A method for controlling an electric heating system to improve the consumption of new energy in high-altitude and cold areas

Abstract

The present invention discloses an electric heating system network operation strategy for improving the consumption of new energy in high-altitude and cold regions, and belongs to the field of energy management technology. It includes: step one, establishing a mathematical model of a heat storage device and a cogeneration unit, and correcting the mathematical model of the heat storage device according to high-altitude and cold environmental parameters, and regulating the working parameters of the heat storage device according to the corrected mathematical model; step two, according to the actual demand of electric load and heat load, the mathematical model of the cogeneration unit and the working parameters of the heat storage device, using the energy distribution model of the electric heating system network to regulate the working parameters of the cogeneration unit. In summary, the present invention adjusts the heat and electricity production of the cogeneration unit according to the demand of electric load and heat load, and establishes an energy distribution model of the electric heating system network, takes the total amount of wasted energy as the objective function, and adjusts each variable to minimize the total amount of wasted energy, thereby achieving maximum wind power consumption.

Description

Technical Field

[0001] The present invention relates to the field of energy management technology, and more specifically, to an electric heating system control method for improving the consumption of new energy in high-altitude and cold areas. Background Art

[0002] For high-altitude and cold areas, which are remote and lack conventional energy such as oil and coal, but have abundant renewable energy such as solar energy and wind energy, it is urgent to establish a more abundant energy system to meet local energy needs.

[0003] Combining power systems with thermal storage systems can store excess renewable energy as heat, converting it into heat during periods of low load and releasing it during peak load periods to alleviate the burden of converting electricity to heat during peak periods. This significantly aids in the absorption of renewable energy and peak load regulation of the power grid.

[0004] However, ensuring the efficient operation of heat storage systems while minimizing economic costs has always been a key issue in the application of heat storage devices. Furthermore, ensuring that heat storage systems possess accurate and effective real-time sensing and feedback capabilities, including dynamic response capabilities, in response to changes in renewable energy output and load fluctuations, while operating under multiple constraints, such as environmental factors in high-altitude and cold regions, uncertainties in renewable energy output, the structure of the heat storage system, and load characteristics, further improving the overall energy efficiency of the heat storage system throughout its cycle, is also a key technology for achieving efficient utilization of integrated energy systems. Summary of the Invention

[0005] In response to the above problems, the present invention provides an electric heating system control method for improving the maximum new energy consumption in high-altitude and cold areas, thereby solving the above technical problems.

[0006] The technical solution adopted in the present invention is as follows:

[0007] In a first aspect, the present invention proposes a method for controlling an electric heating system to improve the consumption of new energy in high-altitude and cold regions, comprising:

[0008] Step 1: Establish a mathematical model of the heat storage device and the cogeneration unit, modify the mathematical model of the heat storage device according to high altitude and cold environment parameters, and adjust the operating parameters of the heat storage device according to the modified mathematical model;

[0009] Step 2: Based on the actual demand of electric load and heat load, the mathematical model of the cogeneration unit and the operating parameters of the heat storage device, the energy distribution model of the electric heating system network is used to control the operating parameters of the cogeneration unit.

[0010] Furthermore, the method for regulating the operating parameters of the heat storage device includes:

[0011] Step 1.3.1: Determine the power transmitted by the fan based on the fan speed and water pump flow rate. Compare the power transmitted by the fan with the sum of the heat power output by the dry-burning tube in the heating unit and the fan circulation power to determine a control method for the fan speed, water pump flow rate, and heat transfer power of the phase change thermal storage brick. The control method includes control strategy 1 and control strategy 2.

[0012] Step 1.3.2: If the power transmitted by the fan is less than the sum of the thermal power output of the dry-burning tubes in the heating unit and the fan circulating power, then execute control strategy 1; Step 1.3.3: If the power transmitted by the fan is greater than or equal to the sum of the thermal power output of the dry-burning tubes in the heating unit and the fan circulating power, then execute control strategy 2.

[0013] Furthermore, the control strategy 1 is specifically as follows:

[0014] Step 1.3.2.1: Calculate the water tank input power based on the actual fan power and the current pump flow rate. Compare the water tank input power with the water tank's thermal power requirements to determine whether the fan speed, pump flow rate, and heat transfer power of the phase change thermal storage bricks need to be adjusted.

[0015] Step 1.3.2.2: If the water tank input power is less than the water tank's thermal power requirement, maintain the pump flow rate, increase the fan speed, and return to step 1.3.1;

[0016] If the input power of the water tank is greater than or equal to the thermal power demand of the water tank, the fan speed is kept unchanged, and the water pump flow rate is reduced to make the input power of the water tank equal to the thermal power demand of the water tank, and the heat transfer power of the phase change heat storage brick is adjusted to meet the requirements. The regulation ends; among them, Indicates the corrected power transmitted by the fan.

[0017] Furthermore, the second control strategy is specifically as follows:

[0018] Step 1.3.3.1: Take the sum of the thermal power output of the dry-burning tube in the heating unit and the fan's circulating power as the fan's transmitted power, and calculate the corresponding water tank input power. Compare the water tank's input power with the water tank's thermal power requirement to determine whether the fan speed, water pump flow rate, and heat transfer power of the phase change thermal storage bricks need to be adjusted.

[0019] Step 1.3.3.2: If the input power to the water tank is less than the thermal power requirement of the water tank, gradually increase the pump flow rate;

[0020] If the input power of the water tank is greater than or equal to the thermal power demand of the water tank, the fan speed is kept unchanged, and the water pump flow rate is reduced to make the input power of the water tank equal to the thermal power demand of the water tank, and the heat transfer power of the phase change heat storage brick is adjusted to 0, and the control ends;

[0021] In the process of gradually increasing the water pump flow rate in step 1.3.3.2, when the water pump flow rate has reached the maximum limit, The power transmitted by the fan is calculated based on the thermal power demand of the water tank, and the fan speed is calculated based on the power transmitted by the fan as the fan control result. The water pump flow rate is maintained at the maximum value, and the heat transfer power of the phase change heat storage brick is adjusted to meet the requirements. End of regulation;

[0022] When the water pump flow rate has not reached the maximum limit, the input power of the water tank is calculated based on the current water pump flow rate and fan speed. If the input power of the water tank is still less than the thermal power demand of the water tank, the water pump flow rate is continued to be increased until the input power of the water tank is equal to the thermal power demand of the water tank. The fan speed and water pump flow rate are maintained unchanged, and the heat transfer power of the phase change heat storage brick is adjusted to 0, and the control is completed.

[0023] Furthermore, the energy distribution model of the electric heating system network is used to control the operating parameters of the cogeneration unit, including:

[0024] Step 2.1: According to the real-time power P of wind power w , electric load e and heat load h, and establish the energy distribution model of the electric heating system network;

[0025] The energy distribution model is: the heat output P of the cogeneration unit hchp is variable X1, and the corresponding power generation is k hp X1; wind power real-time power P w Input power P to the dry-burning tube in the heating unit e is variable X2, then the wind power used to meet the power load is P w -X2; the energy conversion efficiency of the electric boiler is η, and the sum of the heat generated by the electric boiler and the heat generated by the cogeneration unit is the total heat supply. Part of the heat is input into the heat storage device and stored, which is set as variable X3, and the other part of the heat is used to meet the heat load, which is recorded as P hot In addition to the input heat X3, the heat storage device also has output heat X4 and heat dissipation to the outside world Q cwaste , its heat storage E changes with the variables X3, X4, Q cwaste The change will produce corresponding changes, E=X3-X4-Q cwaste , X4=hP hot ;

[0026] Step 2.2: Establish the constraints and objective function of the energy distribution model, solve the objective function through the particle swarm algorithm, find the optimal solution of X1, X2, X3, and X4, and complete the working parameter control based on the optimal solution.

[0027] In a second aspect, the present invention provides an electric heating system control device for improving the consumption of new energy in high-altitude and cold areas, comprising:

[0028] A heat storage device modeling module, which is used to establish a mathematical model of the heat storage device;

[0029] The heat storage device model correction module is used to obtain high-altitude and cold environment parameters and correct the water temperature in the water tank in the heating unit mathematical model and the fan speed in the heat exchange unit mathematical model;

[0030] The combined heat and power unit modeling module is used to establish a mathematical model of the combined heat and power unit;

[0031] a first control module, which is used to control the operating parameters of the heat storage device according to the modified mathematical model of the heat storage device;

[0032] The electric heating system modeling module is used to establish the energy distribution model of the electric heating system network;

[0033] The second control module is used to control the operating parameters of the cogeneration unit using the energy distribution model of the electric heating system network according to the actual demand of electric load and thermal load, the mathematical model of the cogeneration unit and the operating parameters of the heat storage device.

[0034] In a third aspect, the present invention provides a computer-readable storage medium having a program stored thereon. When the program is executed by a processor, the program implements the above-mentioned electric heating system control method for improving the consumption of new energy in high-altitude and cold areas.

[0035] The beneficial effects of the present invention are as follows: the present invention first regulates the operating parameters of the heat storage device in the electric heating system network, and uses the optimal operating parameters and the mathematical model of the cogeneration unit to establish an energy distribution model of the electric heating system network. This can realize real-time regulation of the operating parameters of the cogeneration unit according to the actual needs of the electric load and the thermal load, thereby achieving maximum wind power consumption. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] Figure 1 This is a schematic structural diagram of a heat storage device according to an embodiment of the present invention;

[0037] Figure 2 Schematic diagram of the calculation process of the thermal power demand of the water tank;

[0038] Figure 3 A flow chart of a method for regulating the working parameters of a heat storage device;

[0039] Figure 4 A simplified schematic diagram of energy flow in an electric heating system network according to an embodiment of the present invention;

[0040] Figure 5 1 is a curve showing the input and output power variation of the heat storage device according to an embodiment of the present invention, wherein (a) is input power, and (b) is output power;

[0041] Figure 6 Curves showing changes in heat storage (a), fan speed (b), water inlet flow rate (c), and heat exchange power (d) of the phase change heat storage bricks over time in the heat storage device according to an embodiment of the present invention.

[0042] Figure 7 This is a wind turbine speed adjustment curve under high altitude and cold environment conditions in an embodiment of the present invention;

[0043] Figure 8 The curves of expected wind power generation, electric load, and thermal load changing over time in the embodiment of the present invention are as follows;

[0044] Figure 9 The input power, output power and heat storage capacity change curve of the heat storage device in the embodiment of the present invention;

[0045] Figure 10 The curve showing the change of electric load and actual total power supply in the embodiment of the present invention;

[0046] Figure 11 The heat load and actual total heat supply change curve in the embodiment of the present invention;

[0047] Figure 12 This is a curve showing the change in energy wasted before and after the heat storage device is put into use in an embodiment of the present invention, where (a) is after the device is put into use and (b) is before the device is put into use. DETAILED DESCRIPTION

[0048] The following detailed description of the invention is given in conjunction with the accompanying drawings, which does not limit the invention and is only provided as an example. At the same time, the advantages of the invention will become clearer and easier to understand through the description.

[0049] The electric heating system control method for consuming new energy in high-altitude and cold areas proposed in the present invention mainly includes the following steps:

[0050] S1, establishing a mathematical model of the heat storage device, and modifying the mathematical model of the heat storage device according to high altitude and cold environmental conditions.

[0051] like Figure 1As shown, it shows a schematic structural diagram of a heat storage device according to an embodiment of the present invention, which mainly consists of a heating unit, a heat storage unit, a heat exchange unit, and a heat supply unit. The heating unit is used to convert electrical energy into thermal energy, mainly using a dry-burning tube; the heat storage unit is used to store heat, absorb and release heat at the appropriate time, mainly using phase change heat storage bricks; the heat exchange unit is used to exchange energy between gas with a certain temperature and water in the internal return water pipe, mainly using a fan; the heating unit serves as an intermediate station for energy transfer, and is used to transfer heat to the demand side.

[0052] In a specific implementation of the present invention, the implementation process of step S1 is:

[0053] Step 1.1: Establish mathematical models of the heating unit, heat storage unit, heat exchange unit, and heat supply unit in the heat storage device.

[0054] In this embodiment, a dry-burning tube is used as a heating unit to convert electrical energy into thermal energy. The mathematical model of the heating unit in the heat storage device is expressed as follows:

[0055] P he =αP e

[0056] 0≤P e ≤P emax

[0057] Among them, P e Indicates the input power of the dry-burning tube, P he Indicates the output thermal power of the dry-burning tube. α represents the conversion coefficient of the dry-burning tube's input electrical power to output thermal power. If it is within the limited power range and there is no energy loss, α can be taken as 1, that is, the conversion of electrical power to thermal power is one-to-one.

[0058] Phase change heat storage bricks are used as heat storage units to absorb and release heat. The mathematical model of the heat storage unit in the heat storage device is expressed as follows:

[0059] Q(t)=Q(t-1)+δP xiang (t)Δt

[0060] Among them, Q(t) is the heat stored in the heat storage unit at time t, Q(t-1) is the heat stored in the heat storage unit at time t-1, δ is the heat absorption and release efficiency of the heat storage unit, P xiang (t) is the heat transfer power of the heat storage unit at time t, where the heat transfer power of the phase change heat storage brick is the output power of the dry-burning tube when absorbing heat, that is, P xiang =P he When the phase change heat storage brick releases heat, the heat transfer power is the power transferred by the fan, that is, P xiang =P wind ,; Δt is the time it takes for the heat storage unit to absorb and release heat.

[0061] The fan is the main structure of the heat exchange unit, which is used to exchange energy between the gas at a certain temperature and the water in the internal return pipe. The mathematical model of the heat exchange unit in the heat storage device is:

[0062]

[0063] Among them, v windbase Indicates the basic speed of the fan, P windbase Indicates the power delivered by the fan at the base speed, v wind Indicates the fan speed, Pwind Indicates the power delivered by the fan at a certain speed, v windmin and v windmax They represent the minimum speed and maximum speed of the fan respectively, and a and b are constants.

[0064] The water tank is used as a heating unit, which is equivalent to an intermediate station for energy transfer. To make the model more convenient, the internal water flow rate and return water flow rate are made the same. The mathematical model of the heating unit in the heat storage device is established by using the positive correlation between energy transfer and water flow rate:

[0065]

[0066] Among them, v waterin Indicates the return water velocity inside the water tank, v waterinmax represents the maximum return flow rate inside the water tank, λ is the efficiency of energy transfer between gas and water, P waterin Indicates the power transferred from the outside to the water tank, P waterout Indicates the power transmitted from the water tank to the outside, P wind Indicates the power delivered by the fan at a certain speed; S indicates the cross-sectional area of ​​the return pipe, v waterout represents the water flow rate of the water tank, ρ represents the density of water, c water It represents the specific heat capacity of water, and ΔT represents the temperature difference between the outlet and return water of the water tank.

[0067] Step 1.2: Modify the mathematical model of the heat storage device based on high altitude and cold environmental conditions.

[0068] The high-altitude and cold environmental conditions can be regarded as low-temperature and low-pressure environmental conditions. In the low-temperature and low-pressure environment, the main affected physical quantities are the fan speed and the temperature of the water in the water tank.

[0069] Among them, the temperature of the water in the water tank is mainly affected by the low temperature environment, and its energy dissipation will greatly increase. The main consideration is the impact of the external low-temperature gas on the heat dissipation of the water in the water tank. The heat dissipation is expressed as:

[0070] Q cwaste=A*β*ΔT

[0071] Where A is the surface area of ​​the water tank, β is the heat transfer coefficient, and Q cwaste Indicates the heat dissipation of the water tank.

[0072] The fan speed is mainly affected by the low pressure environment. When the pressure conditions change, the specific volume of the gas will also change. The relationship is:

[0073] P1*v1=P2*v2

[0074] Where P1 represents standard atmospheric pressure, V1 is the specific volume of the gas at standard atmospheric pressure, and P2 and V2 represent the atmospheric pressure and specific volume of the gas after the change in environment. Let C = P1 / P2, which is the gas specific volume correction factor.

[0075] In reality, the volume of gas a fan can transport is only related to the fan's impeller speed and outer diameter, but it's the mass of the gas being transported that truly impacts energy transfer. When pressure decreases, the mass of gas per unit volume decreases, so a correction to the base speed is necessary.

[0076]

[0077] in, Indicates the corrected fan base speed under low pressure environment. is the power delivered by the fan in the corrected low pressure environment.

[0078] Step 1.3: Adjust the operating parameters of the heat storage device according to the constraints of the heat storage device.

[0079] In this embodiment, the operation of the heat storage device is mainly subject to the following constraints:

[0080]

[0081] Among them, P he P is the thermal power output of the dry-burning tube in the heating unit; xiang P is the energy exchange from the phase change heat storage brick in the heat storage unit to the outside, with a positive value of heat release and a negative value of heat absorption; wind P is the power of the fan to drive the gas to the water pipe; windback The power that is not transferred back during the process of the fan driving the gas to transfer power to the water pipe is recorded as the fan circulation power; P need Indicates the thermal power required to be input into the water tank, T waterout Indicates the temperature of the water to be output; ρ indicates the density of water, v waterout Indicates the water flow rate of the water tank, v waterrepresents the water pump flow rate, ΔT1 represents the temperature difference of the water tank before and after heating, ΔT2 represents the difference between the water outlet temperature and the return water temperature of the water tank, and t represents the heating time.

[0082] In addition to the above constraints, the operation of the heat storage device is also subject to maximum power constraints, including the heat storage capacity constraint of the heat storage device, the power constraint of the heating unit, and the power constraint of the water tank's external heat exchange;

[0083] The heat storage capacity constraint of the heat storage device is expressed as:

[0084] 0<E h <E hmax

[0085] The heating unit power constraint is expressed as:

[0086] 0<P hin <P hinmax

[0087] The power constraint of the water tank's outward heat transfer is expressed as:

[0088] 0<P hout <P houtmax

[0089] Among them, E h is the heat storage capacity of the heat storage device, E hmax is the maximum heat storage capacity of the heat storage device; P hin 、P hinmax Respectively represent the heating unit power and its maximum value in the energy storage device, P hout 、P houtmax They represent the outward heat exchange power of the water tank in the energy storage device and its maximum value respectively;

[0090] In this embodiment, the heat storage capacity of the heat storage device needs to be calculated based on the original stored energy, input power, and output power. The calculation formula is:

[0091] E h,t =E h,t-1 +Δt(P hin,t -P hout,t )

[0092] Among them, E h,t represents the heat storage at time t, E h,t-1 represents the heat storage at time t-1, Δt represents the time interval between time t and time t-1, P hin,t represents the power of the heating unit in the energy storage device at time t, P hout,t It represents the heat exchange power of the water tank in the energy storage device at time t.

[0093] Figure 2 shows the power demand P of the water tank needThe calculation flow chart first determines the output power P according to the load demand. waterout , calculate the required outlet water temperature T waterout , calculate the power P that needs to be input into the water tank according to the outlet water temperature need .

[0094] Figure 3 The following is a flow chart showing a method for regulating the operating parameters of a heat storage device. The entire process mainly follows the following three principles:

[0095] 1. When the power transmitted by the fan is less than the input power (the thermal power output by the dry-burning tube in the heating unit), the fan speed can be adjusted to meet the required power P. need ;

[0096] 2. When the power transmitted by the fan is equal to the input power, the required power P can be met by adjusting the pump speed. need ;

[0097] 3. The power transmitted by the fan is equal to the input power, and the pump speed has reached the maximum but still cannot meet the required power P need At this time, the phase change heat storage brick releases heat to the outside, and the power transmitted by the fan can be further increased to meet the required power P need .

[0098] Under the above principles, the regulation of the working parameters of the heat storage device mainly includes the following steps:

[0099] like Figure 3 As shown, the method for regulating the working parameters of the heat storage device is:

[0100] Step 1.3.1: Figure 3 As shown in (a), according to the fan speed v wind and pump flow rate v water , calculate the power delivered by the fan Determine whether it is satisfied If satisfied, calculate the input water tank power P waterin , go to step 1.3.2 and execute control strategy 1; if not satisfied, then make Calculate the input water tank power P waterin , go to step 1.3.3 and execute control strategy 2;

[0101] Step 1.3.2: Figure 3 As shown in (b), the calculated input water tank power P waterin Does it satisfy P waterin <P need , if satisfied, then increase the fan speed v wind , and return to step 1.3.1 to re-judge whether If not satisfied, keep the fan speed v wind unchanged, by adjusting the pump flow rate v water , so that P waterin =P need ; By adjusting the heat transfer power of the phase change heat storage bricks to meet The regulation is over.

[0102] Step 1.3.3: If Figure 3 As shown in (c), the calculated input water tank power P waterin Does it satisfy P waterin <P need If satisfied, go to step 1.3.4; if not satisfied, keep the fan speed v wind unchanged, by adjusting the pump flow rate v water , so that P waterin =P need By adjusting the heat transfer power of the phase change heat storage brick, it can meet the requirements of P xiang =0; control ends.

[0103] Step 1.3.4: Increase the pump flow rate v water , and determine the pump flow rate v water Does it satisfy v water <v watermax , if satisfied, calculate the input water tank power P waterin , go to step 1.3.5; if not satisfied, make v water =v watermax , Depend on Calculate v wind By adjusting the heat transfer power of the phase change heat storage bricks, it can meet the The regulation is over.

[0104] Step 1.3.5: Determine the calculated input tank power P waterin Does it satisfy P waterin <P need If satisfied, return to step 1.3.4; if not satisfied, maintain the fan speed v wind The pump flow rate v remains unchanged. water The heat transfer power of the phase change heat storage brick is adjusted to meet P xiang =0; control ends.

[0105] In one embodiment, we explored how to adjust the operating state of the heat storage device to meet the changing conditions when the output of renewable energy and load demand change. The main adjustment methods are to adjust the fan speed, water pump flow rate and the exchange power of the phase change heat storage brick. The main state quantities are set in advance (the following set quantities are all orders of magnitude, and the specific units can be determined according to the actual experiment): ① The basic speed of the fan v windbase =1500, maximum speed v windmax =4500, minimum speed v windmin =500, the heat power P that the fan can transfer at the basic speed windbase =75;②The maximum water inlet velocity v of the internal pipe waterinmax =10; ③ The product of the density, volume, and specific heat of the water in the water tank ρVc water =5, the initial temperature of water is 25 degrees Celsius; ④ the product of the cross-sectional area of ​​the external pipe, the water flow rate, the water density, and the specific heat capacity of water SvρVc water =5, the return water temperature is 25 degrees Celsius.

[0106] At standard atmospheric pressure and standard temperature, the input power variation curve of the heat storage device is as follows: Figure 5 As shown in (a), the output power change curve of the heat storage device is as follows Figure 5 As shown in (b) of Figure 1, the input power trend is lower in the early and late stages, and higher in the mid-stage. The output power trend is the opposite. This is because during the early and late stages, when wind power is abundant, the electrical load is low, and the thermal load is high. The thermal storage device primarily releases heat, reducing heat production in the combined heat and power generation units. This, coupled with a reduction in power generation due to the "heat-to-electricity" strategy, results in a greater share of the electrical load supplied by wind power. The reverse occurs in the mid-stage.

[0107] Under the above parameters, the simulation results show that the heat storage of the heat storage device, the fan speed, the water flow rate of the internal pipe, and the heat exchange power of the phase change heat storage brick change with time. Figure 6 As shown in (a), (b), (c) and (d).

[0108] Figure 6 The heat storage curve shown in (a) is Figure 5 The input power shown in (a) Figure 5 Compared with the output power curve shown in (b) in the figure, the changing trends are basically consistent. In the early and late stages, the input is low and the output is high, and the heat storage device supplies heat to the outside; in the middle stage, the input is high and the output is low, and the heat storage device stores heat inward.

[0109] Figure 6 The fan speed curve shown in (b) is Figure 5The output power curve shown in (b) is closely related to the fan speed. The fan speed is related to the fan's transmitted power, and the main purpose of the fan's transmitted power is to meet the output power demand. Comparing the two figures, it is found that the change trends of the two curves are basically the same, which is consistent with the expected control effect.

[0110] The water inlet flow rate of the internal pipe, when this value is less than or equal to 5, it means that the power transmitted by the fan is less than the input power and can meet the output power requirement; when this value is greater than 5 and less than 8, it means that the power transmitted by the fan has reached the input power value, and the water inlet flow rate is a basic value of 5 and still cannot meet the output power requirement. By increasing the water inlet flow rate to improve the energy transfer efficiency, the demand can be met; when this value reaches 8, if the output power requirement is still not met, the only way is to control the phase change heat storage bricks to diffuse heat outward and further increase the fan speed to meet the demand. Figure 6 The water inlet velocity curve shown in (c) is Figure 6 The fan speed shown in (d) Figure 7 From the fan speed adjustment curve under high altitude and cold environment conditions shown in the figure, it can be found that the water inlet flow rate value can reach 8 only when the fan speed is at a higher state. When the fan speed is lower, the water inlet flow rate value will also be low. Figure 6 The trend of the water inlet flow rate curve shown in (c) is consistent with the expected control effect.

[0111] In order to more clearly illustrate that the heat storage device is adjusted strictly according to the principle of "fan first, then water pump" during operation, the simulation results at the second moment are selected for illustration. At this time, the water inlet flow rate v waterin =8, the water pump has started to regulate, the fan speed v wind =3750, convert the power P transmitted by the fan wind =187.5, at this time the sum of the thermal power output by the dry-burning tube and the circulating power of the fan is 37.5, the power transmitted by the fan has far exceeded the limit, which is consistent with the water pump having reached the full working state with a margin, and the insufficient power is supplemented by the heat release of the heat storage bricks.

[0112] The heat exchange power curve of phase change heat storage brick is as follows Figure 6 As shown in (d), compare Figure 6 (d) in Figure 6 (c) shows that the experimental results meet expectations.

[0113] In summary, the establishment and simulation of the heat storage device model follow the three operating principles described above. In short, the fan is regulated first, and then the water pump is regulated. When the input of new energy and load fluctuate, the adjustment amount of the fan and water pump is already Figure 6 (c) and (d) in the figure are clearly shown, making the operation process of the heat storage device clearer.

[0114] In another embodiment, a simulation was conducted under high altitude and cold conditions, with the environmental conditions set to low pressure p = 65.25 kPa (standard atmospheric pressure 101.325 kPa) and low temperature T = 0°C. After the environmental factors were substituted into the simulation, the curve of the fan speed changing with time is shown in the figure below. Figure 7 shown.

[0115] Compare Figure 7 and Figure 6 In (b), we can see that the trends of the two curves are basically the same. This is because the load demand has not changed, indicating that the main factor determining the fan speed is still the load demand. The high altitude and cold environment conditions only modify the size of the fan speed. In both figures, the fan speed value at the second moment is taken for further study. Under standard environment, v wind1 =3750, v in high altitude and cold environment wind2 =6308. Considering the correction of low pressure C≈1.55, even for v wind1 After correction, it is still less than v wind2 , which means that low temperature conditions cause more heat dissipation and require the fan to provide a higher speed to meet more power transmission requirements.

[0116] Step 2: Establish the mathematical model and constraints of the cogeneration unit.

[0117] In a combined heat and power (CHP) unit, a gas-fired boiler burns fossil fuels to provide heat. This heated gas simultaneously drives a steam turbine to generate electricity. Therefore, the heat and electricity produced by a CHP unit form a proportional relationship, a formula closely related to the equation of heat-to-electricity.

[0118] In this embodiment, the relationship between the heat output and the power output of the cogeneration unit is:

[0119]

[0120] Where, P chp Indicates the power output of the cogeneration unit, P hchp Indicates the heat output of the cogeneration unit, k hp is the proportional coefficient.

[0121] At the same time, the production capacity of the cogeneration unit needs to be limited, and the constraints are:

[0122] P chpmin <P chp <P chpmax

[0123] Among them, P chpmin 、P chpmaxare the minimum and maximum power output of the cogeneration unit respectively.

[0124] Step 3: Establish an energy distribution model for the electric heating system network based on the requirements of electric load and thermal load.

[0125] In this embodiment, for the electric heating network energy distribution model, only the input power, output power and heat dissipation power are considered. Figure 4 The simplified diagram of energy flow in the electric heating system network is shown, which includes heat storage device, cogeneration unit, electric boiler, etc. Assuming that the real-time power of wind power P w , electric load e and heat load h are all known input quantities, and the heat and power output of the cogeneration unit can be adjusted as needed.

[0126] In order to make the mathematical model clearer, the heat output of the cogeneration unit is set as variable X1. Since the corresponding power output is determined by heat, it is kX1. The real-time power of wind power P is w The amount of electricity converted to heat energy is variable X2, and the amount of electricity used by wind power to meet the power load is P w =X2; Assume that the energy conversion efficiency of the electric boiler is η; the sum of the heat generated by the electric boiler and the heat generated by the cogeneration unit is the total heat supply. Part of the heat is input into the heat storage device and stored as variable X3, and the other part of the heat is used to meet the heat load, recorded as P hot In addition to the input heat X3, the heat storage device also has output heat X4 and heat dissipation Q to the outside world. Its heat storage E changes accordingly with the changes of variables X3, X4, and Q. In this embodiment, X1=P hchp , X2=P e , X4=hP hot , Q=Q cwaste , k=k hp , E=X3-X4-Q.

[0127] In order to meet the requirements of power load and heat load, it is necessary to impose conditions on each variable.

[0128] The constraints on power load are:

[0129] P w -X2+kX1≥e

[0130] The heat load constraints are:

[0131] X1+ηX2-X3+X4≥h

[0132] In fact, the electric load should match the power generation, and the thermal load should match the heat generation. The reason why the constraints of the electric load and the thermal load are in the form of greater than or equal to is to ensure that the electric load and the thermal load can be fully supplied. The difference between the supply and the load will also be calculated as wasted energy.

[0133] For variable X2, its value cannot exceed the amount of wind power generated. For variables X3 and X4, their values ​​will vary depending on the amount of heat stored in the heat storage device. When the amount of heat stored is high, heat input is no longer allowed, i.e. variable X3 is set to 0; when the amount of heat stored is low, heat output is no longer allowed, i.e. variable X4 is set to 0. This is shown in the following formula:

[0134]

[0135] Among them, E min 、E max Represent the minimum heat storage and the maximum heat storage, P wm Indicates the maximum power of wind power, P cim Indicates the maximum input power of the heat storage device, P com Indicates the maximum heat release power of the heat storage device.

[0136] Step 3.4: Establish the energy allocation objective function of the electric heating system network.

[0137] Starting from the mathematical model established above, with the total amount of wasted energy as the target, the objective function is shown in the following formula.

[0138] F=(P w -X2+kX1-e)+(X1+ηX2-X3+X4-h)

[0139] =(1+k)X1-(1-η)X2-X3+X4+P w -eh

[0140] Maximizing wind power consumption means minimizing wasted energy. The particle swarm algorithm is used to find the optimal solution of X1, X2, X3, and X4, so that F changes to the minimum. The operating parameters of the cogeneration unit are controlled according to the optimal solution.

[0141] The present invention takes the total amount of wasted energy as the objective function and adjusts various variables to minimize the total amount of wasted energy, thereby achieving maximum wind power consumption.

[0142] In order to further verify the effect of maximizing wind power consumption of the present invention, the basic values ​​of the entire model are set: 1. The maximum heat storage capacity of the heat storage device E max =2000MJ, minimum value E min=200MJ, initial value E = 1000MJ, maximum input power P cim =150MW, maximum output power P com =150MW; 2. The ratio of cogeneration k = 0.5, the maximum heat generation power P chpmax =600MW; 3. Maximum power P of wind turbine electric heat conversion wm =150MW.

[0143] The curves of wind power generation, electric load and heat load changing with time are as follows: Figure 8 As shown, its configuration mimics the patterns of wind power, electricity, and heat consumption in the Three North regions: 1. In summer, wind power generation and heat load are both low, while electricity load is high; 2. In winter, wind power generation and heat load are both high, while electricity load is low. This conflict between energy output and consumption necessitates the addition of heat storage devices to balance this.

[0144] The curves of the input power, output power and heat storage of the heat storage device over time are as follows: Figure 9 As shown in the figure. The change in heat storage capacity is actually determined by input power and output power, and the trend in the figure meets the requirements. It was observed that in the early and late stages, the output power of the heat storage device is greater than the input power, and the entire heat is released externally. This heat is used to supply the heat load, reducing the heat load borne by the cogeneration unit and reducing heat production. Due to the "heat-based electricity" principle, power production will also decrease accordingly, allowing more electricity load to absorb the excess wind power production. In the middle stage, the heat storage device as a whole absorbs heat from the outside. At this time, the relatively high electricity load and relatively low wind power production require the cogeneration unit to produce more electricity. Because the "heat-based electricity" principle produces heat that exceeds the heat load, it is absorbed by the heat storage device and not wasted.

[0145] The curve of the change of electric load and actual total power supply over time is as follows: Figure 10 The area between the two lines represents the wasted energy. Observations show that energy waste occurs primarily in the early and late stages of wind power generation, during periods of excess wind power capacity. Even with the addition of energy storage, the maximum power limit prevents full energy absorption.

[0146] The curve of heat load and actual heat supply changing with time is as follows: Figure 11 The area between the two lines represents the wasted heat energy. Observations show that heat energy waste occurs primarily in the middle period, when excess heat is generated to meet the electrical load.

[0147] For the objective function, the curve of wasted energy changing with time is as follows: Figure 12 As shown in (a), the energy wasted by comparing it with the model without adding heat storage device Figure 12By comparing with (b) in the figure, it can be seen that the main time points of energy waste are basically the same, but with the addition of the heat storage device, the energy waste is greatly reduced, even less than half, indicating that the addition of the heat storage device provides a good place for the consumption of new energy, and greatly solves the problem of new energy consumption.

[0148] This embodiment also provides an electric heating system control device for improving the consumption of new energy in high-altitude and cold regions, which is used to implement the above-mentioned embodiment. The terms "module", "unit", etc. used below can be a combination of software and / or hardware that implements the predetermined function. Although the system described in the following embodiments is preferably implemented in software, it is also possible to implement it in hardware, or a combination of software and hardware.

[0149] This embodiment provides an electric heating system control system for improving the consumption of new energy in high-altitude and cold areas, including:

[0150] A heat storage device modeling module, which is used to establish a mathematical model of the heat storage device;

[0151] The heat storage device model correction module is used to obtain high-altitude and cold environment parameters and correct the water temperature in the water tank in the heating unit mathematical model and the fan speed in the heat exchange unit mathematical model;

[0152] The combined heat and power unit modeling module is used to establish a mathematical model of the combined heat and power unit;

[0153] a first control module, which is used to control the operating parameters of the heat storage device according to the modified mathematical model of the heat storage device;

[0154] The electric heating system modeling module is used to establish the energy distribution model of the electric heating system network;

[0155] The second control module is used to control the operating parameters of the cogeneration unit using the energy distribution model of the electric heating system network according to the actual demand of electric load and thermal load, the mathematical model of the cogeneration unit and the operating parameters of the heat storage device.

[0156] In a specific implementation of the present invention, the heat storage device modeling module includes:

[0157] A heating unit modeling unit, which establishes a mathematical model using a dry-burning tube as a heating unit;

[0158] A heat storage unit modeling unit, which establishes a mathematical model using phase change heat storage bricks as heat storage units;

[0159] A heat exchange unit modeling unit, which establishes a mathematical model using a fan and a return pipe for storing water as a heat exchange unit;

[0160] A heating unit modeling unit, which establishes a mathematical model using a water tank and a water pump located on a return water pipe as a heating unit;

[0161] High altitude and cold environment parameter correction module.

[0162] In a specific implementation of the present invention, the heat storage device model correction module determines the heat dissipation of the water in the water tank based on the external low-temperature gas. The heat dissipation is specifically:

[0163] Q cwaste =A*β*ΔT

[0164] Where A is the surface area of ​​the water tank, β is the heat transfer coefficient, and Q cwaste Indicates the heat dissipation of the water tank;

[0165] According to the changes in external air pressure conditions and the relationship between air pressure and gas specific volume, the gas specific volume correction coefficient is determined:

[0166] C=P1 / P2

[0167] Wherein, P1 represents the standard atmospheric pressure, P2 represents the air pressure after the environment is changed, and C represents the specific volume correction coefficient of the gas;

[0168] According to the gas specific volume correction coefficient, the basic speed of the fan in the mathematical model of the heat exchange unit is corrected:

[0169]

[0170] in, Indicates the corrected fan base speed under low pressure environment. is the power transmitted by the fan in the corrected low pressure environment.

[0171] In a specific implementation of the present invention, the first control module includes:

[0172] The first judgment unit is used to determine the power transmitted by the fan according to the fan speed and the water pump flow rate, and to determine the control method of the fan speed, the water pump flow rate and the heat transfer power of the phase change heat storage brick by comparing the power transmitted by the fan with the sum of the heat power output by the dry-burning tube in the heating unit and the fan circulation power;

[0173] If the power transmitted by the fan is less than the sum of the heat output of the dry-burning tube in the heating unit and the fan circulation power, control strategy 1 is executed;

[0174] If the power transmitted by the fan is greater than or equal to the sum of the heat power output by the dry-burning tube in the heating unit and the fan circulation power, control strategy 2 is executed;

[0175] The first strategy unit is used to execute the first control strategy, including:

[0176] Calculate the input power of the water tank based on the actual fan power and the current water pump flow rate. Compare the input power of the water tank with the thermal power demand of the water tank to determine whether the fan speed, water pump flow rate, and heat transfer power of the phase change thermal storage bricks need to be adjusted.

[0177] If the input power of the water tank is less than the thermal power requirement of the water tank, the water pump flow rate is kept unchanged, the fan speed is increased, and the process returns to the first judgment unit;

[0178] If the input power of the water tank is greater than or equal to the thermal power demand of the water tank, the fan speed is kept unchanged, and the water pump flow rate is reduced to make the input power of the water tank equal to the thermal power demand of the water tank, and the heat transfer power of the phase change heat storage brick is adjusted to meet the requirements. The regulation ends; among them, Indicates the corrected power transmitted by the fan.

[0179] The second strategy unit is used to execute the second control strategy, including:

[0180] The sum of the thermal power output of the dry-burning tube in the heating unit and the fan circulation power is used as the power transmitted by the fan, and the input power of the water tank corresponding to the power transmitted by the fan is calculated; based on the comparison between the input power of the water tank and the thermal power demand of the water tank, it is determined whether the fan speed, water pump flow rate, and heat transfer power of the phase change heat storage brick need to be adjusted;

[0181] If the input power of the water tank is less than the thermal power requirement of the water tank, gradually increase the water pump flow rate;

[0182] If the input power of the water tank is greater than or equal to the thermal power requirement of the water tank, the fan speed is kept unchanged, and the water pump flow rate is reduced so that the input power of the water tank is equal to the thermal power requirement of the water tank. The heat transfer power of the phase change heat storage brick is adjusted to 0, and the control is completed.

[0183] For the device embodiments, since they basically correspond to the method embodiments, the relevant parts can be referred to the partial description of the method embodiments, and the implementation methods of the remaining modules are not repeated here. The device embodiments described above are merely illustrative, and the modules described as separate components may or may not be physically separated, that is, they may be located in one place or distributed across multiple network units. Those skilled in the art can understand and implement them without expending any creative effort.

[0184] The apparatus embodiments of the present invention can be applied to any device with data processing capabilities, such as a computer or other device. The apparatus embodiments can be implemented through software, hardware, or a combination of software and hardware. For example, a software implementation, as a logically defined apparatus, is implemented by a processor of any device with data processing capabilities, reading corresponding computer program instructions from non-volatile memory into internal memory and executing them.

[0185] An embodiment of the present invention also provides a computer-readable storage medium having a program stored thereon. When the program is executed by a processor, the method for controlling an electric heating system for improving the consumption of new energy in high-altitude and cold regions is implemented.

[0186] The computer-readable storage medium may be an internal storage unit of any device with data processing capabilities described in any of the aforementioned embodiments, such as a hard disk or memory. The computer-readable storage medium may also be an external storage device of any device with data processing capabilities, such as a plug-in hard disk, smart media card (SMC), SD card, flash card, etc., equipped on the device.

[0187] The above description is only a preferred specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any technician familiar with the technical field, within the technical scope disclosed by the present invention, who makes equivalent replacements or changes based on the technical solution and inventive concept of the present invention, should be covered by the scope of protection of the present invention.

Claims

1. A method for controlling an electric heating system to improve the consumption of new energy in high-altitude and cold regions, characterized in that: include: Step 1: Establish mathematical models for the heat storage device and the combined heat and power unit, modify the mathematical model of the heat storage device based on high-altitude and cold environment parameters, and adjust the operating parameters of the heat storage device based on the modified mathematical model; The step 1 comprises: Step 1.1: Establish mathematical models of the heating unit, heat storage unit, heat exchange unit, and heat supply unit in the heat storage device respectively; Step 1.2: Based on the high altitude and cold environment parameters, the water temperature in the water tank in the mathematical model of the heating unit and the fan speed in the mathematical model of the heat exchange unit are corrected; Step 1.3: Regulate the operating parameters of the heat storage device based on the constraints of the heat storage device, the mathematical model of the heating unit, the mathematical model of the heat storage unit, the corrected mathematical model of the heat supply unit, and the corrected mathematical model of the heat exchange unit; Step 2: Based on the actual demand for electrical and thermal loads, the mathematical model of the cogeneration unit, and the operating parameters of the heat storage device, the energy distribution model of the electric and thermal system network is used to control the operating parameters of the cogeneration unit; The second step includes: Step 2.1: According to the real-time power P of wind power w , electric load e and heat load h, and establish the energy distribution model of the electric heating system network; The energy distribution model is: the heat output P of the cogeneration unit hchp is variable X1, and the corresponding power generation is k hp X1; wind power real-time power P w Input power P to the dry-burning tube in the heating unit e is variable X2, then the wind power used to meet the power load is P w -X2; the energy conversion efficiency of the electric boiler is η, and the sum of the heat generated by the electric boiler and the heat generated by the cogeneration unit is the total heat supply. Part of the heat is input into the heat storage device and stored, which is set as variable X3, and the other part of the heat is used to meet the heat load, which is recorded as P hot In addition to the input heat X3, the heat storage device also has output heat X4 and heat dissipation to the outside world Q cwaste , its heat storage E changes with the variables X3, X4, Q cwaste The change will produce corresponding changes, E=X3-X4-Q cwaste , X4=hP hot ; Step 2.2: Establish the constraints and objective function of the energy distribution model, solve the objective function through the particle swarm algorithm, find the optimal solution of X1, X2, X3, and X4, and realize the operating parameter control of the cogeneration unit based on the optimal solution.

2. The electric heating system control method for improving the consumption of new energy in high-altitude and cold areas according to claim 1 is characterized in that: In step 1.1, the dry-burning tube is used as the heating unit, and the mathematical model of the heating unit in the heat storage device is expressed as follows: P he =αP e 0≤P e ≤P emax Among them, P e Indicates the input power of the dry-burning tube, P he Indicates the output thermal power of the dry-burning tube; α indicates the conversion coefficient of the dry-burning tube's input electrical power to output thermal power, P emax Indicates the maximum input power of the dry-burning tube; Taking the phase change heat storage brick as the heat storage unit, the mathematical model of the heat storage unit in the heat storage device is expressed as follows: Q(t)=Q(t-1)+δP xiang (t)Δt Among them, Q(t) is the heat stored in the phase change heat storage brick at time t, Q(t-1) is the heat stored in the phase change heat storage brick at time t-1, δ is the heat absorption and release efficiency of the phase change heat storage brick, P xiang (t) is the heat transfer power of the phase change heat storage brick at time t, where the heat transfer power is the output power of the dry-burning tube when the phase change heat storage brick is absorbing heat, and the heat transfer power is the power transferred by the fan when the phase change heat storage brick is releasing heat; Δt is the time it takes for the heat storage unit to absorb and release heat; The heat exchange unit includes a fan and a return pipe for storing water. The fan is used to guide the gas at a certain temperature to exchange energy with the water in the return pipe. The mathematical model of the heat exchange unit in the heat storage device is expressed as follows: Among them, v windbase Indicates the basic speed of the fan, P windbase Indicates the power delivered by the fan at the base speed, v wind Indicates the fan speed, P wind Indicates the power transmitted by the fan at a certain speed, v windmin and v windmax They represent the minimum speed and maximum speed of the fan respectively, and a and b are constants; The heating unit includes a water tank and a water pump located on the return pipe. The mathematical model of the heating unit in the heat storage device is expressed as follows: Among them, v waterin Indicates the return water velocity inside the water tank, v waterinmax represents the maximum return flow rate inside the water tank, λ is the efficiency of energy transfer between gas and water, P waterin Indicates the external input power to the water tank, which is affected by the flow rate of the water pump; P waterout Indicates the output power of the water tank to the outside, P wind Indicates the power delivered by the fan at a certain speed; S indicates the cross-sectional area of ​​the return pipe, v waterout represents the water flow rate of the water tank; ρ represents the density of water, c water It represents the specific heat capacity of water, and ΔT represents the temperature difference between the outlet and return water of the water tank.

3. The electric heating system control method for improving the consumption of new energy in high-altitude and cold areas according to claim 2 is characterized in that: In step 1.2, the heat dissipation of the water in the water tank is determined based on the external low-temperature gas. The heat dissipation is specifically: Q cwaste =A*β*ΔT Where A is the surface area of ​​the water tank, β is the heat transfer coefficient, and Q cwaste Indicates the heat dissipation of the water tank; According to the changes in external air pressure conditions and the relationship between air pressure and gas specific volume, the gas specific volume correction coefficient is determined: C=P1 / P2 Wherein, P1 represents the standard atmospheric pressure, P2 represents the air pressure after the environment is changed, and C represents the specific volume correction coefficient of the gas; According to the gas specific volume correction coefficient, the basic speed of the fan in the mathematical model of the heat exchange unit is corrected: in, Indicates the corrected fan base speed under low pressure environment. is the power transmitted by the fan in the corrected low pressure environment.

4. The electric heating system control method for improving the consumption of new energy in high-altitude and cold areas according to claim 2 is characterized in that: The mathematical model constraints of the heat storage device are expressed as follows: Among them, P he P is the thermal power output of the dry-burning tube in the heating unit; xiang P is the energy exchange from the phase change heat storage brick in the heat storage unit to the outside, with a positive value of heat release and a negative value of heat absorption; wind P is the power of the fan to drive the gas to the water pipe; windback The power that is not transferred back during the process of the fan driving the gas to transfer power to the water pipe is recorded as the fan circulation power; P need Indicates the thermal power required to be input into the water tank, T waterout Indicates the temperature of the water to be output; ρ indicates the density of water, v waterout Indicates the water flow rate of the water tank, v water represents the water pump flow rate, ΔT1 represents the temperature difference of the water tank before and after heating, ΔT2 represents the difference between the water outlet temperature and the return water temperature of the water tank, and t represents the heating time.

5. The electric heating system control method for improving the consumption of new energy in high-altitude and cold areas according to claim 2 is characterized in that: In step 1.3, the method for regulating the operating parameters of the heat storage device includes: Step 1.3.1: Determine the power transmitted by the fan based on the fan speed and water pump flow rate. Compare the power transmitted by the fan with the sum of the heat power output by the dry-burning tube in the heating unit and the fan circulation power to determine a control method for the fan speed, water pump flow rate, and heat transfer power of the phase change thermal storage brick. The control method includes control strategy 1 and control strategy 2. Step 1.3.2: If the power transmitted by the fan is less than the sum of the thermal power output of the dry-burning tubes in the heating unit and the fan circulating power, then execute control strategy 1; Step 1.3.3: If the power transmitted by the fan is greater than or equal to the sum of the thermal power output of the dry-burning tubes in the heating unit and the fan circulating power, then execute control strategy 2.

6. The electric heating system control method for improving the consumption of new energy in high-altitude and cold areas according to claim 5 is characterized in that: The control strategy 1 is specifically as follows: Step 1.3.2.1: Calculate the water tank input power based on the actual fan power and the current pump flow rate. Compare the water tank input power with the water tank's thermal power requirements to determine whether the fan speed, pump flow rate, and heat transfer power of the phase change thermal storage bricks need to be adjusted. Step 1.3.2.2: If the water tank input power is less than the water tank's thermal power requirement, maintain the pump flow rate, increase the fan speed, and return to step 1.3.1; If the input power of the water tank is greater than or equal to the thermal power demand of the water tank, the fan speed is kept unchanged, and the water pump flow rate is reduced to make the input power of the water tank equal to the thermal power demand of the water tank, and the heat transfer power of the phase change heat storage brick is adjusted to meet the requirements. The regulation ends; among them, Indicates the corrected power transmitted by the fan.

7. The electric heating system control method for improving the consumption of new energy in high-altitude and cold areas according to claim 5 is characterized in that: The second control strategy is specifically as follows: Step 1.3.3.1: Take the sum of the thermal power output of the dry-burning tube in the heating unit and the fan's circulating power as the fan's transmitted power, and calculate the corresponding water tank input power. Compare the water tank's input power with the water tank's thermal power requirement to determine whether the fan speed, water pump flow rate, and heat transfer power of the phase change thermal storage bricks need to be adjusted. Step 1.3.3.2: If the input power to the water tank is less than the thermal power requirement of the water tank, gradually increase the pump flow rate; If the input power of the water tank is greater than or equal to the thermal power requirement of the water tank, the fan speed is kept unchanged, and the water pump flow rate is reduced so that the input power of the water tank is equal to the thermal power requirement of the water tank. The heat transfer power of the phase change heat storage brick is adjusted to 0, and the control is completed.

8. The electric heating system control method for improving the consumption of new energy in high-altitude and cold areas according to claim 7 is characterized in that: In the process of gradually increasing the water pump flow rate in step 1.3.3.2, when the water pump flow rate has reached the maximum limit, The power transmitted by the fan is calculated based on the thermal power demand of the water tank, and the fan speed is calculated based on the power transmitted by the fan as the fan control result. The water pump flow rate is maintained at the maximum value, and the heat transfer power of the phase change heat storage brick is adjusted to meet the requirements. End of regulation; When the water pump flow rate has not reached the maximum limit, the input power of the water tank is calculated based on the current water pump flow rate and fan speed. If the input power of the water tank is still less than the thermal power demand of the water tank, the water pump flow rate is continued to be increased until the input power of the water tank is equal to the thermal power demand of the water tank. The fan speed and water pump flow rate are maintained unchanged, and the heat transfer power of the phase change heat storage brick is adjusted to 0, and the control is completed.

9. The electric heating system control method for improving the consumption of new energy in high-altitude and cold areas according to claim 1 is characterized in that: The mathematical model of the cogeneration unit is expressed as: Where, P chp Indicates the power output of the cogeneration unit, P hchp Indicates the heat output of the cogeneration unit, k hp is the proportionality coefficient; The constraints of the combined heat and power unit are: P chpmin <P chp <P chpmax Among them, P chpmin 、P chpmax are the minimum and maximum power output of the cogeneration unit respectively.

10. The electric heating system control method for improving the consumption of new energy in high-altitude and cold areas according to claim 1 is characterized in that: The constraints of the energy allocation model are: Power load constraints: P w -X2+k hp X1≥e Heat load constraints: X1+ηX2-X3+X4≥h Constraints between variables: Among them, E min 、E max Represent the minimum heat storage and the maximum heat storage, P wm Indicates the maximum power of wind power, P cim Indicates the maximum input power of the heat storage device, P com Indicates the maximum heat release power of the heat storage device.

11. The electric heating system control method for improving the consumption of new energy in high-altitude and cold areas according to claim 1 is characterized in that: The energy allocation model uses the total amount of wasted energy as the objective function, which is expressed as follows: F=(P w -X2+k hp X1-e)+(X1+ηX2-X3+X4-h) =(1+k hp )X1-(1-η)X2-X3+X4+P w -e-h Where F represents the total amount of wasted energy.

12. An electric heating system control device for improving the consumption of new energy in high-altitude and cold regions, used to implement the electric heating system control method for improving the consumption of new energy in high-altitude and cold regions as described in claim 1, characterized in that: The device includes: A heat storage device modeling module, which is used to establish a mathematical model of the heat storage device; The heat storage device model correction module is used to obtain high-altitude and cold environment parameters and correct the water temperature in the water tank in the heating unit mathematical model and the fan speed in the heat exchange unit mathematical model; The combined heat and power unit modeling module is used to establish a mathematical model of the combined heat and power unit; a first control module, which is used to control the operating parameters of the heat storage device according to the modified mathematical model of the heat storage device; The electric heating system modeling module is used to establish the energy distribution model of the electric heating system network; The second control module is used to control the operating parameters of the cogeneration unit using the energy distribution model of the electric heating system network according to the actual demand of electric load and thermal load, the mathematical model of the cogeneration unit and the operating parameters of the heat storage device.

13. A computer-readable storage medium, characterized in that A program is stored thereon, which, when executed by a processor, is used to implement an electric heating system control method for improving the consumption of new energy in high-altitude and cold areas as described in any one of claims 1-11.

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