CN114673707A - Wind tunnel test model angle hydraulic system - Google Patents

Wind tunnel test model angle hydraulic system Download PDF

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Publication number
CN114673707A
CN114673707A CN202210584240.5A CN202210584240A CN114673707A CN 114673707 A CN114673707 A CN 114673707A CN 202210584240 A CN202210584240 A CN 202210584240A CN 114673707 A CN114673707 A CN 114673707A
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China
Prior art keywords
oil
valve
communicated
port
pipeline
Prior art date
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Pending
Application number
CN202210584240.5A
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Chinese (zh)
Inventor
吴志刚
徐开明
饶祝
宿鑫麟
刘忠华
简春梅
陈辅政
蒋海林
高大鹏
许可
江峰
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Low Speed Aerodynamics Institute of China Aerodynamics Research and Development Center
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Low Speed Aerodynamics Institute of China Aerodynamics Research and Development Center
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Application filed by Low Speed Aerodynamics Institute of China Aerodynamics Research and Development Center filed Critical Low Speed Aerodynamics Institute of China Aerodynamics Research and Development Center
Priority to CN202210584240.5A priority Critical patent/CN114673707A/en
Publication of CN114673707A publication Critical patent/CN114673707A/en
Pending legal-status Critical Current

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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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • 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
    • 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
    • F15B1/26—Supply reservoir or sump assemblies
    • 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
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/027—Check valves
    • 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
    • F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
    • F15B19/005—Fault detection or monitoring
    • 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
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
    • 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
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • 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
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • F15B21/0423—Cooling
    • 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
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • F15B21/0427—Heating
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M9/00—Aerodynamic testing; Arrangements in or on wind tunnels
    • G01M9/02—Wind tunnels
    • G01M9/04—Details
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M9/00—Aerodynamic testing; Arrangements in or on wind tunnels
    • G01M9/08—Aerodynamic models
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • F15B2013/0448—Actuation by solenoid and permanent magnet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31594—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having multiple pressure sources and multiple output members

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • General Physics & Mathematics (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

A wind tunnel test model angle hydraulic system comprises: an oil tank; the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder and the beta-direction mechanism rear oil cylinder are respectively provided with two oil cylinders, and a rod cavity and a rodless cavity of each oil cylinder are communicated with a one-way valve; the oil tank is communicated with a servo valve and a reversing valve respectively, four one-way valves corresponding to the alpha mechanism oil cylinder, the beta mechanism front oil cylinder and the beta mechanism rear oil cylinder are connected in parallel and then communicated with a first working port of the servo valve, a second working port of the servo valve is communicated with a liquid supply pipeline, a third working port of the servo valve is communicated with a liquid return pipeline, two one-way valves corresponding to two rod cavities are connected in parallel and then communicated with a first port of the reversing valve, two one-way valves corresponding to two rodless cavities are connected in parallel and then communicated with a second port of the reversing valve, a third port of the reversing valve is communicated with the liquid supply pipeline, and a fourth port of the reversing valve is communicated with the liquid return pipeline.

Description

Wind tunnel test model angle hydraulic system
Technical Field
The invention relates to the technical field of hydraulic pressure, in particular to a wind tunnel test model angle hydraulic system.
Background
Aiming at the 8m multiplied by 6m wind tunnel super-large test model angle device in the prior art, the device is used as a set of model supporting device which operates independently, through the coordinated motion of a yaw rotating shaft, the model can realize the continuous change of a sideslip angle of +/-30 degrees, and through the coordinated design of a tail strut and a pitching angle head, the change of an attack angle of the model from 0 degree to 120 degrees is realized.
However, in a large number of test processes, problems are gradually found, and the problems have influence or hidden troubles on the test effect, the disassembly and assembly convenience and the maintainability.
Disclosure of Invention
The invention aims to provide a wind tunnel test model angle hydraulic system which is remarkably improved in reliability, reliable in movement and capable of meeting the requirement of safe operation.
In order to achieve the above object, the wind tunnel test model angle hydraulic system provided by the invention comprises:
an oil tank;
the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder and the beta-direction mechanism rear oil cylinder are respectively provided with two oil cylinders, a rod cavity and a rodless cavity of each oil cylinder are communicated with a one-way valve, and oil can flow from the oil tank to the oil cylinders through the one-way valves;
a servo valve and a reversing valve are respectively communicated among the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder and the beta-direction mechanism rear oil cylinder and the oil tank,
four one-way valves corresponding to the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder and the beta-direction mechanism rear oil cylinder are connected in parallel and then communicated with a first working port of the servo valve, a second working port of the servo valve is communicated with a liquid supply pipeline, a third working port of the servo valve is communicated with a liquid return pipeline, the liquid supply pipeline and the liquid return pipeline are communicated with an oil tank,
when the servo valve is positioned at the first working position, the first working port and the third working port of the servo valve are communicated, the second working port of the servo valve is disconnected, when the servo valve is positioned at the second working position, the first working port and the second working port of the servo valve are communicated, and the third working port of the servo valve is disconnected;
in the four check valves of the alpha-directional mechanism oil cylinder, two check valves corresponding to two rod cavities are connected in parallel and then communicated with a first port of a reversing valve, two check valves corresponding to two rodless cavities are connected in parallel and then communicated with a second port of the reversing valve, a third port of the reversing valve is communicated with a liquid supply pipeline, a fourth port of the reversing valve is communicated with a liquid return pipeline,
in the four check valves respectively corresponding to the front oil cylinder and the rear oil cylinder of the beta-directional mechanism, the two check valves respectively corresponding to the rod cavity and the rodless cavity are connected in parallel and then communicated with a first port of a reversing valve, the other two check valves are connected in parallel and then communicated with a second port of the reversing valve, a third port of the reversing valve is communicated with a liquid supply pipeline, a fourth port of the reversing valve is communicated with a liquid return pipeline,
when the reversing valve is in the first working position, the first port of the reversing valve is communicated with the third port, the second port of the reversing valve is communicated with the fourth port, and when the reversing valve is in the second working position, the first port of the reversing valve is communicated with the fourth port, and the second port of the reversing valve is communicated with the third port.
Optionally, the method further comprises:
the Y-direction mechanism oil cylinder comprises a first cavity and a second cavity with an expansion link, wherein an oil control pipeline is communicated between the first cavity and an oil tank and communicated with a transposition valve, the oil control pipeline is connected in parallel with a sub-pipeline, two ends of the sub-pipeline are respectively communicated with the oil control pipeline and the second cavity, the sub-pipeline is communicated with an overflow valve, an overflow port of the overflow valve is communicated with an oil return pipeline, and the oil return pipeline is communicated with the oil tank.
Optionally, the sub-pipeline is also communicated with an electromagnetic valve and a switching valve, a one-way valve body is also communicated between the transposition valve and the first cavity,
the first oil port and the second oil port of the transposition valve are respectively communicated with an oil control pipeline, the first oil port of the electromagnetic valve is communicated with the oil control pipeline, the second oil port of the electromagnetic valve is communicated with a sub pipeline, the first working oil port of the transposition valve is communicated with the one-way valve body, the second working oil port of the transposition valve is communicated with the oil control pipeline, and the third working oil port of the transposition valve, the third oil port of the electromagnetic valve and the third oil port of the transposition valve are communicated;
when the transposition valve is located at the first working position, a first oil port of the transposition valve is communicated with a second oil port, and when the transposition valve is located at the second working position, the first oil port of the transposition valve is communicated with a third oil port;
when the electromagnetic valve is located at the first working position, the first oil port and the second oil port of the electromagnetic valve are communicated, and when the electromagnetic valve is located at the second working position, the first oil port and the third oil port of the electromagnetic valve are communicated;
when the change-over valve is in the first working position, the first working oil port and the second working oil port of the change-over valve are communicated, the third working oil port of the change-over valve is disconnected, and when the change-over valve is in the second working position, the first working oil port and the third working oil port of the change-over valve are communicated, and the second working oil port of the change-over valve is disconnected.
Optionally, a one-way valve is communicated between the transposition valve and the one-way valve body, an oil control valve is communicated between the one-way valve and the sub-pipeline, a first port and a second port of the oil control valve conduct the one-way valve and the sub-pipeline, and a third port of the oil control valve is communicated with the oil tank;
when the oil control valve is in the first working position, the first port and the second port of the oil control valve are communicated, the third port of the oil control valve is disconnected, and when the oil control valve is in the second working position, the first port and the third port of the oil control valve are communicated, and the second port of the oil control valve is disconnected.
Optionally, a first pipeline is communicated between the oil tank and the liquid supply pipeline, the first pipeline is connected with a second pipeline and a third pipeline in parallel, the second pipeline is communicated with a ball valve, a pressure measuring joint and a filter, the third pipeline is communicated with an overflow valve body, and the second pipeline and the third pipeline are communicated with the oil tank.
Optionally, two oil pump assemblies are communicated between the oil tank and the first pipeline, and each oil pump assembly comprises: the oil suction filter, the valve, the motor set and the one-way oil suction valve are sequentially communicated, and the two oil pump assemblies suck oil in the oil tank into the first pipeline.
Optionally, the first pipeline is further communicated with an inverted pipeline filter, the first pipeline is communicated with an overflow loop, the overflow loop is communicated with a proportional overflow valve, one end of the overflow loop is communicated between the inverted pipeline filter and the liquid supply pipeline, and the other end of the overflow loop is communicated with the oil tank.
Optionally, the first pipeline is communicated with an overflow sub-loop, the overflow sub-loop is sequentially communicated with a stop valve, an energy accumulator and a high-pressure stop valve, one end of the overflow sub-loop is communicated between the overflow loop and the liquid supply pipeline, and the other end of the overflow sub-loop is communicated with the oil tank.
Optionally, a heater and a cooling device are also included, the heater is used for heating the oil tank,
the cooling device includes: the high-pressure stop valve, the plate heat exchanger, the electromagnetic water valve, the pressure relay and the vane pump are arranged on the cooling liquid path, the electromagnetic water valve is communicated with the cooling liquid path, so that the cooling liquid reaches the plate heat exchanger, one end of the plate heat exchanger is communicated with the oil tank, the other end of the plate heat exchanger is sequentially communicated with the high-pressure stop valve, the pressure relay and the vane pump, and the vane pump can realize oil circulation.
Optionally, the inside of the oil tank is further provided with a liquid level meter check valve, a liquid level liquid thermometer, a liquid level control relay and a temperature sensor.
Compared with the background technology, the wind tunnel test model angle hydraulic system provided by the invention has the advantages that the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder and the beta-direction mechanism rear oil cylinder are respectively provided with the two oil cylinders, the rod cavity and the rodless cavity of each oil cylinder are respectively communicated with the one-way valve, oil can flow from the oil tank to the oil cylinders through the one-way valves, and the independent operation of the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder and the beta-direction mechanism rear oil cylinder can be ensured by respectively controlling the servo valve and the reversing valve, so that the reliable movement is ensured, and the requirement of safe operation is met.
In some embodiments, the wind tunnel test model angle hydraulic system further comprises: the Y-direction mechanism oil cylinder comprises a first cavity and a second cavity with an expansion link, wherein an oil control pipeline is communicated between the first cavity and an oil tank and communicated with a transposition valve, the oil control pipeline is connected in parallel with a sub-pipeline, two ends of the sub-pipeline are respectively communicated with the oil control pipeline and the second cavity, the sub-pipeline is communicated with an overflow valve, an overflow port of the overflow valve is communicated with an oil return pipeline, and the oil return pipeline is communicated with the oil tank. By the arrangement, accurate control of the hydraulic cylinder can be well realized through hydraulic control, coordinated movement of the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder, the beta-direction mechanism rear oil cylinder and the Y-direction mechanism oil cylinder is realized, the safe operation requirement is met, and fault monitoring and the like are realized.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the provided drawings without creative efforts.
Fig. 1 is a schematic diagram of a wind tunnel test model angle hydraulic system provided in an embodiment of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In order that those skilled in the art will better understand the disclosure, the invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
The wind tunnel test model angle hydraulic system provided by the embodiment of the application is shown in reference specification fig. 1 and comprises: the oil tank 1 is used as a component for supplying oil, and the volume of the oil tank 1 can be set to be about 1000L.
The alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder and the beta-direction mechanism rear oil cylinder are respectively provided with two oil cylinders, a rod cavity and a rodless cavity of each oil cylinder are communicated with a one-way valve 23, and the one-way valves 23 can supply oil to flow from the oil tank 1 to the oil cylinders.
A servo valve 21 and a reversing valve 22 are respectively communicated between the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder and the beta-direction mechanism rear oil cylinder and the oil tank 1.
Four one-way valves 23 corresponding to the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder and the beta-direction mechanism rear oil cylinder are connected in parallel and then communicated with a first working port of the servo valve 21, a second working port of the servo valve 21 is communicated with a liquid supply pipeline, a third working port of the servo valve 21 is communicated with a liquid return pipeline, and the liquid supply pipeline and the liquid return pipeline are communicated with the oil tank 1.
When the servo valve 21 is in the first operating position, the first and third working ports of the servo valve 21 are in communication and the second working port of the servo valve 21 is blocked, and when the servo valve 21 is in the second operating position, the first and second working ports of the servo valve 21 are in communication and the third working port of the servo valve 21 is blocked.
In four check valves 23 of the alpha-direction mechanism cylinder, two check valves 23 corresponding to two rod cavities are connected in parallel and then communicated with a first port of a reversing valve 22, two check valves 23 corresponding to two rodless cavities are connected in parallel and then communicated with a second port of the reversing valve 22, a third port of the reversing valve 22 is communicated with a liquid supply pipeline, and a fourth port of the reversing valve 22 is communicated with a liquid return pipeline.
In four check valves 23 corresponding to a front oil cylinder and a rear oil cylinder of the beta-directional mechanism respectively, the two check valves 23 corresponding to a rod cavity and a rodless cavity are connected in parallel and then communicated with a first port of a reversing valve 22, the other two check valves 23 are connected in parallel and then communicated with a second port of the reversing valve 22, a third port of the reversing valve 22 is communicated with a liquid supply pipeline, and a fourth port of the reversing valve 22 is communicated with a liquid return pipeline.
When the direction valve 22 is in the first operating position, the first port and the third port of the direction valve 22 are in communication, and the second port and the fourth port of the direction valve 22 are in communication, and when the direction valve 22 is in the second operating position, the first port and the fourth port of the direction valve 22 are in communication, and the second port and the third port of the direction valve 22 are in communication.
Referring to fig. 1, the diverter valve 22 is shown in a third operating position in which the first port, the second port, the third port and the fourth port are disconnected from each other, and the alpha cylinder, the beta cylinder and the beta cylinder do not operate accordingly. The servo valve 21 is shown in a first operating position, i.e. the first and third working ports of the servo valve 21 are in communication and the second working port of the servo valve 21 is disconnected.
The wind tunnel test model angle hydraulic system further comprises a Y-direction mechanism oil cylinder, the Y-direction mechanism oil cylinder comprises a first cavity and a second cavity with an expansion link, an oil control pipeline is communicated between the first cavity and the oil tank 1 and communicated with a transposition valve 25, the oil control pipeline is connected with sub-pipelines in parallel, two ends of each sub-pipeline are respectively communicated with the oil control pipeline and the second cavity, each sub-pipeline is communicated with an overflow valve 28, an overflow port of each overflow valve 28 is communicated with an oil return pipeline, and each oil return pipeline is communicated with the oil tank 1.
The sub-line is also connected to an electromagnetic valve 26 and a switching valve 29, and a check valve body 24 is also connected between the shift valve 25 and the first chamber.
The first oil port and the second oil port of the change-over valve 25 are respectively communicated with an oil control pipeline, the first oil port of the electromagnetic valve 26 is communicated with the oil control pipeline, the second oil port of the electromagnetic valve 26 is communicated with a sub-pipeline, the first working oil port of the change-over valve 29 is communicated with the check valve body 24, the second working oil port of the change-over valve 29 is communicated with the oil control pipeline, and the third working oil port of the change-over valve 29, the third oil port of the electromagnetic valve 26 and the third oil port of the change-over valve 25 are communicated.
When the transposition valve 25 is in the first working position, the first oil port and the second oil port of the transposition valve 25 are communicated, and when the transposition valve 25 is in the second working position, the first oil port and the third oil port of the transposition valve 25 are communicated.
When the solenoid valve 26 is in the first working position, the first oil port and the second oil port of the solenoid valve 26 are communicated, and when the solenoid valve 26 is in the second working position, the first oil port and the third oil port of the solenoid valve 26 are communicated.
When the switch valve 29 is in the first operating position, the first and second working oil ports of the switch valve 29 are communicated, the third working oil port of the switch valve 29 is blocked, and when the switch valve 29 is in the second operating position, the first and third working oil ports of the switch valve 29 are communicated, and the second working oil port of the switch valve 29 is blocked.
A one-way valve is communicated between the transposition valve 25 and the one-way valve body 24, in the description figure 1, the one-way valve is positioned below the one-way valve body 24 and is connected in series with the one-way valve, an oil control valve is communicated between the one-way valve and the sub-pipeline, a first port and a second port of the oil control valve conduct the one-way valve and the sub-pipeline, and a third port of the oil control valve is communicated with the oil tank 1.
When the oil control valve is in the first working position, the first port and the second port of the oil control valve are communicated, the third port of the oil control valve is disconnected, and when the oil control valve is in the second working position, the first port and the third port of the oil control valve are communicated, and the second port of the oil control valve is disconnected.
When the oil control valve is located at the first working position, the first port and the second port of the oil control valve conduct the one-way valve and the sub-pipeline, the third port of the oil control valve is communicated with the oil tank 1 through the oil unloading pipeline, and oil flows back to the oil tank 1 along the oil unloading pipeline through the oil control valve.
It can be seen that the Y-direction mechanism oil cylinder is only provided with one oil cylinder, the pressure of the inlet liquid of the Y-direction mechanism oil cylinder is measured by an overflow valve 28 and an oil pressure gauge 27, the liquid outlet of the oil cylinder is provided with a one-way valve body 24 and a one-way valve which are connected in series, and the one-way valve body 24 is connected with a switching valve 29 and is connected into a sub-pipeline; the one-way valve is connected with the transposition valve 25 and the electromagnetic valve 26 which are connected in parallel, then is connected into the sub-pipeline and is connected with the conversion valve 29; meanwhile, the one-way valve is connected with an oil control valve (the corresponding electromagnet is 12 DT), the oil control valve is connected with the sub-pipeline and returns oil through an oil discharge pipeline, and the oil discharge pipeline is provided with an energy accumulator.
For convenience of describing control over the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder, the beta-direction mechanism rear oil cylinder and the Y-direction mechanism oil cylinder, reference can be made to the following table I, the table I is a wind tunnel test model angle hydraulic system control diagram, DT represents elements in an electromagnetic valve, specific reference numbers can correspond to marks in the description figure 1, and plus signs and minus signs respectively represent execution when power is on and execution when power is off.
Table one: wind tunnel test model angle hydraulic system control diagram
Figure 484997DEST_PATH_IMAGE001
The state of each electromagnetic valve shown in the figure 1 in the description is an initial state, and when the corresponding mechanism needs to be extended or retracted, the corresponding electromagnetic valve corresponding to the figure 1 in the description should perform corresponding action; for example, for "α goes out to the mechanism cylinder" in table one, 2DT, 3DT and 4DT are plus signs, which indicates that 2DT, 3DT and 4DT are powered and act, and corresponding to 2DT, 3DT and 4DT in fig. 1 of the specification, 3DT act causes the servo valve 21 to move to the left, and 4DT act causes the reversing valve 22 to move to the left, at this time, the oil flow direction from α to the mechanism cylinder can be observed, and finally, α goes out to the mechanism cylinder.
The control of the oil source corresponds to 1DT and 2DT, which is not referred to herein. Similarly, in table one, the relevant contents of "main pump motor set start", "system primary pressure regulation 8 MPa", "system secondary pressure regulation 16 MPa", and "system tertiary pressure regulation 21.5 MPa" are not specifically developed herein.
For the extending and retracting control of the Y-direction mechanism oil cylinder, when the position of the Y-direction mechanism oil cylinder needs to be accurately controlled, 15DT acts, hydraulic oil passes through the transposition valve 25 from an oil control pipeline and enters a first cavity (rodless cavity) of the Y-direction mechanism oil cylinder through the direction controlled by the 15DT of the transposition valve 25, and the oil cylinder extends out.
When the Y-direction mechanism oil cylinder is operated manually or in a standby mode (position precision control is not needed at the moment), the 13DT is operated. Hydraulic oil passes from the oil control line through the solenoid valve 26 and enters the first chamber (rodless chamber) of the Y-direction mechanism cylinder, which extends out, in the direction controlled by 13DT of the solenoid valve 26.
The pipeline between the check valve body 24 and the change-over valve 29 is used for oil return, and can be used as a pressure control oil path for controlling the opening of the check valve body 24 and the check valve below the check valve body. Similarly, the line between the check valve and the oil control valve is also used for oil return, and serves as a pressure control oil path for controlling the opening of the check valve body 24 and the check valve therebelow.
When the Y-direction mechanism oil cylinder retracts, two loops are also arranged. When the position is required to be accurately controlled, high-pressure oil in the oil control pipeline enters a second cavity (rod cavity) of the Y-direction mechanism oil cylinder through the overflow valve 28, and pressure oil in the second cavity pushes the piston to retract. At this time, the check valve body 24 and the check valve thereunder are completely opened by the pressure oil of the two pressure control oil passages.
The hydraulic oil in the second chamber enters the transposition valve 25 through the one-way valve body 24 and the one-way valve below the one-way valve body, meanwhile, the DT16 in the transposition valve 25 obtains a corresponding control signal, and the opening of the transposition valve 25 meets the action requirement and flows back to the oil unloading pipeline through the transposition valve 25.
Still communicate between oil tank 1 and the liquid supply pipeline has the first pipeline, and the first pipeline has second pipeline and third pipeline in parallel, and the second pipeline intercommunication has ball valve 48, pressure measurement joint 49 and filter 34, and the third pipeline intercommunication has overflow valve body 2, and second pipeline and third pipeline all communicate with oil tank 1.
In order to avoid overlong pipelines, an oil inlet pipe 19 can be connected between the liquid supply pipeline and the first pipeline, two ends of the oil inlet pipe 19 are respectively communicated with the liquid supply pipeline and the first pipeline through a quick-change plug 20, and oil in the oil tank 1 enters the oil inlet pipe 19 through the first pipeline and enters the liquid supply pipeline through the oil inlet pipe 19.
The intercommunication has two oil pump assembly between oil tank 1 and the first pipeline, and oil pump assembly includes: the oil suction filter 3, the valve 4, the motor set 5 and the one-way oil suction valve 6 are sequentially communicated, and the two oil pump assemblies suck oil in the oil tank 1 into the first pipeline.
The first pipeline is also communicated with the inverted pipeline filter 9, the first pipeline is communicated with an overflow loop, the overflow loop is communicated with a proportional overflow valve 33, one end of the overflow loop is communicated between the inverted pipeline filter 9 and the liquid supply pipeline, and the other end of the overflow loop is communicated with the oil tank 1.
The first pipeline is communicated with an overflow sub-loop, the overflow sub-loop is sequentially communicated with a stop valve 14, an energy accumulator 30 and a high-pressure stop valve 32, one end of the overflow sub-loop is communicated between the overflow loop and the liquid supply pipeline, and the other end of the overflow sub-loop is communicated with the oil tank 1.
In order to prevent the instantaneous increase of the flow rate and the insufficient oil supply amount of the oil source, a group of energy accumulators 30 is arranged to assist the oil supply energy, the energy accumulators are composed of four devices, each volume is 63L, and the highest working pressure is 31.5 MPa.
Temperature control of the oil is essential to the quality of the oil and the proper operation of the hydraulic system. The oil temperature fluctuation value of the hydraulic system is recommended to be limited to +/-5 ℃, the long-term stable operation temperature is 35 ℃, and the reference temperature cannot be higher than 45 ℃ or lower than 25 ℃.
Referring to the description of the figure 1, an oil source drives two oil pumps to work through two motor sets 5 respectively, the power of each motor is 45kW, the flow rate of each oil pump is 100L/min, and the highest working pressure is 25 MPa; the oil source can be regulated by a three-level overflow valve (an overflow valve body 2, an overflow valve 28 and a proportional overflow valve 33), the pressure boosting mode is unloading-medium pressure-high pressure step-by-step pressure boosting, the pressure reducing mode is high pressure-medium pressure-unloading step-by-step pressure reducing, the pressure is regulated by the three-level overflow valve (the proportional overflow valve 33), and the pressure impact during pressure regulation can be reduced; a safety valve is arranged in parallel with the three-level overflow valve (the proportional overflow valve 33) to play a role in limiting the pressure of the system so as to prevent components from being damaged due to overhigh pressure of the system.
The outlet of the hydraulic pump is provided with a one-way oil suction valve 6 to prevent the hydraulic oil from flowing back and protect the hydraulic pump; a hydraulic filter 7 and an energy storage device 8 are arranged behind the one-way oil suction valve 6 to eliminate pressure pulsation; the first pipeline is provided with an oil filter 18, the return liquid pipeline is provided with a return oil filter 10, the second pipeline is provided with a filter 34, the oil filter 18 and the filter 34 can be specifically a signal transmitter with a filter element for blocking, and the signal transmitter has the functions of transmitting signals to a console and indicating by eyes at the same time; set up pressure sensor 11 on the first pipeline and detect oil circuit pressure, pressure sensor 11 department still can be equipped with manometer switch 12 and shock-resistant manometer 13, has still set up temperature sensor 43 and has detected the temperature of oil tank fluid, and the numerical value of pressure and temperature can conveniently be read out through the digital display table on the control cabinet.
In order to avoid overlong liquid return pipelines, the liquid return pipelines can be connected with a mechanism oil return pipe 16, the mechanism oil return pipe 16 is communicated with the oil tank 1, and the liquid return pipelines and the mechanism oil return pipe 16 can be connected through a quick-change connector 17.
The wind tunnel test model angle hydraulic system further comprises a heater 38 and a cooling device, the heater is used for heating the oil tank 1, the heater 38 can be an electric heater, the heating temperature rise is fast, care needs to be taken when the wind tunnel test model angle hydraulic system is used, oil liquid does not need to be heated excessively, and once the oil temperature reaches the lower limit value of the reference temperature, heating is stopped immediately.
The heater 38 acts on the oil tank 1 directly, and since the lowest ambient temperature may reach-5 ℃, when the temperature of the oil tank 1 is lower than 10 ℃, the viscosity of the oil is high, which is not beneficial to the oil absorption and starting of the hydraulic pump, the oil temperature needs to be increased to more than 25 ℃ by heating, and if the electric heater 38 is used for heating, the temperature can be increased by 10 ℃ in one hour.
In order to well control the temperature of the oil, an independent circulating cooling system is adopted in an oil source, the plate heat exchanger 35 is adopted for cooling the oil temperature, the plate heat exchanger 35 has good cooling effect and high cooling efficiency, cooling water can be tap water and cannot be recycled, otherwise the cooling effect of a cooler is greatly reduced; the cooling device includes: the high-pressure stop valve, the plate heat exchanger 35, the electromagnetic water valve 36, the pressure relay 37 and the vane pump 44, the electromagnetic water valve 36 is communicated with a cooling liquid path, so that cooling liquid reaches the plate heat exchanger 35, a pressure gauge 47 can be further arranged on the cooling liquid path, one end of the plate heat exchanger 35 is communicated with the oil tank 1, the other end of the plate heat exchanger 35 is communicated with the high-pressure stop valve, the pressure relay 37 and the vane pump 44 in sequence, the vane pump 44 is connected with a motor 45, the motor 45 can be a 5.5Kw motor specifically, and oil circulation can be realized by the vane pump 44.
The hydraulic oil used by the system is YH-10 aviation hydraulic oil, and the viscosity-temperature characteristic of the hydraulic oil is good. The hydraulic system is a hydraulic servo system, so the requirement on the cleanliness of oil is high, and in order to ensure that the precision of oil source oil reaches the requirement of 5 mu m, an oil suction filter 3 is arranged at an oil suction port of an oil pump, a 10 mu m oil filter 18 is arranged in a pressure pipeline, and 5 mu m oil filters (an oil return filter 10 and a filter 34) are arranged on two oil return pipes. When oil is filled into the oil tank 1, the oil must pass through an oil filling machine with the filtering precision of 3 mu m, and the unfiltered oil cannot be directly filled into the oil tank 1; the oil tank 1 is made of stainless steel, a totally enclosed mechanism is adopted, the sealing performance is good, dust and oil leakage drops are difficult to enter the oil tank 1, and the bottom of the oil tank 1 can be further provided with an oil drain valve 46.
The inside of the oil tank 1 is also provided with a liquid level meter check valve 40, a liquid level liquid thermometer 41, a liquid level control relay 42 and a temperature sensor 43, thereby fully meeting the temperature control and liquid level control of the hydraulic system. In addition, the oil tank 1 is also provided with an air filter 39, so that the accuracy of the hydraulic system is prevented from being reduced after long-term use due to the fact that impurities enter the oil tank 1.
According to the wind tunnel test model angle hydraulic system, the situation that the pressure fluctuation inside a pipeline is large when the pressure level is converted in the starting (boosting) and closing (reducing) processes of an oil source can be avoided, the severe vibration of an accessory pipeline of an energy accumulator is avoided, and the obvious vibration of a supporting model of a device with a super-large attack angle in a hole is avoided.
The continuous stepless change of the input voltage of the electromagnet corresponding to the relevant electromagnetic valve is utilized to enable the valve core to generate different thrusts, thereby obtaining the continuously changed hydraulic pressure. When the pressure of the oil source is continuously increased from zero to the maximum pressure during starting, the pressure of the oil source is continuously decreased from the maximum pressure to zero during closing, no pressure step exists in the middle process, and the pressure of the oil source reaches stepless pressure regulation. Therefore, the safety of the model is better protected, and the safety of the test is improved.
Meanwhile, the precision guarantee of each direction of oil cylinder can be realized:
mechanism attack angle alpha control precision: < 2.5';
the angular motion is uniform and stable and is adjustable within the range of 0-1 DEG/s;
the up-and-down movement of the Y-direction mechanism is ensured to be stable and flexible, the phenomena of sticking and creeping are avoided, the speed is 40mm/S, and the positioning precision is 1 mm;
the maximum rated working pressure of the hydraulic servo system can reach 21MPa, the actual use pressure is 16MPa, and the safety pressure is far larger than the actual use pressure.
It is noted that, in this specification, relational terms such as first and second, and the like are used solely to distinguish one entity from another entity without necessarily requiring or implying any actual such relationship or order between such entities.
The wind tunnel test model angle hydraulic system provided by the application is described in detail above. The principles and embodiments of the present invention are explained herein using specific examples, which are presented only to assist in understanding the method and its core concepts. It should be noted that, for those skilled in the art, it is possible to make various improvements and modifications to the present invention without departing from the principle of the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.

Claims (10)

1. The utility model provides a wind tunnel test model angle hydraulic system which characterized in that includes:
an oil tank (1);
the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder and the beta-direction mechanism rear oil cylinder are respectively provided with two oil cylinders, a rod cavity and a rodless cavity of each oil cylinder are communicated with a one-way valve (23), and the one-way valves (23) can supply oil to flow from the oil tank (1) to the direction of the oil cylinders;
a servo valve (21) and a reversing valve (22) are respectively communicated among the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder and the beta-direction mechanism rear oil cylinder and the oil tank (1),
the four check valves (23) corresponding to the alpha-direction mechanism oil cylinder, the beta-direction mechanism front oil cylinder and the beta-direction mechanism rear oil cylinder are connected in parallel and then communicated with the first working port of the servo valve (21), the second working port of the servo valve (21) is communicated with a liquid supply pipeline, the third working port of the servo valve (21) is communicated with a liquid return pipeline, the liquid supply pipeline and the liquid return pipeline are communicated with the oil tank (1),
when the servo valve (21) is in a first working position, the first working port and the third working port of the servo valve (21) are communicated, the second working port of the servo valve (21) is disconnected, when the servo valve (21) is in a second working position, the first working port and the second working port of the servo valve (21) are communicated, and the third working port of the servo valve (21) is disconnected;
in the four check valves (23) of the alpha-direction mechanism oil cylinder, the two check valves (23) corresponding to the two rod cavities are connected in parallel and then communicated with a first port of the reversing valve (22), the two check valves (23) corresponding to the two rodless cavities are connected in parallel and then communicated with a second port of the reversing valve (22), a third port of the reversing valve (22) is communicated with the liquid supply pipeline, and a fourth port of the reversing valve (22) is communicated with the liquid return pipeline,
in the four check valves (23) corresponding to the front oil cylinder and the rear oil cylinder of the beta-directional mechanism respectively, the two check valves (23) corresponding to the rod cavity and the rodless cavity are connected in parallel and then communicated with a first port of the reversing valve (22), the other two check valves (23) are connected in parallel and then communicated with a second port of the reversing valve (22), a third port of the reversing valve (22) is communicated with the liquid supply pipeline, and a fourth port of the reversing valve (22) is communicated with the liquid return pipeline,
when the reversing valve (22) is in a first working position, the first port and the third port of the reversing valve (22) are communicated, the second port and the fourth port of the reversing valve (22) are communicated, when the reversing valve (22) is in a second working position, the first port and the fourth port of the reversing valve (22) are communicated, and the second port and the third port of the reversing valve (22) are communicated.
2. The wind tunnel test model angle hydraulic system of claim 1, further comprising:
the Y-direction mechanism oil cylinder comprises a first cavity and a second cavity with an expansion link, wherein an oil control pipeline is communicated between the first cavity and the oil tank (1), the oil control pipeline is communicated with a transposition valve (25), the oil control pipeline is connected with sub-pipelines in parallel, two ends of each sub-pipeline are respectively communicated with the oil control pipeline and the second cavity, each sub-pipeline is communicated with an overflow valve (28), an overflow port of each overflow valve (28) is communicated with an oil return pipeline, and the oil return pipeline is communicated with the oil tank (1).
3. The wind tunnel test model angle hydraulic system according to claim 2, characterized in that the sub-pipeline is further communicated with an electromagnetic valve (26) and a switching valve (29), a one-way valve body (24) is further communicated between the transposition valve (25) and the first cavity,
a first oil port and a second oil port of the transposition valve (25) are respectively communicated with the oil control pipeline, a first oil port of the electromagnetic valve (26) is communicated with the oil control pipeline, a second oil port of the electromagnetic valve (26) is communicated with the sub-pipeline, a first working oil port of the conversion valve (29) is communicated with the one-way valve body (24), a second working oil port of the conversion valve (29) is communicated with the oil control pipeline, and a third working oil port of the conversion valve (29), a third oil port of the electromagnetic valve (26) and a third oil port of the transposition valve (25) are communicated;
when the transposition valve (25) is located at a first working position, a first oil liquid port and a second oil liquid port of the transposition valve (25) are communicated, and when the transposition valve (25) is located at a second working position, the first oil liquid port and a third oil liquid port of the transposition valve (25) are communicated;
when the electromagnetic valve (26) is located at a first working position, a first oil port and a second oil port of the electromagnetic valve (26) are communicated, and when the electromagnetic valve (26) is located at a second working position, the first oil port and a third oil port of the electromagnetic valve (26) are communicated;
when the switching valve (29) is in the first working position, the first working oil port and the second working oil port of the switching valve (29) are communicated, the third working oil port of the switching valve (29) is disconnected, and when the switching valve (29) is in the second working position, the first working oil port and the third working oil port of the switching valve (29) are communicated, and the second working oil port of the switching valve (29) is disconnected.
4. The wind tunnel test model angle hydraulic system according to claim 3, characterized in that a check valve is further communicated between the transposition valve (25) and the check valve body (24), an oil control valve is communicated between the check valve and the sub-pipeline, a first port and a second port of the oil control valve communicate the check valve with the sub-pipeline, and a third port of the oil control valve is communicated with the oil tank (1);
when the oil control valve is in a first working position, the first port and the second port of the oil control valve are communicated, the third port of the oil control valve is disconnected, and when the oil control valve is in a second working position, the first port and the third port of the oil control valve are communicated, and the second port of the oil control valve is disconnected.
5. The wind tunnel test model angle hydraulic system according to any one of claims 1 to 4, characterized in that a first pipeline is further communicated between the oil tank (1) and the liquid supply pipeline, the first pipeline is connected in parallel with a second pipeline and a third pipeline, the second pipeline is communicated with a ball valve (48), a pressure measuring joint (49) and a filter (34), the third pipeline is communicated with an overflow valve body (2), and the second pipeline and the third pipeline are both communicated with the oil tank (1).
6. The wind tunnel test model angle hydraulic system according to any one of claims 1 to 4, wherein two oil pump assemblies are communicated between the oil tank (1) and the first pipeline, and each oil pump assembly comprises: the oil pump assembly comprises an oil suction filter (3), a valve (4), a motor set (5) and a one-way oil suction valve (6) which are sequentially communicated, wherein the oil pump assembly sucks oil in the oil tank (1) into the first pipeline.
7. The wind tunnel test model angle hydraulic system according to claim 5, characterized in that the first pipeline is further communicated with a flip-chip pipeline filter (9), the first pipeline is communicated with an overflow loop, the overflow loop is communicated with a proportional overflow valve (33), one end of the overflow loop is communicated between the flip-chip pipeline filter (9) and the liquid supply pipeline, and the other end of the overflow loop is communicated with the oil tank (1).
8. The wind tunnel test model angle hydraulic system according to claim 7, characterized in that the first pipeline is communicated with an overflow sub-circuit, the overflow sub-circuit is sequentially communicated with a stop valve (14), an accumulator (30) and a high-pressure stop valve (32), one end of the overflow sub-circuit is communicated between the overflow circuit and the liquid supply pipeline, and the other end of the overflow sub-circuit is communicated with the oil tank (1).
9. The wind tunnel test model angle hydraulic system according to any one of claims 1 to 4, further comprising a heater and a cooling device, wherein the heater is used for heating the oil tank (1),
the cooling device includes: high pressure stop valve, plate heat exchanger (35), electromagnetism water valve (36), pressure relay (37) and impeller pump (44), electromagnetism water valve (36) communicate in the coolant liquid way to make cooling liquid reach plate heat exchanger (35) department, the one end intercommunication of plate heat exchanger (35) oil tank (1), the other end communicate in proper order the high pressure stop valve pressure relay (37) with impeller pump (44), oil circulation can be realized in impeller pump (44).
10. The wind tunnel test model angle hydraulic system according to claim 9, characterized in that a liquid level meter check valve (40), a liquid level liquid thermometer (41), a liquid level control relay (42) and a temperature sensor (43) are further arranged inside the oil tank (1).
CN202210584240.5A 2022-05-27 2022-05-27 Wind tunnel test model angle hydraulic system Pending CN114673707A (en)

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JPH09159570A (en) * 1995-12-06 1997-06-20 Mitsubishi Heavy Ind Ltd Piston damper stopping device
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CN112483499A (en) * 2020-12-09 2021-03-12 中国空气动力研究与发展中心高速空气动力研究所 Multifunctional movable oil source system for guaranteeing wind tunnel hydraulic equipment
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Application publication date: 20220628