CN103438611B - 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 drilling; (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, is used alone earth-source hot-pump system, and the caloric receptivity of ground heat exchanger to soil is greater than thermal discharge, and soil mean temperature declines, and system effectiveness declines.The proposition of solar energy earth-source hot-pump system well solves this problem.But China only has the design specification to source heat pump system (" earth-source hot-pump system engineering legislation ") and independent solar energy system (" solar-heating heating engineering technical specification ") individually, also do not issue the relevant design specification for 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 of soil uneven, entire system operational efficiency is lower, cause partial design system normally to run, thus reasonably design drilling depth and heat collector area have great significance for 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, ensure that the whole year of soil mean temperature stablizes, running efficiency of system is high simultaneously.

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, comprise the steps,

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

2) span of the drilling depth L of heat collector area A and ground heat exchanger is determined; By step 1) in the refrigeration duty Q in each interval that obtains _{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 heat collector area A of solar energy _max];

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

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

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

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

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

Preferably, described step 1) in the span of interval number N and M be 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 by following formula (3) and (4), span [0, the A of heat collector area A _max], calculated by following formula (4) and (5);

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

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

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

In formula: I is solar energy irradiation level; η is collector efficiency; t _maxfor the design mean temperature of 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 _∞for the initial temperature of pipe laying region Rock And Soil; F _cfor refrigerating operaton share; F _hfor heat supply running share; R _ffor the heat convection thermal resistance of heat transfer medium and U-tube inwall; R _pefor the wall resistance of U-tube; R _bfor the thermal resistance of well cementing backfilling material; R _sfor thermal resistance; R _spfor the additional thermal resistance that short-term continuous impulse load causes; COP is source pump coefficient of performance in heating; EER is 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 DEG C ~ 36 DEG C; For the design mean temperature t of heat transfer medium in ground heat exchanger under thermal condition _minspan be-2 DEG C ~ 6 DEG C.

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 number of refrigeration duty interval _{c, i}in maximum.

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

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

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

Preferably, described step 4) in program calculation time, 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 material calculation, drilling depth L take 0.5-3m as material calculation, forms some groups of data respectively to heat collector area A and drilling depth L circulation value, calculates often to organize data and corresponding whole year to recept the caloric Q _inhalewith thermal discharge Q _putthe absolute value of difference.

Preferably, the material calculation of described heat collector area A is 1m ², the material calculation of drilling depth L is 1m.

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

Optimization Design of the present invention, according to the simulation of different condition of construction, draw the cooling and heating load in each interval after subregion, thus the span of the drilling depth of collector area and ground heat exchanger can be drawn, the whole year finally obtaining some groups under the span of the drilling depth of different collector areas and ground heat exchanger inhales thermal discharge, therefrom draw and one group of data that the absolute value of suction thermal discharge difference is minimum be the optimal solution of the drilling depth of collector area volume and ground heat exchanger; Because the absolute difference of inhaling thermal discharge is minimum, therefore, it is possible to the mean temperature of stable soil to greatest extent, the overall operation efficiency that guarantee system is higher, solar energy earth-source hot-pump system can be made to drop to minimum on the impact that environment produces simultaneously, realize sustainable development, long-term operation fully reliably.

Further, adopt the system of series connection, can further improve system cloud gray model and service efficiency; By the selection of the Choice and design mean temperature of rational interval number, and the selection of material calculation, the time of computing and the difficulty of simulation can be reduced while guarantee computational accuracy, further reach the object of optimization.

Accompanying drawing explanation

Fig. 1 is the structural representation of 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.

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

Fig. 3 is the annual hourly load figure of terminal temperature difference obtained after structural modeling simulation in example of the present invention.

Fig. 4 is the system cloud gray model soil moisture variation diagram of 5 years obtained after 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.

Detailed description of the invention

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

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

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

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

Preferably when carrying out interval number and dividing, N number of refrigeration duty span that is interval and M thermic load M is 3-15.Can value be further 8 or 9.According to Fig. 3, this preferred embodiment is with 9 refrigeration dutys, and 8 thermic loads are example, and carries out replacement 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) span of the drilling depth L of heat collector area A and ground heat exchanger is determined; By step 1) in the refrigeration duty Q in each interval that obtains _{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 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);

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

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

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

In formula: I is solar energy irradiation level; t _maxfor the design mean temperature of 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 _∞for the initial temperature of pipe laying region Rock And Soil; F _cfor refrigerating operaton share; F _hfor heat supply running share; Q _{h, max}for the maximum heating load of terminal temperature difference; Q _{c, max}for the maximum cold load of 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 region Rock And Soil _∞value, determined by the difference in concrete area, the present embodiment is for Xi'an region; To refrigerating operaton share F _c, heat supply running share F _h, by target setting value during system; To the design mean temperature t of heat transfer medium in ground heat exchanger under cooling condition _maxspan, preferably get 33 DEG C ~ 36 DEG C; To the design mean temperature t for heat transfer medium in ground heat exchanger under thermal condition _minspan, preferably get-2 DEG C ~ 6 DEG C.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 number of refrigeration duty interval _{c, i}in maximum.

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

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

In this preferred embodiment, winter, ground heat exchanger designed caloric receptivity q from the unit interval of soil _{w, max}thermal discharge q is designed to the unit interval of soil with ground heat exchanger in summer _{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 (2) with formula (1).

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

In this preferred embodiment, calculate according to flow process shown in Fig. 2, the value of the parameter in abovementioned steps, and according to the calculating of step, preferably when program calculation, 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 material calculation, drilling depth L take 0.5-3m as material calculation, forms some groups of data respectively to heat collector area A and drilling depth L circulation value, calculates often to organize data and corresponding whole year to recept the caloric Q _inhalewith thermal discharge Q _putthe absolute value of difference; The material calculation that this preferred embodiment gets heat collector area A is 1m ², the material calculation of drilling depth L is 1m.Finally obtaining optimum design parameter is A _design=28m ², L _design=339m.

5) according to step 4) in the optimum heat collector area A that calculates _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, the soil moisture variation diagram that structural system designed in this preferred embodiment runs 5 years can be obtained, as shown in Figure 4, can observe the change drawing soil mean temperature, thus the rate of temperature change obtaining First Year soil being maximum, is 4.65%, dropped to 0.51% by the 5th year, soil mean temperature tends towards stability.

Meanwhile, after optimal design completes, can pass through to continue programming analog computation, to the optimum heat collector area A obtained _designwith optimum drilling depth L _design, compare with the change of the drilling depth Soil Under Conditions temperature of appointing three heat collector areas and the ground heat exchanger got in prior art listed in table four, result as shown in Figure 5, significantly can show that the method for the invention can guarantee that the mean temperature of soil declines less, the soil moisture is comparatively stable, in conjunction with the change of soil mean temperature as shown in Figure 4, thus the solar energy earth-source hot-pump system utilizing Optimization Design of the present invention to design and construct can both be drawn, can with the operation of good performance long-time stable, ambient influnence is little, 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, comprises the steps,

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

2) span of the drilling depth (L) of heat collector area (A) and ground heat exchanger is determined; By step 1) in the cooling and heating load (Q in each interval that obtains _{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 heat collector area (A) of solar energy _max];

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

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

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

5) according to step 4) in the optimum heat collector area (A that calculates _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, described step 1) in the span of load changing rate in each interval be 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, described step 1) in the span of interval number N and M be 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, it 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 by following formula (3) and (4), span [0, the A of heat collector area (A) _max], calculated by following formula (4) and (5);

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

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

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

In formula: I is solar energy irradiation level; η is collector efficiency; t _maxfor the design mean temperature of 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 _∞for the initial temperature of pipe laying region Rock And Soil; F _cfor refrigerating operaton share; F _hfor heat supply running share; R _ffor the heat convection thermal resistance of heat transfer medium and U-tube inwall; R _pefor the wall resistance of U-tube; R _bfor the thermal resistance of well cementing backfilling material; R _sfor thermal resistance; R _spfor the additional thermal resistance that short-term continuous impulse load causes; COP is source pump coefficient of performance in heating; EER is 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 DEG C ~ 36 DEG C; For the design mean temperature (t of heat transfer medium in ground heat exchanger under thermal condition _min) span be-2 DEG C ~ 6 DEG C.

7. a kind of solar energy earth-source hot-pump system Optimization Design according to claim 1 or 5 or 6, 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 number of refrigeration duty interval _{c, i}) in maximum.

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

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

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

9. a kind of solar energy earth-source hot-pump system Optimization Design according to claim 1 or 5 or 6, it is characterized in that, described step 4) in program calculation time, 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 material calculation, drilling depth (L) take 0.5-3m as material calculation, respectively some groups of data are formed to heat collector area (A) and drilling depth (L) circulation value, calculate and inhale thermal discharge (Q the whole year often organizing data corresponding _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 material calculation of described heat collector area (A) is 1m ², the material calculation of drilling depth (L) is 1m.