CN113137650B - Steam heat network system regulation and control method combined with distributed power generation - Google Patents

Steam heat network system regulation and control method combined with distributed power generation Download PDF

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CN113137650B
CN113137650B CN202110409686.XA CN202110409686A CN113137650B CN 113137650 B CN113137650 B CN 113137650B CN 202110409686 A CN202110409686 A CN 202110409686A CN 113137650 B CN113137650 B CN 113137650B
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steam
flow
power generation
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heat load
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CN113137650A (en
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钟崴
张淑婷
林小杰
田兴涛
章楠
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Zhejiang University ZJU
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D1/00—Steam central heating systems
    • F24D1/02—Steam central heating systems operating with live steam
    • 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
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D1/00—Steam central heating systems
    • F24D1/08—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J3/00—Circuit arrangements for ac mains or ac distribution networks
    • H02J3/38—Arrangements for parallely feeding a single network by two or more generators, converters or transformers
    • H02J3/381—Dispersed generators
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J2300/00—Systems for supplying or distributing electric power characterised by decentralized, dispersed, or local generation
    • H02J2300/20—The dispersed energy generation being of renewable origin

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
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Abstract

The invention provides a steam heat network system regulating and controlling method combined with distributed power generation, which comprises a thermal power plant, a steam pipe network system, a distributed power generation system, a micro-grid, a valve system and a coordination control system, wherein after steam produced by the thermal power plant is conveyed to an industrial park through the steam pipe network, one part of the steam is used for supplying real-time steam load-passive load to a thermal user, and the other part of the steam enters a steam turbine of the distributed power generation system to drive a generator to generate power to form active load controllable in system level; when the steam demand of a user is lower than the expected load, the opening of a steam pipeline valve entering a steam turbine of the distributed power generation system is increased, a part of steam is utilized in a power generation mode, and the steam flow in a steam heat supply network is regulated. The steam heat network system combined with distributed power generation and the regulation and control method provided by the invention can effectively solve the problems of steam condensation and water accumulation in a pipe network caused by too low steam pipeline load in the long-distance steam transportation process, and improve the supply and demand cooperativity.

Description

Steam heat network system regulation and control method combined with distributed power generation
Technical Field
The invention belongs to the field of energy Internet, and particularly relates to a steam heat network system combined with distributed power generation and a regulation and control method.
Background
In industrial parks such as chemical industry, medicine, etc., steam is an indispensable energy source in the production process. Continuous steam users and intermittent steam users are arranged in the park, the heat load of the users is different at night and day, and the steam parameters are strictly required. In order to meet the steam requirements of users at different time and with different qualities, the steam supply pressure and temperature can be changed along with the change of the steam supply pressure and temperature, and the condition that partial pipelines stop supplying at night can be realized. The pipeline that stops supplying needs to accomplish the process of heating pipe, drainage, step up in advance in the next day in order to guarantee normal heat supply daytime, and the heating pipe is long-lived and there is the corruption to the pipeline. Meanwhile, the randomness of the change of the steam consumption of the user is strong, so that the supplied steam parameters can fluctuate greatly along with the change of the heat consumption demand of the user, the continuous change of the output of the unit reduces the operation efficiency, the environmental protection performance of the operation is also reduced, the steam condensation is easily caused, and the potential safety hazard of the operation exists. Meanwhile, the steam pipe network transported in a long distance has larger inertia, so that the requirements of users cannot respond in time, and larger hysteresis often exists.
Disclosure of Invention
The invention aims to provide a steam heat network system combined with distributed power generation and a regulation and control method aiming at the defects of the prior art.
The technical scheme adopted by the invention is as follows: a steam heat network system combined with distributed power generation and a regulation and control method are characterized by comprising a thermal power plant, a steam pipe network system, a distributed power generation system, a micro-grid, a valve system and a coordination control system; the steam pipe network system comprises a main steam pipeline and a branch steam pipeline; the distributed power generation system comprises a steam turbine and a generator; the valve system comprises a main valve and other valves, wherein the main valve is a front control valve of a steam turbine of the distributed power generation system, and the other valves are control valves and safety valves of other steam pipelines;
steam generated by the thermal power plant is conveyed to the industrial park through a main steam pipeline; according to the steam utilization characteristics of heat users in an industrial park and the requirements of a thermal power plant, distributed power generation systems are configured at different positions: when the requirement of reducing the flow fluctuation of the main steam pipeline is met, the distributed power generation system is configured at the inlet from the main steam pipeline to the industrial park; when the requirements that the flow of a main steam pipeline is stable and the requirement change of a terminal important user is quickly responded are met, the distributed power generation system is configured in front of the terminal important user; in the same industrial park, the distributed power generation systems can be configured at different positions and can be simultaneously configured in a plurality of places;
after the steam enters the industrial park, one part of the steam is used for meeting the real-time steam load of a heat user, and the other part of the steam enters a steam turbine in the distributed power generation system to do work, so that a generator is driven to generate power and enter a microgrid;
in the technical scheme of the invention, the real-time steam demand of a hot user is only influenced by the production of the hot user and is defined as a passive load; the steam utilized by the distributed power generation system is defined as the active load.
Further, the exhaust steam of the steam turbine of the distributed power generation system can be used for hot water supply or condensation recovery of the industrial park; electricity produced by a generator of the distributed power generation system can enter a micro-grid to be connected to the grid, meet the electrical demand of a park, produce compressed air and electrolyze water to produce hydrogen or electrolyze aluminum;
furthermore, the main valve and other valves in the valve system receive the regulation and control instruction of the cooperative regulation and control system, so that the steam flow in the pipeline and the generated energy of the distributed power generation system are controlled;
the cooperative regulation and control system forms a valve regulation scheme set and a distributed power generation system output scheme according to data of real-time total steam heat load and predicted total steam heat load at the next moment, which are collected by the data center; and finally, transmitting the regulating and controlling instruction to a valve for opening regulation, and transmitting the regulating and controlling instruction to a distributed power generation system for output regulation.
Further, the thermal power plant of the present invention can also supply steam to a plurality of industrial parks at the same time.
Furthermore, steam temperature, pressure and flow measuring devices are arranged at the inlet and outlet of the main steam pipeline, the pipeline bifurcation and the user side front pipeline, and the obtained real-time data are transmitted to a data center in the coordinated control system.
The coordination control system forms a distributed power generation system output scheme according to the following steps:
step S1, establishing a steam load prediction model of each heat user in the industrial park by combining real-time total steam heat load, and obtaining the predicted total steam heat load at the next moment;
step S11, obtaining real-time steam temperature, pressure and flow data of a user by using a steam measuring device in front of the user side, transmitting the data to a data center, and calculating real-time total steam heat load
Qdj(t)＝f(Tdj(t),pdj(t),qdj(t))
Figure GDA0003586946410000031
Wherein Q isdj(t) is the real-time steam heat load, MW, of user j; t isdj(t) is the real-time steam temperature, DEG C, of the user at home; p is a radical ofdj(t) is the real-time steam pressure of the user at j households, Mpa; q. q.sdj(t) is the real-time steam flow of the user before j households in kg/s; qd(t) total steam heat load in real time, MW.
Step S12, obtaining the user steam heat load and the total steam heat load at the next moment by utilizing a machine learning algorithm and combining the real-time user steam heat load according to the regional weather real-time data, the heat supply area and the user steam heat load delay time parameter
Qcj(t+1)＝f(Qd(t),D(t),A,μ)
Figure GDA0003586946410000032
Wherein Q iscj(t +1) is the predicted steam heat load, MW, for user j at the next time; d (t) is regional weather real-time data, including air temperature, wind speed, wind direction, humidity and the like; a is heat supply area and square meter; mu is a user steam heat load delay time parameter; qc(t +1) predicted total steam heat load, MW, at the next instant; k is the total number of users.
Step S2, establishing a main steam pipeline expected flow curve according to the real-time total steam heat load obtained in the step S1 and the predicted total steam heat load at the next moment;
according to the historical operation data of the month of the operation day, calculating to obtain the average maximum total steam load per day
Figure GDA0003586946410000033
The flow rate of the corresponding main steam pipeline is
Figure GDA0003586946410000034
Figure GDA0003586946410000035
If the flow corresponding to the real-time total steam heat load of the user is higher than the flow corresponding to the daily average maximum total steam load and the predicted flow corresponding to the total steam heat load at the next moment is higher than the flow corresponding to the real-time total steam heat load of the user, the expected flow of the main steam pipeline at the next moment is the predicted steam flow corresponding to the total steam heat load at the next moment, and the flow is maintained until the flow corresponding to the total steam heat load at the current moment is lower than the safe flow, namely
When in use
Figure GDA0003586946410000041
And q isc(t+1)＞qdAt the time of (t), the reaction mixture,
Figure GDA0003586946410000042
wherein the content of the first and second substances,
Figure GDA0003586946410000043
the expected flow rate of the main steam pipeline at the next moment is kg/s; q. q.sc(t +1) is the predicted main steam pipeline flow at the next moment in kg/s; q. q ofsIs the minimum safe flow of the main steam pipeline, kg/s.
qc(t+1)＝f(Qc(t+1))
If the flow corresponding to the real-time total steam heat load of the user is higher than the flow corresponding to the average maximum total steam load per day and the predicted flow corresponding to the total steam heat load at the next moment is lower than the flow corresponding to the real-time total steam heat load of the user, the expected flow of the main steam pipeline at the next moment is the expected flow of the main steam pipeline at the current moment, namely the expected flow of the main steam pipeline at the current moment is
When in use
Figure GDA0003586946410000044
And q isc(t+1)≤qdAt the time of (t), the reaction mixture,
qw(t+1)＝qw(t)
if the real-time total steam heat load corresponding flow of the user is lower than the flow corresponding to the daily average maximum total steam load, the expected flow of the main steam pipeline at the next moment is the flow corresponding to the daily average maximum total steam load, and the flow is maintained until the current moment corresponding flow of the total steam heat load is lower than the safe flow, namely
When in use
Figure GDA0003586946410000045
When the temperature of the water is higher than the set temperature,
Figure GDA0003586946410000046
the expected flow of the main steam pipeline is divided into three grades: safe flow, flow corresponding to the average maximum total steam load per day and the maximum flow on the day. The change rate of the ascending and descending flow among each grade of flow is less than a safety threshold value
Figure GDA0003586946410000051
Wherein, delta t is the time required for changing from different gear flows, s; q. q.ssvFor lifting load safety threshold, kg/s2。
Dividing the time required by the lifting flow into two flow intervals equally, wherein the lifting flow rate is qsv(ii) a The total desired steam heat load corresponding to the desired flow rate of the main steam line is
Qw(t+1)＝f(qw(t+1))
Step S3, establishing a valve control model and a distributed power generation system power generation model, and generating a valve regulation scheme and a distributed power generation system output scheme at the next moment;
step S31, establishing a valve system; the main valve in front of the steam turbine of the distributed power generation system is determined by the difference between the total expected steam heat load of the main steam pipeline and the predicted total steam heat load at the next moment
V(t)＝f(|Qw(t+1)-Qc(t+1)|)
Wherein v (t) is the opening degree of the main valve in front of the distributed power generation system.
Step S32, establishing a balance model of the main steam pipeline
Qn(t+1)(1-ηn)＝Qw(t+1)
Wherein Q isn(t +1) is the heat supply, MW; etanIs the vapor transport loss factor.
The active load amount entering the distributed power generation system for power generation at the next moment is
Qe(t+1)＝Qw(t+1)-Qc(t+1)
Wherein Qe(t +1) is the next moment active load, MW; qc(t +1) is the next passive load, MW.
The expected generated energy of the distributed power generation system at the next moment is
Wp(t+1)＝ηeQe(t+1)
Wherein, Wp(t +1) is the electric quantity, MW, produced in the park; etaeTo obtain the power generation efficiency.
The invention has the beneficial effects that:
the invention has established a steam heat network system and regulation and control method that combines distributed power generation, through setting up the systematic type initiative load of distributed power generation, after the steam that the power plant produces is conveyed to the industrial park through the steam pipe network, a part is used for supplying real-time steam load-passive load of the heat consumer, another part enters the steam turbine of the distributed power generation system to drive the generator to generate electricity, become the controllable initiative load of system level; according to the invention, the heat load fluctuation of the main steam pipeline is transferred to the power generation output fluctuation of the distributed power generation system, the heat load fluctuation with larger inertia is transferred to the electric load fluctuation with higher flexibility, the stability of the steam flow of the main steam pipe network and the steam pressure of a user side can be increased, and the flexibility of the heat supply system is increased. In addition, the method can solve the problems of steam condensation and water accumulation in a pipe network caused by too low load of a steam pipeline in the long-distance steam transportation process; the passive response of the source side to the load is reduced, the initiative is improved, the fluctuation of steam parameters and supply quantity in the steam main pipe is reduced, the steam supply is more stable, and the supply and demand cooperativity is improved.
Drawings
FIG. 1 is a diagram of a steam heat grid system incorporating distributed power generation of the present invention;
FIG. 2 illustrates a method of operation of the coordinated control system of the present invention;
FIG. 3 is a method of generating a valving scheme and distributed power generation system output scheme of the present invention;
FIG. 4 is a graph comparing predicted flow and desired flow for a main steam line;
FIG. 5 is a graph comparing predicted outlet steam pressure and expected outlet steam pressure for a main steam line;
detailed description of the preferred embodiment
In order that the present disclosure may be more readily and clearly understood, reference is now made to the following description taken in conjunction with the accompanying drawings.
In fig. 1, a steam heat network system and a regulation and control method for combining distributed power generation comprise a thermal power plant 1, a steam pipe network system 2, a distributed power generation system 3, a microgrid 4, a valve system 5 and a coordination control system 6; the steam pipe network system 2 comprises a main steam pipeline 21 and a branch steam pipeline 22; the distributed power generation system 3 includes a turbine 31 and a generator 32; the valve system 5 comprises a main valve and other valves, wherein the main valve is a front control valve 51 of the steam turbine 31 of the distributed power generation system, and the other valves are control valves and safety valves of other steam pipelines;
the steam generated by the thermal power plant 1 is conveyed to the industrial park through the main steam conduit 21; according to the steam utilization characteristics of heat users in the industrial park and the requirements of the thermal power plant 1, the distributed power generation system 3 is configured at different positions: the distributed power generation system 3 is configured at the inlet of the main steam pipeline 21 to the industrial park only when the requirement of the thermal power plant for reducing the flow fluctuation of the main steam pipeline 21 is met; when the requirements that the flow of the main steam pipeline 21 is stable and the requirement change of the terminal important user is quickly responded are met, the distributed power generation system 3 is configured in front of the terminal important user; in the same industrial park, the distributed power generation system 3 can be configured at different positions and can be configured in a plurality of positions simultaneously;
after the steam enters the industrial park, one part of the steam is used for meeting the real-time steam load of a heat user, and the other part of the steam enters a steam turbine 31 in the distributed power generation system 3 to do work, so that a generator 32 is driven to generate power and enter the microgrid 4;
preferably, the exhaust steam of the steam turbine 31 of the distributed power generation system 3 can be used for hot water supply or condensation recovery of the industrial park; electricity produced by the generator 32 of the distributed power generation system 3 can enter the microgrid 4 to be connected to the power grid, meet the electrical demand of the park, produce compressed air, electrolyze water to produce hydrogen or electrolyze aluminum and the like;
preferably, the main valve and other valves in the valve system 5 receive the regulation and control instruction of the coordination control system 6, so as to control the steam flow in the pipeline and the generated energy of the distributed power generation system;
in fig. 2, the coordination control system 6 forms a valve regulation scheme set and a distributed power generation system output scheme according to data of real-time total steam heat load and predicted total steam heat load at the next moment collected by the data center; and finally, transmitting the regulating and controlling instruction to a valve for opening regulation, and transmitting the regulating and controlling instruction to a distributed power generation system for output regulation.
Preferably, the large scale thermal power plant 1 can supply steam to a plurality of industrial parks simultaneously.
Preferably, steam temperature, pressure and flow measuring devices are arranged at the inlet and outlet of the main steam pipeline, the pipeline branch port and the user side front pipeline, and the obtained real-time data are transmitted to a data center in the coordinated control system 6.
In fig. 3, the coordinated control system 6 forms a distributed power generation system output scheme according to the following steps:
step S1, establishing a steam load prediction model of each heat user in the industrial park by combining real-time total steam heat load, and obtaining the predicted total steam heat load at the next moment;
step S11, obtaining real-time steam temperature, pressure and flow data of a user by using a steam measuring device in front of the user side, transmitting the data to a data center, and calculating real-time total steam heat load
Qdj(t)＝f(Tdj(t),pdj(t),qdj(t))
Figure GDA0003586946410000081
Wherein Q isdj(t) is the real-time steam heat load, MW, of user j; t isdj(t) is the real-time steam temperature, DEG C, of the user at home; p is a radical of formuladj(t) is the real-time steam pressure of the user j before the family, Mpa; q. q.sdj(t) is the real-time steam flow of the user before j households in kg/s; qd(t) total steam heat load in real time, MW.
Step S12, obtaining the user steam heat load and the total steam heat load at the next moment by using a machine learning algorithm according to the regional weather real-time data, the heat supply area, the user steam heat load delay time parameter and the real-time user steam heat load quantity
Qcj(t+1)＝f(Qd(t),D(t),A,μ)
Figure GDA0003586946410000082
Wherein Q iscj(t +1) is the predicted steam heat load, MW, for user j at the next time; d (t) is regional weather real-time data, including air temperature, wind speed, wind direction, humidity and the like; a is heat supply area and square meter; mu is a user steam heat load delay time parameter; qc(t +1) predicted total steam heat load, MW, at the next instant; k is the total number of users.
Step S2, establishing a main steam pipeline expected flow curve according to the real-time total steam heat load obtained in the step S1 and the predicted total steam heat load at the next moment;
according to the historical operation data of the month of the operation day, calculating to obtain the average maximum total steam load per day
Figure GDA0003586946410000083
The flow rate of the corresponding main steam pipeline is
Figure GDA0003586946410000084
Figure GDA0003586946410000085
If the flow corresponding to the real-time total steam heat load of the user is higher than the flow corresponding to the daily average maximum total steam load and the predicted flow corresponding to the total steam heat load at the next moment is higher than the flow corresponding to the real-time total steam heat load of the user, the expected flow of the main steam pipeline at the next moment is the predicted steam flow corresponding to the total steam heat load at the next moment, and the flow is maintained until the flow corresponding to the total steam heat load at the current moment is lower than the safe flow, namely the flow corresponding to the total steam heat load at the current moment is maintained, namely the flow corresponding to the daily average maximum total steam heat load is higher than the flow corresponding to the daily average maximum total steam heat load, and the predicted flow corresponding to the total steam heat load at the next moment is higher than the safe flow
When in use
Figure GDA0003586946410000091
And q isc(t+1)＞qdAt the time of (t), the reaction mixture,
Figure GDA0003586946410000092
wherein the content of the first and second substances,
Figure GDA0003586946410000093
the expected flow rate of the main steam pipeline at the next moment is kg/s; q. q.sc(t +1) is the predicted main steam pipeline flow at the next moment in kg/s; q. q.ssIs the minimum safe flow of the main steam pipeline, kg/s.
qc(t+1)＝f(Qc(t+1))
If the flow corresponding to the real-time total steam heat load of the user is higher than the flow corresponding to the average maximum total steam load per day and the predicted flow corresponding to the total steam heat load at the next moment is lower than the flow corresponding to the real-time total steam heat load of the user, the expected flow of the main steam pipeline at the next moment is the expected flow of the main steam pipeline at the current moment, namely the expected flow of the main steam pipeline at the current moment is
When the temperature is higher than the set temperature
Figure GDA0003586946410000094
And q isc(t+1)≤qdAt the time of (t), the reaction mixture,
qw(t+1)＝qw(t)
if the flow corresponding to the real-time total steam heat load of the user is lower than the flow corresponding to the average maximum total steam load per day, the expected flow of the main steam pipeline at the next moment is the flow corresponding to the average maximum total steam load per day, and the flow is maintained until the flow corresponding to the real-time total steam heat load is lower than the safe flow at the current moment, namely the flow is maintained until the flow corresponding to the real-time total steam heat load is lower than the safe flow
When in use
Figure GDA0003586946410000095
When the temperature of the water is higher than the set temperature,
Figure GDA0003586946410000096
the expected flow of the main steam pipeline is divided into three grades: safe flow, flow corresponding to the average maximum total steam load per day and the maximum flow on the day. The change rate of the ascending and descending flow among each grade of flow is less than a safety threshold value
Figure GDA0003586946410000101
Wherein, Δ t is the time required for changing from different gear flows, s; q. q.ssvFor elevating load safety threshold, kg/s2。
Dividing the time required by the lifting flow into two flow intervals equally, wherein the lifting flow rate is qsv(ii) a The total desired steam heat load corresponding to the desired flow rate of the main steam line is
Qw(t+1)＝f(qw(t+1))
Step S3, establishing a valve control model and a distributed power generation system power generation model, and generating a valve regulation scheme and a distributed power generation system output scheme at the next moment;
step S31, establishing a valve system; the main valve in front of the steam turbine of the distributed power generation system is determined by the difference between the total expected steam heat load of the main steam pipeline and the predicted total steam heat load at the next moment
V(t)＝f(|Qw(t+1)-Qc(t+1)|)
Wherein v (t) is the opening degree of the main valve in front of the distributed power generation system.
Step S32, establishing a balance model of the main steam pipeline
Qn(t+1)(1-ηn)＝Qw(t+1)
Wherein Q isn(t +1) is the heat supply, MW; etanIs the vapor transport loss factor.
The active load amount entering the distributed power generation system for power generation at the next moment is
Qe(t+1)＝Qw(t+1)-Qc(t+1)
Wherein Q ise(t +1) is the next moment active load, MW; qc(t +1) is the passive load, MW, at the next moment.
The expected generated energy of the distributed power generation system at the next moment is
Wp(t+1)＝ηeQe(t+1)
Wherein, Wp(t +1) is the park electricity production quantity, MW; etaeTo obtain the power generation efficiency.
FIG. 4 is a typical operating condition day when the maximum thermal load is lower than the average maximum total daily steam load, i.e., the maximum daily flow in the main steam line is lower than the flow corresponding to the average maximum daily total daily steam load; the flow of the main steam pipeline is lower than the safe flow at night. The flow of the main steam pipeline on the operation day is divided into two grades, namely the flow corresponding to the average highest total steam load and the safe flow. And when the two-gear flow is switched, the lifting flow speed is a lifting load safety threshold. The expected power generation amount of the distributed power generation system is the difference between the expected total steam heat load of the main steam pipeline and the real-time total steam heat load and changes along with the fluctuation of the real-time total steam heat load.
FIG. 5 shows the steam pressure fluctuation at the user side under the condition of FIG. 4. It can be seen that the expected outlet steam pressure of the main steam pipeline is obviously more stable than the predicted outlet steam pressure of the main steam pipeline, and the requirement of a user on steam parameters can be better met.
According to the method, the distributed power generation system type active load is set, the heat load fluctuation of the main steam pipeline is transferred to the power generation output fluctuation of the distributed power generation system, the heat load fluctuation with larger inertia is transferred to the electric load fluctuation with higher flexibility, the steam flow of the main steam pipe network and the stability of the steam pressure at the user side can be increased, and the flexibility of the heat supply system is increased.

Claims (1)

1. A steam heat network regulating and controlling method combined with distributed power generation is characterized by being realized based on a steam heat network system combined with distributed power generation, wherein the system comprises a thermal power plant (1), a steam pipe network system (2), a distributed power generation system (3), a micro-grid (4), a valve system (5) and a coordination control system (6); the steam pipe network system (2) comprises a main steam pipeline (21) and a branch steam pipeline (22); the distributed power generation system (3) comprises a steam turbine (31) and a power generator (32); the valve system (5) comprises main valves and other valves, wherein the main valves are front control valves (51) of a steam turbine (31) of the distributed power generation system, and the other valves are control valves and safety valves of other steam pipelines;
the steam generated by the thermal power plant (1) is conveyed to the industrial park through a main steam pipeline (21); according to the steam utilization characteristics of heat users in an industrial park and the requirements of a thermal power plant (1), a distributed power generation system (3) is configured at different positions: when the demand of the thermal power plant for reducing the flow fluctuation of the main steam pipeline (21) is met, the distributed power generation system (3) is arranged at the inlet of the main steam pipeline (21) to the industrial park; when the requirements that the flow of the main steam pipeline (21) is stable and the requirement change of the terminal important user is rapidly responded need to be met, the distributed power generation system (3) is configured in front of the terminal important user; in the same industrial park, the distributed power generation systems (3) can be configured at different positions and can be simultaneously configured in a plurality of places;
after steam generated by the thermal power plant (1) enters an industrial park, one part of the steam is used for meeting the real-time steam load of a heat user, and the other part of the steam enters a steam turbine (31) in the distributed power generation system (3) to do work, so that a generator (32) is driven to generate power and enter a microgrid (4);
the coordinated control system (6) forms a distributed power generation system output scheme according to the following steps:
step S1, establishing a steam load prediction model of each heat user in the industrial park by combining real-time total steam heat load, and obtaining the predicted total steam heat load at the next moment;
step S11, obtaining real-time steam temperature, pressure and flow data of a user by using a steam measuring device in front of the user side, transmitting the data to a data center, and calculating real-time total steam heat load
Qdj(t)＝f(Tdj(t)，pdj(t)，qdj(t))
Figure FDA0003586946400000021
Wherein Q isdj(t) is the real-time steam heat load, MW, for user j; t isdj(t) is the real-time steam temperature at home of the user j; p is a radical ofdj(t) is the real-time steam pressure of the user at j households, Mpa; q. q.sdj(t) is the real-time steam flow of the user before j households in kg/s; qd(t) total steam heat load in real time, MW; k is the total number of users;
step S12, obtaining the user steam heat load and the total steam heat load at the next moment by utilizing a machine learning algorithm and combining the real-time user steam heat load according to the regional weather real-time data, the heat supply area and the user steam heat load delay time parameter
Qcj(t+1)＝f(Qd(t)，D(t)，A，μ)
Figure FDA0003586946400000022
Wherein Qcj(t +1) is the predicted steam heat load of the next moment user jLotus, MW; d (t) is regional weather real-time data, including air temperature, wind speed, wind direction and humidity; a is the heat supply area, m2(ii) a Mu is a user steam heat load delay time parameter; qc(t +1) predicted total steam heat load, MW, at the next instant;
step S2, establishing a main steam pipeline expected flow curve according to the real-time total steam heat load obtained in the step S1 and the predicted total steam heat load at the next moment;
according to historical operation data of the month of the operation day, calculating to obtain the average maximum total steam load amount per day
Figure FDA0003586946400000023
The flow rate of the corresponding main steam pipeline is
Figure FDA0003586946400000024
Figure FDA0003586946400000025
If the flow corresponding to the real-time total steam heat load of the user is higher than the flow corresponding to the daily average maximum total steam load, and the predicted flow corresponding to the total steam heat load at the next moment is higher than the flow corresponding to the real-time total steam heat load of the user, the expected flow of the main steam pipeline at the next moment is the predicted steam flow corresponding to the total steam heat load at the next moment, and the flow is maintained until the flow corresponding to the total steam heat load at the current moment is lower than the safe flow, namely the flow is maintained
When in use
Figure FDA0003586946400000031
And q isc(t+1)＞qdAt the time of (t), the reaction mixture,
Figure FDA0003586946400000032
wherein the content of the first and second substances,
Figure FDA0003586946400000033
qw(t +1) is the expected flow of the main steam pipeline at the next moment, kg/s; q. q.sc(t +1) is the predicted main steam pipeline flow at the next moment in kg/s; q. q.ssThe minimum safe flow of the main steam pipeline is kg/s;
qc(t+1)＝f(Qc(t+1))
if the flow corresponding to the real-time total steam heat load of the user is higher than the flow corresponding to the average maximum total steam load per day and the predicted flow corresponding to the total steam heat load at the next moment is lower than the flow corresponding to the real-time total steam heat load of the user, the expected flow of the main steam pipeline at the next moment is the expected flow of the main steam pipeline at the current moment, namely the expected flow of the main steam pipeline at the current moment
When the temperature is higher than the set temperature
Figure FDA0003586946400000034
And q isc(t+1)≤qdAt the time of (t), the reaction mixture,
qw(t+1)＝qw(t)
if the flow corresponding to the real-time total steam heat load of the user is lower than the flow corresponding to the average maximum total steam load per day, the expected flow of the main steam pipeline at the next moment is the flow corresponding to the average maximum total steam load per day, and the flow is maintained until the flow corresponding to the real-time total steam heat load is lower than the safe flow at the current moment, namely the flow is maintained until the flow corresponding to the real-time total steam heat load is lower than the safe flow
When in use
Figure FDA0003586946400000035
When the temperature of the water is higher than the set temperature,
Figure FDA0003586946400000036
the expected flow of the main steam pipeline is divided into three grades: the safe flow rate is the flow rate corresponding to the average maximum total steam load per day and the maximum flow rate on the day; the change rate of the ascending and descending flow among each grade of flow is less than a safety threshold value
Figure FDA0003586946400000041
Wherein, Δ t is the time required for changing from different gear flows, s; q. q.ssvFor raising or lowering the safety threshold of the flow, kg/s2；
Dividing the time required by the lifting flow into two flow intervals equally, wherein the lifting flow rate is qsv(ii) a The total desired steam heat load corresponding to the desired flow rate of the main steam line is
Qw(t+1)＝f(qw(t+1))
Step S3, establishing a valve control model and a distributed power generation system power generation model, and generating a valve regulation scheme and a distributed power generation system output scheme at the next moment;
step S31, establishing a valve system; the main valve in front of the steam turbine of the distributed power generation system is determined by the difference between the total expected steam heat load of the main steam pipeline and the predicted total steam heat load at the next moment
V(t)＝f(|Qw(t+1)-Qc(t+1)|)
Wherein, V (t) is the opening degree of a main valve in front of the distributed power generation system;
step S32, establishing a balance model of the main steam pipeline
Qn(t+1)(1-ηn)＝Qw(t+1)
Wherein Q isn(t +1) is the heat supply, MW; etanIs the steam transport loss coefficient;
the active load amount entering the distributed power generation system for power generation at the next moment is
Qe(t+1)＝Qw(t+1)-Qc(t+1)
Wherein Q ise(t +1) is the next moment active load, MW; qc(t +1) is the next moment passive load, MW; wherein the active load is steam utilized by the distributed power generation system and the passive load is steam utilized by the thermal user;
the expected generated energy of the distributed power generation system at the next moment is
Wp(t+1)＝ηeQe(t+1)
Wherein, Wp(t +1) is the park electricity production quantity, MW; etaeTo obtain the power generation efficiency.
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