Heat supply control method and system of heat source tower heat pump unit, electronic equipment and storage medium

Abstract

The invention relates to a heat supply control method and system of a heat source tower heat pump unit, electronic equipment and a storage medium. The heat supply control method specifically comprises the following steps that a heat and mass transfer control body of a heat source tower is divided into a plurality of control body unit models in the air flowing direction; based on the control body unit model, establishing an air side heat quality dynamic model and a solution side heat quality dynamic model interacting with the heat source tower; based on the air side heat mass dynamic model and the solution side heat mass dynamic model, establishing a heat mass balance model of a heat and mass transfer control body of the heat source tower; establishing a heat transfer balance model of the heat source tower heat pump unit based on the working parameters of the heat source tower heat pump unit; and 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, establishing a target function for maximizing heat supply of the heat source tower heat pump unit, and solving the target function to obtain regulation and control results of the heat source tower heat pump and the heat transfer and mass transfer control body thereof.

Description

Technical Field

[0001] The present invention relates to the technical field of heat pump heating, and in particular to a heating control method, system, electronic equipment and storage medium for a heat source tower heat pump unit. Background Art

[0002] Energy is an important component and driving force of social development. In the past, the prosperity of my country's real estate industry led to the continuous expansion of the scale of construction, and the proportion of energy consumed by the operation of total building commodities continued to rise. Among them, the energy of heating and air conditioning accounts for as much as 50% to 70% of the total energy consumption of buildings. With the pursuit of comfortable living and production environment by people in my country's hot summer and cold winter areas, the energy consumption of air conditioning systems also accounts for a large proportion. As a major energy consumer in the construction field, the air conditioning system plays an absolute role in solving energy and environmental problems. Therefore, it is extremely important to find renewable alternative energy sources. With the decline of the real estate industry in the past two years, although the volume of new buildings has decreased, some existing buildings have entered the stage of renovation. The heat source tower heat pump energy supply system can be used in both winter and summer. It can be used in new buildings without other cold and heat sources; it can also replace the original gas boilers and other high-energy consumption equipment for heating in the renovation of buildings.

[0003] In summer, the heat source tower in the heat source tower heat pump energy supply system is used as a cooling tower, and cooling water circulates in the heat source tower; in winter, antifreeze circulates in the heat source tower, which not only solves the problem of frosting and defrosting of the air source heat pump, but also improves the heating efficiency. The heating efficiency of the heat pump unit in winter is an important parameter. In addition to affecting the heating effect of the unit, it directly affects the operating costs of the system. The antifreeze in the heat source tower exchanges sensible heat and latent heat with the air. The heating efficiency of the heat source tower heat pump system will be high only when the outdoor air dry bulb temperature is high and the humidity is high. The outdoor air parameters change at any time. The air and solution parameters entering the tower determine the solution parameters leaving the tower, and at the same time affect the heating efficiency of the heat source tower heat pump unit. How to maintain the efficient operation of the unit under the premise of meeting the heating load has become an issue that needs urgent attention. Summary of the invention

[0004] The present 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 heat and mass transfer control bodies and the conservation of energy of the heat source tower heat pump unit, a related mathematical model of the heat source tower and the heat source tower heat pump unit is established, and a heating logic of the heat source tower heat pump unit is constructed with the maximum heating efficiency of the heat source tower heat pump unit as the goal, so as to reduce the thermal efficiency of the unit under the premise of meeting the system heat load.

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

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

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

[0008] Based on the control volume unit model, the dynamic model of heat quality on the air side and the dynamic model of heat quality on the solution side interacting with the heat source tower are established respectively;

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

[0010] Based on the working 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 and mass transfer control body and the heat transfer balance model of the heat source tower heat pump unit, an objective function for maximizing 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 and mass transfer control body.

[0012] Preferably, the control body unit model is to limit the air and solution heat exchange area of ​​the heat source tower to the heat and mass transfer control body area, regard the packing part of the open cross-flow heat source tower along the air flow direction as a two-dimensional calculation domain, divide it into a finite number of heat and mass transfer control body units, and divide it 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 body unit; y is the vertical node number of the control body unit; n is the number of horizontal division units of the control body; m is the number of vertical division units of the control body; L is the length of the packing area of ​​the heat source tower; H is the height of the packing area of ​​the heat source tower.

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

[0018]

[0019] Where: the subscript air refers to the corresponding parameter with air as the medium; 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; heat air G is the heat difference between air entering and leaving the tower; air，(x，y) is the dry air mass flow rate at the control cell node (x, y); h air，(x，y)is the air enthalpy at the cell node (x, y); Water air is the difference in water vapor content between air entering and leaving the tower; d air，(x，y) is the air humidity at the control cell node (x, y).

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

[0021]

[0022] In the formula: the subscript sol refers to the corresponding parameter with the heat source tower solution as the medium; 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; Heat sol G is the heat difference between the antifreeze solution entering and leaving the tower; sol，(x，y) is the mass flow rate of the antifreeze solution at the control cell node (x, y); h sol，(x，y) is the enthalpy of the antifreeze solution at the cell node (x, y); Water sol is the difference in water content of the antifreeze solution entering and leaving the tower; t sol，(x，y) is the temperature of the antifreeze solution at the control cell node (x, y); w sol，(x，y) is the mass fraction of the antifreeze solution at the control cell node (x, y).

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

[0024] Heat air =Heat sol

[0025] Water air =Water sol

[0026]

[0027] Where: the subscript air refers to the corresponding parameter with air as the medium; the subscript sol refers to the corresponding parameter with the heat source tower solution as the medium; 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; Heat air Water is the heat difference between air entering and leaving the tower; sol The difference in water content of the antifreeze solution entering and leaving the tower; Heat sol Water is the heat difference between the antifreeze solution entering and leaving the tower; sol is the difference in water content of the antifreeze solution entering and leaving the tower; C sol，(x，y) is the mass flow rate of the antifreeze solution at the control cell node (x, y); wsol(x，y) is the mass fraction of the antifreeze solution at the control cell node (x, y).

[0028] Preferably, the heat transfer balance model of the heat source tower heat pump unit considers the internal factors of the unit's heating efficiency, including evaporation temperature, condensation temperature, superheat at the evaporator outlet, and recooling at the condenser outlet. Combined with the thermodynamic calculation of the steam compression heating cycle, the calculation model of the heating capacity of the heat source tower heat pump unit, the compressor input power, and the heating efficiency 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 input power of the compressor of the heat source tower heat pump unit; COP is the heating efficiency of the heat source tower heat pump unit; t zf is the evaporation temperature of the heat pump unit in the heat source tower; t ln is the condensing temperature of the heat pump unit in the heat source tower; t sol，1It is the import of antifreeze solution for heat source tower heat pump unit; t sol，2 is the outlet temperature of the antifreeze solution of the heat source tower heat pump unit; t kt，1 Heat source tower heat pump unit air conditioning hot water inlet; t kt，2 f is the outlet temperature of hot water from the heat pump unit in the heat source tower; zr 、f gl 、f zf 、f ln 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] Where: 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 antifreeze solution at the outlet of the heat source tower; kt is the mass flow rate of hot water for air conditioning in the heat source tower heat pump unit; t sol，(L，H) is the temperature of the antifreeze solution at the outlet of the heat source tower; t sol，(0，0) is the temperature of the antifreeze solution at the entrance of the heat source tower; ρ sol，(L，H)，t Refers to the density of the antifreeze solution on the evaporator side of the heat pump unit in the heat source tower at time t; ρ kt，t Refers to the density of air-conditioning hot water on the condenser side of the heat pump unit in the heat source tower at time t; n zf，t Refers to the speed of the water pump on the evaporator side of the heat source tower heat pump unit at time t; n ln，t Refers to the speed of the water pump on the condenser side of the heat source tower heat pump unit at time t.

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

[0047] A control body unit model building module is used to divide the heat and mass transfer control body of the heat source tower into several control body unit models along the air flow direction;

[0048] The air side and solution side heat quality dynamic model building module is used to respectively establish the air side heat quality dynamic model and the solution side heat quality dynamic model interacting with the heat source tower based on the control body unit model;

[0049] A heat and mass balance model building module for a heat and mass transfer control body is used to build a heat and mass balance model for the heat and mass transfer control body of a heat source tower based on a heat and mass dynamic model on the air side and a heat and mass dynamic model on the solution side;

[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 working 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 for maximizing the heat supply 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, solve the objective function, and obtain the control results of the heat source tower heat pump and its heat and mass transfer control body.

[0052] Preferably, the control volume 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 body unit; y is the vertical node number of the control body unit; n is the number of horizontal division units of the control body; m is the number of vertical division units of the control body; L is the length of the packing area of ​​the heat source tower; H is the height of the packing area of ​​the heat source tower.

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

[0057]

[0058] Where: the subscript air refers to the corresponding parameter with air as the medium; 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; Heat air G is the heat difference between air entering and leaving the tower; air，(x，y) is the dry air mass flow rate at the control cell node (x, y); h air，(x，y) is the air enthalpy at the cell node (x, y); Water airis the difference in water vapor content between air entering and leaving the tower; d air，(x，y) is the air humidity at the control cell node (x, y).

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

[0060]

[0061] In the formula: the subscript sol refers to the corresponding parameter with the heat source tower solution as the medium; 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; Heat sol G is the heat difference between the antifreeze solution entering and leaving the tower; sol，(x，y) is the mass flow rate of the antifreeze solution at the control cell node (x, y); h sol，(x，y) is the enthalpy of the antifreeze solution at the cell node (x, y); Water sol is the difference in water content of the antifreeze solution entering and leaving the tower; t sol，(x，y) is the temperature of the antifreeze solution at the control cell node (x, y); w sol，(x，y) is the mass fraction of the antifreeze solution at the control cell node (x, y).

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

[0063] Hat air =Heat sol ;

[0064] Water air =Water sol ;

[0065]

[0066] Where: the subscript air refers to the corresponding parameter with air as the medium; the subscript sol refers to the corresponding parameter with the heat source tower solution as the medium; 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; Heat air Water is the heat difference between air entering and leaving the tower; sol The difference in water content of the antifreeze solution entering and leaving the tower; Heat sol Water is the heat difference between the antifreeze solution entering and leaving the tower; so l is the difference in water content of the antifreeze solution entering and leaving the tower; G sol，(x，y) is the mass flow rate of the antifreeze solution at the control cell node (x, y); w sol(x，y) is the mass fraction of the antifreeze solution at the control cell 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 is the evaporation temperature of the heat pump unit in the heat source tower; t ln is the condensing temperature of the heat pump unit in the heat source tower; t sol，1 It is the import of antifreeze solution for heat source tower heat pump unit; t sol，2 is the outlet temperature of the antifreeze solution of the heat source tower heat pump unit; t kt，1 Heat source tower heat pump unit air conditioning hot water inlet; t kt，2 f is the outlet temperature of hot water from the heat pump unit in the heat source tower; zr 、f gl 、fzf 、f ln 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] Where: 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 antifreeze solution at the outlet of the heat source tower; kt is the mass flow rate of hot water for air conditioning in the heat source tower heat pump unit; t sol，(L，H) is the temperature of the antifreeze solution at the outlet of the heat source tower; t sol，(0，0) is the temperature of the antifreeze solution at the entrance of the heat source tower; ρ sol，(L，H)，t Refers to the density of the antifreeze solution on the evaporator side of the heat pump unit in the heat source tower at time t; ρ kt，t Refers to the density of air-conditioning hot water on the condenser side of the heat pump unit in the heat source tower at time t; n zf，t Refers to the speed of the water pump on the evaporator side of the heat source tower heat pump unit at time t; n ln，t Refers to the speed of the water pump on the condenser side of the heat source tower heat pump unit at time t.

[0085] In a third aspect, the present invention further provides a computer storage medium, wherein the computer-readable storage medium stores a computer program, and when the computer program is executed by a processor, the heating control method of the heat source tower heat pump unit as described above is implemented.

[0086] In a fourth aspect, the present invention also provides an electronic device comprising a memory and a processor: the memory is used to store computer executable instructions, the processor is used to execute the computer executable instructions, and 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 the present invention are as follows: an antifreeze solution is selected as a representative of the winter circulation medium of the heat source tower, the packing part of the open cross-flow heat source tower is regarded as a two-dimensional calculation domain along the air flow direction, divided into a finite number of control body unit models, and an air-side heat mass dynamic model and a solution-side heat mass dynamic model interacting with the heat source tower are established; considering the unit parameters, a heat transfer balance model of the heat pump unit of the heat source tower is established; based on the above model, an objective function for maximizing the heating capacity of the heat pump unit of the heat source tower is established, and known working parameters are input to obtain the solution result of the objective function, and the solution outlet temperature of the heat source tower is controlled by the solution result of the objective function, and the water pump frequency on the two sides of the heat pump unit of the heat source tower is adjusted to ensure that the thermal efficiency of the heat pump unit of the heat source tower is maximized under the premise of meeting the heat load demand.

[0088] The above description is only an overview of the technical solution of the present invention. In order to more clearly understand the technical means of the present invention and implement it according to the contents of the specification, the following is a detailed description of the preferred embodiments of the present invention in conjunction with the accompanying drawings. The specific implementation of the present invention is given in detail by the following embodiments and their accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0089] The drawings described herein are used to provide a further understanding of the present invention and constitute a part of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

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

[0091] Figure 2 Schematic diagram of the heat and mass transfer control unit model in Example 1;

[0092] Figure 3 A flow chart for solving 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 heating control device for a heat source tower heat pump unit provided in Example 2. DETAILED DESCRIPTION

[0094] The principles and features of the present invention are described below in conjunction with the accompanying drawings. The examples given are only used to explain the present invention and are not used 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, comprising the following steps:

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

[0098] In this embodiment, the heat and mass transfer control body is the packing area, such as Figure 2 As shown in the figure, the packing part of the open cross-flow heat source tower is regarded as a two-dimensional calculation domain along the air flow direction, and is divided into a finite number of heat and mass transfer control volume unit models with a step size of 1, as follows:

[0099] (x, y)∈{(0, 0), (n, m)}

[0100]

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

[0102] B. Based on the control volume unit model, a dynamic model of air-side heat quality interacting with the heat source tower is established; this model is used to describe the heat change model of the air, the dynamic change of the quality (water vapor in the air) and the control unit enthalpy value, as follows:

[0103]

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

[0105]

[0106] Where: the subscript air refers to the corresponding parameter with air as the medium; 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; Heat air G is the heat difference between air entering and leaving the tower; air，(x，y) is the dry air mass flow rate at the control cell node (x, y); H air，(x，y) is the air enthalpy at the cell node (x, y); Water air is the difference in water vapor content between air entering and leaving the tower; d air，(x，y) is the air humidity at the control cell node (x, y).

[0107] C. Based on the control volume unit model, a dynamic model of heat quality on the solution side interacting with the heat source tower is established; this model is used to describe the heat change model of the antifreeze solution, the mass (water content in the solution) change model and the control unit enthalpy value, as follows:

[0108]

[0109] In the formula: the subscript sol refers to the corresponding parameter with the heat source tower solution as the medium; 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; Heat sol G is the heat difference between the antifreeze solution entering and leaving the tower; sol，(x，y) is the mass flow rate of the antifreeze solution at the control cell node (x, y); h sol，(x，y) is the enthalpy of the antifreeze solution at the control cell node (x, y); Wter sol is the difference in water content of the antifreeze solution entering and leaving the tower; t sol，(x，y) is the temperature of the antifreeze solution at the control cell node (x, y); w sol，(x，y) is the mass fraction of the antifreeze solution at the control cell node (x, y).

[0110] D. Based on the dynamic model of heat mass on the air side and the dynamic model of heat mass on the solution side, a heat mass balance model of the heat transfer and mass transfer control body of the heat source tower is established; this model is used to describe the dynamic balance state of heat and mass in the entire packing area, as follows:

[0111] Hat air =Heat sol ;

[0112] Water air =Water sol ;

[0113]

[0114] Where: the subscript air refers to the corresponding parameter with air as the medium; the subscript sol refers to the corresponding parameter with the heat source tower solution as the medium; 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; Heat air Water is the heat difference between air entering and leaving the tower; sol The difference in water content of the antifreeze solution entering and leaving the tower; Heat sol Water is the heat difference between the antifreeze solution entering and leaving the tower; sol G is the difference in water content of the antifreeze solution entering and leaving the tower; sol，(x，y) is the mass flow rate of the antifreeze solution at the control cell node (x, y); w sol，(x，y)is the mass fraction of the antifreeze solution at the control cell node (x, y).

[0115] E. Based on the working parameters of the heat source tower heat pump unit, establish the heat transfer balance model of the heat source tower heat pump unit; consider the internal factors that affect the heating efficiency of the unit, including evaporation temperature, condensation temperature, superheat at the evaporator outlet, and recooling at the condenser outlet. Combined with the thermal calculation of the steam compression heating cycle, when the refrigerant used is constant, the heating capacity and input power of the unit are mainly related to the evaporation temperature and condensation temperature. Simplify the heating capacity and compressor input power of the heat source tower heat pump unit, 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 is the evaporation temperature of the heat pump unit in the heat source tower; t ln is the condensing temperature of the heat pump unit in the heat source tower.

[0120] The refrigerant in the evaporator of the heat source tower heat pump unit exchanges heat indirectly with the antifreeze solution, and the antifreeze solution at the inlet and outlet of the evaporator only has sensible heat changes; the refrigerant in the condenser of the heat source tower heat pump unit exchanges heat indirectly with the air conditioning hot water. For the heat source tower heat pump unit, the inlet and outlet temperatures of the antifreeze solution and the air conditioning hot water affect the evaporation temperature and condensation temperature of the unit. The calculation model of 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] Where: t sol，1 It is the import of antifreeze solution for heat source tower heat pump unit; t sol，2 is the outlet temperature of the antifreeze solution of the heat source tower heat pump unit; t kt，1 Heat source tower heat pump unit air conditioning hot water inlet; t kt，2 : The air conditioning hot water inlet of the heat source tower heat pump unit is the outlet temperature; f zr 、f gl 、f zf 、f ln These are function symbols.

[0127] F. 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 for maximizing 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, as follows:

[0128] The objective function of 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] Where: 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 antifreeze solution at the outlet of the heat source tower;kt is the mass flow rate of hot water for air conditioning in the heat source tower heat pump unit; t sol，(L，H) is the temperature of the antifreeze solution at the outlet of the heat source tower; t sol，(0，0) is the temperature of the antifreeze solution at the entrance of the heat source tower; ρ sol，(L，H)，t Refers to the density of the antifreeze solution on the evaporator side of the heat pump unit in the heat source tower at time t; ρ kt，t Refers to the density of air-conditioning hot water on the condenser side of the heat pump unit in the heat source tower at time t; n zf，t Refers to the speed of the water pump on the evaporator side of the heat source tower heat pump unit at time t; n ln，t Refers to the speed of the water pump on the condenser side of the heat source tower heat pump unit at time t.

[0136] like Figure 3 As shown, relevant calculation parameters are input, such as air inlet temperature and moisture content; and the assumed parameters at the current moment, such as the antifreeze solution flow rate and air inlet flow rate of the heat source tower, and the above model calculation is entered until the goal of maximizing the heating supply of the heat source tower heat pump unit is met, and the control results at the current moment are output, such as the antifreeze solution inlet temperature, flow rate, mass fraction, air inlet and outlet temperature, flow rate, humidity content, air conditioning hot water leaching temperature, flow rate, 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, comprising:

[0139] A control body unit model building module is used to divide the heat and mass transfer control body of the heat source tower into several control body unit models along the air flow direction;

[0140] The air side heat quality dynamic model building module is used to build the air side heat quality dynamic model interacting with the heat source tower based on the control volume unit model;

[0141] Solution side heat quality dynamic model building module, used to build the solution side heat quality dynamic model interacting with the heat source tower based on the control volume unit model;

[0142] A heat and mass balance model building module for a heat and mass transfer control body is used to build a heat and mass balance model for the heat and mass transfer control body of a heat source tower based on a heat and mass dynamic model on the air side and a heat and mass dynamic model on the solution side;

[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 working 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 for maximizing the heat supply 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, solve the objective function, and obtain the control results of the heat source tower heat pump and its heat and mass transfer control body.

[0145] The control volume 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 body unit; y is the vertical node number of the control body unit; n is the number of horizontal division units of the control body; m is the number of vertical division units of the control body; L is the length of the packing area of ​​the heat source tower; H is the height of the packing area of ​​the heat source tower.

[0149] The dynamic model of air-side heat quality 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] Where: the subscript air refers to the corresponding parameter with air as the medium; 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; heat air G is the heat difference between air entering and leaving the tower; air，(x，y) is the dry air mass flow rate at the control cell node (x, y); h air，(x，y) is the air enthalpy at the cell node (x, y); Water air is the difference in water vapor content between air entering and leaving the tower; d air，(x，y) is the air humidity at the control cell node (x, y).

[0153] The dynamic model of heat quality of the solution side interacting with the heat source tower is as follows:

[0154]

[0155] In the formula: the subscript sol refers to the corresponding parameter with the heat source tower solution as the medium; 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; Heat sol G is the heat difference between the antifreeze solution entering and leaving the tower; sol，(x，y) is the mass flow rate of the antifreeze solution at the control cell node (x, y); h sol，(x，y) is the enthalpy of the antifreeze solution at the cell node (x, y); Water sol is the difference in water content of the antifreeze solution entering and leaving the tower; t sol，(x，y) is the temperature of the antifreeze solution at the control cell node (x, y); w sol，(x，y) is the mass fraction of the antifreeze solution at the control cell node (x, y).

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

[0157] Heat air =Heat sol ;

[0158] Water air =Water sol ;

[0159]

[0160] Where: the subscript air refers to the corresponding parameter with air as the medium; the subscript sol refers to the corresponding parameter with the heat source tower solution as the medium; 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; Heat air Water is the heat difference between air entering and leaving the tower; sol The difference in water content of the antifreeze solution entering and leaving the tower; Heat sol Water is the heat difference between the antifreeze solution entering and leaving the tower; sol G is the difference in water content of the antifreeze solution entering and leaving the tower; sol，(x，y) is the mass flow rate of the antifreeze solution at the control cell node (x, y); w sol，(x，y) is the mass fraction of the antifreeze solution at the control cell 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 is the evaporation temperature of the heat pump unit in the heat source tower; t ln is the condensing temperature of the heat pump unit in the heat source tower; t sol，1 It is the import of antifreeze solution for heat source tower heat pump unit; t sol，2 is the outlet temperature of the antifreeze solution of the heat source tower heat pump unit; t kt，1 Heat source tower heat pump unit air conditioning hot water inlet; t kt，2 f is the outlet temperature of hot water from the heat pump unit in the heat source tower; zr 、f gl 、f zf 、f ln These are function symbols.

[0171] The objective function of 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] Where: 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 antifreeze solution at the outlet of the heat source tower; kt is the mass flow rate of hot water for air conditioning in the heat source tower heat pump unit; t sol，(L，H) is the temperature of the antifreeze solution at the outlet of the heat source tower; t sol，(0，0) is the temperature of the antifreeze solution at the entrance of the heat source tower; ρ sol，(L，H)，t Refers to the density of the antifreeze solution on the evaporator side of the heat pump unit in the heat source tower at time t; ρ kt，t Refers to the density of air-conditioning hot water on the condenser side of the heat pump unit in the heat source tower at time t; n zf，t Refers to the speed of the water pump on the evaporator side of the heat source tower heat pump unit at time t; n ln，t Refers to the speed of the water pump on the condenser side of the heat source tower heat pump unit at time t.

[0179] Example 3

[0180] A computer storage medium, wherein the computer readable storage medium stores a computer program, and when the computer program is executed by a processor, the heating control method of the heat source tower heat pump unit as described above is implemented.

[0181] Example 4

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

[0183] Those skilled in the art will appreciate that the embodiments of the present disclosure may be provided as methods, systems or computer program products. Therefore, the present disclosure may take the form of a complete hardware embodiment, a complete software embodiment or an embodiment combining software and hardware. Moreover, the present disclosure may take the form of a computer program product implemented 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] The present disclosure is described with reference to flowcharts and / or block diagrams of methods, devices (systems) and computer program products according to embodiments of the present disclosure. It should be understood that each process and / or block in the flowchart and / or block diagram and the combination of processes and / or blocks in the flowchart and / or block diagram can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, a special-purpose computer, an embedded processor or other programmable data processing device to produce a machine, so that the instructions executed by the processor of the computer or other programmable data processing device generate instructions for implementing the processes in the flowchart and / or block diagram. Figure 1 A process or multiple processes and / or boxes Figure 1 A device that provides the functions specified in a block or multiple blocks.

[0185] These computer program instructions may also be stored in a computer-readable memory capable of directing a computer or other programmable data processing device to operate in a specific manner, so that the instructions stored in the computer-readable memory produce an article of manufacture comprising an instruction device, which implements the process Figure 1 A process or multiple processes and / or boxes Figure 1 A function specified in one or more boxes.

[0186] These computer program instructions can also be loaded onto a computer or other programmable data processing device so that a series of operating steps are executed on the computer or other programmable device to produce a computer-implemented process, thereby providing instructions for implementing the process. Figure 1 A process or multiple processes and / or boxes Figure 1 The steps for the functions specified in one or more boxes.

[0187] The above description is only a preferred embodiment of the present invention and does not limit the present invention in any form. Any ordinary technician in the industry can smoothly implement the present invention as shown in the drawings and described above. However, any equivalent changes, modifications and evolutions made by technicians familiar with the profession without departing from the scope of the technical solution of the present invention using the technical content disclosed above are all equivalent embodiments of the present invention. At the same time, any equivalent changes, modifications and evolutions made to the above embodiments based on the essential technology of the present invention are still within the protection scope of the technical solution of the present invention.

Claims

1. A heating control method for a heat source tower heat pump unit, characterized in that: The following steps are involved: The heat and mass transfer control body of the heat source tower is divided into several control body unit models along the air flow direction; Based on the control volume unit model, the dynamic model of heat mass on the air side and the dynamic model of heat mass on the solution side interacting with the heat source tower are established respectively; Based on the dynamic model of heat mass on the air side and the dynamic model of heat mass on the solution side, a heat mass balance model of the heat and mass transfer control body of the heat source tower is established; Based on the working 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 for maximizing 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 and mass transfer control body.

2. A heating control method for a heat source tower heat pump unit according to claim 1, characterized in that: The control volume unit model is as follows: (x, y)∈{(0, 0), (n, m)} In the formula: x is the horizontal node number of the control body unit; y is the vertical node number of the control body unit; n is the number of horizontal division units of the control body; m is the number of vertical division units of the control body; L is the length of the packing area of ​​the heat source tower; H is the height of the packing area of ​​the heat source tower.

3. The heating control method of a heat source tower heat pump unit according to claim 1, characterized in that: The dynamic model of air-side heat quality interacting with the heat source tower is as follows: h air，(x，y) =1.01t air，(x，y) +1.001d air，(x，y) ×(2501+1.84t air，(x，y) ); Where: the subscript air refers to the corresponding parameter with air as the medium; 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; Heat air G is the heat difference between air entering and leaving the tower; air，(x，y) is the dry air mass flow rate at the control cell node (x, y); h air，(x，y) is the air enthalpy at the cell node (x, y); Water air is the difference in water vapor content between air entering and leaving the tower; d air，(x，y) is the air humidity at the control cell node (x, y).

4. The heating control method of a heat source tower heat pump unit according to claim 1, characterized in that: The dynamic model of heat quality of the solution side interacting with the heat source tower is as follows: In the formula: the subscript sol refers to the corresponding parameter with the heat source tower solution as the medium; 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; Heat sol G is the heat difference between the antifreeze solution entering and leaving the tower; sol，(x，y) is the mass flow rate of the antifreeze solution at the control cell node (x, y); h sol，(x，y) is the enthalpy of the antifreeze solution at the cell node (x, y); Water sol is the difference in water content of the antifreeze solution entering and leaving the tower; t sol，(x，y) is the temperature of the antifreeze solution at the control cell node (x, y); w sol，(x，y) is the mass fraction of the antifreeze solution at the control cell node (x, y).

5. A heating control method for a heat source tower heat pump unit according to claim 4, characterized in that: The heat and mass balance model of the heat and mass transfer control body is as follows: Heat air =Heat sol ; Water air =Water sol ; Where: the subscript air refers to the corresponding parameter with air as the medium; the subscript sol refers to the corresponding parameter with the heat source tower solution as the medium; 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; Heat air Water is the heat difference between air entering and leaving the tower; sol It is the difference in water content of the antifreeze solution entering and leaving the tower; Heat sol Water is the heat difference between the antifreeze solution entering and leaving the tower; sol G is the difference in water content of the antifreeze solution entering and leaving the tower; sol，(x，y) is the mass flow rate of the antifreeze solution at the control cell node (x, y); w sol，(x，y) is the mass fraction of the antifreeze solution at the control cell node (x, y).

6. A 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: Q=f zr (t zf ,t ln ); P=f gl (t zf ,t ln ); t zf =f zf (t sol，1 ,t sol，2 ); t lz =f ln (t kt，1 ,t kt，2 ); Q=f zr (f zf (t sol，1 ,t sol，2 ),f ln (t kt，1 ,t kt，2 )); P=f gl (f zf (t sol，1 ,t sol，2 ),f ln (t kt，1 t kt，2 )); Where: Q is the heating capacity of the heat source tower heat pump unit; P is the input power of the compressor of the heat source tower heat pump unit; COP is the heating efficiency of the heat source tower heat pump unit; t zf is the evaporation temperature of the heat pump unit in the heat source tower; t ln is the condensing temperature of the heat pump unit in the heat source tower; t sol，1 It is the import of antifreeze solution for heat source tower heat pump unit; t sol，2 is the outlet temperature of the antifreeze solution of the heat source tower heat pump unit; t kt，1 It is the hot water inlet of the heat source tower heat pump unit; t kt，2 f is the outlet temperature of hot water from the heat pump unit in the heat source tower; zr 、f gl 、f zf 、f ln These are function symbols.

7. A heating control method for a heat source tower heat pump unit according to claim 6, characterized in that: The objective function of maximizing the heat supply of the heat source tower heat pump unit is as follows: Q=P+C sol，(L，H) ×G sol，(L，H) ×(t sol，1 -t sol，2 ) Q=4.187G kt ×(t kt，1 -t kt，2 ) t sol，1 =t sol，(L，H) t sol，2 =t sol，(0，0) COP=max(COP) Where: 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 antifreeze solution at the outlet of the heat source tower; kt is the air conditioning hot water mass flow of the heat source tower heat pump unit; t sol，(L，H) is the temperature of the antifreeze solution at the outlet of the heat source tower; t sol，(0，0) is the temperature of the antifreeze solution at the entrance of the heat source tower; ρ sol，(L，H)，t Refers to the density of the antifreeze solution on the evaporator side of the heat pump unit in the heat source tower at time t; ρ kt，t Refers to the density of air-conditioning hot water on the condenser side of the heat pump unit in the heat source tower at time t; n zf，t Refers to the speed of the water pump on the evaporator side of the heat source tower heat pump unit at time t; n ln，t Refers to the speed of the water pump on the condenser side of the heat source tower heat pump unit at time t.

8. A heating control device for a heat source tower heat pump unit, characterized in that: include: A control body unit model building module is used to divide the heat and mass transfer control body of the heat source tower into several control body unit models along the air flow direction; The air side and solution side heat quality dynamic model building module is used to respectively establish the air side heat quality dynamic model and the solution side heat quality dynamic model interacting with the heat source tower based on the control body unit model; A heat and mass balance model building module for a heat and mass transfer control body is used to build a heat and mass balance model for the heat and mass transfer control body of a heat source tower based on a heat and mass dynamic model on the air side and a heat and mass dynamic model on the solution side; 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 working 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 for maximizing the heat supply 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, solve the objective function, and obtain the control results of the heat source tower heat pump and its heat and mass transfer control body.

9. A heating control device for a heat source tower heat pump unit according to claim 8, characterized in that: The control volume unit model is as follows: (x, y)∈{(0, 0), (n, m)} In the formula: x is the horizontal node number of the control body unit; y is the vertical node number of the control body unit; n is the number of horizontal division units of the control body; m is the number of vertical division units of the control body; L is the length of the packing area of ​​the heat source tower; H is the height of the packing area of ​​the heat source tower.

10. A heating control device for a heat source tower heat pump unit according to claim 8, characterized in that: The dynamic model of air-side heat quality interacting with the heat source tower is as follows: h air，(x，y) =1.01t air，(x，y) +1.001d air，(x，y) ×(2501+1.84t air，(x，y) ); Where: the subscript air refers to the corresponding parameter with air as the medium; 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; Heat air G is the heat difference between air entering and leaving the tower; air，(x，y) is the dry air mass flow rate at the control cell node (x, y); h air，(x，y) is the air enthalpy at the cell node (x, y); Water air is the difference in water vapor content between air entering and leaving the tower; d air，(x，y) is the air humidity at the control cell node (x, y).

11. A heating control device for a heat source tower heat pump unit according to claim 8, characterized in that: The dynamic model of heat quality of the solution side interacting with the heat source tower is as follows: In the formula: the subscript sol refers to the corresponding parameter with the heat source tower solution as the medium; 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; Heat sol G is the heat difference between the antifreeze solution entering and leaving the tower; sol，(x，y) is the mass flow rate of the antifreeze solution at the control cell node (x, y); h sol，(x，y) is the enthalpy of the antifreeze solution at the cell node (x, y); Water sol is the difference in water content of the antifreeze solution entering and leaving the tower; t sol，(x，y) is the temperature of the antifreeze solution at the control cell node (x, y); w sol，(x，y) is the mass fraction of the antifreeze solution at the control cell node (x, y).

12. A heating control device for a heat source tower heat pump unit according to claim 8, characterized in that: The heat and mass balance model of the heat and mass transfer control body is as follows: Heat air =Heat sol Water air =Water sol Where: the subscript air refers to the corresponding parameter with air as the medium; the subscript sol refers to the corresponding parameter with the heat source tower solution as the medium; 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; Heat air Water is the heat difference between air entering and leaving the tower; sol It is the difference in water content of the antifreeze solution entering and leaving the tower; Heat sol Water is the heat difference between the antifreeze solution entering and leaving the tower; sol G is the difference in water content of the antifreeze solution entering and leaving the tower; sol，(x，y) is the mass flow rate of the antifreeze solution at the control cell node (x, y); w sol，(x，y) is the mass fraction of the antifreeze solution at the control cell node (x, y).

13. A heating control device for a heat source tower heat pump unit according to claim 12, characterized in that: The heat transfer balance model of the heat source tower heat pump unit is as follows: Q=f zr (t zf ,t ln ) P=f gl (t zf ,t lz ) t zf =f zf (t sol，1 ,t sol，2 ) t lz =f ln (t kt，1 ,t kt，2 ) Q=f zr (f zf (t sol，1 ,t sol，2 ),f ln (t kt，1 ,t kt，2 )) P=f gl (f zf (t sol，1 ,t sol，2 ),f ln (t kt，1 ,t kt，2 )) Where: Q is the heating capacity of the heat source tower heat pump unit; P is the input power of the compressor of the heat source tower heat pump unit; COP is the heating efficiency of the heat source tower heat pump unit; t zf is the evaporation temperature of the heat pump unit in the heat source tower; t ln is the condensing temperature of the heat pump unit in the heat source tower; t sol，1 It is the import of antifreeze solution for heat source tower heat pump unit; t sol，2 is the outlet temperature of the antifreeze solution of the heat source tower heat pump unit; t kt，1 It is the hot water inlet of the heat source tower heat pump unit; t kt，2 f is the outlet temperature of hot water from the heat pump unit in the heat source tower; zr 、f gl 、f zf 、f ln These are function symbols.

14. A heating control device for a heat source tower heat pump unit according to claim 13, characterized in that: The objective function of maximizing the heat supply of the heat source tower heat pump unit is as follows: Q=P+C sol，(L，H) ×G sol，(L，H) ×(t sol，1 -t sol，2 ) Q=4.187G kt ×(t kt，1 -t kt，2 ) t sol，1 =t sol，(L，H) t sol，2 =t sol，(0，0) COP=max(COP) Where: C sol，(L，H) G is the specific heat of the antifreeze solution at the outlet of the heat source tower; sol，(L，H) The mass flow rate of the antifreeze solution at the outlet of the heat source tower; G kt , air conditioning hot water mass flow rate of heat source tower heat pump unit; t sol，(L，H) is the temperature of the antifreeze solution at the outlet of the heat source tower; t sol，(0，0) is the temperature of the antifreeze solution at the entrance of the heat source tower; ρ sol，(L，H)，t is the density of the antifreeze solution on the evaporator side of the heat pump unit in the heat source tower at time t; ρ kt，t is the density of hot water for air conditioning on the condenser side of the heat pump unit in the heat source tower at time t; n zf，t is the water pump speed on the evaporator side of the heat source tower heat pump unit at time t; n ln，t is the water pump speed on the condenser side of the heat source tower heat pump unit at time t.

15. A computer storage medium, wherein the computer readable storage medium stores a computer program, characterized in that: When the computer program is executed by a processor, a heating control method for a heat source tower heat pump unit as described in any one of claims 1 to 7 is implemented.

16. An electronic device, characterized in that: It 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. When the computer-executable instructions are executed by the processor, the heating control method of the heat source tower heat pump unit as described in any one of claims 1-7 is implemented.

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