WO2004070211A1 - 油圧作業機 - Google Patents
油圧作業機 Download PDFInfo
- Publication number
- WO2004070211A1 WO2004070211A1 PCT/JP2004/000168 JP2004000168W WO2004070211A1 WO 2004070211 A1 WO2004070211 A1 WO 2004070211A1 JP 2004000168 W JP2004000168 W JP 2004000168W WO 2004070211 A1 WO2004070211 A1 WO 2004070211A1
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- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- hydraulic
- valve
- switching
- switched
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/024—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
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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
-
- 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
- E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
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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
- E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
- E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2285—Pilot-operated systems
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2296—Systems with a variable displacement pump
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- 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
- F15B2211/3052—Shuttle valves
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
- F15B2211/3133—Regenerative position connecting the working ports or connecting the working ports to the pump, e.g. for high-speed approach stroke
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- 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
- F15B2211/315—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
- F15B2211/31582—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 multiple pressure sources 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
- F15B2211/60—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
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a pressure
- F15B2211/6316—Electronic controllers using input signals representing a pressure the pressure being a pilot pressure
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
Definitions
- the present invention relates to a hydraulic working machine such as a hydraulic shovel that drives a working element such as a boom, a arm and a bucket by a plurality of hydraulic cylinders, and in particular, to a bottom of a hydraulic cylinder.
- a hydraulic working machine such as a hydraulic shovel that drives a working element such as a boom, a arm and a bucket by a plurality of hydraulic cylinders, and in particular, to a bottom of a hydraulic cylinder.
- Running state detecting means for detecting the running performance of a three-bar pressure sensor
- Patent Document 2 the technology described in Patent Document 2 is such that during the boom lowering operation, the pressure oil from the main pump is always supplied to the ⁇ VK chamber of the boom cylinder.
- the pressurized oil from the main pump is used for the bus cylinder. If only the private oil from the pot room is not supplied to the pump room and only the oil from the pot room is regenerated into the pump room, the pump consumption horsepower will be increased rather than inconvenient.
- the hydraulic oil discharged from the main pump is supplied to the ⁇ pad and chamber of the bumper cylinder. The supply of pressurized oil to the actuators for driving other working elements has been reduced,
- nap-ups are performed, for example, when escaping from a local area or when traveling down a steep slope while instructing italics with a boom.
- the present invention has been made to solve the deficiencies of the conventional technology, and aims at reducing the power consumption of the main pump and improving the energy efficiency at the time of a simple lowering operation of the work element. It can be a figure and the power of the body
- Hydraulic work that can be done: to provide
- This Ming for forming the serial huge basis of, is by expansion and contraction in the pressure oil to be out of the main pump or al-discharge in the first, and the double-acting type of! ⁇ So Li Sunda to drive the work element, the serial main pump
- a hydraulic working machine comprising: a directional control valve for controlling the flow of oil supplied to the lubricating hydraulic cylinder from the lubricating cylinder; and an operating device for switching the directional control valve.
- the flow path is switched as soon as the supply pressure to the cylinder is set to the specified pressure.
- a change in the flow path that changes the path of the pressure oil supplied from the main pump to the datum of the d-direction control valve to the open side or the closed side in accordance with the switching operation of the switching valve.
- the switchover valve is switched to the first switching position and the flow path is changed.
- the means is switched to the closed side, and the hydraulic oil discharged from the main pump is not supplied to the non-holding pressure supply side of the hydraulic cylinder.
- the jack-up switching valve is switched to the second switching position, and the BB flow path changing means is switched to the open side, and The hydraulic oil discharged from the main pump is supplied to a holding pressure side of the hydraulic cylinder through a bus self-directional control valve.
- the present invention secondly provides a main pump, a working element, and a hydraulic oil discharged from the main pump, which is expanded and contracted to drive the working element.
- a dynamic hydraulic cylinder, a directional control valve for controlling the flow of pressurized oil supplied from the main pump to the bottom chamber and the port V chamber of the front hydraulic cylinder, and the directional control valve A hydraulic work machine provided with an operating device for performing a switching operation between a jack and a zip switching valve that is switched when the bottom pressure of the hydraulic cylinder reaches a predetermined pressure.
- the main pump is moved forward with the switching operation of the tip switching valve.
- a flow changing means F for changing the path of the pressure oil supplied to the directional control valve to the open side or the closed side is provided.
- the valve is switched to the first position of the ac jack-up switching valve, the flow path changing means is closed, and the discharge from the main pump is performed.
- the jack-up switching valve is switched to the second switching position. Switch the flow path changing means to the open side, and supply the hydraulic oil discharged from the main pump to the PV chamber of the hydraulic cylinder through the directional control valve.
- the hydraulic cylinder for the boom provided on the hydraulic cylinder 3 receives a load such as a boom or an arm as a working element when the external force is not acting on the boom chamber side. Pressure.
- a pressing force is applied to the working element
- a tensile force is applied to the hydraulic cylinder for the boom, and the bottom chamber side of the low pressure cylinder becomes low pressure.
- the V-jacket switching valve is moved to the first switching position.
- a first directional control valve for controlling the flow of pressurized oil supplied to the traveling device of BU 1 and controlling the flow of pressure oil supplied to the second traveling device from the second main pump;
- a double-acting hydraulic cylinder that drives the element; and a second hydraulic pump that controls the flow of pressurized oil supplied from the first main pump to the bomb chamber and the PV chamber of the hydraulic cylinder.
- a third directional control valve, a fourth directional control valve for controlling the flow of hydraulic oil supplied from the second main pump to the bomb chamber and the P chamber of the front sd hydraulic cylinder, and A hydraulic operating machine comprising: a first operating device for performing a switching operation of a second directional control valve and a second operating device for performing a switching operation of a third and a fourth directional control valve;
- the jack-up switching valve which is switched when the pressure of the hydraulic pressure cylinder reaches a predetermined pressure, and the switching operation of the corresponding jack-up switching valve
- Flow path changing means for changing the path of the pressure oil supplied from the main pump to the HU third directional control valve to the open side or the closed side; Bei, when during lowering operation of the front work ⁇ hydraulic shea Li Sunda the volume Bokumu ⁇ is the predetermined pressure or more Kiniwa, the serial N'ya Kkia-up switching valve first
- the present invention fourthly provides a hydraulic working machine having the first or second configuration, wherein a meter discharged from a bottom chamber of the hydraulic cylinder is provided. ⁇ Insert the-part of the oil into the ⁇ ⁇ of the hydraulic cylinder. It has a regenerative circuit that regenerates the supplied machin oil.
- the hydraulic cylinder can be used even when a pressing force is applied to the work element during the simple operation of lowering the work element.
- the present invention is configured such that the hydraulic working machine of each of the above-mentioned configurations is provided with a hydraulic pilot-type switching valve as the jack-up switching valve.
- the present invention comprises: a variable displacement hydraulic pump as a main pump; a displacement control means for controlling the displacement of the variable displacement hydraulic pump; ⁇ And one working element, and a small number of actuators that are expanded and contracted by the pressure oil discharged from the displacement hydraulic pump to drive the working element.
- a directional control valve for controlling the amount of pressure oil supplied from the variable displacement hydraulic pump to the hydraulic cylinder, a pilot working device for controlling the shift of the directional control valve, and Operation control means for transmitting tilt control signal to the tilt control means in response to is from the operation EL, and to the working pressure machine, the holding pressure of the previous actuator.
- the vacuum pump switching valve to be switched, and the pressure supplied from the variable volume hydraulic pump to the BU-directional control valve mechanism with the switching operation of the vacuum pump switching valve.
- Flow path changing means for changing the oil / Jib path to an open circuit side or a closed circuit side;
- the J-cap switching valve is switched to the first switching position, and the m-way changing means is switched to the closed side.
- variable displacement hydraulic pump When the pressure oil supplied to the pump is cut off, the displacement of the variable displacement hydraulic pump is controlled to decrease.
- the flow path changing means is switched to the open circuit side by switching the pressure switch and the soap switching valve to the second switching position, and switching to the open circuit side.
- the pressure oil discharged from the variable displacement hydraulic pump is supplied to the actuator via the directional control valve, and the tilt displacement instructing means is used to push the variable displacement hydraulic pump. It is configured to control the increase in volume.
- the hydraulic cylinder for a cylinder receives the weight of a working element such as a boom or a ram, so that the bottom of the bottom chamber has a high pressure.
- the pressing force is applied to the work element
- the pulling force is applied to the hydraulic cylinder cylinder so that the pressure in the drum chamber becomes low.
- Changes in the holding pressure of the actuator such as the bottom pressure of the hydraulic cylinder, are monitored and the holding pressure of the actuator, which drives the work element when the work element is lowered, is monitored.
- the pressure is higher than the specified pressure, -5)
- first and second variable displacement hydraulic pumps as main pumps, and the first and second pumps.
- Variable displacement m The first and second tilt control means for individually controlling the displacement of the hydraulic pump, and the hydraulic oil discharged from the variable displacement hydraulic pump according to Rule 1
- the second variable capacity ⁇ The 20th directional control valve that is supplied from the hydraulic pump to the second travel unit of the HU and controls the hydraulic oil, and the E ⁇
- the first and second ⁇ variable valleys are expanded and contracted by pressurized oil discharged from the JHL type hydraulic pump.
- An actuator a third directional control valve for controlling the flow of pressure oil supplied from the first variable displacement hydraulic pump to the actuator X-motor, and a variable displacement valve of ⁇ 2
- a fourth directional control valve for controlling the flow of pressure oil supplied from the hydraulic pump to the actuator, and a pie control for disconnecting the first and second directional control valves.
- a tilt control means that outputs a tilt control signal to a tilt control means in response to a signal from a vault operating device, the holding pressure of the actuator X Pressure switch, which is switched when the pressure is reached, and the first variable displacement hydraulic pump from the first variable displacement hydraulic pump in accordance with the switching operation of the corresponding jaw / jump switch.
- the jack-up switching valve When the holding pressure is equal to or higher than the predetermined pressure, the jack-up switching valve is switched to the first switching position, and the i-way changing means is switched to the closing side, and the first and the i-th switching means are switched. Pressurized oil supplied from the variable displacement hydraulic pump to lu actuator X unit. The displacement of the variable displacement hydraulic pump of No. 2 is reduced. If the holding pressure of the actuator is lower than the predetermined pressure during the lowering operation of the self-made element. First, the iij jack-up switching valve is switched to the second switching position, the flow path changing means is switched to the open side, and the first and second variable displacement hydraulic pumps are switched. When the pressurized oil discharged from the tank is supplied to the actuator via the third and fourth directional control valves, it is supplied to it by means of the tilt instruction means. To increase the displacement of the variable hydraulic pump
- the flow path changing unit includes an upstream side of the direction control valve.
- the directional control valve With the directional control valve's main port.
- the jack-up switching valve When the jack-up switching valve is switched to the first switching position, the valve is switched to the closed position and the jack switching valve is switched to the second switching position.
- the quantity control valve that is switched to the open position and the center control passport of the directional control valve are connected downstream of the directional control valve.
- the jack-up switching valve has been switched to the first switching position, the valve is switched to the open position and J is switched.
- it is configured to consist of a centrifugal bypass switching valve that can be switched to the closed position.
- the / Ml control valve and the center path switching valve which are switched according to the switching position of the flow path hand flap jack switching valve in the first, second or fifth problem solving means.
- a simple lowering of the work by ⁇ e in the vault chamber reduces the pumping horsepower during the m operation and improves the X energy effect of the hydraulic operation, which generates a large pressing force on the work element. It is possible to make the car body jump up
- the path changing means is provided upstream of the third directional control valve.
- the jack-up switching valve is connected to the port and the above-mentioned jack-up switching valve is switched to the 1st switching position, it is switched to the closed position, and the 13-way jack switching valve is switched to the 2nd switching position.
- the control valve is switched to the open position at the time, and it is switched to the open position.
- the jack-up switching valve is switched to the first switching position
- Switching of 2 It is configured to consist of a center path switching valve that is switched to the closed position when it is switched to fii.
- the present invention provides a ninth and a seventh aspect to achieve the above object.
- a hydraulic pilot switching valve is provided as the jack switching valve, and the hydraulic pipe and the switching valve are restricted to the pilot port.
- a hydraulic pipe type switching valve is provided as a jack-up switching valve
- the signal port of the jack-up switching valve and the bottom chamber of the hydraulic cylinder are provided. It is only necessary to connect and to the oil path.
- the hydraulic pie port type disconnection states that the pie port port of the valve is l3 ⁇ 4L-S), which prevents hunting of the hydraulic pilot type switching valve, and is a simple work element. The transition from the lowering operation force to the pressing operation of the work element can be performed smoothly and reliably.
- the present invention provides the hydraulic working machine according to the tenth or B'J 1 to ninth configuration, wherein the jumper switching valve one
- a magnetic switching valve for controlling the switching operation of the pressure sensor, pressure detecting means for detecting the pressure value of the bottom chamber of the vertical pressure cylinder, and pressure based on the pressure detected by the pressure detecting means.
- a further control means is provided for operating the te sc magnetic switching valve.
- an electromagnetic switching valve is provided as the jack-up switching valve, a small number of hydraulic cylinder bottom chambers (holding pressure side) and the signal of the jack-up switching valve are provided. Since the oil passage connecting the port and the port can be omitted, the hydraulic circuit can be simplified.
- the present invention provides the eleventh aspect of the present invention.
- the tilt instructing means may include, among the operation signal pressures generated by the pilot port operating device, a directing pressure of a predetermined operation signal pressure group.
- a combination of a plurality of control valves is used as a tilting instruction means.
- the required operation signal pressure can be reliably selected with a simple circuit configuration (because it is difficult to push the variable element type hydraulic pump using the tilting instruction means when pushing the work element.
- the hydraulic working machine for increasing and controlling the mussels can be implemented at a low cost.
- the required pressure oil can be reliably supplied to the actuator X-presser during the pressing operation of the working element, which is simple. It is possible to smoothly and reliably perform the ⁇ line from the lowering operation of the work element to the pushing of the work element.
- the work to lower the mi is boom, and the work X Is for booms; 'Ta pressure cylinders have a la configuration
- the work element is provided with a boom, and the work X
- the hydraulic working machine such as a hydraulic cylinder equipped with a hydraulic cylinder for the vehicle and the bomber, can be used as described in the above 5th and 5th.
- the functions and effects described in (6) Problem solver fx are exhibited in order to achieve the above-mentioned purpose, the present invention provides, in
- the-part of the meter oil discharged from the bottom chamber of the hydraulic cylinder for the above-mentioned cylinder is described.
- the system is equipped with a regeneration circuit that regenerates the meta-oil supplied to the cutting chamber.
- the pressure is determined based on the specified pressure.y The difference between the large and small ports is shown.
- the switching position of the valve switching valve is set to the first switching position or the second switching position.
- V jack-up switching valve As described above, if an electromagnetic switching valve is provided as the V jack-up switching valve, a small number of, ie, a low pressure cylinder ⁇ tom chamber and a port of the V-jack shut-off valve are provided. It is possible to reduce the number of oil passages to be connected, and to simplify the hydraulic circuit.
- variable pressure machine of the present invention monitors the change in the bottom pressure of the variable pressure cylinder that drives the element, and monitors the pressure of the hydraulic cylinder that drives the at element during the operation of lowering the element.
- the jack-up switching valve is switched to the first switching position, the fjll road changing means is switched to the closed side, and discharged from the main pump.
- Hydraulic oil The power consumption of the pump during the lowering operation of a simple work element that does not require a pressing force for jacking up the vehicle body is eliminated because it is not supplied to the cylinder P and the chamber.
- the main pump supplies the actuator for driving the other work element.
- the hydraulic pressure applied to the hydraulic cylinder can be relatively increased and the energy efficiency of the hydraulic working machine can be reduced. If it is not soiled, switch the yardcap switching valve to the second switching position and switch the flow path changing means to the open side, and switch the pressure oil discharged from the main pump to the directional control valve. To the chamber of the hydraulic cylinder via the It can generate the necessary driving force for the work element, and the combined operation of the traveling operation and the work lowering operation enables the vehicle body to be captured.
- FIG. 1 is a side view of a hydraulic working machine according to the present invention.
- FIG. 2 is a circuit diagram of a hydraulic circuit according to the first embodiment.
- FIG. 3 shows the configuration of the operating device
- FIG. 4 is a circuit diagram of a hydraulic circuit according to the second embodiment.
- FIG. 5 is a circuit diagram of a hydraulic circuit according to the third embodiment.
- Fig. 6 is a circuit diagram of the hydraulic circuit according to the fourth embodiment.
- Fig. 7 is a circuit diagram of the voltage circuit according to the 5 and m configurations
- Fig. 8 shows the hydraulic circuit of the sixth operational example.
- FIG 9 is a circuit showing the main part of the hydraulic circuit m according to the sixth embodiment.
- FIG. 10 is a circuit diagram of a hydraulic circuit according to a seventh embodiment
- FIG. 11 is a circuit diagram of a hydraulic circuit according to an eighth embodiment ⁇ example
- FIG. 12 is a hydraulic circuit according to a ninth embodiment.
- FIG. 13 is a circuit diagram of a hydraulic circuit according to a tenth embodiment.
- FIG. 14 is a configuration diagram of a shuttle valve group provided in the hydraulic circuit of the tenth embodiment.
- FIG. 1 is a side view of the hydraulic working machine according to the present invention.
- the hydraulic working machine of this example is a hydraulic shovel, and as shown in FIG. 1, a traveling body 3 including left and right traveling devices 1 and 2, and a swiveling white space on the traveling body 3.
- the revolving superstructure 4 attached, a boom 5 rotatably pinned to the B-force and the rotating body 4, and a boom 6 rotatably pinned to the bom 5 at one end.
- a bucket 7 whose end is rotatably pin-connected to the arm 6, a first and second traveling hydraulic motors 89 for driving the traveling unit 12 and a revolving unit 4 are driven.
- Turning hydraulic motor 10 a hydraulic cylinder 11 for driving a boom 5, a hydraulic cylinder 12 for driving a arm 6, and a packet 7.
- FIG. 2 is a circuit diagram of a main part of the hydraulic circuit according to the first embodiment, and FIG. It is clear from these figures that the hydraulic circuit of this example is a hydraulic piezo valve as a jack-up switching valve.
- the hydraulic circuit is a double-acting boom that expands and contracts with the main pump 21 and the pressure oil discharged from the main pump 21 to drive the boom 5.
- Hydraulic cylinder 11 and the hydraulic oil supplied to the boom hydraulic cylinder 11 1 from the main pump 21 to the boom chamber 11 a and the The directional control valve 22 to be controlled, the operation device 23 for switching the directional control valve 22, the pipe pump 24, and the pilot port A jack switching valve 25 that controls the flow of pressurized oil discharged from the pump 24, and a metadata port for the directional control valve 22 upstream of the directional control valve 22 Are connected and switched by the jack-up switching valve 25, and are connected to the center port of the directional control valve 22 below the control valve 26 and the directional control valve 22.
- the center bypass switching valve 27 that is switched by the switching valve 25 and a tank 28.
- the jack V switching valve 25 performs a jack-up.
- a hydraulic pilot type switching valve that is switched to connect the pressure oil discharged from the main pump 21 to the meter side at the time of operation, and the center bypass switching valve 27 is Switching valve for opening and closing the center bypass
- the port control valve 26 is composed of a port valve 261, and this port valve.
- a back-pressure chamber of 26 1 and a pump port side of the directional control valve 22 are connected and shut off.
- the U-directional control valve 22 is provided with a regeneration circuit including a throttle y 29 a 29 b and a check valve 29 c.
- the operating device 23 is provided with an operating lever 23 a and a pump lowering side pressure reducing valve 23 3 which is switched by the operating lever 23 a. b and boom raising side pressure reducing valve 23 c
- an oil passage connecting the directional control valve 22 and the tank 28 is connected to an oil passage 3 7 on the directional control valve 22 side via a center bypass switch valve 27. It is divided into a tank 28 and an oil path 38 on the side Between the valve 22 and the oil passage 38 on the tank 28 side, an oil passage 39 for guiding the-part of the pressure oil discharged from the pot 11a to the tank 28
- a pipe line 40 for supplying a boom lowering signal and a boom raising signal supply are provided between the operating device 23 and the signal port of the directional control valve 22.
- ⁇ V-pump line 41 is provided, and furthermore, the pump pressure for lowering the boom is switched via the jack-up switching valve 25 to the center path switching valve. 2 7 ⁇ Pi ⁇ V for switching signal supply 4 2, 4
- a pipe line 44 for supplying a switching signal is provided between the switching port 26 and the signal port of the switching valve 26 through a jack-up switching valve 25.
- 11a is high pressure to support the white weight of the boom etc.
- the y, n, + jack switchover valve 25 is switched to the switching position 25a, and the ⁇ control valve 26
- the switching valve 26 2 is switched to the switching position 26 a, and the center pass switching valve 27 holds the valve position 27 a, so that the pressure oil discharged from the main pump 21 is
- the oilway 31, the directional control valve 22, the center passport, the oilway 37, the centerpath switch valve 27, and the oilway 38 pass through the tank 28 to the tank 28.
- the operation lever-23 a 3 ⁇ 4 ⁇ When operated in the left direction in the figure, that is, in the direction of lowering the boom, the hydraulic pressure supplied from the pipe pump Z4 ⁇ the pressure reducing valve 23 b , And the reduced pressure is led out to the piping line 40 as a boom lowering signal, and the directional control valve 22 is switched to the switching position 22a. Can be replaced. Then, part of the return oil from the pot chamber 11a is throttled 29b, the check valve 29c and the oil chamber 35 through the oil passage 35. And the remaining oil is squeezed 29 a and oilway 3 Returned to tank 28 via 9.
- the hydraulic cylinder for boom is guided to the tank 28 through the center bypass path 2, J.37, the center path switching valve 27 and the oil passage 38.
- the switching valve 25 is switched to the switching position 25b, and the switching valve of the quantity control valve 26 is connected via the pipe outlet pipe 44 and the pipe outlet pipe 45. Since the pressure oil from the pilot pump 2 supplied to the signal port of 26 2 is shut off, the switching valve 26 2 is set to the valve position 2
- the pressure of the port valve 26 1 is the same as that of the line 33, the pressure oil discharged from the main pump 21 is changed to the oil path 32, and the flow control valve
- operation lever 23a is moved in the right direction in the figure, that is,
- the hydraulic working machine monitors the change in the bottom pressure of the hydraulic cylinder for boom 11, and performs the hydraulic cylinder for boom during the boom lowering operation.
- the jack-up switching valve 25 is switched to the switching position 25a, whereby the switching valve 2 of the OIL village control valve 26 is switched. 6 2 is switched to 1 fc 26 a.
- the center bypass switch valve 27 is set to the valve position 27a, and the hydraulic oil discharged from the main pump 21 is used for the hydraulic pressure for the boom.
- a simple pump that does not require pressing force to make the car ir cap c, because it is not supplied to the cylinder 11 1 Horsepower ' ⁇ £ reduction.
- the pressurized oil discharged from the main pump 21 at the time of the simple boom lowering operation is not supplied to the chamber 11b of the hydraulic boom hydraulic unit 11 and, therefore, the boom is not provided. 5 and the other working elements, for example, the arm 6 and the packet 7 are operated in combination, the main pump 21 to the arm hydraulic cylinder 1
- the hydraulic working machine has a regeneration circuit in which the directional control valves 22 are formed by y29a, 29b and the X-valve 9 or TP *.
- the hydraulic working machine includes a jack V switching valve.
- FIG. 4 is a circuit diagram of a hydraulic circuit according to the second embodiment.
- the hydraulic circuit of the present embodiment has a jack-up switching valve and a center bypass switching valve.
- the feature is that the switching of is performed by a solenoid valve.
- reference numeral 51 denotes a pressure sensor for detecting the bottom pressure of the boom hydraulic cylinder 11
- reference numeral 52 denotes a jack-up switching valve 25 and a center bypass switching valve 27.
- 53 is a solenoid valve for taking in the output signal of the pressure sensor 51 and outputting a command current value supplied to the signal input section of the solenoid valve 52.
- Reference numeral 55 designates a path connecting the signal port of the jack-up switching valve 25 and the solenoid valve 52.
- the pilot line, designated by reference numeral 56 is a pilot line connecting the signal port of the center bypass switching valve 27 to the solenoid valve 52, and corresponds to Fig. 2. The same reference numerals are shown in the parts that do.
- the controller 53 has a bottom pressure value of the boom hydraulic cylinder 11 detected by the pressure sensor 51 and a command current value supplied to the signal input section of the solenoid valve 52.
- the solenoid valve 52 holds the valve position 52 a, and the bottom pressure value detected by the pressure sensor 51 is the range of the bottom pressure value when the pressing force acts on the boom 5.
- a command current for switching the solenoid valve 52 to the switching position 52b is output.
- the reason why the switching valve 26 2 is switched to the switching position 26 a and the center bypass switching valve 27 holds the valve position 27 a is described in the first embodiment.
- the hydraulic working machine according to the present embodiment has the same effects as the hydraulic working machine according to the embodiment, and at least a hydraulic cylinder for a boom.
- FIG. 5 is a circuit diagram of the hydraulic circuit according to the third embodiment I; as can be seen from the diagram of fc, the hydraulic circuit of the present example has a two-way switching valve as an engine switching valve. A solenoid valve is provided, and the switching of the two electromagnetic valves is controlled based on the pot pressure of the hydraulic cylinder for the boom and the pilot pressure of the directional control valve. ing
- reference numeral 51 denotes a boom hydraulic line 11 which outputs the pot pressure of the hydraulic line 11 ⁇ 1 pressure sensor
- reference numerals 616 and 162 denote a first and a second valves constituting a cap switching valve.
- the solenoid valve symbol 6 3 is a pipe line.
- a second pressure sensor for detecting the pressure of 40 is indicated by reference numeral 64.
- the reference numeral 64 denotes the output signal of the first pressure sensor 51 and the output 1 of the second pressure sensor 63.
- m A pipe line connecting the magnetic valve 6 1 and the signal port of the flow control valve 26 to the switching port 26 of the flow control valve 26, and the reference numeral 66 denotes the second solenoid valve 62 and the center no-path switching valve 2
- Figure 7 shows the pilot pipeline connecting the signals in Figure 7 and the other parts corresponding to those in Figure 2 are labeled with the same symbols.
- the bottom pressure of the bottom hydraulic cylinder 11 detected by the first pressure sensor 51 (( ⁇ ⁇ ⁇ ) Pressure) and a finger m value supplied to the signal input sections of the first and second solenoid valves 61 and 62, a first storage section 71 storing the relationship between the first and second solenoid valves 61 and 62, and a second pressure section.
- the bottom pressure value of the hydraulic cylinder for boom 11 detected by the pressure sensor 51 is changed when the boom self-weight falls. If the pressure is within the range of the bottom pressure value, that is, the predetermined pressure P 0 or more,
- the first solenoid valve 61 holds the valve position 61a and the minimum value selection circuit 73 They output a small value of the command current irrespective of the magnitude of the command current output from the second storage unit 72. For this reason, the second fe valve 62 also applies i ⁇ to the valve position m.
- the pressure oil discharged from the pump 24 is supplied to the signal port of the switching valve 262 of the bird control valve 26 via the first solenoid valve 61 and the pilot line 65. Therefore, the switching valve 26 2 is switched to the switching position 26 a, and the hydraulic oil discharged from the pipe pump 24 is shut off by the second solenoid valve 62. Pilot pressure in pipe line 66
- the center path switching valve 27 holds the valve position 27a.
- the first storage unit is provided when the bottom pressure value of 1 falls within the range of the bottom pressure value when the pressing force acts on the boom 5, that is, when the predetermined pressure P0 is lower than y. Since the limit value output from 7 1 is a large value, the first magnetic valve 61 is switched to the switching position lS o 1 b.o From the minimum value selection circuit 73, A flow corresponding to the finger output from the second storage unit 72 is output. Therefore, when the boom lowering operation force is performed, the second solenoid valve 62 is switched to the switching position 62b, and the center bypass switching valve 27 is switched to il'LT2. Switch to 7b. Conversely,
- the valve positions of the first solenoid valve 6 1 and the second solenoid valve 62 are switched to the switching positions 61 bf 62 b, respectively, or the center pass switching valve 27 is switched to the switching position 27 b. If it has been changed, as described in the first embodiment, the regenerated oil and the pressure oil supplied from the main pump 21 are combined into the chamber 11b. To be supplied, so the jack of the car body
- a strong pressing force such as a pressing force is generated.
- the relationship between the jack switching valve 25 and the center path switching valve 27 can be switched in conjunction with each other.
- the latch-up switching valve 25 and the center bypass switching valve 27 are independently switched off and J-switched.
- the first storage unit 71 When the boom port pressure is lower than P o, the first solenoid valve 61 that constitutes the pickup switching valve 25 regardless of whether the boom lowering operation is performed is Switch to switching position 6 1 b
- the soil flow value P i output from the first storage unit 71 is large.
- the finger output from the second thinking part 72 The p-flow pi has a small value, so that the smaller finger -p fs. 11a Pi force, from the minimum value selection circuit 73 Output, and the center bypass switching valve 27 is not switched from the switching position 27a, so that the first solenoid valve 61 is temporarily switched to the switching position 6a. Switching to 1 B y Switching the center bypass switch valve 27 to the switching position 27 b first will cause the pump discharge pressure to rise needlessly and degrade the X energy efficiency.
- the hydraulic working machine according to the second embodiment also has the same effect as the hydraulic working machine according to the second embodiment.
- FIG. 6 is a circuit diagram of a hydraulic circuit according to the fourth embodiment.
- the hydraulic circuit of the present example includes a pressure reducing valve 23 b that constitutes the operating device 23.
- the directional control valve 22 m control valve 26 and the center bypass switching valve 27 are switched by a boom lowering signal, that is, a boom lowering signal.
- reference numeral 51 denotes a pressure sensor of the collection 1 for detecting the bottom pressure of the hydraulic cylinder for boom 11
- reference numeral 8182 denotes a jack-opening valve.
- the first and second magnetic valves 8 3 take in the output signal of the pressure sensor 51 and switch the first and second m magnetic valves 8 1, 8 2.
- a controller for outputting a value, reference numeral 8 is branched from a pilot line 40, and a pilot line connecting to a first solenoid valve 81, reference numeral 85 is a pipe opening. Outlet branching off from the conduit 40 and connecting to the second solenoid valve 82
- reference numeral 86 is the first solenoid valve 81
- the control valve 26 is connected to the communication port of the shut-off valve 26 2. mouth
- Reference numeral 87 denotes a pipe line connecting the second solenoid valve 82 to the signal port of the center bypass switching valve 27, and reference numeral 88 denotes a second solenoid valve.
- a pipe C ! which connects the pressure reducing valve 23 c provided for the boom raising operation provided in the operation device 23 to the boom raising operation.
- the boiler hydraulic cylinder 11 detected by the first pressure sensor 51 and the boom hydraulic cylinder 11 have the same boom pressure value as the first electromagnetic wave.
- Hydraulic cylinder for boom detected by pressure sensor 51 with first notation 91 in which the relationship with finger tin value supplied to signal input section of valve 81 is stored.
- a second storage unit 92 in which the relationship between the bottom pressure value of the above and the command current value supplied to the signal input unit of the second m magnetic valve 82 is stored.
- ⁇ / • II value sets a reference current value in advance and sets the set current value as the limit value.
- the pressure sensor 51 When the boom hydraulic pressure of the boom hydraulic cylinder 11 detected by the above is within the range of the pot pressure value at the time of the fall of the weight of the boom, that is, when the predetermined pressure P 0 or more, the first Electric The valve 81 holds the valve position 81a according to the command current value output from the first storage unit 91, and the second solenoid valve 82 also stores the second storage unit 92 The valve position 82a is held by the command current value output from the controller. Therefore, when the boom lowering operation is performed, the pilot line 40 is connected to the pilot line 84, the first solenoid valve 81, and the pilot port line 86.
- the switching valve 26 2 is switched to the switching position 26a, and the pilot line 85 is also connected. Since the second solenoid valve 82 shuts off the pilot line 87, the pilot pressure does not rise, and the center bypass switching valve 27 holds the valve position 27a.
- the bottom pressure value of the boom hydraulic cylinder 11 detected by the pressure sensor 51 is applied to the boom 5
- the bottom pressure When the pressure is within the range of the pressure value, that is, when the pressure is lower than the predetermined pressure ⁇ 0, the first solenoid valve 81 is output from the first storage unit 91 as as
- the characteristics of the storage units 9 1, 9 2 of the 3rd 1st Ayo 2 are different. This is because, similarly to the third embodiment, the jack switching valve 25 and the center bypass switching valve 27 are switched independently of each other. In particular, in the present embodiment, the two storage units are provided with different characteristics, respectively, so that re-jumping can be cut off. It is possible to change and set the switching timing of each of the switching valve 25 and the center bypass switching valve 27. For example, seeing the relationship between the characteristics in FIG. 6, the reference setting pressure P o When the bottom pressure (BM no B pressure) is low, the set pressure P o is smaller than the set pressure P o and the command pressure P i is stored in the first storage unit 91 to the first storage unit 91.
- the reference setting pressure P o When the bottom pressure (BM no B pressure) is low, the set pressure P o is smaller than the set pressure P o and the command pressure P i is stored in the first storage unit 91 to the first storage unit 91.
- the switching valve 26 2 is switched earlier than the center bypass switching valve 27 because the relationship is also output earlier than the storage unit 92 of the second storage unit 92. In this way, by switching the jack-up switching valve 25 earlier than the center bypass switching valve 27, energy efficient operation can be achieved as in the third embodiment. This is what you get.
- the hydraulic working machine according to the present embodiment has the same effects as the hydraulic working machine according to the second embodiment.
- FIG. 7 is a circuit diagram of a hydraulic circuit according to the fifth embodiment.
- the hydraulic circuit of the present embodiment has a hydraulic circuit for driving the boom and a hydraulic circuit for driving the traveling device. It is characterized by combining circuits.
- reference numeral 8 denotes a right traveling hydraulic motor
- reference numeral 9 denotes a left traveling hydraulic motor
- reference numeral 101 denotes a second main pump
- reference numeral 102 denotes a main pump.
- a second directional control valve for controlling the flow of the pressure oil supplied from 1 to the right traveling hydraulic motor 8, reference numeral 103 is a left traveling hydraulic motor from the second main pump 101.
- the third directional control valve, which controls the flow of pressurized oil supplied to 9, is connected to the main pump 101 at the time of boom lowering operation.
- a directional control valve is a switching valve for supplying the hydraulic oil supplied by the first main pump 21 to the left traveling hydraulic motor 9 when the boom lowering operation is performed, reference numeral 10
- Reference numeral 6 denotes a shuttle valve that gives a switching signal to the switching valve 105 when a boom operation is performed.
- Reference numeral 107 denotes a second main pump 101 and a fourth directional switching valve 1. 0 Oilway connecting 4 and 4, sign 1
- the path passage designated by reference numeral 109, is an oil passage connecting the fourth direction switching valve 104 to the load chamber 11b of the hydraulic cylinder 11 for booms, and the reference numeral 110 is the fourth direction.
- 1 1 2 is an oil passage connecting the main pump 2 1 and the switching valve 105.
- Reference numeral 1 13 is a check valve provided on the oil passage 1 1 2 and reference numeral 1 1 4 is a switching valve 105 and a switching valve.
- An oil passage connecting the directional control valve 103 of No. 3 and a reference numeral 115 is a pipe pressure which is used as a boom lowering signal to the jack-up switching valve 25 ⁇ Pilot pipe
- Reference numeral 116 denotes a pipe line for supplying a boom lowering signal to the signal port of the fourth directional control valve 104
- reference numeral 117 denotes a fourth directional control valve 104.
- a pipe port line for supplying a boom-up signal to the signal port, and reference numeral 118 denotes a pipe line for supplying a switching signal to the signal port of the switching valve 105.
- Other parts corresponding to those in FIG. 2 are indicated by the same reference numerals.
- Operation Reaper — 23 a is in neutral position a As shown in Fig. 7, directional control valve 22 and fourth directional control valve 104 are in neutral position 22b and neutral position 104, respectively. Holding b, the jack switching valve 25 is switched to the y switching position 25a by the pressure on the bottom side of the boom oil cylinder 11. In this state, the pipe outlet pipe 43 is in communication with the tank 28, the center pipe switching valve 27 holds the valve position 27a, and the switching valve 105 has the valve position 1 0 5 a is retained, and the pressure discharged from the main pump 21 is used. % Way 3 1 1-way control valve 22 2-centre passport, oil drainage 37, centapass Switching valve 27 and oil path
- Hydraulic oil guided to tank 28 through 3 8 and discharged from 2 main pump 101 is connected to oil passage 107 oil passage 108 and the third directional control valve.
- the hydraulic chamber for the boom hydraulic cylinder 11 has a hydraulic chamber in the bottom chambers 11a and Pb of the hydraulic cylinder 11 and a chamber 11b. Is not supplied In this state, when the operating lever 23a is operated in the direction of the arrow ⁇ , that is, in the boom lowering direction, the pilot pressure is supplied from the pilot pump 24 and decompressed by the pressure reducing valve 23b. The pilot pressure is led out to the pipe line 40, and the directional control valve 22 is switched to the switching position 22a, and the pilot line is connected to the pilot line 115. The pressure is led to the signal of the switching valve 26 2 via the jack-up switching valve 25, so that the switching valve 26 2 is switched to the switching position 26 a.
- the jack-up switching valve 25 when the bottom pressure is higher than the forage pressure of the jack-up switching valve 25, the jack-up switching valve 25 is maintained at the valve position 25a, so that the flow rate is reduced.
- the switching position of the control valve 26 is also maintained at the switching position 26a, and the center bypass switching valve 27 is also maintained at the valve position 27a. Therefore, the pressure oil discharged from the main pump 21 is supplied to the / JM 31, the center bypass port of the directional control valve 22, the oil passage 37, the center bypass switching valve 27, and the oil passage 3. 8 and to the tank 28, and the pressure discharged from the second main pump 101 is controlled by the oil path 107, the oil path 108, and the third direction control.
- the pipe pressure as a boom lowering signal when the jack switching valve 25 is switched ⁇
- the fourth directional control valve 104 is supplied to the boom lowering side signal port of the fourth directional control valve 104 through the inlet line 1 16, so that the fourth directional control valve 104 is switched to the switching position 1.
- 0 4a was switched to-when the pressure oil discharged from the main pump 21 was supplied to the mouth chamber 11b of the hydraulic cylinder 11 for boom, it was switched to it.
- Hydraulic oil discharged from the main pump 101 of No. 2 passes through the fourth directional control valve 104, the oil path 109 and the oil path 35, and the V chamber of the hydraulic cylinder for boom 11 1 Supply 1 1 b
- the port pressure for the operation of the boom is set to the shuttle valve 106 Oil line 1
- the directional control valve 102 and the third directional control valve 103 are supplied to left and right traveling pressure motors 89 respectively. As a result, if you are working at the same age as the reboom and running, the
- FIG. 8 is a main part circuit diagram of the hydraulic circuit according to the sixth embodiment, and FIG. 6 It is a configuration diagram of the shuttle valve group provided in the hydraulic circuit of the embodiment, and it is apparent from these figures that the hydraulic circuit of the present example is a hydraulic circuit that functions as a jumper switching valve. It is equipped with a P-Pot type switching valve and supplies hydraulic pressure from one variable displacement S-pressure pump to the hydraulic cylinder.
- the hydraulic circuit of the present embodiment has a variable displacement pump (main pump) 21 and a variable displacement hydraulic pump 21 as shown in FIG. 2 with respect to the first embodiment shown in FIG.
- Control of the displacement of the pump (tilt control means) 21 a and the hydraulic oil discharged from the variable displacement hydraulic pump 21 expands and contracts, and the boom (work element) 5 is moved.
- ⁇ directional control valve 22 and directional control valve that control the flow of pressure oil supplied to
- the switching operation of 2 2 is performed.
- the jacking device controls the flow of the oil discharged from the pipe operating device 23, the pipe pump 24, and the pipe V pump 24. Is connected to the meter port of the directional control valve 22 on the upstream side of the directional control valve 22 and the directional control valve 22.
- the switching is performed by the control valve 25 and the downstream side of the phoenix control valve 26 and the directional control valve 22 is connected to the center pass photo of the directional control valve 22.
- the directional control valve 22 is provided with a regeneration circuit including a throttle 29a 29b and a check valve 29C.
- the pilot operation device 23 includes an operation lever 23a and a boom lowering side pressure reducing valve 23b that is switched by the operation lever 23a. And a boom raising side pressure reducing valve 23c.
- the pilot port of the u-ad jack-up switching valve 25 is provided with a throttle 25d for preventing hunting.
- the control valve 26 is connected to the port, and the port valve 26 1 and the port valve 2 are connected.
- the back pressure chamber of No. 1 communicates with the pump port side of the directional control valve 22, and is composed of a pi-cut type switching valve 26 2 that shuts off.
- the shuttle valve group 30 may be one in which individual shuttle valves and hydraulic switching valves are connected by piping, and the required shuttle may be installed in the body of the nozzle. Valves and hydraulic switching valves can be used that are integrated into the body
- the shut-off valves 3 0 1 3 1 5 are arranged above the shut-off valve group 30, and the shut-off valve 30 1 Select the high pressure side of the forward operation signal pressure A f and the traveling right reverse operation signal pressure A r, and set the shuttle valve 302 to the traveling left forward operation signal pressure B f and the traveling left backward operation signal pressure B.
- the high pressure side of r is selected, and the shut-off valve 303 selects the high pressure side of the operation signal pressure C c of the bucket cloud and the operation signal pressure C d of the packet vamp.
- the throttle valve 304 selects the operation signal pressure Du for raising the boom and the pressure side of the operation signal pressure for the shack, and the shal valve 305 selects the operation signal pressure for the arm cloud. Select the high pressure side of Ec and the working signal pressure Ed of the arm dump, and select the high pressure side of the working signal pressure Fr on the turning right and the Is pressure F1 on the turning left.Shuttle valve 3 0 7 preliminary provided in the mouth of spare Akuchueta is against the reserve directional control valve of Pai Lock Bok operating device
- the shuttle valve 3 0 8 3 10 is located in the second stage of the shuttle valve group 30, and the shuttle valve 3 08 is located at the top of the shuttle valve 3 0 1 and the shuttle valve 3.
- Select the pressure side of the operation signal pressure selected in each of 2 and the control valve 309 is the operation selected in each of the uppermost shuttle valve 304 and the shuttle valve 305
- the shuttle valve 310 selects the high pressure side of the operation signal pressure selected by each of the upper shuttle valve 310 and the shuttle valve 307
- the shut-off valve 3 1 1 3 1 2 is arranged at the third stage of the shut-off valve group 30, and the shut-off valve 3 11 1 is connected to the uppermost shut-off valve 30 3 and the 2-stage S.
- the high-pressure side of the operation signal pressure selected by each of the shut-off valves 309 is selected, and the shut-off valve 321 is a two-stage large shut-off valve 309 and a shut-off valve 309.
- the control valves 3 13 and 3 14 are arranged at the fourth stage of the control valve group 30, and the control valve 3 13 is arranged at the top of the control valve 310 and the control valve of the third stage.
- the high-pressure side of the operation signal pressure selected by each of the shut-off valves 3 11 is selected, and the shut-off valve 304 is a three-stage one-hundred shut-off valve 3 1 1 and a shut-off valve 3 1.
- the shut-off valves 3 15 are arranged in five stages of the shut-off valve group 30, and the operating pressure selected by the fourth-stage shut-off valve 3 14 and the boom lowering operation signal pressure D d are high. Select the side.
- the hydraulic switching valve 3 17 is selected by the shut-off valve 3 13, and the pressure is guided to the pressure receiving section 3 17 a, and operates based on the pressure of the received pressure.
- Hydraulic switching valve 3 1 7 is a shuttle valve 3
- step 3 If the pressure selected in step 3 is lower than the tank pressure, reduce the control lea pressure to the tank pressure as shown in the figure and select it with the shut-off valve 3 13 and the high pressure is higher than the tank pressure. Then, from the position ⁇ shown in the figure, the pressure of the outlet 7 and the pressure of the inlet pump 24 are reduced to a control signal pressure centered at the maximum pressure level and output.
- the regulator 21 a of the variable displacement pump 21 is actuated by the control signal pressure (pump control signal XP 1).
- the regulator 21 a raises the pressure of the pump control signal X 2 1
- the pump control signal XP 1 is given, the discharge flow of the variable displacement hydraulic pump 21 is reduced by applying the pump control signal XP 1.
- the directional control valve 22 is switched, and the operation signal from the variable displacement hydraulic pump 21 is received. (The amount of operation of the P-pipe operating device 23) is discharged to the boom hydraulic cylinder 11 1 in the bottom chamber 1 1 a or the ood chamber 1
- the hydraulic switching valve 318 is driven by the pressure selected by the shuttle valve 315 to the pressure section 318a, and operates based on the highest pressure. It is a proportional pressure reducing valve that generates a control signal pressure (bent operation Xf) from the pressure signal.
- a control signal pressure (bent operation Xf) from the pressure signal.
- the hydraulic switching valve 3 1 ⁇ > is moved to the position shown in the drawing to reduce the control signal pressure to the tank pressure.
- the maximum pressure selected by the throttle valve 3 15 exceeds the tank pressure, it is switched from the position shown in the figure, and the pressure of the pipe port pump 24 is controlled by the control signal pressure corresponding to the level of the maximum pressure.
- the swivel brake and x-ray cylinder (not shown) and the M-valve are operated by this control signal pressure (front operation Xf).
- the first embodiment I is provided with a regulator (tilt control means) 21a and tilt control is issued to the regulator 21a.
- a regulator tilt control means 21a and tilt control is issued to the regulator 21a.
- Shuttle en.
- valve group (tilt indicating hand FX) 30 Since the configuration with the valve group (tilt indicating hand FX) 30 is basically the only difference, it will only be described 112 for the J series, which will be a succession to the first embodiment m.
- Operation lever 23a is in the neutral position y, and operation lever 23a is moved leftward in the drawing, that is, the boom is lowered, since tension force is not acting on hydraulic cylinder 11 for boom.
- the boom 5 rotates in the downward direction (so-called self-weight drop).
- the hydraulic oil generated by the pipe operating device 23 enters the jack signal input port G of the control valve group 30.
- the input of the boom lowering signal input port D d and the pressure of the V-cap signal input port G are selected as the maximum pressure with other operation signals and the hydraulic switching valve 3 17 is switched.
- the hydraulic switching valve 3 17 is not switched to the opening, and the state shown in FIG. From 0, the tank pressure is output as the pump control signal X p 1, and the variable capacity is controlled via the regulator 21 a;
- the operation lever-23a is made in the boom lowering direction.
- the pressurized oil from the variable displacement hydraulic pump 21 supplied to the meter port of No. 2 and the regenerated oil discharged from the bottom chamber 11a pass through the oil path 35 to the regenerated oil. Fitted into the mouth chamber 11b of the hydraulic cylinder 11 for the boom, it can generate a strong pressing force such as a jack cap of the vehicle.
- the hydraulic oil generated by the pipe-put preserving device 23 enters the jack-up signal input port G of the shuttle valve group 30 and receives a plurality of other operation signals.
- the pressure is selected and the hydraulic switching valve 3 17 is switched.
- a pressure corresponding to the maximum pressure is output from the y shuttle valve group 30 as the pump control signal X p 1, and the variable displacement hydraulic pump is output via the regulator 21 a. 2 1 is controlled to increase
- the switching valve 25 is switched to the switching position 25b, and the flow control valve 26 is switched to the switching position 26b. Therefore, the oilway 3 2, flow control
- the hydraulic oil supplied from the variable displacement hydraulic pump 21 supplied to the measurement port of the directional control valve 22 through the control valve 26 and the oil passage 33 passes through the oil passage 34.
- the oil is supplied to the bottom chamber 11a, the hydraulic cylinder 11 for boom is extended, and the boom 5 is rotated in the upward direction.
- the pressure oil generated by the pi-Vullet operation device 23 enters the boom raising signal input port Du of the control valve group 30 and enters the other multiple ports.
- the number of operation signals and the maximum pressure are selected, and the hydraulic switching valve 3 17 is switched. As a result, a pressure corresponding to the pre-pressure is output from the shuttle valve group 30 as the pump control signal X ⁇ 1, and the variable displacement hydraulic pump 21 is supplied via the regulator 21a. Is controlled to increase
- the hydraulic collector monitors the change in the boom pressure of the boom hydraulic cylinder 11 and, during the boom lowering operation, the boom hydraulic cylinder.
- the jack-up switching valve 25 is switched to the switching position 25a, and the sound is switched to the flow control valve 26.
- the center bypass switching valve 27 is also set to the valve position 27a, and the hydraulic oil discharged from the variable displacement hydraulic pump 21 is pumped.
- the hydraulic cylinder is not supplied to the chamber 11b of the cylinder 11. Therefore, a simple boom lowering operation that does not require a pressing force to make the car body jack-up is required. The pump consumption horsepower can be reduced.
- the pressure oil discharged from the variable displacement hydraulic pump 21 during simple boom lowering operation is loaded into the load chamber 1 1b of the hydraulic cylinder 11 for boom.
- Hydraulic pump that can be used for multiple operation of chamber 6 and keto 7
- the bottom pressure of the hydraulic cylinder 11 for the boom is lower than a predetermined pressure when the boom 5 is lowered.
- the displacement of the displacement of the variable displacement hydraulic pump 21 is reduced and the boom pressure of the boom / barrier cylinder 11 is lower than the predetermined pressure when the boom 5 is lowered.
- the displacement of the variable displacement hydraulic pump 31 is controlled to be increased by the regulator 21a, so that the horsepower consumed by the pump during the simple boom lowering operation can be reduced.
- the hydraulic circuit for driving the hydraulic cylinder for a cylinder 11 has been described as an example, but the main points of the present invention are not limited to this.
- the hydraulic circuit for driving the hydraulic cylinders for the other working elements has the same configuration as described above.
- a hydraulic cylinder for other working elements there is a hydraulic cylinder for an arm 12, and a hydraulic cylinder for an arm 12 is used for jacking.
- the arm hydraulic cylinder 12 is extended from the state where the arm is pressed to 25, and the arm 6 is turned toward the driver's seat until the arm stands upright.
- pressurized oil is guided to a port chamber (not shown) of the arm hydraulic cylinder 12 to extend the arm hydraulic cylinder 12.
- the pressure in the orifice chamber of the arm hydraulic cylinder 12 is monitored, and the
- FIG. 10 illustrates a seventh example of the hydraulic circuit provided in the hydraulic working machine.
- FIG. 10 is a circuit diagram of a hydraulic circuit according to the seventh embodiment.
- the hydraulic circuit of this example is characterized in that the switching of the jack switching valve and the center bypass switching valve is performed by the m magnetic valve.
- reference numeral 51 denotes a pressure sensor for detecting and outputting the boom pressure of the hydraulic boom cylinder 11
- reference numeral 52 denotes a cam-valve-switching valve 25 and a center bypass.
- the magnetic valve 53 for switching the switching valve 27 receives the output signal of the pressure sensor 51 and changes the signal to the signal input section of the magnetic valve 52.
- Reference numeral 55 denotes a connection between the signal port of the pickup switching valve 25 and the magnetic valve 52.
- Reference numeral 56 denotes a pipe line, which indicates a pilot line connecting the reliable port of the center bypass switch valve 27 and the magnetic valve 52. Corresponding parts have the same reference numerals
- the controller ⁇ 53 has the pot pressure value of the hydraulic cylinder for boom 11 detected by the pressure sensor 51 and the flow value supplied to the signal input section of the solenoid valve 52. Y is stored, and the boat pressure value output by the pressure sensor 51 is within the range of the boat pressure value at the time of falling, that is, when the predetermined pressure P 0 or more. Is that the magnetic valve 52 has the valve position m. 52 a and the pot pressure value detected by the pressure sensor 51 is the boom.
- the boom lowering signal is required.
- the pilot pressure is cut off by the solenoid valve 52, and the pilot line 55, 5 No switching to jack-up due to no pipe pressure at 6
- the valve 25 holds the valve position 25a, the switching valve 26 of the flow control valve 26 is switched to the switching position 26a, and the center bypass switching valve 27 is in the valve position 27. hold a.
- a pilot pressure serving as a boom lowering signal is transmitted through the solenoid valve 52.
- the operation has been described in the first embodiment.
- the pressurized oil supplied to the load chamber 11b is only the regenerated oil discharged from the bottom chamber 11a, and the boom 5 falls by its own weight.
- a pump control signal Xp1 corresponding to the tank pressure is output from the shuttle valve group 30 to the regulator 21a, and the variable displacement hydraulic pump 21 The displacement is controlled to decrease.
- the jack-up switching valve 25 is switched to the switching position 25b and the center bypass switching valve 27 is switched to the switching position 27b, the first As described in the embodiment, the regenerating oil and the pressure oil supplied from the variable displacement hydraulic pump 21 are supplied to the load chamber 11 b in a combined manner, and the jacking force of the vehicle body is increased. Strong pressing force such as can be obtained.
- the pump control signal Xp1 corresponding to the maximum pressure selected by the shuttle valve group 30 is output to the regulator 21a from the shuttle valve group 30. The displacement of the fi hydraulic pump 21 is increased.
- the hydraulic working machine according to the present embodiment has the same effects as the hydraulic working machine according to the sixth embodiment, and at least has the bottom chamber 11 a of the boom hydraulic cylinder 11.
- the oil passage connecting the signal port of the jack-up switching valve 25 can be omitted, so that the hydraulic circuit can be simplified. ⁇ Eighth example of hydraulic circuit>
- FIG. 11 is a circuit diagram of the hydraulic circuit according to the eighth embodiment.
- the hydraulic circuit of this example has two solenoid valves as a switcher and a jumper switching valve, as well as the pot pressure of the hydraulic cylinder for the boom. It is characterized in that switching of these two solenoid valves is controlled based on the V outlet pressure of the directional control valve.o
- Reference numeral 51 denotes a first pressure sensor for detecting the bottom pressure of the hydraulic cylinder 11 for the vehicle
- reference numeral 6 16 2 denotes a jack-up.
- the magnetic valve symbol 63 of 2 is a second pressure sensor for detecting the pipe pressure of the pipe line 40, and the symbol 64 is a second pressure sensor.
- the output signal of the first pressure sensor 51 and the output signal of the second pressure sensor 63 are taken in, and the switching position of the first and second solenoid valves 6 16 is turned off.
- a command that outputs a command current value for switching ⁇ The reference numeral 65 indicates the signal port of the switching valve 26 2 of the first solenoid valve 61 and the control valve 26.
- Reference numeral 66 denotes a pipe line connecting the second ⁇ magnetic valve 62 and the signal port of the center bypass switching valve 27. Other parts corresponding to those in FIG. 8 are denoted by the same reference numerals.
- the controller 64 is connected to the first pressure sensor 5 as shown in FIG.
- the command power / JIL value and the finger / jit value output from the second storage unit 72 the smaller one of + ⁇ six
- T says, " ⁇ aw, choose a value and BU ⁇ 1st magnetic valve 6
- the bottom pressure value of the hydraulic cylinder 11 for the boom detected by the pressure sensor 51 is dropped by the boom's own weight.
- the command current value output from the first storage unit 71 becomes a small value.
- the magnetic valve 6 1 holds the valve position 6 1a, and the minimum value selection circuit 73 outputs an output 2 5B from the second storage unit 7 2
- the hydraulic cylinder for the boom detected by the pressure sensor 51 is used.
- the bottom pressure value of 1 is within the range of the bottom pressure value when the pressing force is applied to the boom 5, that is, the storage units 1 and 1 of the fields 1 and 1 having a pressure lower than the predetermined pressure P0.
- the first magnetic valve 61 is switched to the switching position 61b because the P-flow value output from the P value becomes a large value. Are stored in the second storage unit 72 according to the output command current.
- valve positions of the first magnetic valve 61 and the second magnetic valve 62 constituting the gap switching valve 25 are respectively switched to the switching positions 6 1 b 6 2 b, and Or the center pass switch valve 27 is switched to the switching position 27 b.
- the opening is provided with ⁇ and regenerated oil to the chamber 11 b as described in the first embodiment.
- Control signal Xp1 is output, and the displacement of the variable capacity hydraulic pump 21 is increased and controlled * S)
- the hydraulic working machine according to the present embodiment also has the same effect as the hydraulic working machine according to the seventh embodiment.
- FIG. 12 is a circuit diagram of a hydraulic circuit according to a ninth embodiment, and FIG.
- the hydraulic circuit of the present example is based on the packet pressure by the pressure reducing valve 23 b constituting the packet operating device 23, that is, the boom lowering signal.
- the directional control valve 2 2 The control valve 26 and the center bypass switching valve 27 are switched in ⁇ 3 country 1 2, and reference numeral 5 1 denotes a hydraulic cylinder for a boom. 1 1 bottom tom mouth
- the first pressure sensor that generates pressure, symbols 81 and 82 are the first and second ⁇ solenoid valves forming the jacking TV / VJ switching valve, and the symbol 83 is the pressure sensor 5
- a pilot pipe connecting the reliable small number 7 and a reference numeral 88 is a pressure reducing valve for raising the boom provided in the second solenoid valve 82 and the pilot operating device 23.
- Pilot line connecting 23 c and reference numeral 89 indicates a check valve provided at a connection point between the pilot line 87 and the pilot line 88.
- other portions corresponding to those in FIG. 8 are denoted by the same reference numerals.
- the first pressure sensor 5 As shown in Fig. 12, the first pressure sensor 5
- the relationship between the bottom pressure value of the hydraulic cylinder for boom 11 detected in 1 and the command current value supplied to the signal input section of the first magnetic valve 81 is stored in the first To the storage unit 91 and the bottom pressure value of the hydraulic cylinder for boom 11 detected by the first pressure sensor 51 and the signal input unit of the second solenoid valve 82.
- the second storage unit 9 stores the relationship with
- the bottom pressure value of the hydraulic cylinder for boom 11 detected by the pressure sensor 51 is reduced by the boom gravity weight.
- the first solenoid valve 81 is controlled by the command current value output from the first storage unit 91.
- the second solenoid valve 82 holds the valve position 82a according to the command current value output from the second storage unit 92.
- the pipe line 40 is connected to the pipe line 84, the pipe line 84, the first solenoid valve 81 and the pipe port.
- the bottom pressure of the boom hydraulic cylinder 11 1 detected by the pressure sensor 51 1 is applied to the boom 5 when the bottom pressure is applied to the boom 5.
- the first solenoid valve 81 switches the switching position according to the finger m Jib value output from the first storage unit 91. 8
- the center bypass switching valve 27 is switched to the switching position m. 27 b.
- the amount of the control valve 26 of the control valve 26 is switched to the switching position m 26 a, and the center bypass switch valve 27 is switched to the switching position 27 a.
- the boom 5 has its own weight because only the regenerated oil discharged from the pot chamber 11a power is supplied to the chamber and the chamber 11b as described in the first embodiment.
- a pump control signal XP 1 corresponding to the tank pressure is output to the regulator 21 a from the shuttle valve group 30, and the variable displacement hydraulic pump 21 O
- solenoid valve 8 1 and 2nd solenoid valve S 2 are switched to switching position 8 1b 8 2b '.
- the center or bypass valve 2 7 is switched to switching position 1SL 2 7b y 7L b, L is the 1st fe form, as described in the example, to Pb 11b from the regenerated oil and the pressure pump 21.
- the pressurized oil that flows is supplied with a flowing force, and a strong pressing force such as a J-capping force is generated on the vehicle body.
- the pump control signal XP 1 corresponding to the low pressure is output to the regulator 21 2a by the control valve group 30.
- the variable displacement hydraulic pump 21 is pushed. Volume control is controlled.
- the hydraulic working machine according to the present embodiment has the same effect as the hydraulic working machine according to the seventh embodiment.
- FIG. 13 is a circuit diagram of the hydraulic circuit according to the tenth embodiment. Is a block diagram of a shuttle valve group provided in the hydraulic circuit of the tenth embodiment.
- the hydraulic circuit of the present embodiment is a hydraulic circuit for driving a boom. Additional features a hydraulic circuit for driving the traveling device combined with the circuit
- reference numeral 8 denotes a hydraulic motor for traveling
- reference numeral 9 denotes a hydraulic motor for traveling left
- reference numeral 101 denotes a second allowable hydraulic pump
- Reference numeral 10 denotes a hydraulic pump.
- variable regulator tilt control means
- reference numeral 102 is for right running from the variable displacement hydraulic pump 21.
- a second directional control valve for controlling the flow of pressure supplied to the hydraulic motor 8 reference numeral 103 denotes a second variable displacement hydraulic pump.
- a fourth directional control valve for controlling the flow of pressurized oil supplied from the pump 101 to the hydraulic cylinder 11 for the boom, and the reference numeral 105 indicates a first directional control valve when the boom lowering operation is performed.
- a shut-off valve that gives a switch 1 ⁇ to the switching valve 105, and reference numeral 107 denotes a second variable hydraulic pump 101 and a fourth directional switching valve 104.
- An oil path symbol 110 connecting the load chamber 11b of the J-under 11 is a bottom chamber of the fourth direction switching valve 104 and a hydraulic cylinder pump 11
- An oil passage connecting 1 1a and 1 1 1 is a check valve provided on the oil passage 1 10, 1 1
- Reference numeral 117 denotes a pipe port line for supplying a boom raising signal to the signal of the fourth directional control valve 104.
- Reference numeral 18 denotes a pipe line for supplying a switching signal to the signal port of the switching valve 105, and other portions corresponding to those in FIG. 8 are denoted by the same symbols. Is
- the shuttle valve group 30 provided in the hydraulic circuit of the present example has the shuttle valve group 3 16 and the hydraulic switching valve 3 in the shuttle valve group shown in FIG.
- the hydraulic switching valve 3 19 has the highest pressure selected by the shut-off valve 3 16 and the pressure receiving section 3 1 9 a, which operates based on the maximum pressure and generates a control signal pressure (pump control signal XP 2) from the pressure of the pilot port pump 24.
- the control signal pressure is reduced to the tank pressure at the position shown in the figure, and the control valve 3 16 If the selected station pressure exceeds the tank pressure, it is switched from the position shown in the figure, and the pressure of the pipe pump 24 is controlled by the control Ira pressure according to the level of the pressure.
- the second pressure is generated by the control signal pressure (pump control signal XP 2) from the regulator 110 1 a of the hydraulic pump 101.
- the operation lever 23 is in the neutral position.a As shown in Fig. 13, the directional control valve 22 and the fourth directional control valve 104 are in the neutral position 2 respectively.
- the pilot pressure reduced by 3b is led out to the pilot line 40, and the directional control valve 22 is switched to the switching position 22a.
- the pilot pressure is led to the pilot pipe line 115, and is guided to the signal port of the switching valve 2622 via the jack-up switching valve 25.
- the switching valve 26 2 is switched to the switching position 26 a.
- a part of the return oil from the pot chamber 11a is throttled 29b, the check valve 29c and the load chamber are passed through the oil passage 35. While being regenerated to 11b, the remainder is returned to tank 28 via throttle 29a and oilway 39.
- the jack-up switching valve 25 when the bottom pressure is higher than the operating pressure of the jack-up switching valve 25, the jack-up switching valve 25 is maintained at the valve position 25a.
- the switching position of the control valve 26 is also maintained at the switching position 26a, and the center bypass switching valve 27 is also maintained at the valve position 27a. Therefore, the hydraulic oil discharged from the variable displacement hydraulic pump 21 is supplied to the oil passage 31, the center bypass port of the directional control valve 22, the oil passage 37, the center bypass switching valve 27, and the oil passage 3.
- the oil is guided to the tank 28 through the oil passage 8 and discharged from the second variable displacement hydraulic pump 101 in the oil passage 107, the oil passage 108, and the third direction.
- the valve is connected to the tank 28 via the valve 5 and the switching valve 26 of the quantity control valve 26 is switched to the valve position 26b.
- the valve is discharged from the variable displacement hydraulic pump 21 by Q.
- Pressurized oil is supplied to the metadata of the directional control valve 22 through the oil passage 32, the i-th control valve 26, and the oil passage 33 ⁇ ⁇ *] With the switching of the cap switching valve 25, the pipe pressure as the boom lowering signal is switched to the pipe pressure.
- the directional control valve 104 is switched to the switching position 104a. Accordingly, when the hydraulic oil discharged from the hydraulic pump 21 is supplied to the feed chamber 11b of the hydraulic cylinder 11 for the boom, the second variable hydraulic pump is started. The pressure oil discharged from 101 is the fourth directional control valve.
- ⁇ V is supplied to the chamber 11b, ⁇ V to the chamber 11b is the regenerated oil discharged from the bottom chamber 11a and the pressure oil supplied from the variable capacity hydraulic pump 21 Since it is supplied together with the pressure oil supplied from the second variable displacement hydraulic pump 101, it is possible to generate a strong pressing force such as the vehicle jack-up force.
- the hydraulic oil generated by the pipe operating device 23 enters the jack-up V input signal port G of the shuttle valve group 30 and receives other operation signals. And as pressure is selected and the hydraulic switching valve 3 17 is switched y ⁇ o y, the pump control signal X p 1 from the control valve group 30
- Variable volume hydraulic pumps 2 1, 1 0 1 are controlled via 1 a 1 0 1 a
- the switching valve 105 Since the switching valve 105 is guided to the switching valve 105 via the switching valve 105, the switching valve 105 is switched to the switching position 105b, and the hydraulic oil discharged from the variable displacement hydraulic pump 21 is supplied to the switching valve 105.
- the left and right traveling hydraulic motors 89 are supplied via the second directional control valve 102 and the third directional control valve 103, respectively, to simultaneously operate the boom and the traveling.
- the hydraulic fluid from the displacement hydraulic pump 21 is supplied to the traveling motors 8 and 9 on the left side, and the hydraulic fluid 11 for the second cylinder is supplied to the hydraulic cylinder 11 for the vehicle. Transformation Since the hydraulic oil from the hydraulic pump 101 is supplied, the combined operation of the traveling operation and the lowering operation is performed.
- the hydraulic pipe type switching valve is used as 25, but the above-mentioned seventh to
- M Magneto-hydraulic or electromagnetic switching valve can be used o
- the hydraulic circuit for driving the boom hydraulic cylinder 11 has been described as an example, but the gist of the present invention is not limited to this.
- a hydraulic circuit for driving a hydraulic cylinder for another working element may have the same configuration as described above.
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Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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US10/542,201 US7562615B2 (en) | 2003-01-14 | 2004-01-14 | Hydraulic working machine |
EP04702070A EP1591669A4 (en) | 2003-01-14 | 2004-01-14 | HYDRAULIC WORKING MACHINE |
JP2005504790A JP4279837B2 (ja) | 2003-01-14 | 2004-01-14 | 油圧作業機 |
US12/428,203 US8336443B2 (en) | 2003-01-14 | 2009-04-22 | Hydraulic working machine |
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JP2003005808 | 2003-01-14 | ||
JP2003-5808 | 2003-01-14 | ||
JP2003-143632 | 2003-05-21 | ||
JP2003143632 | 2003-05-21 |
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US10/542,201 A-371-Of-International US7562615B2 (en) | 2003-01-14 | 2004-01-14 | Hydraulic working machine |
US12/428,203 Division US8336443B2 (en) | 2003-01-14 | 2009-04-22 | Hydraulic working machine |
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WO2004070211A1 true WO2004070211A1 (ja) | 2004-08-19 |
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US (2) | US7562615B2 (ja) |
EP (1) | EP1591669A4 (ja) |
JP (1) | JP4279837B2 (ja) |
KR (1) | KR100674158B1 (ja) |
WO (1) | WO2004070211A1 (ja) |
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WO2017183404A1 (ja) * | 2017-03-29 | 2017-10-26 | 株式会社小松製作所 | 作業機械の管理装置 |
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KR20220154496A (ko) * | 2021-05-13 | 2022-11-22 | 볼보 컨스트럭션 이큅먼트 에이비 | 유압기계 |
GB202107462D0 (en) * | 2021-05-26 | 2021-07-07 | Univ Edinburgh | Hydraulic control system |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2134187A (en) * | 1982-12-03 | 1984-08-08 | Orenstein & Koppel Ag | Hydraulic circuit for adjusting on operating cylinder of excavating equipment |
EP0262098A1 (en) * | 1986-09-24 | 1988-03-30 | TRINOVA S.p.A. | A flow recovery system for hydraulic circuits with pumps and pressure compensated distributor valves for working members of earth-moving machines |
JPH0218496U (ja) * | 1988-07-20 | 1990-02-07 | ||
JPH06144794A (ja) * | 1992-11-10 | 1994-05-24 | Komatsu Forklift Co Ltd | 荷役装置におけるリフトシリンダ用油圧回路 |
WO1994013959A1 (en) * | 1992-12-04 | 1994-06-23 | Hitachi Construction Machinery Co., Ltd. | Hydraulic regenerator |
JPH07305379A (ja) * | 1994-05-16 | 1995-11-21 | Shin Caterpillar Mitsubishi Ltd | 建設機械のシリンダ制御回路 |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5174189A (en) * | 1988-06-08 | 1992-12-29 | Teijin Seiki Co., Ltd. | Fluid control apparatus |
JPH0218496A (ja) | 1988-07-06 | 1990-01-22 | New Japan Chem Co Ltd | 水溶性金属加工油剤用基剤 |
US5046309A (en) * | 1990-01-22 | 1991-09-10 | Shin Caterpillar Mitsubishi Ltd. | Energy regenerative circuit in a hydraulic apparatus |
JP2002097673A (ja) * | 2000-09-22 | 2002-04-02 | Shin Caterpillar Mitsubishi Ltd | 作業機械の油圧回路 |
JP2003120604A (ja) * | 2001-10-11 | 2003-04-23 | Shin Caterpillar Mitsubishi Ltd | 流体圧回路 |
WO2004070211A1 (ja) * | 2003-01-14 | 2004-08-19 | Hitachi Construction Machinery Co., Ltd. | 油圧作業機 |
-
2004
- 2004-01-14 WO PCT/JP2004/000168 patent/WO2004070211A1/ja active Application Filing
- 2004-01-14 JP JP2005504790A patent/JP4279837B2/ja not_active Expired - Lifetime
- 2004-01-14 KR KR1020057013058A patent/KR100674158B1/ko active IP Right Grant
- 2004-01-14 US US10/542,201 patent/US7562615B2/en active Active
- 2004-01-14 EP EP04702070A patent/EP1591669A4/en not_active Withdrawn
-
2009
- 2009-04-22 US US12/428,203 patent/US8336443B2/en not_active Expired - Lifetime
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2134187A (en) * | 1982-12-03 | 1984-08-08 | Orenstein & Koppel Ag | Hydraulic circuit for adjusting on operating cylinder of excavating equipment |
EP0262098A1 (en) * | 1986-09-24 | 1988-03-30 | TRINOVA S.p.A. | A flow recovery system for hydraulic circuits with pumps and pressure compensated distributor valves for working members of earth-moving machines |
JPH0218496U (ja) * | 1988-07-20 | 1990-02-07 | ||
JPH06144794A (ja) * | 1992-11-10 | 1994-05-24 | Komatsu Forklift Co Ltd | 荷役装置におけるリフトシリンダ用油圧回路 |
WO1994013959A1 (en) * | 1992-12-04 | 1994-06-23 | Hitachi Construction Machinery Co., Ltd. | Hydraulic regenerator |
JPH07305379A (ja) * | 1994-05-16 | 1995-11-21 | Shin Caterpillar Mitsubishi Ltd | 建設機械のシリンダ制御回路 |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005221026A (ja) * | 2004-02-06 | 2005-08-18 | Hitachi Constr Mach Co Ltd | 油圧作業機の油圧回路 |
JP2006292068A (ja) * | 2005-04-11 | 2006-10-26 | Hitachi Constr Mach Co Ltd | 油圧作業機 |
JP2008101414A (ja) * | 2006-10-20 | 2008-05-01 | Shin Caterpillar Mitsubishi Ltd | 油圧ショベルにおける油圧制御システム |
JP4702894B2 (ja) * | 2006-10-20 | 2011-06-15 | キャタピラー エス エー アール エル | 油圧ショベルにおける油圧制御システム |
JP2011002018A (ja) * | 2009-06-18 | 2011-01-06 | Hitachi Constr Mach Co Ltd | 油圧作業機械 |
JP2012047307A (ja) * | 2010-08-30 | 2012-03-08 | Kyb Co Ltd | 切換弁 |
JP2012052583A (ja) * | 2010-08-31 | 2012-03-15 | Hitachi Constr Mach Co Ltd | 油圧作業機 |
JP2012137148A (ja) * | 2010-12-27 | 2012-07-19 | Hitachi Constr Mach Co Ltd | 油圧作業機 |
JP2013234528A (ja) * | 2012-05-10 | 2013-11-21 | Hitachi Constr Mach Co Ltd | 建設機械の油圧制御装置 |
WO2014073338A1 (ja) | 2012-11-07 | 2014-05-15 | 日立建機株式会社 | 建設機械の油圧駆動装置 |
KR20150070095A (ko) | 2012-11-07 | 2015-06-24 | 히다찌 겐끼 가부시키가이샤 | 건설 기계의 유압 구동 장치 |
US9890518B2 (en) | 2012-11-07 | 2018-02-13 | Hitachi Construction Mahinery Co., Ltd. | Hydraulic drive system for construction machine |
Also Published As
Publication number | Publication date |
---|---|
US8336443B2 (en) | 2012-12-25 |
KR100674158B1 (ko) | 2007-01-24 |
EP1591669A4 (en) | 2010-12-08 |
US20090199552A1 (en) | 2009-08-13 |
EP1591669A1 (en) | 2005-11-02 |
US20060162543A1 (en) | 2006-07-27 |
JPWO2004070211A1 (ja) | 2006-05-25 |
JP4279837B2 (ja) | 2009-06-17 |
KR20050090078A (ko) | 2005-09-12 |
US7562615B2 (en) | 2009-07-21 |
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