CN220667686U - Gas turbine flue gas waste heat utilization device - Google Patents
Gas turbine flue gas waste heat utilization device Download PDFInfo
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- CN220667686U CN220667686U CN202322423279.1U CN202322423279U CN220667686U CN 220667686 U CN220667686 U CN 220667686U CN 202322423279 U CN202322423279 U CN 202322423279U CN 220667686 U CN220667686 U CN 220667686U
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- 239000007789 gas Substances 0.000 title claims abstract description 97
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 title claims abstract description 37
- 239000003546 flue gas Substances 0.000 title claims abstract description 37
- 239000002918 waste heat Substances 0.000 title claims abstract description 33
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 157
- AMXOYNBUYSYVKV-UHFFFAOYSA-M lithium bromide Chemical compound [Li+].[Br-] AMXOYNBUYSYVKV-UHFFFAOYSA-M 0.000 claims abstract description 98
- 238000010521 absorption reaction Methods 0.000 claims abstract description 50
- 239000008236 heating water Substances 0.000 claims abstract description 26
- 238000010438 heat treatment Methods 0.000 claims description 41
- 230000001105 regulatory effect Effects 0.000 claims description 30
- 239000000498 cooling water Substances 0.000 claims description 21
- 238000001816 cooling Methods 0.000 claims description 15
- 239000006096 absorbing agent Substances 0.000 claims description 4
- 238000011144 upstream manufacturing Methods 0.000 claims description 3
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 20
- 239000003345 natural gas Substances 0.000 description 10
- 238000002485 combustion reaction Methods 0.000 description 9
- 230000007423 decrease Effects 0.000 description 7
- 239000000446 fuel Substances 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
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- 238000001914 filtration Methods 0.000 description 4
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- 230000004048 modification Effects 0.000 description 2
- 238000010248 power generation Methods 0.000 description 2
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- RZVAJINKPMORJF-UHFFFAOYSA-N Acetaminophen Chemical group CC(=O)NC1=CC=C(O)C=C1 RZVAJINKPMORJF-UHFFFAOYSA-N 0.000 description 1
- 239000010754 BS 2869 Class F Substances 0.000 description 1
- NINIDFKCEFEMDL-UHFFFAOYSA-N Sulfur Chemical compound [S] NINIDFKCEFEMDL-UHFFFAOYSA-N 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
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- 238000009792 diffusion process Methods 0.000 description 1
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- 230000008020 evaporation Effects 0.000 description 1
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- 230000008014 freezing Effects 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 239000002737 fuel gas Substances 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
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- 239000000463 material Substances 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
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- 239000000126 substance Substances 0.000 description 1
- 229910052717 sulfur Inorganic materials 0.000 description 1
- 239000011593 sulfur Substances 0.000 description 1
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Abstract
The utility model discloses a gas turbine flue gas waste heat utilization device, which comprises a lithium bromide absorption type cold and hot water unit and a plurality of fan wall air treatment units, wherein a driving heat source of the lithium bromide absorption type cold and hot water unit is from a low-temperature economizer device group, and a generator of the lithium bromide absorption type cold and hot water unit is connected with the low-temperature economizer device group through a heating water supply pipe and a heating water return pipe; the fan wall air treatment units are respectively arranged at two sides of the air inlet device, and the fan wall air treatment units are connected with an evaporator of the lithium bromide absorption type cold and hot water unit through a chilled water supply pipe and a chilled water return pipe. The device of the utility model can ensure that the gas turbine can run economically, environmentally-friendly, safely and stably under all working conditions.
Description
Technical Field
The utility model relates to the technical field of gas power stations, in particular to a gas turbine flue gas waste heat utilization device.
Background
1. Air compressor inlet temperature and humidity
Gas turbines are gaining attention for their excellent thermal performance and low pollution emissions. The gas turbine steam combined cycle unit has the advantages of quick start, strong peak shaving performance and increasingly wide application in an electric power system.
The gas turbine is a constant volume power machine. After the gas turbine is connected with the grid, the rotating speed of the gas turbine is not changed any more.
The total power N of the gas-steam combined cycle unit is as follows:
N＝ N t -N st -N y -N zl (1)
in the formula (1): n (N) t -the output (output power) of the gas turbine; n (N) st -the output power of the steam turbine; n (N) zl -the power consumption of the refrigeration unit.
Power consumption N of air compressor y The method comprises the following steps:
N y ＝ M a C pa T 1 (ε (K-1) K -1)/η y (2)
in the formula (2): m is M a -compressor inlet flow rate; t (T) 1 -compressor inlet air temperature; epsilon-compressor pressure ratio; η (eta) y -compressor efficiency; c (C) pa -air constant pressure specific heat capacity; k-air insulation index.
The performance of a gas turbine, as well as its operational safety and economy, are closely related to the quality and characteristics of the atmosphere.
As can be seen from equation (2), compressor power consumption increases as the ambient temperature increases. The compressor mass intake flow decreases as the ambient temperature increases. The compressor pressure ratio decreases with increasing ambient temperature, which will lead to an increase in the exhaust gas temperature of the gas turbine and a decrease in work, even if the rotational speed of the unit and the initial gas temperature before the gas turbine remain constant. Which in turn causes a reduction in gas turbine output. In high temperature weather, the gas turbine output is severely reduced, and the efficiency is also reduced. The ambient temperature has a greater effect on the gas turbine output than the efficiency.
For a class F gas turbine, cooling 35℃air to 15℃in summer increases the gas turbine output by about 11.17%. The gas turbine output is maximized at ambient temperature of about 3 ℃.
The air humidity also affects the power and heat rate of the gas turbine, and when the intake air moisture content increases, the power of the gas turbine decreases and the heat rate increases. However, the influence is generally small, the unit power is changed within 2 per mill and the heat rate is changed within 1% in the whole humidity change range.
2. IGV (Adjustable inlet guide vane)
The combined cycle unit can stably run within the load range of 30% -100%. The change in load is achieved by changing the intake air flow rate and the fuel flow rate under the condition that the fuel/air equivalent ratio is kept unchanged.
The gas turbine is an open cycle with air as a working medium, and the adjustment of the air inlet flow is realized by changing the opening of the IGV of the compressor.
And under normal operation of the unit, the control of the exhaust temperature of the gas turbine is realized through the control of the opening degree of the IGV.
And controlling the air inlet temperature of the gas turbine according to the exhaust temperature and the air pressure at the outlet of the compressor, so that the unit efficiency is highest.
When the gas turbine air inlet system runs in winter, due to the Joule-Thompson throttling effect, icing and frosting phenomena of different degrees can occur at the IGV position and at the muffler and filter element outlet, and the danger of 'swallowing ice' is extremely easy to occur. The decrease of the opening degree of the IGV can cause the temperature of the air inlet of the air compressor to decrease, and the temperature decrease (5-6K) caused by the increase of the air flow rate at the IGV is much larger than that of the silencer (< 1K) and the filter element (< 1K).
When the gas turbine is running, the compressor will not enter surge as long as the compressor pressure ratio does not exceed the value on the surge boundary line. The pressure ratio is ensured not to exceed the operation limit, and the working medium is ensured to be folded to flowAnd the surge flow is larger than the corresponding critical pressure ratio. When the rotation speed and the pressure ratio are unchanged, the opening degree of the IGV is reduced, the flow is reduced, the surge margin is reduced by the compressor, and the compressor can possibly surge.
3. Potential for tail flue gas waste heat utilization
Because of the heat load matching, the heat exchange area of the low-temperature economizer cannot be designed to be too large in order to avoid water vaporization in the low-temperature economizer. During normal operation of the 9F-level gas-steam combined cycle unit, the tail flue gas temperature is generally 80-90 ℃, and the tail flue gas temperature can be reduced to about 70 ℃ because the natural gas has low sulfur content, so that the tail flue gas waste heat has larger recovery potential.
Taking a 9F type gas turbine (model: AE94.3A; smoke volume: 749.6kg/s; tail smoke temperature: 80 ℃) as an example, by increasing the heated area of the low-temperature economizer and reducing the smoke exhaust temperature to 70 ℃, more smoke waste heat is extracted, and the high-temperature hot water generated by the method is used for cooling/heating a gas turbine system, so that the thermodynamic parameters of the steam-water system can be kept unchanged according to heat balance calculation, and power generation cannot be influenced.
The amount of combustion air in a known gas turbine under full load conditions is: 732.2kg/s; consumption of natural gas: 16.875kg/s, the specific heat of natural gas at constant pressure is 2.16 kJ/(kg.K); smoke amount: 749.6kg/s, the specific heat of the flue gas at constant pressure is 1.06 kJ/(kg.K); the outlet water temperature of the low-temperature economizer is 151.5 ℃, the approach point temperature difference of the low-temperature economizer is 3-5 ℃, the inlet water temperature of the low-temperature economizer is not more than 60 ℃, and the maximum water quantity of the high-temperature water in the part is about 75t/h and the maximum heat supply quantity is about 8MW through calculation.
4. NO (NO) x CO emissions
To increase the efficiency of gas turbine operation, conventional thermodynamic cycles strive for higher cycle heat absorption temperatures, but are limited by the turbine blade cooling technology and materials that allow for turbine initial temperatures.
Thermal NO with increasing combustion temperature x The amount of emissions will be greatly increased and the combustion temperature will be limited to avoid economic penalties for environmental reasons and penalties to stop power generation.
Typically, gas turbines employ lean burn, and control the fuel/air equivalence ratio to be less than 1, reducing the gas temperature to within a reasonable range, allowing NO x The emission amount reaches the environmental protection emission standard.
When the gas turbine is operated under the load of less than 75% of rated output, the output power and the temperature before the turbine are ensured not to exceedOver-limiting, the combustion temperature cannot be controlled to produce acceptable NO x In the temperature range of CO level, it is also difficult to maintain continuous premixed combustion, thus NO x The CO emissions cannot meet the low emission requirements.
5. Machine set shutdown problem
In addition, the loss caused by the shutdown of the unit far exceeds the investment of equipment, and the unit shutdown accident caused by the system failure of the voltage regulating station and the failure of the natural gas temperature is avoided, so that the problem of ensuring the safe and reliable operation of the system and the equipment is the first consideration.
6. With respect to charge air cooling
To increase the efficiency of gas turbine operation, in peak shaving mode, the temperature ratio t/t of the gas turbine is typically increased 0 To improve the cycle performance, wherein t is the initial temperature of the fuel gas, t 0 Is the initial temperature of the air intake.
The intake air cooling device is the most effective, safe and reliable method for improving the output of the gas turbine in summer. Charge air coolers typically employ cooling coils and spray coolers.
Adopts a cooling coil cooling mode, and wind resistance (pressure difference between inlet and outlet of cooling coil is 20-30 mH) 2 O) is relatively large, and can cause the power consumption loss of the compressor. The compressor power consumption accounts for about 70% of the power consumption of the gas turbine system.
The spray cooling system is simple, and the initial investment and the running cost are low. However, an increase in air moisture content will load the compressor and gas turbine performance is affected. Trace impurities can cause corrosion of gas turbine blades, and thus the water source for spray cooling systems is typically demineralized water. From the technical and economic point of view, the spray cooling technology is most suitable for being adopted in Xinjiang Turpan region of China.
7. Regarding intake air heating
By increasing the inlet temperature of the compressor and increasing the inlet flow, the pressure ratio of the compressor can be reduced. To ensure safety, the conventional methods are as follows:
1) Before the gas turbine is started, the natural gas must be discharged to the air, and the unit is not allowed to be started until the air inlet temperature is higher than 15 ℃ (the technical specification of GE company is required), so that the discharge loss and the cold source waste are caused;
2) Extracting no more than 5% (mass flow) of high temperature air from the compressor discharge casing to mix with the compressor inlet and inlet air when the ambient temperature falls below 40°f and the difference between the compressor inlet temperature and the dew point temperature is no more than 10°f, but such an inlet bleed air heating system (IBH) reduces gas turbine power and thermal efficiency; when the IBH fails, the safe operation of the unit can be influenced; the air extraction process causes interference to the operation of the gas turbine; because the load fluctuation of the gas turbine is large, the IBH is frequently triggered to start, so that the running economy of the unit is poor;
3) A flue gas recirculation heating system (flue gas recirculation, FGR), i.e. a certain amount of flue gas is extracted and mixed with air before being introduced into the filtration system;
4) A low-grade waste heat exchange device (medium heat exchanger system, HES) of the bottom circulation system is arranged in front of the air inlet filter.
8. Wet blocking phenomenon
In high-humidity weather, the air inlet filter system of the gas turbine is easy to generate wet blockage phenomenon that the pressure difference is suddenly increased under the influence of J-T effect, and a power plant can only deal with the situation that the load of the gas turbine is reduced or the gas turbine jumps. Wet blockage not only greatly reduces the reliability of the inlet air filtering system, but also seriously affects the safety and economy of the operation of the gas turbine.
In view of the above, the present inventors devised a flue gas waste heat utilization device for a gas turbine in order to overcome the above-mentioned problems.
Disclosure of Invention
The utility model aims to overcome the defects that in the prior art, the opening of an IGV is too small under a partial load working condition to enable a compressor to surge, the temperature of a gas turbine is relatively small under a full load working condition, and a wet blocking phenomenon is easy to occur in an air inlet filtering system of the gas turbine, and provides a flue gas waste heat utilization device of the gas turbine.
The utility model solves the technical problems by the following technical proposal:
the utility model provides a gas turbine flue gas waste heat utilization device, which is characterized by comprising: the lithium bromide absorption type cold and hot water unit and the plurality of fan wall air treatment units, a driving heat source of the lithium bromide absorption type cold and hot water unit is from a low-temperature economizer device group, and a generator of the lithium bromide absorption type cold and hot water unit is connected with the low-temperature economizer device group through a heating water supply pipe and a heating water return pipe; the fan wall air treatment units are respectively arranged at two sides of the air inlet device, and the fan wall air treatment units are connected with an evaporator of the lithium bromide absorption type cold and hot water unit through a chilled water supply pipe and a chilled water return pipe.
According to one embodiment of the utility model, a low-temperature economizer device group includes: the device comprises a low-temperature economizer, a low-pressure steam drum/deaerator, a recirculation pump and a condensate pipe, wherein an inlet of a generator of the lithium bromide absorption cold-hot water unit is connected with an outlet of the low-pressure steam drum/deaerator through a heating water supply pipe, an inlet of the low-pressure steam drum/deaerator is connected with an outlet of the low-temperature economizer, an inlet of the low-temperature economizer is connected with the condensate pipe, an inlet of the recirculation pump is connected with an outlet of the generator of the lithium bromide absorption cold-hot water unit through a heating water return pipe, and an outlet of the recirculation pump is connected with the condensate pipe.
According to one embodiment of the utility model, an electric three-way regulating valve is arranged on the heating water return pipe, one inlet of the electric three-way regulating valve is connected with an outlet of a generator of the lithium bromide absorption cold and hot water unit, the other inlet of the electric three-way regulating valve is connected with a heating water supply pipe, and the outlet of the electric three-way regulating valve is connected with a low-temperature economizer device group.
According to one embodiment of the utility model, a chilled water circulating water pump is arranged on the chilled water return pipe.
According to one embodiment of the utility model, the device further comprises a heating heater, wherein a primary water outlet of the heating heater is connected with an inlet of an absorber of the lithium bromide absorption cold and hot water unit through a warm water return pipe, and a primary water inlet of the heating heater is connected with an outlet of a condenser of the lithium bromide absorption cold and hot water unit through a warm water supply pipe.
According to one embodiment of the present utility model, a warm water circulating water pump is provided on the warm water supply pipe, and the warm water circulating water pump is provided upstream of the heating heater.
According to one embodiment of the utility model, the heating heater is arranged in parallel with the dew point heater of the gas turbine system.
According to one embodiment of the utility model, the inlet of the evaporator of the lithium bromide absorption cold and hot water unit is also connected with a cooling water supply pipe, and the outlet of the evaporator of the lithium bromide absorption cold and hot water unit is also connected with a cooling water return pipe.
According to one embodiment of the utility model, a chilled water supply pipe is connected with an inlet of a heating heater through a first pipeline, and a first electric butterfly valve and an electric two-way regulating valve are arranged on the first pipeline; the outlet of the chilled water return pipe and the outlet of the heating heater are connected through a second pipeline, and a second electric butterfly valve is arranged on the second pipeline.
According to one embodiment of the utility model, the warm water return pipe is connected with the cooling water supply pipe through a third pipeline, and a third electric butterfly valve is arranged on the third pipeline; the cooling water return pipe is connected with the warm water supply pipe through a fourth pipeline, and a fourth electric butterfly valve is arranged on the fourth pipeline.
According to one embodiment of the utility model, a fifth electric butterfly valve is arranged on the cooling water supply pipe, a sixth electric butterfly valve is arranged on the cooling water return pipe, a seventh electric butterfly valve is arranged on the warm water supply pipe, an eighth electric butterfly valve is arranged on the warm water return pipe, a ninth electric butterfly valve is arranged on the chilled water supply pipe, and a tenth electric butterfly valve is arranged on the chilled water return pipe.
The utility model has the positive progress effects that:
the gas turbine flue gas waste heat utilization device provided by the utility model further reasonably reduces the tail flue gas temperature, deeply utilizes the tail flue gas waste heat, and generates high-temperature hot water, and the high-temperature hot water can cool/heat the air inlet of the air compressor, heat natural gas, a heating system and the like through the arranged lithium bromide absorption type cold and hot water unit, the fan wall air treatment unit, the heating heater and the like, so that the gas turbine can economically, environmentally-friendly, safe and stably operate under all working conditions. The gas turbine flue gas waste heat utilization device is relatively independent, so that the normal operation of a gas turbine system is not influenced; the gas turbine system can also run throughout the year, and the utilization rate is high, so that the gas turbine system has wide application prospect.
Drawings
The above and other features, properties and advantages of the present utility model will become more apparent from the following description in conjunction with the accompanying drawings and embodiments, in which:
FIG. 1 is a schematic diagram of a gas turbine flue gas waste heat utilization device according to the present utility model.
[ reference numerals ]
Lithium bromide absorption type cold and hot water unit 100
Generator 110
Evaporator 120
Absorber 130
Condenser 140
Air intake device 210
Blower wall air handling unit 220
Low-temperature economizer device group 300
Low-temperature economizer 310
Low pressure drum/deaerator 320
Recirculation pump 1
Dew point heater 3
Heating heater 13
Chilled water circulating water pump 14
Warm water circulating water pump 15
Heating water supply pipe 31
Heating water return pipe 32
Cooling water supply pipe 33
Cooling water return pipe 34
Warm water supply pipe 35
Warm water return pipe 36
Chilled water supply pipe 37
Chilled water return pipe 38
Third pipeline 41
Fourth pipeline 42
First line 43
Second pipeline 44
Electric three-way regulating valve A
Electric two-way regulating valve B
Seventh electric butterfly valve C
Eighth electric butterfly valve D
Third electric butterfly valve E
Fourth electric butterfly valve F
Ninth electric butterfly valve G
Tenth electric butterfly valve H
Fifth electric butterfly valve I
Sixth electric butterfly valve J
First electric butterfly valve K
Second electric butterfly valve L
Detailed Description
In order to make the above objects, features and advantages of the present utility model more comprehensible, embodiments accompanied with figures are described in detail below.
Embodiments of the present utility model will now be described in detail with reference to the accompanying drawings. Reference will now be made in detail to the preferred embodiments of the present utility model, examples of which are illustrated in the accompanying drawings. Wherever possible, the same reference numbers will be used throughout the drawings to refer to the same or like parts.
Furthermore, although terms used in the present utility model are selected from publicly known and commonly used terms, some terms mentioned in the present specification may be selected by the applicant at his or her discretion, the detailed meanings of which are described in relevant parts of the description herein.
Furthermore, it is required that the present utility model is understood, not simply by the actual terms used but by the meaning of each term lying within.
As shown in fig. 1, the present utility model provides a gas turbine flue gas waste heat utilization device, the device comprising: a lithium bromide absorption chiller-heater unit 100 and a plurality of fan wall air treatment units 220,
the driving heat source of the lithium bromide absorption cold and hot water unit 100 is from the low-temperature economizer device group 300, and the generator 110 of the lithium bromide absorption cold and hot water unit 100 is connected with the low-temperature economizer device group 300 through the heating water supply pipe 31 and the heating water return pipe 32;
the fan wall air treatment units 220 cool/heat the intake air of the gas turbine, the plurality of fan wall air treatment units 220 are respectively arranged at two sides of the air intake device 210, and the fan wall air treatment units 220 are connected with the evaporator 120 of the lithium bromide absorption type cold and hot water unit 100 through the chilled water supply pipe 37 and the chilled water return pipe 38.
The low-temperature economizer device group 300 and the air inlet device 210 belong to a gas turbine system and are not in the design and supply range of the utility model. The air inlet system of the gas turbine adopts a mode that hot air generated by the fan wall air processing unit 220 is mixed with outdoor air in winter, so that the air inlet temperature of the gas compressor is not lower than the requirement, the gas turbine is prevented from freezing, the combustion chamber still keeps premixed combustion under partial load, the flame is stabilized in the combustion area by the rotary flow, the flame does not return to the premixing chamber, and the fuel and the air cannot be premixed in the premixing chamber or the premixing chamber cannot be burnt out (diffusion combustion) is avoided.
The fan wall air handling unit 220 has the characteristics of large air quantity, low wind resistance, low power consumption and low investment cost, and has short unit length, and the section size can be adjusted according to actual needs, so that the requirements of the device on arrangement can be met. It has the advantage over the arrangement of cooling/heating coils in the air intake 210 that it has no effect on the resistance of the gas turbine air intake system.
The heating source required by the fan wall air treatment unit 220 adopts warm water produced by the lithium bromide absorption cold and hot water unit 100 to supply water, and the heating water quantity is regulated by the electric two-way regulating valve B.
As shown in fig. 1, as a preferred embodiment of the present utility model, the low-temperature economizer device group 300 includes: the low-temperature economizer 310, the low-pressure steam drum/deaerator 320, the recirculation pump 1 and the condensate pipe 39, wherein the inlet of the generator 110 of the lithium bromide absorption cold-hot water unit 100 is connected with the outlet of the low-pressure steam drum/deaerator 320 through the heating water supply pipe 31, the inlet of the low-pressure steam drum/deaerator 320 is connected with the outlet of the low-temperature economizer 310, the inlet of the low-temperature economizer 310 is connected with the condensate pipe 39, the inlet of the recirculation pump 1 is connected with the outlet of the generator 110 of the lithium bromide absorption cold-hot water unit 100 through the heating water return pipe 32, and the outlet of the recirculation pump 1 is connected with the condensate pipe 39.
The lithium bromide absorption cold and hot water unit 100 adopts high-temperature hot water in a low-pressure steam drum/deaerator 320 as a driving heat source, and the heating water quantity is regulated by a heating water electrolysis three-way regulating valve (A).
The outlet temperature of the low-pressure steam drum/deaerator 320 is 154.5-156.5 ℃, so the lithium bromide absorption cold and hot water unit 100 of the embodiment preferably adopts double-effect refrigeration and single-effect heating, so that the warm water outlet temperature is higher under the working condition of a heat pump.
The effective capacity of the low-pressure steam drum/deaerator 320 is the water supply consumption of the waste heat boiler of 12.5min at the maximum continuous evaporation capacity and the rated heating water quantity of the lithium bromide absorption cold and hot water unit 100.
In order to avoid low-temperature corrosion of the cold-end furnace tube, the water inlet temperature of the low-temperature economizer 310 cannot be lower than a set value, a recirculation pump 1 (constant speed pump) is usually arranged on the system, and part of water outlet of the low-temperature economizer 310 is led to a water inlet of the low-temperature economizer 310 to be mixed with condensed water. The recirculation pump 1 of the present embodiment is preferably a variable frequency pump, and is a circulating water pump as a driving heat source of the lithium bromide absorption chiller-heater unit 100.
As shown in fig. 1, as a preferred embodiment of the present utility model, an electric three-way regulating valve a is provided on the heating water return pipe 32, one inlet of the electric three-way regulating valve a is connected with the outlet of the generator 110 of the lithium bromide absorption cold-hot water unit 100, the other inlet of the electric three-way regulating valve a is connected with the heating water supply pipe 31, and the outlet of the electric three-way regulating valve a is connected with the low-temperature economizer device 300.
As shown in fig. 1, as a preferred embodiment of the present utility model, a chilled water circulating water pump 14 is provided on a chilled water return pipe 38.
As shown in fig. 1, the apparatus further includes a heating heater 13, a primary water outlet of the heating heater 13 is connected to an inlet of an absorber 130 of the lithium bromide absorption cold-hot water unit 100 through a warm water return pipe 36, and a primary water inlet of the heating heater 13 is connected to an outlet of a condenser 140 of the lithium bromide absorption cold-hot water unit 100 through a warm water supply pipe 35, as a preferred embodiment of the present utility model.
As shown in fig. 1, as a preferred embodiment of the present utility model, a warm water circulating water pump 15 is provided to a warm water supply pipe 35, and the warm water circulating water pump 15 is provided upstream of the heating heater 13.
As shown in fig. 1, as a preferred embodiment of the present utility model, a heating heater (13) is provided in parallel with a dew point heater (3) of the gas turbine system.
The dew point heater 3 belongs to a gas turbine system. The heating source of the dew point heater 3 of the natural gas pressure regulating station adopts warm water supply generated by the lithium bromide absorption cold and hot water unit 100 to raise the air inlet temperature of the front module performance heater as much as possible and reduce the amount of medium-pressure heating hot water required by the performance heater.
As shown in fig. 1, as a preferred embodiment of the present utility model, a cooling water supply pipe 33 is further connected to an inlet of the evaporator 120 of the lithium bromide absorption chiller-heater unit 100, and a cooling water return pipe 34 is further connected to an outlet of the evaporator 120 of the lithium bromide absorption chiller-heater unit 100. The cooling water is supplied from the outside.
As shown in fig. 1, as a preferred embodiment of the present utility model, a chilled water supply pipe 37 is connected to an inlet of a heating heater 13 through a first pipe 43, and a first electric butterfly valve K and an electric two-way regulating valve B are provided on the first pipe 43; the chilled water return pipe 38 is connected to the outlet of the heating heater 13 via a second pipe 44, and the second pipe 44 is provided with a second electric butterfly valve L.
As shown in fig. 1, as a preferred embodiment of the present utility model, the warm water return pipe 36 is connected to the cooling water supply pipe 33 through a third pipe 41, and a third electric butterfly valve E is provided on the third pipe 41; the cooling water return pipe 34 is connected to the warm water supply pipe 35 through a fourth pipeline 42, and a fourth electric butterfly valve F is provided on the fourth pipeline 42.
As shown in fig. 1, in a preferred embodiment of the present utility model, a fifth electric butterfly valve I is provided to the cooling water supply pipe 33, a sixth electric butterfly valve J is provided to the cooling water return pipe 34, a seventh electric butterfly valve C is provided to the warm water supply pipe 35, an eighth electric butterfly valve D is provided to the warm water return pipe 36, a ninth electric butterfly valve G is provided to the chilled water supply pipe 37, and a tenth electric butterfly valve H is provided to the chilled water return pipe 38.
When the waste heat boiler operates, the operation mode of one embodiment of the gas turbine flue gas waste heat utilization device is as follows:
1. under the refrigeration condition:
the lithium bromide absorption type cold and hot water unit 100, the fan wall air treatment unit 220, the chilled water circulating water pump 14 and the electric three-way regulating valve A operate; the heating heater 13, the warm water circulating water pump 15 and the electric two-way regulating valve B do not operate;
the third electric butterfly valve E, the fourth electric butterfly valve F, the ninth electric butterfly valve G and the tenth electric butterfly valve H are opened; the seventh electric butterfly valve C, the eighth electric butterfly valve D, the fifth electric butterfly valve I, the sixth electric butterfly valve J, the first electric butterfly valve K, and the second electric butterfly valve L are closed.
The recirculation pump 1, the air intake 210, the low-temperature economizer 310, and the low-pressure drum/deaerator 320 are operated; the dew point heater 3 is not operated.
2. Under the working condition of the heat pump:
the lithium bromide absorption type cold and hot water unit 100, the heating heater 13, the warm water circulating water pump 15 and the electric three-way regulating valve A operate; the chilled water circulation water pump 14 does not operate;
the seventh electric butterfly valve C, the eighth electric butterfly valve D, the fifth electric butterfly valve I and the sixth electric butterfly valve J are opened; the third electric butterfly valve E, the fourth electric butterfly valve F, the ninth electric butterfly valve G, and the tenth electric butterfly valve H are closed.
When the temperature of the inlet air is lower than 5.5 ℃, the fan wall air treatment unit 220 and the electric two-way regulating valve B operate; the first and second electric butterfly valves K and L are opened. Otherwise, the fan wall air handling unit 220 and the electric two-way regulating valve B do not operate; the first and second electric butterfly valves K and L are closed.
The recirculation pump 1, the air intake 210, the dew point heater 3, the low-temperature economizer 310, and the low-pressure drum/deaerator 320 are operated.
3. At other run times:
the electric three-way regulating valve A operates; the lithium bromide absorption type cold and hot water unit 100, the fan wall air treatment unit 220, the heating heater 13, the chilled water circulating water pump 14, the warm water circulating water pump 15 and the electric two-way regulating valve B do not operate; the seventh electric butterfly valve C, the eighth electric butterfly valve D, the third electric butterfly valve E, the fourth electric butterfly valve F, the ninth electric butterfly valve G, the tenth electric butterfly valve H, the fifth electric butterfly valve I, the sixth electric butterfly valve J, the first electric butterfly valve K, and the second electric butterfly valve L are closed. The recirculation pump 1, the air intake 210, the low-temperature economizer 310, and the low-pressure drum/deaerator 320 are operated; the dew point heater 3 is not operated.
According to the flue gas waste heat utilization device of the gas turbine, surge of the gas compressor caused by too small opening of the IGV is avoided under the partial load working condition, and the temperature ratio of the gas turbine is improved under the full load working condition, so that the natural gas fuel input amount is reduced, the load rate and the combined cycle efficiency of the gas turbine are improved, and wet blocking phenomenon of an air inlet filtering system of the gas turbine is avoided under the condition that the total combined cycle output is unchanged.
The gas turbine flue gas waste heat utilization device further reasonably reduces the tail flue gas temperature, deeply utilizes the tail flue gas waste heat, and generates high-temperature hot water, and the high-temperature hot water can be used for cooling/heating the air inlet of the air compressor, heating the natural gas, a heating system and the like through the arranged lithium bromide absorption type cold and hot water unit 100, the fan wall air processing unit 220, the dew point heater 3, the heating heater 13 and the like, so that the gas turbine can economically, environmentally-friendly, safe and stable operate under all working conditions. The device is relatively independent, and the normal operation of the gas turbine system is not influenced; can also run with the gas turbine system all the year round, and has high utilization rate. Under the condition that the total output of the combined cycle is unchanged, the natural gas fuel input amount can be reduced, and the load rate and the combined cycle efficiency of the gas turbine are improved, so that the combined cycle energy-saving device has a wide application prospect.
While the utility model has been described in terms of preferred embodiments, it is not intended to be limiting, but rather to the utility model, as will occur to those skilled in the art, without departing from the spirit and scope of the utility model. Therefore, any modification, equivalent variation and modification of the above embodiments according to the technical substance of the present utility model fall within the protection scope defined by the claims of the present utility model.
Claims (11)
1. A gas turbine flue gas waste heat utilization device, the device comprising: a lithium bromide absorption cold and hot water unit (100) and a plurality of fan wall air treatment units (220),
the driving heat source of the lithium bromide absorption type cold and hot water unit (100) is from the low-temperature economizer device group (300), and the generator (110) of the lithium bromide absorption type cold and hot water unit (100) is connected with the low-temperature economizer device group (300) through a heating water supply pipe (31) and a heating water return pipe (32);
the fan wall air treatment units (220) are used for cooling/heating the inlet air of the gas turbine, the plurality of fan wall air treatment units (220) are respectively arranged on two sides of the air inlet device (210), and the fan wall air treatment units (220) are connected with the evaporator (120) of the lithium bromide absorption type cold and hot water unit (100) through a chilled water supply pipe (37) and a chilled water return pipe (38).
2. The gas turbine flue gas waste heat utilization device according to claim 1, wherein the low-temperature economizer device group (300) includes: the low-temperature economizer (310), the low-pressure steam drum/deaerator (320), the recirculation pump (1) and the condensate pipe (39), the inlet of the generator (110) of the lithium bromide absorption cold-hot water unit (100) is connected with the outlet of the low-pressure steam drum/deaerator (320) through the heating water supply pipe (31), the inlet of the low-pressure steam drum/deaerator (320) is connected with the outlet of the low-temperature economizer (310), the inlet of the low-temperature economizer (310) is connected with the condensate pipe (39), the inlet of the recirculation pump (1) is connected with the outlet of the generator (110) of the lithium bromide absorption cold-hot water unit (100) through the heating water return pipe (32), and the outlet of the recirculation pump (1) is connected with the condensate pipe (39).
3. The gas turbine flue gas waste heat utilization device according to claim 1, wherein an electric three-way regulating valve (a) is arranged on the heating water return pipe (32), one inlet of the electric three-way regulating valve (a) is connected with an outlet of a generator (110) of the lithium bromide absorption cold and hot water unit (100), the other inlet of the electric three-way regulating valve (a) is connected with the heating water supply pipe (31), and an outlet of the electric three-way regulating valve (a) is connected with the low-temperature economizer device group (300).
4. The flue gas waste heat utilization device of a gas turbine according to claim 1, wherein a chilled water circulating water pump (14) is provided on the chilled water return pipe (38).
5. The gas turbine flue gas waste heat utilization device according to claim 1, further comprising a heating heater (13), wherein a primary water outlet of the heating heater (13) is connected with an inlet of an absorber (130) of the lithium bromide absorption cold and hot water unit (100) through a warm water return pipe (36), and a primary water inlet of the heating heater (13) is connected with an outlet of a condenser (140) of the lithium bromide absorption cold and hot water unit (100) through a warm water supply pipe (35).
6. The flue gas waste heat utilization device of the gas turbine according to claim 5, wherein a warm water circulating water pump (15) is provided on the warm water supply pipe (35), and the warm water circulating water pump is provided upstream of the heating heater (13).
7. The gas turbine flue gas waste heat utilization device according to claim 5, wherein the heating heater (13) is arranged in parallel with the dew point heater (3) of the gas turbine system.
8. The flue gas waste heat utilization device of a gas turbine according to claim 5, wherein the inlet of the evaporator (120) of the lithium bromide absorption cold and hot water unit (100) is further connected with a cooling water supply pipe (33), and the outlet of the evaporator (120) of the lithium bromide absorption cold and hot water unit (100) is further connected with a cooling water return pipe (34).
9. The gas turbine flue gas waste heat utilization device according to claim 5, wherein a chilled water supply pipe (37) is connected with an inlet of the heating heater (13) through a first pipeline (43), and a first electric butterfly valve (K) and an electric two-way regulating valve (B) are arranged on the first pipeline (43); the outlet of the chilled water return pipe (38) and the outlet of the heating heater (13) are connected through a second pipeline (44), and a second electric butterfly valve (L) is arranged on the second pipeline (44).
10. The flue gas waste heat utilization device of the gas turbine according to claim 8, wherein the warm water return pipe (36) is connected with the cooling water supply pipe (33) through a third pipeline (41), and a third electric butterfly valve (E) is arranged on the third pipeline (41); the cooling water return pipe (34) is connected with the warm water supply pipe (35) through a fourth pipeline (42), and a fourth electric butterfly valve (F) is arranged on the fourth pipeline (42).
11. The flue gas waste heat utilization device for a gas turbine according to claim 8, wherein a fifth electric butterfly valve (I) is provided on a cooling water supply pipe (33), a sixth electric butterfly valve (J) is provided on a cooling water return pipe (34), a seventh electric butterfly valve (C) is provided on a warm water supply pipe (35), an eighth electric butterfly valve (D) is provided on a warm water return pipe (36), a ninth electric butterfly valve (G) is provided on a chilled water supply pipe (37), and a tenth electric butterfly valve (H) is provided on a chilled water return pipe (38).
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| Application Number | Priority Date | Filing Date | Title |
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| CN202322423279.1U CN220667686U (en) | 2023-09-06 | 2023-09-06 | Gas turbine flue gas waste heat utilization device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322423279.1U CN220667686U (en) | 2023-09-06 | 2023-09-06 | Gas turbine flue gas waste heat utilization device |
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| CN220667686U true CN220667686U (en) | 2024-03-26 |
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2023
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