CN109538317A

CN109538317A - A kind of Dynamic calculation method of the heat regenerative system that can be improved peak load regulation ability and heat regenerative system heat storage can vapor (steam) temperature

Info

Publication number: CN109538317A
Application number: CN201811338591.8A
Authority: CN
Inventors: 曹丽华; 司和勇; 董恩伏; 胡鹏飞; 马汀山; 葛维春; 李树阳; 杨荣祖; 王艳红; 姜铁骝; 罗桓桓; 周桂平; 戴黎
Original assignee: Northeast Dianli University; State Grid Liaoning Electric Power Co Ltd; Electric Power Research Institute of State Grid Liaoning Electric Power Co Ltd; Xian Thermal Power Research Institute Co Ltd
Current assignee: State Grid Liaoning Electric Power Co Ltd; Electric Power Research Institute of State Grid Liaoning Electric Power Co Ltd; Northeast Electric Power University; Xian Thermal Power Research Institute Co Ltd
Priority date: 2018-11-12
Filing date: 2018-11-12
Publication date: 2019-03-29
Anticipated expiration: 2038-11-12
Also published as: CN109538317B

Abstract

The present invention is a kind of heat regenerative system that can be improved peak load regulation ability, including station boiler, steam turbine, generator, condenser, condensate pump, low-pressure heater, oxygen-eliminating device, feed pump, high-pressure heater, small turbine and temperature-decreased pressure reducer, its main feature is that, it further include heat storage can, using heat storage can to heat regenerative system and small turbine steam supply, when unit reduces generation load, heat storage can extracts rich high-temperature steam out of steam turbine, and heat is directly stored in heat storage can in vapour form.When unit load is higher, boiler feedwater increases, and heat regenerative system and small steam turbine steam consumption increase, the steam that at this time heat storage can be stored discharges, and is used for heat regenerative system and small steam turbine vapour, it is possible to reduce from the steam extraction of unit, increase unit output, plays the role of the peak Pinggu that disappears.And provide the Dynamic calculation method of heat storage can temperature change.

Description

A kind of heat regenerative system can be improved peak load regulation ability and heat regenerative system heat storage can steam The Dynamic calculation method of stripping temperature

Technical field

The present invention relates to the monitoring of heat power equipment performance state and diagnostic fields during coal electricity peak load regulation, are that one kind can Improve the heat regenerative system of peak load regulation ability and the Dynamic calculation method of heat regenerative system heat storage can vapor (steam) temperature.

Background technique

In recent years, deepening continuously with national energy conservation and emission reduction policy, clean energy resource is quickly grown.But it is rapid in wind-powered electricity generation While development, it is also faced with serious abandonment problem.Since there are typical regional characters for wind-powered electricity generation, the wind energy resources in China 80% are all Concentrate on " three Norths " area, i.e. northeast, North China and the Northwest；The supply of " three Norths " community energy and energy demand are in reverse point Cloth.The abandonment problem of rationing the power supply becomes increasingly conspicuous, and according to the statistical data of National Energy Board, 2015, wind-powered electricity generation abandonment was rationed the power supply situation aggravation, Annual 33900000000 kilowatt hour of abandonment electricity increases by 21,300,000,000 kilowatt hours, average abandonment rate 15% on year-on-year basis；2016, national wind-powered electricity generation was flat It utilizes hourage 1742 hours, increases by 14 hours on year-on-year basis, annual 49700000000 kilowatt hour of abandonment electricity；2017, national wind-powered electricity generation was flat It utilizes hourage 1948 hours, increases by 206 hours on year-on-year basis.Annual 41900000000 kilowatt hour of abandonment electricity reduces 7,800,000,000 thousand on year-on-year basis Watt-hour, abandonment situation of rationing the power supply is improved, but still very severe.

In terms of the restraining factors for causing abandonment, with the reinforcement of power grid construction, China " three Norths " area is because of rack constraint Influence just gradually reduces, and peak regulation difficulty is just becoming northeast, northwest abandonment main cause.Wherein fired power generating unit ratio height, unit fortune Low row flexibility is the major reason for leading to peak load regulation network scarce capacity.In addition, the fluctuation of network load has apparent peak valley Feature, for the variation for adapting to network load, thermal power generation unit is often in variable load operation operating condition, so that unit performance driving economy It is greatly reduced, corresponding net coal consumption rate and pollutant discharge amount increase.

With a large amount of networkings of the clean energy resourcies such as wind-powered electricity generation, solar energy, it has been further exacerbated by the fluctuation of network load, it is thus right More stringent requirements are proposed for the peaking operation of fired power generating unit.And heat storage can is widely used in thermoelectricity as a kind of energy storage device The peak modulation capacity of unit is improved in factory.But it is all that heat storage can is used to heat supply in current research to realize that thermoelectricity decouples, it should Method can improve the flexibility of unit to a certain extent, but its more single usage make fired power generating unit peak modulation capacity by Limit.

Therefore a kind of heat regenerative system that can sufficiently improve fired power generating unit peak modulation capacity is needed, which can not only dissolve Wind-powered electricity generation realizes the reasonable utilization of clean energy resource, it is often more important that the heat regenerative system can change according to heating demand to be monitored back at any time The variation of hot systems internal performance, and then improve the operational flexibility of regulating units.

Currently, not yet heat storage can is applied in heat regenerative system；Also heat accumulation can be monitored without a kind of circular Temperature change of tank during being filled and deflated by.Regulating units operating load is changing at any time, heat regenerative system thermic load variation characteristic It is difficult to accurate determination, therefore there is technology barriers for the flexible peak regulation of unit.

Summary of the invention

For the problem at present about fired power generating unit peak modulation capacity and flexibility difference, it is an object of the present invention to provide one kind It can be improved the heat regenerative system of peak load regulation ability；And scientific and reasonable, strong applicability is provided, calculate the storage of accurate heat regenerative system The Dynamic calculation method of hot tank vapor (steam) temperature variation.

Realize one of the object of the invention the technical solution adopted is that: a kind of peak load regulation ability that can be improved of the invention Heat regenerative system, it includes station boiler 1, steam turbine 2, generator 3, condenser 4, condensate pump 5, low-pressure heater 6, oxygen-eliminating device 7, feed pump 8, high-pressure heater 9, small turbine 11 and temperature-decreased pressure reducer 12, characterized in that further include heat storage can 10, the electricity The stand superheated steam outlet of boiler 1 is connected with the high pressure cylinder 2-1 entrance of steam turbine 2, the outlet the high pressure cylinder 2-1 of steam turbine 2 and electric The reheater entrance of boiler 1 of standing is connected, and the outlet of the reheater of station boiler 1 is connected with the intermediate pressure cylinder 2-2 entrance of steam turbine 2, vapour The outlet intermediate pressure cylinder 2-2 of turbine 2 is connected with the low pressure (LP) cylinder 2-3 entrance of steam turbine 2, and the low pressure (LP) cylinder 2-3 of steam turbine 2 is exported and coagulated 4 entrance of vapour device is connected, and the outlet of condenser 4 is connected with 5 entrance of condensate pump, the outlet of condensate pump 5 and 6 entrance phase of low-pressure heater Even, the outlet of low-pressure heater 6 is connected with 7 entrance of oxygen-eliminating device, and the outlet of oxygen-eliminating device 7 is connected with 8 entrance of feed pump, and feed pump 8 exports It is connected with 9 entrance of high-pressure heater, the outlet of high-pressure heater 9 is connected with 1 feed-water intake of station boiler, the high pressure cylinder of steam turbine 2 2-1 axis is connected with the intermediate pressure cylinder 2-2 axis of steam turbine 2, the low pressure (LP) cylinder 2-3 axis phase of the intermediate pressure cylinder 2-2 axis and steam turbine 2 of steam turbine 2 Even, the low pressure (LP) cylinder 2-3 axis of steam turbine 2 is connected with 3 axis of generator, the outlet of high-pressure heater 9 and 12 desuperheat of temperature-decreased pressure reducer Water inlet is connected, and the superheated steam outlet of station boiler 1 is connected with temperature-decreased pressure reducer entrance 12, the reheated steam of station boiler 1 Outlet is connected with 12 entrance of temperature-decreased pressure reducer, and the outlet of temperature-decreased pressure reducer 12 is connected with 10 entrance of heat storage can, the middle pressure of steam turbine 2 Cylinder 2-2 steam extraction outlet is connected with 10 entrance of heat storage can, and the outlet intermediate pressure cylinder 2-2 of steam turbine 2 is connected with 10 entrance of heat storage can, described The outlet of heat storage can 10 is connected with 11 entrance of small turbine, and the outlet of small turbine 11 is connected with 4 entrance of condenser, the heat storage can 10 Outlet is connected with the vapour source entrance of the vapour source entrance of oxygen-eliminating device 7, low-pressure heater 6 respectively, the outlet of small turbine 11 and oxygen-eliminating device 7 Outlet is connected.

Realize the object of the invention two the technical solution adopted is that: a kind of heat regenerative system can be improved peak load regulation ability The Dynamic calculation method of heat storage can vapor (steam) temperature, characterized in that it includes the following contents:

(a) heat storage can vapor (steam) temperature changes over time the simplification of dynamic model and assumes link

For the course of work of heat storage can, using heat storage can as research object, heat storage can inside energy storage is established with external load The dynamic model for changing and temperature being caused to change over time makes the following assumptions and simplifies first before establishing model:

1) ignore heat storage can into vapour, steam discharge and steam inside kinetic energy, the variation of potential energy；

2) think that heat storage can heat preservation situation is preferable, can be considered insulation, i.e., heat storage can does not have heat to exchange with external environment；

3) heat storage can does not do work externally in the process into vapour, steam discharge；

4) ignore the variation of heat storage can inner parameter, i.e., parameter is all concentrated on using lumped parameter method by heat storage can outlet Side；

5) ignore the restriction loss of heat storage can to small turbine admission gear；

(b) dynamic mathematical models that heat storage can vapor (steam) temperature changes over time construct link

It is based on step (a) it is assumed that again because heat storage can constantly has steam to flow into, flow out, therefore it is the opening for controlling volume Therrmodynamic system, therefore can be obtained by first law of thermodynamics open loop system energy equation:

In formula: δ Q is the heat that heat storage can is exchanged with the external world, kJ/kg；dE_cvFor the increment of total energy in heat storage can, kJ/kg； h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；C₁For the vapor (steam) velocity for flowing out heat storage can, m/s；Z₁For the steam for flowing out heat storage can The height of present position, m；δm_outFor the quality of steam for flowing out heat storage can, kg；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；C₀ For the vapor (steam) velocity for flowing into heat storage can, m/s；Z₀For the steam present position height for flowing into heat storage can, m；δm_inTo flow into heat storage can Quality of steam, kg；δw_iFor steam inside heat storage can work done, kJ/kg；

According to heat storage can practical work process, ignore lesser interference in the link, and by the 1 of step (a)) assume can Know, does not consider heat storage can into vapour, steam discharge kinetic energy, the variation of potential energy is thought: C₁=0, Z₁=0, C₀=0, Z₀=0；By step (a) 2) assume it is found that heat storage can heat preservation situation it is preferable, can be considered insulation, that is, think: δ Q=0；By the 3 of step (a)) assume It is found that heat storage can does not do work externally in the process into vapour, steam discharge, that is, think: δ w_i=0；By the 4 of step (a)) assume it is found that using Parameter is all concentrated on heat storage can outlet side by lumped parameter method, that is to say, that heat storage can outlet vapor parameter is in heat storage can Portion's steam parameter further indicates that formula (1) are as follows:

0=dE_cv+δm_outh₁-δm_inh₀+0 (2)

In formula: dE_cvFor the increment of total energy in heat storage can, kJ/kg；δm_outFor the quality of steam for flowing out heat storage can, kg；h₁For Flow out the steam enthalpy of heat storage can, kJ/kg；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；δm_inFor the steam matter for flowing into heat storage can Amount, kg,

Formula (2) further indicates that are as follows:

δm_inh₀-δm_outh₁=dE_cv (3)

Due to ignoring the variation of heat storage can steam inside kinetic energy and potential energy, the energy variation of heat storage can steam inside only has heat The variation of mechanical energy, then dE on the right of formula (3)_cvIt indicates are as follows:

dE_cv=d (mu)=Δ U=U₂-U₁ (4)

In formula: dE_cvFor the increment of total energy in heat storage can, kJ/kg；M is heat storage can quality of steam, kg；U is the steaming of unit quality The thermodynamic energy of vapour, kJ/kg；U₁The thermodynamic energy of steam, kJ before changing for heat storage can；U₂For the heat of steam after heat storage can variation Mechanical energy, kJ；Variable quantity of the Δ U for heat storage can steam thermodynamic energy, kJ,

Formula (4) are substituted into formula (3) to obtain:

Δ U=U₂-U₁=δ m_inh₀-δm_outh₁ (5)

In formula: U₁The thermodynamic energy of steam, kJ before changing for heat storage can；U₂The thermodynamic energy of steam after changing for heat storage can, kJ；Δ U is the variable quantity of heat storage can steam thermodynamic energy, kJ；δm_outFor the quality of steam for flowing out heat storage can, kg；h₁For outflow The steam enthalpy of heat storage can, kJ/kg；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；δm_inFor flow into heat storage can quality of steam, Kg,

The variation for considering heat storage can energy in the unit time, by formula (5) both sides simultaneously divided by time d τ, i.e.,

In formula: dU is the Tiny increment dt of heat storage can steam thermodynamic energy, kJ；δm_outFor the quality of steam for flowing out heat storage can, kg； h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；δm_inFor the steaming for flowing into heat storage can Vapour quality, kg；Tiny increment dt of the d τ for the time, s,

Since the total thermodynamic energy of heat storage can has following relationship, U=mu, the thermodynamic energy total to heat storage can takes total differential :

DU=d (mu)=udm+mdu (7)

In formula: dU is the Tiny increment dt of heat storage can steam thermodynamic energy, kJ；M is heat storage can quality of steam, kg；Dm is heat accumulation Tank quality of steam Tiny increment dt, kg；Du is the thermodynamic energy Tiny increment dt of unit quality steam, kJ/kg；U is unit quality steam Thermodynamic energy, kJ/kg,

Bring formula (7) into formula (6) left end, then formula (6) further indicates that are as follows:

In formula: δ m_outFor the quality of steam for flowing out heat storage can, kg；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₀For stream Enter the steam enthalpy of heat storage can, kJ/kg；δm_inFor the quality of steam for flowing into heat storage can, kg；D τ is the Tiny increment dt of time, s；M is storage Hot tank quality of steam, kg；Dm is heat storage can quality of steam Tiny increment dt, kg；Du is the thermodynamic energy Tiny increment dt of unit quality steam, kJ/kg；Thermodynamic energy of the u for unit quality steam, kJ/kg,

In formula (8), due to

In formula: δ m_inFor the quality of steam for flowing into heat storage can, kg；D τ is the Tiny increment dt of time, s；q_m,inTo flow into heat storage can Steam mass flow, kg/s,

In formula (8), due to

In formula: δ m_outFor the quality of steam for flowing out heat storage can, kg；D τ is the Tiny increment dt of time, s；q_m,outFor the storage of outflow system The mass flow of the steam of hot tank, kg/s,

Formula (9) and formula (10) are brought into formula (8) and can be obtained:

In formula: q_m,inFor the mass flow of the steam of inflow heat storage can, kg/s；h₁For the steam enthalpy for flowing out heat storage can, kJ/ kg；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；q_m,outIt is the mass flow of the steam of heat storage can, kg/s for outflow；D τ is The Tiny increment dt of time, s；M is heat storage can quality of steam, kg；Dm is heat storage can quality of steam Tiny increment dt, kg；Du is unit quality The thermodynamic energy Tiny increment dt of steam, kJ/kg；Thermodynamic energy of the u for unit quality steam, kJ/kg,

Formula (11) is the energy equation of heat storage can, now establishes mass-conservation equation to heat storage can, the quality according to system Conservation equation, the quality of steam for flowing into heat storage can subtract increment of the quality of steam equal to heat storage can quality of outflow heat storage can,

The mass-conservation equation of heat storage can indicates as a result, are as follows:

δ m=δ m_in-δm_out (12)

In formula: δ m is the Tiny increment dt of heat storage can quality of steam, kg；δm_inFor the quality of steam for flowing into heat storage can, kg；δm_out For flow out heat storage can quality of steam, kg,

On formula (12) both sides with divided by time d τ, then formula (12) further indicates that are as follows:

In formula: δ m is the Tiny increment dt of heat storage can quality of steam, kg；δm_inFor the quality of steam for flowing into heat storage can, kg；δm_out For the quality of steam for flowing out heat storage can, kg；Tiny increment dt of the d τ for the time, s,

Formula (13) is further deformed into:

In formula: δ m is the Tiny increment dt of heat storage can quality of steam, kg；q_m,inFor flow into heat storage can steam mass flow, kg/s；q_m,outIt is the mass flow of the steam of heat storage can, kg/s for outflow；Tiny increment dt of the d τ for the time, s,

Formula (14) are substituted into formula (11) and are obtained:

In formula: q_m,inFor the mass flow of the steam of inflow heat storage can, kg/s；h₁For the steam enthalpy for flowing out heat storage can, kJ/ kg；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；q_m,outIt is the mass flow of the steam of heat storage can, kg/s for outflow；D τ is The Tiny increment dt of time, s；M is heat storage can quality of steam, kg；Du is the thermodynamic energy Tiny increment dt of unit quality steam, kJ/kg；u For the thermodynamic energy of unit quality steam, kJ/kg,

Since heat accumulation working medium is superheated steam, superheated steam is regarded as ideal close to perfect gas by superheated steam property Gas then has:

Du=c_vdT (16)

In formula: c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；Du is the thermodynamic energy of unit quality steam Tiny increment dt, kJ/kg；DT is the variable quantity of vapor (steam) temperature in heat storage can, DEG C,

Formula (1,6) is substituted into formula (15) and is obtained:

In formula: c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；DT is the variation of vapor (steam) temperature in heat storage can Amount, DEG C；q_m,inFor the mass flow of the steam of inflow heat storage can, kg/s；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₀For Flow into the steam enthalpy of heat storage can, kJ/kg；q_m,outIt is the mass flow of the steam of heat storage can, kg/s for outflow；D τ is the micro- of time Increment, s；M is heat storage can quality of steam, kg；Du is the thermodynamic energy Tiny increment dt of unit quality steam, kJ/kg；U is unit matter The thermodynamic energy of amount steam, kJ/kg,

Using small turbine and feed pump as research object, by the hypothesis 5 of step step (a)) it is found that ignoring heat storage can to small The restriction loss of steam turbine admission gear, therefore small turbine energy balance formula can be obtained are as follows:

In formula: η_oiFor small turbine internal efficiency ratio, %；η_mFor small turbine mechanical efficiency, %；η_bFor water supply pump efficiency Rate, %； D_gsFor feedwater flow, kg/s；P_b' is feed pump inlet pressure, Pa；P_bIt " is water supply pump discharge pressure, MPa；θ_pFor to Avergae specific heat in water pump, kJ/ (kg DEG C)；q_m,inIt is the mass flow of the steam of heat storage can, kg/s for inflow；q_m,outFor outflow It is the mass flow of the steam of heat storage can, kg/s；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₂For exhaust enthalpy of small steam turbine, KJ/kg can be considered definite value in the operation of small turbine steady working condition,

Heat storage can, which is obtained, by formula (18) flows out steam flow are as follows:

In formula: η_oiFor small turbine internal efficiency ratio, %；η_mFor small turbine mechanical efficiency, %；η_bFor water supply pump efficiency Rate, %； D_gsFor feedwater flow, kg/s；P_b' is feed pump inlet pressure, Pa；P_bIt " is water supply pump discharge pressure, MPa；θ_pFor to Avergae specific heat in water pump, kJ/ (kg DEG C)；q_m,inIt is the mass flow of the steam of heat storage can, kg/s for inflow；q_m,outFor outflow It is the mass flow of the steam of heat storage can, kg/s；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₂For exhaust enthalpy of small steam turbine, KJ/kg,

Formula (19) are substituted into formula (17), and are arranged:

In formula: m is heat storage can quality of steam, kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；DT is storage The variable quantity of vapor (steam) temperature in hot tank, DEG C；D τ is the Tiny increment dt of time, s；Thermodynamic energy of the u for unit quality steam, kJ/kg, q_m,inIt is the mass flow of the steam of heat storage can, kg/s for inflow；D_gsFor feedwater flow, kg/s；P_b' is feed pump inlet-pressure Power, MPa； P_bIt " is water supply pump discharge pressure, MPa；θ_pFor avergae specific heat in feed pump, kJ/ (kg DEG C)；h₀To flow into heat accumulation The steam enthalpy of tank, kJ/kg；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₂For exhaust enthalpy of small steam turbine, kJ/kg；η_oiFor Small turbine internal efficiency ratio, %；η_mFor small turbine mechanical efficiency, %；η_bFor the water supply efficiency of pump, %,

It enables:

In formula: D_gsFor feedwater flow, kg/s；P_b' is feed pump inlet pressure, MPa；P_b" it is water supply pump discharge pressure, MPa；θ_pFor avergae specific heat in feed pump, kJ/ (kg DEG C)；η_oiFor small turbine internal efficiency ratio, %；η_mFor small turbine machine Tool efficiency, %；η_bFor the water supply efficiency of pump, %,

Formula (21) are substituted into formula (20) to obtain:

In formula: m is heat storage can quality of steam, kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；DT is storage The variable quantity of vapor (steam) temperature in hot tank, DEG C；D τ is the Tiny increment dt of time, s；Thermodynamic energy of the u for unit quality steam, kJ/kg, q_m,inIt is the mass flow of the steam of heat storage can, kg/s for inflow；P_b' is feed pump inlet pressure, MPa；P_bIt " is pumped out for water supply Mouth pressure, MPa；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₂For small vapour Turbine discharge enthalpy, kJ/kg,

Formula (22) is arranged:

In formula: m is heat storage can quality of steam, kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；DT is storage The variable quantity of vapor (steam) temperature in hot tank, DEG C；D τ is the Tiny increment dt of time, s；Thermodynamic energy of the u for unit quality steam, kJ/kg, q_m,inIt is the mass flow of the steam of heat storage can, kg/s for inflow；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；h₁For outflow The steam enthalpy of heat storage can, kJ/kg；h₂For exhaust enthalpy of small steam turbine, kJ/kg,

Further formula (23) deformation is arranged and obtains temperature in heat storage can and changes with time relationship are as follows:

In formula: dT is the variable quantity of vapor (steam) temperature in heat storage can, DEG C；D τ is the Tiny increment dt of time, s；M is heat storage can steam Quality, kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；U is the thermodynamic energy of unit quality steam, kJ/ Kg, q_m,inIt is the mass flow of the steam of heat storage can, kg/s for inflow；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；h₁For stream The steam enthalpy of heat storage can out, kJ/kg；h₂For exhaust enthalpy of small steam turbine, kJ/kg,

Regard superheated steam as perfect gas, then be tied to form just like ShiShimonoseki it is vertical, i.e.,

U=c_vT (25)

In formula: u is the thermodynamic energy of unit quality steam, kJ/kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg·℃)；T is vapor (steam) temperature in heat storage can, DEG C,

h₁=c_pT (26)

In formula: h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；c_PFor heat storage can steam pressurization specific heat capacity, kJ/ (kg ℃)；T is vapor (steam) temperature in heat storage can, DEG C,

Formula (25), formula (26) are substituted into formula (24) and obtained:

In formula: dT is the variable quantity of vapor (steam) temperature in heat storage can, DEG C；D τ is the Tiny increment dt of time, s；q_m,inTo flow into system The mass flow of the steam of heat storage can, kg/s；M is heat storage can quality of steam, kg；T is vapor (steam) temperature in heat storage can, DEG C；h₀For Flow into the steam enthalpy of heat storage can, kJ/kg；h₂For exhaust enthalpy of small steam turbine, kJ/kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg·℃)； c_PFor heat storage can steam pressurization specific heat capacity, kJ/ (kg DEG C),

It enables:

In formula: c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；c_PFor heat storage can steam pressurization specific heat capacity, kJ/ (kg DEG C),

Formula (28) are substituted into formula (27) to obtain:

Formula (29) is to reflect that temperature changes with time relationship in heat storage can；

Formula (19) are substituted into formula (14) to obtain:

In formula: dm is the variable quantity of heat storage can quality of steam, kg；D τ is the Tiny increment dt of time, s, q_m,inTo flow into heat accumulation The mass flow of the steam of tank, kg/s；D_gsFor feedwater flow, kg/s；P_b' is feed pump inlet pressure, Pa；P_bIt " is feed pump Outlet pressure, Pa；θ_pFor avergae specific heat in feed pump, kJ/ (kg DEG C)；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₂For Exhaust enthalpy of small steam turbine, kJ/kg；η_oiFor small turbine internal efficiency ratio, %；η_mFor small turbine mechanical efficiency, %；η_bFor to Pump efficiency, %,

Formula (21) are substituted into formula (30) to obtain:

In formula: dm is the variable quantity of heat storage can quality of steam, kg；D τ is the Tiny increment dt of time, s；q_m,inTo flow into heat accumulation The mass flow of the steam of tank, kg/s；c_PFor heat storage can steam pressurization specific heat capacity, kJ/ (kg DEG C)；h₂For small steam turbine exhaust steam Enthalpy, kJ/kg；T is vapor (steam) temperature in heat storage can, DEG C,

Formula (31) be in heat storage can quality change with time relationship, formula (29) and formula (31) simultaneous solution are obtained Vapor (steam) temperature changes with time relationship in heat storage can.

The present invention is about a kind of heat regenerative system that can be improved peak load regulation ability and heat regenerative system heat storage can vapor (steam) temperature Dynamic calculation method proposition, based on the idea that

1. heat storage capacity is strong since heat storage can principle is simple, the remaining heat of peak load regulation can be quickly absorbed, it is negative in height The lotus stage can also be applied it in Regenerative Systems of Fossil Fired Power Sets and small turbine system with quick release of energy, the present invention, be kept away Exempt to rely only on heat storage can and carried out the single application scheme such as heat, improved the availability of heat storage can, has increased unit itself and adjust Flexibility.

2. in the dynamic to heat storage can temperature change calculates as heat storage can be regarded to opening therrmodynamic system, therefore can foundation First law of thermodynamics open loop system energy equation carries out dynamic calculating to vapor (steam) temperature in heat storage can；

3. according to heat storage can energy conservation equation and mass-conservation equation be derived by heat storage can jointly vapor (steam) temperature and Quality of steam changes with time relationship, and by simultaneous solution heat storage can energy-balance equation and mass balance equation To calculated result；

4. it is worked to can establish heat storage can according to The Ideal-Gas Equation, mass-conservation equation and energy conservation equation The dynamic model of Cheng Zhongqi internal temperature at any time, by the variation characteristic of vapor (steam) temperature in heat storage can may infer that heat storage can and The working condition of unit.The peak regulation energy of unit can be differentiated in the working condition of heat regenerative system and small steam turbine system according to heat storage can Power, generation load and heating demand, and then reference frame is provided for power unit in economic operation.

5. according to the work characteristics of heat storage can, in conjunction with the actual moving process of Regenerative Systems of Fossil Fired Power Sets and small turbine, The first, second law of thermodynamics further provides the principle for realizing that technical solution of the present invention is followed, it may be assumed that

1. heat storage can is accessed Regenerative Systems of Fossil Fired Power Sets, using the storage system and heat storage capacity of heat storage can, to steam turbine Electric load be adjusted, when underload, absorbs excess steam, and when high load capacity discharges heat compensation heat regenerative system, and then improves machine The peak regulation flexibility of group；

2. the second protection of small turbine vapour source can be realized for small turbine steam supply by the heat storage capacity of heat storage can, it can According to different steam extraction parameter regulation heat regenerative system and small steamer steam supply parameter；Heat storage can is in work always in whole process Make state, steam inside temperature change is gentle, and the utilization rate of heat storage can be improved；

3. the variation that can calculate heat storage can internal temperature according to the storage system time of heat storage can and heat balance theory is special Property, and then the instantaneous operating conditions of available heat storage can, unit may infer that by the changing rule of its steam inside temperature Generation load and thermic load.

4. the dynamic meter of a kind of heat regenerative system that can be improved peak load regulation ability and heat regenerative system heat storage can vapor (steam) temperature Calculation method increases the utilization rate of heat storage can, substantially increases the peak modulation capacity of unit, enhances power grid to the cleanings energy such as wind-powered electricity generation Source is received, and can provide reference for fired power generating unit Peak Load.

Compared with prior art, the invention has the following beneficial technical effects:

A kind of heat regenerative system can be improved peak load regulation ability provided by the invention, using heat storage can to low-pressure heater In condensed water heated, the heat source stream of heat storage can be high pressure cylinder inlet steam, intermediate pressure cylinder after pressure and temperature reducing Inlet steam is also possible to each section of intermediate pressure cylinder pumping, low pressure (LP) cylinder inlet steam；Wherein, high-temperature steam is condensed in heat storage can and is changed It is condensed hydrophobic to be sent by the road to oxygen-eliminating device deoxygenation water tank after heat.Condensed water in low-pressure heater flows through heat storage can heating It is sent into next stage low-pressure heater afterwards, is sent into oxygen-eliminating device later.Bleeder steam can be reduced using heat storage can heat-setting water, Improve unit output.

It the composite can be widely applied to regulating units, at night, Turbo-generator Set is in underload period, while wind-powered electricity generation It contributes larger, running residue steam can be sent into heat storage can using pipeline and carry out heat accumulation, reduce unit output to dissolve wind Electricity improves utilization of new energy resources rate.On daytime, electric load is in the high load capacity period, and wind power output is smaller, can use heat storage can and adds Heat setting is born water, and reduces the sucking rate of unit, increases unit output；The online space of renewable energy can be increased, and played Disappear the effect in peak Pinggu, improves peak load regulation ability.

Variation characteristic of the present invention according to heat storage can steam inside temperature, it can obtain the real-time working shape of heat storage can State, and then can predict generation load and thermic load by unit.

Detailed description of the invention

A kind of heat regenerative system structural schematic diagram can be improved peak load regulation ability Fig. 1 of the invention；

Fig. 2 heat storage can fills vapour vapour source schematic diagram；

Fig. 3 heat storage can is to heat regenerative system steam bleeding schematic diagram；

Fig. 4 heat storage can is to small turbine steam bleeding schematic diagram；

Fig. 5 heat storage can energy balance figure.

Specific embodiment

Present invention will be further explained below with reference to the attached drawings and examples.

Referring to Fig.1~Fig. 5, a kind of heat regenerative system can be improved peak load regulation ability of the invention, it includes power station pot Furnace 1, steam turbine 2, generator 3, condenser 4, condensate pump 5, low-pressure heater 6, oxygen-eliminating device 7, feed pump 8, high-pressure heater 9, small turbine 11 and temperature-decreased pressure reducer 12, characterized in that further include heat storage can 10, the superheated steam of the station boiler 1 goes out Mouth is connected with the high pressure cylinder 2-1 entrance of steam turbine 2, the reheater entrance of high pressure cylinder the 2-1 outlet and station boiler 1 of steam turbine 2 It is connected, the reheater outlet of station boiler 1 is connected with the intermediate pressure cylinder 2-2 entrance of steam turbine 2, the outlet intermediate pressure cylinder 2-2 of steam turbine 2 It is connected with the low pressure (LP) cylinder 2-3 entrance of steam turbine 2, the outlet low pressure (LP) cylinder 2-3 of steam turbine 2 is connected with 4 entrance of condenser, condenser 4 Outlet be connected with 5 entrance of condensate pump, condensate pump 5 outlet is connected with 6 entrance of low-pressure heater, low-pressure heater 6 export and 7 entrance of oxygen-eliminating device is connected, and the outlet of oxygen-eliminating device 7 is connected with 8 entrance of feed pump, the outlet of feed pump 8 and 9 entrance phase of high-pressure heater Even, the outlet of high-pressure heater 9 is connected with 1 feed-water intake of station boiler, in the high pressure cylinder 2-1 axis and steam turbine 2 of steam turbine 2 Cylinder pressure 2-2 axis is connected, and the intermediate pressure cylinder 2-2 axis of steam turbine 2 is connected with the low pressure (LP) cylinder 2-3 axis of steam turbine 2, the low pressure (LP) cylinder of steam turbine 2 2-3 axis is connected with 3 axis of generator, and the outlet of high-pressure heater 9 is connected with 12 desuperheat water inlet of temperature-decreased pressure reducer, power station pot The superheated steam outlet of furnace 1 is connected with temperature-decreased pressure reducer entrance 12, reheated steam outlet and the temperature-decreased pressure reducer 12 of station boiler 1 Entrance is connected, and the outlet of temperature-decreased pressure reducer 12 is connected with 10 entrance of heat storage can, the intermediate pressure cylinder 2-2 steam extraction outlet of steam turbine 2 and heat accumulation 10 entrance of tank is connected, and the outlet intermediate pressure cylinder 2-2 of steam turbine 2 is connected with 10 entrance of heat storage can, the outlet of heat storage can 10 and small vapour 11 entrance of turbine is connected, and the outlet of small turbine 11 is connected with 4 entrance of condenser, the heat storage can 10 export respectively with oxygen-eliminating device 7 Vapour source entrance, low-pressure heater 6 vapour source entrance be connected, small turbine 11 outlet with oxygen-eliminating device 7 export is connected.

Condensed water enters power station pot through condensate pump 5, low-pressure heater 6, oxygen-eliminating device 7, high-pressure heater 9 from condenser 4 Furnace 1 absorbs thermal energy, becomes high temperature and high pressure steam i.e. superheated steam, superheated steam a part enters 2 high pressure cylinder of steam turbine, another Part needs to enter heat storage can 10 according to peak regulation.The reheater that station boiler 1 is entered back by high pressure cylinder steam discharge, in station boiler 1 Reheater in be heated after enter the intermediate pressure cylinder 2-2 or heat storage can 10 of steam turbine 2, while in the intermediate pressure cylinder 2-2 of steam turbine 2 Steam extraction is arranged in portion and middle pressure blow-off line, and into heat storage can 10, the low pressure (LP) cylinder 2-3 some vapor of last steam turbine 2 enters condensing Device 4.

The intermediate pressure cylinder 2-2 steam extraction of superheated steam, reheated steam, steam turbine 2 of the vapour source of heat storage can 10 from station boiler 1 With the position of intermediate pressure cylinder 2-2 four different parameters of steam discharge, as shown in Figure 1.Heat storage can 10 directly stores high temperature and high pressure steam, work Making mode is not generate inside it hydrophobic directly to small turbine 11 or heat regenerative system steam bleeding.It can be with according to the object of steam bleeding It is divided into: 1. to 11 steam supply of small turbine, 2. to 7 steam supply of heat regenerative system mesolow heater 6 and oxygen-eliminating device.It is released from heat storage can 10 Steam acting rear portion enter oxygen-eliminating device 7 and export main feed water pipe road, another part enters condenser 4 by drain water piping.

When unit participates in peak load regulation network, increases clean energy resource electricity volume, unit will reduce electric power output, and it is negative to force down power generation Lotus, it is contemplated that station boiler 1 is adjusted slowly, and quick load change increases by 1 unstability of station boiler, reduces power plant's macroeconomic Property.Excess steam is absorbed by setting heat storage can 10, unit quick load change is realized, and waste heat is stored, in unit liter It is continued to use when high load capacity.

When unit load is lower, the steam extraction valve of 2 intermediate pressure cylinder 2-2 of steam turbine is opened, heat storage can 10 is directly from steam turbine 2 Rich high-temperature steam is extracted in intermediate pressure cylinder 2-2, and heat is directly stored in heat storage can 10 in vapour form.If the external world uses Electric load continues to reduce, then opens 2 intermediate pressure cylinder 2-2 steam discharge of steam turbine again to the steam extraction valve between heat storage can 10, by part vapour The steam discharge of 2 intermediate pressure cylinder 2-2 of turbine is stored in vapour form in heat storage can 10.If stable operation of unit, while in heat storage can 10 Steam pressure when reaching the steam inlet condition of small turbine 11, feed pump 8 is electronic, steam feed pump, can carry out electronic and vapour Dynamic switching.The admission valve for opening small turbine 11, using the steam red switch small turbine 11 in heat storage can 10 and then steam-operating Feed pump 8 is driven, energy-efficient purpose is reached.If at this point, extraneous electric load increases suddenly, for the fortune for cooperating 1 side of station boiler again The quick load up of row at this time should be switched to feed pump 8 by steam-operating electronic to meet the needs of extraneous electric load improves, and be beaten It opens heat storage can 10 and is subtracted to the valve between oxygen-eliminating device 7 and low-pressure heater 6 with heating water supply using the steam in heat storage can 10 Few oxygen-eliminating device 7 and low-pressure heater 6 play the role of the peak Pinggu that disappears in addition from the steam extraction amount in steam turbine 2.

When unit load is higher, 1 confluent of station boiler increases, and heat regenerative system steam consumption also increases, and small turbine 11 loads will also increase, and steam consumption also increases.At this time if extraneous power load reduces, openable high-pressure heater 9 and desuperheat Feed-water valve between pressure reducer 12 opens simultaneously the admission valve between 1 superheated steam of station boiler and heat storage can 10, will be electric 1 superheated steam of boiler of standing is sent directly into heat storage can storage 10 after carrying out decrease temperature and pressure, at this moment if extraneous electric load persistently reduces, The valve between 1 reheated steam of station boiler and heat storage can 10 can be further opened, is stored up being sent into after reheated steam pressure and temperature reducing Hot tank 10 stores, similarly, negative to cooperate the operation of 1 side of station boiler quickly to rise if extraneous electric load increases suddenly at this time again Lotus at this time should be switched to feed pump 8 by steam-operating electronic to meet the needs of extraneous electric load raising, and open heat storage can 10 Valve to oxygen-eliminating device 7 and low-pressure heater 6 reduces 7 He of oxygen-eliminating device to heat water supply using the steam in heat storage can 10 In addition low-pressure heater 6 from the steam extraction amount in steam turbine 2, plays the role of the peak Pinggu that disappears.Operating above measure also can be improved machine The group fast-changing ability of strain burden, the flexibility of unit entirety greatly promote.

As shown in Fig. 2, a kind of heat storage can vapour source of heat regenerative system that can be improved peak load regulation ability of the invention includes Superheated steam, reheated steam, four different parameters such as steam extraction and the pumping of intermediate pressure cylinder 2-2 steam discharge in the middle part of 2 intermediate pressure cylinder 2-2 of steam turbine Steam source, temperature-decreased pressure reducer 12 is installed on superheated steam and reheated steam bleed steam pipework, on the one hand in order to reduce to storage Hot 10 thermal stress of tank variation, on the other hand can be according to heat regenerative system, the steam inlet condition of small turbine 11 greatly to the damage in its service life The matching of parameter is carried out, adjusts the pressure and temperature for entering 10 steam of heat storage can, at any time to meet heat regenerative system and small turbine 11 use the demand of vapour parameter.In addition, the storage capacity of main steam can be increased when higher with vapour parameter, it can when lower with vapour parameter Increase the ratio of 2 intermediate pressure cylinder 2-2 steam extraction of steam turbine.

A kind of dynamic calculating side of heat regenerative system heat storage can vapor (steam) temperature can be improved peak load regulation ability of the invention Method, including the following contents:

6) ignore heat storage can into vapour, steam discharge and steam inside kinetic energy, the variation of potential energy；

7) think that heat storage can heat preservation situation is preferable, can be considered insulation, i.e., heat storage can does not have heat to exchange with external environment；

8) heat storage can does not do work externally in the process into vapour, steam discharge；

9) ignore the variation of heat storage can inner parameter, i.e., parameter is all concentrated on using lumped parameter method by heat storage can outlet Side；

10) ignore the restriction loss of heat storage can to small turbine admission gear；

0=dE_cv+δm_outh₁-δm_inh₀+0 (2)

Formula (2) further indicates that are as follows:

δm_inh₀-δm_outh₁=dE_cv (3)

dE_cv=d (mu)=Δ U=U₂-U₁ (4)

Formula (4) are substituted into formula (3) to obtain:

Δ U=U₂-U₁=δ m_inh₀-δm_outh₁ (5)

DU=d (mu)=udm+mdu (7)

In formula (8), due to

Formula (9) and formula (10) are brought into formula (8) and can be obtained:

δ m=δ m_in-δm_out (12)

Formula (13) is further deformed into:

Formula (14) are substituted into formula (11) and are obtained:

Du=c_vdT (16)

Formula (1,6) is substituted into formula (15) and is obtained:

Formula (19) are substituted into formula (17), and are arranged:

It enables:

Formula (21) are substituted into formula (20) to obtain:

Formula (22) is arranged:

U=c_vT (25)

h₁=c_pT (26)

Formula (25), formula (26) are substituted into formula (24) and obtained:

It enables:

Formula (28) are substituted into formula (27) to obtain:

Formula (19) are substituted into formula (14) to obtain:

Formula (21) are substituted into formula (30) to obtain:

Calculated examples:

Formula (29) is deformed to obtain following formula

In formula: dT is the variable quantity of vapor (steam) temperature in heat storage can, DEG C；D τ is the Tiny increment dt of time, s；Δ τ is between the time Every s；T₀For heat storage can initial temperature, DEG C；T₁For the temperature after Δ τ time interval, DEG C.q_m,inTo flow into the steaming for being heat storage can The mass flow of vapour, kg/s；m₁For T₁Moment heat storage can quality of steam, kg；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；h₂ For exhaust enthalpy of small steam turbine, kJ/kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；c_PFor heat storage can steam pressurization Specific heat capacity, kJ/ (kg DEG C), γ c_PWith c_vThe ratio between.

Further deriving can obtain:

In formula: T₀For heat storage can initial temperature, DEG C；Δ τ is time interval, s；T₁For the temperature after Δ τ time interval, ℃。m₁For T₁Moment heat storage can quality of steam, kg.q_m,inIt is the mass flow of the steam of heat storage can, kg/s for inflow；h₀For stream Enter the steam enthalpy of heat storage can, kJ/kg；h₂For exhaust enthalpy of small steam turbine, kJ/kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg·℃)； c_PFor heat storage can steam pressurization specific heat capacity, kJ/ (kg DEG C), γ c_PWith c_vThe ratio between.

Further deformation can obtain above formula (31)

In formula: dm is the variable quantity of heat storage can quality of steam, kg；D τ is the Tiny increment dt of time, s；q_m,inTo flow into heat accumulation The mass flow of the steam of tank, kg/s；c_PFor heat storage can steam pressurization specific heat capacity, kJ/ (kg DEG C)；h₂For small steam turbine exhaust steam Enthalpy, kJ/kg；T is vapor (steam) temperature in heat storage can, DEG C.Δ τ is time interval, s；m₀For initial time heat storage can quality of steam, kg。m₁For T₁Moment heat storage can quality of steam, kg.

Further deformation can obtain formula (3):

In formula: d τ is the Tiny increment dt of time, s；T is vapor (steam) temperature in heat storage can, DEG C；h₀For the steam for flowing into heat storage can Enthalpy, kJ/kg； h₂For exhaust enthalpy of small steam turbine, kJ/kg；c_pFor heat storage can steam pressurization specific heat capacity, kJ/ (kgK), T₀It is first Beginning temperature, DEG C； T₁For the temperature after Δ τ time interval, DEG C.m₀For initial time heat storage can quality of steam, kg.m₁For T₁When Carve heat storage can quality of steam, kg.

Now be exemplified below: a heat accumulation tank volume is 50m³, pressure 40.5MPa, temperature is 469 DEG C.As shown in Figure 5.Water supply Pump inlet pressure P_b'=0.7MPa；Outlet pressure P_b"=32.4MPa；Specific heat at constant pressure c_p=0.0011367kJ/ (kg DEG C)；It is small Exhaust enthalpy of turbine h₂=2439kJ/kg；Feed pump efficiency eta_b=0.83；Mechanical efficiency η_m=0.99；Small steam turbine internal efficiency ratio η_oi=0.78, feedwater flow D_gs=708.65kg/s；Specific heat at constant pressure c_p=8.3879kJ/ (kg DEG C)；c_v=2.7728kJ/ (kg·℃)；Heat storage can initial time vapour density ρ₀=22.6295kg/m³。

It enables

In formula: c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；c_PFor heat storage can steam pressurization specific heat capacity, kJ/ (kg·℃).Initial mass flow is

m₀=ρ₀× V=22.6295kg/m³×50m³=11314.777kg (6)

In formula: ρ₀For heat storage can initial time vapour density, kg/m³, V is heat accumulation tank volume m³。

In formula: D_gsFor feedwater flow, kg/s；P_b' is feed pump inlet pressure, MPa；P_b" it is water supply pump discharge pressure, MPa；θ_pFor avergae specific heat in feed pump, kJ/ (kg DEG C)；η_oiFor small turbine internal efficiency ratio, %；η_mFor small turbine machine Tool efficiency, %；η_bFor the water supply efficiency of pump, %.

Since initial time heat accumulation pressure tank is higher, and inlet valve is in close state, i.e. q_m,in=0.

This up-to-date style (2) is further deformed into

In formula: T₀For heat storage can initial temperature, DEG C；Δ τ is time interval, s；T₁For the temperature after Δ τ time interval, ℃。m₁For T₁Moment heat storage can quality of steam, kg.；h₂For exhaust enthalpy of small steam turbine, kJ/kg；c_PFor heat storage can steam pressurization ratio Thermal capacitance, kJ/ (kg DEG C), γ c_PWith c_vThe ratio between；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C).

This up-to-date style (4) is further deformed into

In formula: T₀For initial temperature, DEG C；m₀For initial time heat storage can quality of steam, kg.m₁For T₁Moment heat storage can steams Vapour quality, kg.h₂For exhaust enthalpy of small steam turbine, kJ/kg；c_pFor heat storage can steam pressurization specific heat capacity, kJ/ (kgK), when Δ τ is Between be spaced, s.

With unit time 60s for a unit, quality of steam in heat storage can after 60s are as follows:

By m₁Numerical value, which brings formula (7) into, can acquire T₁Value:

The preferred embodiment of the present invention has been described in detail above, but the present invention is not limited to embodiment, Those skilled in the art can also make various equivalent modifications on the premise of not violating the inventive spirit of the present invention Or replacement, these equivalent variation or replacement are all contained in scope of the present application.

Claims

1. a kind of heat regenerative system that can be improved peak load regulation ability, it includes station boiler (1), steam turbine (2), generator (3), condenser (4), condensate pump (5), low-pressure heater (6), oxygen-eliminating device (7), feed pump (8), high-pressure heater (9), small Steam turbine (11) and temperature-decreased pressure reducer (12), characterized in that further include heat storage can (10), the overheat of the station boiler (1) is steamed Vapor outlet is connected with high pressure cylinder (2-1) entrance of steam turbine (2), high pressure cylinder (2-1) outlet of steam turbine (2) and station boiler (1) reheater entrance is connected, and the reheater outlet of station boiler (1) is connected with intermediate pressure cylinder (2-2) entrance of steam turbine (2), Intermediate pressure cylinder (2-2) outlet of steam turbine (2) is connected with low pressure (LP) cylinder (2-3) entrance of steam turbine (2), the low pressure (LP) cylinder of steam turbine (2) The outlet (2-3) is connected with condenser (4) entrance, and condenser (4) outlet is connected with condensate pump (5) entrance, and condensate pump (5) goes out Mouth is connected with low-pressure heater (6) entrance, and low-pressure heater (6) outlet is connected with oxygen-eliminating device (7) entrance, oxygen-eliminating device (7) outlet Be connected with feed pump (8) entrance, feed pump (8) outlet is connected with high-pressure heater (9) entrance, high-pressure heater (9) export and Station boiler (1) feed-water intake is connected, intermediate pressure cylinder (2-2) axis phase of high pressure cylinder (2-1) axis and steam turbine (2) of steam turbine (2) Even, intermediate pressure cylinder (2-2) axis of steam turbine (2) is connected with low pressure (LP) cylinder (2-3) axis of steam turbine (2), the low pressure (LP) cylinder of steam turbine (2) (2-3) axis is connected with generator (3) axis, and high-pressure heater (9) outlet is connected with temperature-decreased pressure reducer (12) desuperheat water inlet, The superheated steam outlet of station boiler (1) is connected with temperature-decreased pressure reducer entrance (12), the reheated steam of station boiler (1) export and Temperature-decreased pressure reducer (12) entrance is connected, and temperature-decreased pressure reducer (12) outlet is connected with heat storage can (10) entrance, the middle pressure of steam turbine (2) Cylinder (2-2) steam extraction outlet is connected with heat storage can (10) entrance, and intermediate pressure cylinder (2-2) outlet of steam turbine (2) enters with heat storage can (10) Mouth is connected, and heat storage can (10) outlet is connected with small turbine (11) entrance, and small turbine (11) outlet enters with condenser (4) Mouth is connected, and the heat storage can (10) exports the vapour source entrance phase with the vapour source entrance of oxygen-eliminating device (7), low-pressure heater (6) respectively Even, small turbine (11) outlet is connected with oxygen-eliminating device (7) outlet.

2. a kind of heat regenerative system that can be improved peak load regulation ability according to claim 1, characterized in that heat storage can steams The Dynamic calculation method of stripping temperature includes the following contents:

For the course of work of heat storage can, using heat storage can as research object, establishes energy storage inside heat storage can and change with external load And the dynamic model for causing temperature to change over time, it makes the following assumptions and simplifies first before establishing model:

It is based on step (a) it is assumed that again because heat storage can constantly has steam to flow into, flow out, therefore it is the opening heating power for controlling volume System, therefore can be obtained by first law of thermodynamics open loop system energy equation:

In formula: δ Q is the heat that heat storage can is exchanged with the external world, kJ/kg；dE_cvFor the increment of total energy in heat storage can, kJ/kg；h₁For Flow out the steam enthalpy of heat storage can, kJ/kg；C₁For the vapor (steam) velocity for flowing out heat storage can, m/s；Z₁To flow out locating for the steam of heat storage can The height of position, m；δm_outFor the quality of steam for flowing out heat storage can, kg；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；C₀For stream Enter the vapor (steam) velocity of heat storage can, m/s；Z₀For the steam present position height for flowing into heat storage can, m；δm_inFor the steaming for flowing into heat storage can Vapour quality, kg；δw_iFor steam inside heat storage can work done, kJ/kg；

According to heat storage can practical work process, ignore lesser interference in the link, and by the 1 of step (a)) assume it is found that not Heat storage can is considered into vapour, steam discharge kinetic energy, the variation of potential energy is thought: C₁=0, Z₁=0, C₀=0, Z₀=0；By step (a) 2) assume it is found that heat storage can heat preservation situation it is preferable, can be considered insulation, that is, think: δ Q=0；By the 3 of step (a)) assume it is found that Heat storage can does not do work externally in the process into vapour, steam discharge, that is, thinks: δ w_i=0；By the 4 of step (a)) assume it is found that using concentrating Parameter is all concentrated on heat storage can outlet side by parametric method, that is to say, that heat storage can outlet vapor parameter is to steam inside heat storage can Vapour parameter further indicates that formula (1) are as follows:

0=dE_cv+δm_outh₁-δm_inh₀+0 (2)

In formula: dE_cvFor the increment of total energy in heat storage can, kJ/kg；δm_outFor the quality of steam for flowing out heat storage can, kg；h₁For outflow The steam enthalpy of heat storage can, kJ/kg；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；δm_inFor flow into heat storage can quality of steam, Kg,

Formula (2) further indicates that are as follows:

δm_inh₀-δm_outh₁=dE_cv (3)

Due to ignoring the variation of heat storage can steam inside kinetic energy and potential energy, the energy variation of heat storage can steam inside only has thermodynamics Can variation, then dE on the right of formula (3)_cvIt indicates are as follows:

dE_cv=d (mu)=Δ U=U₂-U₁ (4)

In formula: dE_cvFor the increment of total energy in heat storage can, kJ/kg；M is heat storage can quality of steam, kg；U is unit quality steam Thermodynamic energy, kJ/kg；U₁The thermodynamic energy of steam, kJ before changing for heat storage can；U₂For the thermodynamics of steam after heat storage can variation Can, kJ；Variable quantity of the Δ U for heat storage can steam thermodynamic energy, kJ,

Formula (4) are substituted into formula (3) to obtain:

Δ U=U₂-U₁=δ m_inh₀-δm_outh₁ (5)

In formula: U₁The thermodynamic energy of steam, kJ before changing for heat storage can；U₂For the thermodynamic energy of steam after heat storage can variation, kJ； Δ U is the variable quantity of heat storage can steam thermodynamic energy, kJ；δm_outFor the quality of steam for flowing out heat storage can, kg；h₁To flow out heat accumulation The steam enthalpy of tank, kJ/kg；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；δm_inFor flow into heat storage can quality of steam, kg,

In formula: dU is the Tiny increment dt of heat storage can steam thermodynamic energy, kJ；δm_outFor the quality of steam for flowing out heat storage can, kg；h₁For Flow out the steam enthalpy of heat storage can, kJ/kg；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；δm_inFor the steam matter for flowing into heat storage can Amount, kg；Tiny increment dt of the d τ for the time, s,

Since the total thermodynamic energy of heat storage can has following relationship, U=mu, the thermodynamic energy total to heat storage can takes total differential to obtain:

DU=d (mu)=udm+mdu (7)

In formula: dU is the Tiny increment dt of heat storage can steam thermodynamic energy, kJ；M is heat storage can quality of steam, kg；Dm is heat storage can steaming Vapour quality Tiny increment dt, kg；Du is the thermodynamic energy Tiny increment dt of unit quality steam, kJ/kg；U is the heating power of unit quality steam Energy, kJ/kg,

In formula: δ m_outFor the quality of steam for flowing out heat storage can, kg；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₀To flow into storage The steam enthalpy of hot tank, kJ/kg；δm_inFor the quality of steam for flowing into heat storage can, kg；D τ is the Tiny increment dt of time, s；M is heat storage can Quality of steam, kg；Dm is heat storage can quality of steam Tiny increment dt, kg；Du is the thermodynamic energy Tiny increment dt of unit quality steam, kJ/ kg；Thermodynamic energy of the u for unit quality steam, kJ/kg,

In formula (8), due to

In formula: δ m_inFor the quality of steam for flowing into heat storage can, kg；D τ is the Tiny increment dt of time, s；q_m,inFor the steaming for flowing into heat storage can The mass flow of vapour, kg/s,

In formula (8), due to

In formula: δ m_outFor the quality of steam for flowing out heat storage can, kg；D τ is the Tiny increment dt of time, s；q_m,outIt is heat storage can for outflow Steam mass flow, kg/s,

Formula (9) and formula (10) are brought into formula (8) and can be obtained:

In formula: q_m,inFor the mass flow of the steam of inflow heat storage can, kg/s；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₀ For the steam enthalpy for flowing into heat storage can, kJ/kg；q_m,outIt is the mass flow of the steam of heat storage can, kg/s for outflow；D τ is the time Tiny increment dt, s；M is heat storage can quality of steam, kg；Dm is heat storage can quality of steam Tiny increment dt, kg；Du is unit quality steam Thermodynamic energy Tiny increment dt, kJ/kg；Thermodynamic energy of the u for unit quality steam, kJ/kg,

Formula (11) is the energy equation of heat storage can, now establishes mass-conservation equation to heat storage can, the conservation of mass according to system Equation, the quality of steam for flowing into heat storage can subtract increment of the quality of steam equal to heat storage can quality of outflow heat storage can,

δ m=δ m_in-δm_out (12)

In formula: δ m is the Tiny increment dt of heat storage can quality of steam, kg；δm_inFor the quality of steam for flowing into heat storage can, kg；δm_outFor stream The quality of steam of heat storage can out, kg,

In formula: δ m is the Tiny increment dt of heat storage can quality of steam, kg；δm_inFor the quality of steam for flowing into heat storage can, kg；δm_outFor stream The quality of steam of heat storage can out, kg；Tiny increment dt of the d τ for the time, s,

Formula (13) is further deformed into:

In formula: δ m is the Tiny increment dt of heat storage can quality of steam, kg；q_m,inFor the mass flow of the steam of inflow heat storage can, kg/s； q_m,outIt is the mass flow of the steam of heat storage can, kg/s for outflow；Tiny increment dt of the d τ for the time, s,

Formula (14) are substituted into formula (11) and are obtained:

In formula: q_m,inFor the mass flow of the steam of inflow heat storage can, kg/s；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₀ For the steam enthalpy for flowing into heat storage can, kJ/kg；q_m,outIt is the mass flow of the steam of heat storage can, kg/s for outflow；D τ is the time Tiny increment dt, s；M is heat storage can quality of steam, kg；Du is the thermodynamic energy Tiny increment dt of unit quality steam, kJ/kg；U is unit The thermodynamic energy of quality steam, kJ/kg,

Since heat accumulation working medium is superheated steam, superheated steam is regarded as perfect gas close to perfect gas by superheated steam property, Then have:

Du=c_vdT (16)

In formula: c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；Du is the micro- increasing of thermodynamic energy of unit quality steam Amount, kJ/kg；DT is the variable quantity of vapor (steam) temperature in heat storage can, DEG C,

Formula (1,6) is substituted into formula (15) and is obtained:

In formula: c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；DT is the variable quantity of vapor (steam) temperature in heat storage can, DEG C； q_m,inFor the mass flow of the steam of inflow heat storage can, kg/s；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₀To flow into storage The steam enthalpy of hot tank, kJ/kg；q_m,outIt is the mass flow of the steam of heat storage can, kg/s for outflow；D τ is the Tiny increment dt of time, s；M is heat storage can quality of steam, kg；Du is the thermodynamic energy Tiny increment dt of unit quality steam, kJ/kg；U is unit quality steam Thermodynamic energy, kJ/kg,

Using small turbine and feed pump as research object, by the hypothesis 5 of step step (a)) it is found that ignoring heat storage can to small steamer The restriction loss of machine admission gear, therefore small turbine energy balance formula can be obtained are as follows:

In formula: η_oiFor small turbine internal efficiency ratio, %；η_mFor small turbine mechanical efficiency, %；η_bFor the water supply efficiency of pump, %； D_gsFor feedwater flow, kg/s；P_b' is feed pump inlet pressure, Pa；P_bIt " is water supply pump discharge pressure, MPa；θ_pFor in feed pump Avergae specific heat, kJ/ (kg DEG C)；q_m,inIt is the mass flow of the steam of heat storage can, kg/s for inflow；q_m,outIt is heat accumulation for outflow The mass flow of the steam of tank, kg/s；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₂For exhaust enthalpy of small steam turbine, kJ/kg, In the operation of small turbine steady working condition, definite value can be considered,

In formula: η_oiFor small turbine internal efficiency ratio, %；η_mFor small turbine mechanical efficiency, %；η_bFor the water supply efficiency of pump, %； D_gsFor feedwater flow, kg/s；P_b' is feed pump inlet pressure, Pa；P_bIt " is water supply pump discharge pressure, MPa；θ_pFor in feed pump Avergae specific heat, kJ/ (kg DEG C)；q_m,inIt is the mass flow of the steam of heat storage can, kg/s for inflow；q_m,outIt is heat accumulation for outflow The mass flow of the steam of tank, kg/s；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₂For exhaust enthalpy of small steam turbine, kJ/kg,

Formula (19) are substituted into formula (17), and are arranged:

In formula: m is heat storage can quality of steam, kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；DT is heat storage can The variable quantity of interior vapor (steam) temperature, DEG C；D τ is the Tiny increment dt of time, s；U is the thermodynamic energy of unit quality steam, kJ/kg, q_m,in It is the mass flow of the steam of heat storage can, kg/s for inflow；D_gsFor feedwater flow, kg/s；P_b' is feed pump inlet pressure, MPa；P_bIt " is water supply pump discharge pressure, MPa；θ_pFor avergae specific heat in feed pump, kJ/ (kg DEG C)；h₀To flow into heat storage can Steam enthalpy, kJ/kg；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₂For exhaust enthalpy of small steam turbine, kJ/kg；η_oiFor small steamer Machine internal efficiency ratio, %；η_mFor small turbine mechanical efficiency, %；η_bFor the water supply efficiency of pump, %,

It enables:

In formula: D_gsFor feedwater flow, kg/s；P_b' is feed pump inlet pressure, MPa；P_bIt " is water supply pump discharge pressure, MPa；θ_p For avergae specific heat in feed pump, kJ/ (kg DEG C)；η_oiFor small turbine internal efficiency ratio, %；η_mFor small turbine machinery effect Rate, %；η_bFor the water supply efficiency of pump, %,

Formula (21) are substituted into formula (20) to obtain:

In formula: m is heat storage can quality of steam, kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；DT is heat storage can The variable quantity of interior vapor (steam) temperature, DEG C；D τ is the Tiny increment dt of time, s；U is the thermodynamic energy of unit quality steam, kJ/kg, q_m,in It is the mass flow of the steam of heat storage can, kg/s for inflow；P_b' is feed pump inlet pressure, MPa；P_bIt " is water supply pump discharge pressure Power, MPa；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₂For small turbine Exhaust enthalpy, kJ/kg,

Formula (22) is arranged:

In formula: m is heat storage can quality of steam, kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；DT is heat storage can The variable quantity of interior vapor (steam) temperature, DEG C；D τ is the Tiny increment dt of time, s；U is the thermodynamic energy of unit quality steam, kJ/kg, q_m,in It is the mass flow of the steam of heat storage can, kg/s for inflow；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；h₁To flow out heat accumulation The steam enthalpy of tank, kJ/kg；h₂For exhaust enthalpy of small steam turbine, kJ/kg,

In formula: dT is the variable quantity of vapor (steam) temperature in heat storage can, DEG C；D τ is the Tiny increment dt of time, s；M is heat storage can steam matter Amount, kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)；Thermodynamic energy of the u for unit quality steam, kJ/kg, q_m,inIt is the mass flow of the steam of heat storage can, kg/s for inflow；h₀For the steam enthalpy for flowing into heat storage can, kJ/kg；h₁For outflow The steam enthalpy of heat storage can, kJ/kg；h₂For exhaust enthalpy of small steam turbine, kJ/kg,

U=c_vT (25)

In formula: u is the thermodynamic energy of unit quality steam, kJ/kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg DEG C)； T is vapor (steam) temperature in heat storage can, DEG C,

h₁=c_pT (26)

In formula: h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；c_PFor heat storage can steam pressurization specific heat capacity, kJ/ (kg DEG C)；T is Vapor (steam) temperature in heat storage can, DEG C,

Formula (25), formula (26) are substituted into formula (24) and obtained:

In formula: dT is the variable quantity of vapor (steam) temperature in heat storage can, DEG C；D τ is the Tiny increment dt of time, s；q_m,inIt is heat storage can to flow into Steam mass flow, kg/s；M is heat storage can quality of steam, kg；T is vapor (steam) temperature in heat storage can, DEG C；h₀To flow into storage The steam enthalpy of hot tank, kJ/kg；h₂For exhaust enthalpy of small steam turbine, kJ/kg；c_vFor heat storage can steam specific heat at constant volume, kJ/ (kg ℃)；c_PFor heat storage can steam pressurization specific heat capacity, kJ/ (kg DEG C),

It enables:

Formula (28) are substituted into formula (27) to obtain:

Formula (19) are substituted into formula (14) to obtain:

In formula: dm is the variable quantity of heat storage can quality of steam, kg；D τ is the Tiny increment dt of time, s, q_m,inFor the steaming for flowing into heat storage can The mass flow of vapour, kg/s；D_gsFor feedwater flow, kg/s；P_b' is feed pump inlet pressure, Pa；P_bIt " is water supply pump discharge pressure Power, Pa；θ_pFor avergae specific heat in feed pump, kJ/ (kg DEG C)；h₁For the steam enthalpy for flowing out heat storage can, kJ/kg；h₂For small steamer Machine exhaust enthalpy, kJ/kg；η_oiFor small turbine internal efficiency ratio, %；η_mFor small turbine mechanical efficiency, %；η_bFor water supply pump efficiency Rate, %,

Formula (21) are substituted into formula (30) to obtain:

In formula: dm is the variable quantity of heat storage can quality of steam, kg；D τ is the Tiny increment dt of time, s；q_m,inFor the steaming for flowing into heat storage can The mass flow of vapour, kg/s；c_PFor heat storage can steam pressurization specific heat capacity, kJ/ (kg DEG C)；h₂For exhaust enthalpy of small steam turbine, kJ/ kg；T is vapor (steam) temperature in heat storage can, DEG C,

Formula (31) be in heat storage can quality change with time relationship, formula (29) and formula (31) simultaneous solution are obtained into heat accumulation Vapor (steam) temperature changes with time relationship in tank.