EP1193400A2 - Hydraulikkreislauf für Baumaschinen - Google Patents

Hydraulikkreislauf für Baumaschinen Download PDF

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Publication number
EP1193400A2
EP1193400A2 EP01302602A EP01302602A EP1193400A2 EP 1193400 A2 EP1193400 A2 EP 1193400A2 EP 01302602 A EP01302602 A EP 01302602A EP 01302602 A EP01302602 A EP 01302602A EP 1193400 A2 EP1193400 A2 EP 1193400A2
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EP
European Patent Office
Prior art keywords
circuit
hydraulic fluid
pressure
attachment
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP01302602A
Other languages
English (en)
French (fr)
Other versions
EP1193400B1 (de
EP1193400A3 (de
Inventor
Yoshiyuki Shimada
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Caterpillar Japan Ltd
Caterpillar Mitsubishi Ltd
Original Assignee
Caterpillar Mitsubishi Ltd
Shin Caterpillar Mitsubishi Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Caterpillar Mitsubishi Ltd, Shin Caterpillar Mitsubishi Ltd filed Critical Caterpillar Mitsubishi Ltd
Publication of EP1193400A2 publication Critical patent/EP1193400A2/de
Publication of EP1193400A3 publication Critical patent/EP1193400A3/de
Application granted granted Critical
Publication of EP1193400B1 publication Critical patent/EP1193400B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • E02F9/2253—Controlling the travelling speed of vehicles, e.g. adjusting travelling speed according to implement loads, control of hydrostatic transmission
    • 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
    • E02F9/2228—Control of flow rate; Load sensing arrangements using pressure-compensating valves including an electronic controller
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2285—Pilot-operated systems
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with 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
    • 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
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • 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
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable 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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40523—Flow control characterised by the type of flow control means or valve with flow dividers
    • F15B2211/4053—Flow control characterised by the type of flow control means or valve with flow dividers using 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow 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
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to 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
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in 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
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure 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
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of a differential 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load 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
    • F15B2211/60—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6654—Flow rate 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • 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
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority

Definitions

  • the present invention relates to a hydraulic circuit which is installed in a construction machine and includes a pressure compensation flow dividing valve.
  • a hydraulic circuit of a construction machine disclosed in Japanese Patent provisional Publication No. 2000-73409 is provided with a pressure compensation flow dividing valve 8 disposed between a group of components consisting of a first pump 2 and a second pump 3, which are adapted to be driven by an engine 1 mounted on a hydraulic shovel, and a group of components consisting of a left-side travelling circuit 5, a right-side travelling circuit 6 and an independent attachment circuit 7.
  • the left-side travelling circuit 5 includes a left-side travelling control spool 11a of a main control valve 11 which is adapted to control hydraulic fluid fed from the first pump 2.
  • the right-side travelling circuit 6 includes a right-side travelling control spool 12a of a main control valve 12 which is adapted to control hydraulic fluid fed from the second pump 3.
  • controlled hydraulic fluid drives hydraulic motors (not shown) of the right and left crawler belt type travelling systems mounted on the hydraulic shovel.
  • the aforementioned independent attachment circuit 7 includes an attachment control valve (not shown) for controlling the hydraulic fluid fed from the first pump 2 and the second pump 3.
  • an attachment e.g. a hydraulic breaker or a crusher, which is attached to the front end of the front working equipment of the hydraulic shovel in the place of the bucket.
  • the pressure compensation flow dividing valve 8 compensates the pressure of the hydraulic fluid that is fed from the first pump 2 and divided so as to flow into the left-side travelling circuit 5 and the independent attachment circuit 7 and also compensates the pressure of the hydraulic fluid that is fed from the second pump 3 and divided so as to flow into the right-side travelling circuit 6 and the independent attachment circuit 7.
  • the pressure compensation flow dividing valve 8 contains a flow dividing control spool valve 13, a pressure compensation valve 14 for constantly maintaining the differential pressure between a B1 port and an A1 port of the flow dividing control spool valve 13 (FB1 - PA1) at a given level, a pressure compensation valve 15 for constantly maintaining the differential pressure between a B2 port and an A2 port of the flow dividing control spool valve 13 (PB2 - PA2) at a given level, and check valves 16,17 respectively disposed in the output circuits extending from the two pressure compensation valves 14,15 to the independent attachment circuit 7.
  • the flow dividing control spool valve 13 has internal oil channels 21,22 having such aperture characteristics that the flow rate of the hydraulic fluid that is fed from the first pump 2 and branches off to the left-side travelling circuit 5 is equal to the flow rate of the hydraulic fluid that is simultaneously fed from the second pump 3 and branches off to the right-side travelling circuit 6.
  • the flow dividing control spool valve 13 is also provided with internal oil channels 23,24 having such aperture characteristics that the flow rate of the hydraulic fluid that is fed from the first pump 2 and branches off to the independent attachment circuit 7 is equal to the flow rate of the hydraulic fluid that is simultaneously fed from the second pump 3 and branches off to the independent attachment circuit 7.
  • the pressure compensation flow dividing valve 8 when simultaneously running the hydraulic shovel and operating its attachment, is capable of feeding hydraulic fluid to the left-side travelling circuit 5 and the right-side travelling circuit 6 at the same flow rate regardless of the position of the flow dividing control spool valve 13 and consequently keeping the hydraulic shovel running straight.
  • each hydraulic pump installed in such a hydraulic shovel as described above has a threshold curve between the pump discharge rate, which is determined by the engine power, and the discharge pressure.
  • a diagram illustrating such a threshold curve (hereinafter called P-Q curve diagram) is shown in Fig. 2.
  • the hydraulic pump is designed such that the higher the discharge pressure, the lower the pump discharge rate.
  • the pressure compensation valves 14,15 function in such a manner that the hydraulic fluid is fed to the independent attachment circuit 7 at a flow rate corresponding to the degree of aperture of the internal oil channels 23,24 of the flow dividing control spool valve 13 regardless of the pressure in the circuit. Therefore, nearly all of the hydraulic fluid discharged from the pump flows into the independent attachment circuit 7 when the pump discharge rate is reduced as shown in the P-Q curve of Fig. 2 as a result of the pressure in the attachment circuit reaching a level high enough to be nearly equal to the relief pressure, should the internal oil channels 23,24 of the flow dividing control spool valve 13 be widely open. As a result, hydraulic fluid stops flowing into main body actuators, such as hydraulic travelling motors, etc.
  • an object of the present invention is to provide a hydraulic circuit of a construction machine, which includes a pressure compensation flow dividing valve and ensures the supply of a necessary amount of hydraulic fluid to main body actuators even if the pressure in the attachment circuit approaches the relief pressure in the course of operating the attachment in conjunction with the main body actuators, thereby preventing sharp reduction in the speed of the main body actuators.
  • the invention as claimed in claim 1 relates to a hydraulic circuit of a construction machine, said hydraulic circuit including main circuits for controlling hydraulic fluid pumped up from a tank by pumps mounted on a construction machine, thereby feeding the hydraulic fluid to main body actuators mounted on the construction machine; an attachment circuit for controlling hydraulic fluid pumped up from the tank by the pumps, thereby feeding the hydraulic fluid to an attachment mounted on the construction machine; a pressure compensation flow dividing valve adapted to compensate the pressure of the hydraulic fluid fed from the pumps and divided so as to flow into the main circuits and the attachment circuit; an external channel for returning into the tank the hydraulic fluid fed from the pressure compensation flow dividing valve to the attachment circuit; and a selector valve adapted to shift from a channel-shutting position to a channel-communicating position when the attachment circuit pressure is increased to a level nearly equal to the relief pressure in the course of operating the attachment in conjunction with the main body actuators.
  • the invention claimed in claim 2 relates to a hydraulic circuit as claimed in claim 1, wherein the pumps comprise a first pump and a second pump; the main circuits have a first main circuit that includes a left-side travelling control spool for controlling a left-side hydraulic travelling motor of the machine body and a second main circuit that includes a right-side travelling control spool for controlling a right-side hydraulic travelling motor of the machine body; and the pressure compensation flow dividing valve includes a single flow dividing control spool valve adapted to control hydraulic fluid so that the hydraulic fluid is fed from the first pump to the first main circuit and from the second pump to the second main circuit and the attachment circuit at the same flow rate.
  • the pressure compensation flow dividing valve ensures that hydraulic fluid is constantly fed into the first main circuit and the second main circuit at the same flow rate.
  • the invention is capable of preventing deviation of the construction machine from running straight.
  • Fig. 1 shows an example of a hydraulic circuit, wherein_a pressure compensation flow dividing valve 38 is disposed between a group of components consisting of a first pump 32 and a second pump 33, which are adapted to be driven by an engine 31 mounted on a construction machine, i.e. a hydraulic shovel in case of the present embodiment, and a group of components consisting of a first main circuit 35, a second main circuit 36 and an independent attachment circuit 37, which is provided independently of these main circuits.
  • the first pump 32 and the second pump 33 function to feed hydraulic fluid pumped up from a tank 39 to the first main circuit 35, the second main circuit 36 and the independent attachment circuit 37 through the pressure compensation flow dividing valve 38.
  • the first main circuit 35 includes a main control valve 41 for controlling hydraulic fluid fed from the first pump 32, while the second main circuit 36 includes a main control valve 42 for controlling hydraulic fluid fed from the second pump 33.
  • the main control valves 41,42 function to supply the main body actuators with the hydraulic fluid that has been fed from the pumps 32,33 through the pressure compensation flow dividing valve 38 to the main control valves 41,42 while controlling directions and flow rates of the hydraulic fluid.
  • the main body actuators consist of hydraulic motors mounted on the lower structure, i.e. the left-side hydraulic travelling motor for driving the left-side crawler belt and the right-side hydraulic travelling motor for driving the right-side crawler belt, a hydraulic swing motor for revolving the super structure on the lower structure, and actuators for driving the boom, arm and the bucket of the front working equipment on the super structure, i.e. an arm hydraulic cylinder, a boom hydraulic cylinder and a bucket hydraulic cylinder.
  • the main control valve 41 of the first main circuit 35 includes a left-side travelling control spool for controlling the left-side hydraulic travelling motor of the machine body
  • the main control valve 42 of the second main circuit 36 includes a right-side travelling control spool for controlling the right-side hydraulic travelling motor of the machine body.
  • either main control valve 41 or 42 includes swing control spools for controlling the swing hydraulic motor, boom control spools for controlling the boom hydraulic cylinder(s), arm control spools for controlling the arm hydraulic cylinder, and bucket control spools for controlling the bucket hydraulic cylinder.
  • the aforementioned independent attachment circuit 37 includes an attachment control valve (not shown) for controlling the hydraulic fluid fed from the first pump 32 and the second pump 33.
  • an attachment control valve for controlling the hydraulic fluid fed from the first pump 32 and the second pump 33.
  • the independent attachment circuit 37 operates an attachment, e.g. a hydraulic breaker or a crusher, which is attached to the front end of the front working equipment of the hydraulic shovel in the place of the bucket.
  • the pressure compensation flow dividing valve 38 compensates the pressure of the hydraulic fluid that is fed from the first pump 32 and divided so as to flow into the first main circuit 35 and the independent attachment circuit 37 and also compensates the pressure of the hydraulic fluid that is fed from the second pump 33 and divided so as to flow into the second main circuit 36 and the independent attachment circuit 37.
  • the pressure compensation flow dividing valve 38 contains a single flow dividing control spool valve 43, a pressure compensation valve 44 for constantly maintaining the differential pressure between a B1 port and an A1 port of the flow dividing control spool valve 43 (PB1 - PA1) at a given level, a pressure compensation valve 45 for constantly maintaining the differential pressure between a B2 port and an A2 port of the flow dividing control spool valve 43 (PB2 - PA2) at a given level, and check valves 46,47 respectively disposed in the output circuits extending from the two pressure compensation valves 44,45 to the independent attachment circuit 37.
  • the aforementioned single flow dividing control spool valve 43 contained in the pressure compensation flow dividing valve 38 is provided with internal oil channels 51,52 extending from the first pump 32 and internal oil channels 53,54 extending from the second pump 33.
  • the internal oil channel 51 is provided for the hydraulic fluid that branches off to the first main circuit 35
  • the internal oil channel 52 is provided for the hydraulic fluid that branches off to the independent attachment circuit 37.
  • the internal oil channel 53 is provided for the hydraulic fluid that branches off to the second main circuit 36
  • the internal oil channel 54 is provided for the hydraulic fluid that branches off to the independent attachment circuit 37.
  • the internal oil channels 51,53 of the flow dividing control spool valve 43 have such aperture characteristics as to make the flow rate of the hydraulic fluid that is fed from the first pump 32 and branches off to the first main circuit 35 equal to the flow rate of the hydraulic fluid that is simultaneously fed from the second pump 33 and branches off to the second main circuit 36.
  • the internal oil channels 52,54 have such aperture characteristics as to make the flow rate of the hydraulic fluid that is fed from the first pump 32 and branches off to the independent attachment circuit 37 equal to the flow rate of the hydraulic fluid that is simultaneously fed from the second pump 33 and branches off to the independent attachment circuit 37.
  • the flow dividing control spool valve 43 controls the hydraulic fluid so that the hydraulic fluid is fed from the first pump 32 to the first main circuit 35 and the attachment circuit 37 at the same flow rate as that of the hydraulic fluid fed from the second pump 33 to the second main circuit 36 and the independent attachment circuit 37.
  • the internal oil channels 52,54 for feeding hydraulic fluid to the independent attachment circuit 37 are respectively provided with variable throttles 55,56, of which the areas of the apertures can be changed in accordance with the spool stroke.
  • the flow dividing control spool valve 43 is so designed as to receive, at one end thereof, the constant force from a spring 57 and receive at the other end the pilot pressure introduced from a Pi port via a pilot pressure introducing channel 58 so that the spool valve stroke is controlled at the equilibrium point between the pushing force of the pilot pressure and the rebounding force of the spring 57.
  • a drain oil channel 64 is drawn out of the flow dividing control spool valve 43 and communicates with a tank 39.
  • a pressure sensor 66 is disposed in an independent attachment line 65, through which hydraulic fluid is fed to the independent attachment circuit 37.
  • An external channel 67 branches off from a priority channel, which is provided between the pressure compensation valve 45 and the check valve 47 in the pressure compensation flow dividing valve 38.
  • An electromagnetic selector valve 68 serving as a selector valve is disposed in the external channel 67 so that the external channel 67 is connected to the tank 39 through the electromagnetic selector valve 68.
  • the electromagnetic selector valve 68 is a selector valve adapted to be shifted from a channel-shutting position to a channel-communicating position by the energized solenoid when the pressure in the independent attachment circuit 37, i.e. the attachment circuit pressure, is increased to a level nearly equal to the relief pressure in the course of operating the attachment in conjunction with the main body actuators.
  • the hydraulic fluid which is fed from the pressure compensation flow dividing valve 38 to the independent attachment circuit 37 can be returned into the tank 39 through the external channel 67 as a result of the electromagnetic selector valve 68 shifting to the channel-communicating position.
  • the aforementioned pressure sensor 66 is connected to an input terminal of a controller 71.
  • the electromagnetic selector valve 68 is connected to an output terminal of the controller 71.
  • the controller 71 is adapted to shift the position of the spool of the control valve of the independent attachment circuit 37 based on output signals corresponding to lever signals input from an attachment operating unit 72, which may be an electric joy stick or the like. Furthermore, based on output signals corresponding to lever signals input from a main body actuator operating unit 73, which may be an electric joy stick or the like, the controller 71 shifts the aforementioned spools of the main control valves 41,42, which function to control the main body actuators.
  • the controller 71 is designed such that, only when signals are input from the pressure sensor 66 to the controller 71 as a result of a rise of high pressure in the proximity of the relief pressure in the independent attachment line 65 while simultaneous operation of the attachment operating unit 72 and the main body actuator operating unit 73 causes electric signals from the two operating units to be simultaneously input to the controller 71, the controller 71 transmits electric switching signals to the solenoid of the electromagnetic selector valve 68, thereby shifting the electromagnetic selector valve 68 to the channel-communicating position to cause the hydraulic fluid fed from the second pump 33 into a channel 76 to flow into the tank 39 via the external channel 67.
  • a bypass channel 74 is provided between the left-side main control valve 41 and the right-side main control valve 42, and a bypass valve 75 is disposed in the bypass channel 74.
  • the bypass valve 75 is designed such that, only when high pressure nearly equal to the relief pressure rises in the independent attachment line 65 while the attachment operating unit 72 and the main body actuator operating unit 73 are simultaneously operated, the solenoid of the bypass valve 75 receives electric signals from the controller 71 so that the bypass valve 75 shifts from the channel-shutting position to the channel-communicating position, thereby opening the bypass channel 74.
  • the hydraulic fluid is constantly fed to an A11 port and an A22 port of the pressure compensation valves 44,45 at an equally divided flow rate, because the oil channel extending from the P1 port through the internal oil channel 52 to the A1 port and the oil channel extending from the P2 port through the internal oil channel 54 to the A2 port always have the same aperture characteristics.
  • the pressure compensation flow dividing valve 38 ensures that the hydraulic fluid is constantly fed from the first pump 32 and the second pump 33 to the independent attachment circuit 37 at the same flow rate so that the hydraulic fluid is constantly fed into the first main circuit 35 and the second main circuit 36 at the same flow rate. Therefore, the vehicle will not deviate from running straight, because the flow rate of the hydraulic fluid fed from the left-side travelling control spool of the first main control valve 41 to the left-side travelling motor is always the same as that of the hydraulic fluid fed from the right-side travelling control spool of the second main control valve 42 to the right-side travelling motor.
  • the pressure sensor 66 detects the increase of pressure and inputs signals indicating it into the controller 71.
  • the controller 71 outputs operating signals to the electromagnetic selector valve 68 so that the electromagnetic selector valve 68 shifts to the channel-communicating position where the external channel 67 communicates with the tank 39.
  • priority hydraulic fluid branching off from the priority channel into the external channel 67 escapes through the electromagnetic selector valve 68 into the tank 39 and reduces the pump discharge pressure of the second pump 33.
  • the aforementioned priority channel is provided in the pressure compensation flow dividing valve 38 in order to carry the hydraulic fluid fed from the second pump 33.
  • the decrease in the pump discharge pressure increases the flow rate of the fluid discharged from the second pump 33, with the flow rate shown in the P-Q curve diagram of Fig. 2 shifting from the point Pa to the point Pb.
  • each main control valve 41,42 is provided with a travelling spool, a difference will arise between the amount of hydraulic fluid in the right-side travelling spool and the left-side travelling spool, resulting in deviation of the vehicle from running straight.
  • bypass valve 75 to feed the oil flowing through the right-side travelling spool of the main control valve 42 to the left-side travelling spool of the main control valve 41 so as to achieve a balanced flow rate.
  • the actuators can function faster than those of the conventional art.
  • the invention when the attachment circuit pressure approaches the relief pressure during conjunctional operation of the attachment and the main body actuators, priority hydraulic fluid that has branched off from the pressure compensation flow dividing valve to the external channel flows through the selector valve into the tank and increases the pump discharge rate so that a greater amount of hydraulic fluid is fed to the main body actuators. Therefore, the invention is free from the problem of the action of the main body actuators becoming extremely slow the moment when the attachment circuit pressure approaches the relief pressure during conjunctional operation of the attachment and the main body actuators, and is consequently capable of increasing the working efficiency of the construction machine.
  • the pressure compensation flow dividing valve ensures that hydraulic fluid is constantly fed into the first main circuit and the second main circuit at the same flow rate. Therefore, as the flow rate of the hydraulic fluid fed from the left-side travelling control spool of the first main circuit to the left-side travelling motor is always the same as that of the hydraulic fluid fed from the right-side travelling control spool of the second main circuit to the right-side travelling motor, the invention is capable of preventing deviation of the construction machine from running straight.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
  • Servomotors (AREA)
EP20010302602 2000-09-11 2001-03-21 Hydraulikkreislauf für Baumaschinen Expired - Lifetime EP1193400B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000274757 2000-09-11
JP2000274757A JP3511504B2 (ja) 2000-09-11 2000-09-11 建設機械の油圧回路

Publications (3)

Publication Number Publication Date
EP1193400A2 true EP1193400A2 (de) 2002-04-03
EP1193400A3 EP1193400A3 (de) 2003-11-12
EP1193400B1 EP1193400B1 (de) 2005-02-02

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EP20010302602 Expired - Lifetime EP1193400B1 (de) 2000-09-11 2001-03-21 Hydraulikkreislauf für Baumaschinen

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EP (1) EP1193400B1 (de)
JP (1) JP3511504B2 (de)
DE (1) DE60108695T2 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102071717A (zh) * 2010-12-16 2011-05-25 重庆航天工业公司 挖掘机自适应控制方法

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3219857B1 (de) 2014-11-10 2023-06-28 Sumitomo (S.H.I.) Construction Machinery Co., Ltd. Arbeitsmaschine
JP6873726B2 (ja) * 2017-02-09 2021-05-19 ナブテスコ株式会社 油圧システム
WO2023162884A1 (ja) * 2022-02-24 2023-08-31 イーグル工業株式会社 流体圧回路

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61211505A (ja) * 1984-11-01 1986-09-19 Toshiba Mach Co Ltd 自走式油圧機械の油圧制御回路
JPH091087A (ja) * 1995-06-12 1997-01-07 Kobelco Kenki Eng Kk 作業車両の散水装置用回路
JPH10102546A (ja) * 1996-09-30 1998-04-21 Yutani Heavy Ind Ltd 建設機械の油圧回路
JP2000073409A (ja) * 1998-08-28 2000-03-07 Shin Caterpillar Mitsubishi Ltd 建設機械の油圧回路

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61211505A (ja) * 1984-11-01 1986-09-19 Toshiba Mach Co Ltd 自走式油圧機械の油圧制御回路
JPH091087A (ja) * 1995-06-12 1997-01-07 Kobelco Kenki Eng Kk 作業車両の散水装置用回路
JPH10102546A (ja) * 1996-09-30 1998-04-21 Yutani Heavy Ind Ltd 建設機械の油圧回路
JP2000073409A (ja) * 1998-08-28 2000-03-07 Shin Caterpillar Mitsubishi Ltd 建設機械の油圧回路

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Title
PATENT ABSTRACTS OF JAPAN vol. 011, no. 048 (M-561), 13 February 1987 (1987-02-13) & JP 61 211505 A (TOSHIBA MACH CO LTD), 19 September 1986 (1986-09-19) *
PATENT ABSTRACTS OF JAPAN vol. 1997, no. 05, 30 May 1997 (1997-05-30) & JP 09 001087 A (KOBELCO KENKI ENG KK), 7 January 1997 (1997-01-07) *
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 09, 31 July 1998 (1998-07-31) & JP 10 102546 A (YUTANI HEAVY IND LTD;KOBE STEEL LTD), 21 April 1998 (1998-04-21) *
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 06, 22 September 2000 (2000-09-22) & JP 2000 073409 A (SHIN CATERPILLAR MITSUBISHI LTD), 7 March 2000 (2000-03-07) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102071717A (zh) * 2010-12-16 2011-05-25 重庆航天工业公司 挖掘机自适应控制方法

Also Published As

Publication number Publication date
JP2002089511A (ja) 2002-03-27
JP3511504B2 (ja) 2004-03-29
DE60108695D1 (de) 2005-03-10
EP1193400B1 (de) 2005-02-02
DE60108695T2 (de) 2006-05-04
EP1193400A3 (de) 2003-11-12

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