CN113356952A - Combined cooling and power system capable of pre-cooling air at inlet of gas turbine and operation method thereof - Google Patents
Combined cooling and power system capable of pre-cooling air at inlet of gas turbine and operation method thereof Download PDFInfo
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/10—Adaptations for driving, or combinations with, electric generators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
- F01K13/006—Auxiliaries or details not otherwise provided for
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
- F01K13/02—Controlling, e.g. stopping or starting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
- F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
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Abstract
The invention discloses a combined cooling and power system capable of pre-cooling inlet air of a gas turbine and an operation method thereof, in the GT-KC-ERC combined cooling and power system, exhaust gas of GT circulation is used as a heat source of ERC, and the heat of GT exhaust gas can be further utilized, so that the temperature is further reduced, and the energy utilization rate is improved; the KC medium lean ammonia solution is used as a heat source of the ERC, the temperature of the refrigerant entering the GT exhaust heat exchanger can be increased, the GT exhaust temperature is not too low, and liquid fluid in the heat exchanger is prevented from occurring to damage the structure of the heat exchanger. According to the invention, through two purposes of the ERC cold energy, the precooling air can be obtained as much as possible under the condition of meeting the refrigeration requirement of a user by changing the flow rate of the air to the user; and the requirement of a power generation end can be met preferentially, and redundant cold energy is conveyed to a user.
Description
Technical Field
The invention belongs to the technical field of combined cooling and power, and particularly relates to a combined cooling and power system capable of pre-cooling air at an inlet of a gas turbine and an operation method thereof.
Background
Kalina Cycle (KC) was proposed in 1984, and since it uses non-azeotropic mixture ammonia water as a Cycle fluid, it can realize good matching with the temperature change curve of the heat source in the heat exchange process, and is widely used in the field of waste heat recovery of medium and low temperature heat sources. Many scholars use the kalina cycle to absorb the waste heat of the Gas Turbine cycle (GT) exhaust and form it into a GT-KC combined cycle power generation system. In addition to the demand for electricity generation, the demand for Refrigeration is also increasing, and further, there has been a combined cooling and power system in which an Ejector Regeneration Cycle (ERC) is used as a bottom Cycle of the GT-KC combined Cycle.
However, the currently proposed GT-KC-ERC combined cooling and power system is simpler in type, the ERC is only used for absorbing the heat of a condenser in the KC under most conditions, and although the gradient utilization of energy can be achieved, the contribution to the improvement of the overall operation efficiency is small; and the existing combined cooling and power supply system has two operation modes: the two modes of 'cooling with power' or 'cooling with power', both of which cause the limitation of a certain aspect of the power generation capacity or the cooling capacity, can not adapt to the needs of users well.
Disclosure of Invention
The present invention is directed to a combined cooling and power system and a method for operating the same, which can pre-cool inlet air of a combustion engine to solve one or more of the above-mentioned problems. In the invention, the exhaust gas of GT cycle and the poor ammonia solution in KC are used as the heat source of ERC, and the cold energy produced by ERC is partially used for users and partially used for precooling the air entering a combustion engine, thus improving the energy utilization rate.
In order to achieve the purpose, the invention adopts the following technical scheme:
the invention relates to a combined cooling and power system capable of pre-cooling air at an inlet of a combustion engine, which comprises:
a compressor;
the cold flow inlet of the preheater is communicated with the outlet of the compressor;
the fuel inlet of the combustion chamber is used for introducing fuel, and the air inlet of the combustion chamber is communicated with the cold flow outlet of the preheater;
the inlet of the gas turbine is communicated with the outlet of the combustion chamber, and the outlet of the gas turbine is communicated with the heat flow inlet of the preheater;
the heat flow inlet of the first heat exchanger is communicated with the heat flow outlet of the preheater;
the heat flow inlet of the second heat exchanger is communicated with the heat flow outlet of the first heat exchanger;
the inlet of the turbine is communicated with the cold flow outlet of the first heat exchanger;
the heat flow inlet of the first heat regenerator is communicated with the outlet of the turbine, and the cold flow outlet of the first heat regenerator is communicated with the cold flow inlet of the first heat exchanger;
the heat flow inlet of the second heat regenerator is communicated with the heat flow outlet of the first heat regenerator;
the first inlet of the first mixer is communicated with the heat flow outlet of the second regenerator;
the heat flow inlet of the first condenser is communicated with the outlet of the first mixer;
the inlet of the first flow divider is communicated with the hot flow outlet of the first condenser, and the first outlet of the first flow divider is communicated with the cold flow inlet of the second heat regenerator;
the first inlet of the second mixer is communicated with the second outlet of the first flow divider;
the hot flow inlet of the second condenser is communicated with the outlet of the second mixer, and the hot flow outlet of the second condenser is communicated with the cold flow inlet of the first heat regenerator;
an inlet of the ammonia water separator is communicated with a cold flow outlet of the second heat regenerator, and a first outlet of the ammonia water separator is communicated with a second inlet of the second mixer;
a heat flow inlet of the third heat exchanger is communicated with a second outlet of the ammonia water separator, and a heat flow outlet of the third heat exchanger is communicated with a second inlet of the first mixer; a cold flow outlet of the third heat exchanger is communicated with a cold flow inlet of the second heat exchanger;
the first inlet of the ejector is communicated with the cold flow outlet of the second heat exchanger;
the heat flow inlet of the third condenser is communicated with the outlet of the ejector;
an inlet of the second flow divider is communicated with a hot flow outlet of the third condenser, and a first outlet of the second flow divider is communicated with a cold flow inlet of the third heat exchanger;
the inlet of the third flow divider is communicated with the second outlet of the second flow divider;
a first inlet of the first evaporator is communicated with a first outlet of the third flow divider;
a third mixer, wherein the first inlet of the third mixer is communicated with the first outlet of the first evaporator, and the outlet of the third mixer is communicated with the second inlet of the ejector;
the heat flow inlet of the second evaporator is used for introducing air, and the heat flow outlet of the second evaporator is communicated with the inlet of the compressor; and a cold flow inlet of the second evaporator is communicated with a second outlet of the third flow divider, and a cold flow outlet of the second evaporator is communicated with a second inlet of the third mixer.
A further development of the invention is that the fluid temperature at the hot outlet of the second heat exchanger is above 80 ℃.
The invention further improves the method and also comprises the following steps: and the first generator is used for generating electricity through the driving of the gas turbine.
The invention further improves the method and also comprises the following steps: and the second generator is used for realizing power generation through turbine driving.
The invention is further improved in that a first regulating valve is arranged between the heat flow outlet of the preheater and the heat flow inlet of the first heat exchanger; a second regulating valve is arranged between the cold flow outlet of the second heat exchanger and the first inlet of the ejector, and a third regulating valve is arranged between the hot flow outlet of the second evaporator and the inlet of the compressor.
The invention is further improved in that a first throttle valve is arranged between the hot flow outlet of the third heat exchanger and the inlet of the first mixer; a second throttle valve is arranged between the inlet of the third flow divider and the second outlet of the second flow divider.
The invention is further improved in that a first booster pump is arranged between the outlet of the first condenser and the inlet of the first flow divider; a second booster pump is arranged between the hot flow outlet of the second condenser and the cold flow inlet of the first heat regenerator; and a third booster pump is arranged between the first outlet of the second flow divider and the cold flow inlet of the third heat exchanger.
The invention is further improved in that the air introduced into the compressor is precooled to 1-5 ℃.
The invention is further improved in that the second outlet temperature of the first evaporator is-4 to 0 ℃.
The invention discloses an operation method of a combined cooling and power system capable of pre-cooling air at an inlet of a combustion engine, which comprises the following steps of:
air is pre-cooled by a refrigerant in the second evaporator and then enters the compressor through the third regulating valve, the air compressed in the compressor is preheated by exhaust gas from the gas turbine in the preheater, the preheated air and fuel enter the combustion chamber for combustion and then enter the gas turbine for expansion to atmospheric pressure, and the generated mechanical power is used for driving the generator to generate power;
the exhaust gas of the gas turbine sequentially passes through the preheater, the first heat exchanger and the second heat exchanger and is finally discharged to the atmosphere; the exhaust of the gas turbine provides heat for an ammonia water working medium in KC in the first heat exchanger, and provides heat for a refrigerant of the ERC in the second heat exchanger;
after recovering the waste heat of GT exhaust in the first heat exchanger, the working ammonia solution enters a turbine to do work and is used for driving a generator to generate electricity; the working ammonia solution after acting sequentially passes through the first heat regenerator and the second heat regenerator, enters the first mixer 13 and is mixed with the poor ammonia solution to form a basic ammonia solution; the basic ammonia solution is condensed by a first condenser, and is divided into two flows after being introduced into a first flow divider 16; one stream of fluid absorbs heat of the working ammonia solution after acting through a second heat regenerator, enters an ammonia water separator and is separated into ammonia-rich steam and ammonia-poor solution, the ammonia-poor solution provides heat for a refrigerant of the ERC in a third heat exchanger, and then is mixed with the working ammonia solution after acting in a first mixer to form a basic ammonia solution; mixing the ammonia-rich steam and the other stream of fluid in a second mixer to form a working ammonia solution;
after the working ammonia solution is condensed by the second condenser, the heat of the working ammonia solution after acting is absorbed in the first heat regenerator and enters the first heat exchanger;
the refrigerant in the ERC firstly absorbs the heat of the lean ammonia solution in the third heat exchanger, and then the residual heat of GT exhaust gas is recovered by the second heat exchanger; then, the refrigerant enters the ejector, is mixed with low-pressure fluid and then exchanges heat with condensed water through a third condenser; in the second flow divider, one fluid is sequentially introduced into a third heat exchanger and a second heat exchanger to absorb the heat of GT and KC, and the other fluid is introduced into a third flow divider to be divided into two fluids; one flow after being divided by the third flow divider enters the first evaporator to convey cold energy for a user side, the other flow enters the second evaporator to pre-cool air, and the two flows are mixed in the third mixer and then enter the ejector.
Compared with the prior art, the invention has the following beneficial effects:
in the GT-KC-ERC combined cooling and power system, the exhaust gas of GT circulation is used as the heat source of ERC, and the heat of GT exhaust gas can be further utilized, so that the temperature is further reduced, and the energy utilization rate is improved. The KC medium lean ammonia solution is used as a heat source of the ERC, the temperature of the refrigerant entering the GT exhaust heat exchanger can be increased, the GT exhaust temperature is not too low (higher than 80 ℃), and liquid fluid in the heat exchanger is prevented from damaging the structure of the heat exchanger.
In the invention, the cold energy produced by ERC can be used for precooling the air entering the combustion engine, the power consumption of the compressor can be reduced, the thermal efficiency of GT is improved, and the air can be precooled to 1-5 ℃.
In the present invention, another part of the cold energy produced by ERC is provided to the user and can be used for refrigeration (-4 to 0 ℃).
In summary, through two uses of the ERC cold energy, the precooling air can be obtained as much as possible under the condition of meeting the refrigeration requirement of the user by changing the flow rate of the air to the user; and the requirement of a power generation end can be met preferentially, and redundant cold energy is conveyed to a user.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art are briefly introduced below; it is obvious that the drawings in the following description are some embodiments of the invention, and that for a person skilled in the art, other drawings can be derived from them without inventive effort.
FIG. 1 is a schematic diagram of a combined cooling and power system for pre-cooling inlet air of a combustion engine according to an embodiment of the present invention;
FIG. 2 is a graph illustrating COP (coefficient of energy efficiency) values of different refrigerants with different refrigeration temperatures in accordance with an embodiment of the present invention;
FIG. 3 is a graph illustrating COP values for different refrigerants with different ERC pressure ratios in an embodiment of the present invention; wherein the ERC pressure ratio refers to the pressure ratio of the cold end of the second heat exchanger 8 and the third condenser 25;
FIG. 4 is a graphical representation of the amount of refrigeration and the amount of work as a function of different refrigeration temperatures in an embodiment of the present invention;
FIG. 5 is a graph illustrating energy costs as a function of different refrigeration temperatures in an embodiment of the present invention;
in fig. 1, a compressor; 2. a preheater; 3. a combustion chamber; 4. a gas turbine; 5. a first generator; 6. a first regulating valve; 7. a first heat exchanger; 8. a second heat exchanger; 9. a turbine; 10. a second generator; 11. a first heat regenerator; 12. a second regenerator; 13. a first mixer; 14. a first condenser; 15. a first booster pump; 16. a first splitter; 17. a second mixer; 18. a second condenser; 19. a second booster pump; 20. an ammonia water separator; 21. a third heat exchanger; 22. a first throttle valve; 23. a second regulating valve; 24. an ejector; 25. a third condenser; 26. a second flow splitter; 27. a third booster pump; 28. a second throttle valve; 29. a third current divider; 30. a first evaporator; 31. a third mixer; 32. a second evaporator; 33. and a third regulating valve.
Detailed Description
In order to make the purpose, technical effect and technical solution of the embodiments of the present invention clearer, the following clearly and completely describes the technical solution of the embodiments of the present invention with reference to the drawings in the embodiments of the present invention; it is to be understood that the described embodiments are only some of the embodiments of the present invention. Other embodiments, which can be derived by one of ordinary skill in the art from the disclosed embodiments without inventive faculty, are intended to be within the scope of the invention.
Referring to fig. 1, a combined cooling and power system for pre-cooling intake air of a combustion engine according to an embodiment of the present invention includes:
GT part: air enters from a first inlet of the second evaporator 32, a first outlet of the second evaporator 32 is connected with an inlet of a third regulating valve 33, an outlet of the third regulating valve 33 is connected with an inlet of the compressor 1, an outlet of the compressor 1 is connected with a first inlet of the preheater 2, a first outlet of the preheater 2 is connected with an inlet of the combustion chamber 3, and fuel enters the combustion chamber 3 together with the air to be combusted. The outlet of the combustion chamber 3 is connected with the inlet of a gas turbine 4 (optionally, the gas turbine 4 is coaxially connected with a first generator 5), the outlet of the gas turbine 4 is connected with the second inlet of a preheater 2, the second outlet of the preheater 2 is connected with the inlet of a first regulating valve 6, the outlet of the first regulating valve 6 is connected with the first inlet of a first heat exchanger 7, the first outlet of the first heat exchanger 7 is connected with the first inlet of a second heat exchanger 8, and the first outlet of the second heat exchanger 8 is connected with the atmosphere.
KC part: the working ammonia solution enters a second inlet of the first heat exchanger 7, a second outlet of the first heat exchanger 7 is connected with an inlet of a turbine 9 (optionally, the turbine 9 is coaxially connected with a second generator 10), an outlet of the turbine 9 is connected with a first inlet of a first regenerator 11, a first outlet of the first regenerator 11 is connected with a first inlet of a second regenerator 12, a first outlet of the second regenerator 12 is connected with a first inlet of a first mixer 13, an outlet of the first mixer 13 is connected with an inlet of a first condenser 14, an outlet of the first condenser 14 is connected with an inlet of a first booster pump 15, and an outlet of the first booster pump 15 is connected with an inlet of a first flow divider 16.
A first outlet of the first flow divider 16 is connected to a first inlet of the second mixer 17, a second outlet of the first flow divider 16 is connected to a second inlet of the second regenerator 12, a second outlet of the second regenerator 12 is connected to an inlet of the ammonia water separator 20, a first outlet of the ammonia water separator 20 is connected to a second inlet of the second mixer 17, a second outlet of the ammonia water separator 20 is connected to a first inlet of the third heat exchanger 21, a first outlet of the third heat exchanger 21 is connected to an inlet of the first throttle valve 22, and an outlet of the first throttle valve 22 is connected to a second inlet of the first mixer 13.
An outlet of the second mixer 17 is connected with an inlet of the second condenser 18, an outlet of the second condenser 18 is connected with an inlet of the second booster pump 19, an outlet of the second booster pump 19 is connected with a second inlet of the first heat regenerator 11, and a second outlet of the first heat regenerator 11 is connected with a second inlet of the first heat exchanger 7.
ERC part: the refrigerant enters a second inlet of the third heat exchanger 21, a second outlet of the third heat exchanger 21 is connected with a second inlet of the second heat exchanger 8, a second outlet of the second heat exchanger 8 is connected with an inlet of a second regulating valve 23, an outlet of the second regulating valve 23 is connected with a first inlet of an ejector 24, an outlet of the ejector 24 is connected with an inlet of a third condenser 25, and an outlet of the third condenser 25 is connected with an inlet of a second flow divider 26.
A first outlet of the second flow divider 26 is connected to an inlet of the third booster pump 27, and an outlet of the third booster pump 27 is connected to a second inlet of the third heat exchanger 21. The second outlet of the second flow divider 26 is connected to the inlet of a second throttle 28, the outlet of the second throttle 28 is connected to the inlet of a third flow divider 29, the first outlet of the third flow divider 29 is connected to the first inlet of a first evaporator 30, and the first outlet of the first evaporator 30 is connected to the first inlet of a third mixer 31. A second outlet of the third flow divider 29 is connected to a second inlet of the second evaporator 32, a second outlet of the second evaporator 32 is connected to a second inlet of the third mixer 31, and an outlet of the third mixer 31 is connected to a second inlet of the ejector 24. The second inlet and the second outlet of the first evaporator 30 are connected to the user side, and exchange heat with the user side to cool the user side.
According to the embodiment of the invention, in the GT-KC-ERC combined cooling and power system, the exhaust gas of GT circulation is used as the heat source of ERC, so that the heat of GT exhaust gas can be further utilized, the temperature of the GT exhaust gas is further reduced, and the energy utilization rate is improved. The KC medium lean ammonia solution is used as a heat source of the ERC, the temperature of the refrigerant entering the GT exhaust heat exchanger can be increased, the GT exhaust temperature is not too low (higher than 80 ℃), and liquid fluid in the heat exchanger is prevented from damaging the structure of the heat exchanger.
The working process of the system in the embodiment of the invention is as follows:
GT part: air enters the compressor 1 through the third regulating valve 33 after being precooled by the refrigerant in the second evaporator 32, the air compressed in the compressor 1 is preheated by exhaust gas from the gas turbine 4 in the preheater 2, the preheated air and fuel enter the combustion chamber 3 together and then are fully combusted, and the air enters the gas turbine 4 and is expanded to atmospheric pressure, and the generated mechanical work is converted into current through the first generator 5 and then is transmitted to the outside.
Thereafter, the exhaust gas of the gas turbine 4 passes through the preheater 2, the first regulating valve 6, the first heat exchanger 7 and the second heat exchanger 8 in this order, and is finally discharged to the atmosphere. Wherein, the exhaust gas of the gas turbine 4 provides heat for ammonia water working medium in KC in the first heat exchanger 7, and provides heat for refrigerant of ERC in the second heat exchanger 8.
KC part: after the waste heat of the GT exhaust is recovered by the working ammonia solution in the first heat exchanger 7, the working ammonia solution enters the turbine 9 to do work and outputs current to the outside through the second generator 10. The working ammonia solution after working passes through the first heat regenerator 11 and the second heat regenerator 12 in sequence, and finally enters the first mixer 13 to be mixed with the lean ammonia solution to form the basic ammonia solution. The base ammonia solution is condensed by the first condenser 14, and then raised in pressure by the first booster pump 15.
Then split into two streams in the first splitter 16; one of the streams absorbs the heat of the working ammonia solution after work is done by the second heat regenerator 12, and enters the ammonia water separator 20 to be separated into ammonia-rich steam and ammonia-poor solution. The ammonia-lean solution first provides heat for the refrigerant of the ERC in the third heat exchanger 21, and then is throttled by the first throttle valve 22 and mixed with the working ammonia solution after work is done in the first mixer 13 to form the basic ammonia solution. The ammonia-rich vapor is then mixed directly with the other stream in a second mixer 17 to form the working ammonia solution.
After the working ammonia solution is condensed by the second condenser 18 and the pressure of the working ammonia solution is increased by the second booster pump 19, the heat of the working ammonia solution after work is absorbed in the first heat regenerator 11, and the working ammonia solution enters the first heat exchanger 7 to complete a cycle.
ERC part: the refrigerant in the ERC first absorbs the heat of the lean ammonia solution in the third heat exchanger 21, rises above 80 ℃, and then recovers the residual heat of the GT exhaust gas through the second heat exchanger 8. Thereafter, the refrigerant enters the ejector 24 through the second regulating valve 23, is mixed with the low-pressure fluid, and exchanges heat with the condensed water through the third condenser 25. In the second splitter 26, a flow of fluid passes through a third booster pump 27 to absorb the heat of GT and KC; the other stream is divided into two streams again in the third flow divider 29 after passing through the second throttle valve 28, one stream enters the first evaporator 30 to deliver refrigeration to the user side, and the other stream enters the second evaporator 32 to pre-cool the air. Finally, the two streams are mixed in third mixer 31 and carried by the high pressure stream into ejector 24.
According to the above embodiments of the present invention, the cooling energy produced by ERC can be used to pre-cool the air entering GT, which can reduce the power consumption of the compressor and increase the thermal efficiency of GT, and the air can be pre-cooled to 1-5 ℃. In the present invention, another part of the cold energy produced by ERC is provided to the user and can be used for refrigeration (-4 to 0 ℃). In summary, through two uses of the ERC cold energy, the precooling air can be obtained as much as possible under the condition of meeting the refrigeration requirement of the user by changing the flow rate of the air to the user; and the requirement of a power generation end can be met preferentially, and redundant cold energy is conveyed to a user.
Referring to fig. 2, in the embodiment of the present invention, the COP of each of the three refrigerants increases with the increase of the cooling temperature, which results in the decrease of the cooling capacity required for pre-cooling the air, and the entrainment rate of the ejector increases, so the COP of ERC increases. Wherein, the COP of R600a and R1234ze is not much different, the absolute value of COP can be increased by 1.3-1.7% by R600a relative to R1234ze, and the absolute value of COP can be increased by 7.9-8.9% by R290 relative to R600 a. For R290, the absolute value of COP decreases by about 1.8% for every 0.5 ℃ decrease in refrigeration temperature.
Referring to fig. 3, in the embodiment of the present invention, the COP values of all three refrigerants increase with the increase of the ERC pressure ratio (the ERC pressure ratio refers to the pressure ratio between the cold end of the second heat exchanger 8 and the third condenser 25), which represents the pressure variation range of the ERC operation, and the larger the pressure ratio, the higher the ejector entrainment rate and the higher the COP. Wherein, the COP of R600a and R1234ze are very similar, the absolute value of COP of R600a relative to R1234ze can be increased by 0.7-1.5%, and the absolute value of COP of R290 relative to R600a can be increased by 6.5-8.2%. For R290, the absolute value of COP decreases by about 2.9% for every 0.5 decrease in pressure ratio.
Referring to fig. 4, in the embodiment of the present invention, the total generated power of the system is reduced from 6295.96kW to 6133.29kW because the temperature of the pre-cooled air entering the compressor is increased and the power consumed by the compressor is reduced due to the increase of the cooling temperature. Meanwhile, the increase of the cooling temperature causes the increase of COP, so that the cooling power of the system is increased from 165.93kW to 402.46 kW. Obviously, the increase in system cooling power is greater than the decrease in power generation power.
Referring to FIG. 5, in the embodiment of the present invention, since the increase of the cooling temperature increases the cooling power, the exchange area of the evaporator needs to be increased, which results in a slight increase of the energy cost from 4.05/kWh to 4.052/kWh. Despite the drop in generated power, the overall efficiency rose from 50.115% to 51.297% due to the significant increase in refrigeration power.
In summary, in the conventional cascade system, the method that GT exhausts gas to KC as a heat source and ERC as a KC heat source is usually adopted, once the power generation amount is determined, the cooling amount is determined, that is, "cooling by work" is determined, because the parameters in the system are all changed cooperatively. In the system of the present invention, the exhaust of GT drives not only the KC but also the ERC; meanwhile, the cold energy generated by the ERC is not only transmitted to the user, but also transmitted to the GT for precooling the air, thereby improving the GT efficiency. In conclusion, the invention can improve the overall efficiency of the system, not only can the exhaust of the GT be further utilized, but also the cold energy of the ERC is used for the GT, and the GT efficiency can be improved in two aspects; instead of "power on cooling" and "power on cooling", the cold energy of the ERC can be used in both ways, giving the user only a portion, and in addition the ERC gets energy from two places with much better flexibility than just getting energy from the KC.
Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art can make modifications and equivalents to the embodiments of the present invention without departing from the spirit and scope of the present invention, which is set forth in the claims of the present application.
Claims (10)
1. A combined cooling and power system for precooling inlet air to a combustion engine, comprising:
a compressor (1);
the cold flow inlet of the preheater (2) is communicated with the outlet of the compressor (1);
the combustion chamber (3), the fuel inlet of the combustion chamber (3) is used for introducing fuel, and the air inlet of the combustion chamber (3) is communicated with the cold flow outlet of the preheater (2);
the inlet of the gas turbine (4) is communicated with the outlet of the combustion chamber (3), and the outlet of the gas turbine (4) is communicated with the heat flow inlet of the preheater (2);
the heat flow inlet of the first heat exchanger (7) is communicated with the heat flow outlet of the preheater (2);
the heat flow inlet of the second heat exchanger (8) is communicated with the heat flow outlet of the first heat exchanger (7);
the inlet of the turbine (9) is communicated with the cold flow outlet of the first heat exchanger (7);
a hot flow inlet of the first heat regenerator (11) is communicated with an outlet of the turbine (9), and a cold flow outlet of the first heat regenerator (11) is communicated with a cold flow inlet of the first heat exchanger (7);
the heat flow inlet of the second regenerator (12) is communicated with the heat flow outlet of the first regenerator (11);
a first mixer (13), wherein a first inlet of the first mixer (13) is communicated with a heat flow outlet of the second regenerator (12);
a first condenser (14), the hot flow inlet of the first condenser (14) is communicated with the outlet of the first mixer (13);
the inlet of the first flow divider (16) is communicated with the hot flow outlet of the first condenser (14), and the first outlet of the first flow divider (16) is communicated with the cold flow inlet of the second regenerator (12);
a second mixer (17), a first inlet of the second mixer (17) is communicated with a second outlet of the first flow divider (16);
a second condenser (18), wherein a hot flow inlet of the second condenser (18) is communicated with an outlet of the second mixer (17), and a hot flow outlet of the second condenser (18) is communicated with a cold flow inlet of the first heat regenerator (11);
an inlet of the ammonia water separator (20) is communicated with a cold flow outlet of the second heat regenerator (12), and a first outlet of the ammonia water separator (20) is communicated with a second inlet of the second mixer (17);
a heat flow inlet of the third heat exchanger (21) is communicated with a second outlet of the ammonia water separator (20), and a heat flow outlet of the third heat exchanger (21) is communicated with a second inlet of the first mixer (13); the cold flow outlet of the third heat exchanger (21) is communicated with the cold flow inlet of the second heat exchanger (8);
an ejector (24), a first inlet of the ejector (24) is communicated with a cold flow outlet of the second heat exchanger (8);
a third condenser (25), the heat flow inlet of the third condenser (25) is communicated with the outlet of the ejector (24);
an inlet of the second flow divider (26) is communicated with a hot flow outlet of the third condenser (25), and a first outlet of the second flow divider (26) is communicated with a cold flow inlet of the third heat exchanger (21);
the inlet of the third flow divider (29) is communicated with the second outlet of the second flow divider (26);
a first evaporator (30), a first inlet of the first evaporator (30) is communicated with a first outlet of the third flow divider (29);
a third mixer (31), a first inlet of the third mixer (31) being in communication with a first outlet of the first evaporator (30), an outlet of the third mixer (31) being in communication with a second inlet of the ejector (24);
a second evaporator (32), wherein a hot flow inlet of the second evaporator (32) is used for introducing air, and a hot flow outlet of the second evaporator (32) is communicated with an inlet of the compressor (1); the cold flow inlet of the second evaporator (32) is communicated with the second outlet of the third flow divider (29), and the cold flow outlet of the second evaporator (32) is communicated with the second inlet of the third mixer (31).
2. The cogeneration system for precooling the inlet air of a combustion engine as recited in claim 1, wherein the fluid temperature at the hot outlet of the second heat exchanger (8) is above 80 ℃.
3. The combined cooling and power system for pre-cooling intake air of a combustion engine as set forth in claim 1, further comprising:
the first generator (5) is used for generating electricity through the driving of the gas turbine (4).
4. The combined cooling and power system for pre-cooling intake air of a combustion engine as set forth in claim 1, further comprising:
and the second generator (10) is used for generating electricity through the driving of the turbine (9).
5. The cogeneration system for precooling the inlet air of a combustion engine as claimed in claim 1, wherein a first regulating valve (6) is arranged between the hot outlet of the preheater (2) and the hot inlet of the first heat exchanger (7); a second regulating valve (23) is arranged between the cold flow outlet of the second heat exchanger (8) and the first inlet of the ejector (24); a third regulating valve (33) is arranged between the hot flow outlet of the second evaporator (32) and the inlet of the compressor (1).
6. The cogeneration system for pre-cooling inlet air of a combustion engine according to claim 1, wherein a first throttle valve (22) is arranged between the hot outflow port of the third heat exchanger (21) and the inlet of the first mixer (13); a second throttle valve (28) is arranged between the inlet of the third flow divider (29) and the second outlet of the second flow divider (26).
7. The combined cooling and power system capable of pre-cooling air at the inlet of the combustion engine according to claim 1, wherein a first booster pump (15) is arranged between the outlet of the first condenser (14) and the inlet of the first flow divider (16); a second booster pump (19) is arranged between the hot flow outlet of the second condenser (18) and the cold flow inlet of the first heat regenerator (11); and a third booster pump (27) is arranged between the first outlet of the second flow divider (26) and the cold flow inlet of the third heat exchanger (21).
8. The combined cooling and power system capable of pre-cooling inlet air of a combustion engine according to claim 1, wherein air introduced into the compressor (1) is pre-cooled to 1-5 ℃.
9. The combined cooling and power system capable of pre-cooling air at the inlet of a combustion engine according to claim 1, wherein the second outlet temperature of the first evaporator (30) is-4 to 0 ℃.
10. A method of operating a combined cooling and power system for precooling engine inlet air as recited in claim 1, comprising the steps of:
air is pre-cooled by a refrigerant in the second evaporator and then enters the compressor through the third regulating valve, the air compressed in the compressor is preheated by exhaust gas from the gas turbine in the preheater, the preheated air and fuel enter the combustion chamber for combustion and then enter the gas turbine for expansion to atmospheric pressure, and the generated mechanical power is used for driving the generator to generate power;
the exhaust gas of the gas turbine sequentially passes through the preheater, the first heat exchanger and the second heat exchanger and is finally discharged to the atmosphere; the exhaust of the gas turbine provides heat for an ammonia water working medium in KC in the first heat exchanger, and provides heat for a refrigerant of the ERC in the second heat exchanger;
after recovering the waste heat of GT exhaust in the first heat exchanger, the working ammonia solution enters a turbine to do work and is used for driving a generator to generate electricity; the working ammonia solution after acting sequentially passes through the first heat regenerator and the second heat regenerator, enters the first mixer 13 and is mixed with the poor ammonia solution to form a basic ammonia solution; the basic ammonia solution is condensed by a first condenser, and is divided into two flows after being introduced into a first flow divider 16; one stream of fluid absorbs heat of the working ammonia solution after acting through a second heat regenerator, enters an ammonia water separator and is separated into ammonia-rich steam and ammonia-poor solution, the ammonia-poor solution provides heat for a refrigerant of the ERC in a third heat exchanger, and then is mixed with the working ammonia solution after acting in a first mixer to form a basic ammonia solution; mixing the ammonia-rich steam and the other stream of fluid in a second mixer to form a working ammonia solution;
after the working ammonia solution is condensed by the second condenser, the heat of the working ammonia solution after acting is absorbed in the first heat regenerator and enters the first heat exchanger;
the refrigerant in the ERC firstly absorbs the heat of the lean ammonia solution in the third heat exchanger, and then the residual heat of GT exhaust gas is recovered by the second heat exchanger; then, the refrigerant enters the ejector, is mixed with low-pressure fluid and then exchanges heat with condensed water through a third condenser; in the second flow divider, one fluid is sequentially introduced into a third heat exchanger and a second heat exchanger to absorb the heat of GT and KC, and the other fluid is introduced into a third flow divider to be divided into two fluids; one flow after being divided by the third flow divider enters the first evaporator to convey cold energy for a user side, the other flow enters the second evaporator to pre-cool air, and the two flows are mixed in the third mixer and then enter the ejector.
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