WO2010058632A1 - 油圧アクチュエータ及び油圧振動試験装置 - Google Patents

油圧アクチュエータ及び油圧振動試験装置 Download PDF

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Publication number
WO2010058632A1
WO2010058632A1 PCT/JP2009/063695 JP2009063695W WO2010058632A1 WO 2010058632 A1 WO2010058632 A1 WO 2010058632A1 JP 2009063695 W JP2009063695 W JP 2009063695W WO 2010058632 A1 WO2010058632 A1 WO 2010058632A1
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Prior art keywords
hydraulic
sensor
pressure chamber
piston
pressure
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PCT/JP2009/063695
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English (en)
French (fr)
Japanese (ja)
Inventor
繁 松本
博至 宮下
一宏 村内
光央 角田
Original Assignee
国際計測器株式会社
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.)
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Application filed by 国際計測器株式会社 filed Critical 国際計測器株式会社
Priority to CN200980146327.7A priority Critical patent/CN102216750B/zh
Priority to KR1020117011087A priority patent/KR101305982B1/ko
Publication of WO2010058632A1 publication Critical patent/WO2010058632A1/ja

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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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M7/00—Vibration-testing of structures; Shock-testing of structures
    • G01M7/02—Vibration-testing by means of a shake table
    • G01M7/022—Vibration control arrangements, e.g. for generating random vibrations
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/02—Servomotor systems with programme control derived from a store or timing device; Control devices therefor
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M7/00—Vibration-testing of structures; Shock-testing of structures
    • G01M7/02—Vibration-testing by means of a shake table
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
    • G01N3/00—Investigating strength properties of solid materials by application of mechanical stress
    • G01N3/32—Investigating strength properties of solid materials by application of mechanical stress by applying repeated or pulsating forces
    • G01N3/36—Investigating strength properties of solid materials by application of mechanical stress by applying repeated or pulsating forces generated by pneumatic or hydraulic means
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
    • G01N2203/00—Investigating strength properties of solid materials by application of mechanical stress
    • G01N2203/0001—Type of application of the stress
    • G01N2203/0005—Repeated or cyclic
    • G01N2203/0008—High frequencies from 10 000 Hz
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
    • G01N2203/00—Investigating strength properties of solid materials by application of mechanical stress
    • G01N2203/003—Generation of the force
    • G01N2203/0042—Pneumatic or hydraulic means
    • G01N2203/0048—Hydraulic means

Definitions

  • the present invention relates to a hydraulic actuator and a hydraulic vibration test apparatus capable of high-speed inversion driving.
  • a vibration test apparatus that vibrates a subject with a hydraulic cylinder
  • a device using a volumetric pump and a servo valve as described in JP-A-2000-2617 is known.
  • Such a vibration test apparatus can vibrate the subject at a high frequency while applying a large load to the subject.
  • An example of a circuit diagram of a hydraulic vibration testing apparatus using a servo valve is shown in FIG.
  • the pump unit 110 drives the volume pump body 111 by a motor 112, and is connected to a hydraulic circuit between the hydraulic oil tank 120 and the servo valve 140. Note that the rotation direction of the motor 112 is limited to one direction, that is, the motor 112 can only rotate forward. Further, the rotation speed of the motor 112 is kept substantially constant.
  • the pump unit 110 has a function of only sending hydraulic oil from the hydraulic oil tank 120 to the servo valve 140, and its flow rate is kept substantially constant.
  • the cylinder unit 130 includes a sleeve 131, a piston 132 that can move within the sleeve 131, and a piston rod 133 that projects from one side of the piston 132 to the outside of the sleeve 131.
  • a vibration table 150 is fixed to the tip of the piston rod 133.
  • the inside of the sleeve 131 is divided into a first pressure chamber 131a and a second pressure chamber 131b by a piston 132.
  • the first pressure chamber 131a and the second pressure chamber 131b are filled with hydraulic oil.
  • the first pressure chamber 131a and the second pressure chamber 131b are connected to the servo valve 140 via pipes 161 and 162, respectively.
  • Servo valve 140 is used to switch the hydraulic oil sent from pump unit 110 to either pipe 161 or 162 and to control the hydraulic pressure of the hydraulic oil sent to the pipe.
  • the servo valve 140 connects a pipe through which hydraulic oil is not sent to a pipe 164 that leads to the hydraulic oil tank 120.
  • the switching operation and hydraulic pressure adjustment operation of the servo valve 140 are controlled by the controller 102.
  • the hydraulic circuit When the hydraulic circuit is configured so that the hydraulic oil is sent from the pump unit 110 to the pipe 161, the hydraulic oil is supplied to the first pressure chamber 131a, and the internal pressure of the first pressure chamber 131a increases. Thereby, the piston 132 is pushed down toward the second pressure chamber 131b, and the vibration table 150 is lowered. At this time, the hydraulic oil in the second pressure chamber 131 b is returned to the hydraulic oil tank 120 via the pipe 162 and the servo valve 140. On the other hand, when the hydraulic circuit is configured so that the hydraulic oil is sent from the pump unit 110 to the pipe 162, the hydraulic oil is supplied to the second pressure chamber 131b, and the internal pressure of the second pressure chamber 131b increases.
  • the piston 132 is pushed up toward the first pressure chamber 131a, and the vibration table 150 is raised.
  • the hydraulic oil in the first pressure chamber 131 a is returned to the hydraulic oil tank 120 via the pipe 161 and the servo valve 140.
  • the pipe 163 from the pump unit 110 to the servo valve 140 and the pipe 164 from the servo valve 140 to the hydraulic oil tank 120 are connected by a bypass pipe 165. All of the hydraulic oil supplied by the pump unit 110 does not go to the hydraulic cylinder unit 130, and a part is returned to the hydraulic oil tank 120 via the bypass pipe 165.
  • check valves 166 and 167 are provided in the respective pipes.
  • the controller 102 controls the servo valve 140 to periodically switch the hydraulic oil to be sent to the first pressure chamber 131a or the second pressure chamber 131b.
  • the vibration table 150 is reciprocated.
  • a part of the hydraulic fluid circulated at a high pressure and a large flow rate is sent to the hydraulic cylinder unit 130 by the servo valve 140. Therefore, the first pressure chamber 131a and the second pressure chamber
  • the pressure in the pressure chamber to which the hydraulic oil is sent rises instantaneously to a high pressure, and the moving direction of the vibration table 150 is switched without causing a time lag. For this reason, it is possible to vibrate the vibration table at a high frequency.
  • the vibration table 150 is provided with an acceleration sensor 103, and a signal indicating the acceleration detected by the acceleration sensor 103 is supplied to the controller 102.
  • the controller 102 calculates the displacement, speed, or acceleration of the vibration table 150 based on the detection result of the acceleration sensor 103, and controls the servo valve 140 so that the vibration table 150 vibrates with a desired displacement, speed, or acceleration waveform. It is possible.
  • a hydraulic actuator using a servo valve in order to supply a desired pressure to a hydraulic cylinder instantaneously and stably, only a part of the hydraulic energy supplied by the pump is driven while continuously driving a pump having a sufficiently large flow rate.
  • a configuration for supplying to a hydraulic cylinder has been adopted. For this reason, the amount of energy consumed by the vibration test apparatus using such a hydraulic actuator is much larger than the energy required for exciting the subject, and wasted energy is consumed.
  • a large-capacity hydraulic oil tank is required to circulate the hydraulic oil by such a pump.
  • the present invention has been made to solve the above problems, and does not require a large-sized pump or hydraulic oil tank, and is a high-output hydraulic actuator capable of high-speed response, and a high frequency while applying a large load to the subject.
  • An object of the present invention is to provide a vibration test apparatus capable of vibrating a subject.
  • a hydraulic pump capable of reversing operation, a piston, and a piston are connected to a sleeve and a piston whose inner space is divided into a first pressure chamber and a second pressure chamber, and a tip projects out of the sleeve.
  • a hydraulic cylinder unit including a piston rod, a first pipe connecting the first pressure chamber to the first intake / exhaust port, and a second pipe connecting the second pressure chamber to the second intake / exhaust port;
  • An actuator is provided that moves the piston up and down by alternately applying hydraulic pressure to the first and second pressure chambers by reverse operation.
  • the actuator further includes a bypass pipe that connects the first and second pipes, and an accumulator that is provided in the middle of the bypass pipe and applies back pressure to the first and second pressure chambers.
  • a hydraulic pump that reversely operates in both forward and reverse directions is used.
  • This hydraulic pump is directly connected to the hydraulic cylinder unit without passing through the servo valve, and drives the hydraulic cylinder unit.
  • a large pump such as that used for a servo valve actuator or No hydraulic oil tank is required.
  • the energy consumption by the actuator according to the embodiment of the present invention is not so large as compared with the energy required for the vibration of the subject. Energy consumption can be greatly reduced.
  • a hydraulic pump that operates in reverse is characterized in that when the pump operation direction is reversed, the pressure of the hydraulic oil decreases, and a time lag of about several tens of milliseconds occurs before the pressure increases sufficiently. For this reason, if the pump is simply connected to the hydraulic cylinder unit, the time lag will occur when the pump drive direction is reversed and the moving direction of the vibration table is switched, and the vibration table is moved during that time. I can't. For this reason, the subject cannot be vibrated at a high frequency (several tens of Hz or more) such that this time lag cannot be ignored.
  • the actuator according to the embodiment of the present invention since the accumulator applies back pressure to the first pressure chamber and the second pressure chamber of the hydraulic cylinder unit via the bypass pipe, the operation direction of the pump is reversed. However, the pressure of the hydraulic oil hardly decreases, and the time lag is extremely small. For this reason, in the actuator according to the embodiment of the present invention, the subject can be vibrated at a high frequency.
  • the back pressure applied by the accumulator to the first pressure chamber and the second pressure chamber is set larger than the minimum pressure required for driving the cylinder of the hydraulic cylinder unit. In this case, there is almost no response delay due to the hydraulic system.
  • the hydraulic pump used in the hydraulic actuator according to the embodiment of the present invention is typically a piston pump.
  • the actuator preferably further includes a servo motor as a drive source for the hydraulic pump.
  • the hydraulic actuator according to the embodiment of the present invention may further include a sensor that detects the movement of the movable portion of the hydraulic actuator (or the object to be driven by the hydraulic actuator) and a controller that controls the servo motor.
  • the controller can control the servo motor based on the detection result of the sensor.
  • the sensor preferably includes any one of a displacement sensor, a speed sensor, an acceleration sensor, and a load sensor.
  • the controller can control the servo motor to drive the piston in accordance with a predetermined displacement, velocity or acceleration waveform based on the detection result of the sensor.
  • the sensor may be detachable from a hydraulic actuator (specifically, a controller).
  • the sensor may include a load sensor.
  • the controller can control the servo motor so that the load detected by the load sensor changes according to a predetermined waveform based on the detection result of the sensor.
  • a vibration test apparatus including the hydraulic actuator described above and a vibration table provided at the tip of the piston rod.
  • the vibration test apparatus preferably further includes a sensor provided on the vibration table and a controller for controlling the servo motor.
  • the senor provided on the vibration table may include a sensor that measures the displacement, speed, or acceleration of the vibration table.
  • the controller can control the servo motor to drive the vibration table according to a predetermined waveform of displacement, speed, or acceleration based on the detection result of the sensor.
  • the senor may include a load sensor that measures a load applied to the subject.
  • the controller can control the servo motor to apply a load to the subject according to a predetermined waveform based on the detection result of the sensor.
  • FIG. 1 is a schematic circuit diagram of a vibration test apparatus according to an embodiment of the present invention.
  • FIG. 2 is a diagram showing a schematic configuration for applying a static load to a subject in the vibration test apparatus according to the embodiment of the present invention.
  • FIG. 3 is a graph plotting acceleration and displacement of the vibration table in the embodiment of the present invention.
  • FIG. 4 is a graph plotting acceleration and displacement of the vibration table in the comparative example.
  • FIG. 5 is a schematic circuit diagram of a conventional hydraulic vibration test apparatus using a servo valve.
  • FIG. 1 is a circuit diagram of a vibration test apparatus according to the present embodiment.
  • the vibration test apparatus 1 includes a pump unit 10, a hydraulic oil tank 20, a hydraulic cylinder unit 30, a vibration table 50, and an accumulator 70.
  • the vibration table 50 is moved up and down by the hydraulic pressure supplied to the hydraulic cylinder unit 30, whereby the subject W fixed on the vibration table 50 is vibrated.
  • the pump unit 10 has a pump body 11 and a servo motor 12.
  • the servo motor 12 is driven by an alternating current output from the servo amplifier 4.
  • the servo motor 12 is configured to be able to rotate the drive shaft 12a in both forward and reverse directions and to precisely adjust the rotational speed of the drive shaft 12a.
  • the servo motor 12 is a low-inertia AC servo motor capable of high-output and high-repetition-rate inversion driving.
  • the pump body 11 is a piston pump capable of sending hydraulic oil from the first intake / exhaust port 11a to the second intake / exhaust port 11b or from the second intake / exhaust port 11b to the first intake / exhaust port 11a.
  • the flow rate and direction of the hydraulic oil supplied by the pump body 11 can be changed. For example, when the servo motor 12 is driven in reverse at a constant cycle, the flow rate and direction of the hydraulic oil flowing between the first intake / exhaust port 11a and the second intake / exhaust port 11b change periodically.
  • the cylinder unit 30 includes a sleeve 31, a piston 32 that can move within the sleeve 31, and a piston rod 33 that projects from one surface of the piston 32 to the outside of the sleeve 31.
  • a vibration table 50 is fixed to the tip of the piston rod 33.
  • the inside of the sleeve 31 is divided into a first pressure chamber 31a and a second pressure chamber 31b by a piston 32.
  • the first pressure chamber 31a and the second pressure chamber 31b are filled with hydraulic oil.
  • the first pressure chamber 31a and the second pressure chamber 31b are connected to the first intake / exhaust port 11a and the second intake / exhaust port 11b of the pump body 11 through pipes 61 and 62, respectively.
  • a high-pressure hose that can withstand a pressure increase (approximately several tens of MPa) of hydraulic oil generated when the vibration table 50 is moved (not causing elastic deformation) is used.
  • the hydraulic oil tank 20 is connected to the first pressure chamber 31a and the second pressure chamber 31b via check valves 63 and 64, respectively.
  • the check valves 63 and 64 open when the internal pressures of the first pressure chamber 31a and the second pressure chamber 31b become lower than the hydraulic pressure (for example, atmospheric pressure) in the hydraulic oil tank 20, respectively. Hydraulic oil is supplied to the pipes 61 and 62.
  • the check valve 63 or the check valve 64
  • the pressure chamber 31a is opened from the working oil tank 20.
  • the hydraulic oil moves to (or the pressure chamber 31b).
  • the hydraulic oil is filled into the pressure chambers 31a and 31b as follows.
  • the first pressure chamber 31a and the second pressure chamber 31b are provided with a valve (not shown) for bleeding air.
  • the pump unit 10 is set so that hydraulic oil and air are sent from the second intake / exhaust port 11b to the first intake / exhaust port 11a.
  • the air in the second pressure chamber 31b and the pipe 62 is released from the valve of the first pressure chamber 31a through the pipe 61.
  • the check valve 64 opens and the hydraulic oil in the hydraulic oil tank 20 passes through the pipes 62 and 61 to the first.
  • the pressure chamber 31a is filled.
  • the valve of the first pressure chamber 31a is closed, the valve of the second pressure chamber 31b is opened, and the hydraulic oil is sent from the first intake / exhaust port 11a to the second intake / exhaust port 11b.
  • the pump unit 10 is driven so that Then, the air in the second pressure chamber 31b and the pipe 62 escapes from the valve of the second pressure chamber 31b, and the piston 32 rises and the hydraulic oil filled in the first pressure chamber 31a is pushed out to the pipe 61. It is.
  • the pump unit 10 When raising the vibration table 50, the pump unit 10 is driven so that the hydraulic oil moves from the first intake / exhaust port 11a to the second intake / exhaust port 11b. Then, the hydraulic oil is supplied to the second pressure chamber 31b through the pipe 62, the piston 32 is pushed into the first pressure chamber 31a, and the piston rod 33 and the vibration table 50 are raised. The hydraulic oil in the first pressure chamber 31a moves to the pump unit 10 via the pipe 61 as the piston 32 moves, and is sent from the pump unit 10 to the second pressure chamber 31b via the pipe 62.
  • the pump unit 10 When the vibration table 50 is lowered, the pump unit 10 is driven so that the hydraulic oil moves from the second intake / exhaust port 11b to the first intake / exhaust port 11a. At this time, since the hydraulic oil is supplied to the first pressure chamber 31a via the pipe 61, the piston 32 is pushed into the second pressure chamber 31a, and the piston rod 33 and the vibration table 50 are lowered. The hydraulic oil in the second pressure chamber 31b moves to the pump unit 10 via the pipe 62 as the piston 32 moves, and is further sent from the pump unit 10 to the first pressure chamber 31a via the pipe 61.
  • the acceleration sensor 3 is attached to the vibration table 50 of the vibration test apparatus 1 according to the present embodiment.
  • the acceleration sensor 3 is connected to the controller 2, and a signal indicating the acceleration detected by the acceleration sensor 3 is supplied to the controller 2.
  • the controller 2 calculates the displacement, speed, or acceleration of the vibration table 50 based on the detection result of the acceleration sensor 3, and sets a target value to be given to the servo amplifier 4 based on the calculation result. send.
  • the servo amplifier 4 generates an alternating current having a period and amplitude set based on a target value designated by the controller 2 from the power supplied from the power supply 5 and outputs the alternating current to the servo motor 12.
  • the vibration table 50 can be vibrated with a predetermined displacement, speed, or acceleration amplitude, for example.
  • a displacement sensor or a speed sensor may be used.
  • the vibration test apparatus 1 supplies hydraulic oil to the first pressure chamber 31a or the second pressure chamber 31b of the hydraulic cylinder unit 30 by the pump unit 10 that can be driven in both forward and reverse directions.
  • the vibration table 50 is moved in the vertical direction, and the subject W fixed thereon is vibrated.
  • the vibration test apparatus 1 includes a bypass pipe 65 that bypasses the pipes 61 and 62, and an accumulator 70 provided in the middle of the bypass pipe 65.
  • the accumulator 70 is a pressure vessel in which a layer of a gas having a predetermined pressure (dry nitrogen gas or the like) is formed, and the first pressure chamber 31a or the second pressure chamber of the hydraulic cylinder unit 30 is connected via pipes 61 and 62.
  • the pressure chamber 31b is pressurized with a constant pressure.
  • the pipe on the side not supplied with hydraulic oil (the pipe 61 when the vibration table 50 is raised and the pipe 62 when the vibration table 50 is lowered) has a low pressure close to atmospheric pressure. It has become. Therefore, immediately after the rising and lowering of the vibration table 50 are switched, the pressure of the piping and pressure chamber to which hydraulic fluid is supplied is increased to a high pressure (10 to several tens of MPa) that can move the piston 32 from this low pressure. It takes a time of about several tens of milliseconds to increase the pressure to the maximum. This period is a time lag when the vibration table 50 does not move. Since this time lag has a magnitude that cannot be ignored with respect to the vibration period, the vibration system 50 cannot be vibrated at a high frequency of several tens of Hz or more in the hydraulic system having such a configuration.
  • the accumulator is always maintained so that the pressures of the pipes 61 and 62 and the pressure chambers 31a and 31b are maintained at a high pressure at which the hydraulic oil can transmit a sufficient driving force to the piston 32. 70 is pressurized.
  • the accumulator 70 can always transmit a necessary load to the hydraulic oil in the pressure chambers 31a and 31b and the pipes 61 and 62 by applying a high back pressure to the first pressure chamber 31a and the second pressure chamber 31b. Kept in a state. For this reason, there is almost no time lag in the configuration without the accumulator 70, and the vibration table 50 can be vibrated at a frequency of several tens of Hz or more.
  • the pressure of the gas layer of the accumulator 70 that is, the pressure applied to the hydraulic oil by the accumulator 70 is set to be larger than the minimum pressure required for the movement of the piston 32.
  • a high-pressure hose or the like that can sufficiently withstand the pressure applied to the hydraulic oil by the accumulator 70 is used.
  • the piston pump used in the pump body 11 of the pump unit 10 is likely to generate pulsation when driven.
  • the pulsation is absorbed by the accumulator 70 provided between the pump unit 10 and the hydraulic cylinder unit 30. 2A, the subject W is sandwiched between the frame 52 and the pressurizing table 50, the vibration table 50 is raised, and a vertical compressive static load is applied to the subject W.
  • FIG. Useful when performing additional compression tests.
  • the above-described feature is that the jigs 53 and 54 attached to the vibration table 50 and the frame 52 ′ are fixed to the subject, the vibration table 50 is lowered, and the subject W It is also useful when performing a tensile test in which a vertical static load in the vertical direction is applied.
  • the subject W is arranged between the frame and the vibration table, and the load applied to the subject W is periodically changed by reciprocating the vibration table. It is also possible to perform a vibration test.
  • a load sensor such as a load cell may be provided on the frame or the vibration table, and the controller 2 may be configured to control the pump unit based on the measurement result of the load sensor. For example, it is possible to perform a so-called fatigue test in which a load is repeatedly applied to the subject W so that the amplitude of the load applied to the subject W is constant.
  • FIG. 3 plots the acceleration and displacement of the vibration table measured when the object W is vibrated by giving a target waveform of a sine wave with a frequency of 50 Hz to the vibration test apparatus 1 (example) according to the present embodiment. It is a graph. 4 plots the acceleration and displacement of the vibration table measured when the object W is vibrated by giving a target waveform of a sine wave with a frequency of 50 Hz to a vibration test apparatus (comparative example) without an accumulator. It is a graph.
  • the measured acceleration and displacement waveforms of the vibration table are sinusoidal, and it can be seen that the workpiece W is vibrated in accordance with the target waveform of 50 Hz.
  • the measured acceleration waveform of the vibration table is greatly broken from the sine wave, and the amplitude thereof is less than 1/10 of the embodiment.
  • the displacement of the vibration table is hardly changed.
  • the vibration test apparatus can vibrate the subject at a high frequency.
  • a piston pump is used as the hydraulic pump of the actuator, but the present invention can be implemented using various types of hydraulic pumps other than the piston pump.
  • a rotary pump such as a gear pump or a vane pump is used.
  • the above exemplary embodiment is an example in which an actuator having a characteristic configuration of the present invention is mounted on a vibration test apparatus.
  • Such an actuator requires high frequency response, low vibration, and low noise. It can be installed in various hydraulic devices and systems.
  • the configuration of the present invention can be applied to a material testing apparatus, a robot arm, or the like.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • General Health & Medical Sciences (AREA)
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  • Life Sciences & Earth Sciences (AREA)
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  • Investigating Strength Of Materials By Application Of Mechanical Stress (AREA)
  • Fluid-Pressure Circuits (AREA)
PCT/JP2009/063695 2008-11-21 2009-07-31 油圧アクチュエータ及び油圧振動試験装置 WO2010058632A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN200980146327.7A CN102216750B (zh) 2008-11-21 2009-07-31 油压致动器和油压振动试验装置
KR1020117011087A KR101305982B1 (ko) 2008-11-21 2009-07-31 유압 액추에이터 및 유압 진동 시험 장치

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JP2008-298837 2008-11-21
JP2008298837 2008-11-21

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WO2010058632A1 true WO2010058632A1 (ja) 2010-05-27

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JP (2) JP5368084B2 (ko)
KR (1) KR101305982B1 (ko)
CN (1) CN102216750B (ko)
TW (1) TWI420090B (ko)
WO (1) WO2010058632A1 (ko)

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CN103016453A (zh) * 2012-12-14 2013-04-03 浙江大学 液压软管脉冲试验系统
CN112879359A (zh) * 2021-01-25 2021-06-01 武汉工程大学 煤层气水平井钻井液压推进系统位移跟踪控制系统与方法

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CN102042847A (zh) * 2010-10-29 2011-05-04 安徽士必达液压器材有限公司 高压脉冲测试系统
CN104614137B (zh) * 2015-01-15 2016-08-31 浙江大学 基于静压气浮解耦装置的三分量标准振动台
KR101671829B1 (ko) * 2015-07-06 2016-11-03 홍국선 기어펌프유닛을 포함하는 유압공급장치, 그리고 이를 포함하는 복합형 유압식 액추에이터
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