CN111058911B - Thermal generator set cold end back pressure real-time control method based on environment wet bulb temperature - Google Patents
Thermal generator set cold end back pressure real-time control method based on environment wet bulb temperature 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
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Abstract
The invention relates to a wet-type circulating cooling thermal generator set cold end backpressure real-time control method based on environment wet bulb temperature. The control process is as follows: determining the temperature of a circulating water inlet of a condenser of a generator set; the power of the circulating pump and the flow of the circulating water of the host are determined: determining the back pressure of the condenser under different working conditions; determining the influence of the backpressure change of the condenser on unit load and the influence of the flow change of circulating water on power consumption; determining the circulating water flow corresponding to the optimal back pressure; sixthly, determining that the circulating water amount corresponds to the comprehensive frequency and frequency distribution of a circulating pump. According to the invention, the DCS control system is used for regulating and controlling the circulating water flow of the main machine in real time according to the heat load change of the condenser, the influence of back pressure on power and the power consumption of the circulating water flow, so that the generator set can maintain the optimal economic back pressure operation, and the economic benefit of the generator set production is improved.
Description
Technical Field
The invention belongs to the technical field of industrial production automation control, and relates to a thermal generator set cold end back pressure real-time control method based on environment wet bulb temperature.
Background
In thermal power generation or chemical enterprises, steam after work is done in a steam turbine needs to be discharged into a condenser to be condensed into water, and then the water is returned to a boiler for recycling. The heat of the condenser is taken away by the circulating water, so that the circulating water and cold air generate heat exchange in the cooling tower, and finally the heat is released into the atmosphere. Wherein the wet cooling tower circulating water directly contacts the air, the cooling tower outlet water temperature is dependent on the ambient wet bulb temperature, the wet bulb temperature represents the lowest temperature that the water can reach by evaporation at a certain time at a certain place. The temperature of the cooling tower effluent is different from the wet bulb temperature, and the size of the difference is related to the structural characteristics of the tower.
The pressure at the steam outlet of the low-pressure cylinder of the steam turbine is called the back pressure of the steam turbine. The change of the back pressure of the unit has important influence on the cycle heat efficiency of the steam turbine unit, so the back pressure of the unit is well controlled, the unit is ensured to run under the optimal back pressure, and the method has important significance on the economy of the unit. The operation backpressure of the condensing turbine in the power plant is influenced by parameters in various aspects, such as heat load of a condenser, operation condition of the condenser, circulating water flow, heat exchange effect of a cooling tower, environment wet bulb temperature, wind speed and the like. The determination of the optimal economic backpressure can be calculated and deduced through a theoretical formula, but the process is complex, and the operation of the optimal economic backpressure cannot be maintained in real time in practice. The backpressure regulation of the wet-type circulating cooling steam turbine unit is generally realized by changing the high and low rotating speeds of a power frequency circulating pump and increasing or decreasing the running number of the circulating pumps to control the circulating water flow, so that the purpose of controlling the backpressure of the unit is achieved, and the wet-type circulating cooling steam turbine unit is in a manual, rough and qualitative regulation mode.
Disclosure of Invention
The invention aims to provide a method for controlling the back pressure of the cold end of a thermal power generating unit in real time based on the temperature of an environmental wet bulb.
The technical scheme of the invention is as follows: a real-time control method for cold end backpressure of a thermal generator set based on environment wet bulb temperature utilizes a DCS control system to obtain an optimal backpressure value under the current working condition according to heat load changes of condensers under different working conditions, influences of backpressure on power and power consumption of circulating water flow of different main machines, and the set is kept to operate under economic backpressure through continuous automatic adjustment of the circulating water flow. The control process is as follows:
determining the temperature of a condenser circulating water inlet of a thermal generator set;
the power of the circulating pump and the flow of the circulating water of the host are determined:
determining the heat load of the condenser under different working conditions, and determining the back pressure of the condenser under different working conditions according to the circulating water flow of the host and the heat load of the condenser;
determining the influence of the backpressure change of the condenser on unit load and the influence of the flow change of circulating water on power consumption;
determining the circulating water flow corresponding to the optimal back pressure by the micro-increment of the condenser back pressure to the unit load and the power consumption micro-increment of the changed circulating water flow;
sixthly, determining the comprehensive frequency and frequency distribution of the circulating pump corresponding to the circulating water quantity.
The condenser circulating water inlet temperature of the generator set is related to the outlet temperature of the wet type circulating cooling tower, the outlet temperature of the wet type cooling tower is mainly influenced by the temperature of an environment wet bulb, and the calculation formula is as follows:
condenser inlet temperature tw1 +. DELTA.t 1 (1)
In the formula: tw1 is wet bulb temperature, deg.c; delta t1 is the difference between the temperature of the cooling tower effluent and the wet bulb temperature in deg.C.
The circulating water flow of the host machine passes through the actual measured flow of the typical frequency, and the actual frequency circulating water flow is obtained by calculating and correcting the flow value. The change of the frequency of the main engine circulating pump influences the main engine circulating water flow, and the main engine circulating water flow is calculated according to a flow proportion formula (2), wherein the calculation formula is as follows:
Q1/Q2＝n1/n2 (2)
in the formula: q1 is the real side operating mode flow, m 3 S); q2 is rated working condition flow m 3 S; n1 is the actual pump speed, rpm; n2 is rated pump speed, rpm。
The condenser back pressure Pn is the saturated steam pressure corresponding to the steam side temperature of the condenser; the calculation formula of the steam side temperature of the condenser is as follows:
tc＝tw1+△t1+△t2+td (3)
in the formula: tc is the condenser steam side temperature; DEG C; tw1 is wet bulb temperature, deg.c; delta t1 is the difference between the water outlet temperature of the cooling tower and the wet bulb temperature, DEG C; delta t2 is the temperature rise of circulating water of the condenser at DEG C; td is condenser end difference, DEG C.
Regarding the temperature rise delta t2 of the circulating water of the condenser, after the heat load and the circulating water quantity of the condenser are determined, a temperature rise formula of the circulating water of the condenser is obtained:
△t2＝q n /G×C (4)
in the formula: delta t2 is the temperature rise of circulating water of the condenser at DEG C; g is the flow rate of circulating water, kg/s; q. q.s n Is the heat load of a condenser, kJ/s; c is the specific heat of water 4.187, kJ/(kg. DEG C.).
The power consumption of the circulating pump corresponds to the comprehensive frequency, and the relation between the power consumption of the circulating pump of the host machine and the comprehensive frequency is as follows:
Pb＝a1f2–b1f+c1 (5)
in the formula: pb: circulating pump power consumption, kW; f: circulation pump frequency, Hz; a1, b1, c 1: a constant term.
The influence of the change of the backpressure of the condenser on the unit load is that the unit power shows a negative increasing trend when the backpressure increases, the influence rate of any backpressure on the unit load in the change range of the backpressure of the unit is obtained according to the backpressure load characteristic curve of the condenser unit, and the influence rate formula of the backpressure on the unit load is derived.
And when the delta Pm is the maximum, the optimal economic backpressure value of the unit is obtained, and the corresponding circulating water flow is the optimal economic circulating water flow.
The comprehensive frequency and frequency distribution mode of the circulating water quantity corresponding to the circulating pump are as follows: determining the comprehensive frequency of the circulating water pump and the distribution of the circulating water frequency according to the optimal circulating water flow; according to a three-dimensional corresponding relation diagram of environment wet bulb temperature, condenser heat load and comprehensive frequency of a main machine circulating water pump, a corresponding two-dimensional relation curve of unit condenser heat load and comprehensive frequency of the main machine circulating water pump is determined according to environment wet bulb temperature points, automatic real-time adjustment of circulation flow is achieved in a unit DCS, and optimal economic back pressure operation is maintained. In a certain temperature interval, the heat load of the condenser and the optimal comprehensive frequency of the main machine circulating water pump are in two-dimensional one-to-one correspondence, the water inlet temperature of the condenser circulating water and the heat load of the condenser of the unit can be determined according to the known environment wet bulb temperature, the optimal comprehensive frequency of the main machine circulating water pump can be obtained, and therefore the optimal comprehensive frequency in the whole working condition range can be generated. And the optimal comprehensive frequency command is distributed to each host circulating water pump, so that the distribution of the circulating pump frequency command is realized. Through the method, the circulating water pumps of the main machines are controlled to operate at the optimal frequency.
The method comprises the steps of determining the inlet water temperature of circulating water of a condenser and the heat load of the condenser according to the environment wet bulb temperature, determining the optimal economic backpressure of a unit, and adjusting the comprehensive frequency of a circulating water pump to change the flow rate of the circulating water so as to maintain the unit to operate at the optimal economic backpressure. And determining corresponding relation curves of heat loads of different condensers and comprehensive frequency of the main machine circulating water pump according to different environment wet bulb temperatures. The configuration of the thermal generator set host circulating pump is that 2-10 variable frequency circulating pumps run in parallel, or 2-10 power frequency circulating pumps run in parallel with 2-10 variable frequency circulating pumps.
According to the method for controlling the back pressure of the cold end of the thermal power generating unit in real time based on the environmental wet bulb temperature, accumulated test data are combined with theoretical derivation, the DCS control system is used for automatically regulating and controlling the flow rate of the circulating water of the main machine in real time according to the heat load change of condensers under different working conditions, the influence of the back pressure on the power, the power consumption of the flow rate of the circulating water of the main machine and the like, the optimal back pressure operation of the cold end of the wet type circulating cooling power generating unit is maintained in real time, and the economic benefit of the unit production is improved.
Drawings
FIG. 1 is a schematic flow chart of a method for controlling back pressure at a cold end of a thermal generator set in real time based on an ambient wet bulb temperature according to the present invention;
FIG. 2 is a graph showing the relationship between the frequency of the circulation pump and the power consumption of the pump;
fig. 3 is a diagram of the relationship between the condenser back pressure and the unit load.
Detailed Description
The present invention will be described in detail below with reference to the accompanying drawings and examples. The scope of protection of the invention is not limited to the embodiments, and any modification made by those skilled in the art within the scope defined by the claims also falls within the scope of protection of the invention.
The invention relates to a thermal generator set cold end backpressure real-time control method based on environment wet bulb temperature, which utilizes a DCS control system to obtain an optimal backpressure value under the current working condition according to condenser heat load changes under different working conditions, the influence of backpressure on power and the power consumption of circulating water flow of different main machines, and enables a unit to be kept to operate under economic backpressure through continuous and automatic adjustment of the circulating water flow. As shown in fig. 1, the control process is as follows:
determining the temperature of a condenser circulating water inlet of a thermal generator set;
the power of the circulating pump and the flow of the circulating water of the host are determined:
determining the heat load of the condenser under different working conditions, and determining the back pressure of the condenser under different working conditions according to the circulating water flow of the host and the heat load of the condenser;
determining the influence of the backpressure change of the condenser on the unit load and the influence of the flow change of circulating water on power consumption;
determining the circulating water flow corresponding to the optimal back pressure by the micro-increment of the condenser back pressure to the unit load and the power consumption micro-increment of the changed circulating water flow;
sixthly, determining the comprehensive frequency and frequency distribution of the circulating pump corresponding to the circulating water quantity.
The condenser circulating water inlet temperature of the generator set is related to the outlet temperature of the wet type circulating cooling tower, the outlet temperature of the wet type cooling tower is mainly influenced by the temperature of an environment wet bulb, and the calculation formula is as follows:
condenser inlet temperature tw1 +. DELTA.t 1 (1)
In the formula: tw1 is wet bulb temperature, deg.c; delta t1 is the difference between the temperature of the cooling tower effluent and the wet bulb temperature in deg.C.
The circulating water flow of the host machine passes through the actual measurement flow of the typical frequency, and the actual frequency circulating water flow is obtained by calculating and correcting the flow value; calculating the circulating water flow of the main machine according to a flow proportion formula (2), wherein the calculation formula is as follows:
Q1/Q2＝n1/n2 (2)
in the formula: q1 is the real side operating mode flow, m 3 S); q2 is rated working condition flow m 3 S; n1 is the actual pump speed, rpm; n2 is the rated operating pump speed, rpm.
The condenser back pressure Pn is a saturated steam pressure corresponding to the steam side temperature of the condenser. The calculation formula of the steam side temperature of the condenser is as follows:
tc＝tw1+△t1+△t2+td (3)
in the formula: tc is the steam side temperature of the condenser; DEG C; tw1 is wet bulb temperature, deg.c; delta t1 is the difference between the water outlet temperature of the cooling tower and the wet bulb temperature, DEG C; delta t2 is the temperature rise of circulating water of the condenser at DEG C; td is condenser end difference, DEG C. The condenser end difference Td is the difference between the steam side temperature of the condenser and the outlet water temperature of the circulating water, and is influenced by the vacuum tightness of the condenser and the cleanness of the heat exchange surface of the condenser.
Regarding the temperature rise delta t2 of the circulating water of the condenser, after the heat load and the circulating water quantity of the condenser are determined, a temperature rise formula of the circulating water of the condenser is obtained:
△t2＝q n /G×C (4)
in the formula: delta t2 is the temperature rise of circulating water of the condenser at DEG C; g is the flow rate of circulating water, kg/s; q. q.s n Is the heat load of a condenser, kJ/s; c is the specific heat of water 4.187, kJ/(kg. DEG C.).
In the formula: td is condenser end difference, DEG C; tc is the condenser steam side temperature, DEG C; tw2 is the temperature of the outlet side outlet water temperature.
Determining the heat load of the condenser under different working conditions: the heat load of the condenser is influenced by conditions such as low-pressure cylinder flow, back pressure, thermodynamic system change and the like, and a fitting formula is obtained after the heat load of the condenser is corrected according to a related performance test according to the corresponding heat load of the condenser under different working conditions of the low-pressure cylinder steam inlet flow calculation unit.
The method comprises the steps of obtaining a typical operating frequency and power consumption corresponding table through testing power consumption values corresponding to different frequency operations of a main engine circulating pump, drawing a frequency and power consumption curve, fitting a mathematical formula, and calculating power consumption corresponding to any frequency through the formula. As shown in table 1, a comparison table of the frequency and the power consumption of the host circulation pump is shown, and a curve of the correspondence relationship between the frequency and the power consumption is shown in fig. 2.
TABLE 1 comparison table of frequency and power consumption of host circulating pump
| Frequency of circulating pumps operating in parallel | Energy consumption of parallel operation circulating pumps |
| Hz | kw |
| 20 | A1 |
| 25 | A2 |
| 30 | A3 |
| 35 | A4 |
| 40 | A5 |
| 45 | |
| 50 | A7 |
The relation between the power consumption of the circulating pump of the main machine and the comprehensive frequency is
Pb＝a1f 2 –b1f+c1 (5)
In the formula: pb: circulating pump power consumption, kW; f: circulation pump frequency, Hz;
a1, b1 and c1 are constant terms, three parallel variable-frequency circulating pumps with power of 1250kW are taken as examples: a1 ═ 0.6; b1 ═ 46.7; c1 ═ 1255.5;
the influence of the backpressure change of the condenser on the unit load is that the unit power shows a negative increasing trend when the backpressure increases. And obtaining the influence rate of any back pressure in the change range of the back pressure of the unit on the load of the unit according to the back pressure load characteristic curve of the condenser unit. Fig. 3 is a graph showing the relationship between the condenser back pressure and the unit load.
And when the delta Pm is the maximum, the optimal economic backpressure value of the unit is obtained, and the corresponding circulating water flow is the optimal economic circulating water flow. Wherein: delta Pj is the increase of the electric power of the unit, kW; delta Pb is the increment of the power consumption of the main engine circulating pump, kW; and the delta Pm is the optimal economic backpressure value, kW. The method determines the circulating water flow corresponding to the optimal economic back pressure of the typical working condition point in the circulating water temperature and load change range of the condenser of the unit.
The comprehensive frequency and frequency distribution mode of the circulating water quantity corresponding to the circulating pump are as follows: determining the comprehensive frequency of the circulating water pump and the distribution of the circulating water frequency according to the optimal circulating water flow; according to a three-dimensional corresponding relation diagram of environment wet bulb temperature, condenser heat load and comprehensive frequency of a main machine circulating water pump, a corresponding two-dimensional relation curve of unit condenser heat load and comprehensive frequency of the main machine circulating water pump is determined according to environment wet bulb temperature points, automatic real-time adjustment of circulation flow is achieved in a unit DCS, and optimal economic back pressure operation is maintained.
The method comprises the steps of determining the inlet water temperature of circulating water of a condenser and the heat load of the condenser according to the environmental wet bulb temperature, determining the optimal economic backpressure of a unit, and adjusting the comprehensive frequency of a circulating water pump to change the flow rate of the circulating water so as to keep the unit in the optimal economic backpressure operation. And determining corresponding relation curves of heat loads of different condensers and comprehensive frequency of the main machine circulating water pump according to different environment wet bulb temperatures. The wet-type circulating cooling thermal generator set is characterized in that a main circulating pump of the thermal generator set is configured to be 8 variable-frequency circulating pumps which are connected in parallel for operation, or 4 power-frequency circulating pumps and 5 variable-frequency circulating pumps which are connected in parallel for operation.
In a certain temperature interval, the heat load of the condenser and the optimal comprehensive frequency of the main machine circulating water pump are in two-dimensional one-to-one correspondence, and the optimal comprehensive frequency of the main machine circulating water pump is obtained by determining the inlet water temperature of the condenser circulating water and the heat load of the condenser of the unit according to the known environment wet bulb temperature. Thereby generating an optimal integrated frequency over the full operating range. And distributing the optimal comprehensive frequency command to each host circulating water pump to realize distribution of the circulating pump frequency command.
Claims (8)
1. A thermal generator set cold end back pressure real-time control method based on environment wet bulb temperature is characterized by comprising the following steps: by utilizing a DCS control system, obtaining an optimal backpressure value under the current working condition according to the heat load change of the condenser under different working conditions, the influence of backpressure on power and the power consumption of circulating water flow of different hosts, and enabling the unit to operate under economic backpressure by continuously and automatically adjusting the circulating water flow; the control process is as follows:
determining the temperature of a condenser circulating water inlet of a thermal generator set;
the power of the circulating pump and the flow of the circulating water of the host are determined:
determining the heat load of the condenser under different working conditions, and determining the back pressure of the condenser under different working conditions according to the circulating water flow of the host and the heat load of the condenser;
determining the influence of the backpressure change of the condenser on unit load and the influence of the flow change of circulating water on power consumption;
determining the circulating water flow corresponding to the optimal back pressure by the micro-increment of the condenser back pressure to the unit load and the power consumption micro-increment of the changed circulating water flow;
sixthly, determining comprehensive frequency and frequency distribution of the circulating pump corresponding to the circulating water amount;
the circulating water quantity corresponds to the comprehensive frequency of the circulating pump and the frequency distribution mode is as follows: determining the comprehensive frequency of the circulating water pump and the distribution of the circulating water frequency according to the optimal circulating water flow; determining a corresponding two-dimensional relation curve of ' unit condenser heat load-main unit circulating water pump comprehensive frequency ' according to an environment wet bulb temperature point by using a three-dimensional corresponding relation graph of environment wet bulb temperature-condenser heat load-main unit circulating water pump comprehensive frequency ', realizing automatic real-time adjustment of circulation flow in a unit DCS, and maintaining optimal back pressure operation; the power consumption of the circulating pump corresponds to the comprehensive frequency, and the relation between the power consumption of the circulating pump of the host and the comprehensive frequency is as follows:
Pb＝a1f 2 –b1f+c1
in the formula: pb: circulating pump power consumption, kW; f: circulation pump frequency, Hz; a1, b1, c 1: a constant term.
2. The method for real-time control of cold end back pressure of a thermal generator set based on ambient wet bulb temperature as claimed in claim 1, wherein: condenser circulating water inlet temperature of the generator set is related to outlet temperature of the wet type circulating cooling tower, outlet water temperature of the wet type cooling tower is mainly influenced by environment wet bulb temperature, and a calculation formula is as follows:
condenser inlet temperature tw1 +. DELTA.t 1 (1)
In the formula: tw1 is wet bulb temperature, deg.c; delta t1 is the difference between the temperature of the cooling tower effluent and the wet bulb temperature in deg.C.
3. The method for real-time control of cold end back pressure of a thermal generator set based on ambient wet bulb temperature as claimed in claim 1, wherein: the circulating water flow of the host machine passes through the actual measurement flow of the typical frequency, and the actual frequency circulating water flow is obtained by calculating and correcting the flow value; calculating the circulating water flow of the main machine according to a flow proportion formula (2), wherein the calculation formula is as follows:
Q1/Q2＝n1/n2 (2)
in the formula: q1 is the real side operating mode flow, m 3 S; q2 is rated working condition flow m 3 S; n1 is the actual pump speed, rpm; n2 is the rated operating pump speed, rpm.
4. The method for real-time control of cold end back pressure of a thermal generator set based on ambient wet bulb temperature as claimed in claim 1, wherein: the condenser back pressure Pn is a saturated steam pressure corresponding to the steam side temperature of the condenser; the calculation formula of the steam side temperature of the condenser is as follows:
tc＝tw1+△t1+△t2+td (3)
in the formula: tc is the steam side temperature of the condenser; DEG C; tw1 is wet bulb temperature, deg.c; delta t1 is the difference between the water outlet temperature of the cooling tower and the wet bulb temperature, DEG C; delta t2 is the temperature rise of circulating water of the condenser at DEG C; td is condenser end difference, DEG C;
regarding the temperature rise delta t2 of the circulating water of the condenser, after the heat load and the circulating water quantity of the condenser are determined, a temperature rise formula of the circulating water of the condenser is obtained:
Δt2＝q n /G×C (4)
in the formula: delta t2 is the temperature rise of circulating water of the condenser at DEG C; g is the flow rate of circulating water, kg/s; q. q.s n Is the heat load of a condenser, kJ/s; c is the specific heat of water 4.187, kJ/(kg. DEG C.).
5. The method for real-time control of cold end back pressure of a thermal generator set based on ambient wet bulb temperature as claimed in claim 1, wherein: the influence of the change of the backpressure of the condenser on the unit load is that the unit power shows a negative increasing trend when the backpressure increases, and the influence rate of any backpressure on the unit load in the backpressure change range of the unit is obtained according to the backpressure load characteristic curve of the condenser unit.
6. The method for real-time control of cold end back pressure of a thermal generator set based on ambient wet bulb temperature as claimed in claim 1, wherein: and regarding to the determination of the circulating water flow corresponding to the optimal back pressure, obtaining the increment delta Pj of the unit electric power after the back pressure change and the increment delta Pb of the main unit circulating pump power consumption corresponding to the back pressure change through the back pressure change corresponding to different circulating water flows and the load change rate corresponding to the back pressure, and when the delta Pm is the maximum, the delta Pj-delta Pb is the optimal back pressure value of the unit, and the corresponding circulating water flow is the most economical circulating water flow.
7. The method for real-time control of cold end back pressure of a thermal generator set based on ambient wet bulb temperature as claimed in claim 1, wherein: the method comprises the steps of determining the inlet water temperature of circulating water of a condenser and the heat load of the condenser according to the environmental wet bulb temperature, determining the optimal back pressure of a unit, and adjusting the comprehensive frequency of a circulating water pump to change the flow rate of the circulating water so as to maintain the unit to operate at the optimal back pressure.
8. The method for real-time control of cold end back pressure of a thermal generator set based on ambient wet bulb temperature as claimed in claim 1, wherein: determining corresponding relation curves of heat loads of different condensers and comprehensive frequency of a circulating water pump of a host according to different environmental wet bulb temperatures; the thermal generator set host circulating pump is configured with 2-10 frequency conversion circulating pumps which are operated in parallel, or 2-10 power frequency circulating pumps and 2-10 frequency conversion circulating pumps which are operated in parallel.
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| CN111981862A (en) * | 2020-09-04 | 2020-11-24 | 内蒙古电力(集团)有限责任公司内蒙古电力科学研究院分公司 | Circulating water flow control method and device of surface type indirect cooling system |
| CN113239538B (en) * | 2021-05-11 | 2024-05-07 | 浙江浙能技术研究院有限公司 | Wet cooling unit condenser economic back pressure calculation method based on condenser end difference and genetic algorithm |
| CN113221272B (en) * | 2021-05-11 | 2024-03-29 | 哈电发电设备国家工程研究中心有限公司 | Wet cooling unit condenser economic back pressure calculation method based on condenser end difference and traversal method |
| CN113221274B (en) * | 2021-05-11 | 2023-09-22 | 哈尔滨沃华智能电力技术有限公司 | Wet cooling unit condenser economic back pressure calculation method based on logarithmic average temperature difference and genetic algorithm |
| CN113864013B (en) * | 2021-10-09 | 2023-07-14 | 中国大唐集团科学技术研究院有限公司西北电力试验研究院 | Cold end optimization method for all-condition of wet-cooling thermal power unit |
| CN114017150B (en) * | 2021-11-05 | 2023-03-17 | 西安热工研究院有限公司 | Multi-circulating-pump coordinated dispatching control system and method for gas-steam combined cycle unit |
| CN114320505B (en) * | 2021-12-31 | 2022-12-02 | 华中科技大学 | Ammonia-doped power plant indirect air cooling system and control method thereof |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102031999A (en) * | 2010-11-23 | 2011-04-27 | 江苏丰泰冷却塔有限公司 | Thermal power generator set with high-efficient circulating system |
| US8820078B1 (en) * | 2013-08-06 | 2014-09-02 | Thomas Edward Duffy | Heat recovery steam generator and method for fast starting combined cycles |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104153981B (en) * | 2014-02-19 | 2017-02-15 | 东南大学 | Method for estimating backpressure data during starting and stopping of power station circulating water pump |
| CN205481304U (en) * | 2016-03-23 | 2016-08-17 | 中机国能电力工程有限公司 | Heat supply energy adjusting device |
-
2019
- 2019-11-27 CN CN201911182401.2A patent/CN111058911B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102031999A (en) * | 2010-11-23 | 2011-04-27 | 江苏丰泰冷却塔有限公司 | Thermal power generator set with high-efficient circulating system |
| US8820078B1 (en) * | 2013-08-06 | 2014-09-02 | Thomas Edward Duffy | Heat recovery steam generator and method for fast starting combined cycles |
Non-Patent Citations (2)
| Title |
|---|
| 变频调速循环水泵的应用及运行优化研究;程东涛等;《电站系统工程》;20141130;第30卷(第6期);第137-140页 * |
| 火电厂凝汽式汽轮机冷端运行优化研究;马立恒等;《汽轮机技术》;20100430;第52卷(第2期);第69-70，72页 * |
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Effective date of registration: 20240826 Address after: 10 Guangning Road, Shijingshan District, Beijing Patentee after: Beijing Jingneng Electric Power Co.,Ltd. Country or region after: China Patentee after: HEBEI ZHUOZHOU JINGYUAN THERMAL ELECTRICITY Co.,Ltd. Address before: 072750 No. 45 Jingnan Street, Changdian Village, Dongxianpo Town, Zhuozhou City, Baoding City, Hebei Province Patentee before: HEBEI ZHUOZHOU JINGYUAN THERMAL ELECTRICITY Co.,Ltd. Country or region before: China |