CN105302984B - A kind of earth source heat pump unit modeling and simulating method - Google Patents
A kind of earth source heat pump unit modeling and simulating method Download PDFInfo
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Abstract
The invention discloses a kind of earth source heat pump unit modeling and simulating method, this method has fully considered influence when earth source heat pump unit is run at part load to its operation energy consumption.When carrying out analogue simulation with this earth source heat pump mathematical model, show that this model is capable of the changing rule of correct response heat pump unit performance in variable parameter operation, it may be assumed that when unit part load ratio is gradually increased, the trend of first increases and then decreases is presented in unit COP；When vaporizer side flow or condenser side flow increase, unit COP increases, and then reduces on the contrary；In cooling mode, when evaporator output water temperature increases, condenser side return water water temperature reduces, unit COP increases, on the contrary, unit COP then reduces.Buried pipe ground-source heat pump system is established on TRNSYS emulation platform using this model, by obtaining to its analogue simulation: when local source uses variable-flow operation, the operation energy consumption of entire air-conditioning system can be saved.
Description
Technical field
The present invention relates to earth source heat pump more particularly to a kind of earth source heat pump unit modeling and simulating methods.
Background technique
The full name of TRNSYS is Transient System Simulation Program, is big by Wisconsin
A instantaneous system simulation program of solar energy development in laboratory is learned, in recent years, in heating ventilation air-conditioning system running optimizatin and energy conservation
Aspect is to have obtained relatively broad application.Variable-flow analogue simulation is being carried out to buried pipe ground-source heat pump system using TRNSYS
When, there are some defects by the earth source heat pump set modules Type927 that discovery TRNSYS is provided, and these defects will be to simulation result
Accuracy impact.Its defect mainly has following two points；
1) unit load side outlet water temperature cannot be set as definite value, be set as 7 DEG C when such as freezing, and when heating is set as 45
℃.Heat pump unit in actual moving process, as long as Building Cooling load within the scope of its cooling or heating capacity, heat pump unit
Load side exit water temperature can be maintained at the temperature of setting well.And not to be able to maintain outlet temperature not only constant by Type927, and
And when unit part load ratio changes, the fluctuation of load side exit water temperature is very big.In cooling mode, work as heat pump unit
When condenser side return water water temperature is constant, condenser side flow is constant, unit part load ratio is gradually increased, the simulation of Type927
As a result as shown in Figure 1.As shown in Figure 1, when unit part load ratio is 0.25, vaporizer side exit water temperature is -391.75
DEG C, this is very unreasonable.
2) do not consider that heat pump unit runs the influence to its performance at part load.In general, unit COP is with portion
The trend for dividing the increase of rate of load condensate that first increases and then decreases is presented.As shown in Figure 1, being gradually increased with part load ratio,
Type927 analog result is shown: when rate of load condensate is less than 0.85, unit COP hardly follows the variation of rate of load condensate and changes,
When rate of load condensate is greater than 0.85, unit COP is sharply increased with the increase of rate of load condensate.Therefore, Type927 is transported at part load
Capable situation is not inconsistent with practical operation situation.
In order to overcome the shortcomings of that Type927 occurs when simulating ground-source heat pump system, increases the accuracy of analogue simulation, have
Necessity studies a kind of new earth source heat pump unit modeling and simulating method for meeting practical operation situation.
Summary of the invention
The purpose of the invention is to provide it is a kind of meet actual operating mode, earth source heat pump load can be applied to
Side, source variable-flow simulation study earth source heat pump unit modeling and simulating method.
In order to achieve the above objectives, the present invention adopts the following technical scheme:
A kind of earth source heat pump unit modeling and simulating method, the specific steps are as follows:
Step 1: the definition of parameter and variable: the variable and parameter in overall model are counted and names and identifies respectively；
Step 2: according to vaporizer side water flow Me, vaporizer side output water temperature Tco, vaporizer side return water water temperature Tei, cold
Condenser side water flow Mc, condenser side return water water temperature Tci, to establish suitable for the earth source heat pump unit that is run under sub-load
Mathematical model；Refrigerating capacity CAP is descended at full capacity to which refrigerating capacity Q, heat pump unit that heat pump unit currently needs be calculatedmax, heat
Input power P needed for pump assembly, condenser side output water temperature TcoWith heat pump unit COP value；
Step 3: earth source heat pump unit emulation module is developed on emulation platform according to the mathematical model of step 2；
Step 4: using the heat pump unit emulation module of step 3 exploitation on emulation platform, analogue simulation is carried out.
Part of load is the load of air-conditioning in 10% to 100% section.
Further, steps are as follows for the calculating of input power P needed for heat pump unit in the step 2:
(2.1) heat pump unit maximum cooling capacity CAP is calculatedmaxThe refrigerating capacity Q currently needed with heat pump unit；
(2.2) compare maximum cooling capacity CAPmaxThe refrigerating capacity Q currently needed, if maximum cooling capacity CAPmaxIt is more than or equal to
When the refrigerating capacity Q currently needed, holding evaporator output water temperature is setting value, if maximum cooling capacity CAPmaxIt is needed less than current
Refrigerating capacity Q when, then the return step 2.1 after improving vaporizer side exit water temperature；
(2.3) pass through heat pump unit required input power P under declared working condition0, input power correction factor Pr1The part and
Heat pump unit input power correction factor P under loadr2Come input power P needed for calculating heat pump unit.
Further, heat pump unit maximum cooling capacity CAP is calculated according to formula (1) in the step (2.1)max:
CAPmax=f1(Me, Mc, Teo, Tci) (1)
The formula (1) can be rewritten as formula (2):
CAPmax=CAP0·CAPr (2)
CAPr=f2(rme, rmc, rTeo, rTci) (3)
Wherein, CAP0For refrigerating capacity of the unit under declared working condition when oepration at full load, CAPrIt is unit under actual condition
The correction factor of refrigerating capacity, rmeFor the ratio of vaporizer side practical water flow and specified water flow；rmcFor the practical water of condenser side
The ratio of flow and specified water flow；rTeoFor the ratio of vaporizer side practical exit water temperature and nominal outlet port water temperature；rTciIt is cold
The ratio of condenser side practical return water water temperature and specified return water water temperature.
Further, the refrigerating capacity Q that current heat pump unit currently needs is calculated according to formula (4) in the step (2.1):
Q=CMeΔt (4)
Wherein, Δ t is vaporizer side supply backwater temperature difference, DEG C, Q is the refrigerating capacity that heat pump unit currently needs, kJ/h.
Further, input power P needed for the heat pump unit is calculated by formula (5):
P=P0Pr1Pr2=P0f6(rme, rmc, rTeo, rTci)f5(PLR) (5)
Wherein, PLR is heat pump unit part load ratio.
Further, condenser side output water temperature T is calculated according to formula (6) in the step 2co:
Wherein, TciFor condenser side return water water temperature, McFor condenser side water flow.
Further, unit COP value is calculated according to formula (4), (5) in the step 2:
Q=CMeΔt (4)
P=P0Pr1Pr2=P0f6(rme, rmc, rTeo, rTci)f5(PLR) (5)
Further, the correction factor of unit refrigerating capacity under actual condition is calculated by formula (8):
CAPr=a1+b1rme+b2rme 2+c1rmc+c2rmc 2+d1rTeo+d2rTeo 2+e1rTci+e2rTci 2+f1rTeorTci (8)。
Further, the input power correction factor Pr1It is calculated with formula (9):
Pr1=a2+b3rme+b4rme 2+c3rmc+c4rmc 2+d3rTeo+d4rTeo 2+e3rTci+e4rTci 2+f2rTeorTci(9)；
Heat pump unit input power correction factor P under the sub-loadr2It is calculated with formula (10):
Pr2=a3+a4PLR+a5PLR2 (10)。
The working principle of the invention is: in actual conditions, when heat pump unit gradually becomes sub-load from oepration at full load
When operation, since total heat exchange amount reduces, the opposite heat exchange area of heat pump unit heat exchanger increases, and heat exchange efficiency improves, so
The efficiency of unit also increases accordingly.Simultaneously because the reduction of condensation temperature, the raising of evaporating temperature, refrigerant flow
Reduce, this further increases the COP of heat pump unit at part load.When the part load ratio of heat pump unit further subtracts
Hour, refrigerant flow continues to reduce, and due to leading to motor radiating deficiency since inspiratory capacity is too low etc., leads to compressor efficiency
It is greatly lowered, so as to cause unit COP sharp fall.The unit being calculated after considering heat pump unit sub-load
COP tallies with the actual situation, and has better guidance to practical application.
The beneficial effects of the present invention are:
1) modeling and simulating method in the present invention, has fully considered that heat pump unit is run at part load to its energy consumption
Influence, by verifying, obtain heat pump unit COP with part load ratio be gradually increased present first increases and then decreases trend, together
When vaporizer side exit water temperature maintain setting value.Modeling and simulating method is demonstrated to tally with the actual situation.
2) by verifying, when the part load ratio of heat pump unit is constant, obtain heat pump unit COP with vaporizer side flow
Than the change modeling relationship of, condenser side flow-rate ratio, unit COP is by vaporizer side flow and the shadow of condenser side changes in flow rate
It rings, no matter which side flow increases, unit COP will all increase, no matter which side flow reduces, unit COP will all reduce, it was demonstrated that
Modeling and simulating method tallies with the actual situation.
3) it by verifying, when the part load ratio of heat pump unit is constant, obtains when the raising of evaporator output water temperature, condensation
When device side return water water temperature reduces, unit COP increases.On the contrary, unit COP then reduces, it was demonstrated that modeling and simulating method meets reality
Situation.
4) using the modeling and simulating method in the present invention, after simulation analysis, show that ground source variable-flow operation can be with
Save the operation energy consumption of entire air-conditioning system.
Detailed description of the invention
Fig. 1 is the schematic diagram of Type927 analog result；
Fig. 2 is the simulation result of heat pump unit module in the present invention.
Fig. 3 is earth source heat pump unit program flow diagram in the present invention；
Fig. 4 be in the present invention heat pump unit COP with vaporizer side flow when condenser side flow-rate ratio variation simulation drawing；
Fig. 5 is the mould that heat pump unit COP changes with vaporizer side output water temperature and condenser side return water water temperature in the present invention
Quasi- figure；
Fig. 6 is the simulation drawing that heat pump unit COP changes with part load ratio, condenser side return water water temperature in the present invention；
Fig. 7 be after being emulated in the present invention source variable-flow with figure compared with source constant flow underground pipe exit water temperature；
Fig. 8 be after being emulated in the present invention source variable-flow with figure compared with source constant flow condensator outlet water temperature；
Fig. 9 be in the present invention emulate after heat pump unit energy consumption, land source side water pump energy consumption with variable frequency pump minimum running frequency become
Change curve graph；
Figure 10 be in the present invention emulate after source total energy consumption with variable frequency pump minimum running frequency change curve.
Specific embodiment
Following will be combined with the drawings in the embodiments of the present invention, and technical solution in the embodiment of the present invention carries out clear, complete
Whole description.
Assuming that refrigerating capacity of the heat pump unit under different operating conditions when oepration at full load is CAPmax, then CAPmaxWith vaporizer side
Water flow, condenser side water flow, vaporizer side exit water temperature, condenser side return water water temperature are related.CAPmaxIt can be by with minor function
It indicates:
CAPmax=f1(Me, Mc, Teo, Tci) (1)
In formula: MeFor vaporizer side water flow, kg/h；McFor condenser side water flow, kg/h；TeoFor vaporizer side water outlet
Water temperature, DEG C；TciFor condenser side return water water temperature, DEG C.
For unified dimension, formula (1) can be rewritten as following formula:
CAPmax=CAP0·CAPr (2)
CAPr=f2(rme, rmc, rTeo, rTci) (3)
In formula: CAP0For refrigerating capacity of the unit under declared working condition when oepration at full load, kJ/h；CAPrIt is unit in reality
The correction factor of refrigerating capacity under operating condition；rmeFor the ratio of vaporizer side practical water flow and specified water flow；rmcFor condenser side
The ratio of practical water flow and specified water flow；rTeoFor the ratio of vaporizer side practical exit water temperature and nominal outlet port water temperature；
rTciFor the ratio of condenser side practical return water water temperature and specified return water water temperature.
Work as TeoWhen for design value, heat pump unit needs refrigerating capacity to be achieved, as shown in formula (4):
Q=CMeΔt (4)
In formula: Q is that heat pump unit needs refrigerating capacity to be achieved, kJ/h；C is the specific heat capacity of fluid, kJ/ (kg DEG C)；Δ t is
Vaporizer side supply backwater temperature difference, DEG C.
As Q≤CAPmaxWhen, holding vaporizer side exit water temperature is set water temperature, such as 7 DEG C；Due to the refrigeration of heat pump unit
Ability is related with condenser side return water temperature, when the refrigeration duty of the demand of building increases to a certain extent, condenser side return water temperature
Degree will be greater than specified return water temperature.At this point, refrigerating capacity when heat pump unit oepration at full load will be less than rated cooling capacity, have
It may cause the refrigerating capacity that the refrigerating capacity that building needs is greater than heat pump unit oepration at full load under such operating condition, i.e. Q >
CAPmax.As Q > CAPmaxWhen, with reference to the processing mode of Type666, i.e., make heat pump machine by improving vaporizer side exit water temperature
The refrigerating capacity enhancing of group, to meet the needs of current refrigeration capacity.
Shown in the calculating of heat pump unit part load ratio such as formula (11):
In formula: PLR is heat pump unit part load ratio.
Input power needed for heat pump unit not only with Me、Mc、Teo、TciIt is related, it is also related with unit part load ratio, such as
Shown in formula (12):
P=f3(Me, Mc, Teo, Tci, PLR) and (12)
And also to do regression analysis convenient for the later period, consider PLR as an independent variable, it may be assumed that
P=f4(Me, Mc, Teo, Tci)f5(PLR) (13)
Equally, formula (13) can be rewritten as following expression convenient for unified dimension:
P=P0Pr1Pr2=P0f6(rme, rmc, rTeo, rTci)f5(PLR) (5)
In formula: P0For heat pump unit under declared working condition required input power, kJ/h；Pr1To descend heat pump unit defeated at full capacity
Enter corrected coefficient of power；Pr2For heat pump unit input power correction factor under sub-load.
Condenser side exit water temperature can be calculated by formula (6):
In formula: TcoFor condenser side output water temperature, DEG C.
The COP that heat pump unit can be calculated by formula (4), formula (5), as shown in formula (7):
With reference to DOE-2 model, CAPr、Pr1、Pr2It can be given by the following formula:
CAPr=a1+b1rme+b2rme 2+c1rmc+c2rmc 2+d1rTeo+d2rTeo 2+e1rTci+e2rTci 2+f1rTeorTci (8)
Pr1=a2+b3rme+b4rme 2+c3rmc+c4rmc 2+d3rTeo+d4rTeo 2+e3rTci+e4rTci 2+f2rTeorTci (9)
Pr2=a3+a4PLR+a5PLR2 (10)
The accuracy and data volume of sample used by the accuracy of this mathematical model relies primarily on solve formula (9), formula
(10) sample that sample is provided from TRNSYS17 Type927, but this sample cannot be directly used to solve, because of sample thus
Originally the vaporizer side exit water temperature that provides and condenser side return water water temperature are its temperature value, and formula (9) and formula (10) using
The ratio of actual temperature and rated temperature, therefore first sample is pre-processed.It is herein 7 DEG C with vaporizer side exit water temperature, cold
It is that declared working condition pre-processes this sample that condenser side return water water temperature, which is 28 DEG C,.Then by solving formula formula by pretreated sample
(9), formula (10).Formula (9), formula (10) are nonlinear multivariable equation, can use MATLAB and do Multiple Non Linear Regression, solve
Each term coefficient in equation out.
Regression analysis is carried out to formula (8) first, following equation can be obtained by regression analysis:
CAPr=0.716+0.4191rme-0.1175rme 2+0.0279rmc+0.0012rmc 2+0.1549rTeo
(14)
+0.0002rTeo 2-0.2929rTci+0.0833rTci 2-0.0001rTeorTci
The coefficient of determination R of this regression model2It is 9531.2 that=0.9968, F, which count magnitude, Probability p corresponding with statistic F
=0, due to p < 0.05, therefore the regression model is set up.
Equally, regression analysis is carried out to formula (9), following equation can be obtained by regression analysis:
Pr1=0.6769+0.1128rme-0.0436rme 2-0.3604rmc+0.1272rmc 2+0.0197rTeo
(15)
-0.0014rTeo 2+0.2134rTci+0.2124rTci 2
The coefficient of determination R of this regression model2It is 19883 that=0.9984, F, which count magnitude, Probability p corresponding with statistic F
=0, due to p < 0.05, therefore the regression model is set up.
For formula (10), since Type927 does not consider influence of the part load ratio to its performance, so the sample of its offer
Correction factor without heat pump unit input power under sub-load.In this regard, using for reference the sample that Type666 is provided herein to solve formula
(10).By fitting of a polynomial, following equation is obtained:
Pr2=0.2726-0.08413PLR+0.8102PLR2 (16)
The coefficient of determination R of this regression model2=0.9991, it is seen that fitting effect is preferable.
By taking cooling in summer operating condition as an example, it is known that the earth source heat pump unit rated cooling capacity of certain model is 1576800kJ/h, volume
Determining COP is 5, and the specified water flow of vaporizer side is 75265kg/h, and the specified water flow of condenser side is 88738kg/h, evaporator
The specified output water temperature in side is 7 DEG C, and the specified return water water temperature of condenser side is 28 DEG C.The above initial value is substituted into heat pump unit mathematical modulo
Type carries out simulation calculating.When the specified output water temperature of vaporizer side and the specified return water water temperature of condenser side remain unchanged, unit is kept
When oepration at full load, when condenser side flow-rate ratio change modeling figure is as shown in Figure 4 with vaporizer side flow for unit COP.
As shown in figure 4, unit COP is influenced by vaporizer side flow and condenser side changes in flow rate, no matter which effluent
Amount increases, and unit COP will all increase, and no matter which side flow reduces, and unit COP will all reduce.This is because evaporator water side
The coefficient of heat transfer and Water in Condenser side coefficient of heat transfer approximation are directly proportional to 0.8 power of fluid flow rate.When water effluent speed reduces,
Evaporator water side, the heat exchange of Water in Condenser side weaken, so as to cause unit COP decline.As it can be seen that the meter of this heat pump unit mathematical model
Result is calculated to be consistent with this rule.
When evaporator, condenser keep specified water flow, when heat pump unit keeps oepration at full load, heat pump unit COP with
Vaporizer side output water temperature, condenser side return water water temperature change modeling figure are as shown in Figure 5.
When evaporator output water temperature increases, condenser side return water water temperature reduces, unit COP increases.On the contrary, unit COP
Then reduce.This is because when evaporator outlet water temperature increases, the evaporating temperature of evaporator can be increased, when condenser side returns
When water water temperature reduces, the condensation temperature of condenser be can decrease, this makes under identical refrigerating capacity, and the acting of compressor subtracts
It is small, to improve the COP of unit.As it can be seen that the calculated result of this heat pump unit mathematical model is also consistent with this rule.
From Fig. 6 it can further be seen that unit COP is on a declining curve, but unit part when condenser side return water temperature increases
Rate of load condensate does not change to the affecting laws of COP, this be actually consistent.As it can be seen that this model being capable of correct response heat pump
The changing rule of unit run time behaviour at part load.
By the above content it is found that the modeling and simulating method in the present invention can be in the changing rule under various operating conditions, Ke Yiyong
In influence of the different operating conditions of simulation to unit performance and operation energy consumption.
It is emulated in TRNSYS using method of the invention, so when developing this module it is necessary to first designing number
According to the interface of transmission, carried out data transmission with facilitating with other modules.For this purpose, the input interface of this module can be by following ginseng
Number is constituted, it may be assumed that vaporizer side return water water temperature Tei, evaporator side inlet water flow Mei, condenser side return water water temperature Tci, condenser
Side entrance water flow Mci.Its output interface can be made of following parameter, it may be assumed that vaporizer side output water temperature Teo, vaporizer side
Outlet stream amount Meo, condenser side output water temperature Tco, condenser side outlet stream amount Mco, unit operation power P, unit COP,
Refrigerating capacity Q, the unit part load ratio PLR that unit provides, herein, vaporizer side outlet stream amount and evaporator side inlet water flow
Measure equal, i.e. Mei=Meo=Me；Condenser side outlet stream amount is equal with condenser side entrance water flow, i.e. Mci=Mco=Mc。
For the ease of being defined on TRNSYS emulation platform to the performance of this heat pump unit, it is also necessary to initial parameter is set, at the beginning of
Beginning parameter can be made of following parameter, it may be assumed that unit rated cooling capacity CAP0, the specified COP of unit, the specified water flow of vaporizer side
Measure Me0, the specified water flow M of condenser sidec0, the specified output water temperature T of vaporizer sideeo0, the specified return water water temperature T of condenser sideci0, with
And formula (8, (9) and (10) every fitting coefficient.Parameter and initial parameter will be inputted as known quantity, output parameter is used as wait ask
Variable is solved, is that theoretical basis works out C programmer by the earth source heat pump unit mathematical model of upper foundation.
In order to guarantee that system is safely and efficiently run, the variable frequency range of variable frequency pump should be limited, determine its minimum fortune
Line frequency.Minimum running frequency is contemplated that the factor in terms of following two is set:
1) minimum discharge that variable frequency pump minimum delivery flow should be required not less than heat pump unit safe operation, unit evaporation
Changes in flow rate range may generally be the 30%~130% of design discharge in device and condenser.
2) variable frequency pump minimum delivery flow should ensure that the fluidised form in underground pipe is turbulent, i.e. reynolds number Re > 2300,
Shown in calculation formula such as formula (17):
In formula: d is buried bore, m；U is velocity in pipes, m/s；V kinematic viscosity, m2/s。
Fluidised form in keeping managing can be calculated by formula (17) and is the minimum flow velocity of turbulent flow, and then calculates the minimum of variable frequency pump
Output flow.
Variable frequency pump minimum output flow chooses the maximum value for the minimum discharge being calculated by the above two o'clock, by calculating,
The minimum running frequency of variable frequency pump cannot be less than 22Hz herein.
Local source supply backwater temperature difference is set as 5 DEG C and variable frequency pump minimum running frequency when being 22Hz, underground pipe outlet
Water temperature is when ground source constant flow operation as shown in fig. 7, condensator outlet water temperature and ground source compared with underground pipe exit water temperature
The comparison of outlet temperature when constant flow is run is as shown in Figure 8.
As it can be seen that underground pipe exit water temperature decreases when local source uses variable-flow operation, and it is entire to freeze season, it is buried
Pipe exit water temperature is run compared with constant flow averagely reduces by 0.92 DEG C.When this is primarily due to local source using variable-flow operation, ground
Source fluid flow rate reduces, but fluid flow state is still turbulent flow in underground pipe, and fluid is elongated by the time of ground heat exchanger,
This makes the heat exchange of fluid and soil more abundant, and then the exit water temperature of underground pipe is caused to reduce.Local source uses simultaneously
It is high when condensator outlet water temperature is run compared with ground source using constant flow when variable-flow operation, it is entire to freeze season, averagely it is higher by
1.42℃.This is because the flow by condenser reduces, caused by the condensation temperature of condenser increases.
When soil initial temperature is 16 DEG C, source use variable-flow operation when, after a refrigeration season, soil mean temperature
It is 18.91 DEG C.When local source is run using constant flow, after a refrigeration season, soil mean temperature is 18.89 DEG C.As it can be seen that
After one refrigeration season, ground source variable-flow operation increases compared with ground source constant flow operation soil mean temperature, but only improves
0.02 DEG C.This is because when local source uses variable-flow operation, although underground pipe exit water temperature reduces, due to by cold
The flow of condenser reduces, so that condenser side heat exchange efficiency is declined and condensation temperature increases, unit performance is still declined.
Since unit performance reduces, the heat for causing it to discharge to ground heat exchanger be increased, so that soil mean temperature be made to have
Increased.
Heat pump unit energy consumption, land source side water pump energy consumption, source total energy consumption (units consumption add ground land source side water pump energy consumption) with
The change curve of variable frequency pump minimum running frequency is as shown in Figures 9 and 10.By Fig. 9, Figure 10 it is found that working as variable frequency pump minimum running frequency
When being gradually increased, since the variable frequency range of variable frequency pump narrows, the whole water that conveys is gradually increased, so that the operation energy consumption of variable frequency pump
It is gradually increased, since the conveying water of variable frequency pump is gradually increased, so that the COP of heat pump unit increases, and then it runs energy
Consumption gradually decreases.When variable frequency pump minimum running frequency is less than 30Hz, source total operation energy consumption variation in ground is smaller, when variable frequency pump most
When small running frequency is greater than 30Hz, source total operation energy consumption in ground is then increased rapidly.
Local source supply backwater temperature difference is set as 5 DEG C, variable frequency pump minimum running frequency is when being set as 22Hz, every energy consumption
It is as shown in table 1 compared with every energy consumption when the operation of ground source constant flow.When ground source constant flow is run, water pump operation power
For 10.6kW.
Table 1 is ground source constant flow operation and ground source variable-flow operation energy consumption comparison sheet
As seen from the above table, although ground source variable-flow operation increased the operation energy consumption of heat pump unit, ground
The operation energy consumption of land source side water pump then greatly reduces, and province's electricity of water pump is greater than the increased power consumption of heat pump unit, finally makes ground source
The total operation energy consumption in side is less, fractional energy savings 6.47%.
The above is only a preferred embodiment of the present invention, it is noted that for the ordinary skill people of the art
For member, various improvements and modifications may be made without departing from the principle of the present invention, these improvements and modifications are also answered
It is considered as protection scope of the present invention.
Claims (8)
1. a kind of earth source heat pump unit modeling and simulating method, which is characterized in that specific step is as follows:
Step 1: the definition of parameter and variable: the variable and parameter in overall model are counted and names and identifies respectively；
Step 2: according to vaporizer side water flow Me, vaporizer side output water temperature Teo, vaporizer side return water water temperature Tei, condenser
Side water flow Mc, condenser side return water water temperature Tci, to establish the mathematics suitable for the earth source heat pump unit run under sub-load
Model；Refrigerating capacity CAP is descended at full capacity to which refrigerating capacity Q, heat pump unit that heat pump unit currently needs be calculatedmax, heat pump machine
Input power P, condenser side output water temperature T needed for groupcoWith heat pump unit COP value；
Step 3: earth source heat pump unit emulation module is developed on emulation platform according to the mathematical model of step 2；
Step 4: using the earth source heat pump unit emulation module of step 3 exploitation on emulation platform, analogue simulation is carried out；
Steps are as follows for the calculating of input power P needed for heat pump unit in the step 2:
(2.1) it calculates heat pump unit and descends refrigerating capacity CAP at full capacitymaxThe refrigerating capacity Q currently needed with heat pump unit；
(2.2) compare heat pump unit and descend refrigerating capacity CAP at full capacitymaxThe refrigerating capacity Q currently needed, if heat pump unit is at full capacity
Lower refrigerating capacity CAPmaxWhen more than or equal to the refrigerating capacity Q currently needed, holding vaporizer side output water temperature is setting value, if heat pump
Unit descends refrigerating capacity CAP at full capacitymaxWhen less than the refrigerating capacity Q currently needed, then returned after improving vaporizer side output water temperature
Step (2.1)；
(2.3) pass through heat pump unit required input power P under declared working condition0, input power correction factor Pr1And sub-load
Lower heat pump unit input power correction factor Pr2Come input power P needed for calculating heat pump unit.
2. a kind of earth source heat pump unit modeling and simulating method as described in claim 1, which is characterized in that the step (2.1)
It is middle that refrigerating capacity CAP is descended according to formula (1) calculating heat pump unit at full capacitymax:
CAPmax=f1(Me, Mc, Teo, Tci) (l)
The formula (1) can be rewritten as formula (2):
CAPmax=CAP0·CAPr (2)
CAPr=f2(rme, rmc, rTeo, rTci) (3)
Wherein, CAP0For refrigerating capacity of the unit under declared working condition when oepration at full load, CAPrFreeze under actual condition for unit
The correction factor of amount, rmeFor the ratio of vaporizer side practical water flow and specified water flow；rmcFor the practical water flow of condenser side
With the ratio of specified water flow；rTeoFor the ratio of vaporizer side practical exit water temperature and nominal outlet port water temperature；rTciFor condenser
The ratio of side practical return water water temperature and specified return water water temperature.
3. a kind of earth source heat pump unit modeling and simulating method as described in claim 1, which is characterized in that the step (2.1)
It is middle that the refrigerating capacity Q that heat pump unit currently needs is calculated according to formula (4):
Q=CMeΔt (4)
Wherein, Δ t is vaporizer side supply backwater temperature difference, DEG C, Q is the refrigerating capacity that heat pump unit currently needs, and kJ/h, C are fluid
Specific heat capacity, kJ/ (kg DEG C).
4. a kind of earth source heat pump unit modeling and simulating method as described in claim 1, which is characterized in that the heat pump unit institute
The input power P needed is calculated by formula (5):
P=P0Pr1Pr2=P0f6(rme, rmc, rTeo, rTci)f5(PLR) (5)
Wherein, rmeFor the ratio of vaporizer side practical water flow and specified water flow；rmcFor the practical water flow of condenser side and volume
Determine the ratio of water flow；rTeoFor the ratio of vaporizer side practical exit water temperature and nominal outlet port water temperature；rTciFor condenser side reality
The ratio of border return water water temperature and specified return water water temperature, PLR are heat pump unit part load ratio；P0It is heat pump unit in declared working condition
Lower required input power, kJ/h；Pr1To descend heat pump unit input power correction factor at full capacity；Pr2For heat pump under sub-load
Unit input power correction factor.
5. a kind of earth source heat pump unit modeling and simulating method as described in claim 1, which is characterized in that root in the step 2
Condenser side water outlet water temperature T is calculated according to formula (6)co:
Wherein, C is the specific heat capacity of fluid, kJ/ (kg DEG C).
6. a kind of earth source heat pump unit modeling and simulating method as described in claim 1, which is characterized in that root in the step 2
Unit COP value is calculated according to formula (4), (5):
Q=CMeΔt (4)
P=P0Pr1Pr2=P0f6(rme, rmc, rTeo, rTci)f5(PLR) (5)
Wherein, C is the specific heat capacity of fluid, and kJ/ (kg DEG C), Δ t are vaporizer side supply backwater temperature difference, DEG C, P0It is heat pump unit in volume
Determine required input power under operating condition, kJ/h；Pr1To descend heat pump unit input power correction factor at full capacity；Pr2For sub-load
Lower heat pump unit input power correction factor, rmeFor the ratio of vaporizer side practical water flow and specified water flow；rmcFor condensation
The ratio of device side practical water flow and specified water flow；rTeoFor the ratio of the practical exit water temperature of vaporizer side and nominal outlet port water temperature
Value；rTciFor the ratio of condenser side practical return water water temperature and specified return water water temperature, PLR is heat pump unit part load ratio.
7. a kind of earth source heat pump unit modeling and simulating method as claimed in claim 2, which is characterized in that the unit is in reality
The correction factor of refrigerating capacity is calculated by formula (8) under operating condition:
CAPr=a1+b1rme+b2rme 2+c1rmc+c2rmc 2+d1rTeo+d2rTeo 2+e1rTci+e2rTci 2+f1rTeorTci (8)。
8. a kind of earth source heat pump unit modeling and simulating method as described in claim 4 or 6, which is characterized in that
The input power correction factor Pr1It is calculated with formula (9):
Pr1=a2+b3rme+b4rme 2+c3rmc+c4rmc 2+d3rTeo+d4rTeo 2+e3rTci+e4rTci 2+f2rTeorTci(9)；
Heat pump unit input power correction factor P under the sub-loadr2It is calculated with formula (10):
Pr2=a3+a4PLR+a5PLR2 (10)。
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| CN111814320B (en) * | 2020-06-23 | 2023-06-09 | 四川大学华西医院 | Dynamic operation simulation test method for variable flow ground source heat pump system |
| CN112560235B (en) * | 2020-12-02 | 2023-08-29 | 上海应用技术大学 | Modeling method of hot water type absorption lithium bromide refrigerating unit |
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