CN103438611A - Optimized design method of solar ground source heat pump system - Google Patents

Abstract

The invention discloses an optimized design method of a solar ground source heat pump system. The optimized design method comprises the following steps of: (1) calculating cold-heat load of an end user and dividing the cold-heat load into cold-heat load intervals; (2) determining the value ranges of an area A of a heat collector and a depth L of a buried pipe; (3) determining the heat absorbing amount and the heat releasing amount of a heat exchanger of the buried pipe; (4) calculating to obtain an optimal area Adesign of the heat collector and an optimal drilling depth Ldesign; (5) carrying out optimized design construction of the solar ground source heat pump system according to the optimal result obtained from calculation in the step (4). The optimized design method disclosed by the invention has the advantages that the optimal solutions of the area of the heat collector and the drilling depth are determined by simulated calculation for different constriction conditions and the minimum absolute value of the difference between the heat absorbing amount and the heat releasing amount in the step (4), so that the average temperature of soil can be furthest stabilized, higher overall operation efficiency of the system can be ensured, simultaneously the influence of the solar ground source heat pump system to the environment can be reduced to be lowest, and sustained development and long-term full and reliable operation are realized.

Description

A kind of solar energy earth-source hot-pump system Optimization Design

Technical field

The present invention relates to the method for designing of solar energy earth-source hot-pump system, be specially a kind of solar energy earth-source hot-pump system Optimization Design.

Background technology

Because the northern area soil moisture is lower, thermic load is large, and heating duration is long, uses separately earth-source hot-pump system, and ground heat exchanger is greater than thermal discharge to the caloric receptivity of soil, and the soil mean temperature descends, and system effectiveness descends.The proposition of solar energy earth-source hot-pump system has well solved this problem.But China only has source heat pump system (" earth-source hot-pump system engineering legislation ") and the design specification of solar energy system (" solar-heating heating engineering technical specification ") individually separately, and also distribution is not correlated with for the design specification of solar energy earth-source hot-pump system.More chaotic for choosing of drilling depth and heat collector area in reality, make the suction thermal discharge imbalance of soil, the entire system operational efficiency is lower, cause the partial design system normally to move, thereby reasonably design drilling depth and heat collector area has great significance for the solar energy earth-source hot-pump system.

Summary of the invention

The object of the present invention is to provide a kind of solar energy earth-source hot-pump system Optimization Design, can meet the demand of indoor cooling and heating load, guarantee that the whole year of soil mean temperature is stable simultaneously, running efficiency of system is high.

The present invention is achieved through the following technical solutions:

A kind of solar energy earth-source hot-pump system Optimization Design, is characterized in that, comprises the steps,

1) calculate the cooling and heating load of terminal temperature difference and divide the cooling and heating load interval; By analog computation draw terminal temperature difference by the time cooling and heating load, and by hourly cooling load according to numerical value be divided into N interval, will by the time thermic load be divided into M interval according to numerical value, make each interval load changing rate be no more than 300kJ/h ²; With in each interval by the time cooling and heating load the maximum refrigeration duty Q interval as this _{c, i}or thermic load Q _{h, j}, and add up each interval refrigeration duty Q _{c, i}or thermic load Q _{h, j}corresponding Time Frequency And H _{c, i}or H _{h, j}, i=1 wherein, 2 ..., N; J=1,2 ..., M;

2) determine the span of heat collector area A and underground pipe degree of depth L; The refrigeration duty Q that each obtaining in step 1) is interval _{c, i}or thermic load Q _{h, j}calculate the span [L of the drilling depth L of ground heat exchanger _min, L _max] and span [0, the A of the heat collector area A of solar energy _max];

3) the suction thermal discharge of buried tube heat exchanger and soil definitely; Calculate the ground heat exchanger whole year of the caloric receptivity Q to soil by following formula (1) and (2) _inhalewith thermal discharge Q _put:

In formula: q _{w, max}for winter ground heat exchanger from unit interval of soil design caloric receptivity; q _{s, max}for summer ground heat exchanger to unit interval of soil design thermal discharge; Q _inhalefor the ground heat exchanger whole year of the total caloric receptivity from soil; Q _putfor the ground heat exchanger whole year of the total thermal discharge to soil; Q _{h, max}maximum heating load for terminal temperature difference; Q _{c, max}maximum cold load for terminal temperature difference;

4) calculate optimum heat collector area A _designwith optimum drilling depth L _design; According to step 2) in the heat collector area A that obtains and the span of drilling depth L, and the ground heat exchanger obtained in step 3) is to the caloric receptivity Q of soil _inhalewith thermal discharge Q _put, by programming, calculate under different heat collector area A and drilling depth L ground heat exchanger whole year to the soil Q that recepts the caloric _inhalewith thermal discharge Q _put, draw annual caloric receptivity Q _inhalewith thermal discharge Q _putthe corresponding heat collector area A of one group of data and the drilling depth L of absolute value minimum of difference, be optimum heat collector area A _designwith optimum drilling depth L _design;

5) according to the optimum heat collector area A calculated in step 4) _designwith optimum drilling depth L _design, carry out the optimal design construction of solar energy earth-source hot-pump system.

Preferably, in described step 1), the span of each interval load changing rate is 20-200kJ/h ².

Preferably, in described step 1), the span of interval number N and M is 3-15.

Preferably, the value of described interval number N is 8 or 9; The value of interval number M is 8 or 9.

Preferably, described solar energy earth-source hot-pump system is train, step 2) in the span [L of drilling depth L _min, L _max] obtained span [0, the A of heat collector area A by following formula (3) and (4) _max], by following formula (4) and (5), calculated;

$L_{\max }=\frac{{1000Q}_{h,\max }[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_h+R_{\mathrm{sp}}\×(1-F_h)]}{(t_{\∞}-t_{\min })}\left(\frac{\mathrm{COP}-1}{\mathrm{COP}}\right)---\left(3\right);$

$L_{\min }=\frac{{1000Q}_{c,\max }[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_c+R_{\mathrm{sp}}\×(1-F_c)]}{(t_{\max }-t_{\∞})}\left(\frac{\mathrm{EER}+1}{\mathrm{EER}}\right)---\left(4\right);$

$L_{\min }=\frac{1000(Q_{h,\max }-A_{\max }\mathrm{I\η}[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_h+R_{\mathrm{sp}}\×(1-F_h)\left]\right)}{(t_{\∞}-t_{\min })}\left(\frac{\mathrm{COP}-1}{\mathrm{COP}}\right)---\left(5\right);$

In formula: I is the solar energy irradiation level; η is collector efficiency; t _maxdesign mean temperature for heat transfer medium in ground heat exchanger under cooling condition; t _minfor the design mean temperature for heat transfer medium in ground heat exchanger under thermal condition; t _∞initial temperature for pipe laying zone Rock And Soil; F _cfor the refrigerating operaton share; F _hfor the heat supply running share; R _fheat convection thermal resistance for heat transfer medium and U-shaped inside pipe wall; R _pewall resistance for U-shaped pipe; R _bthermal resistance for the well cementing backfilling material; R _sfor thermal resistance; R _spthe additional thermal resistance caused for short-term continuous impulse load; COP is the source pump coefficient of performance in heating; EER is the source pump coefficient of performance of refrigerating.

Preferably, the design mean temperature t of heat transfer medium in ground heat exchanger under described cooling condition _maxspan be 33 ℃～36C; Design mean temperature t for heat transfer medium in ground heat exchanger under thermal condition _minspan be-2 ℃～6 ℃.

Preferably, terminal temperature difference maximum heating load Q _{h, max}for thermic load Q in M thermic load interval _{h, j}in maximum; The maximum cold load Q of described terminal temperature difference _{c, max}for refrigeration duty Q in N refrigeration duty interval _{c, i}in maximum.

Preferably, winter, ground heat exchanger was from unit interval of soil design caloric receptivity q _{w, max}with summer ground heat exchanger to unit interval of soil design thermal discharge q _{s, max}by following formula (6) and (7), calculated;

$q_{w,\max }=\frac{t_{\∞}-t_{\min }}{1000[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_h+R_{\mathrm{sp}}+(1-F_h)]}L-\mathrm{AI\η}---\left(6\right);$

$q_{s,\max }=\frac{t_{\max }-t_{\∞}}{1000[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_c+R_{\mathrm{sp}}+(1-F_c)]}L---\left(7\right).$

Preferably, when the programming in described step 4) is calculated, at the span [L of heat collector area A and drilling depth L _min, L _max] and [0, A _max] in, heat collector area A is with 0.5-3m ²for calculating step-length, drilling depth L be take 0.5-3m as calculating step-length, respectively heat collector area A and drilling depth L circulation value is formed to some groups of data, calculates every group of data Q that recepts the caloric the corresponding whole year _inhalewith thermal discharge Q _putthe absolute value of difference.

Preferably, the calculating step-length of described heat collector area A is 1m ², the calculating step-length of drilling depth L is 1m.

Compared with prior art, the present invention has following useful technique effect:

Optimization Design of the present invention, simulation according to different condition of construction, draw each the interval cooling and heating load after subregion, thereby can draw the span of collector area and the underground pipe degree of depth, inhale thermal discharge the last whole year that obtains some groups under the span of different collector areas and the underground pipe degree of depth, therefrom draw one group of data of the absolute value minimum of inhaling the thermal discharge difference, be the optimal solution of collector area volume and the underground pipe degree of depth; Due to the absolute difference minimum of inhaling thermal discharge, therefore the mean temperature of stable soil to greatest extent, the overall operation efficiency that the assurance system is higher, the impact that can make the solar energy earth-source hot-pump system produce environment simultaneously drops to minimum, realize sustainable development, long-term operation fully reliably.

Further, adopt the system of series connection, the operation of further raising system and service efficiency; The selection of the Choice and design mean temperature by rational interval number, and the selection of calculating step-length can reduce the time of computing and the difficulty of simulation when guaranteeing computational accuracy, have further reached the purpose of optimizing.

The accompanying drawing explanation

The structural representation that Fig. 1 is the solar energy earth-source hot-pump system described in example of the present invention; Wherein, 1 is solar thermal collector, and 2 is ground heat exchanger, and 3 is source pump, and 4 is water tank, and 5 is terminal temperature difference.

The calculation process block diagram that Fig. 2 is the Optimization Design in example of the present invention.

Load diagram when Fig. 3 is annual the pursuing of terminal temperature difference obtained after the structural modeling simulation in example of the present invention.

Fig. 4 is the system operation soil moisture variation diagram of 5 years obtained after the structural modeling simulation in example of the present invention.

Fig. 5 is the soil moisture comparison diagram under the method for the invention and existing method condition.

The specific embodiment

Below in conjunction with specific embodiment, the present invention is described in further detail, and the explanation of the invention is not limited.

A kind of solar energy earth-source hot-pump system of the present invention Optimization Design, train take in this preferred embodiment as example, be optimized illustrating of design, the step of Optimization Design of the present invention and thought also can be used in to be applied parallel system or its system, only need to, according to concrete system, utilizing of different parameters technological means of the prior art be determined.The described tandem system configuration of this preferred embodiment, as shown in Figure 1, be embodied as solar thermal collector 1 by water tank 4, and the series connection of ground heat exchanger 2, by source pump 3, with terminal temperature difference 5, is connected, and realizes for warm refrigeration.

When the described system architecture of this preferred embodiment being optimized to design, as shown in Figure 2, it comprises the following steps the calculation process step.

1) calculate cooling and heating load and divide the cooling and heating load interval; By analog computation draw terminal temperature difference by the time cooling and heating load, and by hourly cooling load according to numerical value be divided into N interval, will by the time thermic load be divided into M interval according to numerical value, make each interval load changing rate be no more than 300kJ/h ²; The span of preferred each interval load changing rate is 20-200kJ/h ².

With in each interval by the time cooling and heating load the maximum refrigeration duty Q interval as this _{c, i}or thermic load Q _{h, j}, for represent hourly cooling load that corresponding interval is all or by the time thermic load; And add up each interval refrigeration duty Q _{c, i}or thermic load Q _{h, j}corresponding Time Frequency And H _{c, i}or H _{h, j}, i=1 wherein, 2 ..., N; J=1,2 ..., M; The data in area, Xi'an of preferably take during analog computation are condition, preferably with the TRNSYS simulation softward, are simulated, and system are carried out to the simulation of annual performance.Relevant basic parameter name, abbreviation, value and unit are as shown in Table 1.After system is simulated, obtain, terminal temperature difference as shown in Figure 3 annual by the time load diagram.

Preferably, when carrying out interval number division, N refrigeration duty span interval and M thermic load M is 3-15.Can value be further 8 or 9.Shown in Fig. 3, this preferred embodiment is with 9 refrigeration dutys, and 8 thermic loads are example, and is replaced tabular value and timing statistics frequency, and as shown in Table 2, thermic load numerical value and frequency are as shown in Table 3 for refrigeration duty numerical value and frequency.

2) determine the span of heat collector area A and underground pipe degree of depth L; The refrigeration duty Q that each obtaining in step 1) is interval _{c, i}or thermic load Q _{h, j}calculate the span [L of the drilling depth L of ground heat exchanger _min, L _max] and span [0, the A of the heat collector area A of solar energy _max].

For this preferred train, to the span [L of drilling depth L _min, L _max] can be obtained by following formula (3) and (4) span [0, the A of heat collector area A _max] can be calculated by following formula (4) and (5);

$L_{\max }=\frac{{1000Q}_{h,\max }[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_h+R_{\mathrm{sp}}\×(1-F_h)]}{(t_{\∞}-t_{\min })}\left(\frac{\mathrm{COP}-1}{\mathrm{COP}}\right)---\left(3\right);$

$L_{\min }=\frac{{1000Q}_{c,\max }[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_c+R_{\mathrm{sp}}\×(1-F_c)]}{(t_{\max }-t_{\∞})}\left(\frac{\mathrm{EER}+1}{\mathrm{EER}}\right)---\left(4\right);$

$L_{\min }=\frac{1000(Q_{h,\max }-A_{\max }\mathrm{I\η}[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_h+R_{\mathrm{sp}}\×(1-F_h)\left]\right)}{(t_{\∞}-t_{\min })}\left(\frac{\mathrm{COP}-1}{\mathrm{COP}}\right)---\left(5\right);$

In formula: I is the solar energy irradiation level; t _maxdesign mean temperature for heat transfer medium in ground heat exchanger under cooling condition; t _minfor the design mean temperature for heat transfer medium in ground heat exchanger under thermal condition; t _∞initial temperature for pipe laying zone Rock And Soil; F _cfor the refrigerating operaton share; F _hfor the heat supply running share; Q _{h, max}maximum heating load for terminal temperature difference; Q _{c, max}maximum cold load for terminal temperature difference; All the other parameters are identical with the parameter provided in table one.

Wherein, the initial temperature t of solar energy irradiation level I and pipe laying zone Rock And Soil _∞value, by the difference in concrete area, determined, the present embodiment be take the area, Xi'an as example; To refrigerating operaton share F _c, heat supply running share F _h, the target setting value during by system; Design mean temperature t to heat transfer medium in ground heat exchanger under cooling condition _maxspan, preferably get 33 ℃～36 ℃; To the design mean temperature t for heat transfer medium in ground heat exchanger under thermal condition _minspan, preferably get-2 ℃～6 ℃.Terminal temperature difference maximum heating load Q _{h, max}be exactly thermic load Q in M thermic load interval _{h, j}in maximum; The maximum cold load Q of terminal temperature difference _{c, max}be exactly refrigeration duty Q in N refrigeration duty interval _{c, i}in maximum.

3) the suction thermal discharge of buried tube heat exchanger and soil definitely; Calculate the ground heat exchanger whole year of the caloric receptivity Q to soil by following formula (1) and (2) _inhalewith thermal discharge Q _put:

In formula: q _{w, max}for winter ground heat exchanger from unit interval of soil design caloric receptivity; q _{s, max}for summer ground heat exchanger to unit interval of soil design thermal discharge; Q _inhalefor the ground heat exchanger whole year of the total caloric receptivity from soil; Q _putfor the ground heat exchanger whole year of the total thermal discharge to soil; All the other parameters and step 2) in the parameter that provides identical.

In this preferred embodiment, winter, ground heat exchanger was from unit interval of soil design caloric receptivity q _{w, max}with summer ground heat exchanger to unit interval of soil design thermal discharge q _{s, max}can be calculated by following formula (6) and (7);

$q_{w,\max }=\frac{t_{\∞}-t_{\min }}{1000[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_h+R_{\mathrm{sp}}+(1-F_h)]}L-\mathrm{AI\η}---\left(6\right);$

$q_{s,\max }=\frac{t_{\max }-t_{\∞}}{1000[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_c+R_{\mathrm{sp}}+(1-F_c)]}L---\left(7\right).$

In formula, each parameter is identical with the implication in formula (1) and (2).

4) calculate optimum heat collector area A _designwith optimum drilling depth L _design; According to step 2) in the heat collector area A that obtains and the span of drilling depth L, and the ground heat exchanger obtained in step 3) is to the caloric receptivity Q of soil _inhalewith thermal discharge Q _put, by programming, calculate under different heat collector area A and drilling depth L ground heat exchanger whole year to the soil Q that recepts the caloric _inhalewith thermal discharge Q _put, draw annual caloric receptivity Q _inhalewith thermal discharge Q _putthe corresponding heat collector area A of one group of data and the drilling depth L of absolute value minimum of difference, be optimum heat collector area A _designwith optimum drilling depth L _design.

In this preferred embodiment, according to flow process shown in Fig. 2, calculated, the value of the parameter in aforementioned step, and according to the calculating of step, preferably when programming is calculated, at the span [L of heat collector area A and drilling depth L _min, L _max] and [0, A _max] in, heat collector area A is with 0.5-3m ²for calculating step-length, drilling depth L be take 0.5-3m as calculating step-length, respectively heat collector area A and drilling depth L circulation value is formed to some groups of data, calculates every group of data Q that recepts the caloric the corresponding whole year _inhalewith thermal discharge Q _putthe absolute value of difference; The calculating step-length that this preferred embodiment is got heat collector area A is 1m ², the calculating step-length of drilling depth L is 1m.Finally obtaining optimum design parameter is A _design=28m ², L _design=339m.

5) according to the optimum heat collector area A calculated in step 4) _designwith optimum drilling depth L _design, carry out the optimal design construction of solar energy earth-source hot-pump system.

After optimal design completes, by continuing analog computation, can access the structural system operation soil moisture variation diagram of 5 years designed in this preferred embodiment, as shown in Figure 4, can observe the variation that draws the soil mean temperature, thereby obtain the rate of temperature change maximum of First Year soil, be 4.65%, dropped to 0.51% by the 5th year, the soil mean temperature tends towards stability.

Simultaneously, after optimal design completes, can be by the continuation analog computation of programming, to the optimum heat collector area A obtained _designwith optimum drilling depth L _designwith the variation of appointing the soil moisture under three heat collector areas getting and underground pipe depth conditions in prior art listed in table four, compare, result as shown in Figure 5, can significantly show that the method for the invention can guarantee that the mean temperature of soil descends less, the soil moisture is comparatively stable, variation in conjunction with soil mean temperature as shown in Figure 4, thereby can both draw the solar energy earth-source hot-pump system that utilizes Optimization Design design and construction of the present invention, can be with the long-time stable operation of performance preferably, ambient influnence is little, and system effectiveness is high.

Table one

Table two

Refrigeration duty/kJ/h	56156.1	47686	39950.5	35107.1	31403.4
						Frequency/h	35	107	156	122	145
Refrigeration duty/kJ/h	26711.9	17837.2	6314.6	907.465	?
						Frequency/h	259	397	204	71	?

Table three

Thermic load/kJ/h	1059.845	4983.203	10514.14	14280.96
					Frequency/h	58	133	111	78
Thermic load/kJ/h	18602.53	24472.34	32040.95	40612.14
					Frequency/h	176	134	174	21

Table four

Method for designing	Optimization method design of the present invention	Value	1	Value 2	Value 3
						Heat collector area/m 2	28	79	76	76
Drilling depth/m	339	278	271	379

Claims (10)

1. a solar energy earth-source hot-pump system Optimization Design, is characterized in that, comprise the steps,

1) calculate the cooling and heating load of terminal temperature difference and divide the cooling and heating load interval; By analog computation draw terminal temperature difference by the time cooling and heating load, and by hourly cooling load according to numerical value be divided into N interval, will by the time thermic load be divided into M interval according to numerical value, make each interval load changing rate be no more than 300kJ/h ²; With in each interval by the time cooling and heating load the maximum refrigeration duty (Q interval as this _{c, i}) or thermic load (Q _{h, j}), and add up each interval cooling and heating load (Q _{c, i}, Q _{h, j}) corresponding Time Frequency And H _{c, i}or H _{h, j}, i=1 wherein, 2 ..., N; J=1,2 ..., M;

2) determine the span of heat collector area (A) and the underground pipe degree of depth (L); Cooling and heating load (the Q that each obtaining in step 1) is interval _{c, i}, Q _{h, j}) calculate the span [L of the drilling depth (L) of ground heat exchanger _min, L _max] and span [0, the A of the heat collector area (A) of solar energy _max];

3) the suction thermal discharge of buried tube heat exchanger and soil definitely; Calculate the ground heat exchanger whole year of the suction thermal discharge (Q to soil by following formula (1) and (2) _inhale, Q _put):

In formula: q _{w, max}for winter ground heat exchanger from unit interval of soil design caloric receptivity; q _{s, max}for summer ground heat exchanger to unit interval of soil design thermal discharge; Q _inhalefor the ground heat exchanger whole year of the total caloric receptivity from soil; Q _putfor the ground heat exchanger whole year of the total thermal discharge to soil; Q _{h, max}maximum heating load for terminal temperature difference; Q _{c, max}maximum cold load for terminal temperature difference;

4) calculate optimum heat collector area (A _design) and optimum drilling depth (L _design); According to step 2) in the heat collector area (A) that obtains and the span of drilling depth (L), and the ground heat exchanger obtained in step 3) is to the suction thermal discharge (Q of soil _inhale, Q _put), calculate ground heat exchanger under different heat collector area (A) and drilling depth (L) by programming and the whole year soil is inhaled to thermal discharge (Q _inhale, Q _put), draw the annual thermal discharge (Q that inhales _inhale, Q _put) one group of corresponding heat collector area of data (A) and the drilling depth (L) of absolute value minimum of difference, be optimum heat collector area (A _design) and optimum drilling depth (L _design);

5) according to the optimum heat collector area (A calculated in step 4) _design) and optimum drilling depth (L _design), carry out the optimal design construction of solar energy earth-source hot-pump system.

2. a kind of solar energy earth-source hot-pump system Optimization Design according to claim 1, is characterized in that, in described step 1), the span of each interval load changing rate is 20-200kJ/h ².

3. a kind of solar energy earth-source hot-pump system Optimization Design according to claim 1, is characterized in that, in described step 1), the span of interval number N and M is 3-15.

4. a kind of solar energy earth-source hot-pump system Optimization Design according to claim 3, is characterized in that, the value of described interval number N is 8 or 9; The value of interval number M is 8 or 9.

5. a kind of solar energy earth-source hot-pump system Optimization Design according to claim 1, is characterized in that, described solar energy earth-source hot-pump system is train, step 2) in the span [L of drilling depth (L) _min, L _max] obtained span [0, the A of heat collector area (A) by following formula (3) and (4) _max], by following formula (4) and (5), calculated;

$L_{\max }=\frac{{1000Q}_{h,\max }[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_h+R_{\mathrm{sp}}\×(1-F_h)]}{(t_{\∞}-t_{\min })}\left(\frac{\mathrm{COP}-1}{\mathrm{COP}}\right)---\left(3\right);$

$L_{\min }=\frac{{1000Q}_{c,\max }[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_c+R_{\mathrm{sp}}\×(1-F_c)]}{(t_{\max }-t_{\∞})}\left(\frac{\mathrm{EER}+1}{\mathrm{EER}}\right)---\left(4\right);$

$L_{\min }=\frac{1000(Q_{h,\max }-A_{\max }\mathrm{I\η}[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_h+R_{\mathrm{sp}}\×(1-F_h)\left]\right)}{(t_{\∞}-t_{\min })}\left(\frac{\mathrm{COP}-1}{\mathrm{COP}}\right)---\left(5\right);$

In formula: I is the solar energy irradiation level; η is collector efficiency; t _maxdesign mean temperature for heat transfer medium in ground heat exchanger under cooling condition; t _minfor the design mean temperature for heat transfer medium in ground heat exchanger under thermal condition; t _∞initial temperature for pipe laying zone Rock And Soil; F _cfor the refrigerating operaton share; F _hfor the heat supply running share; R _fheat convection thermal resistance for heat transfer medium and U-shaped inside pipe wall; R _pewall resistance for U-shaped pipe; R _bthermal resistance for the well cementing backfilling material; R _sfor thermal resistance; R _spthe additional thermal resistance caused for short-term continuous impulse load; COP is the source pump coefficient of performance in heating; EER is the source pump coefficient of performance of refrigerating.

6. a kind of solar energy earth-source hot-pump system Optimization Design according to claim 5, is characterized in that, the design mean temperature (t of heat transfer medium in ground heat exchanger under described cooling condition _max) span be 33 ℃～36 ℃; Design mean temperature (t for heat transfer medium in ground heat exchanger under thermal condition _min) span be-2 ℃～6 ℃.

7. according to claim 1 or 5 or 6 described a kind of solar energy earth-source hot-pump system Optimization Design, it is characterized in that terminal temperature difference maximum heating load (Q _{h, max}) be thermic load (Q in M thermic load interval _{h, j}) in maximum; Maximum cold load (the Q of described terminal temperature difference _{c, max}) be refrigeration duty (Q in N refrigeration duty interval _{c, i}) in maximum.

8. according to the described a kind of solar energy earth-source hot-pump system Optimization Design of claim 5 or 6, it is characterized in that, winter, ground heat exchanger was from unit interval of soil design caloric receptivity (q _{w, max}) and summer ground heat exchanger to unit interval of soil design thermal discharge (q _{s, max}) by following formula (6) and (7), calculated;

$q_{w,\max }=\frac{t_{\∞}-t_{\min }}{1000[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_h+R_{\mathrm{sp}}+(1-F_h)]}L-\mathrm{AI\η}---\left(6\right);$

$q_{s,\max }=\frac{t_{\max }-t_{\∞}}{1000[R_f+R_{\mathrm{pe}}+R_b+R_s\×F_c+R_{\mathrm{sp}}+(1-F_c)]}L---\left(7\right).$

9. according to claim 1 or 5 or 6 described a kind of solar energy earth-source hot-pump system Optimization Design, it is characterized in that, when the programming in described step 4) is calculated, at the span [L of heat collector area (A) and drilling depth (L) _min, L _max] and [0, A _max] in, heat collector area (A) is with 0.5-3m ²for calculating step-length, drilling depth (L) be take 0.5-3m as calculating step-length, respectively heat collector area (A) and drilling depth (L) circulation value is formed to some groups of data, calculates every group of data and inhales thermal discharge (Q the corresponding whole year _inhale, Q _put) the absolute value of difference.

10. a kind of solar energy earth-source hot-pump system Optimization Design according to claim 9, is characterized in that, the calculating step-length of described heat collector area (A) is 1m ², the calculating step-length of drilling depth (L) is 1m.

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