Thermal and hydraulic balance control method and system for heating system

Abstract

The present invention discloses a method and system for controlling the thermal and hydraulic balance of a heating system. The method and system for controlling the thermal and hydraulic balance of a heating system obtain the hydraulic / thermal characteristics of the heating system by creating a dynamic mathematical model of the heating system and simulating the mathematical model. Then, the hydraulic / thermal characteristics of the heating system are analyzed to obtain various control parameters of an overall balance control strategy. Then, based on indoor temperature separation technology and an overall balance control strategy of the heating system, the thermal and hydraulic properties of the heating system are controlled, thereby ensuring the heating quality of heat users, improving the energy efficiency of the heating system, and reducing the operating costs of the heating system.

Description

Technical Field

[0001] The present invention relates to the technical field of centralized heating system control, and in particular to a method and system for controlling thermal and hydraulic balance of a heating system. Background Art

[0002] At present, the balance control strategy of the heating system plays a vital role in ensuring the quality of heating for users, optimizing operation, and energy conservation and emission reduction. Especially for large-scale centralized / regional heating systems, the difficulty of balance control gradually increases with the expansion of the scale of heating, the variability of the system structure (heat source and heat network), the increase in the length of the heat network, and the differences in the terminals (heat exchange stations and heat users). In addition to leading to complaints caused by reduced thermal comfort of users, the imbalance of the balanced operating conditions also greatly increases the operating costs of the system, increases pollutant emissions, damages the local ecological environment and system, and affects the realization of the "dual carbon" and "dual control" goals. Therefore, finding and solving the thermal and hydraulic balance control strategy of the heating system is of great significance to the current domestic thermal power generation capacity of more than 10 billion m 2 For the scale of urban heating, it has significant social, economic, environmental and management benefits. Summary of the invention

[0003] The object of the present invention is to provide a method and system for controlling the thermal and hydraulic balance of a heating system, thereby ensuring the heating quality of heat users, improving the energy efficiency of the heating system, and reducing the operating costs of the heating system.

[0004] To achieve the above object, the present invention provides a method for controlling thermal and hydraulic balance of a heating system, comprising:

[0005] S1: Based on the law of conservation of mass and the law of conservation of thermodynamic energy, and based on the design parameters, physical parameters and operation data of the heating system, a simulation analysis is performed to obtain the actual dynamic mathematical model of the heating system;

[0006] S2: By simulating the actual dynamic mathematical model of the heating system, a relationship model between the outdoor temperature and the heat source water supply temperature when the heat source meets the minimum indoor design temperature requirement is obtained, a relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station when the indoor temperature of each heat exchange station user is met, and a relationship model between the secondary network circulation flow ratio of the heat exchange station and the outdoor temperature, solar radiation intensity, and indoor heat gain intensity;

[0007] S3: inputting the outdoor temperature value detected in real time into the relationship model between the outdoor temperature and the heat source water supply temperature to determine the heat source water supply temperature control value to adjust the heat source fuel supply;

[0008] S4: simulating the actual dynamic mathematical model of the heating system to obtain the sum of the required circulation flow rates of the primary sides of each heat exchange station and adjusting the heat source circulation flow rate in combination with the designed circulation flow rate of the primary side of the heat exchange station;

[0009] S5: inputting the real-time detected outdoor temperature value into the relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station to calculate the secondary network water supply temperature setting value, and performing closed-loop compensation control on the secondary network water supply temperature of the heat exchange station according to the error between the secondary network water supply temperature setting value and the measured value of the secondary network water supply temperature;

[0010] S6: The real-time detected outdoor temperature value, solar radiation intensity and average indoor heat gain intensity are input into the relationship model between the secondary network circulation flow ratio of the heat exchange station and the outdoor temperature, solar radiation intensity and indoor heat gain intensity to calculate the secondary network circulation flow of the heat exchange station, and open-loop compensation control of the secondary side circulation flow of the heat exchange station is performed based on the secondary network circulation flow of the heat exchange station.

[0011] Optionally, the S1 includes:

[0012] According to the law of conservation of mass and the law of conservation of thermodynamic energy, and based on the design parameters, physical parameters and operating data of the heating system, an ideal dynamic mathematical model of the heating system is created;

[0013] Based on the basic data and operation data of the heating system, the ideal dynamic mathematical model of the heating system is simulated to obtain the heat transfer area surplus coefficient of the heat exchanger and the heat transfer area surplus coefficient of the radiator of each heat exchange station of the heating system;

[0014] The surplus coefficient of heat transfer area of ​​the heat exchanger and the surplus coefficient of heat transfer area of ​​the radiator of each heat exchange station of the heating system are input into the ideal dynamic mathematical model of the heating system to obtain the actual dynamic mathematical model of the heating system.

[0015] Optionally, S1 also includes: verifying the dynamic response steady-state value of the ideal dynamic mathematical model of the heating system under the conditions of designed outdoor temperature, designed heat network circulation flow and without considering solar radiation and indoor heat gain, so as to determine the accuracy of the ideal dynamic mathematical model of the heating system when the outdoor temperature changes.

[0016] Optionally, the heating system includes three heat exchange stations, and the heat transfer area surplus coefficients of the heat exchangers and the heat transfer area surplus coefficients of the three heat exchange stations are 1.34, 1.4, 1.45, 1.33, 1.41 and 1.35 respectively.

[0017] Optionally, the mathematical description of the actual dynamic mathematical model of the heating system is expressed as:

[0018]

[0019] Among them, T s1 , T r1 , T r2Respectively represent the heat source outlet temperature, heat source return water temperature, and secondary network return water temperature, in °C; C b , C x1 , C x2 , C ht , C a Respectively represent the heat capacity of the boiler body, the primary side of the heat exchanger, the secondary side of the heat exchanger, the radiator and the indoor air, in J / ℃; t represents time, in s; G fd Indicates the rated fuel quantity of the boiler in Nm 3 / s; HV represents the lower heating value of fuel, the unit is J / Nm 3 ; η b represents boiler efficiency; c w Indicates the specific heat of water, the unit is J / Kg℃; G 1d , G 2d Respectively represent the design circulation flow of the primary network and the secondary network, the unit is Kg / s; f x 、f ht Respectively represent the heat transfer area surplus coefficient of the heat exchanger and radiator; U x , U ht , U e They represent the comprehensive heat transfer coefficient of the heat exchanger, radiator and enclosure structure, in W / ℃; LMTD represents the logarithmic mean temperature difference, in ℃; c represents the coefficient in the radiator heat transfer coefficient test; F w Indicates the exterior window area, in m 2 ; F represents the heating area, the unit is m 2 ;q s Indicates the solar radiation intensity in W / m 2 ;q int Indicates the indoor heat gain intensity, in W / m 2 ; i represents the number of the heat exchange station, i=1~3.

[0020] Optionally, the S5 includes:

[0021] Input the real-time detected outdoor temperature value into the relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station to calculate the secondary network water supply temperature setting value, and calculate the error between the secondary network water supply temperature setting value and the actual measured value of the secondary network water supply temperature;

[0022] The error between the set value of the secondary network water supply temperature and the measured value of the secondary network water supply temperature is input into the controller algorithm formula to calculate the flow control parameter of the primary side electric regulating valve of the heat exchange station, wherein the secondary network water supply temperature of the heat exchange station adopts a closed-loop control circuit;

[0023] The flow control parameters of the electric regulating valve on the primary side of the heat exchange station are used to adjust the opening of the electric regulating valve to adjust the water supply temperature of the secondary network in real time.

[0024] Optionally, the open-loop compensation control of the secondary side circulation flow of the heat exchange station according to the secondary network circulation flow of the heat exchange station in S6 specifically includes: frequency conversion control or intermittent control of the circulating water pump of the heat exchange station.

[0025] On the other hand, the present invention also provides a thermal and hydraulic balance control system for a heating system, comprising:

[0026] The mathematical model building module is used to obtain the actual dynamic mathematical model of the heating system by simulation analysis based on the law of conservation of mass and the law of conservation of thermodynamic energy, and based on the design parameters, physical parameters and operation data of the heating system;

[0027] A relationship model acquisition module is used to obtain a relationship model between the outdoor temperature and the heat source water supply temperature when the heat source meets the minimum indoor design temperature requirement by simulating the actual dynamic mathematical model of the heating system, a relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station when the indoor temperature of each heat exchange station user is met, and a relationship model between the secondary network circulation flow ratio of the heat exchange station and the outdoor temperature, solar radiation intensity, and indoor heat gain intensity;

[0028] A first heat source control module, used for inputting the outdoor temperature value detected in real time into the relationship model between the outdoor temperature and the heat source water supply temperature to determine the heat source water supply temperature control value, so as to adjust the heat source fuel supply amount;

[0029] The second heat source control module is used to adjust the heat source circulation flow rate by simulating the actual dynamic mathematical model of the heat supply system to obtain the sum of the circulation flow rates required on the primary side of each heat exchange station and combining the designed circulation flow rate on the primary side of the heat exchange station;

[0030] The first compensation control module is used to input the outdoor temperature value detected in real time into the relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station to calculate the secondary network water supply temperature setting value, and perform closed-loop compensation control on the secondary network water supply temperature of the heat exchange station according to the error between the secondary network water supply temperature setting value and the measured value of the secondary network water supply temperature;

[0031] The second compensation control module is used to input the real-time detected outdoor temperature value, solar radiation intensity and average indoor heat gain intensity into the relationship model between the secondary network circulation flow ratio of the heat exchange station and the outdoor temperature, solar radiation intensity and indoor heat gain intensity to calculate the secondary network circulation flow of the heat exchange station, and perform open-loop compensation control on the secondary side circulation flow of the heat exchange station based on the secondary network circulation flow of the heat exchange station.

[0032] On the other hand, the present invention also provides an electronic device, comprising: a processor and a memory, wherein the memory stores computer-readable instructions, and when the computer-readable instructions are executed by the processor, the thermal and hydraulic balance control method of the base heating system as described above is implemented.

[0033] On the other hand, the present invention further provides a computer-readable storage medium having a computer program stored thereon, wherein the computer program, when executed by a processor, implements the thermal and hydraulic balance control method of a heating system as described above.

[0034] The method of the present invention has the following advantages:

[0035] The thermal and hydraulic balance control method of the heating system of the present invention obtains the hydraulic / thermal characteristics of the heating system by creating a dynamic mathematical model of the heating system and simulating the mathematical model; then, through the hydraulic / thermal characteristics analysis of the heating system, various control parameters of the overall balance control strategy are obtained, and then the thermal and hydraulic of the heating system are controlled based on the indoor temperature separation technology and the overall balance control strategy of the heating system, thereby ensuring the heating quality of heat users, improving the energy efficiency of the heating system, and reducing the operating costs of the heating system. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] Figure 1 It is a schematic flow chart of a method for controlling thermal and hydraulic balance of a heating system according to the present invention;

[0037] Figure 2 It is the process flow and control principle diagram of the heating system;

[0038] Figure 3 It is the dynamic response curve diagram of the ideal dynamic data model of the heating system;

[0039] Figure 4 It is the dynamic response curve diagram of the actual dynamic data model of the heating system;

[0040] Figure 5 It is the dynamic response curve of the heating system under control strategy 1;

[0041] Figure 6 It is the dynamic response curve of the heating system under control strategy 2;

[0042] Figure 7 It is a schematic diagram of the dynamic changes of heat source fuel and circulation flow control variables;

[0043] Figure 8 It is a schematic diagram of the dynamic changes of the secondary network circulation flow control variables of each heat exchange station;

[0044] Fig. 9 It is a schematic diagram of the dynamic change of the balance rate of the heating system;

[0045] Fig.10 It is a structural block diagram of the thermal and hydraulic balance control system of the heating system of the present invention. DETAILED DESCRIPTION

[0046] The following embodiments are used to illustrate the present invention, but are not used to limit the scope of the present invention. In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings of the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, rather than all the embodiments. Based on the described embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work belong to the scope of protection of the present invention.

[0047] For large-scale centralized / regional heating systems, they are usually divided into two types according to the heat network structure balance conditions: thermal balance of primary / secondary networks and hydraulic balance of primary / secondary networks, and their balance calculation and evaluation methods are different. Specifically:

[0048] 1) Hydraulic balance of primary network

[0049] Applicable to constant flow system, evaluate the difference between actual circulation flow and designed circulation flow; variable flow system does not have hydraulic balance problem. The calculation method of hydraulic balance rate of constant flow system is:

[0050]

[0051] Where: r 1hyb represents the hydraulic balance rate of the primary network, in %; i represents the designated heat exchange station; n represents the number of heat exchange stations; G1 represents the actual circulation flow rate on the primary side of the heat exchange station, in T / h; G 1d -The design circulation flow rate of the primary side of the heat exchange station, in T / h.

[0052] 2) Primary network thermal balance

[0053] Evaluate the degree of deviation of the personalized water temperature on the secondary side of the heat exchange station. The water temperature can usually be the personalized secondary side water supply temperature or the secondary side average temperature. The calculation method of the primary network thermal balance rate is (taking the secondary side water supply temperature as an example):

[0054]

[0055] Where: r 1hb Indicates the thermal balance rate of the primary network; T s2sp Indicates the set value of the secondary network water supply temperature of the specified heat exchange station, in °C; T s2 It indicates the actual value of the secondary network water supply temperature of the specified heat exchange station, in °C.

[0056] 3) Secondary network thermal balance

[0057] To evaluate the deviation between the indoor set temperature and the actual temperature of the heat user, the thermal balance rate of the secondary network is calculated as follows:

[0058]

[0059] Where: r 2hb Indicates the thermal balance rate of the primary and secondary networks; T zsp Indicates the personalized indoor temperature of the designated heat exchange station, in °C; T z -Specify the actual indoor temperature of the heat exchange station in °C.

[0060] 4) Secondary network hydraulic balance

[0061] To evaluate the consistency of indoor temperature of users, it is necessary to classify and calculate according to the nature of user usage. The calculation formula of secondary network hydraulic balance rate is as follows:

[0062]

[0063]

[0064] Where: r 2hyb Indicates the hydraulic balance rate of the secondary network; T zarg Indicates the average indoor temperature in °C.

[0065] The following control strategies can be adopted for the thermal balance of the primary / secondary network of the heating system and the hydraulic balance control of the primary / secondary network:

[0066] 1) Heat source heat supply control

[0067] (1) Control the water supply temperature of the heat source and adjust the heat source fuel supply;

[0068] (2) Control the primary network circulation flow and adjust the primary network circulation pump frequency.

[0069] 2) Primary network hydraulic balance control

[0070] (1) Constant flow system: adjust the opening of the electric regulating valve on the primary side of the heat exchange station;

[0071] (2) Variable flow system: does not exist.

[0072] 3) Primary network thermal balance control

[0073] Since heat exchange stations have different thermal characteristics, it is necessary to obtain personalized characteristics of heat exchange stations. Based on the design parameters, physical parameters and actual operation data of each heat exchange station, combined with the laws of thermodynamics, a dynamic mathematical model of the heating system is created, and its personalized parameters are obtained through simulation after verification. Based on personalized secondary side water temperature control of the heat exchange station, the thermal balance of the primary network is achieved.

[0074] 4) Heat exchange station and indoor temperature control (thermal and hydraulic balance control on the secondary side of the heat exchange station)

[0075] (1) Thermal balance control of secondary network of heat exchange station

[0076] By controlling the opening of the electric regulating valve on the primary side of the heat exchange station to track the personalized secondary network water supply temperature and compensate for the outdoor temperature change, the first-level compensation control strategy of the heat exchange station based on the indoor temperature separation technology is achieved.

[0077] (2) Hydraulic balance control of secondary network of heat exchange station

[0078] By adjusting the secondary circulation flow of the heat exchange station, the additional heat gain of heat users (solar radiation and indoor heat gain) is compensated, that is, the secondary compensation control strategy of the heat exchange station based on the indoor temperature separation technology, thereby achieving the hydraulic balance of the secondary network of the heat exchange station.

[0079] (3) Combined control of thermal and hydraulic balance of heat exchange station

[0080] The purpose of joint control is to ensure the heating quality of heat users, improve system energy efficiency and reduce system operating costs.

[0081] (4) Heat source supply and demand matching prediction control

[0082] For large-scale centralized / regional heating systems, the heat source and heat network structure, heat network length and heat capacity should be considered. Therefore, the "source-network" heating load matching control of the heat source needs to adopt a predictive control method, given the water supply temperature and circulation flow of the heat source.

[0083] For the thermal balance of the primary / secondary network and the hydraulic balance of the primary / secondary network, the embodiment of the present invention provides an overall balance control strategy, see Figure 1 As shown, an embodiment of the present invention provides a method for controlling thermal and hydraulic balance of a heating system, comprising:

[0084] S1: Based on the law of conservation of mass and the law of conservation of thermodynamic energy, and based on the design parameters, physical parameters and operation data of the heating system, a simulation analysis is performed to obtain the actual dynamic mathematical model of the heating system;

[0085] Optionally, in this embodiment, S1 includes:

[0086] According to the law of conservation of mass and the law of conservation of thermodynamic energy, and based on the design parameters, physical parameters and operating data of the heating system, an ideal dynamic mathematical model of the heating system is created;

[0087] Based on the basic data and operation data of the heating system, the ideal dynamic mathematical model of the heating system is simulated to obtain the heat transfer area surplus coefficient of the heat exchanger and the heat transfer area surplus coefficient of the radiator of each heat exchange station in the heating system;

[0088] The surplus coefficient of heat transfer area of ​​heat exchangers and the surplus coefficient of heat transfer area of ​​radiators of each heat exchange station of the heating system are input into the ideal dynamic mathematical model of the heating system to obtain the actual dynamic mathematical model of the heating system.

[0089] Optionally, S1 in this embodiment also includes: verifying the dynamic response steady-state value of the ideal dynamic mathematical model of the heating system under the conditions of designed outdoor temperature, designed heat network circulation flow and without considering solar radiation and indoor heat gain, so as to determine the accuracy of the ideal dynamic mathematical model of the heating system when the outdoor temperature changes.

[0090] Optionally, the heating system in this embodiment includes three heat exchange stations, and the heat transfer area surplus coefficients of the heat exchangers and the heat transfer area surplus coefficients of the three heat exchange stations are 1.34, 1.4, 1.45, 1.33, 1.41 and 1.35 respectively.

[0091] Optionally, the mathematical description of the actual dynamic mathematical model of the heating system in this embodiment is expressed as:

[0092]

[0093] Among them, T s1 , T r1 , T r2 Respectively represent the heat source outlet temperature, heat source return water temperature, and secondary network return water temperature, in °C; C b , C x1 , C x2 , C ht , C a Respectively represent the heat capacity of the boiler body, the primary side of the heat exchanger, the secondary side of the heat exchanger, the radiator and the indoor air, in J / ℃; t represents time, in s; G fd Indicates the rated fuel quantity of the boiler in Nm 3 / s; HV represents the lower heating value of fuel, the unit is J / Nm 3 ; η b represents boiler efficiency; c w Indicates the specific heat of water, the unit is J / Kg℃; G 1d , G 2d Respectively represent the design circulation flow of the primary network and the secondary network, the unit is Kg / s; f x、f ht Respectively represent the heat transfer area surplus coefficient of the heat exchanger and radiator; U x , U ht , U e They represent the comprehensive heat transfer coefficient of the heat exchanger, radiator and enclosure structure, in W / ℃; LMTD represents the logarithmic mean temperature difference, in ℃; c represents the coefficient in the radiator heat transfer coefficient test; F w Indicates the exterior window area, in m 2 ; F represents the heating area, the unit is m 2 ;q s Indicates the solar radiation intensity in W / m 2 ;q int Indicates the indoor heat gain intensity, in W / m 2 ; i represents the number of the heat exchange station, i=1~3.

[0094] S2: By simulating the actual dynamic mathematical model of the heating system, the relationship model between the outdoor temperature and the heat source water supply temperature when the heat source meets the minimum indoor design temperature requirement is obtained, the relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station when the indoor temperature of each heat exchange station user is met, and the relationship model between the secondary network circulation flow ratio of the heat exchange station and the outdoor temperature, solar radiation intensity, and indoor heat gain intensity;

[0095] S3: inputting the outdoor temperature value detected in real time into the relationship model between the outdoor temperature and the heat source water supply temperature to determine the heat source water supply temperature control value to adjust the heat source fuel supply;

[0096] S4: By simulating the actual dynamic mathematical model of the heating system, the heat source circulation flow rate is adjusted by combining the sum of the circulation flow rates required on the primary side of each heat exchange station and the designed circulation flow rate on the primary side of the heat exchange station;

[0097] S5: Input the real-time detected outdoor temperature value into the relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station to calculate the secondary network water supply temperature setting value, and perform closed-loop compensation control on the secondary network water supply temperature of the heat exchange station according to the error between the secondary network water supply temperature setting value and the measured value of the secondary network water supply temperature;

[0098] Optionally, in this embodiment, S5 is a first-level compensation control strategy of a heat exchange station based on indoor temperature separation technology, specifically including:

[0099] The real-time detected outdoor temperature value is input into the relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station to calculate the secondary network water supply temperature setting value, and the error between the secondary network water supply temperature setting value and the secondary network water supply temperature actual value is calculated;

[0100] The error between the set value of the secondary network water supply temperature and the measured value of the secondary network water supply temperature is input into the controller algorithm formula to calculate the flow control parameters of the primary side electric regulating valve of the heat exchange station, where the secondary network water supply temperature of the heat exchange station adopts a closed-loop control circuit;

[0101] The flow control parameters of the electric regulating valve on the primary side of the heat exchange station are used to adjust the opening of the electric regulating valve to adjust the water supply temperature of the secondary network in real time.

[0102] S6: The real-time detected outdoor temperature value, solar radiation intensity and average indoor heat gain intensity are input into the relationship model between the secondary network circulation flow ratio of the heat exchange station and the outdoor temperature, solar radiation intensity and indoor heat gain intensity to calculate the secondary network circulation flow of the heat exchange station, and open-loop compensation control of the secondary side circulation flow of the heat exchange station is performed based on the secondary network circulation flow of the heat exchange station.

[0103] Optionally, S6 in this embodiment is a secondary compensation control strategy for the heat exchange station based on indoor temperature separation technology, which performs open-loop compensation control on the secondary side circulation flow of the heat exchange station according to the secondary network circulation flow of the heat exchange station, specifically: frequency conversion control of the circulating water pump of the heat exchange station.

[0104] The interference of the current heating system mainly comes from: outdoor temperature, solar radiation and indoor heat gain. Usually, outdoor temperature plays a major role, while solar radiation and indoor heat gain play a minor role. According to the intensity of the interference, the interference can be divided into two levels: the first level interference is outdoor temperature; the second level interference is solar radiation and indoor heat gain. At present, the heating area of ​​most centralized heating systems in northern China is greater than 1 million m 2 As mentioned above, the system structure adopts an indirect connection mode, that is, the system is composed of a heat source, a primary network, a heat exchange station, a secondary network, and a heat user. The basic unit directly related to the indoor temperature of the heat user can be defined as a heat exchange station, a secondary network, and a heat user. Therefore, the study of the indoor temperature of the heat user is suitable to take the heat exchange station and its downstream as the basic unit (therefore, the control body in this embodiment mainly involves the heat exchange station, the heat exchange station secondary network, and the building heat user), and take the heat exchange station as the key node of automatic control, which not only simplifies very complex problems, but also improves the practicality and practical application value of the research results.

[0105] In the actual operation and control process of the centralized heating system, as the outdoor temperature changes (primary disturbance), in order to meet the heat supply and demand matching between the heat exchange station and the heat users, the heat exchange station changes the water temperature (secondary water supply temperature or secondary average temperature) while keeping the secondary network circulation flow unchanged (constant flow) to ensure the indoor temperature of the heat users. However, the heat matching control of the heat exchange station usually does not consider the dynamic impact of the secondary disturbance on the indoor temperature. Therefore, its actual operation and control results lead to large fluctuations in indoor temperature, which not only affects the thermal comfort of heat users, but also causes indoor temperature overheating, heat supply and system investment waste, and reduces the economic benefits of the heating system.

[0106] In view of this actual situation, with respect to the indoor temperature control parameters and influencing factors of the heating system, in this embodiment, the indoor temperature and heat exchange station control are separated according to the interference intensity action level, so as to grasp the main contradictions while not ignoring the secondary contradictions, in order to improve and enhance the heating quality while reducing the system energy consumption level.

[0107] In this embodiment, the interference affecting the indoor temperature is decomposed and compensated through simulation analysis of the dynamic mathematical model of the heating system, and is used in the control system of the heat exchange station to achieve the purpose of indoor temperature control.

[0108] The implementation process of the thermal and hydraulic balance control method of the heating system according to the embodiment of the present invention is described in detail below:

[0109] A heating system consists of a heat source, three heat exchange stations (1#, 2# and 3#), corresponding secondary networks and users. The total heating area and design heat load are 242,200 m 2 and 10.59MW. The end-user heat dissipation devices are all radiators. Heat exchange station 3# is a public building, and the other two heat exchange stations are civil buildings. The design indoor temperatures of public buildings and civil buildings are 18℃ and 20℃ respectively. The system process flow chart and control principle diagram are as follows Figure 2 shown.

[0110] The ideal dynamic mathematical model of the system created is transformed into an actual dynamic mathematical model after verification, which is used for system characteristic analysis, dynamic simulation, control strategy simulation and energy consumption analysis, etc. by comprehensively applying the laws of conservation of thermodynamic mass and energy, combining system design parameters, physical parameters and operating data, and appropriately simplifying the system on the basis of retaining its main characteristics.

[0111] The dynamic mathematical model is expressed as:

[0112]

[0113] The dynamic mathematical model describes the relationship between the heat gain, heat loss and net heat storage of the control body (heat source boiler, primary side of heat exchanger, secondary side of heat exchanger, radiator and indoor air).

[0114] Where: T s1 , T r1 , T r2 : represent heat source outlet temperature, heat source return water temperature, secondary network return water temperature, ℃; C b , C x1 , C x2 , C ht , C a : heat capacity of boiler body, primary side of heat exchanger, secondary side of heat exchanger, radiator and indoor air, J / ℃; t: time, s; G fd : Rated fuel quantity of boiler, Nm 3 / s; HV: fuel lower calorific value, J / Nm 3 ; η b : boiler efficiency; c w : Specific heat of water, J / Kg℃; G 1d , G 2d : Designed circulation flow of primary and secondary networks, Kg / s; f x 、f ht : Heat transfer area surplus coefficient of heat exchanger and radiator; U x , U ht , U e : Comprehensive heat transfer coefficient of heat exchanger, radiator and enclosure, W / ℃; LMTD: Logarithmic mean temperature difference, ℃; c: Coefficient in radiator heat transfer coefficient test; F w : External window area, m 2 ; F: heating area, m 2 ;q s : Solar radiation intensity, W / m 2 ;q int : Indoor heat gain intensity, W / m 2 ; i represents the number of the heat exchange station, i=1~3.

[0115] The dynamic mathematical model of the heating system consists of 13 dynamic equations and is used for system characteristic acquisition, dynamic simulation, operation status analysis, control strategy and energy consumption analysis.

[0116] Next, the open-loop dynamic response and accuracy of the ideal dynamic mathematical model are verified, specifically:

[0117] When the outdoor temperature is the design outdoor temperature, the heat network circulation flow is the design value, solar radiation and indoor heat gain are not considered, and the heat source fuel control variable is 0.758, the dynamic response of the ideal dynamic model is shown in Figure 3After 5 hours, the dynamic response of the heating system reaches a steady-state value. The supply and return water temperature of the heat source, the supply and return water temperature of the secondary network of the heat exchange station 1#, and the indoor temperature of the users of the heat exchange stations 1#~3# are 110℃, 60℃, 70℃, 50℃, 20℃, 20℃ and 18℃, respectively. They are all system design parameters, indicating that the ideal dynamic mathematical model of the system has sufficient accuracy.

[0118] Through system basic data, operation data and dynamic model simulation, the heat transfer area surplus values ​​of heat exchangers and radiators in heat exchange stations 1# to 3# of the heating system are obtained as follows:

[0119] [f x1 , f x2 , f x3 , f ht1 , f ht2 , f ht3 ] = [1.34, 1.4, 1.45, 1.33, 1.41, 1.35] -- (7)

[0120] After applying the heat transfer area surplus coefficient to the ideal dynamic mathematical model, the dynamic mathematical model of the heating system is transformed into the actual dynamic mathematical model. When the outdoor temperature is the design outdoor temperature, the heat network circulation flow is the design value, and the solar radiation and indoor heat gain and the heat source fuel control variable are not considered to be 0.775, the dynamic response of the actual dynamic mathematical model is shown in Figure 4 . As shown in the figure, the heat source supply and return water temperature, the heat exchange station 1# secondary network supply and return water temperature, and the indoor temperature of the heat exchange station (1#, 2#, 3#) users are 89.17℃, 39.58℃, 54.51℃, 35.01℃, 19.12℃, 20.23℃ and 17.99℃ respectively. It can be seen that under the outdoor design temperature, the heat source water supply temperature does not need to reach the design parameters to meet the minimum indoor design temperature requirements of heat users. In addition, it is impossible for the secondary network heating parameters to meet the indoor temperature control indicators at the same time without control. In the scenario of meeting the minimum indoor temperature requirements, it means that the indoor temperature is overheated.

[0121] Then the characteristic parameters of the heating system are obtained, and the actual dynamic mathematical model of the system is used for simulation to obtain the heat source water supply temperature when the heat source meets the minimum indoor design temperature requirement under different outdoor temperatures and the secondary network water supply temperature when the indoor temperature of each heat exchange station user is met. The specific data are shown in Table 1.

[0122] Table 1 Correspondence between heat source and heat exchange station water supply temperature and outdoor temperature

[0123]

[0124] Further dynamic simulation of system control strategy:

[0125] (1) Dynamic simulation conditions

[0126] Outdoor temperature, solar radiation and indoor heat gain parameters for two consecutive days;

[0127] Outdoor temperature range: -4℃~-15℃;

[0128] Solar radiation range: 0W / m 2 ~157W / m 2 ;

[0129] Indoor heat gain range: 3.7W / m 2 ~6.5W / m 2 .

[0130] (2) Control algorithm

[0131] Except for the open-loop control of the secondary network circulation flow of the heat exchange station, other controllers (C f , C1, C2 and C3) all adopt closed-loop control, and the control algorithm adopts the typical PID calculation mode. Symbol C f , C1, C2 and C3 are respectively the heat source fuel controller, the secondary side water supply temperature controller of heat exchange station 1#, 2# and 3# (see Figure 1 ).

[0132] (3) Control strategy

[0133] This embodiment adopts two system balance control strategies, namely control strategy 1 and control strategy 2. The control principles are as follows: Figure 1 As shown, the control strategies of each subsystem are shown in Table 2:

[0134] Table 2 Control strategy description

[0135]

[0136] (4) Control strategy simulation

[0137] Control strategy 1: Dynamic simulation of the heating system using this control strategy is shown in Figure 5 . Figure 5 (a) shows the dynamic response of the heat source supply and return water temperatures within 2 days. The supply water temperature can change with the change of outdoor temperature, while the return water temperature changes more slowly. Figure 5 (b) The dynamic response of the primary / secondary network supply and return water temperature of heat exchange station 1# is given. The secondary network supply water temperature is about 14.2℃ higher than the primary network return water temperature on average, and the primary network return water temperature is about 3.7℃ higher than the secondary network return water temperature on average. Figure 5 (c) The water supply temperature of the secondary network of heat exchange stations 1#~3# differs by about 1.6℃. Figure 5(d) shows the dynamic change of indoor temperature. Excluding the influence of the initial simulation value (the first 5 hours), the indoor temperature change ranges of heat exchange stations 1# and 2# are 22.4℃~28.4℃ and 23.1℃~28.5℃, respectively, and their average values ​​are 25.3℃ and 25.4℃, respectively. The indoor temperature change range and average value of heat exchange station 3# are 20.5℃~27.7℃ and 22.8℃, respectively. It can be seen that the indoor temperature change range and average value cannot meet the user's thermal comfort and system energy saving and consumption reduction requirements.

[0138] Control strategy 2: Analysis of the problem of excessive indoor temperature and high energy consumption caused by the use of control strategy 1 is mainly due to improper system balance control. Therefore, control strategy 2 uses the thermal and hydraulic balance control method of the heat network and heat exchange station to ensure that the indoor temperature change range and average value of the user meet the requirements while reducing the system operation energy consumption. The dynamic simulation results of the control strategy 2 example are shown in Figure 6 .Compare Figure 6 (a) and Figure 5 (a) It can be seen that when control strategy 2 is adopted, the supply and return water temperatures of the heat source are reduced, and the primary network temperature difference increases. Figure 6 (b) and Figure 5 (b) It can be seen that the secondary network supply and return water temperatures and primary network return water temperatures of control strategy 2 are lower than the corresponding values ​​of control strategy 1, and the secondary network supply and return water temperature difference increases. Figure 6 (c) and Figure 5 (c) It can be seen that the water supply temperature of the heat exchange station in control strategy 2 decreases, and there is a difference of 2.5℃ to 3.5℃ compared with control strategy 1. Figure 6 (d) and Figure 5 (d) It can be seen that, for most of the time, the indoor temperature of users in each heat exchange station can be controlled within the range of ±1°C of the set parameters, which can not only meet the heating quality but also effectively reduce the system energy consumption.

[0139] Finally, the system energy consumption is analyzed

[0140] (1) Heat source and heat consumption analysis

[0141] The dynamic changes of heat source fuel and primary network circulation flow control variables for control strategies 1 and 2 are shown in Figure 7 The fuel control variable can change with the outdoor temperature. The average values ​​of the fuel control variables of control strategies 1 and 2 are 0.649 and 0.565 respectively, which means that control strategy 2 can achieve 12.94% heat saving.

[0142] (2) Analysis of primary grid power consumption

[0143] The heat source primary network flow rate of control strategy 1 is the designed circulation flow rate, and the primary network circulation flow rate of control strategy 2 changes with the primary side circulation flow rate of the three heat exchange stations, that is, the primary network at this time is a variable flow system, and the average value of its flow control variable is 0.686. According to the water pump similarity law (power and circulation flow rate are cubic), the power consumption can be evaluated, and it is calculated that the power consumption of control strategy 2 is 32.28% of that of control strategy 1, which can achieve about 68% power saving.

[0144] (3) Secondary network power saving analysis

[0145] The circulation flow rate of each heat exchange station in control strategy 1 is the design circulation flow rate (u w21 =u w22 =u w23 =1), the dynamic response of the secondary network circulation flow control variables of each heat exchange station in control strategy 2 is as follows Figure 8 The average values ​​of the circulating flow control variables of each heat exchange station are 0.596, 0.642 and 0.626 respectively. According to the water pump similarity law, it can be calculated that the power consumption of each heat exchange station in control strategy 2 is 21.17%, 26.46% and 24.53% of the corresponding power consumption of the heat exchange station in control strategy 1, that is, the average secondary network power saving rate is 75.95%.

[0146] Analysis of system balance:

[0147] (1) Primary network thermal balance rate

[0148] According to the dynamic simulation of different control strategies of the heating system, the dynamic changes of the primary network thermal balance rate of control strategies 1 and 2 are as follows: Fig. 9 As shown. The thermal balance rate of control strategy 1 is 0, because the secondary network water supply temperature of the heat exchange station is not controlled at this time, and there is no secondary network water supply temperature setting parameter. The secondary network water supply temperature of each heat exchange station in control strategy 2 is personalized and controlled, and its thermal balance rate range and average value are 96.08% to 99.84% and 98.27% respectively, indicating that each heat exchange station in control strategy 2 can meet the personalized water supply temperature requirements of the secondary network and realize the first-level compensation of outdoor temperature based on indoor temperature separation technology.

[0149] (2) Secondary network thermal balance rate

[0150] The thermal balance rate of the secondary network of the heat exchange station tracks the deviation between the actual indoor temperature and the designed indoor temperature. The dynamic response of the thermal balance rate of the secondary network of each control strategy is shown in Fig. 9. Since control strategy 1 does not compensate for the system's additional heat gain, the dynamic range of indoor temperature is large, and the average indoor temperature is higher than the designed indoor temperature. Therefore, the range and average value of the secondary network thermal balance rate are 36.59% to 94.31% and 83.46% respectively. Control strategy 2 takes into account solar radiation and indoor heat gain compensation (secondary compensation based on indoor temperature separation technology), which greatly improves the indoor temperature control accuracy. The range and average value of the secondary network thermal balance rate are 97.98% to 99.96% and 99.81% respectively.

[0151] (3) Secondary network hydraulic balance rate

[0152] The hydraulic balance rate of the secondary network needs to be calculated according to the nature of the user. This example uses heat exchange stations 1# and 2# (both are civil construction) for comparative calculation. The dynamic response is shown in Fig. 9 Since the thermal characteristics of heat exchange stations 1# and 2# are similar, the indoor temperature has similar values ​​in the dynamic response of the two control strategies ( Figure 5 (d) and Figure 6 (d)), therefore, the consistency of indoor temperature is high. The hydraulic balance rates of the secondary network of control strategies 1 and 2 are 98.08% and 99.65%, respectively.

[0153] In summary, it can be seen that (1) in large-scale centralized / regional heating systems, it is difficult to meet the thermal comfort requirements of users by only using heat source-based water supply temperature control (the primary network circulation flow is the design flow), and more accurate system balance control is needed; (2) The primary network hydraulic balance judgment is only applicable to constant flow systems; (3) Creating and applying the actual dynamic mathematical model of the heating system can obtain the personalized characteristics of the heat exchange station, which is beneficial to the thermal and hydraulic balance control of the system; (4) The thermal balance of the primary network is an evaluation of the personalized parameter control status of the heat exchange station. The higher its thermal balance rate, the more conducive it is to the precise control of the indoor temperature; (5) The thermal balance of the secondary network of the heat exchange station tracks the deviation between the actual indoor temperature and the design temperature, and the hydraulic balance of the secondary network tracks the consistency of the actual user's indoor temperature. The control strategy of the heat exchange station based on indoor temperature separation technology can not only ensure user supply and demand matching and accurate heating, but also effectively reduce system energy consumption; (6) Based on the overall balance control strategy of the heating system (primary network thermal balance and secondary network thermal / hydraulic balance control), on the basis of meeting accurate heating, it can achieve heat source heat saving of more than 10%, and primary / secondary network electricity saving of more than 50% respectively; (7) Based on the indoor temperature separation technology and the overall balance control strategy of the heating system, it is expected to save 2.5-4 yuan / m 2 The heating operation cost can be reduced, significant social, economic and environmental benefits can be obtained, and it is conducive to building an ecological and sustainable heating system.

[0154] On the other hand, see Fig. 9 As shown, the embodiment of the present invention further provides a thermal and hydraulic balance control system 1 for a heating system, comprising:

[0155] The mathematical model building module 10 is used to obtain the actual dynamic mathematical model of the heating system by simulation analysis based on the law of conservation of mass and the law of conservation of thermodynamic energy and on the design parameters, physical parameters and operation data of the heating system;

[0156] The relationship model acquisition module 20 is used to obtain the relationship model between the outdoor temperature and the heat source water supply temperature when the heat source meets the minimum indoor design temperature requirement by simulating the actual dynamic mathematical model of the heating system, the relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station when the indoor temperature of each heat exchange station user is met, and the relationship model between the secondary network circulation flow ratio of the heat exchange station and the outdoor temperature, solar radiation intensity, and indoor heat gain intensity;

[0157] The first heat source control module 30 is used to input the outdoor temperature value detected in real time into the relationship model between the outdoor temperature and the heat source water supply temperature to determine the heat source water supply temperature control value, so as to adjust the heat source fuel supply amount;

[0158] The second heat source control module 40 is used to adjust the heat source circulation flow rate by simulating the actual dynamic mathematical model of the heating system to obtain the sum of the circulation flow rates required by the primary side of each heat exchange station and combining the designed circulation flow rate of the primary side of the heat exchange station;

[0159] The first compensation control module 50 is used to input the outdoor temperature value detected in real time into the relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station to calculate the secondary network water supply temperature setting value, and perform closed-loop compensation control on the secondary network water supply temperature of the heat exchange station according to the error between the secondary network water supply temperature setting value and the measured value of the secondary network water supply temperature;

[0160] The second compensation control module 60 is used to calculate the secondary network circulation flow of the heat exchange station by inputting the real-time detected outdoor temperature value, solar radiation intensity and average indoor heat gain intensity into the relationship model between the secondary network circulation flow ratio of the heat exchange station and the outdoor temperature, solar radiation intensity and indoor heat gain intensity, and perform open-loop compensation control on the secondary side circulation flow of the heat exchange station based on the secondary network circulation flow of the heat exchange station.

[0161] The specific details of each module in the above-mentioned thermal and hydraulic balance control system of the heating system have been described in detail in the corresponding thermal and hydraulic balance control method of the heating system, so they will not be repeated here.

[0162] On the other hand, an embodiment of the present invention further provides an electronic device, including: a processor and a memory, wherein the memory stores computer-readable instructions, and when the computer-readable instructions are executed by the processor, the thermal and hydraulic balance control method of the heating system as described in the above embodiment is implemented.

[0163] Specifically, the above-mentioned memory and processor can be general-purpose memory and processor, which are not specifically limited here. When the processor runs the computer-readable instructions stored in the memory, it can execute the thermal and hydraulic balance control method of the heating system described in the above embodiment.

[0164] On the other hand, an embodiment of the present invention further provides a computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements the method for controlling thermal and hydraulic balance of a heating system as described in the above embodiment.

[0165] A person of ordinary skill in the art can understand that all or part of the steps in the various methods of the above embodiments can be completed by instructing related hardware through a program, and the program can be stored in a computer-readable storage medium, and the storage medium can include: a flash drive, a read-only memory (ROM), a random access memory (RAM), a magnetic disk or an optical disk, etc.

[0166] Although the present invention has been described in detail above by general description and specific embodiments, it is obvious to those skilled in the art that some modifications or improvements can be made to the present invention. Therefore, these modifications or improvements made without departing from the spirit of the present invention all belong to the scope of protection claimed by the present invention.

Claims

1. A method for controlling thermal and hydraulic balance of a heating system, characterized in that: include: S1: Based on the law of conservation of mass and the law of conservation of thermodynamic energy, and based on the design parameters, physical parameters and operation data of the heating system, a simulation analysis is performed to obtain the actual dynamic mathematical model of the heating system; S2: By simulating the actual dynamic mathematical model of the heating system, a relationship model between the outdoor temperature and the heat source water supply temperature when the heat source meets the minimum indoor design temperature requirement is obtained, a relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station when the indoor temperature of each heat exchange station user is met, and a relationship model between the secondary network circulation flow ratio of the heat exchange station and the outdoor temperature, solar radiation intensity, and indoor heat gain intensity; S3: inputting the outdoor temperature value detected in real time into the relationship model between the outdoor temperature and the heat source water supply temperature to determine the heat source water supply temperature control value to adjust the heat source fuel supply; S4: simulating the actual dynamic mathematical model of the heating system to obtain the sum of the required circulation flow rates of the primary sides of each heat exchange station and adjusting the heat source circulation flow rate in combination with the designed circulation flow rate of the primary side of the heat exchange station; S5: inputting the real-time detected outdoor temperature value into the relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station to calculate the secondary network water supply temperature setting value, and performing closed-loop compensation control on the secondary network water supply temperature of the heat exchange station according to the error between the secondary network water supply temperature setting value and the measured value of the secondary network water supply temperature; S6: Input the real-time detected outdoor temperature value, solar radiation intensity and indoor heat gain intensity average value into the relationship model between the secondary network circulation flow ratio of the heat exchange station and the outdoor temperature, solar radiation intensity and indoor heat gain intensity to calculate the secondary network circulation flow of the heat exchange station, and perform open-loop compensation control on the secondary side circulation flow of the heat exchange station according to the secondary network circulation flow of the heat exchange station; Wherein, the S5 specifically includes: Input the real-time detected outdoor temperature value into the relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station to calculate the secondary network water supply temperature setting value, and calculate the error between the secondary network water supply temperature setting value and the actual measured value of the secondary network water supply temperature; The error between the set value of the secondary network water supply temperature and the measured value of the secondary network water supply temperature is input into the controller algorithm formula to calculate the flow control parameter of the primary side electric regulating valve of the heat exchange station, wherein the secondary network water supply temperature of the heat exchange station adopts a closed-loop control circuit; The flow control parameters of the electric regulating valve on the primary side of the heat exchange station are used to adjust the opening of the electric regulating valve to adjust the water supply temperature of the secondary network in real time.

2. The method for controlling thermal and hydraulic balance of a heating system according to claim 1, characterized in that: The S1 includes: According to the law of conservation of mass and the law of conservation of thermodynamic energy, and based on the design parameters, physical parameters and operating data of the heating system, an ideal dynamic mathematical model of the heating system is created; Based on the basic data and operation data of the heating system, the ideal dynamic mathematical model of the heating system is simulated to obtain the heat transfer area surplus coefficient of the heat exchanger and the heat transfer area surplus coefficient of the radiator of each heat exchange station of the heating system; The surplus coefficient of heat transfer area of ​​the heat exchanger and the surplus coefficient of heat transfer area of ​​the radiator of each heat exchange station of the heating system are input into the ideal dynamic mathematical model of the heating system to obtain the actual dynamic mathematical model of the heating system.

3. The method for controlling the thermal and hydraulic balance of a heating system according to claim 2, characterized in that: The S1 also includes: verifying the dynamic response steady-state value of the ideal dynamic mathematical model of the heating system under the conditions of designed outdoor temperature, designed heat network circulation flow and without considering solar radiation and indoor heat gain, so as to determine the accuracy of the ideal dynamic mathematical model of the heating system when the outdoor temperature changes.

4. The method for controlling thermal and hydraulic balance of a heating system according to claim 2, characterized in that: The heating system includes three heat exchange stations, and the heat transfer area surplus coefficients of the heat exchangers and the heat transfer area surplus coefficients of the three heat exchange stations are respectively: 1.34, 1.4, 1.45, 1.33, 1.41 and 1.

35.

5. The method for controlling thermal and hydraulic balance of a heating system according to claim 2, characterized in that: The mathematical description of the actual dynamic mathematical model of the heating system is expressed as: Among them, T s1 、T r1 、T r2 Respectively represent the heat source outlet temperature, heat source return water temperature, and secondary network return water temperature, in °C; C b , C x1 , C x2 , C ht , C a Respectively represent the heat capacity of the boiler body, the primary side of the heat exchanger, the secondary side of the heat exchanger, the radiator and the indoor air, in J / ℃; t represents time, in s; G fd Indicates the rated fuel quantity of the boiler in Nm 3 / s; HV represents the lower heating value of fuel, the unit is J / Nm 3 ; η b represents boiler efficiency; c w Indicates the specific heat of water, the unit is J / Kg℃; G 1d , G 2d Respectively represent the design circulation flow of the primary network and the secondary network, the unit is Kg / s; f x 、f ht Respectively represent the heat transfer area surplus coefficient of the heat exchanger and radiator; U x , U ht , U e They represent the comprehensive heat transfer coefficient of the heat exchanger, radiator and enclosure structure, in W / ℃; LMTD represents the logarithmic mean temperature difference, in ℃; c represents the coefficient in the radiator heat transfer coefficient test; F w Indicates the exterior window area, in m 2 ; F represents the heating area, the unit is m 2 ;q s Indicates the solar radiation intensity in W / m 2 ;q int Indicates the indoor heat gain intensity, in W / m 2 ; i represents the number of the heat exchange station, i=1~3.

6. The method for controlling thermal and hydraulic balance of a heating system according to claim 1, characterized in that: The open-loop compensation control of the secondary side circulation flow of the heat exchange station according to the secondary network circulation flow of the heat exchange station in S6 is specifically: frequency conversion control of the circulating water pump of the heat exchange station.

7. A thermal and hydraulic balance control system for a heating system, characterized in that: include: The mathematical model building module is used to obtain the actual dynamic mathematical model of the heating system by simulation analysis based on the law of conservation of mass and the law of conservation of thermodynamic energy, and based on the design parameters, physical parameters and operation data of the heating system; A relationship model acquisition module is used to obtain a relationship model between the outdoor temperature and the heat source water supply temperature when the heat source meets the minimum indoor design temperature requirement by simulating the actual dynamic mathematical model of the heating system, a relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station when the indoor temperature of each heat exchange station user is met, and a relationship model between the secondary network circulation flow ratio of the heat exchange station and the outdoor temperature, solar radiation intensity, and indoor heat gain intensity; A first heat source control module, used for inputting the outdoor temperature value detected in real time into the relationship model between the outdoor temperature and the heat source water supply temperature to determine the heat source water supply temperature control value, so as to adjust the heat source fuel supply amount; The second heat source control module is used to adjust the heat source circulation flow rate by simulating the actual dynamic mathematical model of the heat supply system to obtain the sum of the circulation flow rates required on the primary side of each heat exchange station and combining the designed circulation flow rate on the primary side of the heat exchange station; The first compensation control module is used to input the outdoor temperature value detected in real time into the relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station to calculate the secondary network water supply temperature setting value, and perform closed-loop compensation control on the secondary network water supply temperature of the heat exchange station according to the error between the secondary network water supply temperature setting value and the measured value of the secondary network water supply temperature; The second compensation control module is used to calculate the secondary network circulation flow rate of the heat exchange station by inputting the real-time detected outdoor temperature value, solar radiation intensity and average value of indoor heat gain intensity into the relationship model between the secondary network circulation flow rate ratio of the heat exchange station and the outdoor temperature, solar radiation intensity and indoor heat gain intensity, and perform open-loop compensation control on the secondary side circulation flow rate of the heat exchange station according to the secondary network circulation flow rate of the heat exchange station; Wherein, the first compensation control module is specifically used for: Input the real-time detected outdoor temperature value into the relationship model between the outdoor temperature and the secondary network water supply temperature of the heat exchange station to calculate the secondary network water supply temperature setting value, and calculate the error between the secondary network water supply temperature setting value and the actual measured value of the secondary network water supply temperature; The error between the set value of the secondary network water supply temperature and the measured value of the secondary network water supply temperature is input into the controller algorithm formula to calculate the flow control parameter of the primary side electric regulating valve of the heat exchange station, wherein the secondary network water supply temperature of the heat exchange station adopts a closed-loop control circuit; The flow control parameters of the electric regulating valve on the primary side of the heat exchange station are used to adjust the opening of the electric regulating valve to adjust the water supply temperature of the secondary network in real time.

8. An electronic device, characterized in that: include: A processor and a memory, wherein the memory stores computer-readable instructions, and when the computer-readable instructions are executed by the processor, the method for controlling the thermal and hydraulic balance of a heating system as described in any one of claims 1 to 6 is implemented.

9. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by a processor, the thermal and hydraulic balance control method of the heating system as described in any one of items 1-6 is implemented.

Images