment of this invention. It is a schematic block diagram of the hydraulic system of the conventional construction machine.
  • FIG. 1 shows a hydraulic system 1A according to an embodiment of the present invention.
  • the hydraulic system 1A is mounted on, for example, a construction machine such as a hydraulic excavator or a hydraulic crane, a civil engineering machine, an agricultural machine, or an industrial machine.
  • the hydraulic system 1A includes a first hydraulic actuator 26 and a second hydraulic actuator 27, a first main pump 21 that supplies hydraulic oil to the first hydraulic actuator 26 via the first control valve 3A, and a second A second main pump 23 for supplying hydraulic oil to the hydraulic actuator 27 via the second control valve 3B is included.
  • first hydraulic actuator 26 and the first control valve 3A there is one set of the first hydraulic actuator 26 and the first control valve 3A, but a plurality of sets of the first hydraulic actuator 26 and the first control valve 3A may be provided.
  • second hydraulic actuator 27 and the second control valve 3B a plurality of sets of the second hydraulic actuator 27 and the second control valve 3B may be provided.
  • Each of the first main pump 21 and the second main pump 23 is a variable displacement pump that can change the tilt angle.
  • Each of the first main pump 21 and the second main pump 23 may be a swash plate pump or an oblique shaft pump.
  • the tilt angle of the first main pump 21 is adjusted by the first regulator 22, and the tilt angle of the second main pump 23 is adjusted by the second regulator 24.
  • the first main pump 21 is connected to the first control valve 3 ⁇ / b> A by the supply line 11.
  • the discharge pressure of the first main pump 21 is kept below the relief pressure by a relief valve (not shown).
  • the second main pump 23 is connected to the second control valve 3 ⁇ / b> B by the supply line 12.
  • the discharge pressure of the second main pump 23 is kept below the relief pressure by a relief valve (not shown).
  • the first hydraulic actuator 26 is a double-acting cylinder, and the first control valve 3A is connected to the first hydraulic actuator 26 by a pair of supply / discharge lines 31.
  • the first hydraulic actuator 26 may be a single-acting cylinder, and the first control valve 3 ⁇ / b> A may be connected to the first hydraulic actuator 26 through one supply / discharge line 31.
  • the first hydraulic actuator 26 may be a hydraulic motor.
  • the second hydraulic actuator 27 is a double-acting cylinder, and the second control valve 3B is connected to the second hydraulic actuator 27 by a pair of supply / discharge lines 32.
  • the second hydraulic actuator 27 may be a single-acting cylinder, and the second control valve 3B may be connected to the second hydraulic actuator 27 through one supply / discharge line 32.
  • the second hydraulic actuator 27 may be a hydraulic motor.
  • the first control valve 3A When the first operating device 4A is operated, the first control valve 3A is moved from the neutral position to the first position (the position where the first hydraulic actuator 26 is operated in one direction) or the second position (the first hydraulic actuator 26 is moved). The position is switched to the reverse direction.
  • the first control valve 3A is a hydraulic pilot type and has a pair of pilot ports.
  • the first control valve 3A may be an electromagnetic pilot type.
  • the second control valve 3B operates from the neutral position to the first position (position where the second hydraulic actuator 27 is operated in one direction) or the second position (second hydraulic pressure) by operating the second operating device 4B.
  • the actuator 27 is switched to a position for operating the actuator 27 in the reverse direction.
  • the second control valve 3B is a hydraulic pilot type and has a pair of pilot ports.
  • the second control valve 3B may be an electromagnetic pilot type.
  • the first operating device 4 ⁇ / b> A has an operation unit 41 and outputs an operation signal corresponding to an operation amount with respect to the operation unit 41. That is, the operation signal output from the first operating device 4A increases as the operation amount increases.
  • the operation unit 41 is, for example, an operation lever, but may be a foot pedal or the like.
  • the first operating device 4A is a pilot operating valve that outputs a pilot pressure as an operation signal.
  • the first operating device 4 ⁇ / b> A is connected to the pilot port of the first control valve 3 ⁇ / b> A by a pair of pilot lines 42.
  • the pilot pressure (operation signal) output from the first operating device 4A increases, the opening area of the passage through which the first control valve 3A supplies hydraulic oil to the first hydraulic actuator 26 is increased.
  • the first operating device 4A may be an electric joystick that outputs an electric signal as an operation signal.
  • each pilot port of the first control valve 3A is connected to the secondary pressure port of the electromagnetic proportional valve.
  • the second operating device 4B includes an operation unit 43 and outputs an operation signal corresponding to the operation amount for the operation unit 43. That is, the operation signal output from the second controller 4B increases as the operation amount increases.
  • the operation unit 43 is an operation lever, for example, but may be a foot pedal or the like.
  • the second operating device 4B is a pilot operating valve that outputs a pilot pressure as an operation signal.
  • the second operating device 4B is connected to the pilot port of the second control valve 3B by a pair of pilot lines 44.
  • the pilot pressure (operation signal) output from the second operating device 4B increases, the opening area of the passage through which the second control valve 3B supplies hydraulic oil to the second hydraulic actuator 27 is increased.
  • the second operating device 4B may be an electric joystick that outputs an electric signal as an operation signal.
  • each pilot port of the second control valve 3B is connected to the secondary pressure port of the electromagnetic proportional valve.
  • the first regulator 22 described above increases the tilt angle of the first main pump 21 as the control pressure guided to the first regulator 22 increases.
  • the first regulator 22 is connected to the secondary pressure port of the first electromagnetic proportional valve 51 via the first high pressure selection valve 61.
  • the primary pressure port of the first electromagnetic proportional valve 51 is connected to the sub pump 25 by the primary pressure line 13.
  • the discharge pressure of the sub pump 25 is maintained at a set pressure by a relief valve (not shown).
  • the second regulator 24 increases the tilt angle of the second main pump 23 as the control pressure guided to the second regulator 24 increases.
  • the second regulator 24 is connected to the secondary pressure port of the second electromagnetic proportional valve 52 via the second high pressure selection valve 65.
  • the primary pressure port of the second electromagnetic proportional valve 52 is connected to the sub pump 25 by the primary pressure line 14.
  • the first high pressure selection valve 61 has two input ports and one output port.
  • the output port is connected to the first regulator 22 through an output line 62, and one input port is connected to the first electromagnetic proportional valve through an input line 63. It is connected to 51 secondary pressure ports.
  • the other input port of the first high pressure selection valve 61 is connected to the secondary pressure port of the third electromagnetic proportional valve 53 by the input line 64. That is, the first high pressure selection valve 61 selects the higher one of the secondary pressure output from the first electromagnetic proportional valve 51 and the secondary pressure output from the third electromagnetic proportional valve 53 as the control pressure described above. Guide to the first regulator 22.
  • the primary pressure port of the third electromagnetic proportional valve 53 is connected to the sub pump 25 by the primary pressure line 15.
  • the second high-pressure selection valve 65 has two input ports and one output port.
  • the output port is connected to the second regulator 24 through the output line 66, and one input port is connected to the second through the input line 67.
  • the secondary pressure port of the electromagnetic proportional valve 52 is connected.
  • the other input port of the second high pressure selection valve 65 is connected to the secondary pressure port of the third electromagnetic proportional valve 53 by the input line 68. That is, the second high pressure selection valve 65 selects the higher one of the secondary pressure output from the second electromagnetic proportional valve 52 and the secondary pressure output from the third electromagnetic proportional valve 53 as the control pressure described above. Guide to the second regulator 24.
  • Each of the first electromagnetic proportional valve 51, the second electromagnetic proportional valve 52, and the third electromagnetic proportional valve 53 is a direct proportional type that outputs a higher secondary pressure as the drive current increases.
  • the first electromagnetic proportional valve 51, the second electromagnetic proportional valve 52 and the third electromagnetic proportional valve 53 are controlled by the control device 7. More specifically, the control device 7 supplies drive currents based on respective command currents to the first electromagnetic proportional valve 51, the second electromagnetic proportional valve 52, and the third electromagnetic proportional valve 53, respectively.
  • FIG. 1 only a part of the signal lines is drawn for simplification of the drawing.
  • control device 7 has a memory such as a ROM and a RAM and a CPU, and a program stored in the ROM is executed by the CPU.
  • the control device 7 is electrically connected to the pressure sensor 71 provided in each of the pair of pilot lines 42 and electrically connected to the pressure sensor 72 provided in each of the pair of pilot lines 44. Has been.
  • the pressure sensor 71 detects the pilot pressure output from the first operating device 4A.
  • the control device 7 increases the drive current supplied to the first electromagnetic proportional valve 51 as the pilot pressure output from the first operating device 4A increases. That is, the first electromagnetic proportional valve 51 outputs a higher secondary pressure as the pilot pressure output from the first operating device 4A increases. Thereby, the discharge flow volume of the 1st main pump 21 increases, so that the operation amount with respect to the operation part 41 of 4 A of 1st operating devices becomes large.
  • the pressure sensor 72 detects the pilot pressure output from the second operating device 4B.
  • the control apparatus 7 enlarges the drive current sent to the 2nd electromagnetic proportional valve 52, so that the pilot pressure output from the 2nd operating device 4B becomes large. That is, the second electromagnetic proportional valve 52 outputs a higher secondary pressure as the pilot pressure output from the second operating device 4B increases. Thereby, the discharge flow rate of the second main pump 23 increases as the amount of operation with respect to the operation unit 43 of the second operating device 4B increases.
  • the controller 7 monitors the drive current supplied to the first electromagnetic proportional valve 51 (measures the drive current that is flowing from time to time, the same applies hereinafter), so that the first electromagnetic proportional valve 51 functions normally. It is determined whether or not. Further, the control device 7 determines whether or not the second electromagnetic proportional valve 52 functions normally from monitoring of the drive current supplied to the second electromagnetic proportional valve 52.
  • control device 7 compares the command current output from the control device 7 with the actually measured drive current, so that the solenoid that is a component of the electromagnetic proportional valve (51 or 52) is disconnected. It can be determined whether or not contact failure has occurred in the connector of the electrical wiring connected to the solenoid. When it is determined that both the first electromagnetic proportional valve 51 and the second electromagnetic proportional valve 52 function normally, the control device 7 sets the drive current supplied to the third electromagnetic proportional valve 53 to zero.
  • the control device 7 supplies the drive current to be supplied to the third electromagnetic proportional valve 53 in accordance with the pilot pressure output from the first operating device 4A. To change. That is, the control device 7 controls the third electromagnetic proportional valve 53 so that the third electromagnetic proportional valve 53 outputs a higher secondary pressure as the pilot pressure output from the first operating device 4A increases. Thereby, the discharge flow volume of the 1st main pump 21 increases, so that the operation amount with respect to the operation part 41 of 4 A of 1st operating devices becomes large.
  • the control device 7 supplies the drive current to be supplied to the third electromagnetic proportional valve 53 in accordance with the pilot pressure output from the second operating device 4B. To change. That is, the control device 7 controls the third electromagnetic proportional valve 53 so that the third electromagnetic proportional valve 53 outputs a higher secondary pressure as the pilot pressure output from the second operating device 4B increases. Thereby, the discharge flow rate of the second main pump 23 increases as the amount of operation with respect to the operation unit 43 of the second operating device 4B increases.
  • the first electromagnetic proportional valve 51 when the first electromagnetic proportional valve 51 is normal, the secondary pressure of the first electromagnetic proportional valve 51 is guided to the first regulator 22, The tilt angle (discharge flow rate) of the first main pump 21 can be controlled by the 1 electromagnetic proportional valve 51.
  • the first regulator 22 receives a first signal corresponding to the operation signal output from the first operating device 4A.
  • the secondary pressure of the three electromagnetic proportional valve 53 is introduced. Therefore, the tilt angle of the first main pump 21 increases as the operation signal increases. As a result, the first hydraulic actuator 26 can be operated at a sufficient speed.
  • the second electromagnetic proportional valve 52 when the second electromagnetic proportional valve 52 is normal, the secondary pressure of the second electromagnetic proportional valve 52 is guided to the second regulator 24, so the second electromagnetic proportional valve 52 causes the second main pump 23 to The tilt angle (discharge flow rate) can be controlled.
  • the second electromagnetic proportional valve 52 when the second electromagnetic proportional valve 52 does not function normally and its secondary pressure becomes zero, the second regulator 24 receives a second signal corresponding to the operation signal output from the second operation device 4B.
  • the secondary pressure of the three electromagnetic proportional valve 53 is introduced. Therefore, the tilt angle of the second main pump 23 increases as the operation signal increases. As a result, the second hydraulic actuator 27 can be operated at a sufficient speed.
  • the third electromagnetic proportional valve 53 serves as a backup for both the first electromagnetic proportional valve 51 and the second electromagnetic proportional valve 52, the first electromagnetic proportional valve 51 and the second electromagnetic proportional valve 52 are broken down with an inexpensive configuration. Etc.
  • FIG. 2 shows a hydraulic system 1B according to a second embodiment of the present invention.
  • the same components as those in the first embodiment are denoted by the same reference numerals, and a duplicate description is omitted.
  • the first regulator 22 is connected to the secondary pressure port of the first electromagnetic proportional valve 55 through the first secondary pressure line 81, and the second regulator 24 is connected to the second secondary pressure line 85 through the second secondary pressure line 85.
  • the secondary pressure port of the electromagnetic proportional valve 56 is connected.
  • the primary pressure ports of the first electromagnetic proportional valve 55 and the second electromagnetic proportional valve 56 are connected to the sub pump 25 by primary pressure lines 16 and 17, respectively.
  • a first switching valve 91 is provided in the first secondary pressure line 81.
  • the first switching valve 91 is provided to divide the first secondary pressure line 81 into a first upstream flow path 83 on the first electromagnetic proportional valve 55 side and a first downstream flow path 82 on the first regulator 22 side. ing.
  • a second switching valve 92 is provided in the second secondary pressure line 85.
  • the second switching valve 92 is provided to divide the second secondary pressure line 85 into a second upstream flow path 87 on the second electromagnetic proportional valve 56 side and a second downstream flow path 86 on the second regulator 24 side. ing.
  • first switching valve 91 is connected to the second upstream flow path 87 by the first relay flow path 84
  • second switching valve 92 is connected to the first upstream flow path 83 by the second relay flow path 88. Has been.
  • the first switching valve 91 is a pilot type that operates according to the secondary pressure of the first electromagnetic proportional valve 55.
  • the first switching valve 91 blocks the first upstream flow path 83 and communicates the first relay flow path 84 with the first downstream flow path 82 in the neutral position (right position in FIG. 2).
  • the first switching valve 91 When the secondary pressure of the first electromagnetic proportional valve 55 exceeds the first set value ⁇ , the first switching valve 91 is switched to the operating position (left side position in FIG. 2) by the secondary pressure. In the operating position, the first switching valve 91 communicates the first upstream flow path 83 with the first downstream flow path 82 and blocks the first relay flow path 84.
  • the second switching valve 92 is a pilot type that operates according to the secondary pressure of the second electromagnetic proportional valve 56.
  • the second switching valve 92 blocks the second upstream flow path 87 and communicates the second relay flow path 88 with the second downstream flow path 86 in the neutral position (left side position in FIG. 2).
  • the second switching valve 92 When the secondary pressure of the second electromagnetic proportional valve 56 exceeds the second set value ⁇ , the second switching valve 92 is switched to the operating position (right side position in FIG. 2) by the secondary pressure. In the operating position, the second switching valve 92 communicates the second upstream flow path 87 with the second downstream flow path 86 and blocks the second relay flow path 88.
  • the second set value ⁇ may be equal to or different from the first set value ⁇ .
  • Each of the first electromagnetic proportional valve 55 and the second electromagnetic proportional valve 56 is a direct proportional type that outputs a higher secondary pressure as the drive current increases.
  • the first electromagnetic proportional valve 55 and the second electromagnetic proportional valve 56 are controlled by the control device 7. That is, the control device 7 supplies drive current to the first electromagnetic proportional valve 55 and the second electromagnetic proportional valve 56.
  • the control device 7 supplies drive current to the first electromagnetic proportional valve 55 and the second electromagnetic proportional valve 56.
  • FIG. 2 only a part of the signal lines is drawn for simplification of the drawing.
  • the control device 7 increases the drive current supplied to the first electromagnetic proportional valve 55 as the pilot pressure (operation signal, the same applies hereinafter) output from the first operation device 4A increases. More specifically, the control device 7 sets the secondary pressure between the minimum value and the maximum value larger than the first set value ⁇ in accordance with the operation signal output from the first operation device 4A. Is supplied to the first electromagnetic proportional valve 55. As a result, the first switching valve 91 is maintained in the operating position. Accordingly, the first electromagnetic proportional valve 55 outputs a higher secondary pressure to the first regulator 22 as the control pressure as the pilot pressure output from the first operating device 4A increases. Thereby, the discharge flow volume of the 1st main pump 21 increases, so that the operation amount with respect to the operation part 41 of 4 A of 1st operating devices becomes large.
  • control device 7 increases the drive current supplied to the second electromagnetic proportional valve 56 as the pilot pressure output from the second operating device 4B increases. More specifically, the control device 7 sets the secondary pressure between the minimum value and the maximum value larger than the second set value ⁇ in accordance with the operation signal output from the second operation device 4B. Is supplied to the second electromagnetic proportional valve 56. As a result, the second switching valve 92 is maintained in the operating position. Accordingly, the second electromagnetic proportional valve 56 outputs a higher secondary pressure to the second regulator 24 as the pilot pressure output from the second operating device 4B increases. Thereby, the discharge flow rate of the second main pump 23 increases as the amount of operation with respect to the operation unit 43 of the second operating device 4B increases.
  • control device 7 determines whether or not the first electromagnetic proportional valve 55 functions normally from monitoring of the drive current supplied to the first electromagnetic proportional valve 55. In addition, the control device 7 determines whether or not the second electromagnetic proportional valve 56 functions normally from monitoring of the drive current supplied to the second electromagnetic proportional valve 56.
  • the control device 7 When it is determined that the first electromagnetic proportional valve 55 does not function normally, the control device 7 causes the second electromagnetic proportional valve 56 to output a higher secondary pressure as the pilot pressure output from the first operating device 4A increases. The second electromagnetic proportional valve 56 is controlled. Conversely, when it is determined that the second electromagnetic proportional valve 56 does not function normally, the control device 7 causes the first electromagnetic proportional valve 55 to increase the secondary pressure as the pilot pressure output from the second operating device 4B increases. The first electromagnetic proportional valve 55 is controlled to output.
  • the first switching valve 91 when the first electromagnetic proportional valve 55 is normal, the first switching valve 91 is located at the operating position, and therefore the first regulator 22 has the first electromagnetic proportional.
  • the secondary pressure of the valve 55 is introduced. Accordingly, the tilt angle (discharge flow rate) of the first main pump 21 can be controlled by the first electromagnetic proportional valve 55.
  • the first electromagnetic proportional valve 55 when the first electromagnetic proportional valve 55 does not function normally and its secondary pressure becomes zero, the first switching valve 91 is switched to the neutral position, and the first regulator 22 includes the first operating device.
  • the secondary pressure of the second electromagnetic proportional valve 56 is guided according to the operation signal output from 4A. Therefore, the tilt angle of the first main pump 21 increases as the operation signal increases. As a result, the first hydraulic actuator 26 can be operated at a sufficient speed.
  • the discharge flow rate of the second main pump 23 increases, but the hydraulic oil discharged from the second main pump 23 As long as the two-operation device 4B is not operated, there is no particular problem because it is returned to the tank through an unload line or center bypass line (not shown). Further, when the first electromagnetic proportional valve 55 does not function normally and its secondary pressure becomes zero, and both the first operating device 4A and the second operating device 4B are operated, By selecting the larger operation signal, the tilt angle (discharge flow rate) of the first main pump 21 and the second main pump 23 can be controlled by the second electromagnetic proportional valve 56.
  • the second switching valve 92 is located at the operating position, so that the secondary pressure of the second electromagnetic proportional valve 56 is guided to the second regulator 24. Therefore, the tilt angle (discharge flow rate) of the second main pump 23 can be controlled by the second electromagnetic proportional valve 56.
  • the second electromagnetic proportional valve 56 does not function normally and its secondary pressure becomes zero
  • the second switching valve 92 is switched to the neutral position, and the second regulator 24 includes the second operating device.
  • the secondary pressure of the first electromagnetic proportional valve 55 is guided according to the operation signal output from 4B. Therefore, the tilt angle of the second main pump 23 increases as the operation signal increases. As a result, the second hydraulic actuator 27 can be operated at a sufficient speed.
  • the discharge flow rate of the first main pump 21 also increases, but the hydraulic oil discharged from the first main pump 21 As long as the one operating device 4A is not operated, there is no particular problem because it is returned to the tank through an unload line or center bypass line (not shown). Further, when the second electromagnetic proportional valve 56 does not function normally and the secondary pressure becomes zero, and both the first operating device 4A and the second operating device 4B are operated, By selecting the larger operation signal, the tilt angle (discharge flow rate) of the first main pump 21 and the second main pump 23 can be controlled by the second electromagnetic proportional valve 56.
  • the first electromagnetic proportional since the only additional equipment required in the prior art is the switching valves 91 and 92 provided in the first secondary pressure line 81 and the second secondary pressure line 85, the first electromagnetic proportional with an inexpensive configuration. It is possible to cope with a failure of the valve 55 and the second electromagnetic proportional 56 valve. That is, in this embodiment, when one of the first electromagnetic proportional valve 55 and the second electromagnetic proportional valve 56 does not function normally, the other can be used as an alternative.

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

Abstract

La présente invention concerne un système hydraulique qui comprend : une première électrovanne proportionnelle et une deuxième électrovanne proportionnelle qui, plus le signal de fonctionnement délivré par un premier dispositif de commande et un second dispositif de commande est élevé, plus elles délivrent une pression secondaire plus élevée ; une troisième électrovanne proportionnelle qui, lorsque la première électrovanne proportionnelle ne fonctionne pas correctement, délivre une pression secondaire supérieure, plus la quantité de fonctionnement du premier dispositif de commande est élevée, et qui, lorsque la seconde électrovanne proportionnelle ne fonctionne pas correctement, délivre une pression secondaire plus élevée plus la quantité de fonctionnement du second dispositif de commande est élevée ; une première vanne de sélection haute pression qui sélectionne et guide vers un premier régulateur pour une première pompe, la plus haute parmi la sortie de pression secondaire en provenance de la première électrovanne proportionnelle et la sortie de pression secondaire à partir de la troisième électrovanne proportionnelle ; et une seconde vanne de sélection haute pression qui sélectionne et guide vers un second régulateur pour une seconde pompe, la plus haute parmi la sortie de pression secondaire en provenance de la seconde électrovanne proportionnelle et la sortie de pression secondaire à partir de la troisième électrovanne proportionnelle.
PCT/IB2018/053503 2017-03-30 2018-05-18 Système hydraulique WO2018178961A1 (fr)

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JP2017-067527 2017-03-30

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JP2010048396A (ja) * 2008-08-25 2010-03-04 Sumitomo (Shi) Construction Machinery Co Ltd 建設機械のポンプ制御回路
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JP5356477B2 (ja) * 2011-09-06 2013-12-04 住友建機株式会社 建設機械
JP6235917B2 (ja) * 2014-01-23 2017-11-22 川崎重工業株式会社 液圧駆動システム
KR101815411B1 (ko) * 2014-05-16 2018-01-04 히다찌 겐끼 가부시키가이샤 작업 기계의 압유 에너지 회생 장치
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JP2000282515A (ja) * 1999-03-31 2000-10-10 Kobelco Contstruction Machinery Ltd 建設機械の油圧制御回路
JP2004076910A (ja) * 2002-08-22 2004-03-11 Kobelco Contstruction Machinery Ltd 可変容量型油圧モータの制御装置
JP2005265062A (ja) * 2004-03-18 2005-09-29 Kobelco Contstruction Machinery Ltd 作業機械の油圧制御装置
JP2010048396A (ja) * 2008-08-25 2010-03-04 Sumitomo (Shi) Construction Machinery Co Ltd 建設機械のポンプ制御回路
JP2011256814A (ja) * 2010-06-10 2011-12-22 Sumitomo (Shi) Construction Machinery Co Ltd 建設機械のポンプ吐出量制御回路
JP2013185401A (ja) * 2012-03-09 2013-09-19 Sumitomo (Shi) Construction Machinery Co Ltd 建設機械の制御装置及びその制御方法
JP2016114129A (ja) * 2014-12-12 2016-06-23 日立建機株式会社 電気式操作装置及び電気式操作装置を備えた作業機械
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