WO2004005727A1 - 油圧駆動装置 - Google Patents
油圧駆動装置 Download PDFInfo
- Publication number
- WO2004005727A1 WO2004005727A1 PCT/JP2003/008702 JP0308702W WO2004005727A1 WO 2004005727 A1 WO2004005727 A1 WO 2004005727A1 JP 0308702 W JP0308702 W JP 0308702W WO 2004005727 A1 WO2004005727 A1 WO 2004005727A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- cylinder
- pressure
- hydraulic
- side chamber
- boom
- Prior art date
Links
Classifications
-
- 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
- F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
-
- 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
- E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2285—Pilot-operated systems
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2296—Systems with a variable displacement pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
-
- 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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/14—Energy-recuperation 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
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20523—Internal combustion engine
-
- 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
-
- 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
- F15B2211/30525—Directional control valves, e.g. 4/3-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
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
- F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
-
- 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
- F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
- F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
- F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single 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
- F15B2211/30—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
- F15B2211/405—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
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
- F15B2211/41545—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve being connected to multiple 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
- F15B2211/40—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
- F15B2211/60—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
- F15B2211/71—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
-
- 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
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/88—Control measures for saving energy
Definitions
- the present invention relates to a hydraulic drive device provided in a construction machine such as a hydraulic shovel and capable of performing a combined operation of a plurality of hydraulic cylinders.
- FIG. 4 is a hydraulic circuit diagram showing a main part of a hydraulic drive device disclosed in Japanese Patent Application Laid-Open No. 2000-333073
- FIG. 5 is a hydraulic circuit provided with the hydraulic drive device shown in FIG. It is a side view which shows a shovel.
- the hydraulic shovel shown in FIG. 5 includes a traveling body 1, a revolving body 2 provided on the traveling body 1, a boom 3 mounted on the revolving body 2 so as to be rotatable in a vertical direction.
- An arm 4 is mounted on the boom 3 so as to be rotatable in the vertical direction
- a bucket 5 is mounted on the arm 4 so as to be rotatable in the vertical direction.
- Boom 3, arm 4, and socket 5 constitute a front working machine.
- a boom cylinder 6 that is a first hydraulic cylinder that drives the arm 3
- an arm cylinder 7 that is a second hydraulic cylinder that drives the arm 4, for example,
- a bucket cylinder 8 for driving the bucket 5 is provided.
- FIG. 4 shows a hydraulic drive unit having a center bypass type directional control valve for driving a boom cylinder 6 and an arm cylinder 7 of the hydraulic drive units provided in the above-described hydraulic shovel. are doing.
- the boom cylinder 6 has a bottom side chamber 6a and a mouth.
- the boom cylinder 6 When the pressure oil is supplied to the bottom chamber 6a, the boom cylinder 6 is extended and the boom is raised. By supplying the pressurized oil to b, the boom cylinder 6 contracts and the boom is lowered.
- the arm cylinder 7 also includes a bottom chamber 7a and a rod chamber 7b, and the arm cloud is implemented by supplying pressure oil to the bottom chamber 7a.
- the arm dump is performed by supplying the pressurized oil to the load side chamber 7b.
- the hydraulic drive device including the boom cylinder 6 and the arm cylinder 7 includes an engine 20 and a main hydraulic pump driven by the engine 20.
- the directional control valve 24 for the arm which is the second directional control valve for controlling the flow of the pressure oil supplied from the pump 21 to the arm cylinder 7, and the directional control valve 23 for the boom are remotely switched and controlled.
- a directional control valve for boom 23 is provided in a pipe 28 connected to the discharge pipe of the main hydraulic pump 21, and a directional control valve for arm is provided in the pipe 27 connected to the discharge pipe described above. 24 are provided.
- the boom directional control valve 23 and the bottom chamber 6a of the boom cylinder 6 are connected by a main line 29a, and the boom directional control valve 23 and the boom cylinder 6 are locked.
- the main chamber 29b is connected to the side chamber 6b by a main pipeline 29b.
- the arm directional control valve 24 and the bottom side chamber 7a of the arm cylinder 7 are connected by a main line 30a, and the arm directional control valve 24 and the arm directional control valve 24 are connected to each other.
- the rod side chamber 7b of the cylinder 7 is connected by a main pipeline 30b.
- the boom operating device 25 is connected to the pilot pump 22 and controls the pilot pressure generated in response to the operation through one of the pilot lines 25a and 25b.
- the boom direction control valve 23 is switched to the left position or the right position in FIG.
- the arm operating device 26 is also connected to the pilot pump 22 so that the pilot pressure generated in response to the operation is supplied to the pilot lines 26a and 26b.
- the air is supplied to the control room of the directional control valve 24 for the arm via one of them, and the directional control valve 24 for the arm is switched to the left position or the right position in FIG.
- the operation device 25 for a boom shown in FIG. 4 when excavating earth and sand, the operation device 25 for a boom shown in FIG. 4 is operated, and for example, a pilot pipeline is operated. Pilot pressure is generated at 25a, and the directional control valve 23 for boom is switched to the left position in FIG.
- the hydraulic oil discharged from the main hydraulic pump 21 passes through the line 28, the boom directional control valve 23, and the bottom of the boom cylinder 6 via the main line 29a.
- the pressure oil in the load side chamber 6b is supplied to the side chamber 6a, and is returned to the tank 43 via the main line 29b and the boom directional control valve 23.
- the boom cylinder 6 extends as shown by the arrow 13 in FIG. 5, the boom 3 rotates as shown by the arrow 12 in FIG. 5, and the boom is raised. .
- the arm operating device 26 is operated, for example, a pilot pressure is generated in the pilot pipe 26a, and the arm direction is changed.
- the control valve 24 is switched to the left position in FIG. 4, the hydraulic oil discharged from the main hydraulic pump 21 passes through the pipe 27, the arm directional control valve 24, and the main pipe 30a. Then, it is supplied to the bottom chamber 7 a of the arm cylinder 7.
- the pressure oil in the rod side chamber 7b is returned to the tank 43 via the main line 30b and the arm directional control valve 24.
- the arm cylinder 7 extends as shown by the arrow 9 in FIG. 5, and the arm 4 rotates as shown by the arrow 11 in FIG. Is done.
- a bucket operating device (not shown) was operated to switch the bucket directional control valve, as shown in FIG.
- the bucket cylinder 8 When the bucket cylinder 8 is extended in the direction of arrow 10 in FIG. 5, the bucket 5 rotates in the direction of arrow 11 and the desired earth and sand is formed. Excavation work is performed.
- FIG. 6 is a characteristic diagram showing pilot pressure characteristics and cylinder pressure characteristics in the above-described combined operation.
- the horizontal axis represents the excavation time
- the vertical axis represents the pilot pressure generated by the operating device.
- 31 in the lower diagram of FIG. 6 is generated by the arm operating device 26 shown in FIG. 4 and is supplied to the pilot line 26a, i.e., the pilot pressure.
- the pilot pressure at the time of the arm cloud is shown.
- reference numeral 32 denotes a pilot pipe generated by the boom operating device 25 shown in FIG.
- the pilot pressure supplied to the road 25a that is, the pilot pressure when the boom is raised, is shown.
- T1, T2, and T3 indicate the points in time when the boom raising operation was performed.
- the horizontal axis shows the excavation work time
- the vertical axis shows the load pressure generated in the hydraulic cylinders 6, 7, that is, the cylinder pressure
- Numeral 33 in the upper diagram of FIG. 6 indicates the bottom pressure generated in the bottom chamber 7 a of the arm cylinder 7, that is, the arm cylinder pot pressure. It shows the rod pressure generated in the rod side chamber 6b of the boom cylinder 6, that is, the boom cylinder rod pressure.
- the rod side chamber 6b of the boom cylinder 6, which is the first hydraulic cylinder, is connected to the tank 43.
- a hydraulic circuit has been proposed in which a pipe is provided and an over-open single-relief valve 80 is provided on the pipe to release pressurized oil to the tank 43 when the pressure exceeds a predetermined level. Have been.
- the overload relief valve 80 continues to be relieved occurs, the amount of heat generated in the hydraulic circuit becomes large and energy efficiency is increased. It is extremely disadvantageous.
- the present invention has been made in view of the above-described situation in the related art, and has a purpose of providing the first hydraulic system with an operation of supplying hydraulic oil to the pot side chamber of the second hydraulic cylinder.
- An object of the present invention is to provide an oil pressure drive device capable of relieving excessive pressure in a rod side chamber of a cylinder and effectively utilizing pressure oil in the rod side chamber. Disclosure of the invention
- the present invention is provided in a construction machine, and is driven by a main hydraulic pump and pressure oil discharged from the main hydraulic pump.
- a first hydraulic cylinder and a second hydraulic cylinder each having a drum side chamber, and a first directional control valve for controlling the flow of pressure oil supplied from the main hydraulic pump to the first hydraulic cylinder.
- the raw hydraulic port A second directional control valve for controlling the flow of pressure oil supplied from the pump to the second hydraulic cylinder, a first operating device for switching and controlling the first directional control valve, and the second directional control valve A second operating device for switching control of the first hydraulic cylinder, when the pressure in the rod side chamber of the first hydraulic cylinder becomes higher than a predetermined pressure,
- a communication control means for communicating the rod side chamber of the first hydraulic cylinder with the bottom side chamber of the second hydraulic cylinder is provided.
- the second directional control valve is switched by operating the second operating device, and the hydraulic oil of the main hydraulic pump is supplied to the second hydraulic system via the second directional control valve.
- the reaction force of the drive of the second hydraulic cylinder causes the reaction of the first hydraulic cylinder to occur.
- the communication control means is activated, and the pressure oil in the rod side chamber of the first hydraulic cylinder is supplied to the second hydraulic cylinder. It is supplied to the bottom chamber.
- the hydraulic fluid discharged from the main hydraulic pump and supplied through the second directional control valve and the lock of the first hydraulic cylinder are provided in the bottom chamber of the second hydraulic cylinder.
- the pressure oil supplied from the pressure side chamber merges and is supplied.
- the pressure in the rod-side chamber of the first hydraulic cylinder is suppressed to substantially the same pressure as the pressure in the bottom-side chamber of the second hydraulic cylinder, and the pressure of the second hydraulic cylinder is also reduced.
- Speed up in the extension direction can be performed. In this way, it is possible to suppress an excessive increase in the pressure of the opening side chamber of the first hydraulic cylinder.
- the pressure oil in the rod side chamber of the first hydraulic cylinder which was conventionally thrown away by relieving the tank, is selectively increased by the second hydraulic cylinder. It can be used quickly and effectively.
- the communication control means may include a communication path capable of communicating a rod-side chamber of the first hydraulic cylinder with a bottom-side chamber of the second hydraulic cylinder.
- a backflow provided in the communication passage for preventing the flow of pressure oil from the pot side chamber of the second hydraulic cylinder to the rod side chamber of the first hydraulic cylinder.
- Preventing means and the communication passage when the pressure in the port side chamber of the first hydraulic cylinder is lower than the predetermined pressure.
- a switching valve for keeping the communication path in communication when the pressure becomes equal to or higher than the predetermined pressure.
- the pressure oil of the main hydraulic pump is supplied to the bottom chamber of the second hydraulic cylinder, and the independent operation of the second hydraulic cylinder is performed.
- the switching valve is connected.
- the passage is switched so as to maintain the communication state, whereby the pressure oil in the rod-side chamber of the first hydraulic cylinder passes through the communication passage and the backflow prevention means, and the pressure of the second hydraulic cylinder is reduced. It is supplied to the tom side chamber.
- the switching valve includes a variable throttle in which a throttle amount changes according to a pressure of a rod-side chamber of the first hydraulic cylinder.
- the amount of pressure oil supplied from the rod-side chamber of the first hydraulic cylinder to the bottom-side chamber of the second hydraulic cylinder is reduced by the amount of pressure oil in the mouth-side chamber of the first hydraulic cylinder. It is limited according to the pressure, and it is possible to reduce the shock particularly when the switching valve switches from the shut-off state to the communicating state.
- the throttle amount is set on a communication path connecting the bottom side chamber of the second hydraulic cylinder and the backflow prevention means in accordance with the operation amount of the second operation device. It has a configuration with variable variable aperture means.
- the switching valve is configured such that the pressure in the load side chamber of the first hydraulic cylinder becomes high due to the reaction force accompanying the driving of the second hydraulic cylinder, and the switching valve communicates. Even in the state, the throttle amount of the variable throttle valve is determined according to the operation amount of the second operating device, so the supply is supplied from the first hydraulic cylinder side to the second hydraulic cylinder side. The amount of pressurized oil used is limited. Therefore, the operator Unintended extreme increase in the speed of the second hydraulic cylinder can be suppressed.
- a solenoid valve for generating a pilot oil pressure signal for controlling a valve position of the switching valve, and a pressure in a rod side chamber of the first hydraulic cylinder are detected.
- a pressure detection means for detecting an operation amount of the second operating device; a pressure signal from the pressure detection means and an operation signal from the operation amount detection means;
- a controller that executes processing and outputs a drive signal to the solenoid valve is provided.
- the construction machine has a revolving body, a boom rotatably mounted on the revolving body, and an arm rotatably mounted on the boom.
- a hydraulic shovel wherein the first hydraulic cylinder is a boom cylinder for driving the boom, and the second hydraulic cylinder is an arm cylinder for driving the arm.
- the first hydraulic cylinder is a boom cylinder for driving the boom
- the second hydraulic cylinder is an arm cylinder for driving the arm.
- the excavation reaction force causes the boom cylinder to operate.
- the communication control means is activated, and the hydraulic oil in the rod side chamber of the boom cylinder is discharged from the arm cylinder. It is supplied to the pot room.
- the oil in the cylinder side chamber of the arm cylinder is discharged from the main hydraulic pump and supplied through the directional control valve for the arm, and the boom cylinder port
- the pressure oil supplied from the side chamber is combined and supplied. This makes it possible to increase the speed of the arm cylinder in the extension direction, that is, to increase the speed of the arm cloud.
- the construction machine includes a revolving body, a boom rotatably mounted on the revolving body, an arm rotatably mounted on the boom, A hydraulic shovel having a bucket rotatably mounted on the arm, wherein the first hydraulic cylinder is a boom cylinder for driving the boom; (2)
- the hydraulic cylinder is a bucket cylinder for driving the above-mentioned bucket, and the pressure in the rod-side chamber of the boom cylinder becomes higher than a predetermined pressure, the above-mentioned It is characterized in that it has a communication control means for communicating the rod side chamber of the bump cylinder with the pot side chamber of the bucket cylinder.
- the excavation reaction force is applied to the bucket cylinder.
- the communication control means is activated, and the pressure oil in the mouth side chamber of the boom cylinder is bucketed. It is supplied to the cylinder side room. That is, the boom cylinder discharges from the main hydraulic pump into the bottom chamber of the bucket cylinder, and is supplied through a directional control valve for the bucket. And the pressurized oil supplied from the nozzle side chamber. This makes it possible to increase the speed of the bucket cylinder in the direction of extension. Further, it is possible to suppress the pressure in the rod side chamber of the boom cylinder from excessively increasing.
- FIG. 1 is a hydraulic circuit diagram showing a first embodiment of the hydraulic drive device of the present invention
- FIG. 2 is a hydraulic circuit diagram showing a second embodiment of the present invention.
- FIG. 3 is a block diagram showing the processing performed by the controller provided in the second embodiment.
- FIG. 4 is a hydraulic circuit diagram showing a conventional hydraulic drive device.
- FIG. 5 is a side view showing a hydraulic shovel as an example of a construction machine provided with the hydraulic drive device shown in FIG.
- FIG. 6 is a characteristic diagram showing a pi-port pressure characteristic and a cylinder pressure characteristic in a conventional hydraulic drive device.
- FIG. 7 is a diagram for explaining a problem in the related art.
- FIG. 8 is a hydraulic circuit diagram showing another conventional hydraulic drive device. BEST MODE FOR CARRYING OUT THE INVENTION
- FIG. 1 is a circuit diagram showing a first embodiment of the hydraulic drive device of the present invention.
- the same components as those shown in FIGS. 4 and 8 described above are denoted by the same reference numerals.
- the first embodiment shown in FIG. 1 and a second embodiment described later are also provided in a construction machine, for example, the hydraulic shovel shown in FIG. 5 described above. Accordingly, the following description will be made using the reference numerals shown in FIG. 5 as necessary.
- the first embodiment shown in FIG. 1 also has, for example, a center bypass type directional control for driving a first cylinder Boom cylinder 6 and a second cylinder C arm arm cylinder 7. It is composed of hydraulic actuators each equipped with a valve. 4, the boom cylinder 6 also has a bottom side chamber 6a and a rod side chamber 6b, and the first embodiment shown in FIG. 7 also has a bottom chamber 7a and a rod chamber 7b.
- the engine 20 is supplied to the main hydraulic pump 21 and the pilot pump 22 driven by the engine 20, and to the boom cylinder 6.
- a first directional control valve for controlling the flow of pressurized oil i.e., a center-bypass type boom directional control valve 23, a second directional control valve for controlling the flow of pressurized oil supplied to the arm cylinder 7 That is, a center bypass type directional control valve 24 for the arm is provided.
- a first operating device for remotely switching and controlling the boom directional control valve 23, that is, the boom operating device 25 and the arm directional control valve 24 are remotely switched and controlled.
- Lines 27, 28 are connected to the discharge line of the main hydraulic pump 21, and an arm directional control valve 24 is provided in the line 27, and an arm directional control valve 24 is provided in the line 28.
- a directional control valve for boom 23 is provided.
- the boom directional control valve 23 and the bottom side chamber 6a of the boom cylinder 6 are connected by a main line 29a, and the boom directional control valve 23 and the boom cylinder 6 are locked. It is connected to the main room 6b by a main pipeline 29b.
- the arm directional control valve 24 and the bottom side chamber 7a of the arm cylinder 7 are connected by a main line 30a, and the arm directional control valve 24 and the arm cylinder
- the load side chamber 7b of the cylinder 7 is connected with the main pipeline 30b.
- the operating device 25 for the boom and the operating device 26 for the arm are, for example, composed of a pilot-type operating device for generating a pilot pressure, and are connected to the pilot pump 22. You.
- the operation device 25 for the boom is connected to the control room of the directional control valve 23 for the boom via the pilot pipes 25a and 25b, respectively, and the operation device 26 for the arm is connected to the pilot device. They are connected to the control room of the directional control valve 24 for the arm via the lot pipes 26a and 26b, respectively.
- the boom cylinder 6 constituting the first hydraulic cylinder is formed.
- the arm cylinder 7 constituting the second hydraulic cylinder and the rod-side chamber 6b of the boom cylinder 6 A communication control means is provided for communicating with the bottom side chamber 7a.
- the communication control means can communicate between the rod side chamber 6b of the boom cylinder 6 and the bottom side chamber 7a of the damper cylinder 7.
- the communication passage 40 is shut off.
- a switching valve 57 for maintaining the communication path 40 in a communicating state when the pressure becomes higher than a predetermined pressure.
- Arm Cylinder 7 Backflow prevention means for preventing the flow of hydraulic oil from the bottom chamber 7a in the direction of the rod chamber 6b of the boom cylinder 6 such as a check valve 41 and an arm operating device Including variable throttle means, such as a variable throttle valve 54, whose opening area is controlled according to the amount of operation when an arm cloud operation is performed by 26 In.
- the switching valve 57 is a pilot switching valve that can be switched by the pressure of the opening side chamber 6 b of the boom cylinder 6, and the variable throttle valve 54 has an articulated valve.
- the pilot pressure from the pilot line 26 of the operating device 26 for the engine is applied via the control line 55.
- a pipe 56 connecting the rod-side chamber 6b of the boom cylinder 6 and the tank 43 is provided with a single-bar-drill.
- a safety valve 80 is provided.
- the set pressure by the spring 57a for switching the switching valve 57 from the shut-off position to the communication position is lower than the set pressure of the overload relief valve 80. Is set.
- the arm operating device 26 When the arm operating device 26 is operated to supply the pilot port pressure to the pilot pipe line 26a and the arm directional control valve 24 is switched to the left position, the main hydraulic pressure port is switched.
- the pressure oil discharged from the pump 21 is supplied to the bottom side chamber 7a of the arm cylinder 7 via the line 27, the directional control valve 24 for the arm, and the main line 30a. Is done.
- the arm cylinder 7 operates in the extending direction
- the arm 4 shown in FIG. 5 rotates in the direction of the arrow 11, and the arm cladding operation is performed.
- the pilot port pressure is not supplied to the pilot pipelines 25a and 25b of the boom operation system, and the tank pressure is attained.
- the boom directional control valve 23 is in the neutral position. Hold.
- a variable throttle valve 54 provided on the communication passage 40 receives a pilot pressure Pa from the pilot pipe 26 a via the control pipe 55. It is provided with an opening corresponding to the area of the pilot pressure Pa.
- the pressure in the rod side chamber 6b of the boom cylinder 6 is lower than the predetermined pressure, that is, the pressure set by the above-described spring 57a.
- the force by the control pressure applied to the control chamber of the switching valve 57 is smaller than the spring force of the spring 57a, and the switching valve 57 is held at the left position shown in FIG. .
- the load side chamber 6b of the bloom cylinder 6 is in a completely locked state, and during the extension operation of the arm cylinder 7, the bloom cylinder 6 is in a completely locked state.
- the pressure oil in the load side chamber 6 b of 6 is not supplied to the communication passage 40.
- the pressure oil supplied to the communication passage 40 is supplied to the bottom side chamber 7a of the arm cylinder 7 via the main pipeline 30a. That is, the hydraulic oil discharged from the main hydraulic pump 21 and supplied through the arm directional control valve 24 is supplied to the bottom chamber 7 a of the arm cylinder 7.
- the pressurized oil supplied from the rod side chamber 6b of the boom cylinder 6 is combined and supplied.
- the bottom side chamber 6a of the boom cylinder 6 is supplied with oil from the tank 43 via the check valve and the main line 29a. A negative pressure in the drum side chamber 6a is prevented.
- the boom The pressure oil in the rod-side chamber 6b of the cylinder 6 can be sent to the bottom-side chamber 7a of the arm cylinder 7, so that the bump cylinder 6 extends and the arm clamp is extended. Excavation reaction force due to the wood operation can be released, and the lifting of the vehicle body can be prevented.
- the pressure oil that has flowed out of the rod side chamber 6 b of the boom cylinder 6 is supplied to the bottom side chamber 7 a of the arm cylinder 7, so that the arm cylinder 6 extends.
- Speed increase thus, the operation speed of the arm cloud can be increased.
- the boom directional control valve 23 shifts from the valve position shown in FIG. 1 to the left valve position, and the boom cylinder is operated.
- the rod side chamber 6b of No. 6 communicates with the tank 43, and the pressure oil in the rod side chamber 6b is returned to the tank 43. If, for some reason, the pressure in the load side chamber 6b of the boom cylinder 6 becomes higher than the predetermined pressure and the switching valve 57 becomes in communication, the boom Since the pressure oil in the rod-side chamber 6b of the cylinder 6 is supplied to the bottom-side chamber 7a of the arm cylinder 7, the speed of the arm cylinder 6 in the extension direction is increased.
- the bottom side chamber 6a of the boom cylinder 6 is connected to the tank 4 via the boom directional control valve 23. Communicate with 3. At this time, if the pressure in the load side chamber 6b of the boom cylinder 6 becomes higher than the predetermined pressure, and the switching valve 57 becomes in communication, the boom 3 becomes higher than before. However, the excavation force of Arm 4 is increased by that amount, and as a result, the excavation force is about the same as the conventional technology.
- variable throttle valve 54 when a combined operation of the arm dump operation and the program 3 or the arm dump operation alone is performed, the pilot pressure P a is applied to the variable throttle valve 54. Since no pressure is applied, the variable throttle valve 54 remains closed, and the operation is the same as that of the prior art.
- the pressure in the rod-side chamber 6b of the boom cylinder 6 is lower than the predetermined pressure due to the excavation reaction force when the arm clad is operated alone.
- the pressure oil in the rod-side chamber 6b of the boom cylinder 6 can be sent to the pot-side chamber 7a of the arm cylinder 7 and the boom cylinder 6 This allows the excavation reaction force generated by the arm cloud operation to escape, thereby preventing the body from rising.
- the pressure oil flowing out of the rod side chamber 6 b of the boom cylinder 6 is supplied to the pot side chamber 7 a of the arm cylinder 7, the extending direction of the arm cylinder 6 is increased.
- Arm cloud operating speed The speed can be increased.
- the pressurized oil in the rod side chamber 6b of the boom cylinder 6, which has conventionally been discarded in the tank, can be effectively used.
- the throttle amount of the variable throttle valve 54 is controlled in accordance with the arm dump operation amount by the arm operating device 26, the extreme operation of the arm cylinder 7 that may not be expected by the operator is performed. It is possible to reduce the speed increase.
- FIG. 2 is a hydraulic circuit diagram showing the second embodiment
- FIG. 3 is a block diagram showing the processing contents of a controller 68 provided in the second embodiment.
- the switching valve 57 b for holding the communication passage 40 in the communicating state includes a variable throttle, and the variable throttle valve 54 provided in the first embodiment is omitted.
- the switching valve 57 b is controlled in its position by a control pressure from a solenoid valve 69 to which a pilot pressure is supplied via a control line 69 a, and the switching valve 57 b is opened.
- the area (amount of squeezing) is controlled.
- operation amount detection means for detecting the pressure of the pilot pipe 26a for example, a pyrometer
- a pressure detector 67 and a pressure detector for detecting the pressure in the rod side chamber 6 b of the boom cylinder 6, for example, a rod pressure detector 66 are provided.
- signals from the pilot pressure detector 67 and the rod pressure detector 66 are input, predetermined arithmetic processing is performed, and the drive current to the solenoid valve 69 is output.
- a controller 68 is provided.
- Other configurations are the same as those in the first embodiment.
- the operation amount on the arm cloud side by the arm operating device 26 detected by the pilot pressure detector 67, and The pressure in the load side chamber 6b of the boom cylinder 6 detected by the load pressure detector 66 is input to the controller 68, and the controller At 68, the arithmetic processing shown in FIG. 3 is executed. As shown in FIG. 3, the controller 68 responds to this signal when the pressure in the load side chamber 6b of the boom cylinder 6 becomes higher than a predetermined pressure. It has a function generator 68 a that outputs a large value.
- a function generator 68 b that outputs a large value up to 1 and a function generator 68 a, And a multiplier 68 c for multiplying the signal output from 68 b.
- the result of multiplication by the multiplier 68 c is output as a drive signal (current) for the solenoid valve 69.
- the signal increases.
- the hydraulic control force applied from the solenoid valve 69 to the switching valve 57 b increases, and the opening area of the switching valve 57 b also increases.
- the amount of pressure oil supplied from the rod side chamber 6b to the bottom side chamber 7a of the arm cylinder 7 also increases.
- the rod side chamber 6b of the boom cylinder 6 is caused by the excavation reaction force.
- the pressure oil in the rod side chamber 6 b of the boom cylinder 6 can be sent to the bottom side chamber 7 a of the arm cylinder 7. Therefore, the boom cylinder 6 is extended, so that the excavation reaction force caused by the arm cloud operation can be released, and the floating of the vehicle body can be prevented from being lifted. Also, since the pressure oil flowing out of the rod side chamber 6 b of the boom cylinder 6 is supplied to the bottom side chamber 7 a of the arm cylinder 7, the extension direction of the arm cylinder 6 is increased.
- the arm cylinder 7 is described as an example of the second hydraulic cylinder, but the bucket shown in FIG. 5 described above as the second hydraulic cylinder is used as the second hydraulic cylinder. It may be Tosylinder 8. In this case, pressure oil from the rod side chamber 6b of the pump cylinder 6 is supplied to the bottom side chamber of the bucket cylinder 8, and the excavation speed by the bucket 8 is reduced. Only the point that the speed can be increased is different from the case of the arm 4, and the other effects can be obtained similarly to the first and second embodiments.
- the present invention is applied to a hydraulic drive device having a center bypass type directional control valve, but the present invention is not limited to this, and the closed center type directional control valve is not limited to this. It may be configured to be applied to a hydraulic drive device provided with
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE60315997T DE60315997T2 (de) | 2002-07-09 | 2003-07-09 | Hydraulische antriebseinheit |
EP03762902A EP1541872B1 (en) | 2002-07-09 | 2003-07-09 | Hydraulic drive unit |
JP2004519301A JP4384977B2 (ja) | 2002-07-09 | 2003-07-09 | 油圧駆動装置 |
US10/520,144 US7127888B2 (en) | 2002-07-09 | 2003-07-09 | Hydraulic drive unit |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002-200014 | 2002-07-09 | ||
JP2002200014 | 2002-07-09 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004005727A1 true WO2004005727A1 (ja) | 2004-01-15 |
Family
ID=30112497
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2003/008702 WO2004005727A1 (ja) | 2002-07-09 | 2003-07-09 | 油圧駆動装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US7127888B2 (ja) |
EP (1) | EP1541872B1 (ja) |
JP (1) | JP4384977B2 (ja) |
DE (1) | DE60315997T2 (ja) |
WO (1) | WO2004005727A1 (ja) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2007046741A (ja) * | 2005-08-11 | 2007-02-22 | Hitachi Constr Mach Co Ltd | 作業機械の油圧駆動装置 |
WO2012114654A1 (ja) | 2011-02-24 | 2012-08-30 | コベルコ建機株式会社 | 作業アタッチメントを備えた建設機械 |
WO2013175699A1 (ja) | 2012-05-24 | 2013-11-28 | コベルコ建機株式会社 | 建設機械のブーム駆動装置 |
JP2014163072A (ja) * | 2013-02-22 | 2014-09-08 | Hitachi Constr Mach Co Ltd | 油圧ショベルの油圧駆動装置 |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3816893B2 (ja) * | 2003-04-17 | 2006-08-30 | 日立建機株式会社 | 油圧駆動装置 |
JP4410512B2 (ja) * | 2003-08-08 | 2010-02-03 | 日立建機株式会社 | 油圧駆動装置 |
DE10354957A1 (de) * | 2003-11-25 | 2005-06-30 | Bosch Rexroth Ag | Hydraulische Steueranordnung für ein mobiles Arbeitsgerät |
US7827787B2 (en) | 2007-12-27 | 2010-11-09 | Deere & Company | Hydraulic system |
DE102011000239A1 (de) * | 2011-01-20 | 2012-07-26 | Palfinger Platforms GmbH | Hydrauliksystem mit zumindest einer Antriebsmaschine |
US20130168073A1 (en) * | 2011-12-30 | 2013-07-04 | Cnh America Llc | Work vehicle fluid heating system |
JP6231917B2 (ja) * | 2014-03-24 | 2017-11-15 | 川崎重工業株式会社 | 油圧ショベル駆動システム |
CN105544645B (zh) * | 2016-02-24 | 2017-11-14 | 徐州徐工特种工程机械有限公司 | 一种具有安全保护功能的滑移装载机及其工作液压系统 |
CN106223392B (zh) * | 2016-08-31 | 2018-07-24 | 徐州徐工挖掘机械有限公司 | 一种挖掘机回转能量回收系统 |
CN110805094B (zh) * | 2018-08-06 | 2022-03-01 | 柳州柳工挖掘机有限公司 | 挖掘机工作装置液压系统及挖掘控制方法 |
EP3862491B1 (en) * | 2018-10-03 | 2024-04-10 | Sumitomo Heavy Industries, Ltd. | Excavator |
CN114008276B (zh) * | 2019-08-08 | 2023-09-08 | 住友重机械工业株式会社 | 挖土机 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60179504A (ja) * | 1984-02-28 | 1985-09-13 | Mitsubishi Heavy Ind Ltd | エネルギ再生回路 |
JPS60208610A (ja) * | 1984-03-30 | 1985-10-21 | Toshiba Mach Co Ltd | 油圧シリンダの動力回生油圧回路 |
DE10109510A1 (de) * | 2000-07-14 | 2002-01-31 | Komatsu Mfg Co Ltd | Vorrichtung zur Aktuatorensteuerung von Hydraulik-Antriebsmaschinen |
US20030106423A1 (en) * | 2001-10-12 | 2003-06-12 | Shin Caterpillar Mitsubishi Ltd. | Independent and regenerative mode fluid control system |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1010951B (de) | 1956-02-20 | 1957-06-27 | Otto Stockem | Verfahren zur Herstellung pastoeser Kohlenanzuendungsmassen |
JPS55119838A (en) * | 1979-03-09 | 1980-09-13 | Sanyo Kiki Kk | Hydraulic control circuit in loader |
JP2652801B2 (ja) * | 1988-11-30 | 1997-09-10 | カヤバ工業株式会社 | ショベルローダ制御装置 |
DK167322B1 (da) * | 1991-10-28 | 1993-10-11 | Danfoss As | Hydraulisk kredsloeb |
JP3542373B2 (ja) * | 1994-03-15 | 2004-07-14 | 三陽機器株式会社 | 荷役機械の作業用油圧回路 |
US5797310A (en) * | 1997-01-29 | 1998-08-25 | Eaton Corporation | Dual self level valve |
US6389953B1 (en) * | 1998-09-24 | 2002-05-21 | Delta Power Company | Hydraulic leveling control system for a loader type vehicle |
US6502393B1 (en) | 2000-09-08 | 2003-01-07 | Husco International, Inc. | Hydraulic system with cross function regeneration |
JP4562948B2 (ja) * | 2001-05-17 | 2010-10-13 | 日立建機株式会社 | 油圧駆動装置 |
-
2003
- 2003-07-09 WO PCT/JP2003/008702 patent/WO2004005727A1/ja active IP Right Grant
- 2003-07-09 JP JP2004519301A patent/JP4384977B2/ja not_active Expired - Fee Related
- 2003-07-09 US US10/520,144 patent/US7127888B2/en not_active Expired - Lifetime
- 2003-07-09 DE DE60315997T patent/DE60315997T2/de not_active Expired - Lifetime
- 2003-07-09 EP EP03762902A patent/EP1541872B1/en not_active Expired - Lifetime
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60179504A (ja) * | 1984-02-28 | 1985-09-13 | Mitsubishi Heavy Ind Ltd | エネルギ再生回路 |
JPS60208610A (ja) * | 1984-03-30 | 1985-10-21 | Toshiba Mach Co Ltd | 油圧シリンダの動力回生油圧回路 |
DE10109510A1 (de) * | 2000-07-14 | 2002-01-31 | Komatsu Mfg Co Ltd | Vorrichtung zur Aktuatorensteuerung von Hydraulik-Antriebsmaschinen |
US20030106423A1 (en) * | 2001-10-12 | 2003-06-12 | Shin Caterpillar Mitsubishi Ltd. | Independent and regenerative mode fluid control system |
Non-Patent Citations (1)
Title |
---|
See also references of EP1541872A4 * |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2007046741A (ja) * | 2005-08-11 | 2007-02-22 | Hitachi Constr Mach Co Ltd | 作業機械の油圧駆動装置 |
WO2012114654A1 (ja) | 2011-02-24 | 2012-08-30 | コベルコ建機株式会社 | 作業アタッチメントを備えた建設機械 |
JP2012172491A (ja) * | 2011-02-24 | 2012-09-10 | Kobelco Contstruction Machinery Ltd | 建設機械の油圧制御装置 |
US9394666B2 (en) | 2011-02-24 | 2016-07-19 | Kobelco Construction Machinery Co., Ltd. | Construction machine with working attachment |
WO2013175699A1 (ja) | 2012-05-24 | 2013-11-28 | コベルコ建機株式会社 | 建設機械のブーム駆動装置 |
JP2013245727A (ja) * | 2012-05-24 | 2013-12-09 | Kobelco Contstruction Machinery Ltd | 建設機械のブーム駆動装置 |
CN104302930A (zh) * | 2012-05-24 | 2015-01-21 | 神钢建机株式会社 | 工程机械的动臂驱动装置 |
KR20150022883A (ko) | 2012-05-24 | 2015-03-04 | 코벨코 겐키 가부시키가이샤 | 건설 기계의 붐 구동 장치 |
CN104302930B (zh) * | 2012-05-24 | 2016-03-02 | 神钢建机株式会社 | 工程机械的动臂驱动装置 |
US9587656B2 (en) | 2012-05-24 | 2017-03-07 | Kobelco Construction Machinery Co., Ltd. | Boom driving apparatus for construction machine |
JP2014163072A (ja) * | 2013-02-22 | 2014-09-08 | Hitachi Constr Mach Co Ltd | 油圧ショベルの油圧駆動装置 |
Also Published As
Publication number | Publication date |
---|---|
DE60315997D1 (de) | 2007-10-11 |
JPWO2004005727A1 (ja) | 2005-11-04 |
EP1541872B1 (en) | 2007-08-29 |
EP1541872A1 (en) | 2005-06-15 |
DE60315997T2 (de) | 2008-05-15 |
JP4384977B2 (ja) | 2009-12-16 |
US7127888B2 (en) | 2006-10-31 |
US20050144938A1 (en) | 2005-07-07 |
EP1541872A4 (en) | 2005-10-05 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5764968B2 (ja) | 建設機械の油圧制御装置 | |
JP5388787B2 (ja) | 作業機械の油圧システム | |
KR101932304B1 (ko) | 작업 기계의 유압 구동 장치 | |
WO2004005727A1 (ja) | 油圧駆動装置 | |
JP6453898B2 (ja) | 作業機械の油圧駆動システム | |
JP3816893B2 (ja) | 油圧駆動装置 | |
JP4410512B2 (ja) | 油圧駆動装置 | |
JP2010078035A (ja) | 作業機械の油圧シリンダ制御回路 | |
WO2002063108A1 (fr) | Machine de chantier: circuit de commande hydraulique pour verin de fleche | |
JP5938356B2 (ja) | 油圧ショベルの油圧駆動装置 | |
JP2004301214A (ja) | 作業用車両の油圧駆動装置 | |
JP4562948B2 (ja) | 油圧駆動装置 | |
JP2004301215A (ja) | 作業用車両の油圧駆動装置 | |
JP3594680B2 (ja) | 油圧機械の油圧再生装置 | |
JP6591370B2 (ja) | 建設機械の油圧制御装置 | |
KR101186568B1 (ko) | 작업모드 설정기능이 구비된 유압시스템 | |
JP7171475B2 (ja) | 作業機械 | |
JP7207060B2 (ja) | 作業機械の油圧駆動装置 | |
JP2015031377A (ja) | 油圧駆動装置 | |
JP3955521B2 (ja) | 油圧駆動装置 | |
JPH1181391A (ja) | 作業機の制振制御装置 | |
JP3810942B2 (ja) | 建設機械の油圧駆動装置 | |
JP2003056507A (ja) | 伸縮アーム付作業機の油圧回路 | |
JP2020153505A (ja) | 作業機械の油圧駆動装置 | |
JP2020118271A (ja) | 作業機械における油圧シリンダの駆動装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): JP US |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LU MC NL PT RO SE SI SK TR |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
WWE | Wipo information: entry into national phase |
Ref document number: 2004519301 Country of ref document: JP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2003762902 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 10520144 Country of ref document: US |
|
WWP | Wipo information: published in national office |
Ref document number: 2003762902 Country of ref document: EP |
|
WWG | Wipo information: grant in national office |
Ref document number: 2003762902 Country of ref document: EP |