Low-energy-consumption turbine blade cooling test device and test method thereof

Abstract

The invention relates to a low-energy-consumption turbine blade cooling test device and a test method thereof. The test method comprises the following steps: establishing a function relationship of the opening degree of the regulating valve and a function relationship of the heat balance time length, regulating the temperature of the secondary cooling gas through the cooling test device, substituting the function to obtain the opening degree of the regulating valve, and then carrying out the test. The cooling test device comprises a bottom plate, a heat exchange assembly, a cooling source, a control cabinet and the like. The secondary cooling gas is cooled, the ratio of the main flow gas temperature to the secondary flow cooling gas temperature is # imgabs0, low energy consumption in the test process is achieved, meanwhile, heat exchangers with different flow rates can be flexibly selected for cooling, real-time monitoring and heating according to needs can be achieved, it is ensured that the test is accurate and reliable, the device structure is complete, and effective monitoring and adjusting are facilitated.

Description

Technical Field

[0001] The invention relates to the field of ground testing of aviation turbine coolers, and more specifically to a low-energy consumption turbine blade cooling test method and device. Background Art

[0002] In the process of gas turbine development, in order to design turbine cooling blades that meet performance requirements, it is necessary to calculate the mainstream gas temperature T of the turbine blades under thermally similar conditions, that is, the test conditions and the actual operating conditions. m and the secondary cooling gas temperature T c The dimensionless ratio of Under the same conditions, a large number of turbine blade cooling performance tests are carried out to accurately obtain the cooling and heat transfer characteristics of the turbine blades. At present, when conducting turbine blade cooling test research, the commonly used method is to heat the mainstream gas to achieve the temperature ratio of the mainstream gas and the secondary cooling gas in the process of simulating the turbine blade cooling test research. , usually the ratio of the mainstream gas temperature to the secondary cooling gas temperature . A large number of turbine blade cooling characteristic test studies will be carried out during the turbine blade cooling design process. When using this method, since the mainstream gas flow rate is usually about 10 times the secondary cooling gas flow rate, in most basic cooling test studies, the mainstream gas flow rate is even more than 50 times the secondary cooling gas flow rate. Therefore, during the turbine blade cooling test, the energy consumed by heating the mainstream gas is huge and the cost is extremely high. For example, the cooling effect test device for turbine rotor blades disclosed in patent application number CN202010762963.0, in the process of testing the turbine blades, the invention also uses the method of heating the main airflow to construct the temperature field required for the test. In its test process, it is necessary to configure a high-power heating element to continuously inject heat energy into a large amount of mainstream gas, so that the mainstream gas temperature rises to a predetermined level to achieve an adaptive temperature ratio relationship with the secondary cooling gas. However, what follows is that the energy consumption during the test process soars sharply, resulting in a huge waste of energy. Summary of the invention

[0003] An object of the present invention is to solve at least the above problems and / or disadvantages and to provide at least the advantages which will be described hereinafter.

[0004] In order to achieve these objectives and other advantages of the present invention, a low energy consumption turbine blade cooling test method is provided, comprising: Step 1: Carry out a pre-calibration test to make the mainstream gas temperature T m and the secondary cooling gas temperature T cThe ratio is greater than 2, and when the cooling test device reaches thermal equilibrium, record the secondary cooling gas flow m, the outlet temperature T of the secondary cooling gas and the actual opening A of the regulating valve of the cooling test device, and the thermal equilibrium time t s , obtain the pre-calibrated database, and establish the functional relationship between the regulating valve opening A and the flow rate and outlet temperature based on the pre-calibrated database: ; In the above formula, a ij represents a constant determined by the interpolation or fitting conditions, i The value range is from 0 to 3. j The value range is from 0 to 3. m i Expressed as gas flow m of i Power, T j Expressed as the cooling gas outlet temperature T j Power; And the time t to establish thermal equilibrium s Functional relationship between flow rate and outlet temperature: ; In the above formula, b ij constants determined by interpolation or fitting conditions, i The value range is from 0 to 3. j The value range is 0 to 3, m i is the air flow rate m i Power, T j is the cooling gas outlet temperature T j Power; Step 2: In the air inlet pipe of the nozzle, the temperature of the secondary cooling gas is reduced by the cooling test device to achieve low energy consumption during the test preparation process. During the test, different secondary cooling gas flow rates m and secondary cooling gas outlet temperatures T are input into the functional relationship corresponding to step 1 to obtain the theoretical opening A1 of the regulating valve and the thermal equilibrium time t s ; Step 3: Obtain the theoretical opening degree A1 and thermal equilibrium time t of the regulating valve in step 2 s After that, the system control cabinet adjusts the opening of the regulating valve to A1, and controls the cooling test device to start working, and the working time is t s After this series of operations, the mainstream gas temperature T m and the secondary cooling gas temperature T c When the ratio reaches the preset value, the cooling test of the turbine blades is carried out.

[0005] Preferably, in step three, when the outlet temperature of the secondary cooling gas is T1, the actual opening of the regulating valve of the cooling test device is A. When the difference between the actual regulating valve opening A and the theoretical opening A1 is greater than 2%, the actual regulating valve opening A is added to the pre-calibrated database in step one, and the functional relationship of the regulating valve opening is updated to achieve autonomous adjustment of the control accuracy of the system control cabinet.

[0006] Preferably, when the system control cabinet adjusts the opening of the regulating valve to A1, and the working time of the cooling test device is equal to t s Afterwards, the control law of the regulating valve is converted into the PID regulation mode. According to the flow rate of the secondary cooling gas, the control valve on the pipeline of the large-flow heat exchanger or the small-flow heat exchanger is selectively opened to make the secondary cooling gas enter the large-flow or small-flow heat exchanger cooling mode, so that the temperature of the secondary cooling gas can be adjusted to the set temperature value by adjusting the control valve of the cooling test device.

[0007] Preferably, in step three, the cooled secondary cooling gas is measured in real time by a temperature monitoring component, and when the difference between the real-time measured temperature value and the preset temperature is greater than a set value, the cooled secondary cooling gas is heated according to the measurement result; During the heating operation, based on the difference between the real-time measured temperature value and the preset temperature, heater I or heater II is selected to heat the secondary cooling gas at a large flow rate or a small flow rate.

[0008] A low-energy turbine blade cooling test device comprises: a base plate, a heat exchange component arranged on the base plate and connected to a secondary cooling gas, a cooling source arranged on the base plate and connected to an input end of a heat exchange cavity of the heat exchange component, an output end of a ventilation interface of the heat exchange component being connected to a nozzle, and a system control cabinet arranged on the base plate and communicatively connected to the heat exchange component and the cooling source.

[0009] Preferably, the heat exchange assembly comprises: a large flow heat exchanger and a small flow heat exchanger arranged on the bottom plate, the cooling source is communicated with the heat exchange cavity input ends of the large flow heat exchanger and the small flow heat exchanger respectively, and the ventilation interfaces of the large flow heat exchanger and the small flow heat exchanger are communicated with the input pipeline of the secondary cooling gas through a connecting pipeline; Among them, control valves are provided on the air inlet pipes of the large-flow heat exchanger and the small-flow heat exchanger, a mass flow meter is provided on the common air inlet pipe of the large-flow heat exchanger and the small-flow heat exchanger, and regulating valves are provided on the air inlet pipeline from the cooling source to the input end of the corresponding heat exchange cavity. The vaporization output end of each heat exchange cavity is connected to the outside through a pipeline, and the control valve, mass flow meter and regulating valve are communicatively connected to the system control cabinet.

[0010] Preferably, it further comprises: a heater I connected to the gas outlet of the large flow heat exchanger, a heater II connected to the gas outlet of the small flow heat exchanger, and the gas output ends of the heater I and the heater II are connected to the output end of the ventilation interface; Wherein, temperature monitoring components are provided on the connection pipelines between the heater I and the heater II and the large flow heat exchanger and the small flow heat exchanger, and the temperature monitoring components are communicatively connected with the system control cabinet.

[0011] The present invention has at least the following beneficial effects: 1. The secondary cooling gas is cooled by the cooling test device, so that the ratio of the mainstream gas temperature to the secondary cooling gas temperature is ; 2. The PID control method is used to adjust the opening, which can effectively adjust the cooling source flow of the secondary cooling test device and improve the accuracy and stability of temperature regulation; 3. According to the secondary cooling gas flow rate, select large and small flow heat exchangers and corresponding control valves to flexibly match different flow requirements and optimize the cooling effect; 4. Real-time measurement using the temperature monitoring component allows heating of the secondary cooling gas as needed to further precisely control the temperature and ensure the accuracy and reliability of the test.

[0012] Other advantages, objectives and features of the present invention will be embodied in part through the following description, and in part will be understood by those skilled in the art through study and practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] Figure 1 It is a schematic diagram of the overall structure of the cooling test device of the present invention; Figure 2 A top view of the cooling test device of the present invention; Figure 3 It is a schematic diagram of the overall structure of the cooling test device of the present invention; Figure 4 A schematic diagram of a test device using the cooling test method of the present invention; Figure 5 A schematic diagram of the test equipment in the existing turbine blade cooling test.

[0014] Figure numerals: 1. Base plate, 2. Heat exchange component, 21. Large flow heat exchanger, 22. Small flow heat exchanger, 23. Control valve, 24. Mass flow meter, 3. Cooling source, 31. Regulating valve, 4. Ventilation interface output end, 5. System control cabinet, 6. Heater I, 7. Heater II, 8. Temperature monitoring component, 9. Inlet pipe, 10. Vaporization output end, 11. Nozzle, 12. Heating device, 13. Turbine blades, 14. Exhaust section, 15. Cooling test device. DETAILED DESCRIPTION

[0015] The present invention is further described in detail below in conjunction with the accompanying drawings so that those skilled in the art can implement the invention with reference to the description.

[0016] A low-energy consumption turbine blade cooling test method of the present invention comprises: Step 1: Carry out a pre-calibration test to make the mainstream gas temperature T m and the secondary cooling gas temperature T c The ratio is greater than 2, and when the cooling test device 15 reaches thermal equilibrium, the secondary cooling gas flow m, the outlet temperature T of the secondary cooling gas and the actual opening A of the regulating valve 31 of the cooling test device 15 are recorded, and the thermal equilibrium time t s , obtain a pre-calibrated database, and establish a functional relationship between the opening A of the regulating valve 31 and the flow rate and outlet temperature based on the pre-calibrated database: ; And the time t to establish thermal equilibrium s Functional relationship between flow rate and outlet temperature: ; Step 2: In the air inlet pipeline of the nozzle 11, the temperature of the secondary cooling gas is reduced by the cooling test device 15 to achieve low energy consumption during the test preparation process. During the test, different secondary cooling gas flow rates m and secondary cooling gas outlet temperatures T are input into the functional relationship corresponding to step 1 to obtain the theoretical opening A1 of the regulating valve 31 and the thermal equilibrium time t s ; Step 3: The theoretical opening A1 and thermal equilibrium time t of the regulating valve 31 obtained in step 2 are s , the system control cabinet 5 adjusts the opening of the regulating valve 31 to A1, and at the same time allows the cooling test device 15 to work for a time equal to t s Then, the mainstream gas temperature T m and the secondary cooling gas temperature T c When the ratio of reaches a preset value, the cooling test of the turbine blade 13 is carried out. Using this technical solution, in the existing solution, it is assumed that the flow rate of the mainstream gas in the turbine blade cooling test is m a = 20 kg / s, the flow rate of the secondary cooling gas is m c = 1kg / s, the initial temperature of the mainstream gas and the secondary cooling gas is T m =T c =300K.

[0017] Working principle: like Figure 5As shown, during the test and research of the conventional cooling scheme for turbine blades 13, the mainstream gas is heated by the heating device 12 arranged in the nozzle 11, and the secondary cooling gas is also introduced into the nozzle 11. After the test of the turbine blades 13, the mainstream gas and the secondary cooling gas are discharged from the exhaust section 14. Under the test conditions, the heating amount of the mainstream air is Q a (Unit: kJ / s), effective heating capacity of air Q a It can be calculated using the following formula: In the formula, Q a ——Air heating, kJ / s c a ——Specific heat of air, 1.01 kJ / kg℃ (average) m a ——Flow rate of mainstream gas, assuming the maximum flow rate of a test bench is 20kg / s Δ t ——Temperature rise of heated air, take 300℃ The air heating Q a It is 6060 kJ / s.

[0018] And as Figure 4 As shown, using the low energy consumption cooling test method of this patent, under the same primary and secondary flow temperature ratio turbine blade cooling test conditions, the flow rate of the mainstream gas is m a = 20kg / s, flow rate of secondary cooling gas m c = 1kg / s, the initial temperature of the mainstream gas and the secondary cooling gas is T m =T c =300K, Under the test conditions, the effective cooling amount of the secondary gas is Q a '(unit kJ / s), the heat exchanger power is N (unit kW), and the effective air cooling amount is Q a ', In the above formula, Q a '——air cooling amount, kJ / s c a ——Specific heat of air, 1.01 kJ / kg℃ (average) m c ——The flow rate of the secondary cooling gas, assuming a maximum flow rate of 1kg / s for a test bench Δ t ——Air cooling range, take 150℃ The air energy consumption Q a ' is 151.5 kJ / s.

[0019] Energy consumption ratio: , from which it can be seen that the energy consumption is one fortieth of that of the traditional mainstream heating solution.

[0020] The method and steps for realizing high efficiency and energy saving in turbine blade cooling test of the present invention are as follows: 1. Perform a pre-calibration test to obtain the matching characteristics of the secondary cooling gas flow rate-the outlet temperature of the secondary cooling gas-the regulating valve 31 of the cooling source 3. If the flow rate is less than 10% of the maximum flow rate, close the control valve 23 on the large flow pipeline and open the control valve 23 on the small flow pipeline; if the flow rate through the mass flow meter 24 is greater than 10% of the maximum flow rate, close the small flow pipeline and open the large flow pipeline; 2. Open the secondary gas valve, and start the cooling test device 15 according to the pre-set flow rate range of 0kg / s to 1kg / s and the cooling outlet temperature range of 150K to 200K with an interval of 10%. When the cooling test device 15 reaches thermal equilibrium and the outlet temperature is constant, collect and record the secondary cooling gas flow rate, outlet temperature, opening degree of the regulating valve 31 of the cooling source 3 and other information; 3. Based on the collected information such as the secondary cooling gas flow rate, outlet temperature, and opening degree of the regulating valve 31 of the cooling source 3, a functional relationship between the opening degree of the regulating valve 31 of the cooling source 3 and the flow rate and temperature is established: ; And the time t to establish thermal equilibrium s Functional relationship between flow rate and outlet temperature: ; 4. According to the experimental needs, open the inlet valve of the secondary cooling gas, and according to the required outlet temperature of the secondary cooling gas, substitute it into the above functional relationship to obtain the theoretical opening A1 of the regulating valve 31 and the thermal equilibrium time t s ; 5. The secondary cooling gas flows through the secondary flow pipeline flow meter, and the system control cabinet 5 automatically determines the flow range. If the flow rate is less than 10% of the maximum flow rate, the control valve 23 on the pipeline of the large flow heat exchanger 21 is closed, and the control valve 23 on the pipeline of the small flow heat exchanger 22 is opened; if the flow rate through the flow meter is greater than 10% of the maximum flow rate, the control valve 23 of the small flow pipeline is closed, and the control valve 23 of the large flow pipeline is opened; 6. Open the cooling source 3 regulating device, and adjust the opening A1 of the regulating valve 31 and the thermal equilibrium time t according to the above-mentioned theoretical opening A1 of the regulating valve 31. s , given the opening A1 of the regulating valve 31 corresponding to the cooling source 3, and at the same time let the cooling test device 15 work for a time equal to t s Afterwards, the control law of the regulating valve 31 is converted into a PID regulation mode, and the flow rate of the cooling source 3 is adjusted in combination with the PID control method to adjust the secondary flow gas temperature to the set temperature value. Among them, the cooling source 3 used in the present invention is liquid nitrogen. In actual operation, different cooling sources 3 can be selected as needed, and pre-calibration tests can be performed to obtain the functional relationship corresponding to the cooling source 3. At the same time, in the actual operation process, when the outlet temperature of the secondary cooling gas is T1, the actual opening of the regulating valve 31 of the cooling test device 15 is A. When the difference between the actual opening A of the regulating valve 31 and the theoretical opening A1 is greater than 2%, the actual opening A of the regulating valve 31 is added to the pre-calibration database in step one, and the functional relationship of the opening of the regulating valve 31 is updated to realize the autonomous adjustment of the control accuracy of the system control cabinet 5.

[0021] 7. The cooled secondary cooling gas is measured in real time by the temperature monitoring component 8. When the difference between the real-time measured temperature value and the preset temperature is greater than 3K, the cooled secondary cooling gas is heated; wherein, during the heating operation, based on the difference between the real-time measured temperature value and the preset temperature, the heater I6 or the heater II7 is selected to heat the secondary cooling gas at a large flow rate or a small flow rate. The temperature monitoring component 8 is used for real-time measurement, and the secondary cooling gas can be heated as needed to further accurately control the temperature and ensure the accuracy and reliability of the test.

[0022] Figure 1-Figure 3 A low-energy turbine blade cooling test device is shown, comprising: a base plate 1, a heat exchange component 2 arranged on the base plate 1 and connected to the secondary cooling gas, a cooling source 3 arranged on the base plate 1 and connected to the heat exchange cavity input end of the heat exchange component 2, the ventilation interface output end 4 of the heat exchange component 2 is connected to the nozzle 11, and a system control cabinet 5 arranged on the base plate 1 and communicatively connected to the heat exchange component 2 and the cooling source 3. Working principle: The operation of the turbine blade 13 cooling test device 15 starts from the cooling source 3, which provides the cooling medium to the heat exchange cavity input end of the heat exchange component 2 arranged on the base plate 1. The heat exchange component 2 is connected to the secondary cooling gas, which can exchange heat with the secondary cooling gas, reduce the temperature of the secondary cooling gas, and achieve low-energy cooling. In this process, the system control cabinet 5 is connected to the heat exchange component 2 and the cooling source 3 for communication, and the entire cooling process can be monitored and controlled. After the secondary cooling gas is cooled by the heat exchange component 2, its ventilation interface output end 4 sends the cooled gas to the nozzle 11, preparing for the subsequent turbine blade 13 cooling test. At the same time, the system control cabinet 5 can adjust various parameters in the cooling process, such as the opening of the regulating valve 31, the selection of a large-flow or small-flow heat exchanger 22 and its corresponding control valve 23, etc., according to different control strategies, such as the pre-established functional relationship between the opening of the regulating valve 31 and the secondary cooling gas flow rate and outlet temperature, to ensure that the entire cooling process can operate efficiently in a low-energy manner and meet the requirements of the turbine blade 13 cooling test for the secondary cooling gas temperature.

[0023] In the above scheme, the heat exchange assembly 2 includes: a large flow heat exchanger 21 and a small flow heat exchanger 22 arranged on the bottom plate 1, the cooling source 3 is connected to the heat exchange cavity input ends of the large flow heat exchanger 21 and the small flow heat exchanger 22 respectively, and the ventilation interfaces of the large flow heat exchanger 21 and the small flow heat exchanger 22 are connected to the input pipeline of the secondary cooling gas through the connecting pipeline; Among them, the air inlet pipe 9 of the large flow heat exchanger 21 and the small flow heat exchanger 22 is provided with a control valve 23, the common air inlet pipe 9 of the large flow heat exchanger 21 and the small flow heat exchanger 22 is provided with a mass flow meter 24, and the air inlet pipeline from the cooling source 3 to the input end of the corresponding heat exchange cavity is provided with a regulating valve 31, and the vaporization output end 10 of each heat exchange cavity is connected to the outside through a pipeline, and the control valve 23, the mass flow meter 24 and the regulating valve 31 are connected to the system control cabinet 5. With this technical solution, the cooling source 3 provides cooling medium to the heat exchange cavity input end of the large flow and small flow heat exchangers 22. When the secondary cooling gas enters through its input pipeline, the control valve 23 on the air inlet pipe 9 can be controlled by the system control cabinet 5 according to the secondary cooling gas flow rate, and the large flow or small flow heat exchanger 22 can be selected for cooling operation. At the same time, the mass flow meter 24 monitors the gas flow in real time, providing data basis for the control decision of the system control cabinet 5. When the secondary cooling gas flow rate is greater than 10% of the set value, the control valve 23 of the small flow pipeline is closed, and the control valve 23 of the large flow pipeline is opened. The regulating valve 31 adjusts the flow rate of the cooling source 3 according to the instruction of the system control cabinet 5, so that the cooling source 3 can provide the cooling medium to the corresponding heat exchanger at an appropriate flow rate, and finally achieves accurate cooling of the secondary cooling gas, meets the requirements of the turbine blade 13 cooling test for the temperature of the secondary cooling gas, and ensures that the entire cooling process is in a low energy consumption state. The setting of the large flow heat exchanger 21 and the small flow heat exchanger 22 provides the system with two different heat exchange capacity options, which can be flexibly switched according to the size of the secondary cooling gas flow rate, so that the cooling system has better adaptability and flexibility. Through the system control cabinet 5, the switch state of the control valve 23 can be accurately controlled according to the actual situation, and the selection and switching of the large flow or small flow heat exchanger 22 can be realized, ensuring that the secondary cooling gas can be cooled according to the preset flow requirements. The mass flow meter 24 can measure the mass flow rate of the secondary cooling gas entering the system in real time, provide accurate data support for system control, and help to accurately adjust and optimize the cooling process. The regulating valve 31 can accurately adjust the cooling medium supply from the cooling source 3 to the large flow or small flow heat exchanger 22 according to different control signals, and the secondary cooling gas entering the large flow heat exchanger 21 and the small flow heat exchanger 22 performs heat exchange with the cooling medium in their respective heat exchange chambers. The cooling medium absorbs the heat of the secondary cooling gas, which reduces the temperature of the secondary cooling gas, thereby achieving the purpose of cooling. In this process, as the cooling medium absorbs heat, part of the cooling medium will vaporize, and the vaporization output end 10 of each heat exchange chamber is connected to the outside through a pipeline. After heat exchange, the vaporized cooling medium will be discharged to the external environment through these pipelines to ensure the pressure stability in the heat exchange chamber and the continuous heat exchange process.

[0024] The above scheme also includes: a heater I6 connected to the outlet of the large flow heat exchanger 21, a heater II7 connected to the outlet of the small flow heat exchanger 22, and the gas output ends of the heater I6 and the heater II7 are connected to the ventilation interface output end 4; wherein, the heater I6 and the heater II7 are both provided with a temperature monitoring component 8 on the connecting pipelines with the large flow heat exchanger 21 and the small flow heat exchanger 22, and the temperature monitoring component 8 is connected to the system control cabinet 5. With this technical scheme, when the secondary cooling gas is cooled by the large flow heat exchanger 21 or the small flow heat exchanger 22, its temperature may not meet the test requirements due to excessive cooling or other factors. At this time, the gas can be heated by the heater I6 connected to the outlet of the large flow heat exchanger 21 or the heater II7 connected to the outlet of the small flow heat exchanger 22. During the heating process, the temperature monitoring component 8 located on the connecting pipeline will monitor the gas temperature in real time and feed back the information to the system control cabinet 5. The system control cabinet 5 decides whether to start the heater and whether to start the heater I6 or heater II7 according to the preset temperature requirements and the actual monitored temperature information. If the monitored temperature is lower than the set value, the system control cabinet 5 will control the corresponding heater to start, provide heat to the secondary cooling gas, increase its temperature until it reaches a suitable temperature, and finally enter the nozzle 11 from the gas output end of the heater I6 or heater II7, providing the turbine blade 13 cooling test with the required secondary cooling gas, ensuring that the test is carried out under suitable temperature conditions.

[0025] Although the embodiments of the present invention have been disclosed as above, they are not limited to the applications listed in the specification and the implementation modes, and they can be fully applied to various fields suitable for the present invention. For those familiar with the art, additional modifications can be easily implemented. Therefore, without departing from the general concept defined by the claims and the scope of equivalents, the present invention is not limited to the specific details and the illustrations shown and described herein.

Claims

1. A low energy consumption turbine blade cooling test method, characterized in that: include: Step 1: Carry out a pre-calibration test to make the mainstream gas temperature T m The ratio of the secondary cooling gas temperature Tc is greater than 2, and when the cooling test device reaches thermal equilibrium, record the secondary cooling gas flow m, the outlet temperature T of the secondary cooling gas and the actual opening A of the regulating valve of the cooling test device, and the thermal equilibrium time t s , obtain the pre-calibrated database, and establish the functional relationship between the regulating valve opening A and the flow rate and outlet temperature based on the pre-calibrated database: ； In the above formula, a ij represents a constant determined by the interpolation or fitting conditions, i The value range is from 0 to 3. j The value range is from 0 to 3. m i Expressed as gas flow m of i Power, T j Expressed as the cooling gas outlet temperature T j Power; And the time t to establish thermal equilibrium s Functional relationship between flow rate and outlet temperature: ； In the above formula, b ij constants determined by interpolation or fitting conditions, i The value range is from 0 to 3. j The value range is 0 to 3, m i is the air flow rate m i Power, T j is the cooling gas outlet temperature T j Power; Step 2: In the air inlet pipe of the nozzle, the temperature of the secondary cooling gas is reduced by the cooling test device to achieve low energy consumption during the test preparation process. During the test, different secondary cooling gas flow rates m and secondary cooling gas outlet temperatures T are input into the functional relationship corresponding to step 1 to obtain the theoretical opening A1 of the regulating valve and the thermal equilibrium time t s ; Step 3: Obtain the theoretical opening degree A1 and thermal equilibrium time t of the regulating valve in step 2 s After that, the system control cabinet adjusts the opening of the regulating valve to A1, and controls the cooling test device to start working, and the working time is t s After this series of operations, the mainstream gas temperature T m and the secondary cooling gas temperature T c When the ratio reaches the preset value, the cooling test of the turbine blades is carried out.

2. The low energy consumption turbine blade cooling test method according to claim 1, characterized in that: In step three, when the outlet temperature of the secondary cooling gas is T1, the actual opening of the regulating valve of the cooling test device is A. When the difference between the actual regulating valve opening A and the theoretical opening A1 is greater than 2%, the actual regulating valve opening A is added to the pre-calibrated database in step one, and the functional relationship of the regulating valve opening is updated to achieve autonomous adjustment of the control accuracy of the system control cabinet.

3. The low energy consumption turbine blade cooling test method according to claim 1, characterized in that: In step 3, the system control cabinet adjusts the opening of the regulating valve to A1, and the working time of the cooling test device is equal to t s Afterwards, the control law of the regulating valve is converted into the PID regulation mode. According to the flow rate of the secondary cooling gas, the control valve on the pipeline of the large-flow heat exchanger or the small-flow heat exchanger is selectively opened to make the secondary cooling gas enter the large-flow or small-flow heat exchanger cooling mode, so that the temperature of the secondary cooling gas can be adjusted to the set temperature value by adjusting the control valve of the cooling test device.

4. The low energy consumption turbine blade cooling test method according to claim 3, characterized in that: In step three, the cooled secondary cooling gas is measured in real time by a temperature monitoring component. When the difference between the real-time measured temperature value and the preset temperature is greater than the set value, the cooled secondary cooling gas is heated according to the measurement result. During the heating operation, based on the difference between the real-time measured temperature value and the preset temperature, heater I or heater II is selected to heat the secondary cooling gas at a large flow rate or a small flow rate.

5. A low-energy consumption turbine blade cooling test device, applied to the low-energy consumption turbine blade cooling test method according to any one of claims 1 to 4, characterized in that: The invention comprises: a base plate, a heat exchange component arranged on the base plate and connected to the secondary cooling gas, a cooling source arranged on the base plate and connected to the heat exchange cavity input end of the heat exchange component, the ventilation interface output end of the heat exchange component being connected to the nozzle, and a system control cabinet arranged on the base plate and connected to the heat exchange component and the cooling source.

6. The low energy consumption turbine blade cooling test device according to claim 5, characterized in that: The heat exchange assembly comprises: a large flow heat exchanger and a small flow heat exchanger arranged on the bottom plate, the cooling source is communicated with the heat exchange cavity input ends of the large flow heat exchanger and the small flow heat exchanger respectively, and the ventilation interfaces of the large flow heat exchanger and the small flow heat exchanger are communicated with the input pipeline of the secondary cooling gas through the connecting pipeline; Among them, control valves are provided on the air inlet pipes of the large-flow heat exchanger and the small-flow heat exchanger, a mass flow meter is provided on the common air inlet pipe of the large-flow heat exchanger and the small-flow heat exchanger, and regulating valves are provided on the air inlet pipeline from the cooling source to the input end of the corresponding heat exchange cavity. The vaporization output end of each heat exchange cavity is connected to the outside through a pipeline, and the control valve, mass flow meter and regulating valve are communicatively connected to the system control cabinet.

7. The low energy consumption turbine blade cooling test device according to claim 6, characterized in that: Also includes: A heater I connected to the gas outlet of the large-flow heat exchanger, and a heater II connected to the gas outlet of the small-flow heat exchanger, wherein the gas output ends of the heater I and the heater II are connected to the output end of the ventilation interface; Wherein, temperature monitoring components are provided on the connection pipelines between the heater I and the heater II and the large flow heat exchanger and the small flow heat exchanger, and the temperature monitoring components are communicatively connected with the system control cabinet.

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