CN117168826A - Test run performance evaluation method for industrial light single-shaft gas generator - Google Patents
Test run performance evaluation method for industrial light single-shaft gas generator Download PDFInfo
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- 238000012360 testing method Methods 0.000 title claims abstract description 46
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- 239000000446 fuel Substances 0.000 claims abstract description 81
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- 238000002485 combustion reaction Methods 0.000 claims abstract description 28
- 239000007789 gas Substances 0.000 claims description 242
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- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims description 11
- 229910052799 carbon Inorganic materials 0.000 claims description 11
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims description 10
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- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 claims description 4
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- 238000006243 chemical reaction Methods 0.000 claims description 3
- 239000000112 cooling gas Substances 0.000 claims description 3
- 239000007788 liquid Substances 0.000 claims description 3
- 238000005086 pumping Methods 0.000 claims description 3
- 239000000126 substance Substances 0.000 claims description 3
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- 238000010586 diagram Methods 0.000 description 6
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- 239000003345 natural gas Substances 0.000 description 2
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- 239000002283 diesel fuel Substances 0.000 description 1
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Abstract
The invention relates to the technical field of performance measurement of gas generators, in particular to a test run performance evaluation method of an industrial light single-shaft gas generator. The method comprises the following steps: s1: acquiring a test run parameter of the gas generator; s2: calculating initial flow of the gas compressor and calculating fuel characteristics; s3: evaluating the performance of the air compressor; s4: the performance of the combustion chamber is evaluated; s5: high pressure turbine performance assessment; s6: correcting inlet flow of the air compressor; s7: overall gasifier performance assessment. The invention improves the performance evaluation precision of the gas generator under the new energy material, and realizes the evaluation of the performance of the industrial light single-shaft gas generator on the basis of limited test-run monitoring points.
Description
Technical Field
The invention relates to the technical field of performance measurement of gas generators, in particular to a test run performance evaluation method of an industrial light single-shaft gas generator.
Background
The industrial light gas turbine has the characteristics of high power density, high efficiency and high starting speed, is ideal power equipment driven by industrial equipment, and is widely applied to the natural gas pressurizing and conveying industry. The industrial light gas turbine consists of two main units, including gas generator and power turbine, the power turbine is connected directly to driven equipment, such as compressor, and the gas generator produces high temperature and high pressure gas working medium to drive the power turbine and the driven equipment. Therefore, when the gas generator is in fault or the driven equipment is in fault, the whole system is prevented from being seriously influenced, and the driven equipment can be conveniently regulated. Under the structure of an industrial light gas turbine, the whole performance of the gas generator is critical, so that the overall performance of the gas generator is very important to evaluate in the process of developing the gas generator product, and the gas generator product quality assessment is an important link. If the gasifier performance assessment is inaccurate, the gas turbine may not reach the required workload in field applications, failing to drive the plant production properly. Therefore, after the production and maintenance of the gas generator, a separate bench test is performed on the gas generator, and the performance of the gas generator is evaluated according to the bench test result.
The current evaluation of the industrial light gas generator is aimed at the establishment of a full-working-condition performance model of the gas turbine, but no evaluation of the performance of a gas generator unit based on test data is available, such as China patent (CN 202211585450.2) discloses a modeling method of a ship gas turbine starting performance model and China patent (CN 202210400496.6) discloses a method for determining full-flow parameters and component performance of a gas turbine starting process. The existing established gas turbine performance model is mostly established on the basis of a traditional and detailed experimental operation empirical formula, is mostly suitable for performance evaluation when traditional fossil fuels such as natural gas, diesel oil and the like are adopted, and has a certain deviation in performance evaluation of the gas generator under the condition of adopting new energy materials such as hydrogen and the like.
Disclosure of Invention
The invention aims to solve the problems in the prior art, and provides a test performance evaluation method for an industrial light single-shaft gas generator, which improves the performance evaluation precision of the gas generator under new energy materials and realizes the evaluation of the performance of the industrial light single-shaft gas generator on the basis of limited test monitoring points.
The invention provides a test run performance evaluation method of an industrial light single-shaft gas generator, which comprises the following steps of:
s1: acquiring a test run parameter of the gas generator;
s2: calculating initial flow of the gas compressor and calculating fuel characteristics;
s3: evaluating the performance of the air compressor;
s4: the performance of the combustion chamber is evaluated;
s5: high pressure turbine performance assessment;
s6: correcting inlet flow of the air compressor;
s7: overall gasifier performance assessment.
Further, in step S1, the aerodynamic parameters include a total compressor inlet pressure, a total compressor inlet temperature, a static compressor outlet pressure, a total compressor outlet temperature, a total gasifier outlet pressure, a gasifier test run ambient pressure, and a fuel composition for the gasifier.
Further, in step S2, for the fuel of any component, according to the volume percentage of different pure chemical components in the fuel, the mass ratio of different fuel components in the unit volume under the standard condition is calculated, and further according to the low-level heat value of the unit mass of different fuel components in the fuel under the standard condition, the mass ratio of corresponding fuel components is multiplied, so as to calculate the comprehensive low-level heat value of the fuel; calculating to obtain the total low heat value of the fuel; the total lower calorific value of the fuel is calculated as:
LHV total (S) ＝∑LHV Component i η Mass ratio (1)
In the formula (1): LHV (liquid suction volume) Total (S) Is the total lower heating value of the fuel, and is expressed in kJ/kg;
LHV component i Lower heating value of each component such as methane, hydrogen and the like in the fuel;
η mass ratio The mass ratio of each component is calculated by the mole volume ratio of each component in the fuel.
According to different fuel volume percentage examples in the fuel, calculating to obtain the mole amount of each element in the fuel in unit volume, dividing the mole amount of other elements except carbon by the mole amount of carbon element, and normalizing to obtain a corresponding proportion value with the mole ratio of carbon element being 1 and the mole ratio of other elements being 1 as a unit; if the fuel contains no carbon element, the element proportion is directly taken as the ratio of volume percent. Through the link, fuel with any component, but not limited to a certain number of fuels, can be converted into compound components suitable for performance evaluation of the gas generator, and the analysis of the components of the gas is facilitated. According to the volume percentages of different fuels in the fuel, the enthalpy value carried by each fuel component gas at the corresponding temperature before entering the gas generator is calculated, and the enthalpy value is converted into mass percentage according to the volume percentage, so that the total enthalpy value carried by the fuel into the gas generator is calculated.
Further, in step S2, the initial flow rate of the compressor is the initial flow rate of the compressor during the bench test; and calculating a basic flow value based on the total pressure of the outlet of the gas generator, the temperature and the throat area of the tail nozzle, calculating a corrected flow coefficient based on the specific heat ratio and the gas constant of air, and finally obtaining the initial flow of the gas compressor. The calculation formula of the initial flow of the air compressor is as follows:
in the formula (2): m is m Foundation Is a base flow value;
pt_5 is the total pressure of the gas generator outlet, and the unit is Pa;
tt_5 is the total temperature of the outlet of the gas generator, and the unit is K;
A t the throat area of the tail nozzle is m for the gas generator rack test run 2 。
In the formula (3): k is a corrected flow coefficient;
gamma is the specific heat ratio, the unit is 1
R is a gas constant, and the unit is J/kg.K
m Initial initiation ＝K·m Foundation (4)
In the formula (4): m is m Initial initiation For calculation, the initial flow value of the compressor is calculated in kg/s.
Further, in step S2, the initial flow rate of the compressor is the initial flow rate of the compressor during the on-site operation; the method comprises the steps of obtaining the actual physical gas generator spindle rotating speed and the total temperature of a gas compressor inlet in the test run process, calculating to obtain the corrected rotating speed of the gas generator, and calculating to obtain the initial flow of the gas compressor according to a standard gas generator flow empirical formula, wherein the calculation process is as follows: firstly, calculating according to a formula (5) to obtain the reduced rotating speed of the gas generator, and then calculating according to a formula (6) to obtain the initial compressor flow value.
In formula (5): n is n Physical properties The unit is r/min for the actual physical gas generator main shaft rotating speed monitored in the test run process;
tt_2 is the total temperature of the inlet of the compressor, and the unit is K;
in formula (6): n is n Folding device The calculated reduced rotation speed is calculated as formula (5), and the unit is r/min;
w_2 is the initial calculated flow of the compressor, and the unit is kg/s.
Further, in step S3, the mach number of the outlet of the compressor is obtained according to the initial flow rate of the compressor and the area of the static pressure measuring point of the outlet of the compressor, so as to obtain the total pressure of the outlet of the compressor; obtaining an entropy value of a compressor inlet unit by using the total temperature of the compressor inlet and the total pressure of the compressor inlet, giving an initial isentropic compressor outlet and a total pressure of the compressor outlet, calculating an entropy value of the unit mass of the compressor outlet, and iterating until the outlet entropy value is the same as the inlet entropy value, thereby obtaining the isentropic outlet temperature of the final compressor; after the isentropic temperature of the outlet of the air compressor is obtained, the temperature is used for calculating to obtain the enthalpy value of the inlet and the outlet of the air compressor, and the isentropic efficiency of the air compressor is further obtained; the isentropic efficiency calculation formula of the air compressor is as follows:
in the formula (7): p (P) t3 The total pressure of the outlet of the gas compressor is kPaA;
P s3 the total pressure of the outlet of the gas compressor is kPaA;
ma is the compressor outlet Mach number.
In formula (8): η is the isentropic efficiency of the compressor;
h 3s the unit is the outlet enthalpy value of unit mass at the isentropic temperature of the compressor, and the unit is J/kg;
h 3 is a gas compressorThe unit mass outlet enthalpy value at the outlet total temperature is J/kg;
h 2 the unit is the unit mass inlet enthalpy value of the total inlet temperature of the compressor, and the unit is J/kg.
The supercharging efficiency of the air compressor in the air compressor is equal to the isentropic efficiency of the whole air compressor, the actual enthalpy value of the air compressor air exhaust is obtained, the air compressor air exhaust power consumption is further obtained, and the total power consumption of the air compressor is finally obtained.
Pw_HP＝w 3 (h 3 -h 2 )+∑w Air extraction i (h i -h 2 ) (9)
In the formula (9): pw_HP is the total power consumption of the compressor, and the unit is MW;
w 3 the unit is kg/s for the outlet flow of the compressor;
w air extraction i Pumping air flow for the ith-stage air compressor, wherein the unit is kg/s;
h i the enthalpy value carried by the suction of the ith-stage compressor is MJ/kg;
further, in step S4, the gas enthalpy value of the combustion chamber outlet can be obtained according to the gas enthalpy value of the compressor outlet and the fuel carrying enthalpy value of the fuel calculated by the fuel characteristics and the heat generated by the combustion of the fuel, the flow rate and the outlet component of the combustion chamber outlet can be obtained according to the conservation of mass and the chemical reaction formula, and the gas temperature of the combustion chamber outlet can be calculated according to the gas enthalpy value of the combustion chamber outlet and the gas component of the combustion chamber outlet.
Further, in step S5, an input enthalpy of the high-pressure turbine may be obtained according to the enthalpy carried by the gas at the outlet of the combustion chamber and the enthalpy carried by the cooling gas of the high-pressure turbine, and the total temperature at the outlet of the high-pressure turbine is calculated to obtain an output gas enthalpy of the high-pressure turbine, where the difference value is the functional capacity of the high-pressure turbine; and calculating the outlet entropy value by combining the isentropic temperature of the initial high-pressure turbine outlet with the total pressure of the high-pressure turbine outlet, obtaining the final total temperature of the high-pressure turbine outlet when the inlet entropy value and the outlet entropy value are equal through iteration, further calculating the isentropic outlet enthalpy value of the high-pressure turbine, and further obtaining the efficiency of the high-pressure turbine. The high-pressure turbine efficiency calculation formula is:
in the formula (10): η (eta) HP Is high pressure turbine efficiency;
h 4 the total enthalpy value of the inlet of the high-pressure turbine is J/kg;
h 5 the unit is the outlet enthalpy value of unit mass under the total inlet and outlet temperature of the high-pressure turbine, and the unit is J/kg;
h 5s the unit mass inlet enthalpy value of the isentropic outlet total temperature of the high-pressure turbine is J/kg.
Further, in step S6, after the performance evaluation of each component of the first-round gas generator is completed, the given rationality of the initial flow of the gas compressor is evaluated and corrected according to the evaluation result; in the gas generator bench test run, calculating a flow correction coefficient at the tail nozzle through gas components at the outlet of the gas generator, calculating to obtain the outlet flow of the gas generator, subtracting the fuel quantity to obtain the inlet flow of the gas compressor, comparing with the initial inlet flow of the gas compressor obtained by calculation according to the air physical property, and if the difference is large, performing iterative calculation through the initial inlet flow of the gas compressor until a working point with balanced flow is obtained; in the on-site operation process of the gas generator, the initial flow of the gas compressor is corrected by utilizing the power balance of the power consumption of the gas compressor and the work of the high-pressure turbine, and the final corrected inlet flow value of the gas compressor is obtained under the power balance.
Further, in step S7, after the flow correction of the inlet of the compressor is completed, the total pressure of the outlet of the gas generator and the total temperature of the outlet of the gas generator are used to obtain the entropy value of the outlet gas of the gas generator, and the isentropic total temperature iterates after the theoretical expansion work of the outlet gas of the gas generator under the ambient pressure, when the entropy value of the outlet gas of the gas generator is consistent with the entropy value of the outlet gas of the gas generator, the isentropic total temperature after the final theoretical expansion work is obtained, the theoretical expansion enthalpy value is further calculated, the theoretical expansion enthalpy value is subtracted from the theoretical expansion enthalpy value of the outlet gas of the gas generator, the theoretical maximum power of the outlet gas of the gas generator is obtained, and the work potential of the outlet gas of the gas generator can be obtained by combining the calculation of the general expansion work efficiency of the expander; the overall thermal efficiency of the gasifier is calculated based on the fuel input capacity. The working potential calculation formula of the gas at the outlet of the gas generator is as follows:
Pw GG ＝η P ·w GG ·(h 5 -h is8 ) (11)
in the formula (11): pw (Pw) GG The power potential of the gas generator is MW;
η P the method is characterized in that the efficiency of the general expansion work is given according to the efficiency index of the axial flow expander under the current flow;
w GG the unit of the gas flow is kg/s for the outlet of the gas generator;
h 5 the unit mass enthalpy value of the fuel gas at the outlet of the fuel gas generator is MJ/kg;
h is8 the unit mass enthalpy value is MJ/kg under the conditions of the environmental pressure of the gas generator and the isentropic total temperature after theoretical expansion work.
Compared with the prior art, the invention has the following beneficial effects:
the invention evaluates key performance indexes such as the gas generator compressor pressure ratio and efficiency, the high-pressure turbine pressure ratio and efficiency, the combustion chamber outlet temperature, the whole power and efficiency and the like through pressure and temperature data on a limited section of the gas generator obtained through test run monitoring. Thus, the performance data of the component and the whole machine when the gas generator is tested before delivery and is operated on site are obtained, and the component and the whole machine are used for judging whether the product of the gas generator reaches the expected performance index or not and whether the design of the component reaches the expected index or not. The judgment can be suitable for the factory performance quality assessment of the brand new gas generator just produced. The method is also suitable for gas generator products which are repaired or overhauled in the middle period, and the maintenance effect is evaluated after the maintenance. And the method is also suitable for the comparison of the performance attenuation possibly existing in the whole machine operation performance along with the increase of the service time in the long-term operation process of the gas generator product on site.
Drawings
FIG. 1 is a schematic illustration of a gasifier performance evaluation flow according to the present invention;
FIG. 2 is a schematic diagram of a fuel property calculation flow chart according to the present invention;
FIG. 3 is a schematic diagram of an initial flow calculation flow of a compressor according to the present invention;
FIG. 4 is a schematic diagram of a compressor performance evaluation flow chart according to the present invention;
FIG. 5 is a schematic diagram of a combustion chamber performance evaluation flow chart according to the present invention;
FIG. 6 is a schematic illustration of a high pressure turbine performance evaluation flow path in accordance with the present invention;
FIG. 7 is a schematic diagram of a flow correction flow chart of a compressor according to the present invention;
FIG. 8 is a schematic diagram of the overall performance evaluation flow of the gasifier according to the present invention.
Detailed Description
The invention is further described below with reference to examples:
example 1
As shown in fig. 1-7, the method for evaluating the test run performance of the industrial light single-shaft gas generator, as shown in fig. 1, comprises the following steps:
s1: acquiring a test run parameter of the gas generator;
s2: calculating initial flow of the gas compressor and calculating fuel characteristics;
s3: evaluating the performance of the air compressor;
s4: the performance of the combustion chamber is evaluated;
s5: high pressure turbine performance assessment;
s6: correcting inlet flow of the air compressor;
s7: overall gasifier performance assessment.
In step S1, the pneumatic parameters include total compressor inlet pressure, total compressor inlet temperature, static compressor outlet pressure, total compressor outlet temperature, total gasifier outlet pressure, gasifier test run ambient pressure, and fuel composition for the gasifier.
In step S2, the overall calculation flow and output are as shown in fig. 2, and for the fuel with any component, the mass ratio of different fuel components in unit volume under standard conditions is calculated according to the volume percentage of different pure chemical components in the fuel, and the total low heat value of the fuel is calculated by multiplying the mass ratio of corresponding fuel components according to the low heat value of different fuel components in the fuel under standard conditions;
LHV total (S) ＝ΣLHV Component i ·η Mass ratio (1)
In the formula (1): LHV (liquid suction volume) Total (S) Is the total lower heating value of the fuel, and is expressed in kJ/kg;
LHV component i Lower heating value of each component such as methane, hydrogen and the like in the fuel;
η mass ratio The mass ratio of each component is calculated by the mole volume ratio of each component in the fuel.
According to different fuel volume percentage examples in the fuel, calculating to obtain the mole amount of each element in the fuel in unit volume, dividing the mole amount of other elements except carbon by the mole amount of carbon element, and normalizing to obtain a corresponding proportion value with the mole ratio of carbon element being 1 and the mole ratio of other elements being 1 as a unit; if the fuel contains no carbon element, the element proportion is directly taken as the ratio of volume percent. Through the link, fuel with any component, but not limited to a certain number of fuels, can be converted into compound components suitable for performance evaluation of the gas generator, and the analysis of the components of the gas is facilitated. According to the volume percentages of different fuels in the fuel, the enthalpy value carried by each fuel component gas at the corresponding temperature before entering the gas generator is calculated, and the enthalpy value is converted into mass percentage according to the volume percentage, so that the total enthalpy value carried by the fuel into the gas generator is calculated.
And the initial inlet flow value of the gas compressor is given according to two conditions of gas generator rack test run and on-site operation, and the inlet components of the gas compressor are calculated and evaluated according to the ambient humidity, and the calculation flow of the initial flow of the whole gas compressor is shown in figure 3. Firstly, judging whether the performance evaluation data is based on a gas generator rack test run process or a gas generator application test run process in an industrial field.
When the initial flow of the compressor is the initial flow of the compressor during bench test; and calculating a basic flow value based on the total pressure of the outlet of the gas generator, the temperature and the throat area of the tail nozzle, calculating a corrected flow coefficient based on the specific heat ratio and the gas constant of air, and finally obtaining the initial flow of the gas compressor. The calculation formula of the initial flow of the air compressor is as follows:
in the formula (2): m is m Foundation Is a base flow value;
pt_5 is the total pressure of the gas generator outlet, and the unit is Pa;
tt_5 is the total temperature of the outlet of the gas generator, and the unit is K;
A t the throat area of the tail nozzle is m for the gas generator rack test run 2 。
In the formula (3): k is a corrected flow coefficient;
gamma is the specific heat ratio, the unit is 1
R is a gas constant, and the unit is J/kg.K
m Initial initiation ＝Km Foundation (4)
In the formula (4): m is m Initial initiation For calculation, the initial flow value of the compressor is calculated in kg/s.
When the initial flow of the compressor is the initial flow of the compressor in the field operation; the method comprises the steps of obtaining the actual physical gas generator spindle rotating speed and the total temperature of a gas compressor inlet in the test run process, calculating to obtain the corrected rotating speed of the gas generator, and calculating to obtain the initial flow of the gas compressor according to a standard gas generator flow empirical formula, wherein the calculation process is as follows: firstly, calculating according to a formula (5) to obtain the reduced rotating speed of the gas generator, and then calculating according to a formula (6) to obtain the initial compressor flow value.
In formula (5): n is n Physical properties The unit is r/min for the actual physical gas generator main shaft rotating speed monitored in the test run process;
tt_2 is the total temperature of the inlet of the compressor, and the unit is K;
in formula (6): n is n Folding device The calculated reduced rotation speed is calculated as formula (5), and the unit is r/min;
w_2 is the initial calculated flow of the compressor, and the unit is kg/s.
In step S3, the performance evaluation flow of the air compressor is shown in FIG. 4, and the Mach number of the air compressor outlet is obtained according to the initial flow of the air compressor and the area of the static pressure measuring point of the air compressor outlet, so that the total pressure of the air compressor outlet is obtained; obtaining an entropy value of a compressor inlet unit by using the total temperature of the compressor inlet and the total pressure of the compressor inlet, giving an initial isentropic compressor outlet and a total pressure of the compressor outlet, calculating an entropy value of the unit mass of the compressor outlet, and iterating until the outlet entropy value is the same as the inlet entropy value, thereby obtaining the isentropic outlet temperature of the final compressor; after the isentropic temperature of the outlet of the air compressor is obtained, the temperature is used for calculating to obtain the enthalpy value of the inlet and the outlet of the air compressor, and the isentropic efficiency of the air compressor is further obtained; the isentropic efficiency calculation formula of the air compressor is as follows:
in the formula (7): p (P) t3 The total pressure of the outlet of the gas compressor is kPaA;
P s3 the total pressure of the outlet of the gas compressor is kPaA;
ma is the compressor outlet Mach number.
In formula (8): η is the isentropic efficiency of the compressor;
h 3s the unit is the outlet enthalpy value of unit mass at the isentropic temperature of the compressor, and the unit is J/kg;
h 3 the unit is the outlet enthalpy value of unit mass under the total temperature of the outlet of the gas compressor, and the unit is J/kg;
h 2 the unit is the unit mass inlet enthalpy value of the total inlet temperature of the compressor, and the unit is J/kg.
The supercharging efficiency of the air compressor in the air compressor is equal to the isentropic efficiency of the whole air compressor, the actual enthalpy value of the air compressor air exhaust is obtained, the air compressor air exhaust power consumption is further obtained, and the total power consumption of the air compressor is finally obtained.
Pw_HP＝w 3 (h 3 -h 2 )+∑w Air extraction i (h i -h 2 ) (9)
In the formula (9): pw_HP is the total power consumption of the compressor, and the unit is MW;
w 3 the unit is kg/s for the outlet flow of the compressor;
w air extraction i Pumping air flow for the ith-stage air compressor, wherein the unit is kg/s;
h i the enthalpy value carried by the suction of the ith-stage compressor is MJ/kg;
in step S4, the enthalpy value of the outlet gas of the combustion chamber can be obtained according to the enthalpy value of the outlet gas of the compressor and the calculated enthalpy value of the fuel carried by the fuel and the heat generated by the combustion of the fuel, the outlet flow and the outlet component of the combustion chamber can be obtained according to the conservation of mass and the chemical reaction formula, the outlet gas temperature of the combustion chamber can be calculated according to the enthalpy value of the outlet gas of the combustion chamber and the outlet gas component of the combustion chamber, and the overall flow of the combustion chamber performance evaluation is shown in fig. 5.
In step S5, an input enthalpy value of the high-pressure turbine can be obtained according to an enthalpy value carried by the gas at the outlet of the combustion chamber and an enthalpy value carried by the cooling gas of the high-pressure turbine, and an enthalpy value of the gas at the outlet of the high-pressure turbine is obtained by calculating the total temperature of the outlet of the high-pressure turbine, wherein the difference value of the input enthalpy value and the enthalpy value is the functional capacity of the high-pressure turbine; the isentropic temperature of the outlet of the initial high-pressure turbine is combined with the total pressure of the outlet of the high-pressure turbine to calculate the outlet entropy value, the final total temperature of the outlet of the high-pressure turbine is obtained when the inlet entropy value and the outlet entropy value are equal through iteration, the isentropic outlet enthalpy value of the high-pressure turbine is further calculated, and the efficiency of the high-pressure turbine is further obtained, and the overall flow is shown in figure 6. The high-pressure turbine efficiency calculation formula is:
in the formula (10): η (eta) HP Is high pressure turbine efficiency;
h 4 the total enthalpy value of the inlet of the high-pressure turbine is J/kg;
h 5 the unit is the outlet enthalpy value of unit mass under the total inlet and outlet temperature of the high-pressure turbine, and the unit is J/kg;
h 5s the unit mass inlet enthalpy value of the isentropic outlet total temperature of the high-pressure turbine is J/kg.
In step S6, after the performance evaluation of each component of the first-round gas generator is completed, the given rationality of the initial flow of the gas compressor is evaluated and corrected according to the evaluation result, as shown in fig. 7; in the gas generator bench test run, calculating a flow correction coefficient at the tail nozzle through gas components at the outlet of the gas generator, calculating to obtain the outlet flow of the gas generator, subtracting the fuel quantity to obtain the inlet flow of the gas compressor, comparing with the initial inlet flow of the gas compressor obtained by calculation according to the air physical property, and if the difference is large, performing iterative calculation through the initial inlet flow of the gas compressor until a working point with balanced flow is obtained; in the on-site operation process of the gas generator, the initial flow of the gas compressor is corrected by utilizing the power balance of the power consumption of the gas compressor and the work of the high-pressure turbine, and the final corrected inlet flow value of the gas compressor is obtained under the power balance.
In step S7, after finishing the correction of the inlet flow of the gas compressor, obtaining the gas entropy value of the outlet of the gas generator by using the total pressure of the outlet of the gas generator and the total temperature of the outlet of the gas generator, iterating the isentropic total temperature after theoretical expansion work of the gas of the outlet of the gas generator under the environment pressure, obtaining the isentropic total temperature after final theoretical expansion work when the isentropic total temperature is consistent with the gas entropy value of the outlet of the gas generator, further calculating to obtain the enthalpy value after theoretical expansion, subtracting the enthalpy value after theoretical expansion from the enthalpy value of the outlet of the gas generator to obtain the theoretical maximum work-done capability of the gas of the outlet of the gas generator, and calculating to obtain the work-done potential of the gas of the outlet of the gas generator by combining the general expansion work-done efficiency of the expander; the overall heat efficiency of the gasifier is calculated based on the fuel input capacity as shown in fig. 8. The working potential calculation formula of the gas at the outlet of the gas generator is as follows:
Pw GG ＝η P ·w GG ·(h 5 -h is8 ) (11)
in the formula (11): pw (Pw) GG The power potential of the gas generator is MW;
η P the method is characterized in that the efficiency of the general expansion work is given according to the efficiency index of the axial flow expander under the current flow;
w GG the unit of the gas flow is kg/s for the outlet of the gas generator;
h 5 the unit mass enthalpy value of the fuel gas at the outlet of the fuel gas generator is MJ/kg;
h is8 the unit mass enthalpy value is MJ/kg under the conditions of the environmental pressure of the gas generator and the isentropic total temperature after theoretical expansion work.
The description of the directions and the relative positional relationships of the structures, such as the description of the front, back, left, right, up and down, in the present invention does not limit the present invention, but is merely for convenience of description.
Claims (10)
1. The test run performance evaluation method of the industrial light single-shaft gas generator is characterized by comprising the following steps of:
s1: acquiring a test run parameter of the gas generator;
s2: calculating initial flow of the gas compressor and calculating fuel characteristics;
s3: evaluating the performance of the air compressor;
s4: the performance of the combustion chamber is evaluated;
s5: high pressure turbine performance assessment;
s6: correcting inlet flow of the air compressor;
s7: overall gasifier performance assessment.
2. The method for evaluating the test run performance of an industrial light single-shaft gas generator according to claim 1, wherein in step S1, the aerodynamic parameters include a total compressor inlet pressure, a total compressor inlet temperature, a static compressor outlet pressure, a total compressor outlet temperature, a total gas generator outlet pressure, a total gas generator test run ambient pressure, and a fuel composition used by the gas generator.
3. The test run performance evaluation method of an industrial light single-shaft gas generator according to claim 1, wherein in step S2, for the fuel of any component, the mass ratio of different fuel components in a unit volume under standard conditions is calculated according to the volume percentage of different pure chemical components in the fuel, and further, the total low heat value of the fuel is calculated according to the low heat value of the unit mass under standard conditions of the different fuel components in the fuel under standard conditions, multiplied by the mass ratio of the corresponding fuel components; the total lower calorific value of the fuel is calculated as:
LHV total (S) ＝∑LHV Component i ·η Mass ratio (1)
In the formula (1): LHV (liquid suction volume) Total (S) Is the total lower heating value of the fuel, and is expressed in kJ/kg;
LHV component i Lower heating value of each component such as methane, hydrogen and the like in the fuel;
η mass ratio The mass ratio of each component is calculated by the mole volume ratio of each component in the fuel;
according to different fuel volume percentage examples in the fuel, calculating to obtain the mole amount of each element in the fuel in unit volume, dividing the mole amount of other elements except carbon by the mole amount of carbon element, and normalizing to obtain a corresponding proportion value with the mole ratio of carbon element being 1 and the mole ratio of other elements being 1 as a unit; according to the volume percentages of different fuels in the fuel, the enthalpy value carried by each fuel component gas at the corresponding temperature before entering the gas generator is calculated, and the enthalpy value is converted into mass percentage according to the volume percentage, so that the total enthalpy value carried by the fuel into the gas generator is calculated.
4. The method for evaluating the test run performance of an industrial light single-shaft gas generator according to claim 1, wherein in step S2, the initial flow rate of the compressor is the initial flow rate of the compressor during the bench test run; calculating a basic flow value based on the total pressure, the temperature and the throat area of the tail nozzle of the gas generator, calculating a corrected flow coefficient based on the specific heat ratio and the gas constant of air, and finally obtaining the initial flow of the gas compressor; the calculation formula of the initial flow of the air compressor is as follows:
in the formula (2): m is m Foundation Is a base flow value;
pt_5 is the total pressure of the gas generator outlet, and the unit is Pa;
tt_5 is the total temperature of the outlet of the gas generator, and the unit is K;
A t the throat area of the tail nozzle is m for the gas generator rack test run 2 。
In the formula (3): k is a corrected flow coefficient;
gamma is the specific heat ratio, the unit is 1
R is a gas constant, and the unit is J/kg.K
m Initial initiation ＝Km Foundation (4)
In the formula (4): m is m Initial initiation For calculation, the initial flow value of the compressor is calculated in kg/s.
5. The method for evaluating the test run performance of an industrial light single-shaft gas generator according to claim 1, wherein in step S2, the initial flow rate of the compressor is the initial flow rate of the compressor at the time of field operation; acquiring the actual physical gas generator spindle rotating speed and the total temperature of the gas compressor inlet in the test run process, calculating to obtain the corrected rotating speed of the gas generator, and calculating to obtain the initial flow of the gas compressor according to the standard gas generator flow empirical formula; the calculation formula of the initial compressor flow value is as follows:
in formula (5): n is n Physical properties The unit is r/min for the actual physical gas generator main shaft rotating speed monitored in the test run process;
tt_2 is the total temperature of the inlet of the compressor, and the unit is K;
in formula (6): n is n Folding device The calculated reduced rotation speed is calculated as formula (5), and the unit is r/min;
w_2 is the initial calculated flow of the compressor, and the unit is kg/s.
6. The method for evaluating the test run performance of an industrial light single-shaft gas generator according to claim 4 or 5, wherein in step S3, the mach number of the outlet of the gas compressor is obtained according to the initial flow rate of the gas compressor and the area of the static pressure measuring point of the outlet of the gas compressor, so as to obtain the total pressure of the outlet of the gas compressor; obtaining an entropy value of a compressor inlet unit by using the total temperature of the compressor inlet and the total pressure of the compressor inlet, giving an initial isentropic compressor outlet and a total pressure of the compressor outlet, calculating an entropy value of the unit mass of the compressor outlet, and iterating until the outlet entropy value is the same as the inlet entropy value, thereby obtaining the isentropic outlet temperature of the final compressor; after the isentropic temperature of the outlet of the air compressor is obtained, the temperature is used for calculating to obtain the enthalpy value of the inlet and the outlet of the air compressor, and the isentropic efficiency of the air compressor is further obtained; the isentropic efficiency calculation formula of the air compressor is as follows:
in the formula (7): p (P) t3 The total pressure of the outlet of the gas compressor is kPaA;
P s3 the total pressure of the outlet of the gas compressor is kPaA;
ma is the compressor outlet Mach number.
In formula (8): η is the isentropic efficiency of the compressor;
h 3s the unit is the outlet enthalpy value of unit mass at the isentropic temperature of the compressor, and the unit is J/kg;
h 3 the unit is the outlet enthalpy value of unit mass under the total temperature of the outlet of the gas compressor, and the unit is J/kg;
h 2 the unit is the unit mass inlet enthalpy value under the total inlet temperature of the compressor, and the unit is J/kg;
the supercharging efficiency of the air compressor in the air compressor is equal to the isentropic efficiency of the whole air compressor, the actual enthalpy value of the air compressor air exhaust is obtained, the air compressor air exhaust power consumption is further obtained, and finally the total power consumption of the air compressor is obtained, wherein the total power consumption calculation formula of the air compressor is as follows:
Pw_HP＝w 3 (h 3 -h 2 )+∑w air extraction i (h i -h 2 ) (9)
In the formula (9): pw_HP is the total power consumption of the compressor, and the unit is MW;
w 3 the unit is kg/s for the outlet flow of the compressor;
w air extraction i Pumping air flow for the ith-stage air compressor, wherein the unit is kg/s;
h i the unit of the enthalpy value carried by the suction of the ith-stage compressor is MJ/kg.
7. The method for evaluating the test run performance of an industrial light single-shaft gas generator according to claim 6, wherein in the step S4, the gas enthalpy value of the combustion chamber outlet is obtained according to the gas enthalpy value of the gas outlet of the gas compressor and the heat generated by the combustion of the fuel, the gas flow rate and the gas composition of the combustion chamber outlet are obtained according to the conservation of mass and the chemical reaction formula, and the gas temperature of the combustion chamber outlet is calculated according to the gas enthalpy value of the combustion chamber outlet and the gas composition of the combustion chamber outlet.
8. The method for evaluating the test run performance of an industrial light single-shaft gas generator according to claim 7, wherein in step S5, an input enthalpy value of the high-pressure turbine is obtained according to an enthalpy value carried by the gas at the outlet of the combustion chamber and an enthalpy value carried by the cooling gas of the high-pressure turbine, and an enthalpy value of the gas at the outlet of the high-pressure turbine is obtained by calculating the total temperature of the outlet of the high-pressure turbine, wherein the difference value of the input enthalpy value and the enthalpy value is the functional capacity of the high-pressure turbine; the isentropic temperature of the initial high-pressure turbine outlet is combined with the total pressure of the high-pressure turbine outlet to calculate an outlet entropy value, the final total temperature of the high-pressure turbine outlet is obtained when the inlet and outlet entropy values are equal through iteration, the isentropic outlet enthalpy value of the high-pressure turbine is further calculated, and then the high-pressure turbine efficiency is obtained, wherein a high-pressure turbine efficiency calculation formula is as follows:
in the formula (10): η (eta) HP Is high pressure turbine efficiency;
h 4 the total enthalpy value of the inlet of the high-pressure turbine is J/kg;
h 5 the unit is the outlet enthalpy value of unit mass under the total inlet and outlet temperature of the high-pressure turbine, and the unit is J/kg;
h 5s the unit mass inlet enthalpy value of the isentropic outlet total temperature of the high-pressure turbine is J/kg.
9. The method for evaluating the test run performance of an industrial light single-shaft gas generator according to claim 8, wherein in step S6, after the performance evaluation of each component of the first-round gas generator is completed, the given rationality of the initial flow of the gas compressor is evaluated and corrected according to the evaluation result.
10. The test run performance evaluation method of an industrial light single-shaft gas generator according to claim 9, wherein in step S7, after finishing the correction of the inlet flow of the gas compressor, the gas entropy value of the gas generator outlet is obtained by using the total pressure of the gas generator outlet and the total temperature of the gas generator outlet, and the isentropic total temperature iteration is performed after the theoretical expansion work of the gas generator outlet under the environmental pressure, when the isentropic total temperature is consistent with the gas entropy value of the gas generator outlet, the isentropic total temperature after the final theoretical expansion work is obtained, the theoretical expansion enthalpy value is further calculated, the theoretical expansion enthalpy value is subtracted from the gas generator outlet enthalpy value, the theoretical maximum work capacity of the gas generator outlet is obtained, and the work potential of the gas generator outlet gas is calculated by combining the general expansion work efficiency of the expander; the working potential calculation formula of the gas at the outlet of the gas generator is as follows:
Pw GG ＝η P ·w GG ·(h 5 -h is8 ) (11)
in the formula (11): pw (Pw) GG The power potential of the gas generator is MW;
η P the method is characterized in that the efficiency of the general expansion work is given according to the efficiency index of the axial flow expander under the current flow;
w GG the unit of the gas flow is kg/s for the outlet of the gas generator;
h 5 the unit mass enthalpy value of the fuel gas at the outlet of the fuel gas generator is MJ/kg;
h is8 the unit mass enthalpy value is MJ/kg under the conditions of the environmental pressure of the gas generator and the isentropic total temperature after theoretical expansion work;
the overall thermal efficiency of the gasifier is calculated based on the fuel input capacity.
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