CN111829059A - Dynamic modeling method, model and regulation and control system for heat supply system - Google Patents
Dynamic modeling method, model and regulation and control system for heat supply system Download PDFInfo
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Abstract
The invention provides a dynamic modeling method, a model and a regulation and control system for a heating system. The modeling method comprises the following steps: acquiring outdoor meteorological parameters, a topological structure of a centralized heating system and operation condition test data; establishing a dynamic energy flow model of a directly-buried pipeline, a heat exchange station and a heat user containing a radiator in a centralized heating system by adopting a flow method; and combining outdoor meteorological parameters, and connecting the built energy flow models of the direct buried pipeline, the heat exchanger and the building heat users with the radiators into a dynamic energy flow model of the central heating system according to the obtained topological structure. The energy flow model of the centralized heating system describes the dynamic transfer process of heat from the network side to the user side, and has guiding significance for optimizing the regulation strategy of the heating system and improving the operation management level of the heating system.
Description
[ technical field ] A method for producing a semiconductor device
The invention relates to the technical field of heating systems, in particular to a dynamic modeling method, a model and a regulation and control system for a heating system.
[ background of the invention ]
The centralized heating system mainly comprises a heat source, heat exchange stations, a heat supply pipe network and heat users, high-temperature steam produced by the heat source heats circulating water in the primary network through a steam-water heat exchanger, and the circulating water in the primary network is transported through the heat supply pipe network and then completes heat exchange with the circulating water in the secondary network in the secondary heat exchange stations. And the circulating water of the secondary network is transported to a radiator at the user side through a pipeline to complete a heat supply task.
In the actual operation process, the central heating system has the following problems: (1) in the heating period, in order to keep the pressure and flow speed requirements of the working medium of the heating system, the high-power operation of the circulating water pump needs to be kept all the time, and the energy consumption is particularly high under the variable load working condition; (2) the scale of the heating system is large, the related pipelines and other equipment are numerous, most of the pipelines are buried underground, and real-time data of the equipment during operation is lacked, so that the management is not facilitated; (3) when the heating system does not operate under a stable working condition, the working condition is easy to be disordered, the heat transmission delay of a user at the near end is small, the heat loss is small, and the temperature is higher; the heat transmission delay of a remote user is large, the heat loss is large, the indoor temperature cannot reach the design temperature, and the comfort level of the user is reduced no matter the indoor temperature is too high or too low; (4) the system has poor robustness, and when equipment fails, the system cannot give an alarm to a dispatcher and quickly locate the equipment in time, so that the energy consumption is increased and the user is uncomfortable.
Therefore, there is a need to develop a heating system dynamic modeling method, model and regulation system to address the deficiencies of the prior art and to solve or alleviate one or more of the problems.
[ summary of the invention ]
In view of this, the invention provides a dynamic modeling method, a model and a regulation and control system for a heating system, so as to solve the problem of cold and heat imbalance caused by different heat transmission delay times and different heat transfer losses of near-end and far-end users.
In one aspect, the present invention provides a heating system dynamic modeling method, including the steps of:
(1) acquiring outdoor meteorological parameters, a topological structure of a centralized heating system and operation condition test data;
(2) establishing dynamic energy flow models of a direct-buried pipeline, a heat exchanger and a heat user containing a radiator in a centralized heating system by adopting an energy flow method, wherein the dynamic energy flow models are respectively used for describing heat exchange processes of the direct-buried pipeline, the heat exchanger and the heat user containing the radiator in a building;
(3) and combining outdoor meteorological parameters, connecting the built energy flow models of the direct buried pipeline, the heat exchanger and the building heat users containing the radiator into a dynamic energy flow model of a central heating system according to the obtained topological structure, and further describing the dynamic transfer process of heat from the network side to the user side.
The above-described aspect and any possible implementation further provide an implementation, wherein the outdoor weather parameters in step (1) include hours, temperature, and solar radiation intensity, and the temperature and solar radiation intensity are converted into an outdoor air integrated temperature:
wherein, TsaThe comprehensive temperature of outdoor air, unit: k;
Ta,outoutdoor air temperature, unit: k;
rho is the radiation absorption coefficient of the outer surface of the enclosure structure and is less than 1;
solar radiation intensity, unit: w/m2；
ha,outThe convective heat transfer coefficient of the building envelope and outdoor air, unit: w/(m)2·K)。
The above-mentioned aspect and any possible implementation manner further provide an implementation manner, and the method for establishing a dynamic energy flow model of a directly-buried pipeline in a central heating system by using an energy flow method in step (2) includes: establishing a heat transfer differential equation of the directly buried pipeline through a first thermodynamic law;
wherein, Td,Tp,TsThe temperature of the fluid in the pipe, the pipe wall and the soil surface, unit: k;
Cd,Cpthe heat capacity of the fluid in the pipe and the pipe wall is as follows: KJ/K;
the heat capacity is calculated by C ═ mc, where m is the mass of the material, kg, C is the specific heat capacity of the material, J/(kg · K);
Gdfluid heat capacity flow, unit: KW/K;
heat capacity flow is given by the formula G ═ vmc calculation of where vmIs the mass flow rate of the fluid, unit: kg/s; c is the specific heat capacity of the fluid, J/(kg. K);
k is the convective heat transfer coefficient between the fluid and the pipe wall, unit: KW/(m)2·K)；
i(i ═ 1,2,3) insulation, insulation shell and soil thickness, units: km;
λp,λi(i ═ 1,2,3) coefficients of thermal conductivity of pipe wall, insulation shell and soil, in units: KW/(m.K);
A,Ai( i 1,2,3) heat exchange area between adjacent two layers of fluid in the pipe, pipe wall, heat insulation layer shell and soil, unit: km2。
The above-mentioned aspects and any possible implementation manner further provide an implementation manner, in the step (2), the heat transfer differential equation of the buried pipeline is simplified and integrated, and in combination with a thermoelectric comparison theory, the temperature difference is compared with a potential difference, the heat exchange amount is compared with a current, the ratio of the temperature difference to the heat exchange amount is compared with a resistance, and the heat capacity is compared with a capacitance, and the heat transfer differential equation of the buried pipeline is rewritten as follows:
wherein, Td,in(t) pipe inlet fluid temperature, in units: k;
Rdequivalent heat transfer resistance of fluid in the pipe and the wall surface of the pipeline, unit: K/W, the heat transfer resistance is
Calculation of where ad＝(kA)d/Gd；
RsEquivalent heat transfer resistance of the pipeline wall surface and soil, unit: K/W, the heat transfer resistance is
And (4) calculating.
The above-mentioned aspect and any possible implementation manner further provide an implementation manner, and the dynamic energy flow model of the heat exchanger in the step (2) is specifically: establishing a heat transfer differential equation of the heat exchanger through a first thermodynamic law:
Tc,Th,Twcold fluid, hot fluid and heat exchanger wall temperature, unit: k;
Cc,Ch,Cwthe internal cooling and heating fluid and wall surface heat capacity of the heat exchanger are as follows: J/K;
heat capacity is calculated by C ═ mc, where m is mass of material, kg, C is mass specific heat capacity, in units: j/(kg. K);
Gc,Ghthe heat capacity flow of cold and hot fluid, unit: W/K;
heat capacity flow is given by the formula G ═ vmc calculation of where vmIs the mass flow rate of the fluid, unit: kg/s; c is the specific heat capacity of the fluid,unit: j/(kg. K);
kc,khthe convective heat transfer coefficient between cold and hot fluid and the wall surface of the heat exchanger, unit: w/(m)2·K)；
λwThe heat conductivity coefficient of the wall surface of the heat exchanger, unit: W/(m.K);
Ac,Ahthe heat exchange area between the cold and hot fluid and the wall surface of the heat exchanger, unit: m is2。
The above-mentioned aspects and any possible implementation manner further provide an implementation manner, in the step (2), the heat transfer differential equation of the heat exchanger is simplified and integrated, and a thermoelectric comparison theory is combined, the temperature difference is compared with a driving potential, the heat exchange amount is compared with a current, a ratio between the temperature difference and the heat exchange amount is compared with a heat transfer resistance, and the heat capacity is compared with a capacitance, and the heat transfer differential equation of the heat exchanger can be rewritten as follows:
Tc,in(t),Th,in(t) heat exchanger cold fluid inlet temperature, hot fluid inlet temperature, in units: k;
Rhequivalent heat transfer thermal resistance of hot fluid and the wall surface of a heat exchanger, unit: K/W; the heat transfer thermal resistance is
Calculation of where ah＝(kA)h/Gh；
RcEquivalent heat transfer resistance of the wall surface of the heat exchanger and the cold fluid, unit: K/W; the heat transfer thermal resistance is
Calculation of where ac＝(kA)c/Gc。
The above-mentioned aspect and any possible implementation manner further provide an implementation manner, and the dynamic energy flow model of the heat users of the building with the heat radiator in the step (2) is specifically: establishing a heat transfer differential equation of a heat user of a building with a radiator through a first thermodynamic law;
Tr,Td,Ta,Tsawall of radiator, internal fluid, indoor and outdoor integrated temperature, unit: k;
Cr,Cd,Caheat capacity of radiator wall, internal fluid and indoor air, J/K;
heat capacity is calculated by C ═ mc, where m is mass, in units: kg, c is the specific heat capacity of the material, unit: j/(kg. K);
Gdheat capacity flow of radiator fluid, unit: W/K;
heat capacity flow is given by the formula G ═ vmc calculation of where vmIs the mass flow rate of the fluid, unit: kg/s; c is the specific heat capacity of the fluid, in units: j/(kg. K);
kd,kathe convective heat transfer coefficient of the wall surface of the radiator, the internal fluid and the indoor air is as follows, unit: w/(m)2·K)；
i(i 1-4) maintaining the thickness of the structural material of each layer, unit: m;
λw,λi(i 1-4) heat conductivity coefficient of the wall surface of the radiator and each layer maintenance structure material, unit: W/(m.K);
hi(i-1, 2) heat convection coefficient of wall and indoor and outdoor air, unit: w/(m)2·K)；
Ad,AaA is the heat exchange area between the wall surface of the radiator and the internal fluid, the heat exchange area between the indoor air and the external wall and the heat exchange area between the indoor air and the external wall, the unit is as follows: m is2。
The above-mentioned aspects and any possible implementation manners further provide an implementation manner, in the step (2), the differential equation of heat transfer of the building heat consumer with the heat sink is simplified and integrated, and a theory of thermoelectric comparison is combined, the temperature difference is compared with a driving potential, the heat exchange amount is compared with a current, a ratio between the temperature difference and the heat exchange amount is compared with a heat transfer resistance, and the heat capacity is compared with a capacitance, and the differential equation of heat transfer of the building heat consumer with the heat sink can be rewritten as:
Td,in(t) radiator fluid inlet temperature units: k;
Rdequivalent heat transfer resistance between the wall surface of the radiator and fluid in the radiator, unit: K/W; the heat transfer thermal resistance is
Calculation of where ad＝(kA)d/Gd；
RaEquivalent heat transfer resistance of the wall surface of the radiator and indoor air, unit: K/W; the heat transfer resistance is represented by Ra＝1/(kA)aCalculating;
Rsaequivalent heat transfer resistance of indoor air and outdoor air, unit: K/W; the heat transfer thermal resistance is
And (4) calculating.
The above aspect and any possible implementation manner further provide a heating system dynamic model, where the dynamic model includes:
the buried pipeline dynamic energy flow model is used for describing a heat exchange process in the buried pipeline;
the heat exchanger dynamic energy flow model is used for describing a heat exchange process in the heat exchanger;
a radiator-containing building thermal user energy flow model for describing a heat exchange process in a radiator-containing building thermal user;
and the dynamic model combines outdoor meteorological parameters to connect the direct buried pipeline dynamic energy flow model, the heat exchanger dynamic energy flow model and the heat user dynamic energy flow model of the building with the radiator into a heat supply system dynamic model according to the topological structure of the central heat supply system.
The above aspect and any possible implementation manner further provide a heating system dynamic regulation and control system, where the system includes:
the data acquisition module is used for acquiring outdoor meteorological parameters, a topological structure of the central heating system and operation condition test data;
the heat supply system dynamic representation module describes the dynamic transfer process of heat from a network side to a user side through a heat supply system dynamic model, and comprises: the system comprises a direct buried pipeline dynamic energy flow model, a heat exchanger dynamic energy flow model and a building thermal user energy flow model with a radiator;
and the dynamic regulation and control module evaluates delay and loss of heat in each part during transmission through the heat supply system dynamic representation module, and performs scheduling control on the centralized heat supply system according to dynamic characteristics of the whole process of transporting the heat from the source side to the user side obtained through analysis.
Compared with the prior art, the invention can obtain the following technical effects:
1. the scale of a centralized heating system is large, and related pipelines, heat exchangers and heat users are numerous, the dynamic energy flow model of the directly-buried pipeline, the heat exchanger and the building heat users is established based on an energy flow method, so that the delay and loss of heat in the transmission of each part can be accurately estimated;
2. the invention can analyze the dynamic characteristics of the whole process of heat transmission from the source side to the user side on the basis of the technical effects, provides accurate data for the dispatching control of the centralized heating system, and can effectively solve the problem of uneven cooling and heating caused by unequal lengths of pipelines from the heat exchange stations to heat users.
Of course, it is not necessary for any one product in which the invention is practiced to achieve all of the above-described technical effects simultaneously.
[ description of the drawings ]
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed 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 to obtain other drawings based on these drawings without creative efforts.
FIG. 1 is a schematic diagram of a central heating system according to the present invention;
FIG. 2 is a schematic view of the structure of a buried pipeline in embodiment 1;
FIG. 3 is the equivalent thermal resistance network diagram of the buried pipeline in the embodiment 1;
FIG. 4 is a schematic view of the heat exchanger according to embodiment 1;
FIG. 5 is a diagram of an equivalent thermal resistance network of a heat exchanger in example 1;
FIG. 6 is a schematic view showing a structure of a heat consumer of a building including a radiator according to example 1;
FIG. 7 is a diagram of equivalent thermal resistance network for the heat users of the building containing the heat sink in example 1;
fig. 8 is a graph of outdoor integrated air temperature and indoor air temperature based on the modeling simulation of the present invention in example 2.
[ detailed description ] embodiments
For better understanding of the technical solutions of the present invention, the following detailed descriptions of the embodiments of the present invention are provided with reference to the accompanying drawings.
It should be understood that the described embodiments are only some embodiments of the invention, and not all 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 terminology used in the embodiments of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used in the examples of the present invention and the appended claims, the singular forms "a," "an," and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise.
As shown in fig. 2 to 7, a method of constructing a district heating system model according to the present invention includes the steps of:
calculating the comprehensive temperature of the outdoor air: the outer surface of the building maintenance structure is subjected to solar radiation in addition to heat exchange with outdoor air due to temperature difference. In order to simplify the calculation, the combined action of the enclosure structure, the convection heat exchange of outdoor air and the reception of solar radiation can be converted into an outdoor meteorological parameter:
Tsathe comprehensive temperature of outdoor air, K;
Ta,outoutdoor air temperature, K;
rho is the radiation absorption coefficient of the outer surface of the enclosure structure and is less than 1;
i solar radiation intensity, W/m2；
ha,outThe convective heat transfer coefficient between the enclosure structure and the outdoor air, W/(m)2·K)。
Establishing a dynamic energy flow model of the directly buried pipeline: establishing a heat transfer differential equation of the directly buried pipeline by applying a first thermodynamic law:
Td,Tp,Tstemperature of fluid in the pipe, pipe wall and soil surface, K;
Cd,Cpin-tube flowBody and wall heat capacity, J/K. The heat capacity is calculated by C ═ mc, where m is the mass of the material, kg, C is the specific heat capacity of the material, J/(kg · K);
Gdfluid heat capacity flow, W/K. Heat capacity flow is given by the formula G ═ vmc calculation of where vmMass flow of the fluid, kg/s; c is the specific heat capacity of the fluid, J/(kg. K);
k is the convective heat transfer coefficient between the fluid and the tube wall, W/(m)2·K)；
i(i ═ 1,2,3) insulation, insulation shell and soil thickness, m;
λp,λi(i ═ 1,2,3) thermal conductivity of pipe wall, insulation shell and soil, W/(m.K);
A,Ai( i 1,2,3) heat exchange area between adjacent two layers of fluid in pipe, pipe wall, heat-insulating layer shell and soil, m2。
Furthermore, the heat transfer differential equation of the directly buried pipeline is simplified and integrated, and is combined with a thermoelectric analogy theory, the temperature difference is compared with the potential difference, the heat exchange quantity is compared with the current, the ratio of the temperature difference to the heat exchange quantity is compared with the resistance, and the heat capacity is compared with the capacitance, and the heat transfer differential equation of the directly buried pipeline can be rewritten as follows:
Td,in(t) the pipe inlet fluid temperature, K;
Rdequivalent heat transfer resistance, K/W, of the fluid in the pipe and the wall surface of the pipe. The heat transfer thermal resistance is
Calculation of where ad＝(kA)d/Gd；
RsThe equivalent heat transfer resistance, K/W, of the wall surface of the pipeline and the soil. The heat transfer thermal resistance is
And (4) calculating.
Establishing a heat exchanger dynamic energy flow model: establishing a heat transfer differential equation of the heat exchanger by applying a first thermodynamic law:
Tc,Th,Twcold fluid, hot fluid and heat exchanger wall temperature, K;
Cc,Ch,Cwhot cooling fluid in the heat exchanger and wall surface heat capacity, J/K. The heat capacity is calculated by C ═ mc, where m is the mass of the material, kg, C is the specific heat capacity of the material, J/(kg · K);
Gc,Ghthe heat capacity flow of the cold and hot fluid, W/K. Heat capacity flow is given by the formula G ═ vmc, calculating, wherein vm is the mass flow of the fluid, kg/s; c is the specific heat capacity of the fluid, J/(kg. K);
kc,khconvection heat transfer coefficient between cold and hot fluid and wall surface of heat exchanger, W/(m)2·K)；
λwThe heat conductivity coefficient of the wall surface of the heat exchanger, W/(m.K);
Ac,Ahthe heat exchange area between the cold and hot fluid and the wall of the heat exchanger, m2。
Further, the heat transfer differential equation of the heat exchanger is simplified and integrated, and is combined with a thermoelectric analogy theory, the temperature difference is compared with the driving potential, the heat exchange quantity is compared with the current, the ratio between the temperature difference and the heat exchange quantity is compared with the heat transfer resistance, and the heat capacity is compared with the capacitance, and the heat transfer differential equation of the heat exchanger can be rewritten as follows:
Tc,in(t),Th,in(t) heat exchanger cold fluid inlet temperature, hot fluid inlet temperature, K;
Rhequivalent heat transfer resistance, K/W, of the hot fluid and the wall surface of the heat exchanger. The heat transfer thermal resistance is
Calculation of where ah＝(kA)h/Gh；
RcEquivalent heat transfer resistance, K/W, of the heat exchanger wall and the cold fluid. The heat transfer thermal resistance is
Calculation of where ac＝(kA)c/Gc。
Building a heat user dynamic energy flow model of a building with a radiator: establishing a heat transfer differential equation of a heat user of a building with a radiator by applying a first thermodynamic law:
Tr,Td,Ta,Tsathe wall surface of the radiator, the internal fluid, the indoor and outdoor comprehensive temperature, K;
Cr,Cd,Caheat capacity of radiator wall, internal fluid and indoor air, J/K. The heat capacity is calculated by C ═ mc, where m is the mass of the material, kg, C is the specific heat capacity of the material, J/(kg · K);
Gdheat capacity flow of radiator fluid, W/K. Heat capacity flow is given by the formula G ═ vmc calculation of where vmMass flow of the fluid, kg/s; c. CIs the specific heat capacity of the fluid, J/(kg. K);
kd,kaconvection heat transfer coefficient of wall surface of radiator, internal fluid and indoor air, W/(m)2·K)；
i(i 1-4) maintaining the thickness of the structural material m in each layer;
λw,λi(i 1-4) heat conductivity of the heat sink wall surface and each layer maintenance structure material, W/(m.K);
hi(i ═ 1,2) convective heat transfer coefficient between wall and indoor and outdoor air, W/(m)2·K)；
Ad,AaA is the heat exchange area between the wall surface of the radiator and the internal fluid and the indoor air and the heat exchange area between the indoor air and the external wall, m2。
Further, the differential equation of heat transfer of the building heat user with the heat radiator is simplified and integrated, and is combined with a thermoelectric simulation theory, the temperature difference is simulated as a driving potential, the heat exchange quantity is simulated as a current, the ratio between the temperature difference and the heat exchange quantity is simulated as a heat transfer resistance, and the heat capacity is simulated as a capacitance, and the differential equation of the building heat user with the heat radiator can be rewritten as follows:
Td,in(t) radiator fluid inlet temperature, K;
Rdthe equivalent heat transfer resistance, K/W, between the wall of the radiator and the fluid in the radiator. The heat transfer thermal resistance is
Calculation of where ad＝(kA)d/Gd；
RaEquivalent heat transfer resistance, K/W, of the wall of the radiator and the indoor air. The heat transfer resistance is represented by Ra＝1/(kA)aCalculating;
Rsaequivalent heat transfer resistance, K/W, of indoor air and outdoor air. The heat transfer thermal resistance is
And (4) calculating.
The invention also provides a heating system dynamic model based on the method, and the dynamic model comprises the following steps:
the buried pipeline dynamic energy flow model is used for describing a heat exchange process in the buried pipeline;
the heat exchanger dynamic energy flow model is used for describing a heat exchange process in the heat exchanger;
a radiator-containing building thermal user energy flow model for describing a heat exchange process in a radiator-containing building thermal user;
and the dynamic model combines outdoor meteorological parameters to connect the direct buried pipeline dynamic energy flow model, the heat exchanger dynamic energy flow model and the heat user dynamic energy flow model of the building with the radiator into a heat supply system dynamic model according to the topological structure of the central heat supply system.
The invention also comprises a heating system dynamic regulation and control system, which comprises the dynamic model, and the system comprises:
the data acquisition module is used for acquiring outdoor meteorological parameters, a topological structure of the central heating system and operation condition test data;
the heat supply system dynamic representation module describes the dynamic transfer process of heat from a network side to a user side through a heat supply system dynamic model, and comprises: the system comprises a direct buried pipeline dynamic energy flow model, a heat exchanger dynamic energy flow model and a building thermal user energy flow model with a radiator;
the dynamic regulation and control module evaluates delay and loss of heat in each part during transmission through the heat supply system dynamic representation module, and schedules and controls the central heat supply system according to the dynamic characteristics of the whole process of transporting the heat from the source side to the user side obtained through analysis
Example 2
To make sure thatExample 2 illustrates how the component energy flow model of example 1 can be used to build a dynamic energy flow model for a district heating system. As shown in figure 1, a simulated primary heating power pipe network is a single heat source branched pipe network and comprises 2 secondary heat exchange stations, the heat exchange stations adopt a counter-flow plate type heat exchanger for heat exchange, the nominal diameter of a pipeline adopted by the primary pipe network is 300mm, the length of the pipeline is 2km, the designed flow rate is 0.6m/s, the designed water supply and return temperature is 125/70 ℃, the nominal diameter of a pipeline adopted by the secondary network is 150mm, the designed flow rate is 1.6m/s, the designed water supply and return temperature is 65/45 ℃, each secondary network is responsible for the heat load of 5 buildings, and the heat supply radius is 310m2Wherein each building has 11 floors, and the total building area is 23703.3m2Then the heat supply area of each secondary net is 118516.5m2. Because the length of the secondary network pipeline is short, the delay and the loss of the heat transmission of the secondary network pipeline are not considered in the embodiment. In addition, in the embodiment, the heat load of a single room is calculated first and then converted into the heat load of a building, rather than modeling the whole building as a whole, so as to ensure that the rise time of the indoor temperature of the building meets the real situation. Under the above conditions, the calculation of the comprehensive outdoor air temperature and the building indoor air temperature from 11 months to 20 days in 2019 according to the present invention is shown in fig. 8.
Because the operation parameters of the radiator are not changed in the simulation process, the variation trend of the indoor air temperature is completely the same as that of the comprehensive outdoor air temperature, when the comprehensive outdoor air temperature rises, the heat required for maintaining the indoor design temperature is reduced, and the power of the radiator is kept unchanged, so that the indoor air temperature rises; when the integrated outdoor air temperature is lowered, the amount of heat required to maintain the indoor design temperature is increased while the power of the radiator is maintained, so the indoor air temperature is lowered, and fig. 8 shows that the rise time of the indoor air of the building is close to 128min, which is in accordance with the actual situation.
Because the scale of the centralized heating system is large, and related pipelines, heat exchangers and heat users are numerous, the invention establishes a dynamic energy flow model of the directly buried pipelines, the heat exchangers and the building heat users based on an energy flow method, and can accurately evaluate the delay and loss of heat in each part during transmission. The invention can analyze the dynamic characteristics of the whole process of heat transmission from the source side to the user side, provides accurate data for the dispatching control of the centralized heating system, and can effectively solve the problem of uneven cooling and heating caused by unequal lengths of pipelines from the heat exchange stations to heat users.
The method, the model and the regulation and control system for dynamically modeling the heating system provided by the embodiment of the application are introduced in detail. The above description of the embodiments is only for the purpose of helping to understand the method of the present application and its core ideas; meanwhile, for a person skilled in the art, according to the idea of the present application, there may be variations in the specific embodiments and the application scope, and in summary, the content of the present specification should not be construed as a limitation to the present application.
As used in the specification and claims, certain terms are used to refer to particular components. As one skilled in the art will appreciate, manufacturers may refer to a component by different names. This specification and claims do not intend to distinguish between components that differ in name but not function. In the following description and in the claims, the terms "include" and "comprise" are used in an open-ended fashion, and thus should be interpreted to mean "include, but not limited to. "substantially" means within an acceptable error range, and a person skilled in the art can solve the technical problem within a certain error range to substantially achieve the technical effect. The description which follows is a preferred embodiment of the present application, but is made for the purpose of illustrating the general principles of the application and not for the purpose of limiting the scope of the application. The protection scope of the present application shall be subject to the definitions of the appended claims.
It is also noted that the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a good or system that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such good or system. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other like elements in a commodity or system that includes the element.
It should be understood that the term "and/or" as used herein is merely one type of association that describes an associated object, meaning that three relationships may exist, e.g., a and/or B may mean: a exists alone, A and B exist simultaneously, and B exists alone. In addition, the character "/" herein generally indicates that the former and latter related objects are in an "or" relationship.
The foregoing description shows and describes several preferred embodiments of the present application, but as aforementioned, it is to be understood that the application is not limited to the forms disclosed herein, but is not to be construed as excluding other embodiments and is capable of use in various other combinations, modifications, and environments and is capable of changes within the scope of the application as described herein, commensurate with the above teachings, or the skill or knowledge of the relevant art. And that modifications and variations may be effected by those skilled in the art without departing from the spirit and scope of the application, which is to be protected by the claims appended hereto.
Claims (10)
1. A heating system dynamic modeling method is characterized by comprising the following steps:
(1) acquiring outdoor meteorological parameters, a topological structure of a centralized heating system and operation condition test data;
(2) establishing dynamic energy flow models of a direct-buried pipeline, a heat exchanger and a heat user containing a radiator in a centralized heating system by adopting an energy flow method, wherein the dynamic energy flow models are respectively used for describing heat exchange processes of the direct-buried pipeline, the heat exchanger and the heat user containing the radiator in a building;
(3) and combining outdoor meteorological parameters, connecting the built energy flow models of the direct buried pipeline, the heat exchanger and the building heat users containing the radiator into a dynamic energy flow model of a central heating system according to the obtained topological structure, and further describing the dynamic transfer process of heat from the network side to the user side.
2. The method of claim 1, wherein the outdoor weather-meteorological parameters include hours, temperature, and solar radiation intensity, converted to an outdoor air integrated temperature:
wherein, TsaThe comprehensive temperature of outdoor air, unit: k;
Ta,outoutdoor air temperature, unit: k;
rho is the radiation absorption coefficient of the outer surface of the enclosure structure and is less than 1;
solar radiation intensity, unit: w/m2；
ha,outThe convective heat transfer coefficient of the building envelope and outdoor air, unit: w/(m)2·K)。
3. The method according to claim 2, wherein the dynamic energy flow model building method for building the directly buried pipeline in the central heating system by using the energy flow method in the step (2) is as follows: establishing a heat transfer differential equation of the directly buried pipeline through a first thermodynamic law;
wherein, Td,Tp,TsThe temperature of the fluid in the pipe, the pipe wall and the soil surface, unit: k;
Cd,Cpthe heat capacity of the fluid in the pipe and the pipe wall is as follows: KJ/K;
the heat capacity is calculated by C ═ mc, where m is the mass of the material, kg, C is the specific heat capacity of the material, J/(kg · K);
Gdfluid heat capacity flow, unit: KW/K;
heat capacity flow through formulaG＝vmc calculation of where vmIs the mass flow rate of the fluid, unit: kg/s; c is the specific heat capacity of the fluid, J/(kg. K);
k is the convective heat transfer coefficient between the fluid and the pipe wall, unit: KW/(m)2·K)；
i(i ═ 1,2,3) insulation, insulation shell and soil thickness, units: km;
λp,λi(i ═ 1,2,3) coefficients of thermal conductivity of pipe wall, insulation shell and soil, in units: KW/(m.K);
A,Ai(i 1,2,3) heat exchange area between adjacent two layers of fluid in the pipe, pipe wall, heat insulation layer shell and soil, unit: km2。
4. The method according to claim 3, wherein the step (2) of simplifying and integrating the heat transfer differential equation of the buried pipeline and combining the thermoelectric simulation theory, the temperature difference is simulated as a potential difference, the heat exchange quantity is simulated as a current, the ratio of the temperature difference and the heat exchange quantity is simulated as a resistance, and the heat capacity is simulated as a capacitance, and the heat transfer differential equation of the buried pipeline is rewritten as:
wherein, Td,in(t) pipe inlet fluid temperature, in units: k;
Rdequivalent heat transfer resistance of fluid in the pipe and the wall surface of the pipeline, unit: K/W, the heat transfer resistance is
Calculation of where ad＝(kA)d/Gd；
RsEquivalent heat transfer resistance of the pipeline wall surface and soil, unit: K/W, the heat transfer resistance is
And (4) calculating.
5. The method according to claim 4, wherein the dynamic energy flow model of the heat exchanger in the step (2) is specifically: establishing a heat transfer differential equation of the heat exchanger through a first thermodynamic law:
Tc,Th,Twcold fluid, hot fluid and heat exchanger wall temperature, unit: k;
Cc,Ch,Cwthe internal cooling and heating fluid and wall surface heat capacity of the heat exchanger are as follows: J/K;
heat capacity is calculated by C ═ mc, where m is mass of material, kg, C is mass specific heat capacity, in units: j/(kg. K);
Gc,Ghthe heat capacity flow of cold and hot fluid, unit: W/K;
heat capacity flow is given by the formula G ═ vmc calculation of where vmIs the mass flow rate of the fluid, unit: kg/s; c is the specific heat capacity of the fluid, in units: j/(kg. K);
kc,khthe convective heat transfer coefficient between cold and hot fluid and the wall surface of the heat exchanger, unit: w/(m)2·K)；
λwThe heat conductivity coefficient of the wall surface of the heat exchanger, unit: W/(m.K);
Ac,Ahthe heat exchange area between the cold and hot fluid and the wall surface of the heat exchanger, unit: m is2。
6. The method according to claim 5, wherein the heat exchanger heat transfer differential equation in step (2) is simplified and integrated, and in combination with a thermoelectric analogy theory, a temperature difference is compared with a driving potential, a heat exchange amount is compared with a current, a ratio between the temperature difference and the heat exchange amount is compared with a heat transfer resistance, and a heat capacity is compared with a capacitance, and the heat exchanger heat transfer differential equation is rewritten as follows:
Tc,in(t),Th,in(t) heat exchanger cold fluid inlet temperature, hot fluid inlet temperature, in units: k;
Rhequivalent heat transfer thermal resistance of hot fluid and the wall surface of a heat exchanger, unit: K/W; the heat transfer thermal resistance is
Calculation of where ah＝(kA)h/Gh；
RcEquivalent heat transfer resistance of the wall surface of the heat exchanger and the cold fluid, unit: K/W; the heat transfer thermal resistance is
Calculation of where ac＝(kA)c/Gc。
7. The method according to claim 5, wherein the dynamic energy flow model of the heat users of the building with radiators in step (2) is specifically: establishing a heat transfer differential equation of a heat user of a building with a radiator through a first thermodynamic law;
Tr,Td,Ta,Tsawall of radiator, internal fluid, indoor and outdoor integrated temperature, unit: k;
Cr,Cd,Caheat capacity of radiator wall, internal fluid and indoor air, J/K;
Gdheat capacity flow of radiator fluid, unit: W/K;
kd,kathe convective heat transfer coefficient of the wall surface of the radiator, the internal fluid and the indoor air is as follows, unit: w/(m)2·K)；
i(i 1-4) maintaining the thickness of the structural material of each layer, unit: m;
λw,λi(i 1-4) heat conductivity coefficient of the wall surface of the radiator and each layer maintenance structure material, unit: W/(m.K);
hi(i-1, 2) heat convection coefficient of wall and indoor and outdoor air, unit: w/(m)2·K)；
Ad,AaA is the heat exchange area between the wall surface of the radiator and the internal fluid, the heat exchange area between the indoor air and the external wall and the heat exchange area between the indoor air and the external wall, the unit is as follows: m is2。
8. The method according to claim 7, wherein the heat transfer differential equation of the building heat consumer with the heat radiator in the step (2) is simplified and integrated, and is combined with a theory of thermal-electric analogy, and the temperature difference is compared with the driving potential, the heat exchange quantity is compared with the current, the ratio between the temperature difference and the heat exchange quantity is compared with the heat transfer resistance, and the heat capacity is compared with the capacitance, and the heat transfer differential equation of the building heat consumer with the heat radiator can be rewritten as follows:
Td,in(t) radiator fluid inlet temperature units: k;
Rdequivalent heat transfer resistance between the wall surface of the radiator and fluid in the radiator, unit: K/W; the heat transfer thermal resistance is
Calculation of where ad＝(kA)d/Gd；
RaEquivalent heat transfer resistance of the wall surface of the radiator and indoor air, unit: K/W; the heat transfer resistance is represented by Ra＝1/(kA)aCalculating;
Rsaequivalent heat transfer resistance of indoor air and outdoor air, unit: K/W; the heat transfer thermal resistance is
And (4) calculating.
9. A heating system dynamic model comprising the method of any of claims 1 to 8, wherein the dynamic model comprises:
the buried pipeline dynamic energy flow model is used for describing a heat exchange process in the buried pipeline;
the heat exchanger dynamic energy flow model is used for describing a heat exchange process in the heat exchanger;
a radiator-containing building thermal user energy flow model for describing a heat exchange process in a radiator-containing building thermal user;
and the dynamic model combines outdoor meteorological parameters to connect the direct buried pipeline dynamic energy flow model, the heat exchanger dynamic energy flow model and the heat user dynamic energy flow model of the building with the radiator into a heat supply system dynamic model according to the topological structure of the central heat supply system.
10. A heating system dynamic regulation system comprising the dynamic model of claim 9, wherein the system comprises:
the data acquisition module is used for acquiring outdoor meteorological parameters, a topological structure of the central heating system and operation condition test data;
the heat supply system dynamic representation module describes the dynamic transfer process of heat from a network side to a user side through a heat supply system dynamic model, and comprises: the system comprises a direct buried pipeline dynamic energy flow model, a heat exchanger dynamic energy flow model and a building thermal user energy flow model with a radiator;
and the dynamic regulation and control module evaluates delay and loss of heat in each part during transmission through the heat supply system dynamic representation module, and performs scheduling control on the centralized heat supply system according to dynamic characteristics of the whole process of transporting the heat from the source side to the user side obtained through analysis.
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