WO2011058681A1 - 油圧制御装置 - Google Patents
油圧制御装置 Download PDFInfo
- Publication number
- WO2011058681A1 WO2011058681A1 PCT/JP2010/004401 JP2010004401W WO2011058681A1 WO 2011058681 A1 WO2011058681 A1 WO 2011058681A1 JP 2010004401 W JP2010004401 W JP 2010004401W WO 2011058681 A1 WO2011058681 A1 WO 2011058681A1
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- WIPO (PCT)
- Prior art keywords
- pressure
- hydraulic
- flow rate
- accumulator
- oil
- Prior art date
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/14—Energy-recuperation means
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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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
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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
- E02F9/2058—Electric or electro-mechanical or mechanical control devices of vehicle sub-units
- E02F9/2095—Control of electric, electro-mechanical or mechanical equipment not otherwise provided for, e.g. ventilators, electro-driven fans
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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
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
- 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
- E02F9/2278—Hydraulic circuits
- E02F9/2289—Closed circuit
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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
- E02F9/2278—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
- 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
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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
- F15B2211/20507—Type of prime mover
- F15B2211/20515—Electric motor
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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
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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
- F15B2211/20561—Type of pump reversible
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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
- F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
- F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
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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
- F15B2211/27—Directional control by means of the pressure source
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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
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30505—Non-return valves, i.e. check valves
- F15B2211/30515—Load holding 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/625—Accumulators
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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
- F15B2211/60—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
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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
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. torque or rotational speed
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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
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/785—Compensation of the difference in flow rate in closed fluid circuits using differential actuators
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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
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/88—Control measures for saving energy
Definitions
- the present invention relates to a hydraulic control device.
- the hydraulic system is a hydraulic control valve (pressure control valve, electromagnetic switching) that controls at least one of the pressure, direction, and flow rate of the hydraulic oil discharged from the hydraulic pump toward the hydraulic actuator (single rod hydraulic cylinder, hydraulic motor, etc.). Valve, flow control valve, etc.) and is widely used in construction machinery, industrial vehicles, industrial machinery, ships, and the like.
- the hydraulic control device that constitutes a part of the hydraulic system may include an accumulator as an auxiliary power source in consideration of emergency measures such as downsizing of the hydraulic pump, failure of the hydraulic pump or power failure. is there.
- the accumulator is a hydraulic device that stores hydraulic energy, and a gas type, a spring type, or a weight type can be adopted as the energy storage method. Further, the following method can be adopted as the accumulator pressure accumulation method.
- the first pressure accumulating method is a method of accumulating pressure by installing a dedicated pressure accumulating pump separately from the hydraulic pump that drives the hydraulic actuator.
- paragraph 0006 of Patent Document 1 describes that “in a conventional hydraulic circuit, a dedicated electric motor must be installed for driving an accumulator pump that accumulates an actuator”.
- the second pressure accumulation method is a method of accumulating pressure when the hydraulic pump is idle. This is adopted when the flow rate to the main circuit may be small due to equipment having a large number of holding operations, or when the pressure accumulation mode is provided during the cycle operation in which the hydraulic actuator is operated intermittently.
- paragraph 0039 of Patent Document 2 describes that “the pressure oil supplied from the pressure oil supply device is stored in the pressure oil chamber of the accumulator during the idle time of the single rod hydraulic cylinder portion”.
- the third pressure accumulating method is a method of accumulating using surplus oil generated when the hydraulic actuator is driven by the pressure oil discharged from the hydraulic pump.
- the pressure accumulating means uses a surplus oil from the hydraulic control means and pressurizes, for example, a single rod hydraulic cylinder that boosts the surplus oil by the oil pressure of the surplus oil, "Accumulating pressure oil (excess oil in the case of a single rod hydraulic cylinder) that has been boosted by a high-pressure pump that boosts pressure oil by the driving force of a hydraulic motor that generates driving force by the oil pressure of the oil” Yes.
- the first to third pressure accumulation methods have the following problems.
- the present invention stably performs accumulator pressure accumulation regardless of the load and operating speed even when surplus oil is hardly generated by adopting a pump speed control system using a variable speed motor. It is aimed.
- the main present invention for solving the above problems includes a hydraulic pump that is driven by a variable speed motor and discharges an amount of pressure oil corresponding to the number of rotations of the variable speed motor, and the pressure discharged from the hydraulic pump.
- a hydraulic pressure circuit that includes an accumulator and a drive hydraulic circuit that drives the hydraulic actuator by supplying and receiving oil to and from the hydraulic actuator, accumulates the pressure oil in the accumulator, and accumulates the accumulator in a predetermined case
- a pressure accumulating hydraulic circuit configured to supply the actuator to the actuator, an input port, a first output port, and a second output port, the input port from the hydraulic pump of the drive hydraulic circuit
- a first main oil passage through which discharged pressure oil flows, and the first output port is connected to an oil passage leading to the accumulator of the accumulator hydraulic circuit;
- the pressure port is connected to a second main oil passage that supplies pressure oil to the hydraulic actuator of the drive hydraulic circuit, and of the pressure oil that flows into the input port, Pressure oil flows out from the first output port, and an
- the flow rate control mechanism is arranged on the pressure accumulation oil path from the first main oil path to the accumulator.
- the accumulator pressure-accumulating pump is not required, and the hydraulic control device and, consequently, the hydraulic system can be made compact.
- the hydraulic control apparatus may further include a communication / breaker that selectively connects or disconnects the first main oil passage and the second main oil passage.
- the hydraulic control apparatus further includes a pressure detector that detects a pressure accumulated in the accumulator, and the communication / breaker includes the first detector when the pressure detected by the pressure detector exceeds a predetermined pressure.
- the first main oil passage and the second main oil passage are communicated with each other when the pressure detected by the pressure detector is lower than a predetermined pressure. And may be configured to be blocked.
- pressure oil is directly supplied from the hydraulic pump to the hydraulic actuator via the first main oil passage and the second main oil passage by the communication / breaker.
- the pressure oil can be reliably supplied to the input port of the flow rate control mechanism.
- pressure oil is bypass-supplied from the input port of the flow rate control mechanism to the hydraulic actuator via the second output port and the second main oil passage. For this reason, the operation of the hydraulic actuator can be continued even during the pressure accumulation of the actuator.
- the flow rate control mechanism may be a priority valve.
- the input port constitutes the input port of the flow rate control mechanism
- the output port constitutes the first output port of the flow rate control mechanism
- the input port A pressure control valve connected to an input port of the flow rate control valve, and an output port constituting a second output port of the flow rate control mechanism, wherein the pressure control valve includes the flow rate control valve and the pressure control valve.
- FIG. 1 is a diagram showing a configuration of a hydraulic control apparatus that controls a hydraulic actuator according to Embodiment 1 of the present invention.
- the hydraulic control device 2 shown in FIG. 1 adopts a pump rotation speed control method for energy saving, low noise, and compactness of the hydraulic system.
- the pump rotation speed control method is a control method in which the rotation speed of the hydraulic pump is made variable by a variable speed motor.
- the pump rotation speed control method for example, the pump rotation speed can be decelerated in the pressure holding state to save energy.
- the hydraulic control device 2 includes an accumulator 70 as an auxiliary power source in an emergency, and controls the driving of a single rod type hydraulic cylinder 10 employed as a hydraulic actuator, and the accumulator from the reversible rotary pump 21.
- the pressure accumulation to 70 and the discharge of the pressure accumulation oil from the accumulator 70 to the hydraulic cylinder 10 are controlled.
- the hydraulic control device 2 drives the hydraulic cylinder 10 from the reversible rotary pump 21 during pressure accumulation from the reversible rotary pump 21 to the accumulator 70 regardless of the load of the hydraulic cylinder 10 and the operating speed. Therefore, the pressure oil surely flows through both the oil system of the drive hydraulic circuit for the purpose and the oil system of the pressure accumulation hydraulic circuit for accumulating the accumulator 70. Note that the hydraulic cylinder 10 is continuously driven regardless of whether or not the accumulator 70 accumulates pressure.
- the hydraulic control device 2 performs reversible rotation in order to supply only the minimum necessary pressure oil from the reversible rotary pump 21 toward the hydraulic cylinder 10.
- the configuration is such that the pressure oil is supplied only to the oil system of the drive hydraulic circuit for driving the hydraulic cylinder 10 from the pump 21.
- the overall configuration of the hydraulic control apparatus 2 includes a pump unit 20a, a valve unit 30a, an accumulator 70, an oil tank 50, and a control panel 60.
- the drive hydraulic circuit according to the present invention includes the pump unit 20a, a part of the valve unit 30a, and the oil tank 50.
- the pressure accumulating hydraulic circuit according to the present invention includes the pump unit 20a, a part of the valve unit 30a, and the accumulator 70.
- the pump unit 20a includes a reversible rotary pump 21, a variable speed motor 22, a rotational speed detector 23, and check valves 24a and 24b.
- the reversible rotary pump 21 has two input / output ports and is a hydraulic pump that reverses the direction in which the pressure oil flows by changing the rotation direction of the drive shaft.
- the reversible rotary pump 21 is also a variable displacement pump. For example, in order to minimize energy loss (reduction of pump capacity) in the pressure holding state (when the pump flow rate is unnecessary), an operation command from the controller 61 is used.
- a solenoid valve is provided for switching the pump capacity determined in advance based on the solenoid valve.
- One end of the main oil passage 301a is connected to one input / output port 210a of the reversible rotary pump 21, and one end of the main oil passage 301b is connected to the other input / output port 210b of the reversible rotary pump 21. Yes.
- the other end of the main oil passage 301a is connected to the head chamber 11 of the hydraulic cylinder 10, and the other end of the main oil passage 301c communicated with or cut off from the main oil passage 301b by the electromagnetic switching valve 35 is the rod chamber of the hydraulic cylinder 10. 12 is connected.
- the main oil passage 301a is oil disposed between one input / output port 210a of the reversible rotary pump 21 and the head chamber 11 of the hydraulic cylinder 10 via the pilot check valve 31a.
- the pressure oil discharged from the input / output port 210a is supplied to the head chamber 11 through the pilot check valve 31a, and the pressure oil from the head chamber 11 to the input / output port 210a through the pilot check valve 31a is supplied.
- the main oil passage 301b is an oil passage disposed between the other input / output port 210b of the reversible rotary pump 21 and the electromagnetic switching valve 35, and pressure oil discharged from the input / output port 210b is supplied to the electromagnetic switching valve. 35, an oil passage that supplies the rod chamber 12 via the pilot check valve 31b and receives pressure oil from the rod chamber 12 toward the input / output port 210b via the pilot check valve 31b and the electromagnetic switching valve 35. That is, the main oil passage 301b corresponds to only the first main oil passage according to the present invention in which the pressure oil discharged from the input / output port 210b flows when the electromagnetic switching valve 35 is in the shut-off position. When 35 is a communication position, it can be the first main oil passage or the second main oil passage according to the present invention.
- the main oil passage 301c is an oil passage disposed from the electromagnetic switching valve 35 through the pilot check valve 31b to the rod chamber 12 of the hydraulic cylinder 10, and is supplied to the rod chamber 12 through the pilot check valve 31b.
- the oil passage receives pressure oil from the rod chamber 12 through the pilot check valve 31b and the electromagnetic switching valve 35 to the input / output port 210b. That is, the main oil passage 301c corresponds to only the second main oil passage according to the present invention that supplies pressure oil to the hydraulic cylinder 10 when the electromagnetic switching valve 35 is in the shut-off position. In the case of the position, it can be either the first main oil passage or the second main oil passage according to the present invention.
- the variable speed motor 22 is a motor that drives the drive shaft of the reversible rotary pump 21 and is an AC servo motor that switches the rotation speed based on a rotation speed command from the servo drive unit 62.
- the variable speed motor 22 includes a rotation speed detector 23 using a pulse generator for variable speed servo control of the servo drive unit 62.
- the variable speed motor 22 uses a synchronous motor, but an induction motor may be used.
- the rotational speed detector 23 is not limited to the pulse generator, and an encoder that detects the rotational position may be adopted.
- the valve unit 30a includes a three-port hydraulic switching valve 32, a check valve 33a, relief valves 34a and 34b, and an electromagnetic switching valve 35 as a configuration of a driving hydraulic circuit that drives the hydraulic cylinder 10.
- the hydraulic switching valve 32 has two inlet ports X and Y and one outlet port Z, and is provided between the main oil passage 301 a and the main oil passage 301 c and the oil tank 50.
- the hydraulic switching valve 32 has an inlet port X connected to the main oil passage 301a, an inlet port Y connected to the main oil passage 301c, and an outlet port Z connected to the oil passage on the oil tank 50 side. That is, when the rod of the hydraulic cylinder 10 is moved forward (moved from the head side to the rod side), the inlet port Y and the outlet port Z communicate with each other by the hydraulic pressure of the pressure oil supplied to the inlet port X. When the 10 rod is retracted (moved from the rod side to the head side), the inlet port X and the outlet port Z communicate with each other by the hydraulic pressure of the pressure oil supplied to the inlet port Y.
- the check valve 33 a is provided on an oil discharge path (return oil path) 501 between the output port Z of the hydraulic switching valve 32 and the oil tank 50.
- the inlet port of the check valve 33 a is connected to the output port Z of the hydraulic switching valve 32, and the outlet port of the check valve 33 a is connected to the oil tank 50. That is, the check valve 33 a plays a role of preventing a back flow from the oil tank 50 to the output port Z of the hydraulic pressure switching valve 32.
- the electromagnetic switching valve 35 is a valve corresponding to the communication / breaker according to the present invention that selectively connects or disconnects the main oil passage 301b and the main oil passage 301c.
- the electromagnetic switching valve 35 is provided between the pilot check valve 31b and the input / output port 210b of the reversible rotary pump 21 on the main oil passage 301c.
- the electromagnetic switching valve 35 communicates the main oil passage 301b and the main oil passage 301c, and the input / output port 210b of the reversible rotary pump 21 and the rod chamber 12 of the hydraulic cylinder 10 Allow bidirectional flow of pressure oil between (on).
- the valve unit 30a includes a priority valve 36, an electromagnetic switching valve 37, pilot check valves 31a, 31b, and 31c, and a pressure sensor 40 as a configuration of an accumulator driving circuit that uses and accumulates the accumulator 70. .
- the priority valve 36 has an inlet port 361, a priority port 362, and a bypass port 363, and is provided on a pressure accumulation oil passage 701 from the main oil passage 301b to the accumulator 70.
- the reason that the pressure accumulation oil passage 701 starts from the main oil passage 301b instead of the main oil passage 301a is that excess oil is likely to be generated when the hydraulic cylinder 10 moves backward from the rod chamber 12 toward the head chamber 11. In addition, it is easy to ensure the pressure accumulation flow of the accumulator 70.
- the starting point of the pressure accumulating oil passage 701 may be provided in the main oil passage 301a. Even in this case, the same function as when the starting point of the pressure accumulating oil passage 701 is provided in the main oil passage 301b is exhibited.
- the priority valve 36 is a flow rate set to the priority port 362 out of the pressure oil flowing into the inlet port 361 regardless of the flow rate (inflow rate) flowing into the inlet port 361 and the load of each port 362, 363.
- the pressure oil of (accumulation flow rate) flows in preference to the priority port 362, and the excess flow pressure oil obtained by subtracting the pressure accumulation flow from the inflow rate flows toward the bypass port 363.
- 50 (L / min) is set as the rated flow rate per unit time (minute) of the inlet port 361
- 10 (L / min) is set as the rated flow rate per unit time (minute) of the priority port 362
- 40 (L / min) is set as the rated flow rate per unit time (min) of the bypass port 363.
- the flow rate of the pressure oil flowing into the inlet port 361 per unit time (minute) is 20 (L)
- 10 (L) of the pressure oil flowed into the inlet port 361 Is discharged from the priority port 362
- excess 10 (L) of hydraulic oil is discharged from the bypass port 363.
- the inlet port 362 when the flow rate of the pressure oil flowing into the inlet port 361 per unit time (minute) is 5 (L), the inlet port 362 regardless of the magnitude of the load between the priority port 362 and the bypass port 363. All of the 5 (L) pressure oil that has flowed into 361 flows out of the priority port 362.
- the electromagnetic switching valve 37 selects (off) the oil path from the pilot check valves 31a, 31b, 31c to the oil discharge path 501 when using the accumulated oil of the accumulator 70, and drives the hydraulic cylinder 10 with a pump. Is configured to select (ON) an oil passage from the pressure accumulation oil passage 701 to the pilot check valves 31a, 31b, 31c.
- the state of the electromagnetic switching valve 37 shown in FIG. 1 indicates an off state.
- the pilot check valve 31a is provided in the main oil passage 301a, and its inlet port is disposed on the reversible rotary pump 21 side, and its outlet port is provided on the hydraulic cylinder 10 side.
- the pilot port is connected to the electromagnetic switching valve 37.
- the pilot check valve 31b is provided in the main oil passage 301c, its inlet port is disposed on the reversible rotary pump 21 side, and its outlet port is provided on the hydraulic cylinder 10 side.
- the pilot port is connected to the electromagnetic switching valve 37.
- the pilot check valves 31a and 31b are configured to supply pressure oil from the head chamber 11 and the rod chamber 12 of the hydraulic cylinder 10 to the input / output ports 210a and 210b of the reversible rotary pump 21 when using the accumulator oil of the accumulator 70.
- the bidirectional flow of pressure oil between the head chamber 11 and the rod chamber 12 of the hydraulic cylinder 10 and the input / output ports 210a and 210b of the reversible rotary pump 21 is reduced. Play a role to allow.
- the pilot check valve 31c is provided between the accumulator 70 and the main oil passage 301a, and its inlet port is disposed on the accumulator 70 side, and its outlet port is provided on the hydraulic cylinder 10 side.
- the pilot port is connected to the electromagnetic switching valve 37.
- the pilot check valve 31c allows the flow of the accumulated oil from the accumulator 70 to the main oil passage 301a when using the accumulated oil of the accumulator 70, and the main oil from the accumulator 70 when driving the hydraulic cylinder 10 with a pump. It plays a role of blocking the flow of the accumulated oil toward the path 301a.
- the pressure sensor 40 is provided on the pressure accumulation oil passage 701 and indirectly detects the pressure accumulated in the accumulator 70.
- the pressure sensor 40 may be configured to directly detect the pressure accumulated in the accumulator 70. Further, not only the pressure sensor 40 but also a pressure switch may be adopted.
- the valve unit 30a includes relief valves 34a, 34b, 34c, and 34d, stop valves 38a and 38b, and throttles 39a, 39b, and 39c as protection for the above-described configuration.
- the relief valves 34a, 34b, 34c, and 34d monitor the hydraulic pressure of the pressure oil that flows to the position where the relief valves 34a, 34b, 34c, and 34d are provided. It plays a role in discharging pressure oil.
- the stop valves 38a and 38b serve to communicate / shut off the flow of pressure oil by manual operation when the accumulator is repaired.
- the throttles 39a, 39b, and 39c serve to limit the flow rate of the pressure oil that flows to the position where the throttles 39a, 39b, and 39c are provided.
- the control panel 60 includes a controller 61 and a servo drive unit 62, and controls the hydraulic control (pump rotation speed control, accumulator pressure accumulation, discharge, etc.) of the entire hydraulic control device 2.
- the controller 61 has at least a CPU and a memory, and outputs a position command for instructing a rod position of the hydraulic cylinder 10 from an external device (not shown) and rod position information of the hydraulic cylinder 10 detected by the position sensor 13. Obtained and configured to feedback control the rod position of the hydraulic cylinder 10. Specifically, every time the controller 61 acquires the rod position information, the controller 61 generates a rotation speed command for the variable speed motor 22 corresponding to the deviation between the position command and the rod position information, and outputs it to the servo drive unit 62.
- the controller 61 outputs an operation command for switching on and off the solenoid valve provided in the reversible rotary pump 21.
- the capacity of the reversible rotary pump 21 can be changed. For example, when the pressure is high such as during accumulator accumulation, the motor capacity is reduced by selecting a small capacity, and when the pressure is low such as during normal operation, the motor capacity is selected by reducing the motor capacity.
- the controller 61 acquires the pressure information of the accumulator 70 detected by the pressure sensor 40 and determines whether or not the accumulator 70 needs to accumulate pressure.
- the controller 61 monitors whether the pressure information detected by the pressure sensor 40 exceeds a predetermined pressure of the accumulator 70, and the pressure information detected by the pressure sensor 40 indicates the predetermined pressure of the accumulator 70. If it falls below the value, it is determined that the accumulator 70 needs to be accumulated. In addition, when it is determined that the accumulator 70 needs to accumulate pressure, the controller 61 outputs an operation command that instructs a predetermined switching operation of the electromagnetic switching valve 35.
- the servo drive unit 62 has at least a CPU and a memory, obtains a rotational speed command generated from the controller 61 and rotational speed information detected by the rotational speed detector 23, and rotates the variable speed motor 22. It is configured to feedback control the number. Specifically, the servo drive unit 62 generates an inverter command corresponding to the deviation between the rotational speed command and the rotational speed information and outputs it to the variable speed motor 22 every time the rotational speed information is acquired.
- the accumulator 70 adopts a gas type in this embodiment, but may adopt a weight type or a spring type. *
- the pilot check valves 31a and 31b permit the bidirectional flow of the pressure oil between the head chamber 11 and the rod chamber 12 of the hydraulic cylinder 10 and the input / output ports 210a and 210b of the reversible rotary pump 21. Yes.
- the pilot check valve 31 c blocks the flow of accumulated oil from the accumulator 70 toward the head chamber 11 of the hydraulic cylinder 10.
- the reversible rotary pump 21 inputs and outputs the pressure oil in the rod chamber 12 through the pilot check valve 31b and the electromagnetic switching valve 35. Suction is performed from the port 210b, and pressure oil is discharged from the input / output port 210a to the head chamber 11 through the pilot check valve 31a. Since the pressure receiving area of the head chamber 11 is larger than the pressure receiving area of the rod chamber 12, the same amount of pressure oil discharged toward the head chamber 11 does not return from the rod chamber 12. The pressure oil sucked into 210b is insufficient. In order to compensate for the shortage of the pressure oil, the pressure oil stored in the auxiliary oil tank 50 is sucked into the input / output port 210b of the reversible rotary pump 21 via the check valve 24b.
- the reversible rotary pump 21 sucks the pressure oil in the head chamber 11 from the input / output port 210a via the pilot check valve 31a, Pressure oil is discharged from the input / output port 210b toward the rod chamber 12 through the electromagnetic switching valve 35 and the pilot check valve 31b.
- the oil pressure switching valve 32 communicates the input port X and the output port Z in order to drain the excess oil from the head chamber 11 to the oil tank 50 through the oil discharge passage 501.
- the electromagnetic switching valve 37 selects an oil path from the pilot check valves 31a, 31b, 31c toward the oil drain path 501 according to an operation command from the controller 61.
- the pilot check valves 31 a and 31 b block the flow of pressure oil from the head chamber 11 and the rod chamber 12 of the hydraulic cylinder 10 toward the input / output ports 210 a and 210 b of the reversible rotary pump 21.
- the pilot check valve 31 c permits the flow of the accumulated oil from the accumulator 70 toward the head chamber 11 of the hydraulic cylinder 10.
- a loop-like hydraulic circuit including a stop valve 38a, a pilot check valve 31c, a hydraulic cylinder 10, a check valve 33c, and a throttle 39a is configured, and the pressure oil discharged from the rod chamber 12 is supplied to the check valve 33c and the throttle.
- the electromagnetic switching valve 35 permits a bidirectional flow of pressure oil between the input / output port 210b of the reversible rotary pump 21 and the rod chamber 12 of the hydraulic cylinder 10 according to an operation command from the controller 61. Yes. Further, the electromagnetic switching valve 37 selects an oil path from the pressure accumulation oil path 701 to the pilot check valves 31a, 31b, 31c according to an operation command from the controller 61.
- the operating pressure of the hydraulic cylinder 10 is surely lower than the hydraulic pressure of the priority port 362 of the priority valve 36, and therefore the input / output port 210 b of the reversible rotary pump 21. Therefore, no pressure oil flows toward the priority valve 36. Further, the pressure oil does not flow from the rod chamber 12 of the hydraulic cylinder 10 toward the bypass port 363 of the priority valve 36 via the pilot check valve 31b. Further, a check valve 33b for preventing backflow is provided on the priority port 362 side, so that the accumulated oil does not flow from the accumulator 70 toward the priority valve 36.
- the controller 61 monitors whether or not the pressure information detected by the pressure sensor 40 exceeds a predetermined pressure of the accumulator 70. When the pressure information detected by the pressure sensor 40 is lower than the predetermined pressure of the accumulator 70, the controller 61 determines that accumulation of the accumulator 70 is necessary. Then, the controller 61 outputs an operation command for blocking the flow of the pressure oil from the input / output port 210 b of the reversible rotary pump 21 to the rod chamber 12 of the hydraulic cylinder 10 to the electromagnetic switching valve 35.
- the main oil passage 301b and the main oil passage 301c are blocked, and the pressure oil discharged from the input / output port 210b of the reversible rotary pump 21 is directly directed toward the rod chamber 12 of the hydraulic cylinder 10 by the electromagnetic switching valve 35. It does not flow but flows toward the input port 361 of the priority valve 36.
- the controller 61 determines that the pressure information detected by the pressure sensor 40 exceeds a predetermined pressure and the accumulator 70 should complete the pressure accumulation. At this time, the controller 61 outputs an operation command to the electromagnetic switching valve 35 so as to return to the state before the start of pressure accumulation. That is, the bidirectional flow of pressure oil between the input / output port 210b of the reversible rotary pump 21 and the rod chamber 12 of the hydraulic cylinder 10 is permitted. Then, as before the pressure accumulation start, the operating pressure of the hydraulic cylinder 10 becomes lower than the pressure of the priority port 362 of the priority valve 36, so that the pressure oil does not flow toward the priority valve 36. Thereby, the pressure accumulation of the accumulator 70 is completed.
- the priority valve 36 is provided on the pressure accumulation oil passage 701 from the main oil passage 301 b to the accumulator 70.
- a stable flow rate of pressure oil can be used for accumulating the accumulator 70 regardless of the load of the priority port 362 and the bypass port 363 and the operating speed of the hydraulic cylinder 10.
- the pressure-accumulation pump for the accumulator 70 is not required, and the hydraulic control device 2 and thus the hydraulic system can be made compact.
- FIG. 2 is a diagram illustrating a configuration of a hydraulic control apparatus that controls the hydraulic actuator according to the second embodiment of the present invention.
- the hydraulic control device 4 shown in FIG. 2 is different from the hydraulic control device 2 shown in FIG. 1 in that the priority valve 36 is replaced with a flow rate control mechanism in which a flow rate adjustment valve 364 and a pressure control valve 365 are combined. It is. Except for the above differences, the valve unit 30b shown in FIG. 2 is the same as the valve unit 30a shown in FIG.
- the flow rate adjustment valve 364 is provided on the pressure accumulation oil passage 701 between the main oil passage 301 b and the accumulator 70.
- the flow rate adjustment valve 364 has a rated flow rate (L) per unit time (minute). The flow rate of the flow rate that flows into the input port of the flow rate adjustment valve 364 is adjusted to the above-described rated flow rate per unit time, and then the pressure oil of the rated flow rate flows out toward the accumulator 70.
- the pressure control valve 365 is branched from a pressure accumulation oil passage 701 between the main oil passage 301b and the flow rate adjustment valve 364, and is on the oil passage toward the main oil passage 301c between the pilot check valve 31b and the electromagnetic switching valve 35. Is provided.
- the pressure control valve 365 adjusts the flow rate when the hydraulic pressure at the input port of the flow rate adjustment valve 364 exceeds the predetermined pressure for the input port and the hydraulic pressure at the output port of the flow rate adjustment valve 364 exceeds the predetermined pressure for the output port.
- the excess flow rate of the hydraulic oil obtained by subtracting the rated flow rate of the flow rate adjustment valve 364 from the flow rate flowing toward the input port of the valve 364 flows out toward the rod chamber 12 of the hydraulic cylinder 10. That is, the branch path including the pressure control valve 365 serves as the bypass port 363 of the priority valve 36.
- a flow rate control mechanism having a function equivalent to that of the priority valve 36 is used, and the same effect as in the first embodiment can be obtained.
- FIG. 3 is a diagram showing a configuration of a hydraulic control apparatus that controls the hydraulic actuator according to the third embodiment of the present invention.
- the hydraulic control device 6 shown in FIG. 3 is different from the hydraulic control device 2 shown in FIG. 1 in that the hydraulic control device 2 shown in FIG. 3, the hydraulic control device 6 shown in FIG. 3 always returns the pressure oil discharged from the oil pump 25 to the oil tank 50 via the hydraulic cylinder 10. Therefore, the hydraulic control device shown in FIG. 3 is replaced with a hydraulic pump 25 in which the flow of pressure oil discharged from the reversible rotary pump 21 flows in a single direction, as compared with the hydraulic control device 2 shown in FIG.
- the hydraulic switching valve 32 is replaced with a 4-port electromagnetic switching valve 28, the check valve 33a, the relief valves 34a and 34b, and the check valves 24a and 24b are omitted, and a protective relief valve 26 is newly provided.
- the other pump unit 20b and valve unit 30c shown in FIG. 3 are the same as the pump unit 20a and valve unit 30a shown in FIG.
- the oil pump 25 is provided with only one discharge port.
- the oil pump 25 is provided with a solenoid valve for controlling the rotational speed by a variable speed motor 22 connected to the drive shaft and for switching a predetermined pump capacity. ing.
- the 4-port electromagnetic switching valve 28 has two ports X and Z arranged on the main oil passage 301a and two ports Y and W arranged on the main oil passage 301b.
- the port X is connected to the input port of the pilot check valve 31a, and the port Z is connected to the discharge port of the hydraulic pump 25.
- the port Y is connected to the electromagnetic switching valve 35, and the port W is connected to the oil tank 50.
- the relief valve 26 is a pressure control valve that discharges the pressure oil discharged from the hydraulic pump 25 to the oil tank 50 when the hydraulic pressure at the discharge port of the hydraulic pump 25 exceeds a predetermined pressure.
- the hydraulic control device according to the present invention is beneficial when used in a hydraulic control device that controls the rotational speed of a hydraulic pump in order to supply pressure oil to the hydraulic actuator in a necessary amount.
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Abstract
Description
[油圧制御装置の全体構成及び機能]
図1は、本発明の実施の形態1に係る油圧アクチュエータを制御する油圧制御装置の構成を示した図である。
主油路301bは、可逆回転形ポンプ21の他方の入出力ポート210bから電磁切換弁35までの間に配設される油路であり、入出力ポート210bから吐出される圧油を電磁切換弁35、パイロットチェック弁31bを介してロッド室12に供給するとともに、ロッド室12からパイロットチェック弁31b、電磁切換弁35を介して入出力ポート210bに向う圧油を受給する油路である。つまり、主油路301bは、電磁切換弁35が遮断位置の場合には、入出力ポート210bから吐出される圧油が流れる本発明に係る第1の主油路のみに相当し、電磁切換弁35が連通位置の場合には、本発明に係る第1の主油路とも第2の主油路ともなりえる。
パイロットチェック弁31aは、主油路301aに設けられ、その入口ポートが可逆回転形ポンプ21側に配置され、その出口ポートが油圧シリンダ10側に設けられるように構成されている。なお、そのパイロット口は電磁切換弁37と接続されている。
さらに、コントローラ61は、圧力センサ40により検出されるアキュムレータ70の圧力情報を取得して、アキュムレータ70の蓄圧の要否を判別する。具体的には、コントローラ61は、圧力センサ40により検出される圧力情報がアキュムレータ70の所定圧力を上回るか否かを監視しており、圧力センサ40により検出される圧力情報がアキュムレータ70の所定圧力を下回る場合には、アキュムレータ70の蓄圧が必要であると判別する。また、コントローラ61は、アキュムレータ70の蓄圧が必要であると判別した場合には、電磁切換弁35の所定の切り替え操作を指示する操作指令を出力する。
図1に示した油圧制御装置2の油圧シリンダ10駆動時の動作について説明する。
油圧シリンダ10駆動時の場合、電磁切換弁35は、コントローラ61からの操作指令により、主油路301bと主油路301cとが連通し、可逆回転形ポンプ21の入出力ポート210bと油圧シリンダ10のロッド室12との間の圧油の双方向の流れを許可している。また、電磁切換弁37は、コントローラ61からの操作指令により、蓄圧用油路701からパイロットチェック弁31a、31b、31cに向う油路を選択している。これにより、パイロットチェック弁31a、31bは、油圧シリンダ10のヘッド室11及びロッド室12と可逆回転形ポンプ21の入出力ポート210a、210bとの間の圧油の双方向の流れを許可している。また、パイロットチェック弁31cは、アキュムレータ70から油圧シリンダ10のヘッド室11に向う蓄圧油の流れを遮断している。
図1に示した油圧制御装置2のアキュムレータ70使用時の動作について説明する。なお、アキュムレータ70使用時とは、可逆回転形ポンプ21や可変速モータ22の故障や停電などの緊急時にアキュムレータ70に蓄圧されている蓄圧油が利用される状況や、可逆回転形ポンプ21が吐出する圧油の流量を増大するためにアキュムレータ70に蓄圧されている蓄圧油が補助的に利用される状況のことを指している。本実施形態では、前者を想定しており、特に、油圧シリンダ10のロッドをヘッド室11側からロッド室12側に向けて前進させる過程において可逆回転形ポンプ21の故障などが発生した場合に、アキュムレータ70の蓄圧油を利用してロッドをロッド室12の端まで完全に前進させる緊急動作を想定している。
図1に示した油圧制御装置2のアキュムレータ70蓄圧時の動作について説明する。
以上、本実施の形態によれば、可変速モータ22によるポンプ回転数制御方式を採用した油圧システムである場合において、主油路301bからアキュムレータ70へ向う蓄圧用油路701上にプライオリティ弁36を配置したことによって、優先ポート362やバイパスポート363の負荷や油圧シリンダ10の作動速度に関らず、安定した流量の圧油をアキュムレータ70の蓄圧に利用することができる。また、アキュムレータ70の蓄圧専用ポンプが不要となり、油圧制御装置2、ひいては油圧システムのコンパクト化を実現することができる。
図2は、本発明の実施の形態2に係る油圧アクチュエータを制御する油圧制御装置の構成を示した図である。
図3は、本発明の実施の形態3に係る油圧アクチュエータを制御する油圧制御装置の構成を示した図である。
このため、図3に示す油圧制御装置は、図1に示す油圧制御装置2と対比して、可逆回転形ポンプ21が吐出される圧油の流れが単一方向に流れる油圧ポンプ25に置き換わり、油圧切換弁32が4ポート電磁切換弁28に置き換わり、チェック弁33a、リリーフ弁34a、34b、及びチェック弁24a、24bが省略され、保護用のリリーフ弁26が新たに設けられている。なお、図3に示すその他のポンプユニット20b及びバルブユニット30cの構成は、図1に示すポンプユニット20a及びバルブユニット30aと同様である。
10 油圧シリンダ
11 ヘッド室
12 ロッド室
13 位置センサ
20a、20b ポンプユニット
21 可逆回転形ポンプ
22 可変速モータ
23 回転数検出器
24a、24b チェック弁
25 油圧ポンプ
26 リリーフ弁
28 4ポート電磁切換弁
30a、30b、30c バルブユニット
31a、31b、31c パイロットチェック弁
32 油圧切換弁
33a、33b、33c チェック弁
34a、34b、34c、34d リリーフ弁
38a、38b ストップ弁
39a、39b、39c 絞り
35 電磁切換弁
36 プライオリティ弁
361 入力ポート
362 優先ポート
363 バイパスポート
37 電磁切換弁
301a 主油路
301b 主油路(第1の主油路)
301c 主油路(第2の主油路)
40 圧力センサ
50 油タンク
501 排油路
60 制御盤
61 コントローラ
62 サーボドライブユニット
70 アキュムレータ
701 蓄圧用油路
Claims (5)
- 可変速モータにより駆動され、該可変速モータの回転数に応じた量の圧油を吐出する油圧ポンプを含み、該油圧ポンプから吐出される圧油を油圧アクチュエータとの間で供給及び受給して該油圧アクチュエータを駆動する駆動油圧回路と、
アキュムレータを含み、前記圧油を該アキュムレータに蓄積しかつ所定の場合に該アキュムレータに蓄積された圧油を前記油圧アクチュエータに供給するよう構成された蓄圧油圧回路と、
入力ポートと、第1の出力ポートと、第2の出力ポートと、を有し、該入力ポートが前記駆動油圧回路の前記油圧ポンプから吐出される圧油が流れる第1の主油路に接続され、該第1の出力ポートが前記蓄圧油圧回路の前記アキュムレータに至る油路に接続され、該第2の出力ポートが前記駆動油圧回路の前記アクチュエータに圧油を供給する第2の主油路に接続され、かつ該入力ポートに流入される圧油のうち、予め設定される前記アキュムレータの蓄圧用流量の圧油が該第1の出力ポートより流出し、該入力ポートに流入される流量から該蓄圧用流量を差し引いた余剰流量の圧油が前記第2の出力ポートより流出するように構成されている流量制御機構と、
を備える、油圧制御装置。 - 前記第1の主油路と前記第2の主油路とを択一的に連通又は遮断する連通/遮断器をさらに備える、請求項1に記載の油圧制御装置。
- 前記アキュムレータに蓄圧される圧力を検出する圧力検出器をさらに備え、
前記連通/遮断器は、
前記圧力検出器により検出される圧力が所定圧力を上回る場合には前記第1の主油路と前記第2の主油路とを連通し、前記圧力検出器により検出される圧力が所定圧力を下回る場合には前記第1の主油路と前記第2の主油路とを遮断するように構成されている、請求項2に記載の油圧制御装置。 - 前記流量制御機構は、プライオリティ弁である、請求項1乃至3のいずれか1項に記載の油圧制御装置。
- 前記流量制御機構は、
入力ポートが前記流量制御機構の入力ポートを構成しており、出力ポートが前記流量制御機構の第1の出力ポートを構成している流量調整弁と、
入力ポートが前記流量調整弁の入力ポートと接続され、出力ポートが前記流量制御機構の第2の出力ポートを構成している圧力制御弁とを備え、
前記圧力制御弁は、
前記流量調整弁及び前記圧力制御弁の入力ポートの油圧が所定の圧力を上回り、かつ前記流量調整弁の出力ポートの油圧が所定の圧力を上回る場合には前記圧力制御弁の入力ポートと該圧力制御弁の出力ポートとを連通させるように構成されている、
請求項1乃至3のいずれか1項に記載の油圧制御装置。
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EP10829649.2A EP2500583B1 (en) | 2009-11-10 | 2010-07-06 | Hydraulic pressure control device |
US13/505,412 US9217446B2 (en) | 2009-11-10 | 2010-07-06 | Hydraulic controller |
CN201080047935.5A CN102656372B (zh) | 2009-11-10 | 2010-07-06 | 油压控制装置 |
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KR101862868B1 (ko) * | 2011-10-14 | 2018-07-06 | 에스케이이노베이션 주식회사 | 유압구동기를 이용한 유압제어장치 |
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Also Published As
Publication number | Publication date |
---|---|
JP5368943B2 (ja) | 2013-12-18 |
EP2500583B1 (en) | 2015-04-01 |
US20120240566A1 (en) | 2012-09-27 |
US9217446B2 (en) | 2015-12-22 |
CN102656372B (zh) | 2015-01-07 |
EP2500583A4 (en) | 2014-03-26 |
CN102656372A (zh) | 2012-09-05 |
JP2011102608A (ja) | 2011-05-26 |
KR20120080645A (ko) | 2012-07-17 |
KR101381072B1 (ko) | 2014-04-04 |
EP2500583A1 (en) | 2012-09-19 |
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