CN117554083B - Method for loading system by adopting engine casing thermal internal pressure fatigue test - Google Patents
Method for loading system by adopting engine casing thermal internal pressure fatigue test Download PDFInfo
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Abstract
The invention relates to a method for adopting an engine case thermal internal pressure fatigue test loading system, which comprises the steps of establishing the engine case thermal internal pressure fatigue test loading system and a heating model containing heat dissipation, and realizing quantitative control of heater power in the heating process of a tested cavity; establishing a pressurized model containing air leakage, and realizing quantitative control of the mass flow of the tested cavity in the process of adding, releasing or maintaining the pressure of the tested cavity; and establishing temperature-pressure coupling control, and realizing cross iteration control of the temperature and the pressure of the tested cavity in the heating and pressurizing processes of the tested cavity. The invention fully considers the factors such as the mutual influence between temperature and pressure in the loading process, the influence of the test system on the loading process caused by external heat dissipation and air leakage phenomena, and the like, and effectively solves the problem of poor pressure and temperature control precision in the test and assessment process of the thermal internal pressure fatigue of the outer culvert casing of the existing aeroengine.
Description
Technical Field
The invention belongs to the technical field of aeroengines, and particularly relates to a method for loading a system by adopting an engine case thermal internal pressure fatigue test.
Background
An aeroengine is a highly complex and sophisticated thermodynamic machine whose internal structure is designed to meet thermodynamic load requirements. The casing is one of the main components in an aeroengine, acting as a support for the rotor and the stationary stator, and together with other components constitutes an air flow channel of the engine, through which the thrust of the engine is also transmitted to the aircraft. Therefore, the casing is an important load bearing and force transmitting component of the engine. When the fuel gas of the engine flows through each casing, high temperature, high pressure and mechanical load are generated on the casing, wherein the effect of the pressure load on the structural strength of the casing is far greater than the effect of the mechanical load on the casing, and the effect of the high temperature and the high pressure on the structure of the casing is more concerned in test examination.
The requirements for the assessment of the casing are continuously improved along with the development of the aero-engine and the test technology thereof, the assessment of the metal casing in early stage is mainly a normal temperature static strength test, and the assessment mode comprises a normal temperature pressure test and a normal temperature static pressure combined test. In order to improve the effective thrust of the engine, new requirements are put on a checking mode of the casing along with the structural optimization design and the introduction of the light composite material, and the checking mode is mainly implemented by a thermal strength test method, wherein the checking mode comprises a pressurizing capsule with a solid loading medium, a transmission quicksand method and a thermal internal pressure method of a gas loading medium and a gas-liquid loading medium. After the thermal strength assessment analysis is completed, based on the service life and reliability requirements of the engine, the thermal current fatigue strength analysis is further required to be carried out on the casing, and the influence of the repeated start-stop process of the engine on the fatigue life of the casing is mainly simulated. The fatigue life assessment of the case is mainly carried out at normal temperature under most conditions, including a normal-temperature hydraulic fatigue loading mode and a normal-temperature pneumatic fatigue loading mode. With the development of high-temperature resistant composite material technology and the application of a full-size composite material casing, the design requirement cannot be met by adopting normal-temperature fatigue assessment, and the assessment must be performed by applying a real high-temperature environment. Patent document with application publication number of CN 116202755A discloses a high-temperature high-pressure intensity test system and method for an engine casing based on an air medium. The system comprises: the normal temperature and high pressure air subsystem is mainly used for providing normal temperature and high pressure air for the test; the high-temperature high-pressure air subsystem is mainly used for providing high-temperature high-pressure air for the test; the cold and hot air mixing subsystem is mainly used for realizing the rapid loading and unloading speed of temperature load, so that the test efficiency is improved; the temperature and pressure load measurement and control subsystem is mainly used for realizing accurate measurement and coordinated control of temperature load and pressure load of the engine casing. According to the air medium-based engine casing high-temperature high-pressure intensity test system, the real simulation of the high-temperature high-pressure loading environment of the engine casing structure under the test condition can be realized, and the intensity test verification requirement of the engine casing under the actual working load level can be met.
The current urgent need to be solved is: the high-temperature fatigue strength assessment of the casing mainly has the following problems: the temperature and pressure loads such as the influence of the temperature and the pressure in the loading process and the influence of the test system on the external heat dissipation and the air leakage phenomenon are not considered, so that the temperature and the pressure loads cannot be accurately controlled.
Disclosure of Invention
The invention aims to overcome the defects of the technology, and provides a method for adopting the loading system for the thermal internal pressure fatigue test of the engine casing, which fully considers the factors such as the mutual influence between temperature and pressure in the loading process, the influence of the test system on the loading process caused by external heat dissipation and air leakage phenomena and the like, and can effectively realize the accurate control of the temperature and the pressure in the loading process of the thermal internal pressure fatigue test of a tested cavity.
The invention adopts the following technical scheme to realize the aim: a method for adopting an engine case thermal internal pressure fatigue test loading system establishes the engine case thermal internal pressure fatigue test loading system and a heating model containing heat dissipation, and realizes quantitative control of heater power in the heating process of a tested cavity; establishing a pressurized model containing air leakage, and realizing quantitative control of the mass flow of the tested cavity in the process of adding, releasing or maintaining the pressure of the tested cavity; establishing temperature-pressure coupling control, and realizing cross iteration control of the temperature and the pressure of the tested cavity in the heating and pressurizing process of the tested cavity, wherein the specific flow of the temperature-pressure coupling control method is as follows:
firstly, establishing a loading system for a thermal internal pressure fatigue test of an engine case, wherein the loading system comprises an air source system, a temperature loading system, a pressure loading system and a tested cavity, the air source system is connected with the tested cavity, the tested cavity is respectively connected with the pressure loading system and the temperature loading system, and the temperature loading system comprises a control computer, a comprehensive controller, a silicon controlled rectifier power supply, a heater and a temperature sensor; the temperature sensor collects temperature signals in the tested cavity, the temperature signals are transmitted to the control computer through the comprehensive controller, the control computer feeds back information to the comprehensive controller, and the comprehensive controller drives the silicon controlled power supply to control the heater to work, so that a dynamic stable circulating system is formed between the temperature in the tested cavity and the target temperature;
step 1, starting, calling a target temperature dynamic load-keeping subroutine to heat a tested cavity;
step 2, the tested cavity reaches a high-temperature target state;
step 3, entering a high-temperature fatigue pressure loading circulation stage;
step 4, a target pressure loading subprogram is called to pressurize the tested cavity, and a target temperature dynamic load maintaining subprogram is synchronously called to control the heat preservation of the tested cavity;
step 5, the tested cavity reaches a high-temperature high-pressure target state;
step 6, invoking a target pressure dynamic load-keeping subprogram to perform pressure-maintaining control on the tested cavity, and synchronously invoking a target temperature dynamic load-keeping subprogram to perform heat-preserving control on the tested cavity;
step 7, maintaining the tested cavity in a high-temperature high-pressure target state;
step 8, a target pressure unloading subprogram is called to release pressure of the tested cavity, and a target temperature dynamic load maintaining subprogram is synchronously called to control heat preservation of the tested cavity;
step 9, the tested cavity reaches a high-temperature low-pressure target state;
step 10, invoking a target pressure dynamic load-keeping subprogram to perform pressure-maintaining control on the tested cavity, and synchronously invoking a target temperature dynamic load-keeping subprogram to perform heat-preserving control on the tested cavity;
step 11, maintaining a high-temperature low-pressure target state in the tested cavity;
step 12, judging whether the high-temperature fatigue pressure loading cycle is finished, if not, jumping to step 4, and if so, sequentially executing step 13;
step 13, stopping heating and pressurizing;
step 14, checking and testing the state of the tested case;
and 15, carrying out a next-level fatigue test or ending the test.
Further, the flow of the target temperature dynamic maintenance subroutine in step 1 is as follows:
step 1.1, starting to call a subprogram;
step 1.2, a comprehensive controller collects temperature signals of a temperature sensor in a tested cavity;
step 1.3, comparing the measured temperature with the target temperature, if the measured temperature is less than or equal to the target temperature-tolerance lower limit, jumping to step 1.4, if the measured temperature is more than or equal to the target temperature + tolerance upper limit, jumping to step 1.5, and if the target temperature-tolerance lower limit is less than the measured temperature and less than the target temperature + tolerance upper limit, jumping to step 1.6;
step 1.4, driving a heater to work by a silicon controlled power supply, and jumping to step 1.2;
step 1.5, stopping the heater, and jumping to step 1.2;
step 1.6, the temperature loading system maintains an iteration instruction and jumps to step 1.2.
Further, the target pressure loading subroutine described in step 4 has the following flow:
step 4.1, starting to call a subprogram;
step 4.2, collecting pressure signals of the pressure sensor in the tested cavity by the comprehensive controller;
step 4.3, comparing the measured pressure with the target pressure, if the measured pressure is less than the high target pressure plus the upper limit of the tolerance, jumping to step 4.4, and if the measured pressure is more than or equal to the high target pressure plus the upper limit of the tolerance, jumping to step 4.5;
step 4.4, closing a cavity exhaust valve, opening a cavity air inlet valve, pressurizing a tested cavity, and jumping to the step 4.2;
step 4.5, closing a cavity air inlet valve, closing a cavity air outlet valve and enabling the tested cavity to enter a pressure maintaining state, and jumping to the step 4.2;
further, the flow of the target pressure dynamic maintenance subroutine described in step 6 is as follows:
step 6.1, starting to call a subprogram;
step 6.2, collecting pressure signals of the pressure sensor in the tested cavity by the comprehensive controller;
step 6.3, comparing the measured pressure with the target pressure, if the measured pressure is less than or equal to the target pressure-tolerance lower limit, jumping to step 6.4, if the measured pressure is more than or equal to the target pressure + tolerance upper limit, jumping to step 6.5, and if the target pressure-tolerance lower limit is less than the measured pressure and less than the target pressure + tolerance upper limit, jumping to step 6.6;
step 6.4, closing a cavity exhaust valve, opening a cavity air inlet valve, pressurizing a tested cavity, and jumping to the step 6.2;
step 6.5, closing a cavity air inlet valve, opening a cavity air outlet valve, releasing pressure of the tested cavity, and jumping to the step 6.2;
and 6.6, closing a cavity air inlet valve, closing a cavity air outlet valve and enabling the tested cavity to enter a pressure maintaining state, and jumping to the step 6.2.
Further, the flow of the target pressure unloading subroutine described in step 8 is as follows:
step 8.1, starting to call a subprogram;
step 8.2, collecting pressure signals of the pressure sensor in the tested cavity by the comprehensive controller;
step 8.3, comparing the measured pressure with the target pressure, if the measured pressure is less than the low target pressure plus the upper limit of the tolerance, jumping to step 8.4, and if the measured pressure is more than or equal to the low target pressure plus the upper limit of the tolerance, jumping to step 8.5;
step 8.4, closing a cavity air inlet valve, closing a cavity air outlet valve and enabling the tested cavity to enter a pressure maintaining state, and jumping to the step 8.2;
and 8.5, closing a cavity air inlet valve, opening a cavity air outlet valve, releasing pressure of the tested cavity, and jumping to the step 8.2.
Further, the heating model containing heat dissipation, wherein,
the heater power includes an active power for heating the compressed gas within the test case and the test cavity, and a compensating power for compensating for heat dissipated to the environment by the test system,
the expression for heater power is as follows:
(1)
in the middle ofP desg The design power of the heater, W;P eff is a heaterW;ηthe effective power factor of the heater is dimensionless;P comp compensating power for the heater, W;ζthe compensation power factor of the heater is dimensionless;
the effective power expression of the heater is as follows:
(2)
in the middle ofm targ The mass m of the gas in the tested cavity when the tested cavity reaches the target state;e inc j/kg is the energy increase of the gas in the tested cavity from the ambient temperature to the target temperature;t feat is a characteristic time, representing the design time for loading the gas in the subject chamber from the ambient state to the target state, s,
the mass calculation expression of the gas in the cavity when the tested cavity reaches the target state is as follows:
(3)
in the middle ofV cham For the volume of the tested cavity, m 3 ；R g The gas constant of the gas medium, J/(kg.K);T targ k is the target temperature;p targ target pressure, mpa;
the internal energy increase calculation expression for the gas in the test chamber from ambient temperature to the target temperature is as follows:
(4)
in the middle ofc V The specific heat capacity is fixed for gas, J/(kg.K);T targ k is the target temperature;T amb is the ambient temperature, K;
the compensation power expression of the heater is as follows:
(5)
in the middle ofA surf For the effective convection heat exchange area between the tested case piece and the atmospheric environment, m 2 ；hW/(m) is the convective heat transfer coefficient 2 ·K)；T targ K is the target temperature;T amb is the temperature of the environment, K,ε case dimensionless value for the emissivity of the receiver elementε case =1；σTakes the value of Stefan-Boltzmann constantσ=5.67×10 -8 W/(m 2 ·K 4 )。
Further, the main purpose of the pressurized model containing air leakage is to realize quantitative control of the mass flow of the tested cavity in the process of adding, releasing or maintaining pressure to the tested cavity, wherein,
the mass flow expression of the air intake pipe is as follows:
(6)
in the middle ofQ ctrl+ The air inlet mass flow of the tested cavity in the process of pressurizing the tested cavity by the air storage tank is kg/s;A ctrl+ for the effective cross-sectional area of the air inlet pipeline of the tested cavity, m 2 ；κIs a gas isentropic index, and has no dimension valueκ=1.40；p stor The pressure of the gas in the gas storage tank is MPa;ρ stor is the density of gas in the gas storage tank, kg/m 3 ；p cham The pressure of the gas in the tested cavity is MPa;p in* the pressure of the gas in the tested cavity is MPa when the gas inlet pipe is in a critical state in the process of pressurizing the tested cavity by the gas storage tank;
when the air inlet pipeline of the tested cavity is in a critical state in the pressurizing process, the pressure expression of the air in the tested cavity is as follows:
(7)
in the middle ofp stor The pressure of the gas in the gas storage tank is Mpa;κis a gas isentropic index, and has no dimension valueκ=1.40；
The mass flow expression of the exhaust duct is as follows:
(8)
in the middle ofQ ctrl- The exhaust mass flow of the exhaust pipeline in the pressure relief process of the tested cavity is kg/s;A ctrl- for the effective cross-sectional area of the exhaust pipeline of the tested cavity, m 2 ；κIs a gas isentropic index, and has no dimension valueκ=1.40；p cham The pressure of the gas in the tested cavity is MPa;ρ cham to the gas density in the test cavity, kg/m 3 ；p amb Is the ambient pressure, MPa;p out* the pressure of the gas in the tested cavity is MPa when the exhaust pipeline is in a critical state in the pressure relief process of the tested cavity;
when the exhaust pipe of the tested cavity is in a critical state in the pressure release process, the pressure expression of the gas in the tested cavity is as follows:
(9)
in the middle ofp amb Is the ambient pressure, MPa;κis a gas isentropic index, and has no dimension valueκ=1.40；
The mass flow expression of the equivalent blow-by pipe is as follows:
(10)
in the middle ofQ leak The leakage mass flow of the equivalent leakage pipeline in the leakage process of the tested cavity is kg/s;A leak for the effective cross-sectional area of the equivalent leakage pipeline of the tested cavity, m 2 ；κIs a gas isentropic index, and has no dimension valueκ=1.40；p cham The pressure of the gas in the tested cavity is MPa;ρ cham to the gas density in the test cavity, kg/m 3 ；p amb Is the ambient pressure, MPa;p out* is the pressure of the gas in the tested cavity, mpa when the exhaust pipeline is in a critical state in the pressure relief process of the tested cavity.
The beneficial effects are that: compared with the prior art, the method fully considers the factors such as the mutual influence between temperature and pressure in the loading process, the influence of the test system on the loading process caused by external heat dissipation and air leakage phenomena, and the like, and is beneficial to effectively solving the problem of poor pressure and temperature control precision in the test and assessment process of the thermal internal pressure fatigue of the outer culvert casing of the existing aeroengine. Meanwhile, the invention can be widely applied to accurate loading control of temperature and pressure in similar engineering projects. The method is beneficial to effectively solving the problem of poor pressure and temperature control precision in the test and examination process of the thermal internal pressure fatigue of the outer culvert casing of the existing aero engine.
Drawings
FIG. 1 is a schematic diagram of the connection structure of the system of the present invention;
FIG. 2 is a flow chart of a method of testing thermal internal pressure fatigue of a receiver;
FIG. 3 is a "target temperature dynamic load-maintaining" subroutine of the flowchart of FIG. 2;
FIG. 4 is a "target pressure dynamic dwell" subroutine of the flowchart of FIG. 2;
FIG. 5 is a "target pressure load" subroutine of the flowchart of FIG. 2;
FIG. 6 is a "target pressure unloading" subroutine of the flowchart of FIG. 2;
FIG. 7 is a flow chart of an exemplary case thermal internal pressure fatigue test embodiment of the test system;
FIG. 8 is a schematic diagram of a typical fatigue pressure load curve;
FIG. 9 is a load control graph of an exemplary case thermal internal pressure fatigue test embodiment.
In the figure: 10-tested cavity, 20-gas storage tank, 30-gas source air compressor, 40-silicon controlled rectifier power supply, 50-integrated controller, 60-control computer, 70-ambient air, 80-compressed air, 90-high-temperature compressed air and 100-equivalent leakage hole; the device comprises a test case 11-a test case 12-an upper simulation section, a lower simulation section 13-a cavity base 14-a cavity big bolt 15-a cavity big nut 16-a cavity big nut 17-a heater 18-a cavity air inlet pipe 19-a cavity air outlet pipe; 21-cavity air inlet valve, 22-cavity air outlet valve, 23-temperature sensor, 24-pressure sensor, 25-one-way valve, 26-remote air delivery pipe, 27-air storage tank safety valve and 28-air storage tank air outlet pipe; 31-gas storage tank air inlet valve, 32-gas storage tank air inlet pipe.
Detailed Description
In order that the above-recited objects, features and advantages of the present invention will be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings and appended detailed description. In addition, embodiments of the present application and features of the embodiments may be combined with each other without conflict. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, and the described embodiments are merely some, rather than all, embodiments of the present invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the present invention without making any inventive effort, are intended to fall within the scope of the present invention. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used herein in the description of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention.
In various embodiments of the invention, for convenience in description and not limitation, the term "coupled" as used in the specification and claims is not limited to a physical or mechanical connection, but may include an electrical connection, whether direct or indirect. "upper", "lower", "left", "right", etc. are used merely to indicate a relative positional relationship, and when the absolute position of the object to be described is changed, the relative positional relationship is changed accordingly.
Referring to fig. 1 in detail, the embodiment provides a method for adopting an engine casing thermal internal pressure fatigue test loading system, which establishes the engine casing thermal internal pressure fatigue test loading system and a heating model containing heat dissipation, and realizes quantitative control of heater power in the heating process of a tested cavity; establishing a pressurized model containing air leakage, and realizing quantitative control of the mass flow of the tested cavity in the process of adding, releasing or maintaining the pressure of the tested cavity; establishing temperature-pressure coupling control, realizing the cross iterative control of the temperature and the pressure of the tested cavity in the heating and the pressurizing processes of the tested cavity,
firstly, establishing an engine case thermal internal pressure fatigue test loading system, which comprises an air source system, a temperature loading system, a pressure loading system and a tested cavity, wherein the air source system is connected with the tested cavity, the tested cavity is respectively connected with the pressure loading system and the temperature loading system, and the temperature loading system comprises a control computer 60, a comprehensive controller 50, a silicon controlled rectifier power supply 40, a heater 17 and a temperature sensor 23; the temperature sensor 23 collects temperature signals in the tested cavity 10, the temperature signals are transmitted to the control computer 60 through the integrated controller 50, the control computer 60 feeds back information to the integrated controller 50, and the integrated controller 50 drives the silicon controlled power supply 40 to control the heater 17 to work, so that a dynamic stable circulation system is formed between the temperature in the tested cavity and the target temperature;
the air source system mainly comprises an air source air compressor 30, an air source air storage tank 20, an air storage tank air inlet valve 31, an air storage tank safety valve 27 and the like; the air source storage tank 20 is connected with the tested cavity 10 through the check valve 25 and the cavity air inlet valve 21 and is used for providing compressed air 80 for pressure loading of the tested cavity 10.
The temperature loading system mainly comprises a control computer 60, a comprehensive controller 50, a silicon controlled power supply 40, a heater 17, a temperature sensor 23 and the like; the temperature loading system collects temperature signals in the tested cavity 10 through the temperature sensor 23, the temperature signals are transmitted to the control computer 60 through the integrated controller 50, the control computer 60 compares the temperature signals with a program set target temperature and feeds back information to the integrated controller 50, the integrated controller 50 drives the silicon controlled power supply 40 to control the heater 17 to work, and the temperature in the tested cavity 10 and the target temperature are iterated to form dynamic stability.
The pressure loading system mainly comprises a control computer 60, a comprehensive controller 50, an air source system, a cavity air inlet valve 21, a cavity air outlet valve 22, a pressure sensor 24 and the like; the pressure loading system collects pressure signals in the tested cavity 10 through the pressure sensor 24, the pressure signals are transmitted to the control computer 60 through the integrated controller 50, the control computer 60 compares the pressure signals with the target pressure set by a program and feeds back information to the integrated controller 50, the integrated controller 50 drives the cavity air inlet valve 21 and the cavity air outlet valve 22 to work, and the pressure signals are circularly iterated until the pressure in the tested cavity 10 and the target pressure form dynamic stability; wherein the working environment of the cavity exhaust valve 22 is high in temperature, and a pneumatic electromagnetic valve is recommended for meeting the continuous high-temperature working performance.
The tested cavity 10 mainly comprises a tested casing 11, an upper simulation section 12, a lower simulation section 13, a cavity base 14, a cavity large bolt 15, a cavity large nut 16 and the like; the tested cavity 10 is a test cavity which is formed by encircling a tested casing 11, an upper simulation section 12, a lower simulation section 13 and a cavity base 14 and bears temperature and pressure loads; the cavity big bolt 15 and the cavity big nut 16 lock the tested cavity 10, bear the axial force of the tested cavity 10 generated by the internal pressure, and the upper simulation section 12 and the lower simulation section 13 are mainly used for providing the rigidity boundary of the tested casing 11.
Referring to fig. 2 to 6, the invention provides a flow chart of a thermal internal pressure fatigue test method, and a typical fatigue pressure load curve schematic diagram shown in fig. 8, and combines actual measurement data of an engine under a typical flight condition, and by using the test system and the test method provided by the invention, a simulated test of the thermal internal pressure fatigue of the ground of a culvert casing of a typical aeroengine is developed, and a typical embodiment in the test process is shown in fig. 7, wherein the specific flow is as follows:
the specific flow of the temperature-pressure coupling control method of the invention is as follows:
step 1, starting, calling a target temperature dynamic load-keeping subroutine to heat a tested cavity;
step 2, the tested cavity reaches a high-temperature target state;
step 3, entering a high-temperature fatigue pressure loading circulation stage;
step 4, a target pressure loading subprogram is called to pressurize the tested cavity, and a target temperature dynamic load maintaining subprogram is synchronously called to control the heat preservation of the tested cavity;
step 5, the tested cavity reaches a high-temperature high-pressure target state;
step 6, invoking a target pressure dynamic load-keeping subprogram to perform pressure-maintaining control on the tested cavity, and synchronously invoking a target temperature dynamic load-keeping subprogram to perform heat-preserving control on the tested cavity;
step 7, maintaining the tested cavity in a high-temperature high-pressure target state;
step 8, a target pressure unloading subprogram is called to release pressure of the tested cavity, and a target temperature dynamic load maintaining subprogram is synchronously called to control heat preservation of the tested cavity;
step 9, the tested cavity reaches a high-temperature low-pressure target state;
step 10, invoking a target pressure dynamic load-keeping subprogram to perform pressure-maintaining control on the tested cavity, and synchronously invoking a target temperature dynamic load-keeping subprogram to perform heat-preserving control on the tested cavity;
step 11, maintaining a high-temperature low-pressure target state in the tested cavity;
step 12, judging whether the high-temperature fatigue pressure loading cycle is finished, if not, jumping to step 4, and if so, sequentially executing step 13;
step 13, stopping heating and pressurizing;
step 14, checking and testing the state of the tested case;
and 15, carrying out a next-level fatigue test or ending the test.
Referring to fig. 3 in detail, the preferred scheme of this embodiment is that the flow of the target temperature dynamic maintenance subroutine in step 1 is as follows:
step 1.1, starting to call a subprogram;
step 1.2, a comprehensive controller collects temperature signals of a temperature sensor in a tested cavity;
step 1.3, comparing the measured temperature with the target temperature, if the measured temperature is less than or equal to the target temperature-tolerance lower limit, jumping to step 1.4, if the measured temperature is more than or equal to the target temperature + tolerance upper limit, jumping to step 1.5, and if the target temperature-tolerance lower limit is less than the measured temperature and less than the target temperature + tolerance upper limit, jumping to step 1.6;
step 1.4, driving a heater to work by a silicon controlled power supply, and jumping to step 1.2;
step 1.5, stopping the heater, and jumping to step 1.2;
step 1.6, the temperature loading system maintains an iteration instruction and jumps to step 1.2.
Referring to fig. 5 in detail, the preferred scheme of this embodiment is that the target pressure loading subroutine described in step 4 is as follows:
step 4.1, starting to call a subprogram;
step 4.2, collecting pressure signals of the pressure sensor in the tested cavity by the comprehensive controller;
step 4.3, comparing the measured pressure with the target pressure, if the measured pressure is less than the high target pressure plus the upper limit of the tolerance, jumping to step 4.4, and if the measured pressure is more than or equal to the high target pressure plus the upper limit of the tolerance, jumping to step 4.5;
step 4.4, closing a cavity exhaust valve, opening a cavity air inlet valve, pressurizing a tested cavity, and jumping to the step 4.2;
step 4.5, closing a cavity air inlet valve, closing a cavity air outlet valve and enabling the tested cavity to enter a pressure maintaining state, and jumping to the step 4.2;
referring to fig. 4 in detail, the preferred scheme of this embodiment is that the target pressure dynamic maintenance subroutine flow described in step 6 is as follows:
step 6.1, starting to call a subprogram;
step 6.2, collecting pressure signals of the pressure sensor in the tested cavity by the comprehensive controller;
step 6.3, comparing the measured pressure with the target pressure, if the measured pressure is less than or equal to the target pressure-tolerance lower limit, jumping to step 6.4, if the measured pressure is more than or equal to the target pressure + tolerance upper limit, jumping to step 6.5, and if the target pressure-tolerance lower limit is less than the measured pressure and less than the target pressure + tolerance upper limit, jumping to step 6.6;
step 6.4, closing a cavity exhaust valve, opening a cavity air inlet valve, pressurizing a tested cavity, and jumping to the step 6.2;
step 6.5, closing a cavity air inlet valve, opening a cavity air outlet valve, releasing pressure of the tested cavity, and jumping to the step 6.2;
and 6.6, closing a cavity air inlet valve, closing a cavity air outlet valve and enabling the tested cavity to enter a pressure maintaining state, and jumping to the step 6.2.
Referring to fig. 6 in detail, a preferred embodiment of the present embodiment is that the target pressure unloading subroutine described in step 8 has the following flow:
step 8.1, starting to call a subprogram;
step 8.2, collecting pressure signals of the pressure sensor in the tested cavity by the comprehensive controller;
step 8.3, comparing the measured pressure with the target pressure, if the measured pressure is less than the low target pressure plus the upper limit of the tolerance, jumping to step 8.4, and if the measured pressure is more than or equal to the low target pressure plus the upper limit of the tolerance, jumping to step 8.5;
step 8.4, closing a cavity air inlet valve, closing a cavity air outlet valve and enabling the tested cavity to enter a pressure maintaining state, and jumping to the step 8.2;
and 8.5, closing a cavity air inlet valve, opening a cavity air outlet valve, releasing pressure of the tested cavity, and jumping to the step 8.2.
In a preferred embodiment of this embodiment, the heating model with heat dissipation, wherein,
the heater power includes an active power for heating the compressed gas within the test case and the test cavity, and a compensating power for compensating for heat dissipated to the environment by the test system,
the expression for heater power is as follows:
(1)
in the middle ofP desg The design power of the heater, W;P eff is the effective power of the heater, W;ηthe effective power factor of the heater is dimensionless;P comp compensating power for the heater, W;ζthe compensation power factor of the heater is dimensionless;
the effective power expression of the heater is as follows:
(2)
in the middle ofm targ The mass m of the gas in the tested cavity when the tested cavity reaches the target state;e inc j/kg is the energy increase of the gas in the tested cavity from the ambient temperature to the target temperature;t feat is a characteristic time, representing the design time for loading the gas in the subject chamber from the ambient state to the target state, s,
the mass calculation expression of the gas in the cavity when the tested cavity reaches the target state is as follows:
(3)
in the middle ofV cham For the volume of the tested cavity, m 3 ；R g The gas constant of the gas medium, J/(kg.K);T targ k is the target temperature;p targ target pressure, mpa;
the internal energy increase calculation expression for the gas in the test chamber from ambient temperature to the target temperature is as follows:
(4)
in the middle ofc V The specific heat capacity is fixed for gas, J/(kg.K);T targ k is the target temperature;T amb is the ambient temperature, K;
the compensation power expression of the heater is as follows:
(5)
in the middle ofA surf For the effective convection heat exchange area between the tested case piece and the atmospheric environment, m 2 ；hW/(m) is the convective heat transfer coefficient 2 ·K)；T targ K is the target temperature;T amb is the temperature of the environment, K,ε case dimensionless value for the emissivity of the receiver elementε case =1；σTakes the value of Stefan-Boltzmann constantσ=5.67×10 -8 W/(m 2 ·K 4 )。
Further, the main purpose of the pressurized model containing air leakage is to realize quantitative control of the mass flow of the tested cavity in the process of adding, releasing or maintaining pressure to the tested cavity, wherein,
the mass flow expression of the air intake pipe is as follows:
(6)
in the middle ofQ ctrl+ The air inlet mass flow of the tested cavity in the process of pressurizing the tested cavity by the air storage tank is kg/s;A ctrl+ for the effective cross-sectional area of the air inlet pipeline of the tested cavity, m 2 ；κIs a gas isentropic index, and has no dimension valueκ=1.40；p stor The pressure of the gas in the gas storage tank is MPa;ρ stor is the density of gas in the gas storage tank, kg/m 3 ；p cham The pressure of the gas in the tested cavity is MPa;p in* the pressure of the gas in the tested cavity is MPa when the gas inlet pipe is in a critical state in the process of pressurizing the tested cavity by the gas storage tank;
when the air inlet pipeline of the tested cavity is in a critical state in the pressurizing process, the pressure expression of the air in the tested cavity is as follows:
(7)
in the middle ofp stor The pressure of the gas in the gas storage tank is Mpa;κis a gas isentropic index, and has no dimension valueκ=1.40；
The mass flow expression of the exhaust duct is as follows:
(8)
in the middle ofQ ctrl- The exhaust mass flow of the exhaust pipeline in the pressure relief process of the tested cavity is kg/s;A ctrl- for the effective cross-sectional area of the exhaust pipeline of the tested cavity, m 2 ；κIs a gas isentropic index, and has no dimension valueκ=1.40；p cham The pressure of the gas in the tested cavity is MPa;ρ cham to the gas density in the test cavity, kg/m 3 ；p amb Is the ambient pressure, MPa;p out* the pressure of the gas in the tested cavity is MPa when the exhaust pipeline is in a critical state in the pressure relief process of the tested cavity;
when the exhaust pipe of the tested cavity is in a critical state in the pressure release process, the pressure expression of the gas in the tested cavity is as follows:
(9)
in the middle ofp amb Is the ambient pressure, MPa;κis a gas isentropic index, and has no dimension valueκ=1.40；
The mass flow expression of the equivalent blow-by pipe is as follows:
(10)
in the middle ofQ leak The leakage mass flow of the equivalent leakage pipeline in the leakage process of the tested cavity is kg/s;A leak for the effective cross-sectional area of the equivalent leakage pipeline of the tested cavity, m 2 ；κIs a gas isentropic index, and has no dimension valueκ=1.40；p cham The pressure of the gas in the tested cavity is MPa;ρ cham to the gas density in the test cavity, kg/m 3 ；p amb Is the ambient pressure, MPa;p out* is the pressure of the gas in the tested cavity, mpa when the exhaust pipeline is in a critical state in the pressure relief process of the tested cavity.
All relevant parameters in the typical test and analysis model in this embodiment are referenced to the actual data of the ground test system. The pressures described in the analysis are absolute pressures. Volume of the cavity under testV cham Is 0.8m 3 . The gas in the gas storage tank is compressed air, and the gas constant of the airR g 28.96 ×10 -3 J/(kg.K), specific heat capacity of airc V 0.717X 10 3 J/(kg.K), isentropic index of airκ1.40. Absolute pressure value of standard atmospheric environmentp amb Is 0.101MPa. Ambient temperature value of atmospheric environmentT amb 20 ℃ (293.15K). Convection heat transfer coefficient of airhIs 10W/(m) 2 K). The rated power of the heater is designed asP desg =60 kW. Design of gas storage tank volume and sampling of tested cavityV stor =V cham Is 0.8m 3 The initial pressure in the gas storage tank is the upper pressure limit of the gas in the gas storage tankp Ulim The lower pressure limit of the gas in the gas storage tank is set to be 1.00MPap Llim The pressure of the gas in the gas storage tank is set to be 0.90Mpa, and the pressure is automatically controlled by the air compression system and maintained between the upper limit and the lower limit. The target pressure in the tested cavity isp targ =0.653 MPa, the size of the cross-sectional area of the inlet aperture of the chamber under testϕ in Vent cross-sectional area size of the test cavity =7.8mmϕ out Equivalent leakage orifice cross-sectional area size of the test cavity =16.5mmϕ leak =0 mm to 0.4ϕ in . The pressure fatigue loading period ist cycle =50s, intra-cycle pressure loading time oft load =22s, intra-cycle pressure retention time oft hold =3s, periodic internal pressure unloading time oft upload =22s。
The comparison of the temperature and pressure measured curves of the above typical test examples with the temperature and pressure analysis curves calculated by the heat radiation-containing heating model and the air leakage-containing pressurizing model is shown in fig. 9. The pressure analysis is well matched with the actual measurement curve, and the pressure control precision is good. The temperature measured curve is slightly delayed from the analysis curve, because the thermal inertia of the heater 17 is not considered by the heating model containing heat dissipation, the temperature control precision is within +/-5 ℃, and the control requirement within +/-10 ℃ is met.
In summary, compared with the prior art, the invention provides the accurate loading system and the method for the external culvert casing thermal internal pressure fatigue test, which consider the influence on the external heat dissipation and the air leakage phenomenon in the thermal internal pressure loading process, consider the mutual influence of temperature and pressure in the thermal internal pressure loading process, and can effectively realize the accurate control of the temperature and the pressure in the thermal internal pressure fatigue test loading process of the tested cavity.
The comparison of the temperature and pressure measured curves of the above typical test examples with the temperature and pressure analysis curves calculated by the heat radiation-containing heating model and the air leakage-containing pressurizing model is shown in fig. 9. The pressure analysis is well matched with the actual measurement curve, and the pressure control precision is good. The temperature measured curve is slightly delayed from the analysis curve, because the thermal inertia of the heater 17 is not considered by the heating model containing heat dissipation, the temperature control precision is within +/-5 ℃, and the control requirement within +/-10 ℃ is met.
The foregoing detailed description of a system and method for loading a thermal internal pressure fatigue test of an engine casing with reference to the embodiments is illustrative and not limiting, and several embodiments can be listed in the scope defined thereby, and therefore, variations and modifications without departing from the general inventive concept shall fall within the scope of protection of the present invention.
Claims (6)
1. A method for loading a system by adopting an engine case thermal internal pressure fatigue test is characterized by comprising the following steps: the method comprises the steps of establishing a loading system of an engine case thermal internal pressure fatigue test and a heating model containing heat dissipation, and realizing quantitative control of heater power in the heating process of a tested cavity; establishing a pressurized model containing air leakage, and realizing quantitative control of the mass flow of the tested cavity in the process of adding, releasing or maintaining the pressure of the tested cavity; establishing temperature-pressure coupling control, and realizing cross iteration control of the temperature and the pressure of the tested cavity in the heating and pressurizing process of the tested cavity, wherein the specific flow of the temperature-pressure coupling control method is as follows: firstly, establishing a loading system for a thermal internal pressure fatigue test of an engine case, wherein the loading system comprises an air source system, a temperature loading system, a pressure loading system and a tested cavity, the air source system is connected with the tested cavity, the tested cavity is respectively connected with the pressure loading system and the temperature loading system, and the temperature loading system comprises a control computer, a comprehensive controller, a silicon controlled rectifier power supply, a heater and a temperature sensor; the temperature sensor collects temperature signals in the tested cavity, the temperature signals are transmitted to the control computer through the comprehensive controller, the control computer feeds back information to the comprehensive controller, and the comprehensive controller drives the silicon controlled power supply to control the heater to work, so that a dynamic stable circulating system is formed between the temperature in the tested cavity and the target temperature; the pressure loading system collects pressure signals in the tested cavity through the pressure sensor, the pressure signals are transmitted to the control computer through the comprehensive controller, the control computer feeds back information to the comprehensive controller, and then the comprehensive controller drives the cavity air inlet valve and the cavity air outlet valve to work, so that a dynamic stable circulation control system is formed by the pressure in the tested cavity and the target pressure;
step 1, starting, calling a target temperature dynamic load-keeping subroutine to heat a tested cavity;
step 2, the tested cavity reaches a high-temperature target state;
step 3, entering a high-temperature fatigue pressure loading circulation stage;
step 4, a target pressure loading subprogram is called to pressurize the tested cavity, and a target temperature dynamic load maintaining subprogram is synchronously called to control the heat preservation of the tested cavity;
step 5, the tested cavity reaches a high-temperature high-pressure target state;
step 6, invoking a target pressure dynamic load-keeping subprogram to perform pressure-maintaining control on the tested cavity, and synchronously invoking a target temperature dynamic load-keeping subprogram to perform heat-preserving control on the tested cavity;
step 7, maintaining the tested cavity in a high-temperature high-pressure target state;
step 8, a target pressure unloading subprogram is called to release pressure of the tested cavity, and a target temperature dynamic load maintaining subprogram is synchronously called to control heat preservation of the tested cavity;
step 9, the tested cavity reaches a high-temperature low-pressure target state;
step 10, invoking a target pressure dynamic load-keeping subprogram to perform pressure-maintaining control on the tested cavity, and synchronously invoking a target temperature dynamic load-keeping subprogram to perform heat-preserving control on the tested cavity;
step 11, maintaining a high-temperature low-pressure target state in the tested cavity;
step 12, judging whether the high-temperature fatigue pressure loading cycle is finished, if not, jumping to step 4, and if so, sequentially executing step 13;
step 13, stopping heating and pressurizing;
step 14, checking and testing the state of the tested case;
step 15, developing a next-level fatigue test or ending the test;
the heat dissipation-containing heating model comprises effective power and compensation power, wherein the effective power is used for heating compressed gas in a tested casing piece and a tested cavity, the compensation power is used for compensating heat dissipated into the environment through a test system, and the expression of the heater power is as follows:in the middle ofP desg The design power of the heater, W;P eff is the effective power of the heater, W;ηthe effective power factor of the heater is dimensionless;P comp compensating power for the heater, W;ζto addThe compensation power factor of the heater is dimensionless; the effective power expression of the heater is as follows:in the middle ofm targ The mass m of the gas in the tested cavity when the tested cavity reaches the target state;e inc j/kg is the energy increase of the gas in the tested cavity from the ambient temperature to the target temperature;t feat for the characteristic time, the design time s for loading the gas in the tested cavity from the environment state to the target state is represented as follows: />In the middle ofV cham For the volume of the tested cavity, m 3 ；R g The gas constant of the gas medium, J/(kg.K);T targ k is the target temperature;p targ target pressure, mpa; the internal energy increase calculation expression for the gas in the test chamber from ambient temperature to the target temperature is as follows: />In the middle ofc V The specific heat capacity is fixed for gas, J/(kg.K);T targ k is the target temperature;T amb is the ambient temperature, K; the compensation power expression of the heater is as follows: />In the middle ofA surf For the effective convection heat exchange area between the tested case piece and the atmospheric environment, m 2 ；hW/(m) is the convective heat transfer coefficient 2 ·K)；T targ K is the target temperature;T amb is the temperature of the environment, K,ε case dimensionless value for the emissivity of the receiver elementε case =1；σIs Stefan-Boltzmann constant, valueσ=5.67×10 -8 W/(m 2 ·K 4 )。
2. The method according to claim 1, characterized in that: the target temperature dynamic load-keeping subroutine flow described in the step 1 is as follows: step 1.1, starting to call a subprogram; step 1.2, a comprehensive controller collects temperature signals of a temperature sensor in a tested cavity; step 1.3, comparing the measured temperature with the target temperature, if the measured temperature is less than or equal to the target temperature-tolerance lower limit, jumping to step 1.4, if the measured temperature is more than or equal to the target temperature + tolerance upper limit, jumping to step 1.5, and if the target temperature-tolerance lower limit is less than the measured temperature and less than the target temperature + tolerance upper limit, jumping to step 1.6; step 1.4, driving a heater to work by a silicon controlled power supply, and jumping to step 1.2; step 1.5, stopping the heater, and jumping to step 1.2; step 1.6, the temperature loading system maintains an iteration instruction and jumps to step 1.2.
3. The method according to claim 1, characterized in that: the target pressure loading subroutine flow described in step 4 is as follows: step 4.1, starting to call a subprogram; step 4.2, collecting pressure signals of the pressure sensor in the tested cavity by the comprehensive controller; step 4.3, comparing the measured pressure with the target pressure, if the measured pressure is less than the high target pressure plus the upper limit of the tolerance, jumping to step 4.4, and if the measured pressure is more than or equal to the high target pressure plus the upper limit of the tolerance, jumping to step 4.5; step 4.4, closing a cavity exhaust valve, opening a cavity air inlet valve, pressurizing a tested cavity, and jumping to the step 4.2; and 4.5, closing a cavity air inlet valve, closing a cavity air outlet valve and enabling the tested cavity to enter a pressure maintaining state, and jumping to the step 4.2.
4. The method according to claim 1, characterized in that: the flow of the target pressure dynamic load maintaining subroutine in the step 6 is as follows: step 6.1, starting to call a subprogram; step 6.2, collecting pressure signals of the pressure sensor in the tested cavity by the comprehensive controller; step 6.3, comparing the measured pressure with the target pressure, if the measured pressure is less than or equal to the target pressure-tolerance lower limit, jumping to step 6.4, if the measured pressure is more than or equal to the target pressure + tolerance upper limit, jumping to step 6.5, and if the target pressure-tolerance lower limit is less than the measured pressure and less than the target pressure + tolerance upper limit, jumping to step 6.6; step 6.4, closing a cavity exhaust valve, opening a cavity air inlet valve, pressurizing a tested cavity, and jumping to the step 6.2; step 6.5, closing a cavity air inlet valve, opening a cavity air outlet valve, releasing pressure of the tested cavity, and jumping to the step 6.2; and 6.6, closing a cavity air inlet valve, closing a cavity air outlet valve and enabling the tested cavity to enter a pressure maintaining state, and jumping to the step 6.2.
5. The method according to claim 1, characterized in that: the target pressure unloading subroutine flow described in step 8 is as follows: step 8.1, starting to call a subprogram; step 8.2, collecting pressure signals of the pressure sensor in the tested cavity by the comprehensive controller; step 8.3, comparing the measured pressure with the target pressure, if the measured pressure is less than the low target pressure plus the upper limit of the tolerance, jumping to step 8.4, and if the measured pressure is more than or equal to the low target pressure plus the upper limit of the tolerance, jumping to step 8.5; step 8.4, closing a cavity air inlet valve, closing a cavity air outlet valve and enabling the tested cavity to enter a pressure maintaining state, and jumping to the step 8.2; and 8.5, closing a cavity air inlet valve, opening a cavity air outlet valve, releasing pressure of the tested cavity, and jumping to the step 8.2.
6. The method according to claim 1, characterized in that: the air leakage-containing pressurization model aims to realize quantitative control of the mass flow of the tested cavity in the process of adding, releasing or maintaining the pressure of the tested cavity, wherein the mass flow expression of the air inlet pipeline is as follows:in the middle ofQ ctrl+ The air inlet mass flow of the tested cavity in the process of pressurizing the tested cavity by the air storage tank is kg/s;A ctrl+ for the effective cross-sectional area of the air inlet pipeline of the tested cavity, m 2 ；κIs a gas isentropic index, and has no dimension valueκ=1.40；p stor Is an air storage tankInternal gas pressure, MPa;ρ stor is the density of gas in the gas storage tank, kg/m 3 ；p cham The pressure of the gas in the tested cavity is MPa;p in* the pressure of the gas in the tested cavity is MPa when the gas inlet pipe is in a critical state in the process of pressurizing the tested cavity by the gas storage tank; when the air inlet pipeline of the tested cavity is in a critical state in the pressurizing process, the pressure expression of the air in the tested cavity is as follows: />In the middle ofp stor The pressure of the gas in the gas storage tank is Mpa;κis a gas isentropic index, and has no dimension valueκ=1.40; the mass flow expression of the exhaust duct is as follows: />In the middle ofQ ctrl- The exhaust mass flow of the exhaust pipeline in the pressure relief process of the tested cavity is kg/s;A ctrl- for the effective cross-sectional area of the exhaust pipeline of the tested cavity, m 2 ；κIs a gas isentropic index, and has no dimension valueκ=1.40；p cham The pressure of the gas in the tested cavity is MPa;ρ cham to the gas density in the test cavity, kg/m 3 ；p amb Is the ambient pressure, MPa;p out* the pressure of the gas in the tested cavity is MPa when the exhaust pipeline is in a critical state in the pressure relief process of the tested cavity; when the exhaust pipe of the tested cavity is in a critical state in the pressure release process, the pressure expression of the gas in the tested cavity is as follows: />In the middle ofp amb Is the ambient pressure, MPa;κis a gas isentropic index, and has no dimension valueκ=1.40; the mass flow expression of the equivalent blow-by pipe is as follows:in the middle ofQ leak The leakage mass flow of the equivalent leakage pipeline in the leakage process of the tested cavity is kg/s;A leak for the effective cross-sectional area of the equivalent leakage pipeline of the tested cavity, m 2 ；κIs a gas isentropic index, and has no dimension valueκ=1.40；p cham The pressure of the gas in the tested cavity is MPa;ρ cham to the gas density in the test cavity, kg/m 3 ；p amb Is the ambient pressure, MPa;p out* is the pressure of the gas in the tested cavity, mpa when the exhaust pipeline is in a critical state in the pressure relief process of the tested cavity.
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