CN115234973A - Method for determining dynamic heat supply strategy of heat supply network - Google Patents

Method for determining dynamic heat supply strategy of heat supply network Download PDF

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CN115234973A
CN115234973A CN202210780184.2A CN202210780184A CN115234973A CN 115234973 A CN115234973 A CN 115234973A CN 202210780184 A CN202210780184 A CN 202210780184A CN 115234973 A CN115234973 A CN 115234973A
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temperature
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thermal resistance
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CN115234973B (en
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王顺江
郝俊红
戈志华
方王刚
杨云溪
王星策
田亮
东方
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North China Electric Power University
Electric Power Research Institute of State Grid Liaoning Electric Power Co Ltd
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Electric Power Research Institute of State Grid Liaoning Electric Power Co Ltd
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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
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
    • 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
    • F24D3/00—Hot-water central heating systems
    • F24D3/10—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system
    • F24D3/1058—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system disposition of pipes and pipe connections
    • 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
    • F24D3/00—Hot-water central heating systems
    • F24D3/12—Tube and panel arrangements for ceiling, wall, or underfloor heating
    • F24D3/14—Tube and panel arrangements for ceiling, wall, or underfloor heating incorporated in a ceiling, wall or floor
    • F24D3/141—Tube mountings specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2111/00—Details relating to CAD techniques
    • G06F2111/04—Constraint-based CAD
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2111/00—Details relating to CAD techniques
    • G06F2111/06—Multi-objective optimisation, e.g. Pareto optimisation using simulated annealing [SA], ant colony algorithms or genetic algorithms [GA]
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/08—Thermal analysis or thermal optimisation

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Abstract

The invention relates to a method for determining a dynamic heat supply strategy of a heat supply network, which belongs to the field of heat supply, and comprises the steps of firstly constructing an integral dynamic heat flow model of the heat supply system by combining dynamic standard thermal resistance models of a heat exchanger, a pipeline and a building envelope in the heat supply system, thereby establishing a functional relation between the water supply temperature of a heat source and the indoor temperature, then determining a dynamic coordination optimization model of the heat supply network with the minimum indoor temperature fluctuation and the minimum all-day carbon emission as optimization targets, finally iteratively calculating the water supply temperature of the heat source for maintaining the indoor temperature to be stable according to the real-time outdoor temperature, providing the heat supply strategy for the dynamic optimization operation of the heat supply network based on temperature regulation, and improving the comfort level of a user while reducing the carbon emission.

Description

Method for determining dynamic heat supply strategy of heat supply network
Technical Field
The invention relates to the field of heat supply, in particular to a method for determining a dynamic heat supply strategy of a heat supply network.
Background
Along with the appearance of climatic change and extreme weather, heating system still need combine together with the distribution network on further enlarging the heating capacity basis, through realizing the comprehensive collaborative energy supply of user end electricity, heat, promotes the flexibility of user side, establishes the basis for the new electric power system of future structure. Therefore, the heating system is positively changed into efficient cleaning and intelligent safety, the flexibility of the user side is deeply excavated through the flexibility of electric and heat loads, the diversified requirements of the user are met, and more renewable energy sources are consumed. Therefore, an effective control strategy needs to be customized for the central heating system and a complete control system needs to be constructed, but the informatization level of the existing heating system needs to be improved, and the control strategy needs to be perfected.
A typical heating system includes a water supply return line, a heat exchange station, an indoor enclosure, an indoor radiator, etc. In order to fully realize the high cleaning efficiency and the high flexibility of the user side of the heating system, the delay of heat transmission in the heating system, the thermal inertia, the random behavior of the user and the like need to be considered cooperatively in the physical modeling of the heating system. However, due to the multi-parameter and non-linear characteristics of the heating system and the user behaviors which are difficult to quantify, the existing research generally needs to simplify the heating system model to a certain extent, for example, steady-state modeling is adopted, the delay of a heating pipeline is simplified, the heat storage capacity of the system is ignored, disturbance caused by the heat user behaviors and climate change is ignored, and the accurate, rapid and overall coordination control of multiple heat sources, multiple users and multiple sites is difficult to realize.
Therefore, in order to enable the heat supply system to meet the requirement of a user on comfort while reducing energy consumption, a corresponding primary network operation strategy is formulated, supply and return water temperature supply is optimized, and electrification and low carbonization of terminal energy consumption are promoted. Through the novel heat supply network formed by coupling of the heat exchange station, the electric heat conversion system, the waste heat and waste heat utilization system and the like, the energy consumption and the emission are effectively reduced, and the comprehensive utilization rate of energy is improved.
Disclosure of Invention
The invention aims to provide a method for determining a dynamic heat supply strategy of a heat supply network, which is used for reducing carbon emission and improving the comfort of users.
In order to achieve the purpose, the invention provides the following scheme:
a method for determining a dynamic heating strategy of a heat supply network comprises the following steps:
respectively constructing a heat exchanger dynamic standard thermal resistance model, a pipeline dynamic standard thermal resistance model and an enclosure structure dynamic standard thermal resistance model based on a thermoelectric comparison method;
combining a heat exchanger dynamic standard thermal resistance model, a pipeline dynamic standard thermal resistance model and an enclosure structure dynamic standard thermal resistance model to obtain an integral dynamic heat flow model of the heating system;
determining a heat supply network dynamic coordination optimization model taking minimum indoor temperature fluctuation and minimum all-day carbon emission as optimization targets according to an overall dynamic heat flow model of a heat supply system;
and according to the real-time outdoor temperature, based on the integral dynamic heat flow model, performing iterative computation by using the heat supply network dynamic coordination optimization model to obtain the real-time heat source water supply temperature meeting the indoor temperature requirement, and forming a heat supply network dynamic heat supply strategy all day long.
Optionally, the dynamic standard thermal resistance model of the heat exchanger includes: general thermal resistance R between hot fluid and heat exchanger wall h General thermal resistance R between cold fluid and heat exchanger wall c And equivalent heat capacity C b ；
C b One end of R is h One end of (A) and R c Are connected in common at one end, C b The other end of the second switch is grounded;
R h is equivalent to the hot side inlet temperature T of the heat exchanger h,in ，C b One end of R is h One end of (A) and R c Is equivalent to the wall temperature T of the heat exchanger b ，R c Is equivalent to the cold side inlet temperature T of the heat exchanger c,in 。
Optionally, the expression of the dynamic standard thermal resistance model of the heat exchanger is
Figure BDA0003727437950000021
Figure BDA0003727437950000022
Figure BDA0003727437950000023
Wherein M is the heat exchanger wall mass, c p Is the heat capacity of the heat exchanger wall, T h,in (T) the hot side inlet temperature of the heat exchanger at time T, T c,in (T) the cold side inlet temperature of the heat exchanger at time T, T b (t) is the temperature of the heat exchanger wall at the moment t,
Figure BDA0003727437950000024
NTU h and NTU c The ratio of the effective thermal conductance of the heat exchanger to the thermal capacity of the hot fluid and the cold fluid respectively,
Figure BDA0003727437950000025
Figure BDA0003727437950000031
correction factor, k, to characterize the influence of the Heat exchanger flow on the Heat transfer Properties h And k c Heat exchange coefficients of a hot side and a cold side are respectively, and A is the heat exchange area between the working medium and the wall surface; g h And G c Hot volumetric flows, G, of hot and cold fluids, respectively h ＝m h c p,h ，G c ＝m c c p,c ，m h 、m c Mass flow of hot and cold fluids, respectively, c p,h 、 c p,c The specific heat capacities of the hot fluid and the cold fluid are respectively; t is a unit of h,out Is the hot side outlet temperature, T, of the heat exchanger c,out Is the cold side outlet temperature, Q, of the heat exchanger h 、Q c The heat exchange quantities of the hot fluid, the cold fluid and the heat exchange wall surface are respectively.
Optionally, the pipeline dynamic standard thermal resistance model includes: a plurality of heat exchange unit dynamic standard thermal resistance models;
the heat exchange unit dynamic standard thermal resistance model comprises a thermal resistance R of fluid in a pipe and a thermal resistance R of the pipe wall d,i Total thermal resistance R of steel pipe and two layers of outer-coating heat-insulating material s,i And heat capacity C p,i ；
C p,i One end of (A), R d,i Is one end of and R s,i Is connected at one end in common, C p,i The other end of the first and second electrodes is grounded;
R d,i the voltage node at the other end of the heat exchanger is equivalent to the temperature T of the fluid in the pipeline of the ith heat exchange unit d,i ，C p,i One end of (A), R d,i Is one end of and R s,i Is equivalent to the pipe wall temperature T of the pipe of the ith heat exchange unit p,i ，R s,i The voltage node at the other end of the same is equivalent to the soil temperature T of the ith heat exchange unit pipeline s,i 。
Optionally, the expression of the pipeline dynamic standard thermal resistance model is
Figure BDA0003727437950000032
Figure BDA0003727437950000033
Figure BDA0003727437950000034
Figure BDA0003727437950000035
Wherein, T d,i+1 Respectively the temperature of the fluid in the pipeline of the (i + 1) th heat exchange unit, Q i The heat exchange amount between the fluid in the ith heat exchange unit and the tube wall, G d,i Is the heat capacity flow of the fluid in the ith heat exchange unit, M 'is the mass of the tube wall, c' p The heat capacity of the pipe wall is shown,
Figure BDA0003727437950000036
to obtain the inlet temperature of the heat exchange unit at time t,
Figure BDA0003727437950000037
at time T + τ, Δ T is the temperature drop, τ is the time required for the fluid to flow from the head to the tail of the tube-heat exchange unit, L is the tube length of the tube, v is the fluid velocity, and n is the number of heat exchange units.
Optionally, the building envelope dynamic standard thermal resistance model includes: thermal resistance R of fluid and radiator wall l Thermal resistance R of radiator wall and air a Thermal resistance R of air and wall w Thermal resistance R of wall and outdoor air e Heat capacity C of radiator wall r Heat capacity C of indoor air a And heat capacity C of indoor wall w ；
R l One end of (A), R a And C and r are connected in common at one end, R a Another end of (1), R w And C and a are connected in common at one end, R w Another end of (1), R e And C w One end of the two ends are connected in a common point; c r Another end of (1), C a And the other end of (C) w The other ends of the two are grounded;
R l is equivalent to the radiator fluid inlet temperature T l,in ；R l One end of (A), R a And C and r is equivalent to the radiator wall temperature T r ；R a Another end of (1), R w And C and a is equivalent to the indoor temperature T a ；R w Another end of (1), R e And C and w is equivalent to the wall temperature T w ；R e Is equivalent to the outdoor temperature T e 。
Optionally, the expression of the dynamic standard thermal resistance model of the building envelope is
Figure BDA0003727437950000041
Figure BDA0003727437950000042
Figure BDA0003727437950000043
Figure BDA0003727437950000044
Wherein, T l,out Is the inlet temperature of the radiator fluid, Q is the heat exchange quantity of the hot fluid and the wall of the radiator, G l Is indoorsThermal capacity flow of the fluid.
Optionally, the optimization function of the dynamic coordination optimization model of the heat supply network is as follows: minEco 2 ＝min[(E 1 +E 2 )*2.6/(7000*4185.85)](ii) a Wherein Eco 2 For total daily carbon emission, E 1 、 E 2 Respectively consuming energy for heat users and losing heat for transportation;
the operation constraint conditions of the heat supply network dynamic coordination optimization model comprise heat transmission constraint and temperature constraint;
the heat transfer constraint is E in ＝E 1 +E 2 +E out (ii) a Wherein E is in 、E out Respectively system inlet energy and system outlet heat;
the temperature constraint is
T a,min <T a <T a,max
T a,max -T a,min <0.4℃
T a,min >18℃
Wherein, T a,min 、T a,max The minimum value and the maximum value of the indoor temperature are respectively.
Optionally, the obtaining a real-time heat source water supply temperature meeting an indoor temperature requirement by performing iterative computation based on the overall dynamic heat flow model and by using the heat supply network dynamic coordination optimization model according to the real-time outdoor temperature specifically includes:
calculating initial heat source water supply temperature based on the integral dynamic heat flow model according to initial physical property parameters of a heat exchanger, a pipeline and an enclosure structure in a heat supply system and by using an expression of a heat exchanger dynamic standard thermal resistance model, an expression of a pipeline dynamic standard thermal resistance model and an expression of an enclosure structure dynamic standard thermal resistance model in the integral dynamic heat flow model;
calculating the indoor temperature by utilizing the heat supply network dynamic coordination optimization model and an expression of a heat exchanger dynamic standard thermal resistance model, an expression of a pipeline dynamic standard thermal resistance model and an expression of a building envelope dynamic standard thermal resistance model in the integral dynamic heat flow model according to the real-time outdoor temperature and the initial heat source water supply temperature;
if the indoor temperature is within the indoor temperature setting range, outputting the initial heat source water supply temperature;
if the indoor temperature is lower than the lower limit value of the indoor temperature setting range, increasing the initial heat source water supply temperature by a preset temperature in advance for a heat supply delay time to obtain a new heat source water supply temperature, replacing the initial heat source water supply temperature with the new heat source water supply temperature, and simultaneously returning to the step of calculating the indoor temperature by using an expression of a heat exchanger dynamic standard thermal resistance model, an expression of a pipeline dynamic standard thermal resistance model and an expression of a containment structure dynamic standard thermal resistance model in the heat supply network dynamic coordination optimization model and the whole dynamic heat flow model according to the real-time outdoor temperature and the initial heat source water supply temperature;
if the indoor temperature is higher than the upper limit value of the indoor temperature setting range, reducing the initial heat source water supply temperature by a preset temperature in advance by a heat supply delay time to obtain a new heat source water supply temperature, replacing the initial heat source water supply temperature with the new heat source water supply temperature, and simultaneously returning to the step of calculating the indoor temperature by using an expression of a heat exchanger dynamic standard thermal resistance model, an expression of a pipeline dynamic standard thermal resistance model and an expression of an enclosure structure dynamic standard thermal resistance model in the heat supply network dynamic coordination optimization model and the whole dynamic heat flow model according to the real-time outdoor temperature and the initial heat source water supply temperature.
Optionally, the method for determining the heat supply delay time includes:
setting the average outdoor temperature of a heating season as the outdoor temperature, and the water supply temperature of a heat source to just ensure that the indoor temperature is within the indoor temperature setting range and the indoor temperature is in a stable state;
the time average value from the step of 10 c occurring in the temperature of the water supplied from the heat source to the time required to change the indoor temperature by 0.1 c was determined as the heat supply delay time.
According to the specific embodiment provided by the invention, the invention discloses the following technical effects:
the invention discloses a method for determining a dynamic heat supply strategy of a heat supply network, which comprises the steps of firstly constructing an integral dynamic heat flow model of the heat supply system by combining dynamic standard thermal resistance models of a heat exchanger, a pipeline and an enclosure structure in the heat supply system, thereby establishing a functional relation between the water supply temperature of a heat source and the indoor temperature, then determining a dynamic coordination optimization model of the heat supply network with the minimum indoor temperature fluctuation and the minimum all-day carbon emission as optimization targets, finally iteratively calculating the water supply temperature of the heat source for maintaining the indoor temperature to be stable according to the real-time outdoor temperature, providing the heat supply strategy for the dynamic optimization operation of the heat supply network based on temperature regulation, and improving the comfort of users while reducing the carbon emission.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required to be used in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art that other drawings can be obtained according to the drawings without inventive labor.
Fig. 1 is a flowchart of a method for determining a dynamic heating strategy of a heat supply network according to an embodiment of the present invention;
fig. 2 is a schematic diagram of a dynamic heating strategy of a heat supply network according to an embodiment of the present invention;
fig. 3 is a physical model of a district central heating system according to an embodiment of the present invention;
FIG. 4 is a physical model of a counterflow heat exchanger provided in accordance with embodiments of the present invention;
FIG. 5 is a dynamic standard thermal resistance model of a counterflow heat exchanger according to an embodiment of the present invention;
FIG. 6 is an overall physical model of a pipeline provided by an embodiment of the present invention;
FIG. 7 is a sectional model of a pipeline provided by an embodiment of the present invention;
FIG. 8 is a dynamic standard thermal resistance model of a tube-heat exchange unit according to an embodiment of the present invention;
FIG. 9 is a schematic view of an enclosure provided by an embodiment of the invention;
FIG. 10 is a dynamic standard thermal resistance model of a building envelope according to an embodiment of the present invention;
FIG. 11 is an overall dynamic standard thermal resistance model of a central heating system including users according to an embodiment of the present invention;
fig. 12 is a flowchart of dynamic simulation based on standard thermal resistance according to an embodiment of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The invention aims to provide a method for determining a dynamic heat supply strategy of a heat supply network, which is used for reducing carbon emission and improving the comfort of users.
In order to make the aforementioned objects, features and advantages of the present invention more comprehensible, the present invention is described in detail with reference to the accompanying drawings and the detailed description thereof.
The embodiment of the invention provides a method for determining a dynamic heat supply strategy of a heat supply network, which comprises the following steps as shown in figures 1-2:
step S1, respectively constructing a heat exchanger dynamic standard thermal resistance model, a pipeline dynamic standard thermal resistance model and an enclosure structure dynamic standard thermal resistance model based on a thermoelectric comparison method.
Fig. 3 shows a typical central heating system in an urban area, in which a heat source heats primary heat supply network water, high-temperature hot water is conveyed to a regional heat exchange station through a primary network pipeline, the heat exchange station heats secondary network return water through a heat exchanger, the heated return water conveys heat to each heat user through a secondary network pipeline, heat is released through an indoor radiator, indoor air is heated, and the return water continues to return to the heat exchange station, so that the whole heating process is completed.
The dynamic process of the urban central heating system to be considered comprises the following steps: the heat exchange station comprises a heat exchanger wall, a water supply and return pipeline wall, an indoor radiator wall, indoor air, the heat storage and release capacity of a concrete wall of the enclosure structure and the time delay of the water supply and return pipeline. Aiming at the processes, the invention introduces a standard thermal resistance method to construct an integral dynamic heat flow model of the system.
The construction process of the dynamic standard thermal resistance model of the heat exchanger, the water supply and return pipelines and the building envelope of the heat exchange station is described below.
(1) Heat exchanger of heat exchange station
In the overall dynamic process of the heating system, the dynamic process of the heat exchange equipment mainly comprising the heat exchange station and the heat exchanger is included, and a dynamic heat flow model of the heat exchange equipment is introduced for modeling analysis. The dynamic process analysis of the heat exchanger introduces the following assumptions: the heat exchange is carried out between cold and hot fluids, and the heat exchange of the cold and hot fluids with the surrounding environment is neglected; the flow rate and the heat capacity of the fluid are kept unchanged, and the physical parameters of the fluid are kept constant; the heat transfer coefficient of the whole heat exchanger surface is kept unchanged, the axial heat conduction in the heat exchange wall is neglected, and the wall or fluid of the heat exchanger has no internal heat source and the like.
The heat exchange and heat storage capacity performed by the heat exchanger of the heat exchange station comprises: the primary net supplies heat exchange between hot water and the heat exchange wall, and heat exchange between the heat storage energy of the heat exchange wall and the return water of the secondary net.
FIG. 4 is a schematic diagram of the operation of a counter-flow heat exchanger with the direction of the hot fluid flow being positive x-axis and the inlet temperature at the hot side of the heat exchanger being T h,in Cold side inlet temperature of T c,in The temperature of the heat exchange wall is T b Length is L h According to the model and by combining a heat flow method, the expression of the dynamic heat exchange process for describing the temperature change of the pipe wall is obtained as follows:
Figure BDA0003727437950000081
wherein M is the mass (kg) of the tube wall, c p Is the heat capacity (J.kg) of the heat exchanger wall -1 ·K -1 )，R h And R c Is a baseThe ratio of the inlet temperature difference to the heat exchange quantity is defined and used for representing the general thermal resistance of the heat exchange performance of the heat exchange unit, and the expression is as follows:
Figure BDA0003727437950000082
Figure BDA0003727437950000083
wherein NTU h And NTU c The number of hot end heat transfer units and the number of cold end heat transfer units of the heat exchanger are respectively expressed, namely the ratio of effective thermal conductance of the heat exchanger to thermal capacity flow of hot fluid and cold fluid, and the specific expression is as follows:
Figure BDA0003727437950000084
Figure BDA0003727437950000091
Figure BDA0003727437950000092
in order to represent a correction factor of the influence of the heat exchanger flow on the heat exchange performance, the value of a general countercurrent heat exchanger is 1, k h And k c Heat transfer coefficient of hot side and cold side (W.m) -2 ·K -1 ) A is the heat exchange area (m) between the working medium and the wall surface 2 )。
Wherein G is h,i And G c,i Heat capacity flows (W.K) of hot and cold fluids, respectively -1 ) I.e. the product of mass flow and specific heat, the expressions are:
G h ＝m h c p,h (6)
G c ＝m c c p,c (7)
in addition, when the working medium flows into another heat exchange unit in one heat exchange unit, heat exchange can be generated between cold and hot fluid and the pipe wall, and according to a first law of thermodynamics, the inlet temperature of the latter heat exchange unit is satisfied:
Figure BDA0003727437950000093
Figure BDA0003727437950000094
based on a thermoelectric analogy method, a dynamic standard thermal resistance model of the heat exchanger is constructed by analogy of a temperature node as a voltage node, a thermal resistance as a resistance and a thermal capacity as a capacitance, as shown in fig. 5, wherein T is h Is the hot side inlet temperature, T, of the heat exchanger c Is the cold side inlet temperature, T, of the heat exchanger b Is the wall temperature of the heat exchanger, R h And R c Respectively represents the universal thermal resistance between the hot fluid and the cold fluid and the pipe wall, C b Representing the equivalent heat capacity of the heat exchanger walls.
(2) Pipe line
The heat exchange and heat storage capacity of the heat supply pipeline comprises: heat exchange between the water supply and the pipeline, heat exchange between the pipeline and the heat insulating material, heat exchange between the heat insulating material and the soil and heat storage of the steel pipeline, and the time delay of a single heat exchange unit is calculated by adopting a segmentation method. The pipeline comprises a rigid polyurethane insulation layer, a PE insulation layer and a steel central pipe, but is not limited to the pipeline material and the insulation material.
The laying mode of the heat supply system secondary network transport pipeline is mainly underground laying, fluid in the pipeline exchanges heat with the heat preservation layer and soil, the pipeline modeling is similar to that of the heat exchanger, and only one hot fluid exists in the pipeline. The hot water inlet temperature of the pipeline is T d,in Wall temperature of T p The length of the tube is L d The fluid in the tube flows at a velocity v. Considering that the pipeline is long, the delay in the heat supply process is not negligible, the pipeline wall has large heat capacity, the heat storage of the pipeline part needs to be considered, and a modeling mode of a segmentation method is introduced for convenient calculation. Divide the heat exchange pipeline intoAnd (3) calculating respective heat exchange processes for the n heat exchange units, respectively calculating the respective heat exchange processes for each unit, considering that the physical parameters of the model are kept unchanged in each section, analyzing by using one heat exchange unit, and obtaining a physical model shown in figures 6 and 7.
The expressions describing the heat exchange process of the fluid in the pipeline and the heat exchange process of the pipe wall are respectively as follows:
Figure BDA0003727437950000101
Figure BDA0003727437950000102
in the formula, R s,i The total thermal resistance T of the steel pipe and two layers of outer heat-insulating materials d,i 、T p,i 、T s,i Respectively the temperature of fluid in the pipeline of the ith heat exchange unit, the temperature of the wall of the pipeline and the temperature of soil C p Representing the heat capacity of the pipe wall.
Based on a thermoelectric analogy method, a temperature node is analogized to a voltage node, a thermal resistance is analogized to a resistance, a thermal capacity is analogized to a capacitance, a dynamic standard thermal resistance model of the pipeline is constructed, and the standard thermal resistance model of a certain heat exchange unit of the pipeline is shown in figure 8.
In the analysis of the dynamic transmission process of the heat supply pipeline, the heat supply pipeline is generally longer, and the temperature propagation has longer time delay. The invention uses the thermal R to simulate the inductive concept in the electrical principle and uses the time delay generated by the fluid in the pipeline flow L To indicate. Meanwhile, in the process of flowing in the pipeline, heat exchange with the ambient environment exists, and a temperature drop Delta T exists. Assuming that the time required for the working medium to flow from the head end to the tail end of a certain heat exchange unit of the pipeline is tau, the working medium flowing through the head end of the pipeline at the moment t can flow to the tail end of the pipeline at the moment t + tau, and the outlet temperature of the heat exchange unit is as follows:
Figure BDA0003727437950000103
for a certain heat exchange unit, the time τ required for the working fluid to flow can be calculated by the following formula:
Figure BDA0003727437950000104
(3) Enclosure structure
The heat exchange and heat storage capacity performed on the hot user side includes: heat exchange between the water supply and the wall of the radiator, heat exchange between the wall of the radiator and the air, heat exchange between the air and the wall, heat exchange between the wall and the outdoor air, heat storage of the concrete wall, heat storage of the wall of the radiator and heat storage of the indoor air. The walls include concrete walls, granite protective layers, cement mortar protective layers, and polyethylene foam board insulation layers, but are not limited to the mentioned building materials.
The building envelope is used as a part which forms a building space and is directly related to a hot user, the modeling of the building is very important, the internal rooms of the building are numerous, and the modeling calculation amount of each room of the whole building is large. Therefore, the invention simplifies a certain room into a cuboid, and as shown in fig. 9, the modeling analysis of the heat load and the indoor temperature dynamic change is carried out on the cuboid, and the influence of factors such as heat supply area, the material characteristics and thickness of the building enclosure, outdoor temperature and the like on the water supply temperature is mainly analyzed. The model considers heat storage of a radiator, heat storage of room air and heat storage of a concrete wall.
In modeling the heat flow of a room, the following assumptions are made: 1) The heat exchange between the air in the room is sufficient, the temperature distribution is uniform and the temperature distribution is the same everywhere; 2) Heat loss caused by air leakage is ignored, other heat sources except the radiator in the room are ignored, and heat exchange with walls of other rooms is not considered; 3) Differences in solar radiation due to differences in the geographical location of the room are ignored.
Based on the assumptions, obtaining an expression for describing the heat exchange process of the fluid, the radiator wall, the indoor air and the wall in the indoor enclosure structure: the expression describing the heat exchange process of the fluid, the radiator wall, the indoor air and the wall in the indoor envelope structure is as follows:
Figure BDA0003727437950000111
Figure BDA0003727437950000112
Figure BDA0003727437950000113
Figure BDA0003727437950000114
wherein Q is the heat exchange amount of the hot fluid with the wall of the heat exchanger, G l Is the heat capacity flow of the fluid in the chamber, R l 、 R a 、R w 、R e Respectively the thermal resistance expressions of fluid and heat exchanger wall, heat exchanger wall and air, air and wall, wall and outdoor air, T r 、T a 、T w 、T e Respectively radiator wall temperature, indoor temperature, wall temperature and outdoor temperature, C r 、C a 、C w The heat capacities of the radiator wall, the indoor air and the indoor wall are respectively expressed.
Based on a thermoelectric analogy method, a temperature node is analogized to a voltage node, a thermal resistance is analogized to a resistance, and a thermal capacitance is analogized to a capacitance, so that a dynamic heat flow model of the enclosure structure shown in fig. 10 is constructed.
As can be seen from the above, the standard thermal resistance model is not only related to the physical parameters of the system, but also related to the operation conditions and initial parameters of the system.
And S2, combining the dynamic standard thermal resistance model of the heat exchanger, the dynamic standard thermal resistance model of the pipeline and the dynamic standard thermal resistance model of the enclosure structure to obtain an integral dynamic heat flow model of the heating system.
Based on the dynamic heat flow models of the respective sections, the overall dynamic heat flow model of the heating system shown in fig. 11 is obtained based on the thermoelectric comparison method. The heat starts from the inlet of the hot side of the heat exchange station and passes from left to right: the heat exchanger of the heat exchange station, a secondary network water supply pipeline, a heat user radiator and a secondary network water return pipeline return to a cold side inlet of the heat exchange station to finish the heat transmission process.
And S3, determining a heat supply network dynamic coordination optimization model taking minimum indoor temperature fluctuation and minimum all-day carbon emission as optimization targets according to the overall dynamic heat flow model of the heat supply system.
The step of establishing a heat supply network dynamic coordination optimization model taking minimum indoor temperature fluctuation and minimum all-day carbon emission as optimization targets comprises the following steps of:
determining a running constraint;
determining an optimization objective;
determining a decision variable;
establishing a coordination optimization model based on operation constraints, optimization targets and decision variables;
aiming at a cogeneration unit and a distributed energy conversion system, a system energy conservation equation is used as heat transmission constraint, and a heat source medium actual set temperature interval is used as temperature constraint;
the energy conservation equation is:
E in ＝E 1 +E 2 +E out
E in 、E 1 、E 2 、E out respectively, system inlet energy, heat consumer consumed energy, transportation lost heat, and system outlet heat.
The temperature interval constraints are set as follows:
T a,min <T a <T a,max
T a,max -T a,min <0.4℃
T a,min >18℃
the step of determining an optimization objective comprises:
the method is characterized in that the comfort degree of a heat user is guaranteed, namely indoor temperature fluctuation is reduced to serve as a first optimization target, and the minimum carbon emission in the whole day is taken as a second optimization target.
The step of determining a decision variable comprises:
by the mass flow Q of the heat supply pipe network and the heat supply temperature T of the heat source time by time h,i Any one or more of the initial temperature T of each part of the heat supply pipe network and the initial temperature heat supply area A of the user enclosure structure is/are combined to be used as a decision variable;
the target variable including heat supply E 1 Heat loss E 2 User indoor temperature T a Any one or any combination of a plurality thereof.
And S4, according to the real-time outdoor temperature, performing iterative computation based on the integral dynamic heat flow model and by using the heat supply network dynamic coordination optimization model to obtain the real-time heat source water supply temperature meeting the indoor temperature requirement.
Because the heating system is complex, multiple components are coupled with each other, and the accuracy of directly carrying out numerical calculation is not high, a theoretical value of the water supply temperature, which is required by a heat user, is obtained by adopting a calculation and iteration mode along with the change of the outdoor temperature. And calculating and analyzing the dynamic heat flow model by utilizing Matlab software. Fig. 12 shows a flow structure of the calculation. The method comprises the following specific steps: the method comprises the following specific steps:
1) According to the known parameters of the heat exchanger, the pipeline and the room, the initial calculation is carried out by combining the formulas (1) to (17) according to the outdoor temperature T e Supply water temperature T required for change h (ii) a Known heat exchanger, pipe, room parameters include: initial water temperature in each pipeline, initial temperature of pipe wall, initial temperature of wall and initial temperature of indoor air.
2) Calculating the whole dynamic heat flow model of the heating system to obtain the indoor temperature T when the water supply temperature is adopted a ；
3) On the premise of considering the heat supply time delay, comparing the indoor temperature with the indoor temperature set range, if the indoor temperature is higher than the set range, reducing the temperature of the primary network water supply in advance, and if the indoor temperature is lower than the set range, increasing the temperature of the primary network water supply in advance;
4) Recalculating a new indoor temperature according to the new primary network water supply temperature;
5) And comparing the new indoor temperature, and when the indoor temperature is in the set temperature range, quitting outputting the result, otherwise, continuing iterative calculation.
Based on the flow shown in fig. 11, there is a thermal sense R due to the temperature change of the fluid in the indoor radiator relative to the temperature change of the primary grid heating L Furthermore, the temperature variation in the room is delayed from the temperature variation of the fluid in the indoor radiator, so that the heat sensor R cannot be used L The delay of the indoor temperature affected by the temperature change of the primary mesh is described. For this situation, the present invention proposes a heat supply delay time: the outdoor temperature is set as the average temperature of a certain heating season, the heating temperature is just ensured to be within the set temperature range, when the indoor temperature is in a steady state, the water supply temperature is respectively subjected to 10 ℃ step change, the time average value is required when the indoor temperature changes by 0.1 ℃, the time is set as the delay time of the heat supply network, and the change of the water supply temperature caused by the indoor temperature is advanced by one delay time of the heat supply network.
The invention sets the following three scenes according to different user requirements:
(1) All-day heat supply type: that is, the indoor temperature is ensured to be within the set temperature range all day.
(2) Concave heat supply all day: namely conditioning and heating, 18: 00-day 8:00 normal heat supply, ensuring that the indoor temperature is in a set temperature range, 8: 00-day 18: and supplying heat at the temperature of 35 ℃ at the time of 00.
(3) Following user heating type: according to the behavior of the user's home and work habits, during the user's home, i.e. daily 18: 00-day 8:00 normal heat supply is carried out, the indoor temperature is ensured to be within a set temperature range, and the heat supply is stopped when a user leaves home in the daytime.
According to the outdoor temperature change, the time-by-time heat supply temperature required to be provided by the heat source outlet is calculated according to the iterative calculation flow introduced in the figure 12 and aiming at three heat supply scenes, and a heat supply strategy meeting the standard is designed. And in order to minimize heat consumption and avoid early heating, the proper heating time is obtained by iteration of the steps shown in fig. 12, so that the indoor temperature at 18 hours is just higher than the lowest value of the set temperature range.
And calculating the heating temperature of the primary network by adopting an iteration method on the premise of considering energy conservation and user comfort, and aiming at different heating modes, obtaining a heating strategy meeting the heating requirement.
Step S4 can calculate the temperature, heat exchange amount, carbon emission and the like of each part in the whole system, and comprises the water supply and return temperatures of the hot water side and the cold water side of the heat exchange station, the temperature of the heat exchange wall, the temperature of water at each point in the pipeline and the temperature of the pipe wall, the water supply and return temperatures of indoor heat supply hot water, the temperature of the wall of the heat exchanger, the average value of the indoor temperature, the temperature of the wall and the like.
The invention provides a method for adjusting a target variable through temperature, which can adjust indoor temperature based on temperature change of a primary network and improve comfort of a heat user. The heat supply strategy provided by the invention is beneficial to the optimization of the load distribution on the demand side of the heat supply system, improves the safety and stability of the system, improves the economic benefit and the environmental benefit of the heat supply system, and provides a new idea for subsequent operation scheduling and planning construction.
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
The principle and the implementation mode of the invention are explained by applying a specific example, and the description of the embodiment is only used for helping to understand the method and the core idea of the invention; also, it is obvious to those skilled in the art that various changes and modifications can be made in the embodiments and applications of the invention. In view of the above, the present disclosure should not be construed as limiting the invention.

Claims (10)

1. A method for determining a dynamic heat supply strategy of a heat supply network is characterized by comprising the following steps:
respectively constructing a heat exchanger dynamic standard thermal resistance model, a pipeline dynamic standard thermal resistance model and an enclosure structure dynamic standard thermal resistance model based on a thermoelectric comparison method;
combining a heat exchanger dynamic standard thermal resistance model, a pipeline dynamic standard thermal resistance model and a building envelope dynamic standard thermal resistance model to obtain an integral dynamic heat flow model of the heating system;
determining a heat supply network dynamic coordination optimization model taking minimum indoor temperature fluctuation and minimum all-day carbon emission as optimization targets according to an overall dynamic heat flow model of a heat supply system;
and according to the real-time outdoor temperature, based on the integral dynamic heat flow model, performing iterative computation by using the heat supply network dynamic coordination optimization model to obtain the real-time heat source water supply temperature meeting the indoor temperature requirement, and forming a heat supply network dynamic heat supply strategy all day long.
2. The method for determining a dynamic heating strategy of a heat supply network according to claim 1, wherein the dynamic standard thermal resistance model of the heat exchanger comprises: general thermal resistance R between hot fluid and heat exchanger wall h General thermal resistance R between cold fluid and heat exchanger wall c And equivalent heat capacity C b ；
C b One end of (A) R h Is one end of and R c Is connected at one end in common, C b The other end of the first and second electrodes is grounded;
R h is equivalent to the hot side inlet temperature T of the heat exchanger h,in ，C b One end of (A), R h Is one end of and R c Is equivalent to the wall temperature T of the heat exchanger b ，R c Is equivalent to the cold side inlet temperature T of the heat exchanger c,in 。
3. The method for determining the dynamic heating strategy of the heat supply network according to claim 2, wherein the expression of the dynamic standard thermal resistance model of the heat exchanger is
Figure FDA0003727437940000011
Figure FDA0003727437940000012
Figure FDA0003727437940000013
Wherein M is the heat exchanger wall mass, c p Is the heat capacity of the heat exchanger wall, T h,in (T) the hot side inlet temperature of the heat exchanger at time T, T c,in (T) the cold side inlet temperature of the heat exchanger at time T, T b (t) is the temperature of the heat exchanger wall at the moment t,
Figure FDA0003727437940000021
NTU h and NTU c The ratio of the effective thermal conductance of the heat exchanger to the thermal capacity of the hot fluid and the cold fluid respectively,
Figure FDA0003727437940000022
Figure FDA0003727437940000023
correction factor, k, for characterizing the influence of the heat exchanger flow on the heat exchange performance h And k c Heat exchange coefficients of a hot side and a cold side are respectively, and A is the heat exchange area between the working medium and the wall surface; g h And G c Heat capacity flows, G, of hot and cold fluids, respectively h ＝m h c p,h ，G c ＝m c c p,c ，m h 、m c Mass flow of hot and cold fluids, respectively, c p,h 、c p,c The specific heat capacities of the hot fluid and the cold fluid are respectively; t is h,out Is the hot side outlet temperature, T, of the heat exchanger c,out Is the cold side outlet temperature, Q, of the heat exchanger h 、Q c The heat exchange quantity of the hot fluid, the cold fluid and the heat exchange wall surface is respectively.
4. The method of claim 3, wherein the pipeline dynamic standard thermal resistance model comprises: a plurality of heat exchange unit dynamic standard thermal resistance models;
the dynamic standard thermal resistance model of the heat exchange unit comprises fluid in a pipe and heat on the pipe wallResistance R d,i Total thermal resistance R of steel pipe and two layers of external thermal insulation materials s,i And heat capacity C p,i ；
C p,i One end of (A) R d,i Is one end of and R s,i Is connected at one end in common, C p,i The other end of the first and second electrodes is grounded;
R d,i voltage node at the other end of the heat exchange unit is equivalent to the temperature T of fluid in the pipeline of the ith heat exchange unit d,i ，C p,i One end of (A), R d,i Is one end of and R s,i Is equivalent to the pipe wall temperature T of the ith heat exchange unit pipe p,i ，R s,i The voltage node at the other end of the same is equivalent to the soil temperature T of the ith heat exchange unit pipeline s,i 。
5. The method for determining the dynamic heating strategy of the heat supply network according to claim 4, wherein the expression of the pipeline dynamic standard thermal resistance model is
Figure FDA0003727437940000024
Figure FDA0003727437940000025
Figure FDA0003727437940000026
Figure FDA0003727437940000027
Wherein, T d,i+1 Respectively the temperature of fluid in the pipeline of the (i + 1) th heat exchange unit, Q i The heat exchange amount between the fluid in the ith heat exchange unit and the tube wall G d,i Is the heat capacity flow of the fluid in the ith heat exchange unit, M 'is the mass of the duct wall, c' p Indicating heat of the pipe wallThe volume of the liquid to be treated is,
Figure FDA0003727437940000031
to obtain the inlet temperature of the heat exchange unit at time t,
Figure FDA0003727437940000032
at time T + τ, Δ T is the temperature drop, τ is the time required for the fluid to flow from the head to the tail of the tube-heat exchange unit, L is the tube length of the tube, v is the fluid velocity, and n is the number of heat exchange units.
6. The method of claim 5, wherein the building envelope dynamic standard thermal resistance model comprises: thermal resistance R of fluid and radiator wall l Thermal resistance R of radiator wall and air a Thermal resistance R of air and wall w Thermal resistance R of wall and outdoor air e And heat capacity C of radiator wall r Heat capacity C of indoor air a And heat capacity C of indoor wall w ；
R l One end of (A), R a And C r Are connected in common at one end, R a Another end of (1), R w And C and a are connected in common at one end, R w Another end of (1), R e And C and w are connected in common; c r Another end of (1), C a And the other end of (C) and w the other ends of the two are grounded;
R l is equivalent to the radiator fluid inlet temperature T l,in ；R l One end of (A), R a And C and r is equivalent to the radiator wall temperature T r ；R a Another end of (1), R w And C and a is equivalent to the indoor temperature T a ；R w Another end of (1), R e And C and w is equivalent to the wall temperature T w ；R e Is equivalent to the outdoor temperature T e 。
7. The method for determining the dynamic heating strategy of the heat supply network according to claim 6, wherein the expression of the building envelope dynamic standard thermal resistance model is
Figure FDA0003727437940000033
Figure FDA0003727437940000034
Figure FDA0003727437940000035
Figure FDA0003727437940000036
Wherein, T l,out Is the inlet temperature of the radiator fluid, Q is the heat exchange quantity of the hot fluid and the wall of the radiator, G l Is the thermal mass flow of the fluid in the chamber.
8. The method for determining a dynamic heating strategy of a heat supply network according to claim 7, wherein the optimization function of the dynamic coordination optimization model of the heat supply network is as follows: minEco 2 ＝min[(E 1 +E 2 )*2.6/(7000*4185.85)](ii) a Wherein Eco 2 For total daily carbon emission, E 1 、E 2 Respectively consuming energy for heat users and losing heat for transportation;
the operation constraint conditions of the heat supply network dynamic coordination optimization model comprise heat transmission constraint and temperature constraint;
the heat transfer constraint is E in ＝E 1 +E 2 +E out (ii) a Wherein E is in 、E out Respectively system inlet energy and system outlet heat;
the temperature constraint is
T a,min <T a <T a,max
T a,max -T a,min <0.4℃
T a,min >18℃
Wherein, T a,min 、T a,max The minimum value and the maximum value of the indoor temperature are respectively.
9. The method for determining the dynamic heat supply strategy of the heat supply network according to claim 8, wherein the obtaining of the real-time heat source water supply temperature meeting the indoor temperature requirement based on the overall dynamic heat flow model and the iterative computation by using the dynamic coordination optimization model of the heat supply network according to the real-time outdoor temperature specifically comprises:
calculating the initial heat source water supply temperature based on the integral dynamic heat flow model according to the initial physical property parameters of a heat exchanger, a pipeline and an enclosure structure in the heat supply system and by utilizing an expression of a heat exchanger dynamic standard thermal resistance model, an expression of a pipeline dynamic standard thermal resistance model and an expression of an enclosure structure dynamic standard thermal resistance model in the integral dynamic heat flow model;
calculating the indoor temperature by utilizing the heat supply network dynamic coordination optimization model and an expression of a heat exchanger dynamic standard thermal resistance model, an expression of a pipeline dynamic standard thermal resistance model and an expression of a building envelope dynamic standard thermal resistance model in the integral dynamic heat flow model according to the real-time outdoor temperature and the initial heat source water supply temperature;
if the indoor temperature is within the indoor temperature setting range, outputting the initial heat source water supply temperature;
if the indoor temperature is lower than the lower limit value of the indoor temperature setting range, increasing the initial heat source water supply temperature by a preset temperature in advance by a heat supply delay time to obtain a new heat source water supply temperature, replacing the initial heat source water supply temperature with the new heat source water supply temperature, and simultaneously returning to the step of calculating the indoor temperature by using an expression of a heat exchanger dynamic standard thermal resistance model, an expression of a pipeline dynamic standard thermal resistance model and an expression of a building envelope dynamic standard thermal resistance model in the heat supply network dynamic coordination optimization model and the whole dynamic heat flow model according to the real-time outdoor temperature and the initial heat source water supply temperature;
if the indoor temperature is higher than the upper limit value of the indoor temperature setting range, reducing the initial heat source water supply temperature by a preset temperature in advance by a heat supply delay time to obtain a new heat source water supply temperature, replacing the initial heat source water supply temperature with the new heat source water supply temperature, and returning to the step of calculating the indoor temperature by using an expression of a heat exchanger dynamic standard thermal resistance model, an expression of a pipeline dynamic standard thermal resistance model and an expression of an enclosure structure dynamic standard thermal resistance model in the heat supply network dynamic coordination optimization model and the whole dynamic heat flow model according to the real-time outdoor temperature and the initial heat source water supply temperature.
10. The method for determining the dynamic heating strategy of the heat supply network according to claim 9, wherein the method for determining the heating delay time comprises the following steps:
setting the average outdoor temperature in a heating season as the outdoor temperature, and the water supply temperature of a heat source to just ensure that the indoor temperature is within the indoor temperature setting range and the indoor temperature is in a stable state;
the average value of the time required for the temperature of the room to change from the step of 10 c occurring in the temperature of the water supplied from the heat source to 0.1 c was determined as the heat supply delay time.
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