WO2009123047A1 - 建設機械の油圧回路 - Google Patents

建設機械の油圧回路 Download PDF

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Publication number
WO2009123047A1
WO2009123047A1 PCT/JP2009/056266 JP2009056266W WO2009123047A1 WO 2009123047 A1 WO2009123047 A1 WO 2009123047A1 JP 2009056266 W JP2009056266 W JP 2009056266W WO 2009123047 A1 WO2009123047 A1 WO 2009123047A1
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WO
WIPO (PCT)
Prior art keywords
valve
pressure
negative control
control pressure
unload
Prior art date
Application number
PCT/JP2009/056266
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
慎一 池生
均 瀬川
Original Assignee
株式会社不二越
ナブテスコ株式会社
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 株式会社不二越, ナブテスコ株式会社 filed Critical 株式会社不二越
Priority to JP2010505828A priority Critical patent/JP5357864B2/ja
Priority to CN200980105395.9A priority patent/CN101946096B/zh
Publication of WO2009123047A1 publication Critical patent/WO2009123047A1/ja

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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
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • 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
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating 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
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • 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
    • E02F9/2292—Systems with two or more pumps
    • 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
    • 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"
    • F15B11/0423—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" by controlling pump output or bypass, other than to maintain constant speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5156—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a return line and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7128—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/77—Control of direction of movement of the output member
    • F15B2211/7741—Control of direction of movement of the output member with floating mode, e.g. using a direct connection between both lines of a double-acting cylinder

Definitions

  • the unloading valve communicates the first unloading passage with the tank by connecting the first unloading passage with the neutral position for blocking the connection between the first unloading passage and the second unloading passage and the tank.
  • the first negative control pressure is input to one chamber of the unload valve
  • the second negative control pressure is input to the other chamber of the unload valve
  • the first negative control pressure is the first negative control pressure.
  • the first switching position is established when the pressure is higher than the two negative control pressures
  • the second switching position is achieved when the second negative control pressure is higher than the first negative control pressure.
  • the discharge flow rate of the split pump will increase and the excess flow rate of oil flowing through the first unloading passage will increase.
  • the unload valve moves to the first switching position.
  • the excess oil which is going to flow through the first unloading passage can be released from the unloading valve to the tank, and the energy loss at the first throttle can be reduced.
  • a second pilot passage one end of which is connected to the non-operation signal generating valve and the other end of which is connected to the low pressure selection valve, is provided in the second pilot passage, and the output of the non-operation signal generating valve And a shuttle valve that selects the higher oil pressure of the third negative control pressure and outputs the oil pressure to the regulator.
  • a hydraulic pressure signal input to one of the chambers of the non-operation signal generating valve as an auto idle signal for idle control of the engine.
  • the second switching position is set.
  • a first nonreturn valve provided between a first branch point on the upstream side of the first throttle and one chamber of the unload valve, the direction from the first branch point toward the unload valve being a forward direction;
  • a second check valve provided in parallel with the first check valve and having a forward direction from the unload valve toward the first branch point, and a second upstream side of the second throttle
  • a third check valve provided between the branch point and the other chamber of the unload valve and having a forward direction from the second branch point toward the unload valve; and the third check valve
  • a fourth check valve provided in parallel and having a forward direction from the unload valve toward the second branch point, the second check valve including a discharge flow rate of the split pump (discharge volume Pressure when the first negative control pressure is higher than the pressure that maximizes the Check valve is preferably open when the second negative control pressure is in a pressure higher than the pressure that maximizes the discharge flow rate of the split pump (discharge capacity).
  • the unload valve shutoff position holding mechanism can be formed with a simple configuration of four check valves.
  • FIG. 16 is a discharge pressure-flow rate characteristic diagram of the pump when the horsepower characteristic is changed according to the pilot pressure.
  • FIG. 6 is a discharge pressure-flow rate characteristic diagram of the pump when changing the pump displacement in accordance with the pilot pressure.
  • It is a circuit diagram showing a hydraulic circuit of a construction machine concerning a 2nd embodiment of the present invention. It is a circuit diagram showing a hydraulic circuit of a construction machine concerning a 3rd embodiment of the present invention.
  • FIG. 1 is a circuit diagram showing a hydraulic circuit of a construction machine according to a first embodiment of the present invention.
  • the pump 111 is a split flow in which an even number of pistons are fitted in one cylinder block connected to the input shaft by a spline, discharges an equal volume of liquid, and has one swash plate 112 Type variable displacement piston pump (split pump), which includes a constant torque control mechanism 142 for effectively utilizing engine horsepower.
  • split pump Type variable displacement piston pump
  • the pump discharge flow rates Q1 and Q2 indicate the discharge flow rates of the pumps 111 and 111a
  • the pump pressures P1 and P2 indicate the pump pressures of the pumps 111 and 111a.
  • the pump 111 and the pump 111a constitute a pump 111 (one-cylinder two-port discharge split pump) having one swash plate 112.
  • the control valves 115 and 116 are roughly divided into two in order to drive a plurality of actuators 119, 120, 125, 126 and 127 for each discharge flow rate of the pump 111, and a plurality of switches disposed in each valve 115 and 116 Valves 118 and 124 (in other words, the plurality of switching valves 118 are the first direction switching valve of the first system, and the plurality of switching valves 124 are the second direction switching valve of the second system)
  • the openings (not shown) of the center bypass passages 13 and 14 are reduced in size according to the amount of operation of the valves 118 and 124, and the flow is led to the actuators 119, 120, 125, 126 and 127.
  • the center bypass passage 13 is, in other words, the first unloading passage connected to one of the discharge ports of the split pump
  • the center bypass passage 14 is, in other words, connected to the other discharge port of the split pump Second unloading passage.
  • the swash plate 112 of the pump 111 is one. Because the pump 111 always discharges an approximately equal volume of oil from the two discharge ports of the pump 111, each pump according to the flow rate passing through the tank ports 121, 128 of the two control valves 115, 116, For example, the discharge amount of the pump 111, 111a could not be reduced optimally.
  • Energy saving can be achieved by reducing the discharge flow rate of the pump 111 only when surplus oil is generated in any of the control valves 115 and 116 at the time of standby without lever operation or at the time of slight operation or the like. .
  • the low pressure selection valve 131 even when the back pressures of the control valves 115 and 116 are equal, one of the pressures is led to the external pilot port of the pump 111.
  • the hydraulic pressure of the center bypass passage 13 between the fixed throttle 9 and the switching valve 118 disposed at the most downstream side (the most downstream side in the direction of the oil flowing through the center bypass passage 13) among the plurality of switching valves 118 Is the first negative control pressure, and between the fixed throttle 10 and the switching valve 124 disposed on the most downstream side (the most downstream side in the direction of the oil flowing through the center bypass passage 14) among the plurality of switching valves 124
  • the hydraulic pressure of the center bypass passage 14 is the second negative control pressure.
  • the first negative control pressure is introduced to the low pressure selection valve 131 via the negative control pressure line 123
  • the second negative control pressure is introduced to the low pressure selection valve 131 via the negative control pressure line 130.
  • the minimum pressure (the lower one of the first negative control pressure and the second negative control pressure) selected by the low pressure selection valve 131 and output to the constant torque control mechanism 142 is the third negative control pressure.
  • the hydraulic circuit 201 includes three first direction switching valves 6x to 6z of the first system connected to the first unload passage 13 and three third of the second system connected to the second unload passage 14. Two-way switching valves 7x to 7z are provided.
  • the first direction switching valves 6x to 6z and the second direction switching valves 7x to 7z are all center bypass type and hydraulic pilot type direction switching valves. Further, the first direction switching valves 6x to 6z are arranged in series in the first unloading passage 13, and the second direction switching valves 7x to 7z are arranged in series in the second unloading passage 14.
  • the second direction switching valve 7x is a valve that controls the supply of pressure oil to the right traveling motor 60
  • the second direction switching valve 7y is a valve that controls the supply of pressure oil to the swing hydraulic motor 59
  • the second direction switching valve 7z is a valve that controls the supply of pressure oil to the arm hydraulic cylinder 58 that operates the arm.
  • the hydraulic circuit 201 is configured to set the lower one of the first negative control pressure which is the hydraulic pressure on the upstream side of the first throttle 9 and the second negative control pressure which is the hydraulic on the upstream side of the second throttle 10 to a third negative control pressure.
  • the first negative pressure which is the hydraulic pressure of the first unloading passage 13 between the first direction switching valve 6 z and the first throttle 9
  • the second negative pressure which is the hydraulic pressure of the second unloading passage 14 between the second direction switching valve 7 z and the second throttle 10 is input to the other chamber 82 of the selection valve 8.
  • a regulator pilot passage 16 connecting the low pressure selection valve 8 and the regulator 52 is provided.
  • the third negative control pressure output from the low pressure selection valve 8 is input to the regulator 52 through the regulator pilot passage 16.
  • a second unload valve 3 is provided for releasing the tank 54 from the second unload passage 14 upstream of the second direction switching valve 7x.
  • the upstream passage 75 of the second unload valve 3 is connected to the second unload passage 14 upstream of the second direction switching valve 7 x, and the downstream passage 73 of the second unload valve 3 is connected to the discharge passage 71. It is connected.
  • FIG. 10 is a graph showing the discharge flow rate characteristic of the split pump 51 and the opening characteristic of the unload valves 2 and 3.
  • the turning hydraulic motor 59 is operated by operating the second direction switching valve 7y.
  • the second negative control pressure becomes lower than the first negative control pressure.
  • the second negative control pressure is selected by the low pressure selection valve 8 and output as the third negative control pressure, and is input to the regulator 52 through the regulator pilot passage 16.
  • the discharge flow rate from the discharge port 51 a and the discharge port 51 b of the split pump 51 both increases to the necessary flow rate of the second system.
  • FIG. 7 is a circuit diagram showing a hydraulic circuit 202 according to a third embodiment of the present invention.
  • the present embodiment will be described focusing on differences from the second embodiment.
  • the same components as those of the second embodiment are denoted by the same reference numerals (the same applies to the other embodiments).
  • the hydraulic circuit 202 includes the unload flow control valves 4 and 5.
  • the hydraulic circuit 202 includes a first unloading flow control valve 4 provided in the downstream passage 72 of the first unloading valve 2 between the first unloading valve 2 and the tank 54. ing.
  • the first unload flow control valve 4 has a shutoff position 4b and a communication position 4a, and the pressure on the downstream side of the first unload control valve 2 is input to one chamber 41 and the first flow control valve spring 43 is disposed.
  • the pressure in the first unloading passage 13 upstream of the first direction switching valve 6x (the pressure on the upstream side of the first unloading valve 2) is input to the other chamber 42.
  • the hydraulic circuit 203 according to the fourth embodiment includes the non-operation signal generation valve 15.
  • a first pilot passage 18 upstream of the most upstream sub valve 11 x is connected to one chamber 61 of the non-operation signal generation valve 15 via a passage 77.
  • a spring 62 is disposed in the chamber 61.
  • a first pilot passage 18 on the upstream side of the most upstream sub valve 11 x is connected to the other chamber 63 of the non-operation signal generation valve 15 via a passage 78.
  • a throttle 19 is provided in the first pilot passage 18 between the passage 78 and the sub valve 11x.
  • the passage 78 corresponds to the pressing means disposed in the other chamber 63 of the present invention, and the pressure of the pilot pump 53 is input to the chamber 63 via the passage 78.
  • a spring may be disposed in the chamber 63 and the spring may be used as a pressing unit. Also, the spring and the passage 78 may be used in combination.
  • the first unload valve 2 and the second unload valve 3 release the oil from the unload passages 13 and 14 upstream of the first direction switching valve 6x and the second direction switching valve 7x to the tank 54, respectively.
  • excess oil which is going to flow through the unloading passages 13 and 14 can be released from the unloading valves 2 and 3 to the tank 54 even when all the directional control valves 6x to 7z are not operated.
  • the energy loss at the first aperture 9 and the second aperture 10 can be further reduced.
  • any one direction switching valve when any one direction switching valve is operated, the corresponding sub valve switches to the shut off position.
  • the pressures before and after the throttle 19 become almost equal, and the non-operation signal generating valve 15 switches to the position 15a.
  • one second chamber 22 of the first unloading valve 2 and one second chamber 32 of the second unloading valve 3 are both connected to the tank 54.
  • the non-operation signal generating valve 15 when all the direction switching valves 6x to 7z of the first system and the second system are not operated, the non-operation signal generating valve 15 is in the state of the position 15b. At this time, the pressure from the pilot pump 53 that is higher than the discharge pressure of the split pump 51 acts on the second pilot passage 20. Thereby, the shuttle valve 17 selects the high pressure from the pilot pump 53 and outputs the high pressure to the regulator 52. As a result, the discharge flow rate of the split pump 51 decreases to Qmin. That is, the non-operation signal generation valve 15 outputs an oil pressure signal for reducing the discharge flow rate of the split pump 51 when all the direction switching valves 6x to 7z are not operated.
  • the hydraulic circuit can be simplified by using the signal from the non-operation signal generation valve 15 in combination with the signal for regulator and the signal for unload valve.
  • the negative control pressure is set to a pressure lower than 3 MPa, and the pressure of the pilot pump 53 is set to 3 MPa or more.
  • the hydraulic pressure signal (pilot pressure signal) from the first pilot passage 18 input to one chamber 61 of the non-operation signal generation valve 15 is sent to the control unit of the engine (not shown) via the port 79, It is used as an auto idle signal for idle control of the engine.
  • the hydraulic circuit can be simplified by using the signal for the non-operation signal generation valve 15 and the auto idle signal in combination.
  • FIG. 9 is a circuit diagram showing a hydraulic circuit 204 according to a fifth embodiment of the present invention.
  • the hydraulic circuit 204 of this embodiment is a combination of the hydraulic circuit 202 of the third embodiment and the hydraulic circuit 203 of the fourth embodiment.
  • FIG. 11 is a circuit diagram showing a hydraulic circuit 205 according to a sixth embodiment of the present invention.
  • the present embodiment will be described focusing on differences from the third embodiment.
  • the same components as those of the third embodiment are denoted by the same reference numerals.
  • the main difference between the sixth embodiment and the third embodiment is that the hydraulic circuit 205 according to the sixth embodiment includes the unload valve shutoff position holding mechanism 94.
  • the hydraulic circuit 205 holds the first unload valve 2 at the shutoff position 2b when the first negative control pressure maximizes the discharge flow rate of the split pump 51, and the second negative control pressure maximizes the discharge flow rate of the split pump 51.
  • the unload valve shutoff position holding mechanism 94 is provided to hold the second unload valve 3 in the shutoff position 3b.
  • the first negative control pressure makes the discharge flow rate of the split pump 51 maximum, it means that the first negative control pressure is 0 to Pf in FIG. 10A.
  • the second negative control pressure maximizes the discharge flow rate of the split pump 51 it means that the second negative control pressure is 0 to Pf in FIG. 10 (a).
  • the unload valve shutoff position holding mechanism 94 configured by the two check valves 91 and 92 is configured such that the pressure in the other chambers 23 and 33 of the first unload valve 2 and the second unload valve 3 is Pf. Don't get lower pressure than that.
  • FIG. 13 is a graph showing the relationship between the first negative control pressure and the second negative control pressure when the direction switching valve is operated.
  • the discharge flow rate of the split pump 51 is small (see FIG. 10A).
  • the discharge flow rate from the discharge port 51a and the discharge port 51b of the split pump 51 is Qmin.
  • the pressure in the other chambers 23 and 33 of the first unload valve 2 and the second unload valve 3 is maintained at Pf by the unload valve shutoff position holding mechanism 94.
  • the second unload valve 3 switches (moves) from the blocking position 3b to the communication position 3a by a stroke amount corresponding to the negative control differential pressure (Pb1-Pf), and responds to the negative control differential pressure (Pb1-Pf).
  • the excess oil (the amount of oil corresponding to the pressure of Pb1-Pf) of the second system flows through the downstream passage 73 and escapes to the tank 54 (FIG. 10 (b)). reference).
  • the first unload valve 2 is at the shutoff position 2b.
  • the second direction switching valve 7y and the second direction switching valve 7z of the second system are further operated, and as a result, as shown in FIG. 13 (b), the second negative control pressure Pb1 is higher than Pa1. Suppose that the pressure is low Pb2.
  • FIG. 12 is a circuit diagram showing a hydraulic circuit 206 according to a seventh embodiment of the present invention.
  • the hydraulic circuit 206 of this embodiment is a combination of the hydraulic circuit 205 of the sixth embodiment and the hydraulic circuit 203 of the fourth embodiment.
  • FIG. 14 is a circuit diagram showing a hydraulic circuit 301 according to an eighth embodiment of the present invention.
  • the present embodiment will be described focusing on differences from the second embodiment.
  • the same components as those of the second embodiment are denoted by the same reference numerals.
  • the hydraulic circuit 301 sets the amount of oil corresponding to the pressure difference between the first negative control pressure and the second negative control pressure in the most upstream first direction.
  • the unloading valve 25 is provided to release the tank 54 from the first unloading passage 13 upstream of the switching valve 6x.
  • the unload valve 25 sets the amount of oil corresponding to the pressure difference between the first negative control pressure and the second negative control pressure to the most upstream side. It is also a valve for releasing the tank 54 from the second unloading passage 14 upstream of the two-way switching valve 7x.
  • the unload valve 25 is connected to a first branched unload passage 13a branched from the first unload passage 13 between the split pump 51 and the first direction switching valve 6x. Further, the unload valve 25 is also connected to a second branched unload passage 14a branched from the second unload passage 14 between the split pump 51 and the second direction switching valve 7x. Further, the downstream side passages 72 and 73 of the unloading valve 25 are connected to the discharge passage 71.
  • first negative control pressure is input to one chamber 26 of the unload valve 25, and the second negative control pressure is input to the other chamber 27 of the unload valve 25.
  • the unload valve 25 is in the first switching position 25a when the first negative control pressure is higher than the second negative control pressure, and is in the second switching position 25c when the second negative control pressure is higher than the first negative control pressure. .
  • the state in which the unload valve 25 is in the first switching position 25a and the first unload passage 13 is in communication with the tank 54 means that the opening area of the unload valve 25 to be communicated is not zero. That is, it does not mean that only the state in which the opening area of the valve is maximized (the same applies to the second switching position 25c).
  • FIG. 10 (b) is also a graph showing the opening characteristic of the unloading valve 25.
  • the opening characteristic of the unloading valve 25 is linear, but the opening characteristic of the unloading valve 25 is non-linear depending on the manufacturing convenience of the unloading valve 25 and the preference of the operator. It may be For example, as shown by the alternate long and short dash line in FIG. 10B, by making the opening characteristic concave, the supply flow rate at the time of combined operation can be increased and the pressure can be increased only at the time of additional combined operation. The strength of the operation increases. Further, as shown by a two-dot chain line in FIG. 10B, by making the opening characteristic into a convex shape, the soft feeling of the operation is enhanced.
  • the operation of the hydraulic shovel (the operation of the hydraulic circuit 301) will be described with reference to FIG. First, it is assumed that all the directional control valves 6x to 7z of the first and second systems are not operated. At this time, since both the first negative control pressure and the second negative control pressure are high, the third negative control pressure selected by the low pressure selection valve 8 and input to the regulator 52 is also high. Accordingly, the discharge flow rate of the split pump 51 is small (see FIG. 10A). For example, the discharge flow rate from the discharge port 51a and the discharge port 51b of the split pump 51 is Qmin.
  • the turning hydraulic motor 59 is operated by operating the second direction switching valve 7y.
  • the second negative control pressure becomes lower than the first negative control pressure.
  • the second negative control pressure is selected by the low pressure selection valve 8 and output as the third negative control pressure, and is input to the regulator 52 through the regulator pilot passage 16.
  • the discharge flow rate from the discharge port 51 a and the discharge port 51 b of the split pump 51 both increases to the necessary flow rate of the second system.
  • the unload valve 25 switches (moves) from the neutral position 25b to the first switching position 25a by a stroke amount corresponding to the negative control differential pressure, and becomes an unload valve opening area according to the negative control differential pressure.
  • the surplus oil of the first system (the amount of oil corresponding to the negative control pressure difference) flows through the downstream passage 72 and is released to the tank 54 (see FIG. 10B).
  • FIG. 15 is a circuit diagram showing a hydraulic circuit 302 according to a ninth embodiment of the present invention.
  • the present embodiment will be described focusing on differences from the eighth embodiment.
  • the same components as those in the eighth embodiment are denoted by the same reference numerals.
  • the hydraulic circuit 302 further includes a second unloading flow control valve 5 provided in the downstream passage 73 of the unloading valve 25.
  • the second unloading flow control valve 5 is provided with the shutoff position 5 b and the communication position 5 a, the pressure of the second system downstream of the unloading valve 25 is input to one chamber 51, and The pressure (pressure on the upstream side of the unloading valve 25) of the second unloading passage 14 on the upstream side of the two-way switching valve 7x is input, and the spring 54 for the second floating valve is disposed.
  • FIG. 16 is a circuit diagram showing a hydraulic circuit 303 according to a tenth embodiment of the present invention. The present embodiment will be described focusing on differences from the eighth embodiment. The main difference between the tenth embodiment and the eighth embodiment is that the hydraulic circuit 303 according to the tenth embodiment includes the neutral unload valve 35 and the non-operation signal generation valve 15.
  • the neutral unload valve 35 is disposed upstream of the first unload passage 13 upstream of the first direction switching valve 6x and on the upstream side of the second direction switching valve 7x when all the direction switching valves 6x to 7z are not operated. Oil is released from the second unloading passage 14 to the tank 54. As shown in FIG. 16, the neutral unload valve 35 is connected to the first branch unload passage 13a and the second branch unload passage 14a, and is connected to the discharge passage 71 via the passage 83 on the downstream side thereof. doing. The neutral unload valve 35 also has a shutoff position 35b and a communication position 35a.
  • any one direction switching valve when any one direction switching valve is operated, the corresponding sub valve switches to the shut off position.
  • the pressures before and after the throttle 19 become almost equal, and the non-operation signal generating valve 15 switches to the position 15a.
  • all the pilot chambers 36 of the neutral unload valve 35 are connected to the tank 54, and the neutral unload valve 35 is in the shutoff position 35b.
  • the hydraulic circuit 303 is provided with a second pilot passage 20 having one end connected to the non-operation signal generation valve 15 and the other end connected to the low pressure selection valve 8.
  • the hydraulic circuit 303 includes the shuttle valve 17 provided in the second pilot passage 20.
  • the hydraulic circuit can be simplified by using the signal from the non-operation signal generation valve 15 in combination with the signal for regulator and the signal for unload valve.
  • FIG. 17 is a circuit diagram showing a hydraulic circuit 304 according to an eleventh embodiment of the present invention.
  • the hydraulic circuit 304 of the present embodiment is a combination of the hydraulic circuit 302 of the ninth embodiment and the hydraulic circuit 303 of the tenth embodiment.
  • FIG. 18 is a circuit diagram showing a hydraulic circuit 305 according to a twelfth embodiment of the present invention.
  • the present embodiment will be described focusing on differences from the ninth embodiment.
  • the same components as those of the ninth embodiment are denoted by the same reference numerals.
  • the main difference between the twelfth embodiment and the ninth embodiment is that the hydraulic circuit 305 according to the twelfth embodiment is provided with an unload valve shutoff position holding mechanism 87.
  • the hydraulic circuit 305 is at a position (neutral position 25 b or second switching position 25 c) that shuts off between the first unload passage 13 and the tank 54 when the first negative control pressure maximizes the discharge flow rate of the split pump 51.
  • the second check valve 95 and the fourth check valve 84 each have a spring 97 and a spring 86.
  • the spring 97 is designed such that the second check valve 95 opens when the first negative control pressure is higher than the pressure at which the discharge flow rate of the split pump 51 is maximized.
  • the spring 86 is designed such that the fourth check valve 84 opens when the second negative control pressure is higher than the pressure at which the discharge flow rate of the split pump 51 is maximized.
  • the pressure that maximizes the discharge flow rate of the split pump 51 refers to the pressure of Pf in FIG.
  • FIG. 13 is a graph showing the relationship between the first negative control pressure and the second negative control pressure when the direction switching valve is operated.
  • the discharge flow rate of the split pump 51 is small (see FIG. 10A).
  • the discharge flow rate from the discharge port 51a and the discharge port 51b of the split pump 51 is Qmin.
  • the actuators 55 to 57 are operated by operating the first direction switching valve 6x, the first direction switching valve 6y, the first direction switching valve 6z of the first system, and the second direction switching valve 7x of the second system.
  • the pressure oil is supplied to operate, and as a result, as shown in FIG. 13A, the first negative control pressure becomes a pressure Pa1 lower than Pf, and the second negative control pressure Pb1 (Pf ⁇ It is assumed that Pb1 ⁇ Ps).
  • the first negative control pressure (Pa1) is selected by the low pressure selection valve 8 and is output as the third negative control pressure and input to the regulator 52.
  • the discharge flow rate from the discharge port 51 a and the discharge port 51 b of the split pump 51 both become Qmax (maximum flow rate).
  • the unload valve 25 switches (moves) from the neutral position 25b to the second switching position 25c by a stroke amount corresponding to the negative control differential pressure (Pb1-Pf), and responds to the negative control differential pressure (Pb1-Pf).
  • the excess oil (the amount of oil corresponding to the pressure of Pb1-Pf) of the second system flows through the downstream passage 73 and escapes to the tank 54 (FIG. 10 (b)). reference).
  • FIG. 19 is a circuit diagram showing a hydraulic circuit 306 according to a thirteenth embodiment of the present invention.
  • the hydraulic circuit 306 of the present embodiment is a combination of the hydraulic circuit 305 of the twelfth embodiment and the hydraulic circuit 303 of the tenth embodiment.
  • the back pressure of the oil flowing through the two center bypasses is the external signal pressure (the first negative control pressure and the second negative control pressure).
  • the lower one of the external signal pressures selected by the low pressure selection valve third negative control pressure
  • the back pressure of oil flowing through three or more center bypasses three or more unloading passages
  • the minimum pressure selected by the low pressure selection valve of the external signal pressure is fed back to the pump It is also good.
  • the present invention can be applied to a hydraulic circuit having three or more center bypasses.
  • Hydraulic circuit of construction machine 2 first unloading valve 3: second unloading valve 4: first unloading flow control valve 5: second unloading flow control valve 6x, 6y, 6z: first direction switching valve 7x, 7y, 7z: second direction switching valve 8: low pressure selection valve 9: first throttle 10: second throttle 13: first unloading passage (center bypass) 14: 2nd unloading passage (center bypass) 51, 111: Split pump 52: Regulator 54: Tank 112: Swash plate 115, 116: Control valve 118, 124: Switch valve 119, 120, 125, 126, 127: Actuator

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PCT/JP2009/056266 2008-03-31 2009-03-27 建設機械の油圧回路 WO2009123047A1 (ja)

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JP2017009087A (ja) * 2015-06-25 2017-01-12 ナブテスコ株式会社 油圧駆動装置
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JP2020076474A (ja) * 2018-11-09 2020-05-21 ヤンマー株式会社 建設機械
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