A low-energy consumption turbine blade cooling test device and its test method

Abstract

The present invention relates to a low - energy - consumption turbine blade cooling test device and its test method. The test method is to establish the functional relationships of the regulating valve opening degree and the thermal equilibrium duration. The secondary cooling gas temperature is adjusted by the cooling test device, and after substituting into the function to obtain the regulating valve opening degree, the test is carried out. It also involves operations such as PID control. The cooling test device includes a bottom plate, a heat exchange component, a cooling source, a control cabinet, etc. The present invention cools the secondary cooling gas to make the ratio of the mainstream gas temperature to the secondary flow cooling gas temperature achieve low energy consumption during the test process. At the same time, heat exchangers with different flow rates can be flexibly selected for cooling, and it can monitor in real - time and heat as needed to ensure the accuracy and reliability of the test. The device has a complete structure, which is conducive to effective monitoring and adjustment.

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:

[0005] 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. When the cooling test device reaches thermal equilibrium, record the secondary cooling gas flow rate 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 duration t s , obtain a pre-calibrated database, and establish a functional relationship between the opening A of the regulating valve and the flow rate and outlet temperature based on the pre-calibrated database:

[0006] ;

[0007] In the above formula, a ij represents a constant determined by interpolation or fitting conditions, i The value range of is from 0 to 3, j The value range of is from 0 to 3, m i represents the m power of the gas flow rate i , and T j represents the j power of the cooling gas outlet temperature T;

[0008] And establish a functional relationship between the thermal equilibrium duration t s and the flow rate and outlet temperature:

[0009] ;

[0010] In the above formula, b ij is a constant determined by interpolation or fitting conditions, i The value range of is from 0 to 3, j The value range of is from 0 to 3, and m i is the i power of the gas flow rate m, and T j is the j power of the cooling gas outlet temperature T;

[0011] Step 2: In the intake pipeline of the nozzle, reduce the temperature of the secondary cooling gas through the cooling test device to achieve low energy consumption during the test preparation process. During the test, input different secondary cooling gas flow rates m and the outlet temperature T of the secondary cooling gas into the corresponding functional relationship in Step 1 to obtain the theoretical opening A of the regulating valve 1 and the thermal equilibrium duration t s ;

[0012] Step 3: After obtaining the theoretical opening A of the regulating valve 1 and the thermal equilibrium duration t s in Step 2, the system control cabinet adjusts the opening of the regulating valve to A 1 , and at the same time controls the cooling test device to start working, and the working duration is t s, After this series of operations, the ratio of the mainstream gas temperature T m to the secondary cooling gas temperature T c reaches a preset value, and then the cooling test of the turbine blade is carried out.

[0013] Preferably, in step three, when the outlet temperature of the secondary cooling gas is T 1 , 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 A 1 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 realize the autonomous adjustment of the control accuracy of the system control cabinet.

[0014] Preferably, when the system control cabinet adjusts the opening of the regulating valve to A 1 and the working duration of the cooling test device is equal to t s , the control law of the regulating valve changes to the PID regulation mode. According to the magnitude of the secondary cooling gas flow rate, by selectively opening the control valves on the pipelines of the large-flow heat exchanger or the small-flow heat exchanger, the secondary cooling gas enters the large-flow or small-flow heat exchanger cooling mode, so as to adjust the temperature of the secondary flow cooling gas to the set temperature value by adjusting the control valve of the cooling test device.

[0015] Preferably, 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, heating operation is performed on the cooled secondary cooling gas according to the measurement result;

[0016] Among them, 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 in a large flow or a small flow.

[0017] A low-energy-consumption turbine blade cooling test device, comprising: a bottom plate, a heat exchange component arranged on the bottom plate and communicating with the secondary cooling gas, a cooling source arranged on the bottom plate and communicating with the input end of the heat exchange cavity of the heat exchange component, the output end of the air vent interface of the heat exchange component is communicated with a nozzle, and a system control cabinet arranged on the bottom plate and communicating with the heat exchange component and the cooling source.

[0018] Preferably, the heat exchange component includes: a large-flow heat exchanger and a small-flow heat exchanger arranged on the bottom plate, the cooling source is respectively communicated with the input ends of the heat exchange cavities of the large-flow heat exchanger and the small-flow heat exchanger, and the air vent 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 connecting pipelines;

[0019] Among them, control valves are provided on the intake pipes of the large-flow heat exchanger and the small-flow heat exchanger, a mass flow meter is provided on the common intake pipe of the large-flow heat exchanger and the small-flow heat exchanger, regulating valves are provided on the intake pipelines from the cooling source to the input ends of the corresponding heat exchange chambers, the vaporization output ends of each heat exchange chamber are communicated with the outside through pipelines, and the control valves, the mass flow meter and the regulating valves are communicatively connected with the system control cabinet.

[0020] Preferably, it further includes: a heater I communicated with the outlet end of the large-flow heat exchanger, and a heater II communicated with the outlet end of the small-flow heat exchanger, and the gas output ends of the heater I and the heater II are communicated with the output end of the ventilation interface;

[0021] Among them, temperature monitoring components are provided on the connecting pipelines of the heater I and the heater II with the large-flow heat exchanger and the small-flow heat exchanger, and the temperature monitoring components are communicatively connected with the system control cabinet.

[0022] The present invention has at least the following beneficial effects: 1. Cooling the secondary cooling gas through the cooling test device to make the ratio of the temperature of the main gas to the temperature of the secondary cooling gas ;

[0023] 2. Adopting the PID control method to adjust the opening degree can effectively adjust the flow rate of the cooling source of the secondary flow cooling test device and improve the accuracy and stability of temperature regulation;

[0024] 3. Selecting the large-flow and small-flow heat exchangers and corresponding control valves according to the flow rate of the secondary cooling gas can flexibly match different flow rate requirements and optimize the cooling effect;

[0025] 4. By using the temperature monitoring component for real-time measurement, the secondary cooling gas can be heated as needed to further accurately control the temperature and ensure the accuracy and reliability of the test.

[0026] Other advantages, objectives and features of the present invention will be partially reflected by the following description, and partially will be understood by those skilled in the art through the research and practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 is the overall structural schematic diagram of the cooling test device of the present invention;

[0028] Figure 2 is the top view of the cooling test device of the present invention;

[0029] Figure 3 is the overall structural schematic diagram of the cooling test device of the present invention;

[0030] Figure 4 is the schematic diagram of the test equipment adopting the cooling test method of the present invention;

[0031] Figure 5 It is a schematic diagram of test equipment in the existing turbine blade cooling test.

[0032] Reference numerals: 1, bottom plate; 2, heat exchange assembly; 21, large-flow heat exchanger; 22, small-flow heat exchanger; 23, control valve; 24, mass flowmeter; 3, cooling source; 31, regulating valve; 4, ventilation interface output end; 5, system control cabinet; 6, heater I; 7, heater II; 8, temperature monitoring assembly; 9, intake pipe; 10, vaporization output end; 11, nozzle; 12, heating device; 13, turbine blade; 14, exhaust section; 15, cooling test device. Specific implementation mode

[0033] The following further elaborates on the present invention in conjunction with the accompanying drawings, enabling those skilled in the art to implement it with reference to the text of the specification.

[0034] A low-energy-consumption turbine blade cooling test method of the present invention includes:

[0035] Step 1: Conduct a pre-calibration test to make the ratio of the mainstream gas temperature T m and the secondary cooling gas temperature T c greater than 2. When the cooling test device 15 reaches thermal equilibrium, record the secondary cooling gas flow rate 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, and the thermal equilibrium duration t s , obtain a pre-calibration 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-calibration database:

[0036] ;

[0037] And establish a functional relationship between the thermal equilibrium duration t s and the flow rate and outlet temperature:

[0038] ;

[0039] Step 2: In the intake pipeline of the nozzle 11, reduce the temperature of the secondary cooling gas through the cooling test device 15 to achieve low energy consumption during the test preparation process. During the test, input different secondary cooling gas flow rates m and the outlet temperature T of the secondary cooling gas into the corresponding functional relationships in Step 1 to obtain the theoretical opening A 1 of the regulating valve 31 s and the thermal equilibrium duration t;

[0040] Step 3: The theoretical opening A 1 of the regulating valve 31 obtained in Step 2 s, the system control cabinet 5 adjusts the opening of the regulating valve 31 to A 1 , and at the same time makes the working duration of the cooling test device 15 equal to t s After that, make the ratio of the mainstream gas temperature T m and the secondary cooling gas temperature T c reach the preset value, and then carry out the cooling test of the turbine blade 13. With this technical solution, in the existing solution, assuming that the flow rate of the mainstream gas in the turbine cascade cooling test is m a = 20 kg / s, and the flow rate of the secondary cooling gas is m c = 1 kg / s, and the initial temperatures of the mainstream gas and the secondary cooling gas are both T m = T c = 300K.

[0041] Working principle:

[0042] As Figure 5 shown, during the experimental research process of the traditional turbine blade 13 cooling scheme, the mainstream gas is heated by setting a heating device 12 in the nozzle 11. While heating and raising the temperature of the mainstream gas, the secondary cooling gas is also introduced into the nozzle 11. After the test of the turbine blade 13, the mainstream gas and the secondary cooling gas are discharged from the exhaust section 14. When the test working condition is reached, the heating amount of the mainstream air is Q a (unit: kJ / s), and the effective heating amount of the air Q a can be calculated by the following formula:

[0043]

[0044] In the formula, Q a —— Heating amount of air, kJ / s

[0045] c a —— Specific heat of air, 1.01 kJ / kg℃ (average)

[0046] m a —— Flow rate of the mainstream gas, assuming the maximum flow rate of a test bench is 20 kg / s

[0047] Δ t —— Temperature rise of the heated air, taking 300℃

[0048] Then the heating amount of the air Q a is 6060 kJ / s.

[0049] As shown in Figure 4 the low - energy - consumption cooling test method of this patent, under the same main - and - secondary - flow temperature ratio turbine cascade cooling test conditions, the flow rate of the mainstream gas is m a = 20 kg / s, and the flow rate of the secondary - flow cooling gas m c = is 1 kg / s. The initial temperatures of both the mainstream gas and the secondary - flow cooling gas are T m = T c = 300 K. Under the test conditions where Q a the effective cooling capacity of the secondary - flow gas is Q a ’ (unit: kJ / s), the heat exchanger power is N (unit: kW), and the effective cooling capacity of the air is

[0050]

[0051] In the above formula, Q a ’ —— the cooling capacity of the air, kJ / s

[0052] c a —— the specific heat of the air, 1.01 kJ / kg℃ (average)

[0053] m c —— the flow rate of the secondary - flow cooling gas, assuming the maximum flow rate of a test bench is 1 kg / s

[0054] Δ t —— the cooling range of the air, taking 150℃

[0055] Then the air energy consumption Q a ’ is 151.5 kJ / s.

[0056] Energy consumption ratio: , from which it can be seen that the energy consumption is one - fortieth of the traditional mainstream heating scheme.

[0057] The implementation methods and steps for high - efficiency energy - saving of the turbine cascade cooling test in the present invention:

[0058] 1. Conduct 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. When the flow rate is less than 10% of the maximum flow rate, close the control valve 23 on the large flow rate pipeline and open the control valve 23 on the small flow rate pipeline; if the flow rate through the mass flow meter 24 is greater than 10% of the maximum flow rate, close the small flow rate pipeline and open the large flow rate pipeline.

[0059] 2. Open the secondary gas path valve. According to the pre-set flow rate range of 0 kg / s to 1 kg / s and the temperature range of the cooling outlet temperature of 150 K to 200 K at intervals of 10%, start the cooling test device 15. When the cooling test device 15 reaches thermal equilibrium and the outlet temperature is constant, collect and record information such as the secondary cooling gas flow rate, the outlet temperature, and the opening degree of the regulating valve 31 of the cooling source 3.

[0060] 3. According to the information such as the secondary cooling gas flow rate, the outlet temperature, and the opening degree of the regulating valve 31 of the cooling source 3 collected, establish the functional relationship between the opening degree of the regulating valve 31 of the cooling source 3 and the flow rate and temperature:

[0061] ;

[0062] And establish the functional relationship between the thermal equilibrium duration t s and the flow rate and the outlet temperature:

[0063] ;

[0064] 4. According to the experimental requirements, 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 degree A of the regulating valve 31 1 and the thermal equilibrium duration t s ;

[0065] 5. When the secondary cooling gas flows through the secondary flow pipeline flow meter, the system control cabinet 5 automatically determines the flow rate range. When the flow rate is less than 10% of the maximum flow rate, close the control valve 23 on the large flow rate heat exchanger 21 pipeline and open the control valve 23 on the small flow rate heat exchanger 22 pipeline; if the flow rate through the flow meter is greater than 10% of the maximum flow rate, close the control valve 23 on the small flow rate pipeline and open the control valve 23 on the large flow rate pipeline.

[0066] 6. Start the cooling source 3 adjustment device. According to the theoretical opening degree A of the regulating valve 31 1 and the thermal equilibrium duration t s obtained above, set the opening degree A of the regulating valve 31 corresponding to the cooling source 3 1 , and at the same time make the working duration of the cooling test device 15 equal to t sAfter that, the control law of the regulating valve 31 changes to the PID regulation mode, and the flow rate of the cooling source 3 is adjusted in combination with the PID control method to adjust the temperature of the secondary flow gas to the set temperature value. Among them, the cooling source 3 adopted in the present invention is liquid nitrogen. In actual operation, different cooling sources 3 can be selected according to needs, and pre-calibration tests can be carried out to obtain the corresponding function relationship of the cooling source 3. At the same time, during the actual operation process, when the outlet temperature of the secondary cooling gas is T 1 When it is, the actual opening degree of the regulating valve 31 of the cooling test device 15 is A. When the difference between the actual opening degree A of the regulating valve 31 and the theoretical opening degree A 1 When the difference between the two is greater than 2%, the actual opening degree A of the regulating valve 31 is added to the pre-calibration database in step one, and the function relationship of the opening degree of the regulating valve 31 is updated to realize the autonomous adjustment of the control accuracy of the system control cabinet 5.

[0067] 7. The temperature of 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, heating operation is performed on the cooled secondary cooling gas; among them, during the heating operation process, based on the difference between the real-time measured temperature value and the preset temperature, the heater I 6 or the heater II 7 is selected to heat the secondary cooling gas in a large flow rate or a small flow rate. By using the temperature monitoring component 8 to measure in real time, the heating operation of the secondary cooling gas can be performed as needed, further accurately controlling the temperature, and ensuring the accuracy and reliability of the test.

[0068] Figures 1 - 3 There is shown a low-energy consumption turbine blade cooling test device, including: a bottom plate 1, a heat exchange component 2 arranged on the bottom plate 1 and communicating with the secondary cooling gas, a cooling source 3 arranged on the bottom plate 1 and communicating with the heat exchange cavity input end of the heat exchange component 2, the air vent interface output end 4 of the heat exchange component 2 is communicated with a nozzle 11, and a system control cabinet 5 arranged on the bottom plate 1 and communicating with the heat exchange component 2 and the cooling source 3.

[0069] Working principle:

[0070] The operation of the cooling test device 15 for the turbine blade 13 starts from the cooling source 3. The cooling source 3 supplies the cooling medium to the input end of the heat exchange chamber of the heat exchange assembly 2 provided on the bottom plate 1. The heat exchange assembly 2 is in communication with the secondary cooling gas, and it can perform heat exchange on the secondary cooling gas to reduce the temperature of the secondary cooling gas and achieve low-energy consumption cooling. During this process, the system control cabinet 5 is communicatively connected to the heat exchange assembly 2 and the cooling source 3, and can monitor and control the entire cooling process. When the secondary cooling gas is cooled by the heat exchange assembly 2, its vent interface output end 4 sends the cooled gas to the nozzle 11 to prepare for the subsequent cooling test of the turbine blade 13. At the same time, the system control cabinet 5 can adjust various parameters during the cooling process according to different control strategies, such as according to the pre-established functional relationship between the opening of the regulating valve 31 and the flow rate and outlet temperature of the secondary cooling gas, such as the opening of the regulating valve 31, selecting a large-flow or small-flow heat exchanger 22 and its corresponding control valve 23, etc., to ensure that the entire cooling process can operate efficiently in a low-energy consumption manner and meet the requirements for the temperature of the secondary cooling gas in the cooling test of the turbine blade 13.

[0071] In the above solution, the heat exchange assembly 2 includes: a large-flow heat exchanger 21 and a small-flow heat exchanger 22 provided on the bottom plate 1. The cooling source 3 is respectively communicated with the input ends of the heat exchange chambers of the large-flow heat exchanger 21 and the small-flow heat exchanger 22. The vent interfaces of the large-flow heat exchanger 21 and the small-flow heat exchanger 22 are communicated with the input pipeline of the secondary cooling gas through a connecting pipeline;

[0072] Among them, control valves 23 are provided on the intake pipes 9 of the large-flow heat exchanger 21 and the small-flow heat exchanger 22. A mass flow meter 24 is provided on the common intake pipe 9 of the large-flow heat exchanger 21 and the small-flow heat exchanger 22. Control valves 31 are provided on the intake pipe paths from the cooling source 3 to the input ends of the corresponding heat exchange chambers. The vaporization output ends 10 of each heat exchange chamber are communicated with the outside through pipelines. The control valves 23, the mass flow meter 24, and the control valves 31 are communicatively connected to the system control cabinet 5. With this technical solution, the cooling source 3 provides a cooling medium to the input ends of the heat exchange chambers of the large-flow and small-flow heat exchangers 22. When the secondary cooling gas enters through its input pipeline, according to the flow rate of the secondary cooling gas, the system control cabinet 5 controls the control valve 23 on the intake pipe 9 to select the large-flow or small-flow heat exchanger 22 for cooling operation. At the same time, the mass flow meter 24 monitors the gas flow rate in real time, providing a data basis for the control decision of the system control cabinet 5. When the flow rate of the secondary cooling gas 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 control 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, ultimately achieving precise cooling of the secondary cooling gas, meeting the temperature requirement of the secondary cooling gas for the turbine blade 13 cooling test, and ensuring 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 two different heat exchange capacity options for the system, which can be flexibly switched according to the flow rate of the secondary cooling gas, making the cooling system have better adaptability and flexibility. Through the system control cabinet 5, the on-off state of the control valve 23 can be accurately controlled according to the actual situation, realizing the selection and switching of the large-flow or small-flow heat exchanger 22, and ensuring that the secondary cooling gas can be cooled according to the preset flow rate requirements. The mass flow meter 24 can measure the mass flow rate of the secondary cooling gas entering the system in real time, providing accurate data support for system control, and helping to precisely adjust and optimize the cooling process. The control valve 31 can accurately adjust the supply of the cooling medium from the cooling source 3 to the large-flow or small-flow heat exchanger 22. The secondary cooling gas entering the large-flow heat exchanger 21 and the small-flow heat exchanger 22 exchanges heat with the cooling medium in their respective heat exchange chambers. The cooling medium absorbs the heat of the secondary cooling gas, reducing the temperature of the secondary cooling gas, thereby achieving the purpose of cooling. In this process, due to the absorption of heat by the cooling medium, part of the cooling medium will vaporize. The vaporization output ends 10 of each heat exchange chamber are communicated with the outside through pipelines, and the vaporized cooling medium after heat exchange will be discharged to the external environment through these pipelines to ensure the pressure stability in the heat exchange chamber and the continuous progress of the heat exchange process.

[0073] In the above solution, it further includes: a heater I 6 connected to the gas outlet end of the large-flow heat exchanger 21, and a heater II 7 connected to the gas outlet end of the small-flow heat exchanger 22. The gas output ends of the heater I 6 and the heater II 7 are connected to the output end of the ventilation interface 4. Among them, temperature monitoring components 8 are arranged on the pipelines connecting the heater I 6 and the heater II 7 to the large-flow heat exchanger 21 and the small-flow heat exchanger 22, and the temperature monitoring components 8 are communicatively connected to the system control cabinet 5. With this technical solution, 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 overcooling or other factors. At this time, the heater I 6 connected to the gas outlet end of the large-flow heat exchanger 21 or the heater II 7 connected to the gas outlet end of the small-flow heat exchanger 22 can be used to heat the gas. During the heating process, the temperature monitoring component 8 located on the pipeline will monitor the gas temperature in real time and feedback the information to the system control cabinet 5. The system control cabinet 5 decides whether to start the heater and which heater, i.e., the heater I 6 or the heater II 7, to start according to the preset temperature requirement and the actually 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 to increase its temperature until it reaches a suitable temperature, and finally enter the nozzle 11 from the gas output end of the heater I 6 or the heater II 7 to provide the secondary cooling gas meeting the requirements for the cooling test of the turbine blade 13, ensuring that the test is carried out under suitable temperature conditions.

[0074] Although the embodiments of the present invention have been disclosed as above, it is not limited to the applications listed in the specification and the embodiments. It can be fully applied to various fields suitable for the present invention. For those familiar with the field, additional modifications can be easily made. Therefore, without departing from the general concept defined by the claims and the equivalent scope, the present invention is not limited to the specific details and the illustrated examples here.

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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