Air source heat pump whole life cycle management method, system, medium and equipment

Abstract

The application relates to the technical field of intelligent management, and provides an air source heat pump full life cycle management method, system, medium and equipment, which comprises the following steps: acquiring evaporation pressure and condensation pressure, calculating evaporation temperature and condensation temperature through a temperature-pressure curve, calculating compressor heating capacity through a heating capacity fitting formula, and further calculating air source heat pump system heating capacity; calculating compressor current through a current fitting formula according to the evaporation temperature and the condensation temperature, and calculating the average value of the compressor current in a period of time; comparing the evaporation temperature and the condensation temperature with a safe operation boundary and a dynamic early warning threshold value to perform fault judgment; comparing the average current with a rated value and a maximum rated current to perform fault judgment; performing fault judgment based on the air source heat pump system heating capacity through a flow method and an estimation method; and recording the frequency of fault occurrence to evaluate the residual value of equipment. The application can help users optimize equipment maintenance strategies and reduce operation costs.

Description

Technical Field

[0001] The present invention belongs to the field of intelligent management technology, and in particular relates to a full life cycle management method, system, medium and equipment for an air source heat pump. Background Art

[0002] The statements in this section merely provide background information related to the present invention and do not necessarily constitute prior art.

[0003] The intelligent and efficient operation of air source heat pump systems depends on the coordination of the entire chain of "design-construction-control-operation and maintenance". However, the systemic problems exposed in current design ideas and engineering practices show that the disconnect between technological advancement and engineering feasibility has become a core bottleneck, resulting in the basic inability to implement intelligent construction and the problem of high investment and low returns.

[0004] (1) The real-time coupling mechanism of “user load-equipment status-environmental variables” has not been established, resulting in a conflict between energy efficiency goals and equipment life;

[0005] (2) The equipment life cycle management is superficial, based only on the countdown of the design life, without considering the dynamic evaluation of equipment performance degradation;

[0006] (3) Due to the mismatch between design parameters and operating parameters, the general design load is large, resulting in the widespread false labeling of equipment on the market. The equipment does not meet the nameplate parameters, and the cooling capacity / heating capacity and unit energy efficiency do not meet the design parameters. If the operating strategy is implemented according to the provided parameters, there will be a serious mismatch between demand and equipment, and the data provided by the manufacturer cannot be directly applied to modeling. Summary of the Invention

[0007] In order to solve the technical problems existing in the above-mentioned background technology, the present invention provides a full life cycle management method, system, medium and equipment for air source heat pumps. Through real-time calculation of multiple parameters (such as heating amount, current, etc.), the equipment status is dynamically monitored, which effectively solves the problem of false parameter labeling, and realizes accurate fault classification through multi-dimensional comparison (temperature threshold comparison and current monitoring, etc.). On this basis, the residual value of the equipment is dynamically evaluated, which can help users optimize equipment maintenance strategies and reduce operating costs.

[0008] In order to achieve the above object, the present invention adopts the following technical solutions:

[0009] A first aspect of the present invention provides a method for managing an air source heat pump throughout its life cycle, comprising:

[0010] Obtain the evaporation pressure and condensing pressure, and calculate the evaporation temperature and condensation temperature using the temperature-pressure curve. Calculate the compressor heating capacity based on the evaporation temperature and condensation temperature using the heating capacity fitting formula. Multiply the compressor heating capacity by the number of compressors and the heat transfer coefficient as the heating capacity of the air source heat pump system. Calculate the compressor current based on the evaporation temperature and condensation temperature using the current fitting formula, and average the compressor current over a period of time to obtain the average current.

[0011] Compare the evaporating temperature and condensing temperature with the safe operating boundary and dynamic warning threshold to make a fault diagnosis; compare the average current with the rated value and the maximum rated current to make a fault diagnosis; based on the heating capacity of the air source heat pump system, make a fault diagnosis through the flow method and estimation method; record the frequency of faults and evaluate the residual value of the equipment.

[0012] Furthermore, the steps of the flow method include: obtaining the mass flow rate of the unit, combining the change of the inlet and outlet water temperature difference to calculate the actual heating capacity of the unit; obtaining the number of compressors and the heat exchange coefficient, calculating and multiplying the product of the compressor heating capacity obtained by fitting to obtain the fitted heating capacity of the unit; calculating the ratio of the actual heating capacity of the computer unit to the fitted heating capacity to perform fault judgment.

[0013] Furthermore, the estimation method includes the following steps: obtaining the number of compressors and the heat transfer coefficient, calculating the product of the compressor heating capacity obtained by fitting, and obtaining the fitting heating capacity of the unit. ; and obtain the rated flow and estimated traffic , combined with the change of inlet and outlet water temperature difference , perform fault diagnosis: When Calculate the rated temperature difference when ;when , calculate the heat exchange temperature difference between the fluorine circuit and the water circuit. When the heat exchange temperature difference between the fluorine circuit and the water circuit is greater than the rated value, the heating is normal. The condensing temperature is used to qualitatively determine whether the unit has a fault. When season , then ,if If the value is greater than the rated threshold, the compressor or heat exchanger is considered to be faulty.

[0014] Furthermore, the safe operation boundary is determined according to a maximum condensing temperature limit line, a minimum condensing temperature limit line, a maximum evaporating temperature limit line, a minimum evaporating temperature limit line, a maximum exhaust temperature, a maximum compression ratio limit line and a minimum pressure difference limit line.

[0015] Furthermore, it also includes: calculating the compressor power through the power fitting formula according to the evaporating temperature and the condensing temperature; obtaining the input power of the air source heat pump system by calculating the compressor power × the number of compressors × the compressor power coefficient + the fan power × the number of fans + the auxiliary power; calculating the ratio of the heating amount of the air source heat pump system to the input power of the air source heat pump system to obtain the energy efficiency of the unit.

[0016] Furthermore, it also includes: calculating the input current of the air source heat pump system by calculating compressor current×the number of compressors×the compressor current coefficient+the fan current×the number of fans.

[0017] Furthermore, it also includes: obtaining the design thermal index and building area, calculating the design thermal load; based on the design thermal load, combined with the real-time indoor and outdoor temperatures, calculating the real-time heating load or real-time cooling load.

[0018] A second aspect of the present invention provides an air source heat pump full life cycle management system, comprising:

[0019] The simulation operation module is configured to: obtain the evaporation pressure and condensation pressure, and calculate the evaporation temperature and condensation temperature using the temperature-pressure curve; calculate the compressor heating capacity based on the evaporation temperature and condensation temperature using the heating capacity fitting formula, and multiply the compressor heating capacity by the number of compressors and the heat exchange coefficient as the heating capacity of the air source heat pump system; calculate the compressor current based on the evaporation temperature and condensation temperature using the current fitting formula, and calculate the average value of the compressor current over a period of time to obtain the average current;

[0020] The self-diagnosis module is configured to: compare the evaporation temperature and condensation temperature with the safe operation boundary and dynamic warning threshold to make a fault judgment; compare the average current with the rated value and the maximum rated current to make a fault judgment; make a fault judgment based on the heating amount of the air source heat pump system through the flow method and the estimation method; record the frequency of fault occurrence and evaluate the residual value of the equipment.

[0021] A third aspect of the present invention provides a computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements the steps in the above-mentioned method for managing the entire life cycle of an air source heat pump.

[0022] The fourth aspect of the present invention provides a computer device, comprising a computer-readable storage medium, a processor, and a computer program stored on the computer-readable storage medium and executable on the processor, wherein when the processor executes the program, the steps in the method for managing the entire life cycle of an air source heat pump as described above are implemented.

[0023] Compared with the prior art, the present invention has the following beneficial effects:

[0024] This invention dynamically monitors equipment status through real-time calculation of multiple parameters (such as heating capacity and current), effectively solving the problem of false parameter labeling. It also achieves accurate fault classification through multi-dimensional comparison (temperature threshold comparison and current monitoring, etc.), and dynamically evaluates the residual value of the equipment on this basis, helping users optimize equipment maintenance strategies and reduce operating costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The accompanying drawings, which constitute a part of the present invention, are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute improper limitations on the present invention.

[0026] Figure 1 This is a flow chart of a method for managing the entire life cycle of an air source heat pump according to the first embodiment of the present invention;

[0027] Figure 2 This is a flowchart of constructing a rough energy consumption model according to the first embodiment of the present invention;

[0028] Figure 3 This is a flow chart for constructing an accurate device model according to the first embodiment of the present invention;

[0029] Figure 4 This is a flow chart of determining whether a unit is normal according to the first embodiment of the present invention;

[0030] Figure 5 1 is a schematic diagram of the safe operating range of the compressor according to the first embodiment of the present invention;

[0031] Figure 6 Schematic diagram of dynamic warning threshold value of embodiment 1 of the present invention;

[0032] Figure 7 It is a structural diagram of a computer device according to the fourth embodiment of the present invention. DETAILED DESCRIPTION

[0033] To make the purpose, technical solutions and advantages of the embodiments of the present invention more clear, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention.

[0034] It should be noted that the following detailed descriptions are illustrative and intended to provide further explanation of the present invention. Unless otherwise specified, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the art to which the present invention belongs.

[0035] Example 1

[0036] This embodiment provides a full life cycle management method for an air source heat pump.

[0037] This embodiment provides a method for managing the entire life cycle of an air source heat pump. Figure 1 As shown, the following steps are included:

[0038] Step 1: Modeling in stages.

[0039] The principle of "fine modeling of core equipment and rough modeling of the environment" is adopted.

[0040] For uncontrollable demand parameters that cannot be adjusted, such as building heat transfer and water resistance, rough modeling is performed as operating strategy constraints. This allows the initial conditions of the operating strategy to be used without historical data or accurately measured variables. This allows the program to be relatively unified during the rough modeling phase, reducing deployment difficulty.

[0041] For adjustable equipment, such as air-source heat pumps, precise modeling is required. The unit's capacity and operating boundaries must be determined to ensure accuracy and prevent frequent adjustments during operation that could cause the fluorine system to oscillate beyond its limits, potentially damaging the equipment. This work can be accomplished by establishing a unified database for equipment from different manufacturers, which can be accessed during configuration to reduce deployment complexity. Non-standard equipment requires remodeling based on its performance to avoid mislabeling of equipment that could cause overall regulatory performance to shift.

[0042] Step 101: Obtain static parameters (unchangeable parameters provided by manufacturers, design institutes, etc.) and dynamic parameters (equipment status parameters, instrument detection parameters, etc.) through the data acquisition system.

[0043] Among them, static parameters include: thermal index in HVAC design , building area S; terminal design method in HVAC design; design indoor temperature in HVAC design and outdoor temperature ; Unit configuration, including the number of compressors and fans; refrigerant type; compressor brand and safe operating limit; compressor current parameters, fan current parameters; unit manufacturer's sample unit current calibration value as the initial value; unit manufacturer's sample input power parameters; compressor power, fan power and auxiliary power parameters; unit manufacturer's sample heating and cooling capacity parameters; compressor heating / cooling capacity / expansion valve opening parameters.

[0044] Among them, dynamic parameters include: operating data such as cooling and heating capacity, flow rate, room temperature, etc. of the air source heat pump system; and unit module modeling information, which is included in the joint calculation process.

[0045] Step 102: Figure 2 As shown in the figure, a rough energy consumption model is constructed based on the design institute parameters using building area and cooling and heating loads.

[0046] (1) Calculate the cooling / heating load of the building.

[0047] Apply the corresponding formula ,in, is the design heat load, is the design thermal index, S is the building area, and the design heat load of the air source heat pump system can be obtained.

[0048] (2) Based on the terminal design method in HVAC design, the model is distinguished by the cooling and heating types of the building to determine whether it is cooling or heating.

[0049] (3) It is not a cold or warm situation.

[0050] Using the formula , establish a rough energy consumption model and determine the target heat load. is the target heat load, is the design heat load, is the real-time outdoor temperature, is the target indoor temperature, is the design outdoor temperature, Design indoor temperature.

[0051] The building's target temperature and heat load are calibrated to calculate the heat load demand at different temperatures. This formula, based on the principle of heat transfer, reflects the relationship between temperature difference and heat load. In practical applications, by setting different target and outdoor temperature values, the corresponding heat load can be calculated, providing a reference for the operation of the air source heat pump system.

[0052] A multi-point calibration method is used to correct heat demand. Due to the numerous factors that affect heat load in actual operation, such as indoor and outdoor temperature fluctuations and changes in building heat loss, a single-point calculation cannot accurately reflect actual heat demand. The multi-point calibration method uses multiple measurements of temperature and heat load data under different operating conditions to establish a more accurate mathematical model, correcting the heat demand calculation results and improving accuracy.

[0053] After obtaining basic parameters such as building area, design outdoor temperature, design indoor temperature, and design thermal index, the system is divided into 21 intervals according to the calculated values ​​of outdoor temperature and indoor temperature and the deviation from the set values. A 20-point calibration is performed using the two-point method.

[0054] During the later operation, regular calibration is performed according to the outdoor temperature to establish the model ,in is the real-time heat load, is the target heat load, To calibrate the deviation value, the operating range is divided into multiple levels such as -16°C to 22°C according to the temperature. The linear result is calculated according to the calibration value based on the two-point linear method in each range. The two-point method is based on the principle of linear interpolation. Through two known temperature points and their corresponding heat load values, the heat load of other temperature points is inferred. After that, the corresponding heat demand is calculated based on the numerical value. Similarly, the target indoor temperature deviation value model is established. , the calibration interval is the same as the load, where For real-time indoor temperature, is the target indoor temperature, To calibrate the deviation value, the system is recalibrated every year based on historical data regression and the results are sent to the operation management department to provide data support for subsequent air source heat pump system operation control.

[0055] That is, according to the target indoor and outdoor temperatures, the indoor temperature target value and heat load are corrected; finally, the corrected and .

[0056] (4) It is a cold or warm situation.

[0057] There are differences between cooling load and heating load in many aspects. In the dominant heat transfer direction, cooling load is heat transfer from outdoor to indoor, while heating load is heat transfer from indoor to outdoor. In terms of the role of internal heat sources, the heat dissipation of personnel and equipment in the cooling load needs to be offset by refrigeration, which is a positive contribution; in the heating load, internal heat sources can reduce part of the heating load, which is a negative contribution. In terms of humidity influence, humidity is the key factor of cooling load, and the latent heat load of fresh air accounts for a large proportion; the heating load mainly focuses on temperature, and the latent heat load can be ignored. In terms of calculation method, the cooling load needs to adopt dynamic non-steady-state calculation, taking into account the heat storage delay and hourly radiation heat gain; the heating load can adopt steady-state or quasi-steady-state calculation. In terms of design parameters, the cooling load involves the outdoor calculated dry-bulb temperature and wet-bulb temperature, while the heating load only involves the outdoor calculated dry-bulb temperature.

[0058] The total cooling load can be decomposed into a variable part that changes with temperature and a fixed part that is independent of temperature. The real-time cooling load is calculated by the formula Calculate, where is the real-time cooling load, is the design cooling load, is the real-time outdoor temperature, For real-time indoor temperature, is the design outdoor temperature, For the design indoor temperature, For real-time outdoor humidity, For real-time indoor humidity, To design outdoor humidity, is the design indoor humidity. The variable proportion α is related to the outdoor temperature. It is related to the outdoor humidity, and α+β<1 is determined by multi-point calibration method. Under different outdoor temperature and humidity, α, The coefficients are different. Since cooling load is affected by many factors and difficult to calculate accurately, and there is a reserve load consideration, the room temperature correction coefficient and load deviation are not calculated. Generally, the number of units to be turned on is determined by determining a rough ratio to prevent inefficiency caused by selecting too many units. The water temperature is used to increase or decrease the load of the compressor to control the precise load.

[0059] The establishment and calculation ideas of the cooling demand module are similar to those of heating. Both require obtaining basic parameters, performing original calculations, multi-point calibration, water supply estimation, and load calculations. However, there are differences in the algorithms. In terms of cooling capacity calculation, the cooling load changes rapidly, energy consumption is highly uncertain, and it is greatly affected by user behavior. The amount of calculation required is greater. Rapid cooling is required in the early stage, and the load must be maintained subsequently. User behavior must also be monitored. Regarding equipment issues, when air source heat pumps are providing cooling, the spacing between surface coolers is affected by frost caused by heating in winter. The actual cooling capacity is less than the marked capacity, and the initial coefficient should be lower. In terms of the impact of flow distribution, the unit flow cannot be arbitrarily adjusted during cooling, otherwise the evaporation temperature will be too low, damaging the equipment. The restrictions need to be increased during modeling.

[0060] (5) Simulate combined heating / cooling operation.

[0061] (A) Calculation process.

[0062] First, the heat load and target water outlet temperature calculated by the heating / cooling load module are sent to the unit module.

[0063] Determine the unit's heating / cooling capacity based on the target outlet water temperature and outdoor temperature .

[0064] Then, based on the real-time heat load , calculate the heating / cooling capacity of the unit at this temperature , get the number of units turned on , determine the operation strategy;

[0065] According to the heat load, use the formula , calculate the theoretical flow rate required by the air source heat pump system, where is the mass flow rate of the air source heat pump system, Calculate the mass flow rate required to meet the demand for the air source heat pump system temperature difference .

[0066] Then, according to the number of units turned on, n, the flow rate of the air source heat pump system is compared. With unit flow , calculate the flow required to meet the demand and take the larger value for execution.

[0067] (B) The unit model data is compared with the data acquisition system and runs iteratively.

[0068] If the actual operation is consistent with the model, continue the iterative operation (A) and perform joint data operations.

[0069] If the actual operation is inconsistent with the model, the user will be prompted to perform multi-point calibration correction.

[0070] Each heating season and cooling season shall correct their respective coefficients Q 22 、T n22 , α, β, recalibrate 20 points using historical data.

[0071] Step 103: Figure 3 As shown, a relatively accurate equipment model is constructed based on the selected machine configuration and HVAC configuration.

[0072] (1) Determine the type of modeling machine and the number of internal core components, including the number of compressors, fans, etc.

[0073] (2) Solving the evaporation and condensation temperatures. Based on the refrigerant type, the established polynomial refrigerant model is retrieved and the polynomial coefficients (e.g., P0-P6) are sent to the edge end. The evaporation and condensation temperatures x and y are determined based on the evaporation and condensation pressures.

[0074] Linear fitting is performed based on the different refrigerants, and the temperature and pressure are compared using the polynomial method. This method is universal for mixed refrigerants within the operating range. The specific steps are as follows:

[0075] (A) Gauge pressure Pg is the pressure calculated with atmospheric pressure as zero pressure. The actual evaporation pressure x11 = the low pressure detected by the sensor + 1.01 bar, and the actual condensing pressure x12 = the high pressure detected by the sensor + 1.01 bar.

[0076] (B) Fitting the temperature-pressure curve based on the temperature-pressure comparison table (abbreviated as temperature-pressure table).

[0077] The R22 temperature and pressure curve was fitted based on the R22 (difluorochloromethane) temperature and pressure table shown in Table 1. KPA and BAR are the pressure units KPa (kilopascals) and bar (bar, kilograms), respectively.

[0078] Table 1. R22 temperature and pressure comparison table

[0079]

[0080] The formula for establishing the refrigerant temperature and pressure curve (polynomial refrigerant model) is: ;in, The corresponding is the absolute pressure of the refrigerant (actual evaporation pressure or actual condensation pressure), is the polynomial coefficient, n is the order, so according to different refrigerants, different coefficients can be filled in according to different refrigerants. When reducing the order, just fill in 0.

[0081] As shown in Table 2, coefficients for representative refrigerants are established.

[0082] Table 2. Coefficients of representative refrigerants

[0083]

[0084] This allows the establishment of high-order polynomials to calculate different temperature and pressure curves based on different refrigerant types, without the need for other tools and deployment at the edge.

[0085] (3) Modeling the safe operating range of the compressor. Modeling is done based on the compressor brand and safe operating boundary, and the model is sent to the edge end boundary. An early warning envelope interval is established, and the evaporation temperature x and condensation temperature y are used to determine whether it is normal.

[0086] According to the set maximum condensing temperature limit line, minimum condensing temperature limit line, maximum evaporating temperature limit line, minimum evaporating temperature limit line, maximum exhaust temperature and maximum compression ratio limit line, and minimum pressure difference limit line, the compressor operating range can be modeled and the compressor safe operating range can be constructed.

[0087] Taking a scroll compressor as an example, the compressor performance curve is divided into 8 segments, such as Figure 5 As shown. This divides the compressor operating range into multiple zones: A, B, C, D, E, F, G, H, and I. Zone A is enclosed by segments 2, 3, 4, 5, 6, 7, and 8. When the compressor operates continuously, it is in normal operation within this zone. Zone B, located below segment 3, is the half-decay zone of compressor efficiency. Zone C, located below segment 4, exhibits poor oil supply capacity, resulting in vibration and noise. Zone D, located to the left of segment 5, is prone to motor overload and lubricant dilution. Zone E, located above segment 6, is prone to motor overload and excessive pressure. Zone F, located above segment 7, is prone to motor overload and excessive pressure. Zone G, located above segment 1, exhibits excessively high compressor exhaust temperature and pressure ratio. Zone H, located to the left of segment 2, exhibits insufficient motor cooling and poor return oil cooling. Section I, defined by segments 1, 2, and 8, is a wet spray zone, and the compressor should not operate in this zone for extended periods. Based on the compressor's performance curve, it's possible to determine if the fluorine system is at risk of damage.

[0088] Based on the performance envelope curve of the compressor, it can be determined whether there is a risk of damage to the fluorine circuit system.

[0089] For example, for an air-source heat pump unit using a shell-and-tube heat exchanger, the ideal heat exchange temperature difference is 5°C. For a plate heat exchanger, the ideal heat exchange temperature difference is 2°C. During heating, the difference between the condensing temperature and the outlet water temperature should not exceed 60% of the ideal temperature difference for any extended period. If this value is exceeded, the heat exchanger needs cleaning. During summer cooling, to prevent freezing of the shell-and-tube heat exchanger, the difference between the evaporating temperature and the outlet water temperature should not exceed 7°C. Similarly, determine whether the compressor and fluorine circuit are functioning properly.

[0090] First, model the factory enclosure, such as Figure 5 As shown in the figure, the marked intervals are shown, where x is the evaporation temperature and y is the condensation temperature. A coordinate system is established based on the evaporation and condensation temperatures, and the safe operating boundary is determined by the calculated values.

[0091] As shown in Table 3, based on the safe operating range of the compressor, the compressor prompts, alarms, minor faults, and major faults are divided, and a dynamic early warning threshold is established within the safe operating range of the compressor. When the threshold is triggered, a corresponding alarm is issued, such as Figure 6 shown.

[0092] Table 3. Linear safe operation boundary table

[0093]

[0094] The calculated evaporation temperature and condensation temperature are compared with the safe operation boundary and dynamic warning threshold, and corresponding alarms are issued.

[0095] (4) Compressor performance modeling. Establish a heat / cooling polynomial model based on compressor performance. , sent to the edge end (P00-P03), and the polynomial heat transfer correction coefficient η is established ms , and sent to the edge end (P00-P03).

[0096] The heating capacity of the machine depends on the heating capacity of the compressor, so the curve of the compressor directly determines the heating capacity of the machine, and the heating capacity of the compressor can be judged by the current real-time evaporation temperature and condensation temperature.

[0097] The heating capacity fitting formula of the compressor is:

[0098]

[0099] in, Generates heat for the compressor; x is the evaporation temperature in degrees Celsius; y is the condensation temperature in degrees Celsius; p ij are the heating polynomial coefficients, i and j is a non-negative integer that satisfiesi + j ≤ n , generally speaking, i or i For variable frequency compressors, multiple curves are required to calculate the compressor's heat output. Two extreme operating conditions, 45rps and 90rps (or 120rps), need to be established, and the operating range should be between the two curves.

[0100] As shown in Table 4, the coefficients of representative compressors are established.

[0101] Table 4. Coefficients of representative compressors

[0102]

[0103] Similarly, a current polynomial model is established based on the compressor performance , sent to the edge end (P00-P03) to establish the polynomial current correction coefficient ε ms , sent to the edge end (P00-P03);

[0104] Establishing a cooling capacity polynomial model based on compressor performance (Cooling and heating are mutually exclusive, and are both marked as ), sent to the edge end (P00-P03) to establish the polynomial thermal correction coefficient η ms , sent to the edge end (P00-P03);

[0105] Developing a polynomial model of input power based on compressor performance , sent to the edge end (P00-P03) to establish the polynomial power correction coefficient , and sent to the edge end (P00-P03).

[0106] (5) Auxiliary equipment modeling.

[0107] For auxiliary fans, electric control systems, heating cables and other models, modeling is required to calculate the corresponding input power, where the fan input power is , the input power of the electric control system and heating cable is .

[0108] (6) Comprehensive unit modeling.

[0109] First, obtain the evaporation pressure and condensation pressure, and calculate the evaporation temperature and condensation temperature corresponding to the evaporation pressure and condensation pressure through the temperature fitting formula. x and y .

[0110] Then, according to the evaporation temperature x and condensation temperaturey , calculate the heating / cooling capacity of the compressor through the heating capacity fitting formula, power fitting formula and current fitting formula , compressor power , compressor current Equal value.

[0111] Then according to the unit heat exchange model , calculate the heating / cooling capacity of the air source heat pump system , where the heating / cooling capacity of the compressor is , the number of compressors in the unit is , the unit heat transfer coefficient is . With heat transfer coefficient (heat transfer efficiency ) as an example, the solution is: ,and , according to the actual operation of the heat pump, let , and then get the unit heat transfer coefficient and heat transfer efficiency ,in, The actual heating capacity of the machine. Calculate the heating capacity for the machine, is the number of compressors in the unit, The temperature difference between the inlet and outlet water of the unit is calculated as a polynomial based on the regression of the test points. As the performance coefficient compensation value, the regression calculation is performed based on the historical data to form a polynomial fitting surface. , are the polynomial coefficients.

[0112] Then according to the unit power model , calculate the input power of the air source heat pump system , where the compressor power is , the number of compressors is , the compressor power coefficient is , the fan power is , the number of fans is , the auxiliary power is .

[0113] According to the unit current model , calculate the air source heat pump system current ,in is the compressor current, is the number of compressors, is the compressor current coefficient, is the fan current, is the number of fans.

[0114] According to the current correction factor , judge the operating status of the compressor, and combine it with the opening of the expansion valve to determine whether the compressor is short of fluorine, overloaded, etc.

[0115] According to the heat transfer coefficient of the unit ,, determine whether the unit is falsely marked, calculate the correct heating / cooling capacity, and determine the aging coefficient based on this.

[0116] Then, calculate the heating capacity of the air source heat pump system / the input power of the air source heat pump system to obtain the energy efficiency of the unit. =Q mn / P mn , to determine whether the unit is optimal.

[0117] (8) Detection feedback.

[0118] In this embodiment, the coefficient correction refers to the correction of characteristic coefficients such as the evaporation temperature compensation value. , condensing temperature compensation value , heat transfer coefficient ( ), power coefficient ( )、Current coefficient( )、Energy Efficiency Coefficient( ) etc. During operation, historical data is used for iteration and recorded in the database as the basis for judging unit aging.

[0119] In this embodiment, the saturation temperatures corresponding to the evaporating pressure and the condensing pressure are first compared with the saturation temperatures corresponding to the calibrated evaporating pressure and the condensing pressure; when the deviation is large, the coefficient correction function is triggered, and when the deviation is within the range, the coefficient is not triggered to be used.

[0120] Specifically, obtain the simulated ambient temperature and simulated water outlet temperature When heating, the simulated ambient temperature , calculate the evaporation temperature compensation value , unit heat exchange efficiency Equivalent value; based on simulated water outlet temperature , calculate the condensation temperature compensation value In cooling, the evaporation temperature compensation value , condensing temperature compensation value .

[0121] Specifically, the polynomial correction coefficients are iterated according to the current feedback at runtime. ; During operation, the heat exchange coefficient of the unit is corrected according to the iterative polynomial based on the water temperature and flow feedback: During operation, the power coefficient of the unit is corrected according to the iterative polynomial feedback from the electricity meter: The highest order polynomial coefficients calculated from the regression Make a judgment, when When it is less than the set threshold, a reduced-order regression calculation is performed, and a more stable polynomial is selected for calculation to avoid overfitting.

[0122] Step 2: Based on the equipment configuration and target operating conditions, simulate the operation and propose operating parameters.

[0123] Step 3: Compare the established model with the actual operation and make a status judgment to determine whether it conforms to the model. If it does, the model is corrected using historical data based on the actual values ​​that conform to the model and the correction cycle.

[0124] like Figure 4 As shown, specifically including:

[0125] (1) Determine the number of compressors / fans based on the actual state of the machine; read the manufacturer's system enclosure parameters and compressor performance, heat pump parameter performance, etc.; perform polynomial fitting modeling, and calibrate the initial coefficients based on the manufacturer's performance parameters and also perform modeling.

[0126] (2) Generate the unit model, including evaporation and condensation temperature, compressor and unit conversion capacity, unit operating parameters, etc.

[0127] (3) Determine the target operating conditions (outdoor ambient temperature / water supply temperature / flow rate / indoor target temperature, etc.); based on the target operating conditions, decompose them into unit operating conditions (such as the flow rate of each unit, whether it is turned on, etc.); call the unit model to calculate the target operating parameters, and the results are formed into a data table;

[0128] (4) Iterate and run to the target operating condition; compare the evaporation and condensation temperatures to confirm that the x and y values ​​are correct and determine the operating boundaries to ensure that the model calculation is correct; obtain the outdoor air temperature, inlet and outlet water temperatures, and determine whether they are consistent with the model; if so, proceed to step (5); if not, proceed to step (8);

[0129] (5) Determine the operating current and input power, and further determine the parameters such as the expansion valve opening related to them, and determine whether the compressor pressure ratio is normal; obtain the operating current (unit) of the air source heat pump, the expansion valve opening, and the power consumption of the equipment, and determine whether they are consistent with the model; if so, proceed to step (6); if not, proceed to step (8);

[0130] (6) Verify the heating / cooling capacity of the air source heat pump and determine whether the capacity of the unit has declined; obtain the unit flow rate, inlet and outlet water temperature, intake and exhaust temperature, cooling and heating capacity, etc.; determine whether it is consistent with the model; if so, proceed to step (7); if not, proceed to step (8);

[0131] (7) Verify the energy efficiency of the unit and verify the degree of aging based on the data previously obtained by the data acquisition system; obtain the compressor operating time and determine whether it is consistent with the model. If so, proceed to step (9); if not, proceed to step (11).

[0132] (8) Determine whether it is within a reasonable range; if not, proceed to step (11); if it is within a reasonable range, determine whether it exceeds the threshold; if it exceeds the threshold, proceed to step (11); if it does not exceed the threshold, determine whether parameter iteration is required, if so, proceed to step (10); if not, proceed to step (9);

[0133] (9) Iterative operation;

[0134] (10) Using historical data, the relationship between the correction coefficient and the operating conditions is learned through machine learning; the correction coefficient is modeled so that the actual operating conditions are close to the normal value, and then return to step (2).

[0135] (11) Record the frequency of failures and assess the residual value of the equipment.

[0136] Among them, the judgment of the operating current in step (5) includes: taking the fixed-frequency unit as an example, after the fan is started, the current is detected, and the compressor working current is fitted according to the evaporation and condensation temperature of the compressor. The compressor current is averaged for detection, and the detection is performed once every 5 minutes to calculate the average current; judging whether it drops to the rated range within a period of time. When the average current of the compressor is higher than the rated value by 10% but lower than the maximum rated current of the compressor, it can be judged that the compressor is heavily loaded at this time. It can be judged that the compressor is abnormal at this time and needs to be shut down for maintenance. At this time, external reasons such as the expansion valve opening should be checked; judging whether the current is too small. When the average current of the compressor is lower than the rated value by 10%, it can be judged that the compressor load is light. At this time, the compressor should be checked for cross-flow.

[0137] When the fan blades become loose due to faults such as fan reversal or rolling keys, the fan operating current is less than the normal operating current. Therefore, by judging whether the torque drops during startup and whether the current is too small after startup, it is possible to determine whether the cooling fan is normal. At the same time, the fan operating time is recorded. When the operating time is close to the rated life of the fan, it is reminded to replace the fan in time. For variable frequency fans, in addition to the inverter to determine the stall fault, according to the square torque reduction characteristics of the fan water pump, there are , where the rated power at power frequency is P1, the rated speed at power frequency is n1, the output power after frequency conversion is P2, and the actual speed after frequency conversion is n2. If the calculated output power ratio is incorrect, it is determined that the fan is off-shaft or rotating in reverse.

[0138] In step (6), the capacity of the unit is determined by the flow method and the estimation method.

[0139] (A) The flow rate method refers to an air source heat pump system with a heat meter or flow meter. The flow rate has been measured. At this time, the heat meter and the actual temperature difference of the computer group have been determined. The compressor operation signal is used to determine whether the air source heat pump system is running. Taking a fixed frequency machine as an example, this embodiment uses a 10-minute delay as the delay time for all compressors to run:

[0140] according to , calculate the actual heating / cooling capacity of the i-th unit , judge the actual working status of each module machine at this time, where, is the mass flow rate of the i-th unit, is the inlet and outlet water temperature difference of the i-th unit, and i is the unit number.

[0141] according to , calculate the fitted heating / cooling capacity of the i-th unit, where n is the number of compressors, f(x,y) is the fitted heating / cooling capacity of the air source heat pump, is the heat transfer coefficient, x is the evaporation temperature in °C, y is the condensation temperature in °C, is the fitted heating / cooling capacity of the i-th unit, in kWh.

[0142] So there is , taking the dual system air source heat pump module as an example, when When the machine is working in a reasonable area, , at this time the machine's heating / cooling capacity is low, and you need to continue to observe the cause; when At this time, it can be judged that the heating / cooling capacity of the unit is far less than the rated value, but the compressor is working. At this time, it can be judged that one of the modules is not working. The compressor current can be combined to judge whether the machine compressor has a suction cup or fluorine path heat exchange problem. At this time, it can be determined that the unit is basically not outputting power and the compressor is not doing any work. Combined with the compressor current, it can be determined whether the machine compressor has a suction cup or fluorine circuit heat exchange problem.

[0143] The variable frequency machine needs to calculate the real-time heating capacity based on the speed and evaporation and condensation temperature. The temperature difference calculation is the same as that of the fixed frequency machine.

[0144] (B) Estimation method: When the air source heat pump system does not have detection elements such as heat and cold meters and flow meters, it is necessary to use the internal temperature and pressure detection of the unit to estimate the equipment performance and determine whether there is a problem with the machine.

[0145] The idea is not to check the actual heating / cooling capacity (the same below), calculate ,in is the fitting heating / cooling capacity (the same below), n is the number of compressors, is the heat transfer coefficient.

[0146] according to , then , using the hypothesis method, To estimate the flow rate, It is the temperature difference between the inlet and outlet water of the air source heat pump module, which can be used to determine two states.

[0147] (a) At this time, because the unit can be turned on normally, it means that the water flow detection switch is normal and the water flow is greater than the minimum water flow. This proves that the actual mass flow ,in is the rated flow rate, To estimate the flow rate (the same below), For the minimum flow, first according to , the temperature difference between the water inlet and outlet of the computer group, is the rated temperature difference (the same below).

[0148] when When ,in The heat exchange temperature difference between the fluorine circuit and the water circuit, is the condensation temperature, is the outlet water temperature, is the rated inlet and outlet water temperature difference, = is the inlet and outlet water temperature difference of the i-th unit, where i is the unit number. Based on the rated temperature difference of different heat exchangers (e.g., 5°C for shell and tube heat exchangers and 2°C for plate heat exchangers, see the component specifications for details), determine the current operating status. When the heat exchange temperature difference between the fluorine circuit and the water circuit is greater than the rated value, the machine is heating normally. Based on the condensing temperature Y, determine qualitatively whether there is a problem with the unit and, at the same time, increase the water flow rate of the air source heat pump module.

[0149] when When the temperature difference cannot be widened, the flow rate is unknown, so it is necessary to judge whether the flow rate increase is reasonable. , it can be deduced , using the hypothesis method, let , then: , substitute the numerical value for estimation. If the flow rate exceeds 40% of the rated flow rate due to pipeline resistance, it can be roughly considered abnormal. At this time, it is necessary to determine whether there is a compressor or heat exchanger failure. If the flow rate exceeds 80% of the rated flow rate, the compressor or heat exchanger should be considered to have a fault.

[0150] (b) , first according to , the temperature difference between the water inlet and outlet of the computer group, when When, and At this time, it is judged that the temperature difference is large and the flow estimation The valuation is too high. Need to calculate ,in The heat exchange temperature difference between the fluorine circuit and the water circuit, is the condensation temperature, is the outlet water temperature, The rated inlet and outlet water temperature difference. The operating status at this time is determined based on the rated temperature difference of different heat exchangers. When the heat exchanger temperature difference is greater than the rated value, the machine is heating normally. The condensing temperature can be used to qualitatively determine whether there is a problem with the unit. At the same time, it is recommended to increase the water flow rate of the air source heat pump module.

[0151] The variable frequency machine calculates heat through real-time speed and evaporation and condensation temperature. Other calculations are the same as those of the fixed frequency machine.

[0152] The flow method and the estimation method can both exist at the same time to simplify the corresponding calculations and thus determine the actual condition of the machine.

[0153] Step 4: Based on the operation feedback, modify the operation strategy, iterate the operation strategy table, and optimize the operation strategy.

[0154] Example 2

[0155] This embodiment provides an air source heat pump full life cycle management system, which specifically includes:

[0156] The simulation operation module is configured to: obtain the evaporation pressure and condensation pressure, and calculate the evaporation temperature and condensation temperature using the temperature-pressure curve; calculate the compressor heating capacity based on the evaporation temperature and condensation temperature using the heating capacity fitting formula, and multiply the compressor heating capacity by the number of compressors and the heat exchange coefficient as the heating capacity of the air source heat pump system; calculate the compressor current based on the evaporation temperature and condensation temperature using the current fitting formula, and calculate the average value of the compressor current over a period of time to obtain the average current;

[0157] The self-diagnosis module is configured to: compare the evaporation temperature and condensation temperature with the safe operation boundary and dynamic warning threshold to make a fault judgment; make a fault judgment based on the heating amount of the air source heat pump system through the flow method and estimation method; compare the average current with the rated value and the maximum rated current to make a fault judgment; record the frequency of fault occurrence and evaluate the residual value of the equipment.

[0158] It should be noted here that the various modules in this embodiment correspond one-to-one to the various steps in Example 1, and the specific implementation processes are the same, which will not be repeated here.

[0159] Example 3

[0160] This embodiment provides a computer-readable storage medium having a computer program stored thereon. When the program is executed by a processor, the steps of the air source heat pump full life cycle management method as described in the first embodiment above are implemented.

[0161] Example 4

[0162] This embodiment provides a computer device, such as Figure 7 As shown, the system includes a computer-readable storage medium 1003, a processor 1001, a communication interface 1002, and a computer program stored on the computer-readable storage medium 1003 and executable on the processor 1001. The processor 1001, the communication interface 1002, and the computer-readable storage medium 1003 may be connected via a bus or other means. The communication interface 1002 is used to receive and send data, and when the processor 1001 executes the program, the steps of the air source heat pump life cycle management method described in the first embodiment are implemented.

[0163] The foregoing description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Those skilled in the art will readily appreciate that various modifications and variations of the present invention are possible. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention shall be included within the scope of protection of the present invention.

Claims

1. A full life cycle management method for an air source heat pump, characterized in that: include: Obtain the evaporation pressure and condensation pressure, and calculate the evaporation temperature and condensation temperature using the temperature-pressure curve. Calculate the compressor heat capacity based on the evaporation temperature and condensation temperature using the heating rate fitting formula. Multiply the compressor heat capacity by the number of compressors and the heat exchange coefficient as the heating rate of the air source heat pump system. According to the evaporation temperature and condensation temperature, the compressor current is calculated using the current fitting formula, and the average value of the compressor current over a period of time is calculated to obtain the average current; Compare the evaporation temperature and condensation temperature with the safe operation boundary and dynamic warning threshold to determine faults; compare the average current with the rated value and maximum rated current to determine faults; and use flow rate and estimation methods based on the heating capacity of the air source heat pump system to determine faults. Record the frequency of failures and assess the residual value of equipment; The estimation method includes the following steps: obtaining the number of compressors and the heat transfer coefficient, calculating the product of the compressor heating capacity obtained by fitting, and obtaining the fitting heating capacity of the unit. ; and obtain the rated flow and estimated traffic , combined with the change of inlet and outlet water temperature difference , perform fault diagnosis: When Calculate the rated temperature difference when ;when , calculate the heat exchange temperature difference between the fluorine circuit and the water circuit. When the heat exchange temperature difference between the fluorine circuit and the water circuit is greater than the rated value, the heating is normal. The condensing temperature is used to qualitatively determine whether the unit has a fault. When season , then ,if If the value is greater than the rated threshold, the compressor or heat exchanger is considered to be faulty.

2. The air source heat pump full life cycle management method according to claim 1, characterized in that: The flow method includes the following steps: obtaining the mass flow of the unit, and calculating the actual heating capacity of the unit in combination with the change in the inlet and outlet water temperature difference; obtaining the number of compressors and the heat transfer coefficient, and calculating the product of the calculated and fitted compressor heating capacity to obtain the fitted heating capacity of the unit; and calculating the ratio of the actual heating capacity of the unit to the fitted heating capacity to perform fault diagnosis.

3. The air source heat pump full life cycle management method according to claim 1, characterized in that: The safe operation boundary is determined according to a maximum condensing temperature limit line, a minimum condensing temperature limit line, a maximum evaporating temperature limit line, a minimum evaporating temperature limit line, a maximum exhaust temperature, a maximum compression ratio limit line and a minimum pressure difference limit line.

4. The air source heat pump full life cycle management method according to claim 1, characterized in that: Also includes: According to the evaporation temperature and condensation temperature, the compressor power is calculated using the power fitting formula; The input power of the air source heat pump system is obtained by calculating the compressor power × the number of compressors × the compressor power coefficient + the fan power × the number of fans + the auxiliary power; the energy efficiency of the unit is obtained by calculating the ratio of the heating capacity of the air source heat pump system to the input power of the air source heat pump system.

5. The air source heat pump full life cycle management method according to claim 1, characterized in that: Also includes: The input current of the air source heat pump system is calculated by calculating the compressor current × the number of compressors × the compressor current coefficient + the fan current × the number of fans.

6. The air source heat pump full life cycle management method according to claim 1, characterized in that: Also includes: Obtain design thermal index and building area, and calculate design heat load; Calculates the real-time heating load or cooling load based on the design heating load and the real-time indoor and outdoor temperatures.

7. An air source heat pump full life cycle management system, characterized in that: include: The simulation operation module is configured to: obtain the evaporation pressure and condensation pressure, calculate the evaporation temperature and condensation temperature through the temperature-pressure curve; calculate the compressor heat capacity based on the evaporation temperature and condensation temperature using the heating fitting formula, and use the product of the compressor heat capacity, the number of compressors, and the heat exchange coefficient as the heating capacity of the air source heat pump system; According to the evaporation temperature and condensation temperature, the compressor current is calculated using the current fitting formula, and the average value of the compressor current over a period of time is calculated to obtain the average current; The self-diagnosis module is configured to: compare the evaporation temperature and condensation temperature with the safe operation boundary and dynamic warning threshold to determine faults; compare the average current with the rated value and maximum rated current to determine faults; and determine faults based on the heating capacity of the air source heat pump system using flow method and estimation method; Record the frequency of failures and assess the residual value of equipment; The estimation method includes the following steps: obtaining the number of compressors and the heat transfer coefficient, calculating the product of the compressor heating capacity obtained by fitting, and obtaining the fitting heating capacity of the unit. ; and obtain the rated flow and estimated traffic , combined with the change of inlet and outlet water temperature difference , perform fault diagnosis: When Calculate the rated temperature difference when ;when , calculate the heat exchange temperature difference between the fluorine circuit and the water circuit. When the heat exchange temperature difference between the fluorine circuit and the water circuit is greater than the rated value, the heating is normal. The condensing temperature is used to qualitatively determine whether the unit has a fault. When season , then ,if If the value is greater than the rated threshold, the compressor or heat exchanger is considered to be faulty.

8. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the program is executed by a processor, the steps in the air source heat pump full life cycle management method as described in any one of claims 1 to 6 are implemented.

9. A computer device comprising a computer-readable storage medium, a processor, and a computer program stored on the computer-readable storage medium and executable on the processor, wherein: When the processor executes the program, the steps of the air source heat pump full life cycle management method according to any one of claims 1 to 6 are implemented.

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