CN109028609B - Design method for series-parallel arrangement of flat plate type solar heat collector array - Google Patents
Design method for series-parallel arrangement of flat plate type solar heat collector array Download PDFInfo
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Abstract
The invention discloses a serial-parallel connection arrangement design method of a flat plate type solar heat collector array, which comprises the steps of firstly calculating the heat collection efficiency and the heat collection quantity of a single heat collector according to time-by-time environmental parameters in the operation time period of the heat collector, secondly calculating the heat collection performance of the heat collector array in different serial-parallel connection modes by taking the thermal performance calculation result of the single heat collector as the basis, and optimizing the arrangement design of the heat collector by integrating the influences and economic effects of the heat collection quantity, the heat collection efficiency and the resistance of different arrays to determine the optimal arrangement scheme. The method can calculate the heat collection and heat collection efficiency of the series heat collector set according to the solar irradiance, the outdoor air temperature, the heat collection medium inlet temperature and the heat collection medium circulation flow. And calculating to obtain the dynamic thermal performance of the heat collector arrays with different serial numbers according to the time-by-time meteorological parameters, and optimally designing the arrangement mode of the flat-plate type solar heat collection arrays by respectively taking the annual cost value and the system power consumption as objective functions.
Description
Technical Field
The invention relates to the technical field of solar heat utilization, in particular to a design method for series-parallel arrangement of a flat-plate solar heat collector array applied to building heating.
Background
Solar energy is used as a clean, renewable and sustainable energy source and has extremely high utilization value. Solar heating systems are developed more and more mature in China. The flat-plate solar heat collector has simple structure and low manufacturing cost, is the leading product in the heat collector market in China and is widely applied to solar heating systems.
Some western remote areas in China have vigorous heat supply requirements, but a traditional large-scale centralized heat supply system is difficult to set due to the limitation of the economic development level, but the areas have abundant solar energy resources, and are suitable for building a large-scale solar centralized heat supply system to meet the requirements of heat users. The heat collection effect and the system economy of the large-scale solar heat collector are in great relation with the arrangement mode of the heat collector array, so that the production and living environment of residents in western regions can be improved and the development of a solar central heating system can be promoted if the arrangement problem of the large-scale solar heat collector array can be solved.
The existing heat collector array calculation and arrangement method has two defects, firstly, based on static analysis, only the uniformity of flow distribution and the thermal performance of a heat collector are concerned, and the influence of the change of the heat collection quantity and the heat collection efficiency of the heat collection array in the whole heating season along with the change of the meteorological conditions such as irradiation, ambient temperature and the like is not considered; and secondly, only the influence of heat collection is considered in the arrangement and arrangement process of the heat collector array, and the influence of economic benefits brought by different arrangement and arrangement modes in actual engineering is neglected.
Disclosure of Invention
In order to solve the problems in the prior art, the invention provides a serial-parallel arrangement design method for a flat plate type solar heat collector array, which solves the problems of low arrangement heat collection effect and low system economy of the heat collector in the prior art.
The technical scheme of the invention is as follows: a design method for serial and parallel arrangement of a flat plate type solar heat collector array comprises the following steps:
(1) establishing a heat transfer mathematical model of a single flat-plate solar collector based on heat transfer science and a control volume balance method, solving the heat transfer model by utilizing Matlab software, inputting the inlet temperature and the flow of a heat collecting medium, and calculating the outlet temperature and the heat collecting efficiency of the heat collecting medium;
(2) calling a heat transfer mathematical model of a single flat-plate solar collector, inputting environmental parameters, heat collection medium inlet parameters and the number of the series-connected flat-plate solar collectors, and calculating to obtain the heat collection amount of the flat-plate solar collectors with different series-connected numbers under the hourly meteorological parameters;
(3) determining the parallel number required by the heat collector groups with different series numbers under the condition of meeting the heat demand of a heat user;
(4) the method is characterized in that the cost annual value of a heat collector array is used as an objective function to carry out optimization design on the arrangement of the heat collector array, and the arrangement scheme of the flat-plate type solar heat collector array with the lowest cost annual value is used as an optimization scheme.
The invention has the beneficial effects that:
(1) according to the method, under the condition of inputting outdoor weather time-by-time parameters, the time-by-time heat collection and heat collection efficiency of a single heat collector along with the change of outdoor environment parameters can be calculated;
(2) the method can calculate the hourly heat collection and heat collection efficiency of the heat collector array under different serial and parallel numbers, and can determine the heat collector array arrangement mode with the maximum heat collection effect according to the application site area and the user requirements;
(3) the method comprehensively considers the heat collection effect and the annual cost value of the large flat plate heat collector array, and obtains the optimal arrangement mode of the flat plate solar heat collector array under the condition of ensuring the heat demand and the economy of users.
The method can calculate the heat collection and heat collection efficiency of the series heat collector set according to the solar irradiance, the outdoor air temperature, the heat collection medium inlet temperature and the heat collection medium circulation flow. And calculating to obtain the dynamic thermal performance of the heat collector arrays with different serial numbers according to the time-by-time meteorological parameters, and optimally designing the arrangement mode of the flat-plate type solar heat collection arrays by respectively taking the annual cost value and the system power consumption as objective functions.
Drawings
FIG. 1 is a schematic view of the heat collector;
FIG. 2 is a schematic diagram of coordinate axis creation;
FIG. 3 is a flow chart of thermal performance calculation for a heat collector;
FIG. 4 illustrates a series collector group thermal performance calculation process;
FIG. 5 is a schematic view of the connection of heat collecting pipes;
wherein: 1-a glass cover plate; 2-an air layer; 3-heat collecting plate; 4-working medium; 5-insulating layer; 6-outer shell.
Detailed Description
1. Mathematical model for establishing thermal performance of flat-plate solar collector
A mathematical model of the flat plate type solar collector is established based on a control volume balance method, a single flat plate collector can be structurally divided into five parts shown in the attached drawing 1-1, namely a glass cover plate 1, and the lower corner of a related variable is marked as c; an air layer 2; the collector panel 3, the lower angle of the relevant variable is marked as p; working medium 4, the lower corner of the related variable is marked as l; a heat-insulating layer 5; the shell 6, the lower corner of the relevant variable is marked s.
The heat transfer process of the heat collector model is divided into the following parts:
(1) both the glass cover plate and the heat collecting plate absorb solar radiation;
(2) the glass cover plate, the shell and the environment are subjected to radiation heat exchange;
(3) natural convection heat exchange is carried out on air between the glass cover plate and the heat collecting plate, and convection heat exchange is carried out between the glass cover plate and the shell and the external environment and between the working medium flow passage and the working medium;
(4) the glass cover plate, the heat collection plate, the working medium and the shell conduct heat along the x direction, and heat is conducted between the heat collection plate and the shell;
(5) the working medium in the working medium flow passage carries away heat in a convection way.
Discretization of the calculation region is performed, i.e. dividing the control volume, which is the smallest geometrical unit to which the control equations are applied. The working medium is divided into (n +1) control bodies along the flowing direction of the working medium, namely the direction x, in one dimension, the node of each control body is positioned at the center of the control body, and the length of the control body is delta x, as shown in the attached figure 1-2. The following steady-state thermal balance node equation set is established according to the energy balance principle,
1) thermal equilibrium equation of glass cover plate
Sc(i)+qcond,c(i)+qconv,c-p(i)+qrad,c-p(i)-qconv,c-a(i)-qrad,c-a(i)＝0 (1)
Sc(i)＝αcIcWΔx (2)
qconv,c-a(i)＝hconv,c-a[Tc(i)-Ta]WΔx (3)
qconv,c-p(i)＝hconv,c-p[Tp(i)-Tc(i)]WΔx (4)
qrad,c-p＝hrad,c-p[Tp(i)-Tc(i)]WΔx (6)
In the formula: sc(i) -solar radiation absorbed by the glass cover plate inode; q. q.sconv,c-a(i) -the convective heat transfer between the glass cover plate i-node and the external environment; q. q.sconv,c-p(i) The natural convection heat exchange quantity of the air interlayer between the i-node of the glass cover plate and the i-node of the heat collecting plate is realized; q. q.srad,c-a(i) The radiation heat exchange quantity between the glass cover plate i node and the external environment; q. q.srad,c-p(i) The radiation heat exchange quantity of the i node of the glass cover plate and the heat collecting plate is measured; q. q.scond,c(i) Heat transfer from glass cover plate node i to node i-1 and node i +1 αc-the solar radiation absorption of the glass cover plate; i iscIlluminance of solar radiation, W/m2(ii) a W is the corresponding width of a single flow channel of the heat collecting plate, m; h isconv,c-a-convective heat transfer coefficient between the glass cover plate and the external environment, W/(m)2·K)；hconv,c-pThe natural convection heat transfer coefficient of the air interlayer, W/(m)2·K)；εc-glass cover plate surface emissivity; sigmasb-boltzmann's constant; t issky-the sky temperature, K; h israd,c-pRadiation heat exchange coefficient between the glass cover plate and the heat collecting plate, W/(m)2·K)；δc-glass cover plate thickness, m; lambda [ alpha ]cThe thermal conductivity of the glass cover plate, W/(m.K).
2) Heat balance equation of heat collecting plate
Sp(i)+qcond,p(i)-qconv,c-p(i)-qrad,c-p(i)-qcond,p-s(i)-qconv,p-l(i)＝0 (8)
Sp(i)＝τcαpIcWΔx (9)
qconv,p-l(i)＝2πRΔxhp-l[Tp(i)-Tl(i)](11)
In the formula: sp(i) -solar radiation absorbed by the collector panel inode; q. q.scond,p(i) The heat conduction of the node i of the heat collection plate, the node i-1 and the node i + 1; q. q.sconv,c-p(i) The natural convection heat exchange quantity of the air interlayer between the i-node of the glass cover plate and the i-node of the heat collecting plate is realized; q. q.srad,c-p(i) The radiant heat exchange between the glass cover plate node i and the heat collecting plate node i; q. q.scond,p-s(i) The heat conduction between the i-node of the heat collecting plate and the i-node of the shell is realized; q. q.sconv,p-l(i) The heat exchange amount by convection between the node i of the heat collecting plate and the node i of the fluid working medium; tau iscSolar radiation transmittance of glass cover plate αp-the solar radiation absorption of the glass cover plate; deltap-thickness of the collector plate, m; lambda [ alpha ]p-heat collection plate thermal conductivity, W/(m · K); h isp-l-convective heat transfer coefficient between pipe wall and working medium, W/(m)2K); r-inner diameter of pipe, m; deltab-thickness of the insulation layer, m; lambda [ alpha ]bThe thermal conductivity coefficient of the insulating layer, W/(m.K).
3) Heat balance equation of fluid working medium
qconv,l(i)＝qcond,l(i)+qconv,p-l(i) (13)
In the formula: q. q.sconv,l(i) -heat carried away by thermal convection of the fluid working medium i-node; q. q.scond,l(i) The heat conduction of the fluid working medium i node, the i-1 node and the i +1 node; q. q.sconv,p-l(i) The heat exchange amount by convection between the node i of the heat collecting plate and the node i of the fluid working medium; rholDensity of the fluid working medium, kg/m 3; c. Cp,lThe constant pressure specific heat of the fluid working medium, J/(kg. K).
4) Thermal equilibrium equation of collector shell
qcond,s(i)+qcond,p-s(i)-qconv,s-a(i)-qrad,s-a(i)＝0 (16)
qconv,s-a(i)＝hconv,s-a[Ts(i)-Ta]WΔx (18)
hconv,s-a＝5.7+3.8Vwind(19)
In the formula: q. q.scond，s(i) Heat conduction from the shell i node to the i-1 node and the i +1 node; q. q.scond，p-s(i) -heat transfer between the shell i-node and the heat collecting plate i-node; q. q.sconv，s-a(i) -the convective heat transfer between the shell i-node and the external environment; q. q.srad，s-a(i) -the amount of radiation heat exchange between the shell i-node and the external environment; deltas-shell thickness, m; lambda [ alpha ]s-shell thermal conductivity, W/(m · K); h isconv，s-a-the convective heat transfer coefficient between the housing and the external environment; epsilons-shell surface emissivity.
5) Heat collection and heat collection efficiency of heat collector
Qu＝mcp,l(Tout-Tin) (21)
In the formula: qu-the collector collects heat, W; m is heat collecting medium mass flow rate, kg/s; t isin-collector inlet temperature, K; t isoutCollector outlet temperature, K, η collector efficiency.
2. Solving mathematical model by using Matlab software
And carrying out iterative solution on the established node equation set by utilizing Matlab software, wherein the solution method comprises the following steps:
(1) setting the maximum number of iterations 1 × 106The iteration is prevented from entering a dead loop. Iterative accuracy e is 1 × 10-4。
(2) Assumptions are made about the average temperature of the glass cover plate, the heat collection plates and the housing.
(3) And solving a matrix equation, and calculating the temperature of the glass cover plate, the heat collecting plate and the shell of each node.
(4) Respectively judging the calculated average temperature of the glass cover plate, the average temperature of the heat collecting plate and the average temperature of the shell, namely phi*Whether the differences from the assumed value Φ are both smaller than e.
(5) If yes, the calculation is considered to be converged, the calculation is stopped, and a calculation result is output.
(6) If not, the calculated value is taken as an assumed value, and the matrix equation is solved again for judgment. Until a convergence condition is satisfied.
(7) If the iteration number does not converge after exceeding the maximum iteration number, the calculation is considered not to converge.
(8) And calling a thermal performance calculation model of the single heat collector to calculate the thermal performance of the series heat collector group.
The specific solving process is shown in fig. 3 and fig. 4.
3. Optimization design for heat collector array arrangement
The heat collectors form a solar heat collector system through a certain connection mode, and the connection mode of the heat collectors mainly comprises three modes of series connection, parallel connection and series-parallel connection. The series connection mode means that the outlet of the previous heat collector is connected with the inlet of the next heat collector, and the flow rate of each heat collector is equal; the parallel connection mode is that the inlet and the outlet of the two heat collectors are respectively connected, and the total water flow of the parallel heat collectors is equal to the sum of the water flows of all branches; the series-parallel connection mode is divided into two types: parallel-series connection and series-parallel connection, wherein the parallel-series connection mode is that a plurality of heat collectors are connected in parallel, and all parallel heat collector groups are connected in series again; the series-parallel connection mode is that a plurality of heat collectors are connected in series, and all the heat collector groups connected in series are connected in parallel.
The connection mode adopted by the invention is a series-parallel connection mode shown in figure 5, namely a plurality of heat collectors are firstly connected in series to form a heat collector group, and a plurality of heat collector groups are then connected in parallel to form the whole heat collector array. Finally, the total flow of the heat collector array is equal to the sum of the flows of all the parallel branches, and the total heat collection amount of the heat collector array is equal to the sum of the heat collection amounts of all the heat collectors.
The design variables include the number of series-connected heat collectors in each group, the number of sets of parallel heat collectors required, and the flow rate of each heat collector group. And under the condition of meeting the requirements of users, obtaining a set of results for optimizing the objective function by optimizing the design variables. The number of parallel heat collection sets and the area of the heat collectors in the design variables are calculated by the number of the heat collectors in each set in series, the medium circulation flow rate on the heat collector sets and the annual solar heat collection amount required by users.
And (3) combining the heat demand of a heat user in a heating season, and inputting the serial number and the flow value of the heat collectors in different combinations in a calculation program to obtain the parallel number of the corresponding heat collector arrays. And (3) calculating the initial investment and the operating cost of the system of each combined heat collector array by taking a cost annual value formula (23) of the heat collector arrays as an objective function, and taking the combination of the lowest cost annual value as the arrangement scheme of the optimal flat-plate type solar heat collector array.
Cr＝(N1+N2)×pe(24)
ΔP＝(1+a)×Rm×L+ΔPj(26)
ΔPj＝1.716×1012Q2+6.318×106Q+9.9 (27)
In the formula: c-annual cost value, Yuan; cr-annual operating costs, yuan; c1The cost of the solar heat collecting plate is low; c2The initial investment of the system is fixed, and the cost includes cost of a water pump, a valve, a pipeline and the like; i-equipment discount rate; n-equipment service life; n is a radical of1-power consumption of the solar circulation pump, kJ; n is a radical of2-auxiliary heat source power consumption, kJ; p is a radical ofe-electricity price, yuan/(kWh); qzTotal flow of heat collector tubes, m3S-total hours of operation of the collector, h ηs-water pump efficiency; Δ P-collector array line resistance, Pa; rm-pipe specific friction, Pa/m; l-pipe length, m; a is local equivalent resistance coefficient; delta Pj-local resistance of the collector, Pa; q-collector circulation flow, m3/s。
Although the present invention has been described with reference to the accompanying drawings, the present invention is not limited to the above embodiments, which are only illustrative and not restrictive, and those skilled in the art can make many modifications without departing from the spirit and scope of the present invention as defined in the appended claims.
Claims (3)
1. A design method for serial and parallel arrangement of a flat plate type solar heat collector array is characterized by comprising the following steps:
(1) establishing a heat transfer mathematical model of a single flat-plate solar collector based on heat transfer science and a control volume balance method, solving the heat transfer model by utilizing Matlab software, inputting the inlet temperature and the flow of a heat collecting medium, and calculating the outlet temperature and the heat collecting efficiency of the heat collecting medium;
the single flat-plate solar collector comprises a glass cover plate, an air layer, a heat collecting plate, a working medium, a heat insulating layer and a shell; the heat transfer process of the heat collector model is divided into the following parts:
a. both the glass cover plate and the heat collecting plate absorb solar radiation;
b. the glass cover plate, the shell and the environment are subjected to radiation heat exchange;
c. natural convection heat exchange is carried out on air between the glass cover plate and the heat collecting plate, and convection heat exchange is carried out between the glass cover plate and the shell and the external environment and between the working medium flow passage and the working medium;
d. the glass cover plate, the heat collection plate, the working medium and the shell conduct heat along the x direction, and heat is conducted between the heat collection plate and the shell;
e. the heat is carried away by the convection of working media in the working medium flow channel;
the following steady-state thermal balance node equation set is established according to the energy balance principle,
1) thermal equilibrium equation of glass cover plate
Sc(i)+qcond,c(i)+qconv,c-p(i)+qrad,c-p(i)-qconv,c-a(i)-qrad,c-a(i)＝0 (1)
Sc(i)＝αcIcWΔx (2)
qconv,c-a(i)＝hconv,c-a[Tc(i)-Ta]WΔx (3)
qconv,c-p(i)＝hconv,c-p[Tp(i)-Tc(i)]WΔx (4)
qrad,c-p＝hrad,c-p[Tp(i)-Tc(i)]WΔx (6)
In the formula: sc(i) -solar radiation absorbed by the glass cover plate inode; q. q.sconv,c-a(i) -the convective heat transfer between the glass cover plate i-node and the external environment; q. q.sconv,c-p(i) The natural convection heat exchange quantity of the air interlayer between the i-node of the glass cover plate and the i-node of the heat collecting plate is realized; q. q.srad,c-a(i) The radiation heat exchange quantity between the glass cover plate i node and the external environment; q. q.srad,c-p(i) The radiation heat exchange quantity of the i node of the glass cover plate and the heat collecting plate is measured; q. q.scond,c(i) Heat transfer from glass cover plate node i to node i-1 and node i +1 αc-the solar radiation absorption of the glass cover plate; i iscIlluminance of solar radiation, W/m2(ii) a W is the corresponding width of a single flow channel of the heat collecting plate, m; h isconv,c-a-convective heat transfer coefficient between the glass cover plate and the external environment, W/(m)2·K)；hconv,c-pThe natural convection heat transfer coefficient of the air interlayer, W/(m)2·K)；εc-glass cover plate surface emissivity; sigmasb-boltzmann's constant; t issky-the sky temperature, K; h israd,c-pRadiation heat exchange coefficient between the glass cover plate and the heat collecting plate, W/(m)2·K)；δc-glass cover plate thickness, m; lambda [ alpha ]c-glass cover plate thermal conductivity, W/(m · K);
2) heat balance equation of heat collecting plate
Sp(i)+qcond,p(i)-qconv,c-p(i)-qrad,c-p(i)-qcond,p-s(i)-qconv,p-l(i)＝0 (8)
Sp(i)＝τcαpIcWΔx (9)
qconv,p-l(i)＝2πRΔxhp-l[Tp(i)-Tl(i)](11)
In the formula: sp(i) -solar radiation absorbed by the collector panel inode; q. q.scond,p(i) The heat conduction of the node i of the heat collection plate, the node i-1 and the node i + 1; q. q.sconv,c-p(i) The natural convection heat exchange quantity of the air interlayer between the i-node of the glass cover plate and the i-node of the heat collecting plate is realized; q. q.srad,c-p(i) The radiant heat exchange between the glass cover plate node i and the heat collecting plate node i; q. q.scond,p-s(i) The heat conduction between the i-node of the heat collecting plate and the i-node of the shell is realized; q. q.sconv,p-l(i) The heat exchange amount by convection between the node i of the heat collecting plate and the node i of the fluid working medium; tau iscSolar radiation transmittance of glass cover plate αp-the solar radiation absorption of the glass cover plate; deltap-thickness of the collector plate, m; lambda [ alpha ]p-heat collection plate thermal conductivity, W/(m · K); h isp-l-convective heat transfer coefficient between pipe wall and working medium, W/(m)2K); r-inner diameter of pipe, m; deltab-thickness of the insulation layer, m; lambda [ alpha ]bThe thermal conductivity coefficient of the insulating layer, W/(m.K);
3) heat balance equation of fluid working medium
qconv,l(i)＝qcond,l(i)+qconv,p-l(i) (13)
In the formula: q. q.sconv,l(i) -heat carried away by thermal convection of the fluid working medium i-node; q. q.scond,l(i) The heat conduction of the fluid working medium i node, the i-1 node and the i +1 node; q. q.sconv,p-l(i) The heat exchange amount by convection between the node i of the heat collecting plate and the node i of the fluid working medium; rholDensity of the fluid working medium, kg/m 3; c. Cp,lThe specific heat at constant pressure of the fluid working medium, J/(kg. K);
4) thermal equilibrium equation of collector shell
qcond,s(i)+qcond,p-s(i)-qconv,s-a(i)-qrad,s-a(i)＝0 (16)
qconv,s-a(i)＝hconv,s-a[Ts(i)-Ta]WΔx (18)
hconv,s-a＝5.7+3.8Vwind(19)
In the formula: q. q.scond，s(i) Heat conduction from the shell i node to the i-1 node and the i +1 node; q. q.scond，p-s(i) -heat transfer between the shell i-node and the heat collecting plate i-node; q. q.sconv，s-a(i) -the convective heat transfer between the shell i-node and the external environment; q. q.srad，s-a(i) -the amount of radiation heat exchange between the shell i-node and the external environment; deltas-shell thickness, m; lambda [ alpha ]s-shell thermal conductivity, W/(m · K); h isconv，s-a-the convective heat transfer coefficient between the housing and the external environment; epsilons-shell surface emissivity;
5) heat collection and heat collection efficiency of heat collector
Qu＝mcp,l(Tout-Tin) (21)
In the formula: qu-the collector collects heat, W; m is heat collecting medium mass flow rate, kg/s; t isin-collector inlet temperature, K; t isoutOutlet of heat collectorMouth temperature, K; η -collector efficiency.
(2) Calling a heat transfer mathematical model of a single flat-plate solar collector, inputting environmental parameters, heat collection medium inlet parameters and the number of the series-connected flat-plate solar collectors, and calculating to obtain the heat collection amount of the flat-plate solar collectors with different series-connected numbers under the hourly meteorological parameters;
(3) determining the parallel number required by the heat collector groups with different series numbers under the condition of meeting the heat demand of a heat user;
(4) the method is characterized in that the cost annual value of a heat collector array is used as an objective function to carry out optimization design on the arrangement of the heat collector array, and the arrangement scheme of the flat-plate type solar heat collector array with the lowest cost annual value is used as an optimization scheme.
2. The design method for the series-parallel connection arrangement of the flat-plate type solar heat collector array according to claim 1 is characterized in that the established node equation set is iteratively solved by Matlab software, and the solving method is as follows:
(1) setting the maximum number of iterations 1 × 106Preventing iteration from entering a dead loop; iterative accuracy e is 1 × 10-4；
(2) Making assumptions about the average temperature of the glass cover plate, the heat collection plate and the housing;
(3) solving a matrix equation, and calculating the temperature of the glass cover plate, the heat collecting plate and the shell of each node;
(4) respectively judging the calculated average temperature of the glass cover plate, the average temperature of the heat collecting plate and the average temperature of the shell, namely phi*Whether the differences from the assumed value phi are all less than e;
(5) if yes, the calculation is considered to be converged, the calculation is stopped, and a calculation result is output;
(6) if not, the calculated value is taken as an assumed value, the matrix equation is solved again, and judgment is carried out; until a convergence condition is satisfied;
(7) if the iteration times exceed the maximum iteration times and are not converged, the calculation is considered not to be converged;
(8) and calling a thermal performance calculation model of the single heat collector to calculate the thermal performance of the series heat collector group.
3. The design method for the serial-parallel arrangement of the flat-plate type solar heat collector arrays according to claim 1, wherein the cost year value formula (23) of the heat collector arrays in the step (4) is an objective function, the initial investment and the running cost of the system of each combined heat collector array are calculated, and the combination of the lowest cost year values is used as the arrangement scheme of the optimal flat-plate type solar heat collector array:
Cr＝(N1+N2)×pe(24)
ΔP＝(1+a)×Rm×L+ΔPj(26)
ΔPj＝1.716×1012Q2+6.318×106Q+9.9 (27)
in the formula: c-annual cost value, Yuan; cr-annual operating costs, yuan; c1The cost of the solar heat collecting plate is low; c2The initial investment of the system is fixed, and the cost includes cost of a water pump, a valve, a pipeline and the like; i-equipment discount rate; n-equipment service life; n is a radical of1-power consumption of the solar circulation pump, kJ; n is a radical of2-auxiliary heat source power consumption, kJ; p is a radical ofe-electricity price, yuan/(kWh); qzTotal flow of heat collector tubes, m3S-total hours of operation of the collector, h ηs-water pump efficiency; Δ P-collector array line resistance, Pa; rm-pipe specific friction, Pa/m; l-pipe length, m; a is local equivalent resistance coefficient; delta Pj-local resistance of the collector, Pa; q-collector circulation flow, m3/s。
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| CN110378076B (en) * | 2019-08-21 | 2021-07-27 | 南京工程学院 | Quantitative evaluation method for temperature deviation of trough type solar heat collection field |
| CN111992026B (en) * | 2020-07-20 | 2022-05-03 | 张家港市锦明机械有限公司 | Denitration double-reactor arrangement method and system for realizing online switching |
| CN111737925B (en) * | 2020-08-24 | 2020-11-27 | 杭州锅炉集团股份有限公司 | Heliostat structure based on phase-change material and design optimization method thereof |
| CN112013553B (en) * | 2020-09-10 | 2022-01-28 | 吉林大学 | Adjustable condenser for flat-plate heat pipe solar collector and heat supply control method thereof |
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