WO2000055509A1 - Controleur d'actionneur - Google Patents

Controleur d'actionneur Download PDF

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Publication number
WO2000055509A1
WO2000055509A1 PCT/JP1999/006004 JP9906004W WO0055509A1 WO 2000055509 A1 WO2000055509 A1 WO 2000055509A1 JP 9906004 W JP9906004 W JP 9906004W WO 0055509 A1 WO0055509 A1 WO 0055509A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pump
valves
control
cylinder
Prior art date
Application number
PCT/JP1999/006004
Other languages
English (en)
Japanese (ja)
Inventor
Tomio Mizuno
Kazunori Yoshino
Kimimasa Onda
Original Assignee
Shin Caterpillar Mitsubishi Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shin Caterpillar Mitsubishi Ltd. filed Critical Shin Caterpillar Mitsubishi Ltd.
Publication of WO2000055509A1 publication Critical patent/WO2000055509A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
    • F15B2211/30595—Assemblies of multiple valves having multiple valves for multiple output members with additional valves between the groups of valves for multiple output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups

Definitions

  • the present invention relates to an actuator control device having a flow connection valve. Thread
  • Fig. 5 shows the hydraulic system installed on construction machines such as hydraulic shovels in the past.
  • the control valve 1 which is located at the center of Fig. 5, includes the control of the meter, the control of the meter, and the control of the noise.
  • a single straight running spool valve 1 str for ensuring straight running.
  • this control valve 1 is supplied with pressurized oil from two main pumps 2 and 3, and two pumps are provided.
  • the cylinders 4bo and stick cylinders 4st which are one of the places where it is necessary to supply the pressurized oil, are as follows: It is necessary to supply pressure oil for the second pump from the excess spool valves lbo2 and lst2 for the boom and the stick. , The original direction The above eight spool valves are required in combination with the spool valves lbol and 1stl for the boom and the stick for controlling. Let's go. 4 bu is a notebook cylinder, 4 trL is a motor for left running, 4 trR is a motor for right running, and 4 sw is a motor for upper turning. .
  • one traveling straightening step for ensuring traveling straightness when simultaneously operating the traveling system and the other actuators.
  • a total of 9 spool valves are required, resulting in a redundant structure.
  • the conventional control valve 1 includes a main passage, a meter-out passage, and an inos passage, each of which has a spool valve.
  • the engine is driven by the notch that is optimized for the constant engine speed, which is located individually, so that the load fluctuation and engine When the rotation speed of the engine changes, the fluctuation of the hydraulic pump discharge flow rate causes the disturbance to be lost, and the operability deteriorates. It also has.
  • the number of the spool valves is large, and a relief valve with a make-up function is also required.
  • the control valve control "Kutoi-Dai is difficult, and the control valve is connected to the control valve. There is a good noise point between the engine speed and the engine speed.Because the engine speed can only be established in a narrow range of conditions, Changes in the number of turns, etc., affect operability.
  • the present invention has been made in view of such a point. Therefore, the number of operating valves is reduced to improve the operability by reducing the number of operating valves, thereby improving the operability. Its purpose is to plan. Disclosure of the invention
  • the actuator control device of the present invention is operated by a plurality of pumps and a pump pressure fluid supplied from the plurality of pumps. And between the multiple bombs and the multiple actuaries, each of which is located at a different location. And one or more control valves, which are controlled in a one-to-one manner, and a plurality of pumps that are installed between the passages of the pump pressure fluid supplied from the plurality of pumps.
  • a flow-position coupling valve that has a closed position where the pump pressure fluid is diverted and supplied to the operating valve, and an open position where it is coupled and supplied to the operating valve. It is provided with and.
  • the operation valve set up one-to-one with Actuate Yue by means of the flow coupling valve also requires a maximum of multiple pumps. A sufficient amount of pump pressure fluid can be supplied by combining the flows discharged from the pump, so that the number of operating valves can be reduced compared to the past, and the installation space can be reduced. You can do the best connection.
  • this actuator control device The control valve and the flow connection valve are built in the control valve.
  • the control valve can be totally connected by reducing the number of stations of the operating valve.
  • the operating valve is provided between the pump and the actuator and is a metering knob for controlling the flow rate in response to an input signal.
  • a metering knob is provided between the actuator and the tank to control the flow rate according to the input signal. It is.
  • the meter side and the meter out side are connected to each other by the meta level and the meter out level. Since separation and control are performed individually, changes in the situation can be achieved by eliminating defects that can only be established in a narrow range of conditions where there is a current favorable noise point. It is possible to deal with the situation flexibly and improve operability.
  • the above-mentioned outlet is a neurot valve that controls the flow rate continuously by an external signal, and a neurot valve. G by valve. It is equipped with a port valve for controlling the flow rate drained to the tank by the pilot control. In this configuration, the control of the poppet valve is controlled by an external signal via a pilot valve through the use of an external signal.
  • the large flow rate drained from the pocket valve can be controlled, and the flow rate amplification function can be obtained.
  • this actuating device controls the port valve to drain the port valve due to the overload of the actuating device. It is equipped with a pressure control valve to be controlled. In this configuration, if an excessively large negative pressure is generated over a short period of time, the pressure control valve is actuated by the negative pressure and the pop valve is operated. The drain valve controls the shut-off valve, so that overload can be released immediately and there is no need to separately install an expensive line relief valve. You can stop down.
  • the poppet valve has a make-up function that is opened by a negative pressure generated in a circuit connected to the poppet valve. It is a thing. In this configuration, when a negative pressure is generated in the circuit, the negative pressure causes the poppet valve to open and then passes through the poppet valve.
  • the tank can be supplemented so that the liquid in the tank is sucked into the negative pressure generating part in the circuit, and the voiding of the liquid can be canceled.
  • the above-mentioned actuating mechanism includes a one-sided cylinder type actuating mechanism, and the one-sided, cylinder-type actuating mechanism is included in the above-described one-way cylinder type actuating mechanism.
  • the lube inn which controls Yue overnight is located on the two main roads between the pump and the two rooms of Actu Yue.
  • Each was equipped with a separate split spool valve.
  • the piston of the one-sided cylinder type actuator has a pressure receiving area of the rod side chamber and the head side chamber. Due to the difference, the two spool valves in the main passage are opened at the same time, and the metering knob is closed.
  • this actuator control device was installed in each of a plurality of pump systems, one for each pump system. It is equipped with a noise valve. And, in this configuration, each operating valve has its own noise. Since no bypass valves were installed and one bypass valve was installed for each one-pump system, the control for noise control was eliminated. You can try to make a good idea.
  • this actuator control device is located on a construction machine equipped with two motors, one for left-hand drive and one for right-hand drive.
  • the two operating valves for controlling the pump pressure fluid supplied to the two traveling motors are provided in a common pump system. .
  • this actuator control device is a pump for supplying pump pressure fluid to a cylinder type actuator of a construction machine.
  • a flow coupling valve is placed in the part where the system and the pump system that supplies the pump pressure fluid overnight to the motor-type actuator, and where they merge. It is what has been done. In this configuration, even with one flow connection valve, a sufficient pump pressure fluid is supplied to the operation valve that is provided one-to-one with the actuator. Can be paid.
  • this actuator control device is a Boom cylinder, a Stick cylinder, a Note cylinder, and a left-hand drive.
  • FIG. 1 is a hydraulic circuit diagram showing a first embodiment of a control device for an actuator according to the present invention.
  • FIG. 2 is a cross-sectional view showing an example of a flow-amplification type port valve in the hydraulic circuit of the above.
  • FIG. 3 is a hydraulic circuit diagram showing a second embodiment of the actuator control device according to the present invention.
  • FIG. 4 is a hydraulic circuit diagram showing a third embodiment of the actuator control device according to the present invention.
  • FIG. 5 is a circuit diagram showing an example of a hydraulic circuit of a conventional construction machine. Best form to carry out the invention
  • FIG. 1 shows an actuator for controlling the hydraulic shovel overnight, in which the hydraulic oil as the hydraulic oil in the tank 11 is sucked and discharged.
  • Pumps 12 and 13 and six actuators operated by pump pressure oil supplied from these pumps 12 and 13.
  • control valves 15bo, 15st, 15bu 15trL, 15trR, and 15sw that control each actuating unit on a one-to-one basis are included.
  • a control valve 15 is provided.
  • the actuator 14bo controlled by the operating valve 15bo is a cylinder, and the actuator controlled by the operating valve 15st is 14st. It is a cylinder and is controlled by the operating valve 15bu.
  • the actuator 14bu is a socket cylinder and is controlled by the operating valve 15trL.
  • the motor operated 14trL is a left running motor
  • the motor operated 14trR controlled by a control valve 15trR is a right running motor. Therefore, the actuator 14sw controlled by the operating valve 15sw is the upper rotation mode.
  • the operating valves 15bo, 15st and 15bu of the working machine are provided between the pumps 12 and 13 and the actuators 14bo, 14st and 14bu to respond to the input signal.
  • a flow-amplification type meter-out knob 17 with a line relief function that controls the flow rate in response to a force signal is installed separately from each other. It has been broken.
  • the operation valves 15 trL and 15 trR of the traveling system are provided between the pumps 12 and 13 and the actuators 14trL and 14trR, and flow according to the input signal.
  • One metering knob 18 for volume control, and 14trL, 14trR and And a flow-amplification type filter knob 19 which is provided between the power supply 11 and the flow-amplifier and which controls the flow in response to an input signal. It is set up.
  • the swirl-type operation valve 15sw is provided between the pumps 12 and 13 and the actuator 14sw and is used to control the flow rate according to the input signal.
  • a flow amplifier with a relief function and a flow knob 17 are separated from each other.
  • One-sided cylinder type actuator such as a boom cylinder, a disc cylinder and a socket cylinder.
  • 14st and 14bu each of which controls the flow rate on the main side of the meter, is a 2 port 2 position type sprue which is divided into two. This is a valve between the pump 1213 and the two chambers 14bo, 14st, and 14bu, each of which has a single-sided, cylinder-type actuator.
  • Each of these spool valves is installed in the intake circuit.
  • a left-running motor, a right-running motor, and a top-turning motor are similar to those of the night-time type.
  • 14 trL, 14trR, 14sw The metering knob 18, which controls the flow rate on each of the metering sides, is assembled into a single 3-port, 3-position spool valve. It is.
  • 1 1 Ket Cylinder and Load Swing Type Actuator such as Mooring for Upper Rotation Mooring of 14bo, 14st, 14bu, 14sw
  • the metering knob 17 that controls the flow rate on each side is a flow-amplification type poppet with a line-relief function that is divided into two parts. These valves are located in the main circuit between the tank 11 and the two rooms 14k, 14st, 14bu, and 14sw. ⁇ Each set valve is provided.
  • the flow rate control is performed on the outer side of each of the actuators 14trL and 14trR, such as a motor for left-hand running and a motor for right-hand running, respectively.
  • the meter out valve 19 to be controlled is not a valve with a line relief function, but a two-part flow amplification type poppet valve is Each is provided in each of the main passages between the link 11 and the two rooms, 14trL and 14trR, respectively.
  • pump lines 21 and 22 in the control valve 15 serve as passages for the pump pressure oil supplied from the two pumps 12 and 13.
  • a flow connection valve 23 is provided between the two pumps, and the flow connection valve 23 separates the pump pressure oil supplied from the two pumps 12 and 13. Closed position cl to be supplied to the operation valves 15bo, 15st, 15bu, 15trL, 15trR, and 15sw by separate pump lines 24 and 25, and two pumps 12
  • the pump pressure oil from 13 is joined and the pump lines 24 and 25 are connected and supplied to the operation valves 15bo, 15st, 15bu, 15tr L, 15trR and 15sw. It has an opening position op to be supplied.
  • each of the pump systems is provided with one bypass valve 31 and 32 for each one pump system, and these bypass valves 31 and 32 are all open.
  • the pump pressure oil is drained to the tank 11 and the operation valves 15bo, 15st, 15bu, 15trL, By preventing the pressurized supply of pump pressure oil to the 15trR, 15sw, and by switching to the cut-off position during operation of the actuator Pressurize and supply pump pressure oil to each operation valve.
  • a relief valve 35 is provided between the two pump lines 26, 27 and the evening line 33 via two check valves 34.
  • the relief pressure as an oil pressure source is set by the relief valve 35.
  • All of the above-mentioned metal knobs 16 and 18, the metal outlet knobs 17 and 19, the flow coupling valve 23 and the bypass valves 31 and 32 are all electromagnetic.
  • the operating part that is, a solenoid, is equipped with an operating lever (not shown) for operating each actuator remotely. It is controlled by an electric signal output from a controller (not shown) which is electrically connected to the power supply. It is recommended that the control valves 16 and 18 and the control valves 17 and 19 and the flow connection valve 23 be controlled proportionally according to the electric signal. No.
  • Fig. 2 shows the flow-amplification type with line relief function used for the control valves 15bo, 15st, 15bu, and 15sw.
  • -Evening knob 17 is shown, and a neurot valve 41 that continuously controls the flow rate by an electric signal from the outside and a neurot valve
  • the port valve 42 which controls the flow rate drained to the tank 11 by the neurot control by the port valve 41, and the actuator valve
  • a pressure control valve 43 having a line relief function for drain control of the port valve 42 by an excessive load pressure is provided.
  • the port valve 42 also has a make-up function that is opened by a negative pressure generated in a circuit connected to the port valve 42. .
  • the poppet valve 42 is provided with one end of a sheet valve body 44 with a nozzle.
  • a control section 45 is formed, a slit 46 is formed in the peripheral surface of the central portion in the axial direction, and a valve sheet is connected to the tank side communication path 47 at the other end.
  • a drain flow rate control section 49 which is fitted and disengaged with respect to the toe section 48 is formed, and a plurality of notches 50 are formed in the drain flow rate control section 49.
  • the nozzle control unit 45 faces the spring chamber 51, and the sheet valve body 44 is valved by the coil spring 52 contained in the spring chamber 51. It is pressed to the sheet part 48 side, and is urged in the closing direction.
  • the port valve 42 is connected from the spring chamber 51 to the tank side passage 47 by using the sheet valve body 44 as a means for controlling the outlet.
  • the above-mentioned NOS port valve 41 is provided in a passage 53 provided in the above manner.
  • the pilot valve 41 is an electromagnetic actuator, that is, a solenoid. It has a node 54, and the opening is controlled proportionally by staking it to a non-illustrated beam by an electric signal from a controller not shown.
  • the sheet valve body is controlled.
  • the opening of the 44 notches 50 is controlled to the equilibrium position.
  • Valve 43 is interposed.
  • the pressure control valve 43 includes a pressure receiving portion 57 that detects the oil pressure in the negative pressure passage 56 that is communicated with the actuator and a pressure receiving portion 57, and the pressure receiving portion 57 and the pressure receiving portion 57.
  • the poppet valve part 58 installed in the pipe, the coil spring 60 for pressing the poppet valve part 58 against the sheet part 59, and the coil spring An adjustment screw 61 for adjusting the biasing force of 60 is provided.
  • the pressure control valve 43 has a force for pressing the pressure receiving portion 57 by the negative pressure of the negative pressure passage 56 greater than the biasing force of the coil 60. Then, the poppet valve portion 58 is separated from the seat portion 59 and the tank side passageway 47 passes through the passage 55 from the spring chamber 51 of the port valve 42 via the passageway 55. Controls the amount of drain flow to the drain.
  • the normal position of the sheet valve body 44 is adjusted by the biasing force of the coil spring 60 adjusted by the adjusting screw 61 of the pressure control valve 43.
  • the pressure control valve 43 has a line relief function that can adjust the set pressure of the negative pressure passage 56.
  • the flow-amplification type meter valve 19 used for the operating valves 15trL and 15trR of the traveling system is the same as that of the above-mentioned valve 17. This is a structure excluding the pressure control valve 43.
  • a command electric signal corresponding to the operation direction and the operation amount is transmitted.
  • the controller is input to the controller, and the controller is programmed with the command electric signal from the operating lever and the controller.
  • the drive electric signal corresponding to the control mode based on the software is transmitted to each of the operation valves 15bo, 15st, 15bu, 15trL, 15trR, and 15sw.
  • the solenoids are output to the solenoids 16 and 18 and the relays 17 and 19, respectively, and are controlled individually.
  • the pumps were installed on the meter side between pumps 12 and 13 and the actuators 14bo, 14st, 14bu, 14trL, 14trR, and 14sw, respectively.
  • the spool valve controls the flow rate directly by the controller.
  • a port valve 42 provided on the meter side between the tank 11 and the 14bo, 14st, 14bu, 14trL, 14trR, 14sw is provided with a control valve.
  • the flow rate is controlled indirectly via a nozzle port valve 41 controlled by a pump.
  • the inner knob 16 shown at the bottom of the operating valve 15 st is opened, and the mail shown at the upper part is opened.
  • the valve 16 shown at the top of the control valve 15 st was closed, and the valve 16 shown at the top was closed and shown at the bottom.
  • the meter out knob 17 is controlled to be closed, the stick cylinder operates in the extension direction. If controlled in the opposite way, the stick cylinder operates in the contraction direction.
  • all of the meta-in knobs 16 and the meta-valve 17 have an e-mail ring function proportional to the lever operation amount. Therefore, the cylinder operation speed can also be controlled.
  • each block is one block, and when these operating valves 15bo and 15st are controlled to operate the actuators 14bo and 14st, the signal is output. Is detected, electricity is supplied to the flow rate coupling valve 23 for supplying the hydraulic oil, and the flow rate coupling valve 23 is switched to the open position op.
  • the hydraulic oil discharged from the pump line 21 and the hydraulic oil discharged from the pump 13 to the pump line 22 are combined, and the pump oil is mixed. Operate two pump oils via line 24 Supply to valves 15bo and 15st.
  • the required flow rate can be met with a total of seven operation valves including the flow connection valve 23, and the number of operation valve stations is reduced by IJ compared to the conventional method.
  • the connection of the roll valve 15 can be achieved.
  • the main knobs 16 and 18 and the main outlets 16 and 18 are provided. Since the separation between 17 and 19 can be controlled, it can only be realized under the narrow range of conditions where there is a good point where the current situation is affected.
  • the controller can be used flexibly to address this shortcoming.
  • the meter outlet 17 is a flow-amplified type valve whose flow rate can be controlled by a nozzle port valve 41 as shown in FIG. A set valve 42 is provided, and a line relief valve function is also provided by a pressure control valve 43 where necessary for the flow amplification type port valve 42. Because of this structure, there is no need to provide an independent and expensive line relief valve. Since it also has a backup function, it is suitable for control on the main side.
  • each of the operation valves 15bo 15st, 15bu, 15trL, 15trR, and 15sw has its own noise control.
  • the embodiment shown in FIG. 1 described above controls the pump pressure oil supplied to the two traveling motors for left traveling and right traveling. Since the two control valves 15trL and 15trR to be controlled are installed in a common pump system using a common pump line 25, the left and right travels are performed. There is no danger that different pump systems will be supplied with different pump flow rates for the two running motors for different running systems.
  • the driving motors are always driven at the same speed due to the left and right running systems where each motor is driven, especially the tuning function of the left and right rollers. This eliminates the need for the conventional straight-running throttle valve 1 str.
  • a pump system that supplies pump pressurized oil to the cylinder type actuators 14b, 14st, and 14bu of construction machinery, and a motor type actuator. Since the pump system that supplies the pump pressure oil to 14trL, 14trR, and 14sw overnight, the flow coupling valve 23 was placed in the part where the pump system oil merged.
  • One of the flow connection valves 23 also has the operation valves 15bo, 15st, 15bu, and 15sw provided in a one-to-one relationship with the actuating units 14bo, 14st, 14bu, 14trL, 14trR, and 14sw. Sufficient pump pressure oil can be supplied to trL, 15trR, and 15sw.
  • FIG. 3 shows a hydraulic system according to another embodiment. This implementation depends on the features and negatives of the boom cylinder, stick cylinder, and socket cylinder.
  • the pump line 21 drawn from the left pump 12 passes through the pump line 63 via the pump line 63. It is always connected to the control valve 15st of the stick cylinder, and the other flow valves 15bo, 15bu, 15trL, 15trR, and 15sw of the other actuators are connected to the first flow rate.
  • the pump oil is supplied from the pump line 65 via the joint valve 64 and the pump lines 67 and 68 via the second flow rate joint valve 66.
  • the pump 13 on the right side is operated by the pump cylinders 22 and 65 to operate the cylinder cylinder and the bucket cylinder.
  • the other operation valves 15st, 15trL, 15trR, and 15sw of the actuator are connected to the third flow connection provided between the pump lines 22 and 67.
  • the pressurized oil is supplied via the joint valve 69 and the second flow rate joint valve 66.
  • Table 1 shows the contents arranged for the opening degrees of, 66 and 69.
  • FIG. 4 shows an embodiment of the hydraulic circuit in which the first flow connection valve 64 is omitted.
  • the embodiment shown in FIG. 4 is a two-pump oil connection to the operation valves 15bo and 15st of the boom cylinder and the stick cylinder.
  • the pressure loss of the pump 12 on one side is slightly increased due to the two flow connection valves 6669 through the two flow connection valves 6669, as shown in FIG. 3.
  • B There is a tendency to increase compared to when the valve 64 is opened alone.
  • the implementation shown in Fig. 4 is considered. In the form of Is beneficial.
  • one pump 12 is connected to the stick cylinder operating valve 15 st.
  • the operating valves for the left-running motor, right-running motor and top-rotating motor 15trL, 15trR Supply pressure oil to 15sw, and other pumps 13 are always connected to the operation valves 15b0, 15st of the boom cylinder and bucket cylinder.
  • the number of operating valve stations can be reduced as compared with the conventional hydraulic system, and all operating valves and flow can be reduced.
  • the control valve 15 having a built-in quantity coupling valve can also perform control as a whole.
  • flexible control that does not fix the relationship between the meter's inner knobs 16 and 18 and the meter-out knobs 17 and 19 is possible.
  • the actuator control device of the present invention can be applied to other construction machines such as hydraulic shovels, bulldozers, loaders, etc.
  • Other industrial machines with multiple actuators that are activated by pump pressure fluid supplied from multiple pumps. Can be widely applied.

Abstract

Montée entre une pluralité de pompes (12, 13) et une pluralité d'actionneurs (14bo, 14st, 14bu, 14trL, 14trR, 14sw) adaptés pour être actionnés par une huile sous pression pompée se trouve une soupape de régulation (15) dans laquelle est logée une pluralité de soupapes de commande (15bo, 15st, 15bu, 15trL, 15trR, 15sw) régulant les actionneurs en une correspondance de un à un. Une soupape (23) de combinaison de débit, montée dans la soupape de commande (15), est disposée entre les conduits de pompe (21, 23) afin d'acheminer une huile sous pression à partir d'une pluralité de pompes (12, 13). Cette soupape (23) de combinaison de débit présente une position fermée (c1) dans laquelle l'huile sous pression pompée provenant de la pluralité de pompes (12, 13) est séparée pour être acheminée jusqu'aux soupapes de commande individuelles, et une position ouverte (op) dans laquelle les écoulements d'huile sont combinés pour être acheminés jusqu'aux soupapes de commande individuelles. Ainsi, le nombre d'ensembles de soupapes de commande est réduit pour obtenir un contrôleur compact.
PCT/JP1999/006004 1999-03-18 1999-10-29 Controleur d'actionneur WO2000055509A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11072924A JP2000266009A (ja) 1999-03-18 1999-03-18 アクチュエータ制御装置
JP11/72924 1999-03-18

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WO2000055509A1 true WO2000055509A1 (fr) 2000-09-21

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Cited By (3)

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Publication number Priority date Publication date Assignee Title
EP2947331A4 (fr) * 2013-01-17 2016-10-12 Jiangsu Hengli Highpressure Oil Cylinder Co Ltd Appareil hydraulique basé sur un mode de commande de confluence
EP2669527A3 (fr) * 2012-05-31 2017-03-08 Liebherr-France SAS Bloc de commande hydraulique et système hydraulique
JP2020094642A (ja) * 2018-12-13 2020-06-18 キャタピラー エス エー アール エル 建設機械の油圧制御回路

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JP4850575B2 (ja) * 2006-04-27 2012-01-11 株式会社タダノ 油圧アクチュエータ制御装置
KR20150129072A (ko) * 2011-12-28 2015-11-19 두산인프라코어 주식회사 굴삭기 선회모터의 메이크업 유량조절장치
KR101970110B1 (ko) * 2018-11-14 2019-04-17 두산인프라코어 주식회사 굴삭기 선회모터의 메이크업 유량조절장치
JP2022047627A (ja) * 2020-09-14 2022-03-25 川崎重工業株式会社 液圧駆動システム

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JPS5420225U (fr) * 1977-07-12 1979-02-09
JPS5983807A (ja) * 1982-11-04 1984-05-15 Daikin Ind Ltd 二流量合流回路
JPH0489934A (ja) * 1990-08-01 1992-03-24 Hitachi Constr Mach Co Ltd 土木・建設機械の油圧駆動装置
JPH04136512A (ja) * 1990-09-28 1992-05-11 Komatsu Ltd 油圧回路に用いる操作弁装置

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JPS5420225U (fr) * 1977-07-12 1979-02-09
JPS5983807A (ja) * 1982-11-04 1984-05-15 Daikin Ind Ltd 二流量合流回路
JPH0489934A (ja) * 1990-08-01 1992-03-24 Hitachi Constr Mach Co Ltd 土木・建設機械の油圧駆動装置
JPH04136512A (ja) * 1990-09-28 1992-05-11 Komatsu Ltd 油圧回路に用いる操作弁装置

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2669527A3 (fr) * 2012-05-31 2017-03-08 Liebherr-France SAS Bloc de commande hydraulique et système hydraulique
EP2947331A4 (fr) * 2013-01-17 2016-10-12 Jiangsu Hengli Highpressure Oil Cylinder Co Ltd Appareil hydraulique basé sur un mode de commande de confluence
US9988792B2 (en) 2013-01-17 2018-06-05 Jiangsu Hengli Highpressure Oil Cylinder Co., Ltd. Hydraulic apparatus based on confluence control mode
JP2020094642A (ja) * 2018-12-13 2020-06-18 キャタピラー エス エー アール エル 建設機械の油圧制御回路
WO2020119947A3 (fr) * 2018-12-13 2020-07-23 Caterpillar Sarl Circuit de commande hydraulique pour engin de chantier
CN113167056A (zh) * 2018-12-13 2021-07-23 卡特彼勒Sarl 用于工程机器的液压控制回路
CN113167056B (zh) * 2018-12-13 2022-04-12 卡特彼勒Sarl 用于工程机器的液压控制回路
DE112019005768B4 (de) 2018-12-13 2022-10-06 Caterpillar Sarl Hydrauliksteuerkreis für eine baumaschine
JP7198072B2 (ja) 2018-12-13 2022-12-28 キャタピラー エス エー アール エル 建設機械の油圧制御回路
US11629479B2 (en) 2018-12-13 2023-04-18 Caterpillar Sarl Hydraulic control circuit for a construction machine

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