A heat supply control method and system of a heat source tower heat pump unit, an electronic device, and a storage medium

Abstract

This invention relates to a heating control method, system, electronic equipment, and storage medium for a heat source tower heat pump unit. The specific steps are as follows: The heat and mass transfer control body of the heat source tower is divided into several control body unit models along the airflow direction; based on the control body unit models, dynamic models of air-side heat and mass transfer and solution-side heat and mass transfer interact with the heat source tower are established; based on the air-side and solution-side dynamic models of heat and mass transfer, a heat mass balance model of the heat source tower's heat and mass transfer control body is established; based on the operating parameters of the heat source tower heat pump unit, a heat transfer balance model of the heat source tower heat pump unit is established; based on the heat mass balance model of the heat and mass transfer control body and the heat transfer balance model of the heat source tower heat pump unit, an objective function maximizing the heating supply of the heat source tower heat pump unit is established; the objective function is solved to obtain the control results of the heat source tower heat pump and its heat and mass transfer control body.

Description

Technical Field

[0001] This invention relates to the field of heat pump heating technology, specifically to a heating control method, system, electronic equipment, and storage medium for a heat source tower heat pump unit. Background Technology

[0002] Energy is a crucial component and driving force of social development. During the booming real estate industry in my country, the scale of construction expanded continuously, leading to a sustained increase in the proportion of energy consumed in the total operation of buildings. Among this, heating and air conditioning accounted for 50% to 70% of total building energy consumption. With the increasing demand for comfortable living and working environments in my country's hot-summer and cold-winter regions, the energy consumption of air conditioning systems also remains significant. As a major energy consumer in the building sector, air conditioning systems play a crucial role in addressing energy and environmental issues; therefore, finding renewable alternative energy sources is extremely important. While the volume of new buildings has decreased due to the recent downturn in the real estate industry, some existing buildings are already undergoing renovation. Heat source tower heat pump energy supply systems are suitable for both winter and summer use. They can be used in new buildings where no other heat or cold sources are available, and in renovated buildings, they can replace high-energy-consuming equipment such as gas boilers for heating.

[0003] In summer, the heat source tower in a heat pump energy supply system functions as a cooling tower, with cooling water circulating inside. In winter, antifreeze circulates within the tower, solving both the frosting and defrosting issues of air-source heat pumps and improving heating efficiency. The heating efficiency of the heat pump unit in winter is a crucial parameter, directly impacting system operating costs in addition to its heating performance. The antifreeze in the heat source tower exchanges sensible and latent heat with the air; the heating efficiency of the heat pump system is only high when the outdoor dry-bulb temperature is high and humidity is high. Outdoor air parameters change constantly; the parameters of the air and solution entering the tower determine the parameters of the solution exiting the tower, thus affecting the heating efficiency of the heat pump unit. Maintaining efficient unit operation while meeting the heating load is a pressing issue. Summary of the Invention

[0004] This invention provides a heating control method, system, electronic equipment, and storage medium for a heat source tower heat pump unit. Based on the conservation of heat and mass between the heat and mass transfer control bodies and the energy conservation of the heat source tower heat pump unit, a mathematical model related to the heat source tower and the heat source tower heat pump unit is established. The heating logic of the heat source tower heat pump unit with the maximum heating efficiency of the heat source tower heat pump unit as the target is built, and the unit's thermal efficiency is reduced under the premise of meeting the system heat load.

[0005] The solution of the present invention to the above-mentioned technical problems is as follows:

[0006] In a first aspect, the present invention provides a heating control method for a heat source tower heat pump unit, comprising the following steps:

[0007] The heat and mass transfer control volume of the heat source tower is divided into several control volume unit models along the air flow direction;

[0008] Based on the control volume unit model, dynamic models of heat and mass on the air side and the solution side that interact with the heat source tower are established respectively.

[0009] Based on the dynamic models of heat and mass on the air side and the dynamic models of heat and mass on the solution side, a heat and mass balance model of the heat transfer and mass transfer control body of the heat source tower is established.

[0010] Based on the operating parameters of the heat source tower heat pump unit, a heat transfer balance model of the heat source tower heat pump unit is established.

[0011] Based on the heat mass balance model of the heat transfer and mass transfer control body and the heat transfer balance model of the heat source tower heat pump unit, an objective function to maximize the heat supply of the heat source tower heat pump unit is established. The objective function is solved to obtain the control results of the heat source tower heat pump and its heat transfer and mass transfer control body.

[0012] Preferably, the control volume unit model confines the air-solution heat exchange region of the heat source tower to the heat and mass transfer control volume region. The packing portion of the open crossflow heat source tower is considered as a two-dimensional computational domain along the airflow direction, and divided into a finite number of heat and mass transfer control volume units with a step size of 1, as follows:

[0013] (x, y) ∈ {(0, 0), (n, m)}

[0014]

[0015]

[0016] In the formula: x is the horizontal node number of the control unit; y is the vertical node number of the control unit; n is the number of horizontally divided units of the control unit; m is the number of vertically divided units of the control unit; L is the length of the heat source tower packing area; H is the height of the heat source tower packing area.

[0017] Preferably, the dynamic model of air-side heat mass interacting with the heat source tower is as follows:

[0018]

[0019] In the formula: the subscript 'air' indicates that the corresponding parameter uses air as the medium; 'x' is the horizontal node number of the control volume unit; 'y' is the vertical node number of the control volume unit; 'n' is the number of horizontally divided control volume units; 'm' is the number of vertically divided control volume units; heat air G represents the heat difference between the air entering and leaving the tower. air，(x，y) h is the dry air mass flow rate at the control unit node (x,y); air，(x，y)The enthalpy of air at the control unit node (x,y); Water air The difference in water vapor content between the air entering and leaving the tower; d air，(x，y) This refers to the air humidity at the control unit node (x, y).

[0020] Preferably, the solution-side heat mass dynamic model interacting with the heat source tower is as follows:

[0021]

[0022] In the formula: the subscript sol indicates that the corresponding parameter uses the heat source tower solution as the medium; x is the horizontal node number of the control volume unit; y is the vertical node number of the control volume unit; n is the number of horizontally divided control volume units; m is the number of vertically divided control volume units; Heat sol The difference in heat between the inlet and outlet of the antifreeze solution in the tower; G sol，(x，y) h is the mass flow rate of the antifreeze solution at the control unit node (x,y); sol，(x，y) The enthalpy of the antifreeze solution at the control unit node (x,y); Water sol The difference in moisture content between the inlet and outlet of the antifreeze solution in the tower; t sol，(x，y) w represents the temperature of the antifreeze solution at the control unit node (x, y). sol，(x，y) This represents the mass fraction of the antifreeze solution at the control unit node (x, y).

[0023] Preferably, the heat and mass balance model of the heat and mass transfer control volume is as follows:

[0024] Heat air =Heat sol

[0025] Water air =Water sol

[0026]

[0027] In the formula: the subscript "air" indicates that the corresponding parameter uses air as the medium; the subscript "sol" indicates that the corresponding parameter uses the heat source tower solution as the medium; "x" is the horizontal node number of the control volume unit; "y" is the vertical node number of the control volume unit; "n" is the number of horizontally divided units of the control volume; "m" is the number of vertically divided units of the control volume; Heat air The difference in heat between the air entering and leaving the tower; Water sol The difference in moisture content between the inlet and outlet of the antifreeze solution; Heat sol The heat difference between the inlet and outlet of the antifreeze solution in the tower; Water sol The difference in moisture content between the inlet and outlet of the antifreeze solution in the tower; C sol，(x，y) w is the mass flow rate of the antifreeze solution at the control unit node (x,y);sol(x，y) This represents the mass fraction of the antifreeze solution at the control unit node (x, y).

[0028] Preferably, the heat transfer balance model of the heat source tower heat pump unit considers the intrinsic factors of the unit's heating efficiency, including evaporation temperature, condensation temperature, superheat at the evaporator outlet, and recooling at the condenser outlet. Combining the thermodynamic calculations of the vapor compression heating cycle, the calculation model for the heating capacity, compressor input power, and heating efficiency of the heat source tower heat pump unit is simplified as follows:

[0029] Q = f zr (t zf , t ln );

[0030] P = f gl (t zf , t lz );

[0031]

[0032] t zf =f zf (t sol，1 , t sol，2 );

[0033] t lz =f ln (t kt，1 , t kt，2 );

[0034] Q = f zr (f zf (t sol，1 , t sol，2 ), f ln (t kt，1 , t kt，2 ));

[0035] P = f gl (f zf (t sol,1 , t sol,2 ), f ln (t kt，1 , t kt，2 ));

[0036]

[0037] Where: Q is the heating capacity of the heat source tower heat pump unit; P is the compressor input power of the heat source tower heat pump unit; COP is the heating efficiency of the heat source tower heat pump unit; t zf The evaporation temperature of the heat pump unit in the heat source tower; t ln The condensing temperature of the heat pump unit in the heat source tower; t sol，1For the antifreeze solution inlet of the heat pump unit in the heat source tower; t sol，2 The outlet temperature of the antifreeze solution in the heat pump unit of the heat source tower; t kt，1 The heat source tower heat pump unit's air conditioning hot water inlet; t kt，2 f is the outlet temperature of the hot water for the air conditioning unit of the heat source tower heat pump unit. zr f gl f zf f ln All of these are function symbols.

[0038] Preferably, the objective function for maximizing the heat supply of the heat source tower heat pump unit is as follows:

[0039] Q = P + C sol，(L，H) ×G sol，(L，H) ×(t sol，1 -t sol，2 )

[0040] Q = 4.187G kt ×(t kt,1 -t kt,2 )

[0041] t sol,1 =t sol，(L，H)

[0042] t sol,2 =t sol，(0，0)

[0043] COP = max(COP)

[0044]

[0045] In the formula: C sol，(L，H) G is the specific heat of the antifreeze solution at the outlet of the heat source tower. sol，(L，H) G is the mass flow rate of the antifreeze solution at the outlet of the heat source tower. kt The mass flow rate of hot water for air conditioning in the heat pump unit of the heat source tower; t sol，(L，H) The temperature of the antifreeze solution at the outlet of the heat source tower; t sol，(0，0) ρ is the temperature of the antifreeze solution at the inlet of the heat source tower. sol，(L，H)，t ρ represents the density of the antifreeze solution on the evaporator side of the heat pump unit in the heat source tower at time t. kt，t The density of the air-conditioning hot water on the condenser side of the heat pump unit at time t; n zf，t At time t, the water pump speed on the evaporator side of the heat pump unit in the heat source tower; n ln，t The speed of the water pump on the condenser side of the heat pump unit in the heat source tower at time t.

[0046] Secondly, the present invention provides a heating control device for a heat source tower heat pump unit, comprising:

[0047] The control volume unit model construction module is used to divide the heat and mass transfer control volume of the heat source tower into several control volume unit models along the air flow direction.

[0048] The module for constructing dynamic heat and mass models of air and solution sides is used to establish dynamic heat and mass models of air and solution sides that interact with the heat source tower, based on the control volume unit model.

[0049] The heat mass balance model construction module of the heat transfer and mass transfer control body is used to establish the heat mass balance model of the heat source tower based on the air-side heat mass dynamic model and the solution-side heat mass dynamic model.

[0050] The heat transfer balance model of the heat source tower heat pump unit is used to establish the heat transfer balance model of the heat source tower heat pump unit based on the operating parameters of the heat source tower heat pump unit.

[0051] The heat source tower heat pump unit heating solution module is used to establish an objective function to maximize the heating of the heat source tower heat pump unit based on the heat mass balance model of the heat transfer and mass transfer control body and the heat transfer balance model of the heat source tower heat pump unit. The objective function is solved to obtain the control results of the heat source tower heat pump and its heat transfer and mass transfer control body.

[0052] Preferably, the control unit model is as follows:

[0053] (x, y) ∈ {(0, 0), (n, m)}

[0054]

[0055] In the formula: x is the horizontal node number of the control unit; y is the vertical node number of the control unit; n is the number of horizontally divided units of the control unit; m is the number of vertically divided units of the control unit; L is the length of the heat source tower packing area; H is the height of the heat source tower packing area.

[0056] Preferably, the dynamic model of air-side heat mass interacting with the heat source tower is as follows:

[0057]

[0058] In the formula: the subscript 'air' indicates that the corresponding parameter uses air as the medium; 'x' is the horizontal node number of the control volume unit; 'y' is the vertical node number of the control volume unit; 'n' is the number of horizontally divided control volume units; 'm' is the number of vertically divided control volume units; 'Heat'... air G represents the heat difference between the air entering and leaving the tower. air，(x，y) h is the dry air mass flow rate at the control unit node (x,y); air，(x，y) The enthalpy of air at the control unit node (x,y); Water airThe difference in water vapor content between the air entering and leaving the tower; d air，(x，y) This refers to the air humidity at the control unit node (x, y).

[0059] Preferably, the solution-side heat mass dynamic model interacting with the heat source tower is as follows:

[0060]

[0061] In the formula: the subscript sol indicates that the corresponding parameter uses the heat source tower solution as the medium; x is the horizontal node number of the control volume unit; y is the vertical node number of the control volume unit; n is the number of horizontally divided control volume units; m is the number of vertically divided control volume units; Heat sol The difference in heat between the inlet and outlet of the antifreeze solution in the tower; G sol，(x，y) h is the mass flow rate of the antifreeze solution at the control unit node (x,y); sol，(x，y) The enthalpy of the antifreeze solution at the control unit node (x,y); Water sol The difference in moisture content between the inlet and outlet of the antifreeze solution in the tower; t sol，(x，y) w represents the temperature of the antifreeze solution at the control unit node (x, y). sol，(x，y) This represents the mass fraction of the antifreeze solution at the control unit node (x, y).

[0062] Preferably, the heat and mass balance model of the heat and mass transfer control volume is as follows:

[0063] Hat air =Heat sol ;

[0064] Water air =Water sol ;

[0065]

[0066] In the formula: the subscript "air" indicates that the corresponding parameter uses air as the medium; the subscript "sol" indicates that the corresponding parameter uses the heat source tower solution as the medium; "x" is the horizontal node number of the control volume unit; "y" is the vertical node number of the control volume unit; "n" is the number of horizontally divided units of the control volume; "m" is the number of vertically divided units of the control volume; Heat air The difference in heat between the air entering and leaving the tower; Water sol The difference in moisture content between the inlet and outlet of the antifreeze solution; Heat sol The heat difference between the inlet and outlet of the antifreeze solution in the tower; Water so l represents the difference in moisture content between the inlet and outlet of the antifreeze solution; G sol，(x，y) w is the mass flow rate of the antifreeze solution at the control unit node (x,y); sol(x，y) This represents the mass fraction of the antifreeze solution at the control unit node (x, y).

[0067] Preferably, the heat transfer balance model of the heat source tower heat pump unit is as follows:

[0068] Q = f zr (t zf , t ln );

[0069] P = f gl (t zf , t lz );

[0070]

[0071] t zf =f zf (t sol，1 , t sol，2 );

[0072] t lz =f ln (t kt，1 , t kt，2 );

[0073] Q = f zr (f zf (t sol，1 , t sol，2 ), f ln (t kt，1 , t kt，2 ));

[0074] P = f gl (f zf (t sol，1 , t sol，2 ), f ln (t kt，1 , t kt，2 ));

[0075]

[0076] Where: Q is the heating capacity of the heat source tower heat pump unit; P is the compressor input power of the heat source tower heat pump unit; COP is the heating efficiency of the heat source tower heat pump unit; t zf The evaporation temperature of the heat pump unit in the heat source tower; t ln The condensing temperature of the heat pump unit in the heat source tower; t sol，1 For the antifreeze solution inlet of the heat pump unit in the heat source tower; t sol，2 The outlet temperature of the antifreeze solution in the heat pump unit of the heat source tower; t kt，1 The heat source tower heat pump unit's air conditioning hot water inlet; t kt，2 f is the outlet temperature of the hot water for the air conditioning unit of the heat source tower heat pump unit. zr f gl fzf f ln All of these are function symbols.

[0077] Preferably, the objective function for maximizing the heat supply of the heat source tower heat pump unit is as follows:

[0078] Q = P + C sol，(L，H) ×G sol，(L，H) ×(t sol，1 -t sol，2 )

[0079] Q = 4.187G kt ×(t kt，1 -t kt，2 )

[0080] t sol，1 =t sol，(L，H)

[0081] t sol，2 =t sol，(0，0)

[0082] COP = max(COP)

[0083]

[0084] In the formula: C sol，(L，H) G is the specific heat of the antifreeze solution at the outlet of the heat source tower. sol，(L，H) G is the mass flow rate of the antifreeze solution at the outlet of the heat source tower. kt The mass flow rate of hot water for air conditioning in the heat pump unit of the heat source tower; t sol，(L，H) The temperature of the antifreeze solution at the outlet of the heat source tower; t sol，(0，0) ρ is the temperature of the antifreeze solution at the inlet of the heat source tower. sol，(L，H)，t ρ represents the density of the antifreeze solution on the evaporator side of the heat pump unit in the heat source tower at time t. kt，t The density of the air-conditioning hot water on the condenser side of the heat pump unit at time t; n zf，t At time t, the water pump speed on the evaporator side of the heat pump unit in the heat source tower; n ln，t The speed of the water pump on the condenser side of the heat pump unit in the heat source tower at time t.

[0085] Thirdly, the present invention also provides a computer storage medium storing a computer program that, when executed by a processor, implements the heating control method of the heat source tower heat pump unit as described above.

[0086] Fourthly, the present invention also provides an electronic device, including a memory and a processor: the memory is used to store computer-executable instructions, and the processor is used to execute the computer-executable instructions, wherein when the computer-executable instructions are executed by the processor, the heating control method of the heat source tower heat pump unit as described above is implemented.

[0087] The beneficial effects of this invention are as follows: Antifreeze solution is selected as the representative circulating medium of the heat source tower in winter. The packing portion of the open crossflow heat source tower is considered as a two-dimensional computational domain along the airflow direction, divided into a finite number of control volume unit models. Dynamic models of air-side heat mass and solution-side heat mass are established to interact with the heat source tower. Considering unit parameters, a heat transfer balance model for the heat source tower heat pump unit is established. Based on the above models, an objective function for maximizing the heating capacity of the heat source tower heat pump unit is established. Known operating parameters are input, and the solution result of the objective function is obtained. The solution outlet temperature of the heat source tower is controlled by the solution result, and the pump frequency on both sides of the heat source tower heat pump unit is adjusted. Under the premise of meeting the heat load requirements, the thermal efficiency of the heat source tower heat pump unit is maximized.

[0088] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention and to implement it according to the contents of the specification, the preferred embodiments of the present invention are described in detail below with reference to the accompanying drawings. Specific embodiments of the present invention are given in detail below with reference to the accompanying drawings. Attached Figure Description

[0089] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this invention, illustrate exemplary embodiments of the invention and are used to explain the invention, but do not constitute an undue limitation of the invention. In the drawings:

[0090] Figure 1 A flowchart of a heating control method for a heat source tower heat pump unit provided in Example 1;

[0091] Figure 2 This is a schematic diagram of the heat and mass transfer control volume unit model in Example 1;

[0092] Figure 3 This is a flowchart of the solution to the objective function of maximizing the heat supply of the heat source tower heat pump unit in Example 1;

[0093] Figure 4 This is a module diagram of a heat supply control device for a heat source tower heat pump unit provided in Example 2. Detailed Implementation

[0094] The principles and features of the present invention are described below with reference to the accompanying drawings. The examples given are only for explaining the present invention and are not intended to limit the scope of the present invention.

[0095] Example 1

[0096] like Figure 1 As shown, this embodiment provides a heating control method for a heat source tower heat pump unit, including the following steps:

[0097] A. Divide the heat and mass transfer control volume of the heat source tower into several control volume unit models along the air flow direction;

[0098] In this embodiment, the heat and mass transfer control volume is the packing region, such as... Figure 2 As shown, the packing section of the open crossflow heat source tower is considered as a two-dimensional computational domain along the airflow direction, and divided into a finite number of heat and mass transfer control volume element models with a step size of 1, as detailed below:

[0099] (x, y) ∈ {(0, 0), (n, m)}

[0100]

[0101] In the formula: x is the horizontal node number of the control unit; y is the vertical node number of the control unit; n is the number of horizontally divided units of the control unit; m is the number of vertically divided units of the control unit; L is the length of the heat source tower packing area; H is the height of the heat source tower packing area.

[0102] B. Based on the control volume unit model, establish a dynamic model of air-side heat and mass that interacts with the heat source tower. This model is used to describe the heat change model of air, the dynamic change of mass (water vapor in the air), and the enthalpy value of the control unit, as detailed below:

[0103]

[0104] h air，(x，y) =1.01t air，(x，y) +1.001d air，(x，y) ×(2501+1.84t air，(x，y) );

[0105]

[0106] In the formula: the subscript 'air' indicates that the corresponding parameter uses air as the medium; 'x' is the horizontal node number of the control volume unit; 'y' is the vertical node number of the control volume unit; 'n' is the number of horizontally divided control volume units; 'm' is the number of vertically divided control volume units; 'Heat'... air G represents the heat difference between the air entering and leaving the tower. air，(x，y) H represents the dry air mass flow rate at control unit node (x,y); air，(x，y) The enthalpy of air at the control unit node (x,y); Water air The difference in water vapor content between the air entering and leaving the tower; d air，(x，y) This refers to the air humidity at the control unit node (x, y).

[0107] C. Based on the control volume unit model, establish a dynamic model of heat and mass on the solution side that interacts with the heat source tower. This model is used to describe the heat change model, mass (water content in the solution) change model, and enthalpy value of the control unit of the antifreeze solution, as detailed below:

[0108]

[0109] In the formula: the subscript sol indicates that the corresponding parameter uses the heat source tower solution as the medium; x is the horizontal node number of the control volume unit; y is the vertical node number of the control volume unit; n is the number of horizontally divided control volume units; m is the number of vertically divided control volume units; Heat sol The difference in heat between the inlet and outlet of the antifreeze solution in the tower; G sol，(x，y) h is the mass flow rate of the antifreeze solution at the control unit node (x,y); sol，(x，y) The enthalpy of the antifreeze solution at the control unit node (x,y); Wter sol The difference in moisture content between the inlet and outlet of the antifreeze solution in the tower; t sol，(x，y) w represents the temperature of the antifreeze solution at the control unit node (x, y). sol，(x，y) This represents the mass fraction of the antifreeze solution at the control unit node (x, y).

[0110] D. Based on the dynamic heat and mass model of the air side and the dynamic heat and mass model of the solution side, establish a heat and mass balance model for the heat transfer and mass transfer control volume of the heat source tower; this model is used to describe the dynamic heat and mass balance state of the entire packing region, as detailed below:

[0111] Hat air =Heat sol ;

[0112] Water air =Water sol ;

[0113]

[0114] In the formula: the subscript "air" indicates that the corresponding parameter uses air as the medium; the subscript "sol" indicates that the corresponding parameter uses the heat source tower solution as the medium; "x" is the horizontal node number of the control volume unit; "y" is the vertical node number of the control volume unit; "n" is the number of horizontally divided units of the control volume; "m" is the number of vertically divided units of the control volume; Heat air The difference in heat between the air entering and leaving the tower; Water sol The difference in moisture content between the inlet and outlet of the antifreeze solution; Heat sol The heat difference between the inlet and outlet of the antifreeze solution in the tower; Water sol The difference in moisture content between the inlet and outlet of the antifreeze solution in the tower; G sol，(x，y) w is the mass flow rate of the antifreeze solution at the control unit node (x,y); sol，(x，y)This represents the mass fraction of the antifreeze solution at the control unit node (x, y).

[0115] E. Based on the operating parameters of the heat source tower heat pump unit, a heat transfer balance model for the heat source tower heat pump unit is established. The intrinsic factors affecting the unit's heating efficiency include evaporation temperature, condensation temperature, evaporator outlet superheat, and condenser outlet recooling. Combined with the thermodynamic calculations of the vapor compression heating cycle, when the refrigerant used is constant, the unit's heating capacity and input power are mainly related to the evaporation and condensation temperatures. The simplified heating capacity and compressor input power of the heat source tower heat pump unit are as follows:

[0116] Q = f zr (t zf , t ln );

[0117] P = f gl (t zf , t lz );

[0118]

[0119] Where: Q is the heating capacity of the heat source tower heat pump unit; P is the compressor input power of the heat source tower heat pump unit; COP is the heating efficiency of the heat source tower heat pump unit; t zf The evaporation temperature of the heat pump unit in the heat source tower; t ln This refers to the condensing temperature of the heat pump unit in the heat source tower.

[0120] In the evaporator of a heat source tower heat pump unit, the refrigerant and antifreeze solution exchange heat indirectly, with only sensible heat changes occurring at the inlet and outlet of the antifreeze solution. In the condenser, the refrigerant and air conditioning hot water exchange heat indirectly. For the heat source tower heat pump unit, the inlet and outlet temperatures of the antifreeze solution and air conditioning hot water affect the unit's evaporation and condensation temperatures. The calculation model for the unit's heating capacity, compressor input power, and heating efficiency can be optimized as follows:

[0121] t zf =f zf (t sol，1 , t sol，2 );

[0122] t lz =f ln (t kt，1 , t kt，2 );

[0123] Q = f zr (f zf (t sol，1 , t sol，2 ), f ln (t kt，1 , t kt，2 ));

[0124] P = f gl (f zf (t sol，1 , t sol，2 ), f ln (t kt，1 , t kt，2 ));

[0125]

[0126] In the formula: t sol，1 For the antifreeze solution inlet of the heat pump unit in the heat source tower; t sol，2 The outlet temperature of the antifreeze solution in the heat pump unit of the heat source tower; t kt，1 The heat source tower heat pump unit's air conditioning hot water inlet; t kt，2 The inlet temperature of the hot water for the heat pump unit's air conditioning system is the same as the outlet temperature; f zr f gl f zf f ln All of these are function symbols.

[0127] F. Based on the heat mass balance model of the heat transfer and mass transfer control system and the heat transfer balance model of the heat source tower heat pump unit, an objective function to maximize the heat supply of the heat source tower heat pump unit is established. The objective function is solved to obtain the control results of the heat source tower heat pump and its heat transfer and mass transfer control system, as follows:

[0128] The objective function for maximizing the heat supply of the heat source tower heat pump unit is established as follows:

[0129] Q = P + C sol，(L，H) ×G sol，(L，H) ×(t sol，1 -t sol，2 )

[0130] Q = 4.187G kt ×(t kt，1 -t kt，2 )

[0131] t sol，1 =t sol，(L，H)

[0132] t sol，2 =t sol，(0，0)

[0133] COP = max(COP)

[0134]

[0135] In the formula: C sol，(L，H) G is the specific heat of the antifreeze solution at the outlet of the heat source tower. sol，(LLH) G is the mass flow rate of the antifreeze solution at the outlet of the heat source tower.kt The mass flow rate of hot water for air conditioning in the heat pump unit of the heat source tower; t sol，(L，H) The temperature of the antifreeze solution at the outlet of the heat source tower; t sol，(0，0) ρ is the temperature of the antifreeze solution at the inlet of the heat source tower. sol，(L，H)，t ρ represents the density of the antifreeze solution on the evaporator side of the heat pump unit at time t. kt，t The density of the air-conditioning hot water on the condenser side of the heat pump unit at time t; n zf，t At time t, the water pump speed on the evaporator side of the heat pump unit in the heat source tower; n ln，t The speed of the water pump on the condenser side of the heat pump unit in the heat source tower at time t.

[0136] like Figure 3 As shown, input the relevant calculation parameters, such as the air inlet temperature and humidity; and the assumed parameters at the current moment, such as the flow rate of the antifreeze solution entering the heat source tower and the air inlet flow rate. Enter the above model for calculation until the goal of maximizing the heating of the heat pump unit in the heat source tower is met. Output the control results at the current moment, such as the temperature, flow rate, and mass fraction of the antifreeze solution entering the tower, the temperature, flow rate, and humidity of the air entering and exiting the tower, the leaching temperature and flow rate of the air conditioning hot water, and the unit water pump speed, etc.

[0137] Example 2

[0138] like Figure 4 As shown, this embodiment provides a heating control device for a heat source tower heat pump unit, including:

[0139] The control volume unit model construction module is used to divide the heat and mass transfer control volume of the heat source tower into several control volume unit models along the air flow direction.

[0140] The air-side heat mass dynamic model construction module is used to establish an air-side heat mass dynamic model that interacts with the heat source tower based on the control volume unit model.

[0141] The solution-side heat and mass dynamic model construction module is used to establish a solution-side heat and mass dynamic model that interacts with the heat source tower based on the control volume unit model.

[0142] The heat mass balance model construction module of the heat transfer and mass transfer control body is used to establish the heat mass balance model of the heat source tower based on the air-side heat mass dynamic model and the solution-side heat mass dynamic model.

[0143] The heat transfer balance model of the heat source tower heat pump unit is used to establish the heat transfer balance model of the heat source tower heat pump unit based on the operating parameters of the heat source tower heat pump unit.

[0144] The heat source tower heat pump unit heating solution module is used to establish an objective function to maximize the heating of the heat source tower heat pump unit based on the heat mass balance model of the heat transfer and mass transfer control body and the heat transfer balance model of the heat source tower heat pump unit. The objective function is solved to obtain the control results of the heat source tower heat pump and its heat transfer and mass transfer control body.

[0145] The control unit model is as follows:

[0146] (x, y) ∈ {(0, 0), (n, m)}

[0147]

[0148] In the formula: x is the horizontal node number of the control unit; y is the vertical node number of the control unit; n is the number of horizontal division units of the control unit; m is the number of vertical division units of the control unit; L is the length of the heat source tower packing area; H is the height of the heat source tower packing area.

[0149] The dynamic model of air-side heat mass interacting with the heat source tower is as follows:

[0150] h air，(x，y) =1.01t air，(x，y) +1.001d air，(x，y) ×(2501+1.84t air，(x，y) );

[0151]

[0152] In the formula: the subscript 'air' indicates that the corresponding parameter uses air as the medium; 'x' is the horizontal node number of the control volume unit; 'y' is the vertical node number of the control volume unit; 'n' is the number of horizontally divided control volume units; 'm' is the number of vertically divided control volume units; heat air G represents the heat difference between the air entering and leaving the tower. air，(x，y) h is the dry air mass flow rate at the control unit node (x,y); air，(x，y) The enthalpy of air at the control unit node (x,y); Water air The difference in water vapor content between the air entering and leaving the tower; d air，(x，y) This refers to the air humidity at the control unit node (x, y).

[0153] The solution-side heat mass dynamic model that interacts with the heat source tower is as follows:

[0154]

[0155] In the formula: the subscript sol indicates that the corresponding parameter uses the heat source tower solution as the medium; x is the horizontal node number of the control volume unit; y is the vertical node number of the control volume unit; n is the number of horizontally divided control volume units; m is the number of vertically divided control volume units; Heat sol The difference in heat between the inlet and outlet of the antifreeze solution in the tower; G sol，(x，y) h is the mass flow rate of the antifreeze solution at the control unit node (x,y); sol，(x，y) The enthalpy of the antifreeze solution at the control unit node (x,y); Water sol The difference in moisture content between the inlet and outlet of the antifreeze solution in the tower; t sol，(x，y) w represents the temperature of the antifreeze solution at the control unit node (x, y). sol，(x，y) This represents the mass fraction of the antifreeze solution at the control unit node (x, y).

[0156] The heat and mass balance model of the heat and mass transfer control volume is as follows:

[0157] Heat air =Heat sol ;

[0158] Water air =Water sol ;

[0159]

[0160] In the formula: the subscript "air" indicates that the corresponding parameter uses air as the medium; the subscript "sol" indicates that the corresponding parameter uses the heat source tower solution as the medium; "x" is the horizontal node number of the control volume unit; "y" is the vertical node number of the control volume unit; "n" is the number of horizontally divided units of the control volume; "m" is the number of vertically divided units of the control volume; Heat air The difference in heat between the air entering and leaving the tower; Water sol The difference in moisture content between the inlet and outlet of the antifreeze solution; Heat sol The heat difference between the inlet and outlet of the antifreeze solution in the tower; Water sol The difference in moisture content between the inlet and outlet of the antifreeze solution in the tower; G sol，(x，y) w is the mass flow rate of the antifreeze solution at the control unit node (x,y); sol，(x，y) This represents the mass fraction of the antifreeze solution at the control unit node (x, y).

[0161] The heat transfer balance model of the heat source tower heat pump unit is as follows:

[0162] Q = f zr (t zf , t ln );

[0163] P = f gl (t zf, t lz );

[0164]

[0165] t zf =f zf (t sol，1 , t sol，2 );

[0166] t lz =f ln (t kt，1 , t kt，2 );

[0167] Q = f z r(f zf (t sol，1 , t sol，2 ), f ln (t kt，1 , t kt，2 ));

[0168] P = f gl (f zf (t sol，1 , t sol，2 )f ln (t kt，1 , t kt，2 ));

[0169]

[0170] Where: Q is the heating capacity of the heat source tower heat pump unit; P is the compressor input power of the heat source tower heat pump unit; COP is the heating efficiency of the heat source tower heat pump unit; t zf The evaporation temperature of the heat pump unit in the heat source tower; t ln The condensing temperature of the heat pump unit in the heat source tower; t sol，1 For the antifreeze solution inlet of the heat pump unit in the heat source tower; t sol，2 The outlet temperature of the antifreeze solution in the heat pump unit of the heat source tower; t kt，1 The heat source tower heat pump unit's air conditioning hot water inlet; t kt，2 f is the outlet temperature of the hot water for the air conditioning unit of the heat source tower heat pump unit. zr f gl f zf f ln All of these are function symbols.

[0171] The objective function for maximizing the heat supply of the heat source tower heat pump unit is as follows:

[0172] Q = P + C sol，(L，H) ×G sol，(L，H) ×(t sol，1 -t sol，2 )

[0173] Q = 4.187G kt ×(t kt，1 -t kt，2 )

[0174] t sol，1 =t sol，(L，H)

[0175] t sol，2 =t sol，(0，0)

[0176] COP = max(COP)

[0177]

[0178] In the formula: C sol，(L，H) G is the specific heat of the antifreeze solution at the outlet of the heat source tower. sol，(LLH) G is the mass flow rate of the antifreeze solution at the outlet of the heat source tower. kt The mass flow rate of hot water for air conditioning in the heat pump unit of the heat source tower; t sol，(L，H) The temperature of the antifreeze solution at the outlet of the heat source tower; t sol，(0，0) ρ is the temperature of the antifreeze solution at the inlet of the heat source tower. sol，(L，H)，t ρ represents the density of the antifreeze solution on the evaporator side of the heat pump unit in the heat source tower at time t. kt，t The density of the air-conditioning hot water on the condenser side of the heat pump unit at time t; n zf，t At time t, the water pump speed on the evaporator side of the heat pump unit in the heat source tower; n ln，t The speed of the water pump on the condenser side of the heat pump unit in the heat source tower at time t.

[0179] Example 3

[0180] A computer storage medium storing a computer program that, when executed by a processor, implements the heating control method for a heat source tower heat pump unit as described above.

[0181] Example 4

[0182] An electronic device includes a memory and a processor: the memory is used to store computer-executable instructions, and the processor is used to execute the computer-executable instructions, wherein when the computer-executable instructions are executed by the processor, the heating control method of the heat source tower heat pump unit as described above is implemented.

[0183] Those skilled in the art will understand that embodiments of this disclosure can be provided as methods, systems, or computer program products. Therefore, this disclosure can take the form of a completely hardware embodiment, a completely software embodiment, or an embodiment combining software and hardware aspects. Furthermore, this disclosure can take the form of a computer program product embodied on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.

[0184] This disclosure is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of this disclosure. It will be understood that each block of the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, special-purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, create a machine for implementing the flowchart illustrations. Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0185] These computer program instructions may also be stored in a computer-readable storage medium that can direct a computer or other programmable data processing device to function in a particular manner, such that the instructions stored in the computer-readable storage medium produce an article of manufacture including instruction means, which are implemented in a process Figure 1 One or more processes and / or boxes Figure 1 The function specified in one or more boxes.

[0186] These computer program instructions may also be loaded onto a computer or other programmable data processing equipment to cause a series of operational steps to be performed on the computer or other programmable equipment to produce a computer-implemented process, thereby providing instructions that execute on the computer or other programmable equipment for implementing the process. Figure 1 One or more processes and / or boxes Figure 1 The steps of the function specified in one or more boxes.

[0187] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention in any way. Those skilled in the art can readily implement the present invention based on the accompanying drawings and the above description. However, any modifications, alterations, or variations made by those skilled in the art without departing from the scope of the present invention, utilizing the disclosed technical content, are equivalent embodiments of the present invention. Furthermore, any modifications, alterations, or variations made to the above embodiments based on the essential technology of the present invention are still within the protection scope of the present invention.

Claims

1. A heating control method for a heat source tower heat pump unit, characterized in that, Includes the following steps: The heat and mass transfer control volume of the heat source tower is divided into several control volume unit models along the air flow direction; The control unit model is as follows: In the formula: Number the horizontal nodes of the control unit; Number the longitudinal nodes of the control unit; The number of horizontally divided units for the control body; The number of units to be divided vertically within the control volume; The length of the packing area in the heat source tower; The height of the packing area in the heat source tower; Based on the control volume unit model, dynamic models of heat and mass on the air side and the solution side that interact with the heat source tower are established respectively. The dynamic model of air-side heat mass interacting with the heat source tower is as follows: ； ； ； In the formula: the subscript air indicates that the corresponding parameter uses air as the medium; Number the horizontal nodes of the control unit; Number the longitudinal nodes of the control unit; The number of horizontally divided units for the control body; The number of units to be divided vertically within the control volume; This represents the heat difference between the air entering and leaving the tower. Let be the dry air mass flow rate at the control unit node (x, y); Here is the air enthalpy at the control unit node (x, y); The difference in water vapor content between the air entering and leaving the tower; The humidity of the air at the control node (x, y); Based on the dynamic models of heat and mass on the air side and the dynamic models of heat and mass on the solution side, a heat and mass balance model of the heat transfer and mass transfer control body of the heat source tower is established. Based on the operating parameters of the heat source tower heat pump unit, a heat transfer balance model of the heat source tower heat pump unit is established. Based on the heat mass balance model of the heat transfer and mass transfer control body and the heat transfer balance model of the heat source tower heat pump unit, an objective function to maximize the heat supply of the heat source tower heat pump unit is established, and the objective function is solved to obtain the control results of the heat source tower heat pump and its heat transfer and mass transfer control body.

2. The heating control method for a heat source tower heat pump unit according to claim 1, characterized in that, The solution-side heat mass dynamic model that interacts with the heat source tower is as follows: ； ； ； In the formula: the subscript sol indicates that the corresponding parameter uses the heat source tower solution as the medium; Number the horizontal nodes of the control unit; Number the longitudinal nodes of the control unit; The number of horizontally divided units for the control body; The number of units to be divided vertically within the control volume; The difference in heat between the inlet and outlet of the antifreeze solution in the tower; Let be the mass flow rate of the antifreeze solution at the control unit node (x, y); The enthalpy of the antifreeze solution at the control unit node (x, y); The difference in moisture content between the inlet and outlet of the antifreeze solution; The temperature of the antifreeze solution at the control unit node (x, y); The mass fraction of the antifreeze solution at the control unit node (x, y).

3. The heating control method for a heat source tower heat pump unit according to claim 2, characterized in that, The heat and mass balance model of the heat and mass transfer control volume is as follows: ； ； ， ； In the formula: the subscript air indicates that the corresponding parameter uses air as the medium; the subscript sol indicates that the corresponding parameter uses the solution in the heat source tower as the medium; Number the horizontal nodes of the control unit; Number the longitudinal nodes of the control unit; The number of horizontally divided units for the control body; The number of units to be divided vertically within the control volume; This represents the heat difference between the air entering and leaving the tower. The difference in moisture content between the inlet and outlet of the antifreeze solution; The difference in heat between the inlet and outlet of the antifreeze solution in the tower; The difference in moisture content between the inlet and outlet of the antifreeze solution; Let be the mass flow rate of the antifreeze solution at the control unit node (x, y); The mass fraction of the antifreeze solution at the control unit node (x, y).

4. The heating control method for a heat source tower heat pump unit according to claim 1, characterized in that, The heat transfer balance model of the heat source tower heat pump unit is as follows: ； ； ； ； ； ； ； ； In the formula: Provide heating capacity for the heat pump unit in the heat source tower; This is the input power for the compressor of the heat pump unit in the heat source tower; The heating efficiency of the heat source tower heat pump unit; The evaporation temperature of the heat pump unit in the heat source tower; This refers to the condensing temperature of the heat pump unit in the heat source tower. For the antifreeze solution inlet of the heat pump unit in the heat source tower; The outlet temperature of the antifreeze solution for the heat pump unit in the heat source tower; For the hot water inlet of the heat pump unit's air conditioning system; The outlet temperature of the hot water for the air conditioning unit of the heat source tower heat pump unit; f zr 、f gl 、f zf 、 f ln All of these are function symbols.

5. The heating control method for a heat source tower heat pump unit according to claim 4, characterized in that, The objective function for maximizing the heat supply of the heat source tower heat pump unit is as follows: In the formula: The specific heat of the antifreeze solution at the outlet of the heat source tower; This refers to the mass flow rate of the antifreeze solution at the outlet of the heat source tower. The mass flow rate of hot water for air conditioning in the heat pump unit of the heat source tower; The temperature of the antifreeze solution at the outlet of the heat source tower; The temperature of the antifreeze solution at the inlet of the heat source tower; The density of the antifreeze solution on the evaporator side of the heat pump unit in the heat source tower at time t; The density of the air-conditioning hot water on the condenser side of the heat pump unit in the heat source tower at time t; At time t, the water pump speed on the evaporator side of the heat pump unit in the heat source tower; The speed of the water pump on the condenser side of the heat pump unit in the heat source tower at time t.

6. A heating control device for a heat source tower heat pump unit, characterized in that, include: The control volume unit model construction module is used to divide the heat and mass transfer control volume of the heat source tower into several control volume unit models along the air flow direction. The control unit model is as follows: In the formula: Number the horizontal nodes of the control unit; Number the longitudinal nodes of the control unit; The number of horizontally divided units for the control body; The number of units to be divided vertically within the control volume; The length of the packing area in the heat source tower; The height of the packing area in the heat source tower; The module for constructing dynamic heat and mass models of air and solution sides is used to establish dynamic heat and mass models of air and solution sides that interact with the heat source tower, based on the control volume unit model. The dynamic model of air-side heat mass interacting with the heat source tower is as follows: ； ； ； In the formula: the subscript air indicates that the corresponding parameter uses air as the medium; Number the horizontal nodes of the control unit; Number the longitudinal nodes of the control unit; The number of horizontally divided units for the control body; The number of units to be divided vertically within the control volume; This represents the heat difference between the air entering and leaving the tower. Let be the dry air mass flow rate at the control unit node (x, y); Here is the air enthalpy at the control unit node (x, y); The difference in water vapor content between the air entering and leaving the tower; The humidity of the air at the control node (x, y); The heat mass balance model construction module of the heat transfer and mass transfer control body is used to establish the heat mass balance model of the heat source tower based on the air-side heat mass dynamic model and the solution-side heat mass dynamic model. The heat transfer balance model of the heat source tower heat pump unit is used to establish the heat transfer balance model of the heat source tower heat pump unit based on the operating parameters of the heat source tower heat pump unit. The heat source tower heat pump unit heating solution module is used to establish an objective function to maximize the heating of the heat source tower heat pump unit based on the heat mass balance model of the heat transfer and mass transfer control body and the heat transfer balance model of the heat source tower heat pump unit, and solve the objective function to obtain the control results of the heat source tower heat pump and its heat transfer and mass transfer control body.

7. The heating control device for a heat source tower heat pump unit according to claim 6, characterized in that, The solution-side heat mass dynamic model that interacts with the heat source tower is as follows: ； ； ； In the formula: the subscript sol indicates that the corresponding parameter uses the heat source tower solution as the medium; Number the horizontal nodes of the control unit; Number the longitudinal nodes of the control unit; The number of horizontally divided units for the control body; The number of units to be divided vertically within the control volume; The difference in heat between the inlet and outlet of the antifreeze solution in the tower; Let be the mass flow rate of the antifreeze solution at the control unit node (x, y); The enthalpy of the antifreeze solution at the control unit node (x, y); The difference in moisture content between the inlet and outlet of the antifreeze solution; The temperature of the antifreeze solution at the control unit node (x, y); The mass fraction of the antifreeze solution at the control unit node (x, y).

8. The heating control device for a heat source tower heat pump unit according to claim 6, characterized in that, The heat and mass balance model of the heat and mass transfer control volume is as follows: ； ； ， ； In the formula: the subscript air indicates that the corresponding parameter uses air as the medium; the subscript sol indicates that the corresponding parameter uses the solution in the heat source tower as the medium; Number the horizontal nodes of the control unit; Number the longitudinal nodes of the control unit; The number of horizontally divided units for the control body; The number of units to be divided vertically within the control volume; This represents the heat difference between the air entering and leaving the tower. The difference in moisture content between the inlet and outlet of the antifreeze solution; The difference in heat between the inlet and outlet of the antifreeze solution in the tower; The difference in moisture content between the inlet and outlet of the antifreeze solution; Let be the mass flow rate of the antifreeze solution at the control unit node (x, y); The mass fraction of the antifreeze solution at the control unit node (x, y).

9. The heating control device for a heat source tower heat pump unit according to claim 8, characterized in that, The heat transfer balance model of the heat source tower heat pump unit is as follows: ； ； ； ； ； ； ； ； In the formula: Provide heating capacity for the heat pump unit in the heat source tower; This is the input power for the compressor of the heat pump unit in the heat source tower; The heating efficiency of the heat source tower heat pump unit; The evaporation temperature of the heat pump unit in the heat source tower; This refers to the condensing temperature of the heat pump unit in the heat source tower. For the antifreeze solution inlet of the heat pump unit in the heat source tower; The outlet temperature of the antifreeze solution for the heat pump unit in the heat source tower; For the hot water inlet of the heat pump unit's air conditioning system; The outlet temperature of the hot water for the air conditioning unit of the heat source tower heat pump unit; f zr 、f gl 、f zf 、 f ln All of these are function symbols.

10. The heating control device for a heat source tower heat pump unit according to claim 9, characterized in that, The objective function for maximizing the heat supply of the heat source tower heat pump unit is as follows: In the formula: The specific heat of the antifreeze solution at the outlet of the heat source tower; This refers to the mass flow rate of the antifreeze solution at the outlet of the heat source tower. The mass flow rate of hot water for air conditioning in the heat pump unit of the heat source tower; The temperature of the antifreeze solution at the outlet of the heat source tower; The temperature of the antifreeze solution at the inlet of the heat source tower; The density of the antifreeze solution on the evaporator side of the heat pump unit in the heat source tower at time t; The density of the air-conditioning hot water on the condenser side of the heat pump unit in the heat source tower at time t; At time t, the water pump speed on the evaporator side of the heat pump unit in the heat source tower; The speed of the water pump on the condenser side of the heat pump unit in the heat source tower at time t.

11. A computer storage medium storing a computer program, characterized in that, When the computer program is executed by the processor, it implements the heating control method of the heat source tower heat pump unit as described in any one of claims 1-5.

12. An electronic device, characterized in that, Includes a memory and a processor: the memory is used to store computer-executable instructions, and the processor is used to execute the computer-executable instructions, which, when executed by the processor, implement the heating control method of the heat source tower heat pump unit as described in any one of claims 1-5.

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