Ice storage air conditioning operation scheduling method based on variable air volume control

Abstract

The application discloses an ice storage air conditioner operation scheduling method based on variable air volume control. Historical statistical data of city refrigeration load are acquired, and then a building internal setting temperature curve is fitted, and a load typical operation scene is generated based on the historical statistical data of city refrigeration load; the building internal setting temperature curve is constrained according to preset human comfort boundary conditions, upper and lower boundary curves of the building internal setting temperature curve are obtained, and then are converted into a building refrigeration demand curve; a model constraint condition is constructed according to the building refrigeration demand curve, and then an ice storage air conditioner operation optimization model based on variable air volume control is constructed; the load typical operation scene is input into the ice storage air conditioner operation optimization model based on variable air volume control to obtain a scheduling result. The application can further release the regulation potential of the ice storage air conditioner, expand the power system demand response load resource pool, and improve the supply and demand balance ability of the power grid to cope with the randomness and fluctuation of new energy output.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of power system dispatch and operation, and particularly relates to an ice storage air conditioner operation scheduling method based on variable air volume control. BACKGROUND

[0002] The randomness and volatility of renewable energy output bring new challenges to power system power balance. In order to cope with the risk of supply and demand imbalance brought by the increasing proportion of new energy units, potential regulation resources in the system need to be tapped. The power consumption of building air conditioning system in urban power grid accounts for a high proportion, and the air conditioning system has significant regulation potential due to the heat insulation capacity of building envelope. Ice storage air conditioner can convert electric energy into cold energy for storage during low valley period of electricity price, and supply cold energy during peak period of electricity price to reduce the power consumption of ice storage air conditioner. At the same time, in the process of ice storage air conditioner participating in demand response, the comfort boundary of users needs to be considered, and therefore an ice storage air conditioner system based on variable air volume control is proposed. As an important demand response resource of urban power grid, ice storage air conditioner needs to propose an ice storage air conditioner operation scheduling method based on variable air volume control.

[0003] In the existing ice storage air conditioner scheduling method, the model of ice storage air conditioner unit is relatively rough, the influence of air outlet rate of air conditioner on human comfort is not considered, and the ice storage air conditioner is not considered as a demand response load resource in the process of scheduling and participating in power system demand response, and the regulation potential of ice storage air conditioner is ignored. SUMMARY

[0004] In view of the problems in the above background art, the present application provides an ice storage air conditioner operation scheduling method based on variable air volume control.

[0005] The technical scheme adopted by the present application is as follows:

[0006] The present application comprises the following steps:

[0007] S1, obtaining historical statistical data of urban refrigeration load, fitting to obtain building internal set temperature curve, and generating load typical operation scene based on the historical statistical data of urban refrigeration load;

[0008] S2, constraining the building internal set temperature curve according to the preset human comfort boundary condition, obtaining the upper boundary and lower boundary curve of the building internal set temperature curve, and then converting to the refrigeration demand curve of the building;

[0009] S3, constructing model constraint condition according to the refrigeration demand curve of the building, and then constructing ice storage air conditioner operation optimization model based on variable air volume control;

[0010] S4. Input the typical load operation scenario into the ice storage air conditioning operation optimization model based on variable air volume control to obtain the scheduling result.

[0011] The historical statistical data of urban cooling load in step S1 includes historical data of urban summer ambient temperature, historical data of urban building cooling power consumption, historical data of air conditioning load response capacity, and historical data of electricity market cost curves.

[0012] The temperature curve set inside the building in step S1 is a preset curve for the building's internal temperature in a typical load operation scenario, used to characterize the relationship between the building's indoor temperature and time.

[0013] The upper and lower boundary curves of the temperature curve set inside the building in step S2 are specifically the highest upper boundary curve and the lowest lower boundary curve of temperature set according to the boundary conditions of human comfort, which are used to limit the allowable fluctuation range of indoor temperature over time.

[0014] In step S2, the cooling demand curve of the building is a function curve of cooling power changing with time, calculated based on the upper and lower boundary curves of the set temperature curve inside the building.

[0015] In step S1, the typical load operation scenario is generated by generating a load operation scenario set through historical statistical data of urban cooling load, and then the typical load operation scenario is extracted from the load operation scenario set using the K-means clustering method.

[0016] The cooling demand curve of the building in step S2 is obtained by processing according to the following steps:

[0017] 1) Substitute the preset human comfort boundary conditions into the human comfort model to obtain the upper and lower boundary curves of the set temperature curve inside the building.

[0018] 2) The upper and lower boundary curves of the set temperature curve inside the building are used to constrain the second-order thermodynamic dynamic model of the building to obtain the cooling capacity required for the building to maintain the set temperature range at each time, thus forming the cooling demand curve of the building.

[0019] The model constraints in step S3 include human comfort boundary constraints, building cooling demand constraints, and ice storage air conditioning system operation constraints.

[0020] (1) The human comfort boundary constraints are set according to the following formula:

[0021] NET A (t)=37-(37-T A in (t)) / (0.68-0.0014RH A(t)+1 / (1.76+1.4(u m,s wind (t)) 2 ))

[0022] NET min ≤NET A (t)≤NET max

[0023] In the formula, NET A (t) represents the net effective temperature at time t, T A in (t) represents the set indoor temperature of the building, RH A (t) represents the indoor relative humidity at time t, u m,s wind (t) represents the fan speed of the indoor ice storage air conditioner, NET min and NET max These are the minimum and maximum values ​​of the net effective temperature, respectively.

[0024] (2) The building cooling demand constraint is set according to the following formula:

[0025] Q A,r LD (t)=Q A,r AC (t)+Q A,r IS,dis (t)

[0026] Q A,r AC (t)=COP AC ×(P A,r AC (t)-P A,r ch (t))

[0027] In the formula, Q A,r LD Q(t) represents the required cooling capacity of the room at time t. A,r AC (t) is the power (Q) that provides cooling capacity to the ice storage air conditioning chiller. A,r IS,dis (t) represents the cooling power supplied to the interior of the building in the scene when the ice storage tank of the ice storage air conditioner melts ice, COP. AC For ice storage air conditioning chillers, P A,r AC (t) represents the electrical power P of the ice storage air conditioning unit providing cooling to the interior of the building in the scene. A,r ch (t) is the electrical power that provides cooling capacity to the ice maker and ice storage tank for the ice storage air conditioner;

[0028] (3) The operating constraints of the ice storage air conditioning system include the operating constraints of the ice storage air conditioning system in the ice storage state, the operating constraints of the ice storage air conditioning system in the ice melting state, and the operating constraints of the ice storage tank of the ice storage air conditioning system in the ice storage working state and the ice melting working state.

[0029] (3.1) The operating constraints of the ice storage air conditioner in ice storage mode are set according to the following formula:

[0030] Q min AC ≤Q A,r AC (t)≤Q max AC

[0031] U A,r IS,ch (t)×Q min IS,ch ≤Q A,r IS,ch (t)≤U A,r IS,ch (t)×Q max IS,ch

[0032] Q A,r AC (t)=Q A,r LD (t)+Q A,r IS,ch (t)

[0033] Q A,r IS,dis (t)=0

[0034] C A,r IS (t)=C A,r IS (t-1) / (1-η IS,loss )+η IS,ch ×Q A,r IS,ch (t)×Δt

[0035] P A,r ch (t)+P A,r AC (t)=P A,r LD (t)

[0036] P A,r ch (t)=Q A,r IS,ch (t) / η EER IS

[0037] P A,r AC (t)=Q A,r AC (t) / η EER AC

[0038] In the formula, Q A,r AC (t) is the power (Q) that provides cooling capacity to the ice storage air conditioning chiller. min AC and Q max AC Q represents the minimum and maximum power output of the ice storage air conditioning unit, respectively. A,r IS,ch (t) represents the cooling capacity of the refrigeration mechanism under the ice storage tank operation state of the ice storage air conditioning system, Q. min IS,ch and Q max IS,ch U represents the minimum and maximum values ​​of the cooling capacity power of the refrigeration mechanism under the ice storage tank operation conditions of the ice storage air conditioner. A,r IS,ch (t) represents the operating state of the ice storage air conditioner during ice storage, Q A,r IS,dis (t) represents the power of cooling supplied by the ice storage air conditioning system when the ice storage tank is melting ice, Q A,r LD (t) represents the required cooling capacity of the room at time t, C. A,r IS (t) and C A,r IS (t-1) represent the cold storage capacity reserves of the ice storage tank in the ice storage air conditioning system at time t and time t-1, respectively, η IS,loss η represents the cooling capacity loss rate of the ice storage tank in an ice storage air conditioning system. IS,ch P represents the ice-making efficiency of an ice storage air conditioning system, where Δt is the time interval of a calculation step. A,r AC (t) represents the electrical power P of the ice storage air conditioning unit providing cooling to the interior of the building in the scene. A,r ch (t) represents the electrical power P that supplies cooling capacity to the ice maker in the ice storage air conditioner. A,r LD (t) represents the total power consumption of the ice storage air conditioner at time t, η EER IS and η EER AC These are the energy efficiency ratios of ice storage air conditioning ice makers and refrigeration units, respectively.

[0039] (3.2) The operating constraints of the ice storage air conditioner in the ice-melting state are set according to the following formula:

[0040] Q min AC ≤Q A,r AC (t)≤Q max AC

[0041] Q A,r AC (t)=COP AC ×P A,r AC (t)

[0042] U A,r IS,dis (t)×Q min IS,dis ≤Q A,r IS,dis (t)≤U A,r IS,dis (t)×Q max IS,dis

[0043] Q A,r AC (t)+Q A,r IS,dis (t)=Q A,r LD (t)

[0044] Q A,r IS,ch (t)=0

[0045] C A,r IS (t)=C A,r IS (t-1) / (1-η IS,loss )-Q A,r IS,dis (t) / η IS,dis ×Δt

[0046] P A,r AC (t)=P A,r LD (t)

[0047] P A,r ch (t)=0

[0048] P A,r AC (t)=Q A,r AC (t) / η EERAC

[0049] In the formula, Q A,r AC (t) is the power (Q) that provides cooling capacity to the ice storage air conditioning chiller. min AC and Q max AC Q represents the minimum and maximum power output of the ice storage air conditioning unit, respectively. A,r IS,ch (t) represents the cooling capacity of the ice-making mechanism of the ice storage air conditioner in ice storage operation mode, Q. A,r IS,dis (t) represents the power of cooling supplied by the ice storage air conditioning system when the ice storage tank is melting ice, Q min IS,dis and Q max IS,dis η represents the minimum and maximum power supplied by the ice storage tank of the ice storage air conditioner during ice melting operations, respectively. IS,dis This represents the ice melting efficiency of the ice storage tank in the ice storage air conditioning system, where Δt is the time interval of one calculation step.

[0050] (3.3) The operating constraints of the ice storage tank for the ice storage air conditioning system under both the ice storage and ice melting working states are set according to the following formula:

[0051] C min IS ≤C A,r IS (t)≤C max IS

[0052] C A,r IS (0)=C A,r IS (T)=ε IS ×C max IS

[0053] C A,r IS (t)=C A,r IS (t-1) / (1-η IS,loss )+(η IS,ch ×Q A,r IS,ch (t)-Q A,r IS,dis (t) / η IS,dis )×Δt

[0054] In the formula, C A,r IS (t) and C A,rIS (t-1) represents the cold storage capacity of the ice storage tank in the ice storage air conditioning system at times t and t-1, C min IS and C max IS C represents the minimum and maximum values ​​of the cold storage capacity of the ice storage tank in an ice storage air conditioning system. A,r IS (0) and C A,r IS (T) represents the initial and final time values ​​of the ice storage capacity reserve of the ice storage air conditioning ice tank, respectively. ε IS η represents the initial cooling capacity reserve coefficient of the ice storage tank in an ice storage air conditioning system, where T is an optimization period. IS,loss η represents the cooling capacity loss rate of the ice storage tank in an ice storage air conditioning system. IS,ch Q represents the ice-making efficiency of an ice storage air conditioning unit. A,r IS,ch (t) represents the cooling capacity of the ice-making machine in the ice storage air conditioner during ice storage operation, Q. A,r IS,dis (t) represents the power of cooling supplied by the ice storage air conditioning system when the ice storage tank is melting ice, η IS,dis Δt represents the ice melting efficiency of the ice storage tank in the ice storage air conditioning system, where Δt is the time interval of a calculation step.

[0055] In step S3, the objective function of the ice storage air conditioning operation optimization model based on variable air volume control is set according to the following formula:

[0056] min f=Σ(α×M AC t +β×M PMV t -γ×M DR t )

[0057] M AC t =(P A,r LD (t)+P A,r wind (t))×ζ e t ×Δt

[0058] M PMW t =(v PMV ) 2 ×ζ PMV t

[0059] M DR t =P A,rDR (t)×ζ DR t ×T DR

[0060] In the formula, min f is the objective function of the ice storage air conditioning operation optimization model, and M AC t v represents the total power consumption cost of the ice storage air conditioning system at time t, where Δt is the time interval of a calculation step. PMV For human comfort, M PMV t M represents the cost of user comfort loss. DR t P represents the reward for user participation in demand response. α, β, and γ are the weighting coefficients for the total power consumption cost of ice storage air conditioning, the cost of user comfort loss, and the reward for user participation in demand response, respectively, under multi-objective optimization conditions. A,r LD (t) represents the power consumption of the ice storage air conditioner at time t, P A,r wind (t) represents the power consumption of the internal fan of the ice storage air conditioner at time t, ζ e t Let ζ be the unit electricity cost parameter in the electricity market at time t. PMV t Let P be the unit cost of user comfort loss at time t. A,r DR (t) represents the demand response capacity that the ice storage air conditioning system should provide at time t, ζ DR t Let T be the reward received by a user for participating in demand response at time t. DR The duration of user participation in the demand response.

[0061] The scheduling results include the total operating cost of the ice storage air conditioner, the operating status and power consumption of the internal fan of the ice storage air conditioner, the operating status and power consumption of the ice storage air conditioner, the cooling power curve of the ice storage air conditioner, and the indoor temperature curve of the building.

[0062] The beneficial effects of this invention are as follows:

[0063] Based on the actual operation of ice storage air conditioning, a refined model of ice storage air conditioning units based on variable air volume control was established, considering the impact of the air outlet rate of the internal fan of the ice storage air conditioning unit on the human comfort of indoor personnel. In the ice storage air conditioning operation scheduling model, a typical scenario of ice storage air conditioning load participating in demand response was constructed to further explore the regulation potential of ice storage air conditioning, expand the demand response load resource pool of the power system, and improve the power grid's ability to balance supply and demand in response to the randomness and fluctuation of new energy output. Attached Figure Description

[0064] Figure 1 This invention relates to an ice storage air conditioning operation scheduling method based on variable air volume control.

[0065] Figure 2 This is a schematic diagram of the second-order ordinary differential equation constructed based on the dynamic changes of building thermal in this invention.

[0066] Figure 3 This is a structural diagram of an ice storage air conditioner based on variable air volume control according to the present invention.

[0067] Figure 4 This is a diagram showing the operating status of the ice storage air conditioner under the ice storage state of this invention.

[0068] Figure 5 This is a diagram showing the operating status of the ice storage air conditioner under the ice melting state of this invention. Detailed Implementation

[0069] The present invention will be further described and illustrated below with reference to the accompanying drawings and specific embodiments.

[0070] like Figure 1 As shown, this embodiment includes the following steps:

[0071] S1. Obtain historical statistical data on urban cooling load, then fit the set temperature curve inside the building, and generate typical load operation scenarios based on the historical statistical data of urban cooling load.

[0072] S2. Constrain the set temperature curve inside the building according to the preset human comfort boundary conditions to obtain the upper and lower boundary curves of the set temperature curve inside the building, and then use the second-order equivalent thermal parameter model to convert it into the cooling demand curve of the building.

[0073] S3. Construct model constraints based on the building's cooling demand curve, and then construct an ice storage air conditioning operation optimization model based on variable air volume control.

[0074] S4. Input the typical load operation scenario into the ice storage air conditioning operation optimization model based on variable air volume control to obtain the scheduling result.

[0075] The historical statistical data of urban cooling load in step S1 includes historical data of urban summer ambient temperature, historical data of urban building cooling power consumption, historical data of air conditioning load response capacity, and historical data of electricity market cost curves.

[0076] In step S1, the temperature curve set inside the building is a curve that is artificially preset for the temperature inside the building in a typical load operation scenario. It serves as the baseline for the cooling capacity required by the indoor space, and then as the baseline for the cooling capacity output of the subsequent ice storage air conditioner. The horizontal and vertical axes are time and temperature, respectively, used to characterize the relationship between the indoor temperature of the building and time.

[0077] In step S2, the upper and lower boundary curves of the temperature curve set inside the building are specifically the highest upper boundary curve and the lowest lower boundary curve of the temperature set according to the boundary conditions of human comfort. These curves serve as the boundary curves for the required cooling capacity of the indoor space, limiting the output range of the cooling capacity of the subsequent ice storage air conditioner. The horizontal and vertical axes represent time and temperature, which are used to limit the allowable fluctuation range of indoor temperature over time.

[0078] In step S2, the building's cooling demand curve is a function curve of cooling power changing with time, calculated based on the upper and lower boundary curves of the building's internal set temperature curve according to the second-order differential equation of the indoor building. This curve is used to specify the output curve of the ice storage air conditioning cooling capacity, with the horizontal and vertical axes representing time and cooling power.

[0079] In step S1, the typical load operation scenario is generated by using historical statistical data of urban cooling load to create a set of load operation scenarios. Then, the K-means clustering method is used and the Elbow Method is used to determine the number of clusters. The typical load operation scenario is then extracted from the set of load operation scenarios.

[0080] The historical data on urban ambient temperature, electricity market price curves, building cooling power consumption curves, and air conditioning load response capacity include: statistical data on urban ambient temperature, electricity market price, and building cooling power consumption every 15 minutes during the summer, totaling 96 data points in 24 hours; and building air conditioning load response capacity data every 15 minutes during a certain period in the summer, with the air conditioning load response duration set at 2 hours, totaling 8 data points.

[0081] Typical load operation scenarios are obtained through the following process:

[0082] For N N T Given a massive number of scenarios to be clustered, we set the maximum number of typical scenarios, K, and initialize the K-means clustering target to reduce the number of scenarios before starting the clustering iteration. k A scenario {C1, C2, C3, ..., C k The initial cluster center is used as the initial cluster center scene. The distance from each scene to the initial center scene is calculated as follows:

[0083] D(M i C j )=(Σt=1 NT (M it -C jt ) 2 ) 0.5

[0084] In the formula, D(M) i C j ) is the first i This concludes the first scene. k The central scenario C of the secondary clustering iteration j k The distance, N T The data dimension for the scenario.

[0085] After calculating the distance from each scene to the central scene, the first clustering is performed based on the closest initial central scene, yielding the initial clustering results. Based on these initial clustering results, the centers of each cluster are determined and used as the new cluster center scenes.

[0086] Repeated iterations until the changes in the cluster center scenario satisfy the convergence condition will yield the final result. k Using a cluster center scenario as a typical operating scenario, calculate the sum of distances D between all scenarios of each cluster and the center of that cluster in the results of this clustering iteration. k as follows:

[0087] D k =Σ i=1 N D(M i C j k )

[0088] This concludes the current clustering process. Let k = k + 1, and proceed with the next clustering iteration.

[0089] when k = K At that time, all clustering iterations are completed, resulting in K typical operating scenarios for ice storage air conditioning participating in demand response. The distance to the actual operating scenario S on a certain summer day in the area is calculated as follows:

[0090] D(K i ,S)=(Σ t=1 NT (K it -S t ) 2 ) 0.5

[0091] In the formula, D(K) i S) is the first i Scene S i The distance N to the actual operating scenario S on a certain summer day in this location. T For the data dimensions of the scenario;

[0092] After calculating the distances from K typical operating scenarios to the actual scenario, according to D(K) i Depending on the changes in typical operating scenarios, D(K) is selected. i The scenario corresponding to the minimum value of S) serves as a typical operating scenario for ice storage air conditioning based on variable air volume control to participate in demand response.

[0093] The load operation scenario set is a collection of multiple load operation situations formed by fitting, dividing or clustering historical statistical data of urban cooling load; the typical load operation scenario is a representative load scenario extracted from the load operation scenario set.

[0094] like Figure 2 As shown in the figure, the second-order ordinary differential equation based on the building's thermal dynamics process is used to calculate the building's cooling demand curve based on the upper and lower boundary curves of the indoor temperature.

[0095] The cooling demand curve of the building in step S2 is obtained by processing according to the following steps:

[0096] 1) Substitute the preset human comfort boundary conditions into the human comfort model to obtain the upper and lower boundary curves of the set temperature curve inside the building.

[0097] 2) The upper and lower boundary curves of the set temperature curve inside the building are used to constrain the second-order thermodynamic dynamic model of the building to obtain the cooling capacity required for the building to maintain the set temperature range at each time, thus forming the cooling demand curve of the building.

[0098] The cooling demand curve of the building in step S2 is obtained by processing the following formula:

[0099] -1≤v PMW ≤+1

[0100] v PMV =(0.303e -0.036M +0.028)×{(MW)-3.05×10 -3 [5733-6.99(MW)-P a -0.42[(MW)

[0101] -58.15]-1.7×10 -5 M(5857-P a -1.4×10 -3 M(34-t a )

[0102] -3.96×10 -8 f c1 [(tc1 +273) 4 -(t r +273) 4 ]–f c1 h c (t c1 -t a )}

[0103] T A in (t)=t a

[0104] C in ×dT A in (t) / dt=(T A out (t)-T A in (t)) / R out +(T A m (t)-T A in (t)) / R m +Q A in (t)-Q A,r LD (t)

[0105] C m ×dT A m (t) / dt=(T A in (t)-T A m (t)) / R m

[0106] In the formula, v PMW Human comfort level -1 ≤ v PMW ≤+1 represents the preset boundary conditions for human comfort, M represents the preset human metabolic rate, W represents the heat consumed by the human body during external work, and P represents the heat consumed by the human body during external work. a For water vapor partial pressure, t a f is the air temperature. c1 t represents the ratio of human body surface area when clothed to when naked. c1 For the surface temperature of clothing, t r h is the average value of the radiation temperature. c For convective heat transfer intensity, C in The equivalent heat capacity of building air, expressed in kilojoules per degree Celsius; T A in (t) represents the set indoor temperature of the building, in degrees Celsius; T Aout (t) represents the outdoor temperature, in degrees Celsius; R out Equivalent thermal resistance of building exterior, expressed in degrees Celsius per kilowatt; T A m (t) represents the building thermal mass temperature, in degrees Celsius; R m Q represents the equivalent thermal resistance inside a building, expressed in degrees Celsius per kilowatt. A in (t) represents the total heat generated by indoor occupants and electrical equipment, expressed in kilowatts; Q A,r LD (t) represents the required cooling capacity of the room at time t, in kilowatts (kW) and kilowatts (C). m Equivalent heat capacity of building interior thermal mass, expressed in kilojoules per degree Celsius.

[0107] The maximum adjustable range of the set temperature based on the daily set temperature curve inside the building is obtained by calculating the human comfort boundary. For buildings with indoor environmental parameter (temperature, humidity, wind speed) monitoring capabilities, the adjustable range of the set temperature can be obtained. According to the International Organization for Standardization (ISO) and my country's comfort standards, the thermal comfort standard is set as -1 ≤ PMV ≤ +1. After determining the PMV boundary, with other factors remaining constant, by changing only the set temperature based on the daily set temperature curve inside the building, the adjustable boundary of the building's internal set temperature considering user comfort can be obtained.

[0108] A thermodynamic equivalent model is used to establish the relationship between the power consumption of the air conditioning load and physical parameters such as the set temperature, ambient temperature, and energy efficiency ratio. This relationship is typically expressed mathematically as a second-order ordinary differential equation. The second-order ordinary differential equation contains Q... A,r LD (t) represents the required cooling capacity of the room at time t, in kilowatts. It is related to the cooling power of the ice storage air conditioner and the cooling capacity of the ice storage tank, as shown in the following formula:

[0109] Q A,r LD (t)=COP AC ×(P A,r AC (t)-P A,r ch (t))+Q A,r IS,dis (t);

[0110] The specific constraints of the model constructed based on the building's cooling demand curve are as follows: In order to ensure that the actual indoor temperature curve is within the upper and lower boundaries of the set indoor temperature, the building's cooling demand curve is calculated, which in turn affects the constraints on the cooling capacity output of the ice storage air conditioner, namely the upper and lower boundary conditions of the cooling capacity output of the ice storage air conditioner.

[0111] likeFigure 3 As shown in the figure, the diagram illustrates the structure of an ice storage air conditioner, explaining the electrical and cooling capacity transfer relationships between the various components within the ice storage air conditioner.

[0112] The model constraints in step S3 include human comfort boundary constraints, building cooling demand constraints, and ice storage air conditioning system operation constraints.

[0113] (1) Human comfort boundary constraints are set according to the following formula:

[0114] NET A (t)=37-(37-T A in (t)) / (0.68-0.0014RH A (t)+1 / (1.76+1.4(u m,s wind (t)) 2 ))

[0115] NET min ≤NET A (t)≤NET max

[0116] In the formula, NET A (t) represents the net effective temperature at time t, T A in (t) represents the set indoor temperature of the building, RH A (t) represents the indoor relative humidity at time t, u m,s wind (t) represents the fan speed of the indoor ice storage air conditioner, NET min and NET max These are the minimum and maximum values ​​of the net effective temperature, respectively.

[0117] (2) Building cooling demand constraints shall be set according to the following formula:

[0118] Q A,r LD (t)=Q A,r AC (t)+Q A,r IS,dis (t)

[0119] Q A,r AC (t)=COP AC ×(P A,r AC (t)-P A,r ch (t))

[0120] In the formula, Q A,rLD Q(t) represents the required cooling capacity of the room at time t. A,r AC (t) is the power (Q) that provides cooling capacity to the ice storage air conditioning chiller. A,r IS,dis (t) represents the cooling power supplied to the interior of the building in the scene when the ice storage tank of the ice storage air conditioner melts ice, COP. AC For ice storage air conditioning chillers, P A,r AC (t) represents the electrical power P of the ice storage air conditioning unit providing cooling to the interior of the building in the scene. A,r ch (t) is the electrical power that provides cooling capacity to the ice maker and ice storage tank for the ice storage air conditioner;

[0121] (3) The operating constraints of the ice storage air conditioning system include the capacity constraints of ice storage air conditioning participating in demand response, the working status constraints of ice storage air conditioning units, the operating constraints of ice storage air conditioning in the cold storage working state, the operating constraints of ice storage air conditioning in the ice melting working state, the operating constraints of the ice storage tank in the cold storage working state and the ice melting working state, and the operating constraints of ice storage air conditioning based on variable air volume control.

[0122] (3.1) As Figure 4 As shown in the figure, the working status of each component of the ice storage air conditioner and the transmission paths of electrical energy and cooling capacity are illustrated in the ice storage state. The operating constraints of the ice storage air conditioner in the ice storage state are set according to the following formula:

[0123] Q min AC ≤Q A,r AC (t)≤Q max AC

[0124] U A,r IS,ch (t)×Q min IS,ch ≤Q A,r IS,ch (t)≤U A,r IS,ch (t)×Q max IS,ch

[0125] Q A,r AC (t)=Q A,r LD (t)+Q A,r IS,ch (t)

[0126] Q A,r IS,dis (t)=0

[0127] C A,r IS (t)=C A,r IS (t-1) / (1-η IS,loss )+η IS,ch ×Q A,r IS,ch (t)×Δt

[0128] P A,r ch (t)+P A,r AC (t)=P A,r LD (t)

[0129] P A,r ch (t)=Q A,r IS,ch (t) / η EER IS

[0130] P A,r AC (t)=Q A,r AC (t) / η EER AC

[0131] In the formula, Q A,r AC (t) is the power (Q) that provides cooling capacity to the ice storage air conditioning chiller. min AC and Q max AC Q represents the minimum and maximum power output of the ice storage air conditioning unit, respectively. A,r IS,ch (t) represents the cooling capacity of the refrigeration mechanism under the ice storage tank operation state of the ice storage air conditioning system, Q. min IS,ch and Q max IS,ch U represents the minimum and maximum values ​​of the cooling capacity power of the refrigeration mechanism under the ice storage tank operation conditions of the ice storage air conditioner. A,r IS,ch (t) represents the operating state of the ice storage air conditioner during ice storage, Q A,r IS,dis (t) represents the power of cooling supplied by the ice storage air conditioning system when the ice storage tank is melting ice, Q A,r LD (t) represents the required cooling capacity of the room at time t, C. A,r IS (t) and C A,rIS (t-1) represent the cold storage capacity reserves of the ice storage tank in the ice storage air conditioning system at time t and time t-1, respectively, η IS,loss η represents the cooling capacity loss rate of the ice storage tank in an ice storage air conditioning system. IS,ch P represents the ice-making efficiency of an ice storage air conditioning system, where Δt is the time interval of a calculation step. A,r AC (t) represents the electrical power P of the ice storage air conditioning unit providing cooling to the interior of the building in the scene. A,r ch (t) represents the electrical power P that supplies cooling capacity to the ice maker in the ice storage air conditioner. A,r LD (t) represents the total power consumption of the ice storage air conditioner at time t, η EER IS and η EER AC These are the energy efficiency ratios of ice storage air conditioning ice makers and refrigeration units, respectively.

[0132] (3.2) As Figure 5 As shown in the figure, the working status of each component of the ice storage air conditioner and the transmission paths of electrical energy and cooling capacity are illustrated in the ice-melting state. The operating constraints of the ice storage air conditioner in the ice-melting state are set according to the following formula:

[0133] Q min AC ≤Q A,r AC (t)≤Q max AC

[0134] Q A,r AC (t)=COP AC ×P A,r AC (t)

[0135] U A,r IS,dis (t)×Q min IS,dis ≤Q A,r IS,dis (t)≤U A,r IS,dis (t)×Q max IS,dis

[0136] Q A,r AC (t)+Q A,r IS,dis (t)=Q A,r LD (t)

[0137] QA,r IS,ch (t)=0

[0138] C A,r IS (t)=C A,r IS (t-1) / (1-η IS,loss )-Q A,r IS,dis (t) / η IS,dis ×Δt

[0139] P A,r AC (t)=P A,r LD (t)

[0140] P A,r ch (t)=0

[0141] P A,r AC (t)=Q A,r AC (t) / η EER AC

[0142] In the formula, Q A,r AC (t) is the power (Q) that provides cooling capacity to the ice storage air conditioning chiller. min AC and Q max AC Q represents the minimum and maximum power output of the ice storage air conditioning unit, respectively. A,r IS,ch (t) represents the cooling capacity of the ice-making mechanism of the ice storage air conditioner in ice storage operation mode, Q. A,r IS,dis (t) represents the power of cooling supplied by the ice storage air conditioning system when the ice storage tank is melting ice, Q min IS,dis and Q max IS,dis These represent the minimum and maximum values ​​of the cooling capacity supplied by the ice storage tank of the ice storage air conditioner during ice melting operation, respectively.

[0143] (3.3) The operating constraints of the ice storage tank for ice storage air conditioning in both the cold storage and melting operation states shall be set according to the following formula:

[0144] C min IS ≤C A,r IS (t)≤C max IS

[0145] C A,r IS (0)=C A,r IS (T)=ε IS ×C max IS

[0146] C A,r IS (t)=C A,r IS (t-1) / (1-η IS,loss )+(η IS,ch ×Q A,r IS,ch (t)-Q A,r IS,dis (t) / η IS,dis )×Δt

[0147] In the formula, C A,r IS (t) and C A,r IS (t-1) represents the cold storage capacity of the ice storage tank in the ice storage air conditioning system at times t and t-1, C min IS and C max IS C represents the minimum and maximum values ​​of the cold storage capacity of the ice storage tank in an ice storage air conditioning system. A,r IS (0) and C A,r IS (T) represents the initial and final time values ​​of the ice storage capacity reserve of the ice storage air conditioning ice tank, respectively. ε IS η represents the initial cooling capacity reserve coefficient of the ice storage tank in an ice storage air conditioning system, where T is an optimization period. IS,loss η represents the cooling capacity loss rate of the ice storage tank in an ice storage air conditioning system. IS,ch Q represents the ice-making efficiency of an ice storage air conditioning unit. A,r IS,ch (t) represents the cooling capacity of the ice-making machine in the ice storage air conditioner during ice storage operation, Q. A,r IS,dis (t) represents the power of cooling supplied by the ice storage air conditioning system when the ice storage tank is melting ice, η IS,dis This represents the ice melting efficiency of the ice storage tank in the ice storage air conditioning system, where Δt is the time interval of one calculation step.

[0148] (3.4) The capacity constraints for ice storage air conditioning in demand response shall be set according to the following formula:

[0149] P A,r DR (t)≤P A,rLD (t)

[0150] In the formula, P A,r DR (t) represents the demand response capacity that the ice storage air conditioning system should provide at time t, P A,r LD (t) represents the power consumption of the ice storage air conditioner at time t;

[0151] (3.5) The operating status constraints of the ice storage air conditioning unit shall be set according to the following formula:

[0152] U A,r IS,ch (t)+U A,r IS,dis (t)≤1

[0153] In the formula, U A,r IS,ch (t) and U A,r IS,dis (t) represents the 0-1 state variables of the ice storage and melting states of the ice storage air conditioner, respectively;

[0154] (3.6) The operating constraints based on variable air volume control shall be set according to the following formula:

[0155] u min wind ≤u A,r wind (t)≤u max wind

[0156] Q down IS,ch ≤Q A,r IS,ch (t)-Q A,r IS,ch (t-1)≤Q up IS,ch

[0157] Q down IS,dis ≤Q A,r IS,dis (t)-Q A,r IS,dis (t-1)≤Q up IS,dis

[0158] Q down AC ≤Q A,r AC (t)-Q A,r AC (t-1)≤Q up AC

[0159] In the formula, u min wind and u max wind The minimum and maximum fan speeds provided by u for the indoor fan of the ice storage air conditioner are respectively set. A,r wind (t) represents the air velocity provided by the internal fan of the ice storage air conditioner at time t, Q down IS,ch and Q up IS,ch Q represents the minimum and maximum values ​​of the change in the ice storage power of the ice maker in ice storage air conditioning under ice storage operation. A,r IS,ch (t-1) and Q A,r IS,ch (t) represents the ice-making power of the ice storage air conditioner's ice maker at time t-1 and time t, respectively. down IS,dis and Q up IS,dis Q represents the minimum and maximum values ​​of the change in cooling power supplied to the ice storage tank during ice melting operation of the ice storage air conditioner. A,r IS,dis (t-1) and Q A,r IS,dis (t) represents the ice melting power of the ice storage tank in the ice storage air conditioning system at time t-1 and time t, respectively. down AC and Q up AC Q represents the minimum and maximum values ​​of the refrigeration power variation of the ice storage air conditioning unit. A,r AC (t-1) and Q A,r AC (t) represents the cooling power of the ice storage air conditioning unit at time t-1 and time t, respectively.

[0160] The ice storage air conditioning operation optimization model based on variable air volume control aims to minimize the operating cost of building ice storage air conditioning, including energy purchase cost, user comfort loss cost, and user participation demand response return.

[0161] In step S3, the objective function of the ice storage air conditioning operation optimization model based on variable air volume control is set according to the following formula:

[0162] min f=Σ(α×M AC t +β×M PMV t -γ×M DR t )

[0163] MAC t =(P A,r LD (t)+P A,r wind (t))×ζ e t ×Δt

[0164] M PMW t =(v PMV ) 2 ×ζ PMV t

[0165] M DR t =P A,r DR (t)×ζ DR t ×T DR

[0166] P A,r wind (t)=u A,r wind (t)×η EER wind

[0167] In the formula, min f is the objective function of the ice storage air conditioning operation optimization model, and M AC t v represents the total power consumption cost of the ice storage air conditioning system at time t, where Δt is the time interval of a calculation step. PMV For human comfort, M PMV t M represents the cost of user comfort loss. DR t P represents the reward for user participation in demand response. α, β, and γ are the weighting coefficients for the total power consumption cost of ice storage air conditioning, the cost of user comfort loss, and the reward for user participation in demand response, respectively, under multi-objective optimization conditions. A,r LD (t) represents the power consumption of the ice storage air conditioner at time t, P A,r wind (t) represents the power consumption of the internal fan of the ice storage air conditioner at time t, ζ e t Let ζ be the unit electricity cost parameter in the electricity market at time t. PMV t Let P be the unit cost of user comfort loss at time t. A,r DR (t) represents the demand response capacity that the ice storage air conditioning system should provide at time t, ζ DR tLet T be the reward received by a user for participating in demand response at time t. DR The duration of user participation in the demand response.

[0168] Ice storage air conditioning based on variable air volume control mainly consists of four components: a fan, a chiller, an ice maker, and an ice storage tank. The ice maker and ice storage tank can be considered equivalent to an ice storage tank that simultaneously consumes cooling and electricity for ice making and supplies cooling for ice melting. Its operation can be divided into two stages: ice making and cooling storage, and ice melting and cooling. Nighttime temperatures are lower than daytime temperatures, resulting in lower cooling load demand, which the chiller can independently meet. Simultaneously, electricity prices are lower at night. Making and storing ice at night and then melting it during the day reduces operating costs, as mathematically expressed below:

[0169] Q A,r AC (t)=COP AC ×P A,r AC (t)

[0170] C A,r IS (t)=C A,r IS (t-1) / (1-η IS,loss )+(η IS,ch ×Q A,r IS,ch (t)-Q A,r IS,dis (t) / η IS,dis )×Δt

[0171] In the formula, Q A,r AC (t) represents the power of the ice storage air conditioning unit to deliver cooling capacity into the building, C A,r IS (t) and C A,r IS (t-1) represent the cold storage capacity reserves of the ice storage tank in the ice storage air conditioning system at time t and time t-1, respectively, η IS,loss η represents the cooling capacity loss rate of the ice storage tank in an ice storage air conditioning system. IS,ch and η IS,dis Δt represents the ice-making efficiency of the ice storage air conditioning system and the ice-melting efficiency of the ice storage tank, respectively, and Δt represents the time interval of a calculation step.

[0172] The ice storage tank model for ice storage air conditioning is as follows:

[0173] C A,r IS (0)=C A,r IS (T)=ε IS ×C maxIS

[0174] In the formula, C A,r IS (0) and C A,r IS (T) represents the initial and final time values ​​of the ice storage capacity reserve of the ice storage air conditioning ice tank, respectively. ε IS This represents the initial cooling capacity reserve coefficient of the ice storage tank in an ice storage air conditioning system, where T is an optimization period.

[0175] The fan model for a variable air volume ice storage air conditioner is shown in the following equation:

[0176] P A,r wind (t)=u A,r wind (t)×η EER wind

[0177] In the formula, P A,r wind (t) represents the power consumption of the internal fan of the ice storage air conditioner, u A,r wind (t) represents the air velocity provided by the internal fan of the ice storage air conditioner, η EER wind This refers to the power consumption of the internal fan of an ice storage air conditioner at a unit wind speed.

[0178] The working states of ice storage air conditioning based on variable air volume control can be divided into ice storage state and ice melting state. In the ice storage working mode, the ice storage air conditioning chiller will provide cooling capacity to both the building and the ice maker. At this time, the power consumption of the ice storage air conditioning is the sum of the power consumption of the ice storage air conditioning chiller and the ice maker, as shown in the following formula:

[0179] Q A,r AC (t)=Q A,r LD (t)+Q A,r IS,ch (t)

[0180] Q A,r IS,dis (t)=0

[0181] C A,r IS (t)=C A,r IS (t-1) / (1-η IS,loss )+η IS,ch ×Q A,r IS,ch (t)×Δt

[0182] P A,rch (t)+P A,r AC (t)=P A,r LD (t)

[0183] P A,r ch (t)=Q A,r IS,ch (t) / η EER IS

[0184] P A,r AC (t)=Q A,r AC (t) / η EER AC

[0185] In the formula, Q A,r AC (t) represents the power of the ice storage air conditioning chiller to deliver cooling capacity into the building, Q. A,r IS,ch (t) represents the power value of the ice storage air conditioning chiller supplying cooling capacity to the ice maker, Q. A,r IS,dis (t) represents the power value of P, which supplies cooling capacity to the ice storage tank of the ice storage air conditioning system. A,r AC (t) and P A,r ch (t) represents the power consumption of the ice storage air conditioning chiller and the power consumption of the ice maker, respectively. A,r LD (t) represents the total power consumption of the ice storage air conditioner during the refrigeration process, and η represents the total power consumption of the ice storage air conditioner. EER IS and η EER AC These are the energy efficiency ratios of ice storage air conditioning chillers and ice storage tank ice makers, respectively.

[0186] In ice-melting mode, the ice storage air conditioning chiller and ice storage tank will simultaneously provide cooling to the building. At this time, the ice storage air conditioning ice maker no longer consumes electrical power to store cooling capacity, and the power consumption of the ice storage air conditioning is only the power consumption of the ice storage air conditioning chiller, as shown in the following formula:

[0187] Q A,r AC (t)+Q A,r IS,dis (t)=Q A,r LD (t)

[0188] Q A,r IS,ch (t)=0

[0189] C A,r IS (t)=C A,r IS (t-1) / (1-η IS,loss )-Q A,r IS,dis (t) / η IS,dis ×Δt

[0190] P A,r AC (t)=P A,r LD (t)

[0191] P A,r ch (t)=0

[0192] P A,r AC (t)=Q A,r AC (t) / η EER AC

[0193] In the formula, Q A,r AC (t) and Q A,r IS,dis (t) represents the power values ​​of the cooling capacity provided by the ice storage air conditioning refrigeration unit and the cooling capacity provided by the ice storage tank melting ice, respectively. A,r AC (t) and P A,r ch (t) represents the power consumption of the ice storage air conditioning chiller and the ice storage air conditioning ice maker, respectively. A,r LD (t) represents the total power consumption of the ice storage air conditioner during the refrigeration process, and η represents the total power consumption of the ice storage air conditioner. EER AC Energy efficiency ratio of ice storage air conditioning ice makers.

[0194] The scheduling results include the total operating cost of the ice storage air conditioning system, the operating status and power consumption of the internal fan of the ice storage air conditioning system, the operating status and power consumption of the ice storage air conditioning system, the cooling power curve of the ice storage air conditioning system, and the indoor temperature curve of the building.

[0195] This invention considers the uncertainties in demand response scenarios involving ice storage air conditioning. It generates a massive number of scenarios from historical urban building power consumption and urban environmental data, and then reduces these scenarios. Based on user comfort boundaries, the upper and lower boundaries of the building's set temperature curve are modified; and based on the variable air volume (VAV) control of ice storage air conditioning, operational constraints on its VAV control are added. Through a second-order equivalent thermal parameter model of the building, the building's cooling load demand curve and its upper and lower boundaries are obtained. Based on the building's cooling load demand curve and the intraday real-time electricity price curve, optimal scheduling of ice storage air conditioning based on VAV control is achieved when loads participate in demand response under typical scenarios. The VAV-based ice storage air conditioning operation scheduling method will further release the regulation potential of ice storage air conditioning, expand the power system's demand response load resource pool, and improve the grid's ability to balance supply and demand in response to the randomness and volatility of new energy output.

[0196] The above specific embodiments are only used to explain the present invention and are not intended to limit the present invention. Those skilled in the art can make various modifications and improvements without departing from the principles and core concepts of the present invention. Any equivalent substitutions, modifications, and similar solutions made based on the claims and description of the present invention are within the protection scope of the present invention.

Claims

1. A method for scheduling the operation of an ice storage air conditioning system based on variable air volume control, characterized in that, Includes the following steps: S1. Obtain historical statistical data on urban cooling load, then fit the set temperature curve inside the building, and generate typical load operation scenarios based on the historical statistical data of urban cooling load. S2. Constrain the building's internal temperature curve according to the preset human comfort boundary conditions to obtain the upper and lower boundary curves of the building's internal temperature curve, and then convert them into the building's cooling demand curve. S3. Construct model constraints based on the building's cooling demand curve, and then construct an ice storage air conditioning operation optimization model based on variable air volume control. S4. Input typical load operation scenarios into the ice storage air conditioning operation optimization model based on variable air volume control to obtain scheduling results; In step S3, the objective function of the ice storage air conditioning operation optimization model based on variable air volume control is set according to the following formula: min f=Σ(α×M AC t +β×M PMV t -γ×M DR t ) M AC t =(P A,r LD (t)+P A,r wind (t))×ζ e t ×Δt M PMW t =(in PMV ) 2 ×ζ PMV t M DR t =P A,r DR (t)×ζ DR t ×T DR In the formula, min f is the objective function of the ice storage air conditioning operation optimization model, and M AC t v represents the total power consumption cost of the ice storage air conditioning system at time t, where Δt is the time interval of a calculation step. PMV For human comfort, M PMV t M represents the cost of user comfort loss. DR t P represents the reward for user participation in demand response. α, β, and γ are the weighting coefficients for the total power consumption cost of ice storage air conditioning, the cost of user comfort loss, and the reward for user participation in demand response, respectively, under multi-objective optimization conditions. A,r LD (t) represents the power consumption of the ice storage air conditioner at time t, P A,r wind (t) represents the power consumption of the internal fan of the ice storage air conditioner at time t, ζ e t Let ζ be the unit electricity cost parameter in the electricity market at time t. PMV t Let P be the unit cost of user comfort loss at time t. A,r DR (t) represents the demand response capacity that the ice storage air conditioning system should provide at time t, ζ DR t Let T be the reward received by a user for participating in demand response at time t. DR The duration of user participation in the demand response.

2. The ice storage air conditioning operation scheduling method based on variable air volume control according to claim 1, characterized in that: The historical statistical data of urban cooling load in step S1 includes historical data of urban summer ambient temperature, historical data of urban building cooling power consumption, historical data of air conditioning load response capacity, and historical data of electricity market cost curves.

3. The ice storage air conditioning operation scheduling method based on variable air volume control according to claim 1, characterized in that: The temperature curve set inside the building in step S1 is a preset curve for the building's internal temperature in a typical load operation scenario, used to characterize the relationship between the building's indoor temperature and time. The upper and lower boundary curves of the temperature curve set inside the building in step S2 are specifically the highest upper boundary curve and the lowest lower boundary curve of temperature set according to the boundary conditions of human comfort, which are used to limit the allowable fluctuation range of indoor temperature over time. In step S2, the cooling demand curve of the building is a function curve of cooling power changing with time, calculated based on the upper and lower boundary curves of the set temperature curve inside the building.

4. The ice storage air conditioning operation scheduling method based on variable air volume control according to claim 1, characterized in that: In step S1, the typical load operation scenario is generated by generating a load operation scenario set through historical statistical data of urban cooling load, and then the typical load operation scenario is extracted from the load operation scenario set using the K-means clustering method.

5. The ice storage air conditioning operation scheduling method based on variable air volume control according to claim 1, characterized in that: The cooling demand curve of the building in step S2 is obtained by processing according to the following steps: 1) Substitute the preset human comfort boundary conditions into the human comfort model to obtain the upper and lower boundary curves of the set temperature curve inside the building. 2) The upper and lower boundary curves of the set temperature curve inside the building are used to constrain the second-order thermodynamic dynamic model of the building to obtain the cooling capacity required for the building to maintain the set temperature range at each time, thus forming the cooling demand curve of the building.

6. The ice storage air conditioning operation scheduling method based on variable air volume control according to claim 1, characterized in that: The model constraints in step S3 include human comfort boundary constraints, building cooling demand constraints, and ice storage air conditioning system operation constraints. (1) The human comfort boundary constraints are set according to the following formula: NET A (t)=37-(37-T A in (t)) / (0.68-0.0014RH A (t)+1 / (1.76+1.4(u m,s wind (t)) 2 )) NET min ≤NET A (t)≤NET max In the formula, NET A (t) represents the net effective temperature at time t, T A in (t) represents the set indoor temperature of the building, RH A (t) represents the indoor relative humidity at time t, u m,s wind (t) represents the fan speed of the indoor ice storage air conditioner, NET min and NET max These are the minimum and maximum values ​​of the net effective temperature, respectively. (2) The building cooling demand constraint is set according to the following formula: Q A,r LD (t)=Q A,r AC (t)+Q A,r IS,dis (t) Q A,r AC (t)=COP AC ×(P A,r AC (t)-P A,r ch (t)) In the formula, Q A,r LD Q(t) represents the required cooling capacity of the room at time t. A,r AC (t) is the power (Q) that provides cooling capacity to the ice storage air conditioning chiller. A,r IS,dis (t) represents the cooling power supplied to the interior of the building in the scene when the ice storage tank of the ice storage air conditioner melts ice, COP. AC For ice storage air conditioning chillers, P A,r AC (t) represents the electrical power P of the ice storage air conditioning unit providing cooling to the interior of the building in the scene. A,r ch (t) is the electrical power that provides cooling capacity to the ice maker and ice storage tank for the ice storage air conditioner; (3) The operating constraints of the ice storage air conditioning system include the operating constraints of the ice storage air conditioning system in the ice storage state, the operating constraints of the ice storage air conditioning system in the ice melting state, and the operating constraints of the ice storage tank of the ice storage air conditioning system in the cold storage working state and the ice melting working state. (3.1) The operating constraints of the ice storage air conditioner in ice storage mode are set according to the following formula: Q min AC ≤Q A,r AC (t)≤Q max AC U A,r IS,ch (t)×Q min IS,ch ≤Q A,r IS,ch (t)≤U A,r IS,ch (t)×Q max IS,ch Q A,r AC (t)=Q A,r LD (t)+Q A,r IS,ch (t) Q A,r IS,dis (t)=0 C A,r IS (t)=C A,r IS (t-1) / (1-th IS,loss )+η IS,ch ×Q A,r IS,ch (t)×Δt P A,r ch (t)+P A,r AC (t)=P A,r LD (t) P A,r ch (t)=Q A,r IS,ch (t) / η EER IS P A,r AC (t)=Q A,r AC (t) / η EER AC In the formula, Q A,r AC (t) is the power (Q) that provides cooling capacity to the ice storage air conditioning chiller. min AC and Q max AC Q represents the minimum and maximum power output of the ice storage air conditioning unit, respectively. A,r IS,ch (t) represents the cooling capacity of the refrigeration mechanism under the ice storage tank operation state of the ice storage air conditioning system, Q. min IS,ch and Q max IS,ch U represents the minimum and maximum values ​​of the cooling capacity power of the refrigeration mechanism under the ice storage tank operation conditions of the ice storage air conditioner. A,r IS,ch (t) represents the operating state of the ice storage air conditioner during ice storage, Q A,r IS,dis (t) represents the power of cooling supplied by the ice storage air conditioning system when the ice storage tank is melting ice, Q A,r LD (t) represents the required cooling capacity of the room at time t, C. A,r IS (t) and C A,r IS (t-1) represent the cold storage capacity reserves of the ice storage tank in the ice storage air conditioning system at time t and time t-1, respectively, η IS,loss η represents the cooling capacity loss rate of the ice storage tank in an ice storage air conditioning system. IS,ch P represents the ice-making efficiency of an ice storage air conditioning system, where Δt is the time interval of a calculation step. A,r AC (t) represents the electrical power P of the ice storage air conditioning unit providing cooling to the interior of the building in the scene. A,r ch (t) represents the electrical power P that supplies cooling capacity to the ice maker from the ice storage air conditioner. A,r LD (t) represents the total power consumption of the ice storage air conditioner at time t, η EER IS and η EER AC These are the energy efficiency ratios of ice storage air conditioning ice makers and refrigeration units, respectively. (3.2) The operating constraints of the ice storage air conditioner in the ice-melting state are set according to the following formula: Q min AC ≤Q A,r AC (t)≤Q max AC Q A,r AC (t)=COP AC ×P A,r AC (t) U A,r IS,dis (t)×Q min IS,dis ≤Q A,r IS,dis (t)≤U A,r IS,dis (t)×Q max IS,dis Q A,r AC (t)+Q A,r IS,dis (t)=Q A,r LD (t) Q A,r IS,ch (t)=0 C A,r IS (t)=C A,r IS (t-1) / (1-η IS,loss )-Q A,r IS,dis (t) / η IS,dis ×Δt P A,r AC (t)=P A,r LD (t) P A,r ch (t)=0 P A,r AC (t)=Q A,r AC (t) / η EER AC In the formula, Q A,r AC (t) is the power (Q) that provides cooling capacity to the ice storage air conditioning chiller. min AC and Q max AC Q represents the minimum and maximum power output of the ice storage air conditioning unit, respectively. A,r IS,ch (t) represents the cooling capacity of the ice-making mechanism of the ice storage air conditioner in ice storage operation mode, Q. A,r IS,dis (t) represents the power of cooling supplied by the ice storage air conditioning system when the ice storage tank is melting ice, Q min IS,dis and Q max IS,dis η represents the minimum and maximum power supplied by the ice storage tank of the ice storage air conditioner during ice melting operations, respectively. IS,dis This represents the ice melting efficiency of the ice storage tank in the ice storage air conditioning system, where Δt is the time interval of one calculation step. (3.3) The operating constraints of the ice storage tank for the ice storage air conditioning system under both the ice storage and ice melting working states are set according to the following formula: C min IS ≤C A,r IS (t)≤C max IS C A,r IS (0)=C A,r IS (T)=ε IS ×C max IS C A,r IS (t)=C A,r IS (t-1) / (1-th IS,loss )+(the IS,ch ×Q A,r IS,ch (t)-Q A,r IS,dis (t) / h IS,dis )×Δt In the formula, C A,r IS (t) and C A,r IS (t-1) represents the cold storage capacity of the ice storage tank in the ice storage air conditioning system at times t and t-1, C min IS and C max IS C represents the minimum and maximum values ​​of the cold storage capacity of the ice storage tank in an ice storage air conditioning system. A,r IS (0) and C A,r IS (T) represents the initial and final time values ​​of the ice storage capacity reserve of the ice storage air conditioning ice tank, respectively. ε IS η represents the initial cooling capacity reserve coefficient of the ice storage tank in an ice storage air conditioning system, where T is an optimization period. IS,loss η represents the cooling capacity loss rate of the ice storage tank in an ice storage air conditioning system. IS,ch Q represents the ice-making efficiency of an ice storage air conditioning unit. A,r IS,ch (t) represents the cooling capacity of the ice-making machine in the ice storage air conditioner during ice storage operation, Q. A,r IS,dis (t) represents the power of cooling supplied by the ice storage air conditioning system when the ice storage tank is melting ice, η IS,dis Δt represents the ice melting efficiency of the ice storage tank in the ice storage air conditioning system, where Δt is the time interval of a calculation step.

7. The ice storage air conditioning operation scheduling method based on variable air volume control according to claim 1, characterized in that: The scheduling results include the total operating cost of the ice storage air conditioner, the operating status and power consumption of the internal fan of the ice storage air conditioner, the operating status and power consumption of the ice storage air conditioner, the cooling power curve of the ice storage air conditioner, and the indoor temperature curve of the building.

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