Investigation of Thermopressor with Incomplete Evaporation for Gas Turbine Intercooling Systems
Abstract
:1. Introduction
2. Literature Review
- (1)
- (2)
- Injected water drop separation on the blades and the compressor casing and related possible complications in its operation [46,47]. Due to insufficiently efficient spraying of the injected water, already in the compressor’s first stages (according to the injection area) there is an intensive drop separation on the working blades with the liquid layer formation. Moving layers are torn from the edges of the blades, resulting in the formation of so-called secondary drops, which are separated on the compressor housing [48].
- (3)
- Providing sufficient intensity of injected water evaporation and cooling the compressed airflow [49]. Several times less moisture evaporates from the surface of the droplets in the airflow (the evaporation share from the surface of the droplets is usually less than 20%) than from the liquid layer surface on the blades and compressor housing [50].
- (4)
- Mechanical losses due to the drop acceleration of the flow and rotating blades’ deceleration of the impellers drop by their repeated deposition and surface failure of the blades and housing, as well as friction, liquid layer on the blades’ surface, and compressor housing [22,51]. As a result, the stage’s internal efficiency and the compressor are reduced [52].
- (5)
- (1)
- Cyclic air intercooling the gas turbine by a thermopressor provides an increase in power by increasing the working fluid mass flow rate, increasing efficiency and reducing fuel consumption by reducing the compressed air temperature, and, consequently, reducing the compression power cost.
- (2)
- Intercooling of the gas turbine cycle air by a thermopressor provides increased power due to more efficient liquid spraying in the thermopressor itself by providing incomplete droplet evaporation and reducing droplet diameter (dispersion) to less than 30 μm, consequently decreasing relative fuel consumption by reducing power consumption in the compressor since the compression process is approximately isothermal.
- (3)
- A thermopressor is a multifunctional device that implements three main functions: air (gas) compression–compressor; air (gas) cooling–heat exchanger; and providing an effective liquid (water) spray nozzle. This versatility allows, on the one hand, to increase the power plant efficiency, reduce fuel consumption, and increase power by reducing the cost of compressing the working fluid, therefore increasing the working fluid consumption in the cycle.
3. Materials and Methods
- (1)
- At the entrance in front of the air filter;
- (2)
- After compressing the air in the compressor and cleaning from oil and moisture;
- (3)
- After heating the air in the duct air heater at the entrance of the thermopressor;
- (4)
- In the thermopressor evaporation chamber;
- (5)
- At the thermopressor diffuser outlet (the discharge pipe).
4. Results and Discussion
5. Conclusions
- The use of incomplete evaporation in a thermopressor to provide contact cooling of the cycled air of gas turbines makes it possible to obtain a highly dispersed flow before going into the high-pressure compressor.
- It was determined that the increase in pressure due to the effect of thermo-gas-dynamic compression depends on the influence of the aerodynamic resistance of the dispersed flow droplets in the thermopressor evaporation chamber. Water injection has a positive effect over the necessary amount for evaporation, but only in the area gw = 4–10% (0.0175–0.0487 kg/s), and a further increase in gw will result in a decrease in relative increase pressure εtp. Moreover, the increased relative velocity in the evaporation chamber (up to Ma = 0.74) shifts the limit value of gw to a narrower range of gw = 6–8%.
- It has been experimentally shown that excessive liquid injection into the thermopressor for air cooling makes it possible to increase the relative pressure in the thermopressor to εtp = 1–3% (5–10 kPa). However, this makes it possible to ensure effective liquid high-dispersion spraying in the airflow with simultaneous air cooling up to 301–307 K.
- The highly dispersed flow thus acquired with the use of the thermopressor can be pre-evaporated in the high-pressure compressor stage. This will allow the compression process to operate closer to an isothermal process.
- The maximum error value of the increased pressure in the thermopressor during measurements, corresponding to the Student’s dispersion, does not exceed δtp = ±4.00%.
- Based on experimental data, empirical equations are obtained for calculating the relative pressure increase in the thermopressor for intercooling systems of power plant engines’ cyclic air. The equation can calculate the thermopressor characteristics under incomplete water evaporation (up to gw = 10%) in the flowing part.
- The obtained data on the optimal amount of water for injection and empirical equations for determining the pressure increase in the thermopressor correspond to low-consumption thermopressors with an airflow rate of up to 0.52 kg/s, evaporation chamber diameters of up to 50 mm (relative flow path length ltp is from 3 to 10), and a Mach number from 0.3 to 0.8.
Author Contributions
Funding
Data Availability Statement
Conflicts of Interest
Nomenclature
CHAT | Cascaded Humidified Advanced Turbine | |
GE | General Electric | |
HAT | Humidified Advanced Turbine or Humidified Air Turbine | |
WAC | Water Atomization Cooling | |
Symbols and units | ||
δw | droplet diameter | μm |
Ga | air mass flow | kg/s |
gw | relative water amount | % |
Gw | water injected mass flow | kg/s |
ltp | relative flow path length | |
Ma | Mach number | |
P | flow pressure | Pa |
Pw | water pressure at the inlet to the nozzle | MPa |
Ta | air temperature | °C; K |
ΔPtp | flow pressure increases in the thermopressor | Pa; % |
T1/T2 | relative temperature | |
εtp | thermopressor degree of pressure increase | |
Subscripts | ||
1 | before | |
2 | after | |
a | air | |
tp | thermopressor | |
w | water |
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Equation | Coefficient | R | R2 | |||||
---|---|---|---|---|---|---|---|---|
y0 | x0 | a | b | c | d | |||
Plane: | 1.0101 | – | 0.1745 | −3.8608 | – | – | 0.9255 | 0.8566 |
Paraboloid: | 0.7985 | – | 0.3159 | 9.7491 | −0.1479 | −209.01 | 0.9832 | 0.9667 |
Gaussian: | 0.0237 | 1.0174 | 1.0859 | 1.7044 | 0.0465 | – | 0.9820 | 0.9533 |
Lorentzian: | 0.0240 | 0.9934 | 1.0880 | 2.2880 | 0.0611 | – | 0.9820 | 0.9641 |
Equation | Coefficient | R | R2 | |||||
---|---|---|---|---|---|---|---|---|
y0 | x0 | a | b | c | d | |||
Plane: | 1.0808 | – | 0.0048 | −1.1982 | – | – | 0.9299 | 0.8647 |
Paraboloid: | 1.0664 | – | 0.0961 | −1.3433 | −0.0869 | 0.6821 | 0.9307 | 0.8663 |
Gaussian: | −3.0078 | 0.5553 | 6.7176 | 2.1882 | 1.5781 | – | 0.9312 | 0.8672 |
Lorentzian: | −0.6391 | 0.5568 | 1.8002 | 3.0152 | 0.7955 | – | 0.9313 | 0.8673 |
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Yu, Z.; Løvås, T.; Konovalov, D.; Trushliakov, E.; Radchenko, M.; Kobalava, H.; Radchenko, R.; Radchenko, A. Investigation of Thermopressor with Incomplete Evaporation for Gas Turbine Intercooling Systems. Energies 2023, 16, 20. https://doi.org/10.3390/en16010020
Yu Z, Løvås T, Konovalov D, Trushliakov E, Radchenko M, Kobalava H, Radchenko R, Radchenko A. Investigation of Thermopressor with Incomplete Evaporation for Gas Turbine Intercooling Systems. Energies. 2023; 16(1):20. https://doi.org/10.3390/en16010020
Chicago/Turabian StyleYu, Zidong, Terese Løvås, Dmytro Konovalov, Eugeniy Trushliakov, Mykola Radchenko, Halina Kobalava, Roman Radchenko, and Andrii Radchenko. 2023. "Investigation of Thermopressor with Incomplete Evaporation for Gas Turbine Intercooling Systems" Energies 16, no. 1: 20. https://doi.org/10.3390/en16010020