A method and system for optimizing condensation heat exchange process of a heat pump type water heating device

Abstract

This invention discloses a method and system for optimizing the condensation heat exchange process of a heat pump water heater, specifically relating to the field of heat pump control technology, and is used to solve the problem of terminal heat exchange attenuation. This invention generates a condensation heat exchange process frame sequence and constructs condensation heat exchange state units by collecting refrigerant-side state data, water-side heat exchange data, and actuator operation data. Based on condensation heat exchange boundary rules, it identifies the high-efficiency heating zone, heat exchange attenuation zone, and protection approach zone, determines the attenuation state at the end of the condensation heat exchange, and generates phased adjustment paths for the compressor, electronic expansion valve, and circulating water pump. Finally, it updates the boundary rules based on control effect feedback, achieving early intervention and closed-loop optimization of the condensation heat exchange process, improving heating efficiency and operational stability.

Description

Technical Field

[0001] This invention relates to the field of heat pump control technology, and more specifically, to a method and system for optimizing the condensation heat exchange process of a heat pump water heater. Background Technology

[0002] In the field of heat pump water heating equipment control, heat pump water heating equipment has been widely used in scenarios such as domestic hot water, centralized water supply for hotels and apartments, hot water supply for school dormitories, and commercial constant temperature water supply. These devices typically use computer programs to coordinate the operation of components such as compressors, condensers, electronic expansion valves, evaporators, circulating water pumps, and water tanks. The high-temperature, high-pressure refrigerant discharged from the compressor exchanges heat with the circulating water on the water side in the condenser, thus achieving heating. Existing technical solutions mostly use target outlet water temperature, water tank temperature, condensing pressure, or exhaust temperature as the main control criteria. By adjusting the compressor operating frequency, the opening degree of the electronic expansion valve, and the speed of the circulating water pump, hot water heating, pressure protection, and energy consumption control are achieved. These solutions generally focus on achieving the target water temperature and high-pressure protection response. Their technical implementation involves the compression heat pump cycle, monitoring of the condensing heat exchange process, and the coordinated control of the actuators.

[0003] However, when heat pump water heaters are operating near the target water temperature or during high-temperature water supply, the inlet water temperature and tank temperature gradually increase, the heat exchange temperature difference between the two sides of the condenser decreases, and the condensing pressure, exhaust temperature, and compressor input power tend to rise continuously. Meanwhile, the effective temperature rise on the water side and the heat exchange per unit power consumption may gradually decrease. Existing control methods usually still increase the frequency based on the water temperature difference, or only trigger frequency reduction protection when the condensing pressure and exhaust temperature approach the protection threshold. They lack early identification of the process boundary of condensing heat exchange from the high-efficiency heating zone to the heat exchange decay zone and the protection approach zone. This will cause the equipment to continue to maintain a high compressor output in the later stage of heating, and the opening of the electronic expansion valve and the circulation water flow will be difficult to match the actual heat exchange state in time. This will result in the condensing pressure climbing, the heat exchange efficiency decreasing, the energy consumption increasing, and the protection action becoming more frequent, affecting the stability of hot water supply and the economic efficiency of equipment operation. Summary of the Invention

[0004] In order to overcome the above-mentioned defects of the prior art, the present invention provides a method and system for optimizing the condensation heat exchange process of a heat pump water heater, so as to solve the problem of heat exchange attenuation in the final stage in the above-mentioned background art.

[0005] To achieve the above objectives, the present invention provides the following technical solution:

[0006] A method for optimizing the condensation heat exchange process of a heat pump water heater includes:

[0007] Collect refrigerant-side status data, water-side heat exchange data, and actuator operation data during the heating operation of heat pump water heaters, and align them with a unified sampling period to generate a condensation heat exchange process frame sequence.

[0008] Based on the frame sequence of the condensation heat exchange process, the characteristics of heat release change on the refrigerant side, heat absorption response on the water side, adjustment of the actuator and energy consumption change are extracted to construct a condensation heat exchange state unit.

[0009] The condensation heat exchange state unit is matched with the condensation heat exchange boundary rule to determine whether the current condensation heat exchange process is in the high-efficiency heating zone, the heat exchange attenuation zone, or the protection approach zone. The attenuation state of the final stage of condensation heat exchange is identified when the condensation pressure continues to rise, the effective temperature rise on the water side decreases, and the heat exchange per unit power consumption decreases.

[0010] Based on the current condensation heat exchange process interval and the attenuation state of the final stage of condensation heat exchange, a phased adjustment path is generated. In the high-efficiency heating zone, the compressor heating output is maintained. In the heat exchange attenuation zone, the compressor frequency is limited and the opening of the electronic expansion valve and the circulating water flow are corrected in conjunction. In the protection approach zone, frequency reduction and water-side heat exchange enhancement control are implemented.

[0011] The system collects data on the condensing pressure drop after control, the water-side temperature rise recovery, energy consumption changes, and protection action triggering status. It then generates a control effect feedback, updates the condensing heat exchange boundary rules, and outputs the optimization results of the condensing heat exchange process.

[0012] In a preferred embodiment, the refrigerant-side status data includes condensing pressure, exhaust temperature, condenser refrigerant inlet temperature, condenser refrigerant outlet temperature, and refrigerant-side temperature difference.

[0013] The water-side heat exchange data includes water-side inlet temperature, water-side outlet temperature, circulating water flow rate, water-side temperature rise, and water-side temperature rise change.

[0014] The operating data of the actuator includes compressor operating frequency, electronic expansion valve opening degree, circulating water pump speed, compressor input power, and protection status flags.

[0015] In a preferred embodiment, the step of aligning and generating the condensation heat transfer process frame sequence according to a uniform sampling period includes:

[0016] Using the compressor operating cycle or condensing pressure sampling cycle as a unified sampling cycle, timestamp correction is performed on the refrigerant-side state data, water-side heat exchange data, and actuator operating data;

[0017] Data within the same sampling period are grouped into single frames according to the acquisition time, and frame status flags are set for missing data, abrupt data, and protection-triggered data.

[0018] Arrange the data of each single frame in the order of sampling time to generate a condensation heat exchange process frame sequence containing refrigerant side field, water side field, actuator field, energy consumption field and frame status marker.

[0019] In a preferred embodiment, the construction of the condensation heat exchange state unit includes:

[0020] Using multiple consecutive condensation heat exchange process frames as analysis windows, the following parameters are extracted: condensation pressure change rate, exhaust temperature change rate, refrigerant side temperature difference change, water side effective temperature rise change rate, circulating water flow response, compressor frequency change, electronic expansion valve opening change, and compressor input power change.

[0021] The heat exchange per unit power consumption is generated based on the water-side temperature rise, circulating water flow rate, and compressor input power.

[0022] The above data are linked together in the same analysis window to generate a condensation heat exchange state unit that includes fields for refrigerant side heat release change, water side heat absorption response, actuator adjustment, and energy consumption change.

[0023] In a preferred embodiment, the condensation heat transfer boundary rules include pressure ramp-up boundary, temperature rise decay boundary, heat transfer per unit power consumption boundary, and protection margin boundary.

[0024] When the rate of change of condensing pressure does not exceed the pressure ramp-up boundary, the rate of change of effective temperature rise on the water side is not lower than the temperature rise decay boundary, and the heat exchange per unit power consumption meets the heat exchange per unit power consumption boundary, the current condensing heat exchange process is divided into the high-efficiency heating zone.

[0025] If the protection approach zone conditions are not met, when the rate of change of condensing pressure exceeds the pressure ramp-up boundary, the rate of change of effective temperature rise on the water side is lower than the temperature rise decay boundary, or the heat transfer per unit power consumption is lower than the heat transfer per unit power consumption boundary, the current condensing heat transfer process is divided into the heat transfer decay zone.

[0026] When the condensing pressure, exhaust temperature, or compressor input power is close to the corresponding protection threshold and the protection margin is lower than the protection margin boundary, the current condensing heat exchange process is classified as the protection approach zone.

[0027] In a preferred embodiment, identifying the attenuation state at the end of the condensation heat exchange includes:

[0028] If, within multiple consecutive analysis windows, the rate of change of condensing pressure is consistently higher than the pressure ramp-up boundary, the rate of change of effective temperature rise on the water side is consistently lower than the temperature rise decay boundary, and the heat exchange per unit power consumption decreases continuously, then it is determined that the current condensing heat exchange process has entered the decay state of the final stage of condensing heat exchange.

[0029] Based on the effective temperature rise recovery range of the water side before and after the circulation water flow rate adjustment, the attenuation state of the final stage of the condensation heat exchange is categorized. When the effective temperature rise recovery range of the water side is lower than the preset recovery range after the circulation water flow rate increases, it is categorized as a refrigerant-side heat release-limited type attenuation. When the effective temperature rise recovery range of the water side reaches the preset recovery range after the circulation water flow rate increases, it is categorized as a water-side heat absorption-insufficient type attenuation.

[0030] In a preferred embodiment, generating the phased adjustment path includes:

[0031] Based on the current interval of the condensation heat exchange process and the type of attenuation state at the end of the condensation heat exchange, a high-efficiency heating section, an attenuation suppression section, and a protection and prevention section are generated.

[0032] During the high-efficiency heating stage, the compressor maintains its current heating output and keeps the electronic expansion valve opening and circulating water flow rate stable.

[0033] In the attenuation suppression section, the compressor frequency increment is limited, and the electronic expansion valve opening correction amount or circulating water flow rate adjustment amount is generated according to the attenuation of the last stage with limited heat release on the refrigerant side or the attenuation of the last stage with insufficient heat absorption on the water side.

[0034] The protection and prevention section generates compressor frequency reduction, electronic expansion valve limit correction, and circulating water pump speed increase.

[0035] In a preferred embodiment, the step of performing frequency reduction and water-side heat transfer enhancement control in the protection approach zone includes:

[0036] The protection margin is generated based on the difference between the condensing pressure, exhaust temperature, and compressor input power and the corresponding protection threshold.

[0037] When the protection margin is lower than the preset protection margin boundary, the compressor is prohibited from continuing to increase its frequency, and protection and prevention control commands are output in the order of compressor frequency reduction, electronic expansion valve opening correction, and circulating water pump speed increase.

[0038] If the controlled condensing pressure does not reach the preset drop condition, the compressor frequency will continue to be reduced while the circulating water flow rate is increased until the current condensing heat exchange process exits the protection approach zone.

[0039] In a preferred embodiment, generating control effect feedback and updating condensation heat transfer boundary rules includes:

[0040] A control effect feedback is generated based on the condensation pressure drop before and after the execution of the control command, the water side temperature rise recovery, the heat exchange recovery per unit power consumption, and the protection action trigger status.

[0041] When the condensing pressure does not drop or the heat exchange per unit power consumption does not recover, tighten the pressure ramp-up boundary, the heat exchange per unit power consumption boundary, and the stage switching conditions.

[0042] When the water-side temperature rise recovers and no protection action is triggered, maintain or relax the corresponding temperature rise attenuation boundary and protection margin boundary.

[0043] Write the updated condensation heat exchange boundary rules into the boundary rule library for the next heating operation cycle.

[0044] A system for optimizing the condensation heat exchange process of a heat pump water heater, used to implement the aforementioned method for optimizing the condensation heat exchange process of a heat pump water heater, comprising:

[0045] The data acquisition module is used to collect refrigerant-side status data, water-side heat exchange data, and actuator operation data during the heating operation of heat pump water heaters, and generate a condensation heat exchange process frame sequence by aligning them according to a unified sampling period.

[0046] The frame sequence generation module is used to extract the characteristics of heat release change on the refrigerant side, heat absorption response on the water side, adjustment of the actuator and energy consumption change based on the frame sequence of the condensation heat exchange process, and to construct a condensation heat exchange state unit.

[0047] The state construction module is used to match the condensation heat exchange state unit with the condensation heat exchange boundary rules, determine whether the current condensation heat exchange process is in the high-efficiency heating zone, the heat exchange attenuation zone or the protection approach zone, and identify the attenuation state of the final stage of condensation heat exchange when the condensation pressure continues to rise, the effective temperature rise on the water side attenuates and the heat exchange per unit power consumption decreases.

[0048] The attenuation identification module is used to generate a phased adjustment path based on the current interval of the condensation heat exchange process and the attenuation state of the end of the condensation heat exchange. In the high-efficiency heating zone, it maintains the compressor heating output, in the heat exchange attenuation zone, it limits the compressor frequency increase and links to correct the opening of the electronic expansion valve and the circulating water flow, and in the protection approach zone, it performs frequency reduction and water-side heat exchange enhancement control.

[0049] The adjustment and control module is used to collect data on the condensing pressure drop status, water side temperature rise recovery status, energy consumption change status, and protection action trigger status after control, generate control effect feedback, update condensing heat exchange boundary rules, and output the optimization results of the condensing heat exchange process.

[0050] The technical effects and advantages of this invention are as follows:

[0051] This invention achieves continuous sensing, process zoning, and early intervention of the condensation heat exchange state during the heating operation of heat pump water heaters by constructing a closed-loop optimization mechanism that includes a condensation heat exchange process frame sequence, condensation heat exchange state units, and a final-stage attenuation identification and phased adjustment path. The system integrates refrigerant-side state data, water-side heat exchange data, and actuator operation data to identify the final-stage attenuation state of condensation heat exchange, characterized by a continuous rise in condensation pressure, a decrease in effective water-side temperature rise, and a drop in heat exchange per unit power consumption. It can determine the trend of condensation heat exchange transitioning from the high-efficiency heating zone to the heat exchange attenuation zone or the protection approach zone before high-pressure protection or exhaust temperature protection is triggered.

[0052] Based on this, control actions such as electronic expansion valve opening correction, compressor frequency increase limitation, compressor frequency decrease, and circulating water flow regulation are generated according to the refrigerant-side heat release-limited terminal attenuation and water-side insufficient heat absorption-limited terminal attenuation. This enables coordinated regulation among the compressor, electronic expansion valve, and circulating water pump, reducing high-pressure inefficient operation, ineffective frequency increase, and frequent protection shutdowns in the later stage of temperature rise. The control effect feedback provides feedback on condensing pressure drop, water-side temperature rise recovery, energy consumption changes, and protection action trigger status, and updates the condensing heat exchange boundary rules, enabling the equipment to adapt to heat exchanger attenuation, water load changes, and operating environment changes, thereby improving condensing heat exchange efficiency, operational stability, and heating energy efficiency. Attached Figure Description

[0053] Figure 1 This is a flowchart of an optimization method for the condensation heat exchange process of a heat pump water heater according to the present invention.

[0054] Figure 2 This is a schematic diagram of the structure of an optimized condensation heat exchange process system for a heat pump water heater according to the present invention. Detailed Implementation

[0055] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0056] Example 1: As Figure 1 As shown, an optimization method for the condensation heat exchange process of a heat pump water heater includes the following:

[0057] In this embodiment, an air source heat pump water heater is used as an example for illustration. The heat pump water heater includes a compressor, a condenser, an electronic expansion valve, an evaporator, a circulating water pump, a water tank, and a controller. The condenser is used to exchange heat between the high-temperature and high-pressure refrigerant discharged by the compressor and the circulating water on the water side, thereby heating the water in the water tank or water supply circuit to the target temperature.

[0058] During the heating operation of the equipment, as the water inlet temperature and water tank temperature gradually increase, the condensing pressure, exhaust temperature and compressor input power may rise simultaneously, while the water side temperature rise and heat exchange per unit power consumption may gradually decrease. Especially when approaching the target outlet water temperature or during the high-temperature water supply stage, the condensing heat exchange is prone to change from a state of efficient heating to a state of heat exchange attenuation.

[0059] This embodiment identifies the end-of-line decay state during the condensation heat exchange process by collecting refrigerant-side status data, water-side heat exchange data, and actuator operation data. Before the high-pressure protection or exhaust temperature protection is triggered, the compressor operating frequency, electronic expansion valve opening, and circulating water pump speed are optimized and controlled in stages.

[0060] It should be noted that the controller includes at least a data access unit, a frame sequence generation unit, a state unit construction unit, a boundary rule matching unit, an adjustment path generation unit, an execution control unit, and a feedback update unit;

[0061] The data access unit receives refrigerant-side status data, water-side heat exchange data, and actuator operation data. The frame sequence generation unit aligns the data according to a uniform sampling period and generates a condensation heat exchange process frame sequence. The status unit construction unit extracts refrigerant-side heat release changes, water-side heat absorption responses, actuator adjustment, and energy consumption change characteristics from the condensation heat exchange process frame sequence and generates a condensation heat exchange status unit. The boundary rule matching unit matches the condensation heat exchange status unit with the condensation heat exchange boundary rules to determine the current condensation heat exchange process interval and identify the condensation heat exchange terminal attenuation state. The adjustment path generation unit generates a phased adjustment path based on the interval and terminal attenuation type. The execution control unit outputs corresponding control commands to the compressor, electronic expansion valve, and circulating water pump. The feedback update unit generates a control effect feedback based on the controlled condensation pressure drop status, water-side temperature rise recovery status, energy consumption change status, and protection action trigger status, and updates the condensation heat exchange boundary rules.

[0062] Collect refrigerant-side status data, water-side heat exchange data, and actuator operation data during the heating operation of a heat pump water heater. Generate a condensation heat exchange process frame sequence aligned with a unified sampling period. Specific implementation includes:

[0063] In this embodiment, when the heat pump water heater is in heating operation, the controller synchronously collects refrigerant-side status data, water-side heat exchange data, and actuator operation data, and organizes the above data into a condensation heat exchange process frame sequence to characterize the condensation heat exchange process. The refrigerant-side status data is used to reflect the heat release of the refrigerant in the condenser and the high-pressure side operation status. The water-side heat exchange data is used to reflect the heat absorption status of the water flowing through the condenser. The actuator operation data is used to reflect the regulation status of the compressor, electronic expansion valve, and circulating water pump on the condensation heat exchange process.

[0064] All three types of data are collected based on the operating time of the heat pump water heater's own controller to avoid the same condensation heat exchange state being incorrectly split due to inconsistent sampling times of different sensors or control components.

[0065] Specifically, the refrigerant-side status data includes condensing pressure, exhaust temperature, condenser refrigerant inlet temperature, condenser refrigerant outlet temperature, and refrigerant-side temperature difference. The condensing pressure can be collected by a pressure detection unit installed on the high-pressure pipeline on the refrigerant side of the condenser, which is used to characterize the pressure state of the refrigerant during the condensation and heat release process.

[0066] The exhaust temperature can be collected by a temperature detection unit installed on the compressor exhaust pipe to reflect the state of the high-temperature refrigerant discharged by the compressor;

[0067] The refrigerant inlet temperature of the condenser is the temperature of the refrigerant before it enters the condenser, and the refrigerant outlet temperature of the condenser is the temperature of the refrigerant after it flows out of the condenser. The two are obtained by temperature detection units installed on the refrigerant inlet pipe and the refrigerant outlet pipe of the condenser, respectively.

[0068] The refrigerant-side temperature difference is the temperature difference between the refrigerant inlet temperature and the refrigerant outlet temperature of the condenser, used to reflect the degree of heat release change of the refrigerant after passing through the condenser.

[0069] The water-side heat exchange data includes water-side inlet temperature, water-side outlet temperature, circulating water flow rate, water-side temperature rise, and water-side temperature rise change. The water-side inlet temperature is the temperature of the water before it enters the condenser water-side heat exchange channel, and the water-side outlet temperature is the temperature of the water after it flows out of the condenser water-side heat exchange channel. Both are obtained by temperature detection units installed at the condenser water-side inlet and water-side outlet, respectively.

[0070] The circulating water flow rate can be obtained from the flow detection unit on the water-side circulating pipeline or the operating feedback data of the circulating water pump; the water-side temperature rise is the increase in the water-side outlet temperature relative to the water-side inlet temperature, which is used to reflect the temperature change of the water side after absorbing heat from the refrigerant during the current sampling period.

[0071] The change in water-side temperature rise is the magnitude of the change in water-side temperature rise in the current sampling period relative to the water-side temperature rise in the previous effective sampling period. It is used to determine whether the water-side heat absorption effect has increased, decreased, or tended to stabilize.

[0072] The operating data of the actuator includes compressor operating frequency, electronic expansion valve opening, circulating water pump speed, compressor input power and protection status flags. Among them, the compressor operating frequency is fed back by the compressor drive control unit and is used to characterize the degree of adjustment of the compressor to the refrigerant circulation volume and exhaust state.

[0073] The opening degree of the electronic expansion valve is fed back by the electronic expansion valve control unit, which is used to characterize the degree of regulation of the refrigerant flow state by the throttling component;

[0074] The speed of the circulating water pump is fed back by the circulating water pump drive unit to characterize the water-side flow regulation status;

[0075] The compressor input power can be fed back by the power detection unit of the electronic control board or the compressor drive module to characterize the electrical power consumed in the current heating operation;

[0076] The protection status flag is generated by the equipment controller based on the trigger status of high pressure protection, exhaust temperature protection, compressor overload protection, and abnormal water flow protection, and is used to distinguish normal operation data from protection action-related data.

[0077] When generating the condensation heat exchange process frame sequence, a unified sampling period is first determined. This unified sampling period can be either the compressor operating cycle or the condensation pressure sampling cycle. When the equipment controller refreshes the compressor operating frequency, electronic expansion valve opening, and circulating water pump speed according to the compressor operating cycle, the compressor operating cycle can be used as the unified sampling period.

[0078] When the condensing pressure sampling period can reflect the condensing pressure rise process more promptly, and the equipment controller can obtain other data feedback within this period, the condensing pressure sampling period can be used as a unified sampling period. The unified sampling period should be kept consistent during the same heating operation to ensure that each condensing heat exchange process frame formed subsequently has a comparable time interval.

[0079] During the timestamp correction process, the controller converts the original acquisition time of refrigerant side status data, water side heat exchange data and actuator operation data to the same operating time reference. For data with multiple acquisition values ​​within the same unified sampling period, the valid acquisition value closest to the end time of the sampling period is selected as the data of the corresponding field of that period.

[0080] For data that is not returned in time within the same unified sampling period, the data of the same field in the previous valid sampling period is called to temporarily fill in the missing data, and a missing data mark is set at the same time so that the field can be identified as the missing data rather than the real synchronously collected data in the subsequent status judgment. This can avoid the entire frame of data being directly discarded due to short-term delay of a single sensor or communication jitter.

[0081] During the single-frame data merging process, the condensing pressure, exhaust temperature, condenser refrigerant inlet temperature, condenser refrigerant outlet temperature, refrigerant side temperature difference, water-side inlet temperature, water-side outlet temperature, circulating water flow rate, water-side temperature rise, water-side temperature rise change, compressor operating frequency, electronic expansion valve opening, circulating water pump speed, compressor input power, and protection status flag are merged into one frame of data after time stamp correction within the same unified sampling period. This single frame of data is used to describe the condensing heat exchange status of the heat pump water heater within one sampling period. Its fields are divided into refrigerant side fields, water side fields, actuator fields, energy consumption fields, and frame status flags according to the data meaning. Among them, the refrigerant side fields store condensing pressure, exhaust temperature, condenser refrigerant inlet temperature, condenser refrigerant outlet temperature, and refrigerant side temperature difference.

[0082] The water-side fields store the water-side inlet temperature, water-side outlet temperature, circulating water flow rate, water-side temperature rise, and water-side temperature rise change.

[0083] The Execution Components field stores the compressor operating frequency, electronic expansion valve opening, circulating water pump speed, and protection status flags, while the Energy Consumption field stores the compressor input power.

[0084] When setting frame status flags, missing data, mutation data and protection trigger data are marked separately. Missing data refers to data that was not received in the current unified sampling period and was supplemented with data from the previous valid sampling period.

[0085] Abrupt data refers to data in which the current field changes beyond the allowable range of the device relative to the previous valid sampling period, or data whose operating logic is inconsistent with that of adjacent fields. For example, the compressor input power increases abnormally instantaneously while the compressor operating frequency remains unchanged, or the circulating water flow rate suddenly drops sharply while the circulating water pump speed remains unchanged.

[0086] Protection trigger data refers to data that has been triggered or is in the pre-trigger confirmation process of high pressure protection, exhaust temperature protection, compressor overload protection or water flow abnormal protection. By setting frame status flags, it is possible to identify whether the current frame is a valid frame, a complete frame, an abnormal frame or a protection-related frame when constructing the condensing heat exchange state unit, thereby improving the reliability of the condensing heat exchange process judgment.

[0087] Finally, the controller arranges the data of each single frame according to the sampling time sequence to form a condensation heat exchange process frame sequence. The condensation heat exchange process frame sequence is not a historical record of a single parameter, but a data sequence composed of refrigerant-side fields, water-side fields, actuator fields, energy consumption fields, and frame status flags in multiple consecutive sampling periods. Through this condensation heat exchange process frame sequence, the temporal relationship between changes in condensation pressure, exhaust temperature, water-side temperature rise, circulating water flow rate, compressor operating frequency, electronic expansion valve opening, circulating water pump speed, and compressor input power can be continuously reflected, providing data for extracting the characteristics of refrigerant-side heat release, water-side heat absorption response, actuator adjustment, and energy consumption changes.

[0088] Based on the frame sequence of the condensation heat exchange process, the characteristics of refrigerant-side heat release change, water-side heat absorption response, actuator adjustment, and energy consumption change are extracted to construct a condensation heat exchange state unit. Specific implementation includes:

[0089] After obtaining the condensation heat exchange process frame sequence, the controller uses multiple consecutive condensation heat exchange process frames as an analysis window, performs correlation processing on the refrigerant side field, water side field, actuator field and energy consumption field in the window, extracts the characteristics of refrigerant side heat release change, water side heat absorption response, actuator adjustment and energy consumption change, and constructs condensation heat exchange state unit.

[0090] The analysis window consists of multiple condensation heat exchange process frames arranged continuously according to the sampling time. The window length can be preset by the controller according to the equipment sampling cycle and the response speed of the condensation heat exchange process.

[0091] In specific settings, the analysis window length is determined based on the response lag time of condensing pressure, water-side temperature rise, and circulating water flow rate during normal heating of the equipment, ensuring that an analysis window can cover at least one state change process after adjustment of the actuator. The controller can combine two or more consecutive effective condensing heat exchange process frames into an analysis window and update it forward with one or more sampling periods as the rolling step size. The number of consecutive windows used to determine continuous rise, continuous fall, and continuous decline is a configurable parameter of the controller. This number of consecutive windows should be able to exclude accidental changes caused by single sensor fluctuations or short-term water disturbances. When the number of effective frames in a consecutive window is insufficient, the controller delays the identification of the final attenuation state until an effective condensing heat exchange process frame that meets the judgment requirements is obtained.

[0092] During the same heating operation, the analysis window is updated by scrolling forward according to the sampling time, so that each condensing heat exchange state unit corresponds to a continuous running segment. For condensing heat exchange process frames with missing data markers, abrupt data markers, or protection trigger markers, the controller does not delete them directly, but determines whether they participate in feature extraction based on the frame status markers.

[0093] When a field is used to temporarily fill in data, the field is only used to maintain the continuity of the window and is not used as the main basis for judging the attenuation of the final stage of condensation heat exchange.

[0094] When a frame is marked as a mutation and its authenticity cannot be confirmed by the trend of previous and subsequent frames, the frame is marked as a low-confidence frame when calculating the change trend, in order to avoid misjudgment of the condensation heat exchange state unit due to single-point anomalies.

[0095] When extracting the heat release change characteristics of the refrigerant side, the controller reads the condensing pressure, exhaust temperature and refrigerant side temperature difference from the refrigerant side field in the analysis window, and generates the condensing pressure change rate, exhaust temperature change rate and refrigerant side temperature difference change amount according to the changes in the start frame, end frame and intermediate consecutive frames of the analysis window. The condensing pressure change rate is used to characterize the degree to which the condensing pressure rises, falls or remains stable over time in the analysis window. It can be determined by comparing the condensing pressure difference between the effective frames before and after in the analysis window and combining the corresponding sampling time interval.

[0096] The exhaust temperature change rate is used to characterize the trend of compressor exhaust temperature change within the analysis window, and its acquisition method is the same as that of condensing pressure change rate.

[0097] The change in refrigerant temperature difference is used to characterize the range of change in the difference between the refrigerant inlet temperature and the refrigerant outlet temperature of the condenser within the analysis window, and is used to determine whether the heat release state of the refrigerant after passing through the condenser is weakened, enhanced or abnormally fluctuating.

[0098] Through the above processing, the refrigerant-side heat release change field includes at least the condensing pressure change rate, the exhaust temperature change rate, and the refrigerant-side temperature difference change.

[0099] When extracting the water-side heat absorption response characteristics, the controller reads the water-side inlet temperature, water-side outlet temperature, circulating water flow rate, water-side temperature rise, and water-side temperature rise change from the water-side fields in the analysis window, and further determines the water-side effective temperature rise change rate and circulating water flow response. The water-side effective temperature rise refers to the water-side temperature rise result used to characterize the actual water-side heat absorption effect in the current window after removing missing data markers, abrupt data markers, and protection trigger markers that cause interference to the water-side temperature rise.

[0100] When there is a short-term missing water-side inlet temperature or water-side outlet temperature in the analysis window, the controller prioritizes using adjacent valid frames to confirm the water-side temperature rise trend, avoiding directly using the supplemented data as the basis for the effective temperature rise change. The water-side effective temperature rise change rate is used to characterize the degree to which the water-side effective temperature rise increases, decreases, or remains stable over time in the analysis window. It is determined by comparing the water-side effective temperature rise changes of previous and subsequent valid frames in the analysis window and combining the sampling time interval.

[0101] The circulating water flow response is used to characterize the magnitude and direction of change of circulating water flow after the adjustment of the actuator. For example, whether the circulating water flow increases after the speed of the circulating water pump is increased, and whether the effective temperature rise on the water side recovers after the circulating water flow increases. Through the above processing, the water-side heat absorption response field includes at least the rate of change of effective temperature rise on the water side and the circulating water flow response, and can further retain the water-side inlet temperature, water-side outlet temperature, water-side temperature rise and water-side temperature rise change as auxiliary judgment fields.

[0102] When extracting the adjustment features of the actuator, the controller reads the compressor operating frequency, electronic expansion valve opening and circulating water pump speed from the actuator field in the analysis window, and generates the compressor frequency change and electronic expansion valve opening change. The compressor frequency change is used to characterize the compressor's frequency increase, frequency decrease or maintenance state in the analysis window, which can be determined by comparing the compressor operating frequency of the start and end valid frames of the analysis window.

[0103] The change in the opening of the electronic expansion valve is used to characterize the opening, closing or stable state of the electronic expansion valve within the analysis window. It can be determined by comparing the change in the opening of the electronic expansion valve before and after within the analysis window. In this embodiment, the circulating water pump speed can be used together with the circulating water flow response to determine whether the water-side adjustment is effective. That is, when the circulating water pump speed is adjusted but the circulating water flow does not change accordingly, it indicates that the water-side execution response is insufficient.

[0104] When the circulating water flow rate and the effective temperature rise on the water side recover synchronously after the speed of the circulating water pump is adjusted, it indicates that the heat absorption response on the water side has been improved.

[0105] When extracting energy consumption change characteristics, the controller reads the compressor input power from the energy consumption field and generates the compressor input power change amount. The compressor input power change amount is used to characterize the change in the compressor power consumption status within the analysis window. It can be determined by comparing the compressor input power of the effective frames before and after within the analysis window. When the compressor input power continues to increase, but the effective temperature rise on the water side does not increase synchronously or the heat exchange per unit power consumption decreases, it indicates that the current condensation heat exchange process may have a high pressure and low efficiency trend.

[0106] When the effective temperature rise on the water side increases synchronously with the increase in compressor input power and the condensing pressure does not rise abnormally, it indicates that the current condensing heat exchange is still in a relatively effective temperature rise state.

[0107] When generating heat exchange per unit power consumption, the controller processes the water-side temperature rise, circulating water flow rate, and compressor input power within the same analysis window. Specifically, it first determines the change in water volume through the condenser water-side heat exchange channel within the analysis window based on the circulating water flow rate, then determines the heat absorption effect obtained by the water side within the analysis window based on the water-side temperature rise. Subsequently, it correlates this heat absorption effect with the compressor input power within the same analysis window to obtain the water-side heat exchange capacity corresponding to the unit input power, i.e., heat exchange per unit power consumption. The heat exchange per unit power consumption is used to measure the actual heat exchange effect obtained by the water side under the current compressor power consumption level. An increase in its value indicates that the water-side heat absorption effect is enhanced under the same power consumption conditions, while a decrease in its value indicates that the water-side heat absorption effect is weakened under the same power consumption conditions. For physical property parameters required for heat exchange calculations such as the specific heat of water, the equipment controller can use preset constants or call them according to the equipment calibration parameters, and they are not considered as operating data that needs to be dynamically collected.

[0108] After completing the above feature extraction, the controller correlates the condensing pressure change rate, exhaust temperature change rate, refrigerant side temperature difference change, water side effective temperature rise change rate, circulating water flow response, compressor frequency change, electronic expansion valve opening change, compressor input power change, and heat exchange per unit power consumption obtained within the same analysis window to generate a condensing heat exchange state unit. The condensing heat exchange state unit is not a single sensor data, but a data unit that uniformly describes the refrigerant side heat release change, water side heat absorption response, actuator adjustment, and energy consumption change with the same analysis window as the time boundary.

[0109] The condensation heat exchange state unit includes at least a refrigerant-side heat release change field, a water-side heat absorption response field, an actuator adjustment field, and an energy consumption change field. The refrigerant-side heat release change field stores the condensation pressure change rate, the exhaust temperature change rate, and the refrigerant-side temperature difference change.

[0110] The water-side heat absorption response field stores the effective temperature rise rate and the circulating water flow response.

[0111] The actuator adjustment field stores the compressor frequency change and the electronic expansion valve opening change, and is associated with the circulating water pump speed change;

[0112] The energy consumption change field stores the change in compressor input power and the heat exchange per unit of power consumption. Through this condensation heat exchange status unit, the controller can determine whether the condensation pressure continues to rise, whether the water-side heat absorption weakens, whether the adjustment of the actuator matches the heat exchange response, and whether the energy input is converted into effective water-side heat exchange. This provides data for matching condensation heat exchange boundary rules, dividing the high-efficiency heating zone, the heat exchange decay zone, or the protection approach zone.

[0113] The condensation heat transfer state unit is matched with the condensation heat transfer boundary rule to determine whether the current condensation heat transfer process is in the high-efficiency heating zone, the heat transfer attenuation zone, or the protection approach zone. The attenuation state of the final stage of condensation heat transfer is identified when the condensation pressure continues to rise, the effective temperature rise on the water side decreases, and the heat transfer per unit power consumption decreases. Specific implementation includes:

[0114] After obtaining the condensing heat exchange state unit, the controller matches the condensing pressure change rate, water-side effective temperature rise change rate, unit power heat exchange, exhaust temperature, compressor input power, and related protection status flags in the condensing heat exchange state unit with the pre-set condensing heat exchange boundary rules to determine whether the current condensing heat exchange process is in the high-efficiency heating zone, heat exchange attenuation zone, or protection approach zone. The condensing heat exchange boundary rules are used to describe the allowable condensing pressure rise trend, water-side heat absorption attenuation trend, unit power heat exchange capacity change trend, and operating margin before protection action of the heat pump water heater under different heating stages. It is not a single fixed temperature control value, but a set of rules composed of pressure rise boundary, temperature rise attenuation boundary, unit power heat exchange boundary, and protection margin boundary.

[0115] The above boundary rules can be determined by the equipment factory calibration data, the compressor's allowable operating range, the electronic expansion valve's adjustment range, the circulating water pump's flow adjustment range, and historical heating operation records, and can be corrected after the subsequent control effect feedback is generated. However, safety protection thresholds such as the high pressure protection threshold, the exhaust temperature protection threshold, and the compressor input power protection threshold cannot be arbitrarily relaxed due to this correction.

[0116] When initializing the condensing heat exchange boundary rules, the controller first reads the compressor's allowable operating pressure range, allowable exhaust temperature range, allowable compressor input power range, allowable electronic expansion valve opening range, and allowable circulating water pump speed range to form equipment operating constraints. Then, it calls the historical operating records or factory test records of the equipment during normal heating and temperature rise, and selects the operating segments that do not trigger protection actions, have stable condensing pressure changes, stable water-side temperature rise, and do not continuously decrease the heat exchange per unit power consumption as stable operating samples.

[0117] Subsequently, based on the distribution range of condensing pressure change rate, water-side effective temperature rise change rate, and heat transfer per unit power consumption in the stable operation samples, the pressure ramp-up boundary, temperature rise decay boundary, and heat transfer per unit power consumption boundary are determined; at the same time, based on the allowable advance distance between condensing pressure, exhaust temperature, and compressor input power and the corresponding safety protection threshold, the protection margin boundary is determined.

[0118] All of the above boundary rules are stored in the boundary rule library and are associated with the equipment model, condenser specifications, compressor specifications, circulating water pump specifications, and heating operation mode, so that the corresponding boundary rules can be called in different equipment or different operation modes.

[0119] The pressure ramp-up boundary is used to determine whether the rate of change of condensing pressure has exceeded the allowable increase under the current heating stage. Specifically, the controller compares the rate of change of condensing pressure in the current analysis window with the pressure ramp-up boundary. When the rate of change of condensing pressure does not exceed the pressure ramp-up boundary, it means that the current condensing pressure is still within an acceptable range of increase or stability.

[0120] When the rate of change of condensing pressure exceeds the pressure ramp-up boundary, it indicates that the condensing pressure is ramping up at a relatively rapid pace, and the condensing heat exchange process may begin to shift from a high-efficiency heat exchange state to a high-pressure, low-efficiency state. The temperature rise decay boundary is used to determine whether the effective temperature rise rate of change on the water side has fallen below the allowable range. When the effective temperature rise rate of change on the water side is not lower than the temperature rise decay boundary, it indicates that the heat absorption effect on the water side remains stable or improves.

[0121] When the effective temperature rise rate of the water side is lower than the temperature rise decay boundary, it indicates that the effective temperature rise of the water side decays within the same analysis window or continuous analysis window, indicating that the effective heat obtained by the water side from the condenser is insufficient. The unit power consumption heat exchange boundary is used to determine whether the water side heat exchange capacity corresponding to the unit input power meets the current operating requirements. When the unit power consumption heat exchange meets the unit power consumption heat exchange boundary, it indicates that the compressor input power can be effectively converted into water side heat exchange effect.

[0122] When the heat exchange per unit power consumption is lower than the heat exchange per unit power consumption boundary, it indicates that the equipment has a trend of increased energy consumption but decreased effective heat exchange benefits.

[0123] The protection margin boundary is used to determine the safe distance between the current operating state and the protection threshold. Specifically, the controller calculates the difference between the condensing pressure and the high pressure protection threshold, the difference between the exhaust temperature and the exhaust temperature protection threshold, and the difference between the compressor input power and the power protection threshold. Based on the above differences, it determines whether the current operating state is close to the corresponding protection threshold. When any of the above differences is less than the preset allowable margin, it indicates that the current condensing heat exchange process has approached the protection action area.

[0124] When the protection margin is lower than the protection margin boundary, the controller divides the current condensation heat exchange process into the protection approach zone. The protection margin is used to identify the risk of protection triggering in advance, and does not replace the original high-pressure protection, exhaust temperature protection or power protection actions of the equipment. The original protection actions are still executed independently by the equipment safety control logic.

[0125] When dividing the heat exchange interval, the controller prioritizes the protection approach zone, followed by the heat exchange attenuation zone, and finally the high-efficiency heating zone. Specifically, when the condensing pressure, exhaust temperature, or compressor input power approaches the corresponding protection threshold, and the protection margin is lower than the protection margin boundary, regardless of whether the condensing pressure change rate, water-side effective temperature rise change rate, and heat exchange per unit power consumption simultaneously meet other conditions, the current condensing heat exchange process is prioritized as the protection approach zone. This priority setting prevents the equipment from being misjudged as a normal heat exchange attenuation state when it is close to the protection boundary, thereby ensuring that the controller prioritizes the execution of protection and preventive measures such as frequency reduction and water-side heat exchange enhancement.

[0126] If the protection approach zone conditions are not met, the controller further determines whether the current condensation heat exchange process is in the heat exchange decay zone. When any of the following conditions are met: the condensation pressure change rate exceeds the pressure rise boundary, the effective temperature rise change rate on the water side is lower than the temperature rise decay boundary, or the heat exchange per unit power consumption is lower than the heat exchange per unit power consumption boundary, it indicates that the current condensation heat exchange process has shown at least one of the following decay characteristics: accelerated pressure rise, insufficient heat absorption on the water side, or decreased heat exchange capacity per unit energy consumption. The controller divides the current condensation heat exchange process into the heat exchange decay zone. The heat exchange decay zone does not necessarily mean that the equipment has failed, but rather that the condensation heat exchange process has deviated from the efficient heating state and needs to be controlled and intervened before the high-pressure protection is triggered.

[0127] When the rate of change of condensing pressure does not exceed the pressure ramp-up boundary, the rate of change of effective temperature rise on the water side is not lower than the temperature rise decay boundary, and the heat exchange per unit power consumption meets the heat exchange per unit power consumption boundary, the controller divides the current condensing heat exchange process into the high-efficiency heating zone. The high-efficiency heating zone indicates that the upward trend of condensing pressure is within the allowable range, the heat absorption response on the water side has not shown significant decay, and the compressor input power can be effectively converted into heat exchange on the water side. At this time, the compressor can maintain its heating output, allowing the equipment to continue to perform the normal heating process.

[0128] After dividing the interval, the controller further identifies the condensation heat exchange terminal attenuation state. The condensation heat exchange terminal attenuation state refers to the operating state of a heat pump water heater in the later stages of heating, when the water temperature is close to the target temperature, the water supply is high, or the water-side inlet temperature is high. During this stage, the condensation pressure continuously rises while the effective water-side temperature rise gradually decreases, and the heat exchange per unit power consumption continuously declines. This state differs from a single pressure increase or a single temperature rise fluctuation; it requires a consistent attenuation trend across multiple consecutive analysis windows. Specifically, the controller treats multiple adjacent condensation heat exchange state units as continuous judgment objects. When the rate of change of condensation pressure is consistently higher than the pressure rise boundary, the rate of change of effective water-side temperature rise is consistently lower than the temperature rise attenuation boundary, and the heat exchange per unit power consumption continuously decreases as the analysis window progresses, the current condensation heat exchange process is determined to have entered the condensation heat exchange terminal attenuation state. The criteria for consistently higher, consistently lower, and continuously decreasing are based on the judgment results of multiple consecutive analysis windows, not on a single sampling point or a single abnormal frame, thus avoiding misidentification due to sensor jitter, short-term water usage disturbances, or communication delays.

[0129] In this embodiment, the controller also types the attenuation state of the final stage of condensation heat exchange based on the recovery range of the effective water-side temperature rise before and after the circulating water flow rate adjustment. The recovery range of the effective water-side temperature rise refers to the degree of recovery of the effective water-side temperature rise relative to the state before the adjustment, used to determine whether the enhanced water-side heat exchange capacity can improve the condensation heat exchange state, specifically including:

[0130] When the controller detects that the condensation heat exchange process has entered the final stage of decay, the circulating water flow rate can be increased within the allowable circulating water pump speed range of the equipment. In the subsequent analysis window, observe whether the effective temperature rise on the water side recovers, whether the heat exchange per unit power consumption improves, and whether the condensation pressure change rate drops.

[0131] If the effective temperature rise recovery of the water side is lower than the preset recovery range after the circulation water flow rate is increased, it indicates that simply increasing the water flow rate has failed to effectively improve the heat absorption effect of the water side. At this time, the attenuation of the final stage of condensation heat exchange is more likely to be caused by factors such as limited heat release capacity of the refrigerant side, mismatch of refrigerant circulation state, deviation of electronic expansion valve adjustment or increase of heat exchanger thermal resistance. The controller marks this state as the attenuation of the final stage with limited heat release on the refrigerant side.

[0132] When the circulating water flow rate increases, the effective temperature rise recovery range on the water side reaches the preset recovery range, indicating that increasing the circulating water flow rate can effectively improve the water side heat absorption response. The current terminal attenuation is mainly related to insufficient water side heat absorption capacity, low water side flow rate, or water side heat exchange lag. The controller marks this state as terminal attenuation due to insufficient water side heat absorption. The preset recovery range can be preset by the equipment controller based on the rated heating capacity of the heat pump water heater, the adjustment range of the circulating water pump, the heat exchange capacity of the condenser water side, and historical heating operation records. It can also be corrected based on the actual recovery results in subsequent control effect feedback.

[0133] When determining the preset recovery range, the controller can use one or more analysis windows before the circulating water flow rate is adjusted as the reference window before adjustment, and one or more analysis windows after the circulating water flow rate is adjusted as the observation window after adjustment. The reference window before adjustment is used to determine the degree of attenuation of the effective temperature rise on the water side, and the observation window after adjustment is used to determine whether the effective temperature rise on the water side has recovered. If the effective temperature rise on the water side in the observation window after adjustment recovers relative to the reference window before adjustment, and the heat exchange per unit power consumption does not continue to decrease, then it is considered that the circulating water flow rate adjustment has an effective improvement effect on the heat absorption on the water side.

[0134] If the effective temperature rise on the water side in the observation window is insufficient after adjustment and the rate of change of condensing pressure has not yet fallen back, it is considered that simply increasing the water side flow rate is insufficient to improve the final stage attenuation. The preset recovery range is used to distinguish between the two results mentioned above, and its value should not exceed the normal water side temperature rise range that the circulating water pump can cause under the current operating mode.

[0135] By using type tags, the controller can distinguish control priorities when generating phased adjustment paths later:

[0136] For refrigerant-side heat release-limited terminal attenuation, the focus should be on correcting the opening of the electronic expansion valve and limiting the compressor frequency increase;

[0137] For the terminal attenuation caused by insufficient heat absorption on the water side, the focus should be on increasing the circulating water flow rate and observing the recovery of the effective temperature rise on the water side. This makes the optimization of the condensation heat exchange process more targeted, rather than simply controlling it based on the outlet water temperature or condensation pressure.

[0138] Based on the current condensation heat exchange process interval and the attenuation state at the end of the condensation heat exchange, a phased adjustment path is generated. In the high-efficiency heating zone, the compressor's temperature rise output is maintained; in the heat exchange attenuation zone, the compressor's frequency increase is limited, and the opening of the electronic expansion valve and the circulating water flow rate are adjusted accordingly; in the protection approach zone, frequency reduction and water-side heat exchange enhancement control are implemented. Specific implementation includes:

[0139] After identifying the current condensation heat exchange process interval and the attenuation state at the end of the condensation heat exchange, the controller generates a phased adjustment path based on the type marking of the current condensation heat exchange process interval and the attenuation state at the end of the condensation heat exchange. The phased adjustment path is used to specify the adjustment sequence, adjustment range, and execution limit of the compressor operating frequency, electronic expansion valve opening, and circulating water pump speed under different condensation heat exchange states. This phased adjustment path is not a single frequency increase or decrease command generated solely based on the outlet water temperature or target water temperature, but rather combines the division results of the high-efficiency heating zone, heat exchange attenuation zone, and protection approach zone, as well as the type marking of the attenuation state at the end of the refrigerant side with limited heat release or the attenuation state at the end of the water side with insufficient heat absorption, to determine whether to maintain the heating, suppress the attenuation, or execute protective prevention control.

[0140] When generating the phased adjustment path, the controller determines the adjustment intensity level based on the degree to which the condensing pressure change rate deviates from the pressure ramp-up boundary, the degree to which the effective water-side temperature rise change rate deviates from the temperature rise decay boundary, the degree to which the heat transfer per unit power consumption deviates from the heat transfer per unit power consumption boundary, and the degree to which the protection margin is lower than the protection margin boundary. The adjustment intensity levels can be divided into mild adjustment, moderate adjustment, and protective prevention adjustment, with different adjustment intensity levels corresponding to different compressor frequency adjustment ranges, electronic expansion valve opening adjustment ranges, and circulating water pump speed adjustment ranges, respectively.

[0141] When generating adjustment quantities, the controller first determines the priority adjustment object based on the current interval and the attenuation type at the end, then determines the adjustment amplitude based on the adjustment intensity level, and finally performs amplitude limiting processing based on the compressor's allowable frequency range, the electronic expansion valve's allowable opening range, and the circulating water pump's allowable speed range, so that the generated compressor frequency reduction, electronic expansion valve opening correction, and circulating water pump speed increase are all within the allowable working range of the actuators.

[0142] Specifically, when the current condensation heat exchange process is in the high-efficiency heating zone, the controller generates a high-efficiency heating segment. The high-efficiency heating segment indicates that the condensation pressure change rate has not exceeded the pressure ramp-up boundary, the effective temperature rise change rate on the water side has not fallen below the temperature rise decay boundary, and the heat exchange per unit power consumption meets the heat exchange per unit power consumption boundary. This means that the compressor input power can be effectively converted into water-side heat exchange effect. At this time, the controller maintains the current heating output of the compressor, so that the compressor continues to operate according to the current heating demand, without actively triggering frequency reduction or heat exchange suppression control.

[0143] At the same time, the opening of the electronic expansion valve and the circulation water flow are kept stable. That is, the opening of the electronic expansion valve is only finely adjusted according to the original refrigerant circulation stability control requirements of the equipment, and the speed of the circulating water pump is only finely adjusted according to the water side flow stability requirements, so as to avoid the decrease in heating rate or refrigerant circulation fluctuations caused by premature intervention in the high-efficiency heating stage.

[0144] When the current condensation heat exchange process is in the heat exchange decay zone, or when the decay state at the end of the condensation heat exchange has been identified but has not yet entered the protection approach zone, the controller generates a decay suppression section. The control objective of the decay suppression section is to limit the condensation pressure from continuing to rise, suppress the heat exchange per unit power consumption from continuing to decrease, and make targeted linkage corrections to the opening of the electronic expansion valve or the circulating water flow rate according to the type of decay at the end. In this stage, the controller first limits the compressor frequency increment, that is, in subsequent control cycles, the compressor is not allowed to continue to rapidly increase the frequency according to the conventional water temperature difference control logic, or the compressor frequency increase is limited to a range smaller than the conventional frequency increase, thereby preventing the continued increase of the high-pressure load on the refrigerant side when the heat exchange benefit has already decreased.

[0145] For refrigerant-side heat release-limited terminal attenuation, the controller focuses on generating the electronic expansion valve opening correction amount, specifically including:

[0146] The electronic expansion valve opening correction amount refers to the amount of opening change that needs to be adjusted based on the current electronic expansion valve opening to improve the refrigerant circulation state and suppress abnormal rise in condensing pressure. This opening correction amount is determined by the controller based on the condensing pressure change rate, exhaust temperature change rate, refrigerant side temperature difference change, compressor frequency change, and heat exchange change trend per unit power consumption.

[0147] When the condensing pressure continues to rise and the effective temperature rise on the water side is insufficient after the water-side flow rate increases, it indicates that simply increasing the heat absorption capacity of the water side cannot effectively improve the heat exchange state. At this time, the controller corrects the opening of the electronic expansion valve to rematch the refrigerant flow rate with the compressor operating frequency, and limits the compressor frequency increment to reduce the tendency of high pressure accumulation on the condenser side. During the correction of the electronic expansion valve opening, a limit on the opening change is also set to avoid the electronic expansion valve opening changing too much in a short period of time, which would lead to unstable liquid supply on the evaporator side or abnormal compressor suction state.

[0148] For the terminal attenuation caused by insufficient heat absorption on the water side, the controller focuses on generating the circulating water flow rate adjustment. The circulating water flow rate adjustment refers to the amount of flow rate change that needs to be adjusted based on the current circulating water flow rate to enhance the heat absorption capacity on the water side. This adjustment is determined by the controller based on the effective temperature rise rate on the water side, the circulating water flow rate response, the circulating water pump speed, the water side temperature rise recovery, and the heat exchange rate change trend per unit power consumption.

[0149] When the effective temperature rise on the water side reaches the preset recovery range after the circulation water flow rate increases, it indicates that insufficient heat absorption on the water side is an important reason for the terminal attenuation. At this time, the controller increases the circulation water flow rate by increasing the speed of the circulation water pump, so that the water side can remove the heat released by the condenser more in a timely manner, thereby reducing the trend of the condensing pressure continuing to rise. During the circulation water flow rate adjustment process, the controller also limits the single increase range and the number of consecutive increases of the circulation water pump speed to avoid water side temperature fluctuations, increased pipeline noise, or abnormally high pump consumption caused by sudden changes in flow rate.

[0150] When the current condensing heat exchange process is in the protection approach zone, the controller generates a protection prevention section. The control objective of the protection prevention section is to reduce the condensing side pressure load and heat load in advance before the equipment is actually triggered by high-pressure protection, exhaust temperature protection, or power protection, so that the current condensing heat exchange process exits the protection approach zone. The protection prevention section includes compressor frequency reduction, electronic expansion valve limit correction, and circulating water pump speed increase. Among them, compressor frequency reduction refers to the frequency reduction required based on the current compressor operating frequency, which is used to directly reduce the refrigerant circulation compression load and the tendency of high-pressure side pressure to rise.

[0151] The electronic expansion valve limit correction amount refers to the limited adjustment amount made within the allowable opening range of the electronic expansion valve, which is used to cooperate with the compressor frequency reduction to maintain stable refrigerant circulation.

[0152] The increase in circulating water pump speed refers to the increase in speed within the allowable speed range of the circulating water pump, which is used to enhance the heat exchange capacity on the water side and remove heat from the condenser side.

[0153] The three control variables mentioned above are generated according to the principle of prioritizing protection and prevention. Among them, compressor frequency reduction is used to reduce the risk of protection triggering, electronic expansion valve amplitude limiting correction is used to maintain refrigerant circulation stability, and circulating water pump speed increase is used to enhance water-side heat exchange and absorption capacity.

[0154] When performing frequency reduction and water-side heat exchange enhancement control in the protection approach zone, the controller first generates a protection margin based on the difference between the condensing pressure, exhaust temperature, and compressor input power and the corresponding protection threshold. Specifically, the controller compares the distance between the current condensing pressure and the high-pressure protection threshold, the distance between the current exhaust temperature and the exhaust temperature protection threshold, and the distance between the current compressor input power and the power protection threshold, and uses the above distances as the basis for judging the risk of protection triggering. When any of these distances is less than the safe lead time allowed by the equipment, it indicates that the current operating state is close to the corresponding protection threshold.

[0155] When the protection margin is lower than the preset protection margin boundary, the controller confirms that the current condensation heat exchange process is in the protection approach zone and needs to perform protection prevention control. The protection margin is a judgment condition for advance control and does not change the original high pressure protection threshold, exhaust temperature protection threshold and power protection threshold of the equipment.

[0156] When the protection margin is lower than the preset protection margin boundary, the controller first prohibits the compressor from continuing to increase the frequency. Prohibiting the compressor from continuing to increase the frequency means that the normal frequency increase request caused by the water temperature not reaching the target value is blocked in the protection prevention section, so that the compressor operating frequency no longer increases.

[0157] Subsequently, the controller outputs protection and prevention control commands in the order of compressor frequency reduction, electronic expansion valve opening correction, and circulating water pump speed increase;

[0158] First, the compressor frequency is reduced to directly reduce the load on the high-pressure side of the refrigerant. Then, the electronic expansion valve opening is corrected to match the throttling state with the refrigerant circulation volume after the frequency reduction.

[0159] Finally, increasing the speed of the circulating water pump is to enhance the heat exchange capacity on the water side, so that the heat released by the condenser can be absorbed by the water side in a timely manner. The above sequence can avoid insufficient control effect caused by only increasing the water flow rate without reducing the high-pressure load of the compressor, or only reducing the frequency without improving the heat exchange on the water side.

[0160] After the protection and prevention control command is executed, the controller continues to collect the subsequent condensation heat exchange process frame sequence, and determines whether the condensation pressure drop state has reached the preset drop condition based on the new condensation heat exchange state unit. The preset drop condition may include at least one of the following: the condensation pressure change rate is no longer higher than the pressure rise boundary, the protection margin between the condensation pressure and the high pressure protection threshold is restored to above the preset protection margin boundary, the exhaust temperature no longer continues to rise, and the heat exchange per unit power consumption no longer continues to decrease.

[0161] If the controlled condensing pressure does not fall below the preset fall condition, it indicates that the current protection and prevention control is insufficient to remove the condensing heat exchange process from the protection approach zone. The controller continues to reduce the compressor operating frequency and maintain the increased circulating water flow, while keeping the electronic expansion valve opening within the stable range after the limit correction, until the current condensing heat exchange process exits the protection approach zone.

[0162] When the controller confirms that the condensing pressure drop has reached the preset drop condition, and the condensing pressure, exhaust temperature, and compressor input power are no longer close to the corresponding protection threshold, it determines that the current condensing heat exchange process has exited the protection approach zone. After exiting the protection approach zone, the controller does not immediately resume normal rapid temperature rise control, but instead re-determines whether the current process belongs to the heat exchange decay zone or the high-efficiency temperature rise zone based on the condensing heat exchange status unit. If it is still in the heat exchange decay zone, it continues to execute the decay suppression section control.

[0163] If the system has recovered to the high-efficiency heating zone, gradually remove the frequency increase limit to allow the compressor, electronic expansion valve, and circulating water pump to return to a stable heating control state.

[0164] Through the above method, this embodiment can complete early intervention before the actual triggering of condensation pressure protection or exhaust temperature protection, avoid frequent equipment shutdowns, and restore the condensation heat exchange process from the high pressure and low efficiency trend to a controllable heat exchange state.

[0165] Therefore, the phased adjustment path in this embodiment is reflected as follows:

[0166] In the high-efficiency heating section, excessive intervention is not used to ensure the heating efficiency of hot water. In the attenuation suppression section, the opening of the electronic expansion valve or the circulation water flow rate are adjusted according to the attenuation of the end section due to the limited heat release on the refrigerant side or the attenuation of the end section due to insufficient heat absorption on the water side, so as to avoid using the same control action to deal with different attenuation causes.

[0167] In the protection and prevention phase, based on the protection margin, measures such as prohibiting frequency increase, reducing compressor frequency, correcting electronic expansion valve opening, and increasing circulating water pump speed are implemented to reduce the risk of protection triggering in advance.

[0168] By using a phased control method, heat pump water heaters can identify the process of condensation heat exchange transitioning from high-efficiency heating to high-pressure low-efficiency in the later stages of hot water heating, and optimize the condensation heat exchange process before the protection action occurs.

[0169] The system collects data on the condensing pressure drop after control, water-side temperature rise recovery, energy consumption changes, and protection action triggering status; generates a control effect feedback report; updates the condensing heat transfer boundary rules; and outputs the optimization results of the condensing heat transfer process. Specific implementation includes:

[0170] After the control command corresponding to the phased adjustment path is executed, the controller continues to collect the condensing pressure drop status, water side temperature rise recovery status, energy consumption change status, and protection action trigger status after the control is implemented, and generates a control effect feedback based on this. The control effect feedback is used to record the actual improvement results of the control command on the condensing heat exchange process. It does not simply record whether the control command has been issued, but compares the condensing pressure, water side temperature rise, heat exchange per unit power consumption, and protection action status before and after the execution of the control command. It is used to determine whether the phased adjustment path effectively suppresses the attenuation at the end of the condensing heat exchange, reduces the risk of protection triggering, and whether the condensing heat exchange boundary rules need to be corrected.

[0171] Specifically, before outputting the phased adjustment path, the controller uses the changes in condensing pressure, water-side temperature rise, heat exchange per unit power consumption, and protection status flags within the current analysis window as the reference for control.

[0172] Within one or more subsequent analysis windows after the control command is executed, a new condensation heat exchange process frame sequence is acquired, and the corresponding condensation heat exchange state unit is reconstructed. The condensation pressure change, water side temperature rise, heat exchange per unit power consumption, and protection status flag in the subsequent analysis window are used as the results after control.

[0173] By comparing the baseline before control and the results after control, the magnitude of the condensing pressure drop, the magnitude of the water-side temperature rise recovery, the magnitude of the heat exchange recovery per unit power consumption, and the trigger status of the protection action are obtained.

[0174] The magnitude of the condensing pressure drop is used to characterize whether the condensing pressure changes from a continuous rise to a fall or stabilization after the control command is executed. If the condensing pressure after control is lower than the condensing pressure before control, or the rate of change of condensing pressure recovers from being higher than the pressure rise boundary to being below the pressure rise boundary, then the condensing pressure is considered to have a downward or controlled trend.

[0175] If the condensing pressure continues to rise after control, or the rate of change of condensing pressure remains above the pressure ramp-up boundary, then the condensing pressure is considered not to have fallen back. The water-side temperature rise recovery amplitude is used to characterize whether the water-side heat absorption effect has improved after the control command is executed. It can be determined by comparing the water-side temperature rise or the rate of change of effective water-side temperature rise before and after control. If the effective water-side temperature rise no longer decays after control, or the rate of change of effective water-side temperature rise recovers to a state not lower than the temperature rise decay boundary, then the water-side temperature rise is considered to have recovered.

[0176] The recovery range of heat exchange per unit power consumption is used to characterize whether the effective water-side heat exchange capacity corresponding to the compressor input power has improved. If the heat exchange per unit power consumption no longer decreases continuously after control, or recovers to the state that meets the boundary of heat exchange per unit power consumption, then the heat exchange per unit power consumption is considered to have recovered. The protection action triggering state is used to indicate whether the high pressure protection, exhaust temperature protection, compressor overload protection or water flow abnormal protection is triggered after the control command is executed, or whether it is still in the approaching state before the protection is triggered.

[0177] When generating a control effect feedback record, the controller writes the interval to which the condensation heat exchange process belongs, the type of attenuation state at the end of the condensation heat exchange, the executed compressor frequency reduction, the electronic expansion valve opening correction, the circulating water flow rate adjustment, the condensation pressure drop, the water side temperature rise recovery, the unit power heat exchange recovery, and the protection action trigger status into the same feedback record. This feedback record is used to explain the correspondence between the input status of the control action, the control action, and the output effect.

[0178] For example, if the current state is marked as insufficient heat absorption on the water side and the controller increases the speed of the circulating water pump, and if the water side temperature rise recovers, the heat exchange per unit power consumption recovers, and no protection action is triggered, then the control effect feedback record is a valid recovery.

[0179] If the condensing pressure does not drop after the circulating water pump speed is increased and the heat exchange per unit power consumption does not recover, the control effect feedback record will be insufficient. In this way, the controller can establish a feedback relationship between the actual control effect and the aforementioned condensing heat exchange boundary rules.

[0180] When updating the condensation heat transfer boundary rules, the controller corrects the pressure ramp-up boundary, unit power heat transfer boundary, temperature rise decay boundary, protection margin boundary, and stage switching conditions based on the control effect feedback. The stage switching conditions refer to the judgment conditions that the controller uses when switching between the high-efficiency heating stage, the decay suppression stage, and the protection prevention stage. These conditions include whether the condensation pressure change rate exceeds the pressure ramp-up boundary, whether the effective temperature rise change rate on the water side is lower than the temperature rise decay boundary, whether the unit power heat transfer is lower than the unit power heat transfer boundary, and whether the protection margin is lower than the protection margin boundary.

[0181] When the control effect feedback indicates that the condensing pressure has not dropped or the heat exchange per unit power consumption has not recovered, it means that the original condensing heat exchange boundary rule identified the condensing heat exchange attenuation trend too late, or the intervention of the phased adjustment path was not timely enough. At this time, the controller tightens the pressure rise boundary, the heat exchange per unit power consumption boundary and the phase switching condition. Tightening the pressure rise boundary means that the controller can judge the existence of heat exchange attenuation risk under a small condensing pressure rise trend, so as to enter the attenuation suppression stage or the protection prevention stage earlier.

[0182] Tightening the heat transfer boundary per unit power consumption refers to increasing the sensitivity to the decrease in heat transfer per unit power consumption, so that the equipment can identify heat transfer decay earlier when the energy input fails to be effectively converted into water-side heat absorption effect.

[0183] The tightening stage switching condition refers to making the controller switch from the high-efficiency heating stage to the attenuation suppression stage, and from the attenuation suppression stage to the protection and prevention stage earlier, so as to avoid implementing control intervention only after the condensing pressure has already risen significantly.

[0184] When the control effect feedback indicates that the water-side temperature rise has recovered and no protection action has been triggered, it means that the current condensation heat exchange boundary rules and the phased adjustment path can restore the condensation heat exchange process to a controllable state. At this time, the controller can keep the corresponding temperature rise decay boundary and protection margin boundary unchanged.

[0185] If the water-side temperature rise recovers and the heat exchange per unit power consumption recovers without any protection action being triggered in multiple consecutive heating operation cycles, the controller can appropriately relax the corresponding temperature rise attenuation boundary and protection margin boundary within the allowable range of the equipment, so that the equipment avoids entering the attenuation suppression stage or protection prevention stage too early.

[0186] The relaxation of the corresponding boundaries only applies to the advance identification boundaries and stage switching boundaries in the optimized control of the condensation heat exchange process, and does not change the original high-pressure protection threshold, exhaust temperature protection threshold, compressor overload protection threshold, and water flow abnormality protection threshold of the equipment.

[0187] In this embodiment, the updating of the condensation heat transfer boundary rules adopts a hierarchical recording method, specifically including:

[0188] The controller first saves the boundary rules before the update, the control effect feedback, and the boundary rules after the update simultaneously, forming a traceable boundary update record;

[0189] The updated condensation heat exchange boundary rules are then written into the boundary rule library for the next heating operation cycle. The boundary rule library is used to provide pressure ramp-up boundary, temperature rise decay boundary, heat exchange per unit power consumption boundary, protection margin boundary and stage switching conditions after the start of the next heating operation, so that the next heating operation cycle can be optimized based on the actual control effect of the previous cycle.

[0190] If the updated boundary rules conflict with the equipment safety protection threshold, the controller will prioritize retaining the safety protection threshold and limit the boundary rules to ensure that the updated condensing heat exchange boundary rules are always within the equipment's allowable operating range.

[0191] It should be noted that the updated condensing heat transfer boundary rules take effect first in the next heating operation cycle, and do not directly overwrite the currently executing protection and prevention control process, in order to avoid control oscillations caused by frequent changes in boundary rules within the same control process. When writing the updated condensing heat transfer boundary rules, the controller also saves the update version number, applicable operating mode, update time, and corresponding control effect feedback.

[0192] If, after applying the updated boundary rules in the next heating cycle, the condensing pressure fails to drop, the heat exchange per unit power consumption fails to recover, or protection actions are frequently triggered, the controller will mark the updated rule as incompatible and revert to the previous version of the condensing heat exchange boundary rules or the factory-calibrated boundary rules.

[0193] Through the aforementioned control effect feedback and boundary rule update process, this embodiment can feed back the control results of a single heating operation to the next heating operation cycle, so that the optimization of the condensing heat exchange process no longer depends on a fixed control boundary. For changes in condensing heat exchange characteristics caused by gradual scaling of the heat exchanger, performance degradation of the circulating water pump, changes in refrigerant circulation state, or changes in the operating environment, the controller can gradually correct the condensing heat exchange boundary rules according to the condensing pressure drop state, water side temperature rise recovery state, energy consumption change state, and protection action trigger state. This improves the timeliness of identifying the attenuation state at the end of the condensing heat exchange and the adaptability of the phased adjustment path, and finally outputs the optimization results of the condensing heat exchange process.

[0194] The optimization results of the condensation heat exchange process may include the final interval state of the current heating operation cycle, whether condensation heat exchange end-stage attenuation has occurred, end-stage attenuation type marking, executed adjustment paths, control effect feedback, and updated condensation heat exchange boundary rules, which are used for subsequent operation control and operation record traceability of heat pump type hot water equipment.

[0195] Example 2: An optimization system for the condensation heat exchange process of a heat pump water heater, such as... Figure 2 As shown, it specifically includes:

[0196] The data acquisition module is used to collect refrigerant-side status data, water-side heat exchange data, and actuator operation data during the heating operation of heat pump water heaters, and generate a condensation heat exchange process frame sequence by aligning them according to a unified sampling period.

[0197] The frame sequence generation module is used to extract the characteristics of heat release change on the refrigerant side, heat absorption response on the water side, adjustment of the actuator and energy consumption change based on the frame sequence of the condensation heat exchange process, and to construct a condensation heat exchange state unit.

[0198] The state construction module is used to match the condensation heat exchange state unit with the condensation heat exchange boundary rules, determine whether the current condensation heat exchange process is in the high-efficiency heating zone, the heat exchange attenuation zone or the protection approach zone, and identify the attenuation state of the final stage of condensation heat exchange when the condensation pressure continues to rise, the effective temperature rise on the water side attenuates and the heat exchange per unit power consumption decreases.

[0199] The attenuation identification module is used to generate a phased adjustment path based on the current interval of the condensation heat exchange process and the attenuation state of the end of the condensation heat exchange. In the high-efficiency heating zone, it maintains the compressor heating output, in the heat exchange attenuation zone, it limits the compressor frequency increase and links to correct the opening of the electronic expansion valve and the circulating water flow, and in the protection approach zone, it performs frequency reduction and water-side heat exchange enhancement control.

[0200] The adjustment and control module is used to collect data on the condensing pressure drop status, water side temperature rise recovery status, energy consumption change status, and protection action trigger status after control, generate control effect feedback, update condensing heat exchange boundary rules, and output the optimization results of the condensing heat exchange process.

[0201] The above embodiments can be implemented, in whole or in part, by software, hardware, firmware, or any other combination thereof. When implemented using software, the above embodiments can be implemented, in whole or in part, as a computer program product. The computer program product includes one or more computer instructions or computer programs. When the computer instructions or computer programs are loaded or executed on a computer, all or part of the processes or functions described in the embodiments of this application are generated. The computer can be a general-purpose computer, a special-purpose computer, a computer network, or other programmable device. The computer instructions can be stored in a computer-readable storage medium or transmitted from one computer-readable storage medium to another. For example, the computer instructions can be transmitted from one website, computer, server, or data center to another website, computer, server, or data center via wired or wireless (e.g., infrared, wireless, microwave, etc.) means. The computer-readable storage medium can be any available medium that a computer can access or a data storage device such as a server or data center that includes one or more sets of available media. The available medium can be a magnetic medium (e.g., floppy disk, ATA hard disk, magnetic tape), an optical medium (e.g., DVD), or a semiconductor medium. The semiconductor medium can be a solid-state ATA hard disk.

[0202] It should be understood that in the various embodiments of this application, the order of the above-mentioned processes does not imply the order of execution. The execution order of each process should be determined by its function and internal logic, and should not constitute any limitation on the implementation process of the embodiments of this application.

[0203] Those skilled in the art will recognize that the units and algorithm steps of the various examples described in conjunction with the embodiments disclosed herein can be implemented in electronic hardware, or a combination of computer software and electronic hardware. Whether these functions are implemented in hardware or software depends on the specific application and design constraints of the technical solution. Those skilled in the art can use different methods to implement the described functions for each specific application, but such implementation should not be considered beyond the scope of this application.

[0204] In the several embodiments provided in this application, it should be understood that the disclosed systems, apparatuses, and methods can be implemented in other ways. For example, the apparatus embodiments described above are merely illustrative; for instance, the division of units is only a logical functional division, and in actual implementation, there may be other division methods. For example, multiple units or components may be combined or integrated into another system, or some features may be ignored or not executed. Furthermore, the coupling or direct coupling or communication connection shown or discussed may be through some interfaces; the indirect coupling or communication connection between apparatuses or units may be electrical, mechanical, or other forms.

[0205] The units described as separate components may or may not be physically separate. The components shown as units may or may not be physical units; they may be located in one place or distributed across multiple network units. Some or all of the units can be selected to achieve the purpose of this embodiment, depending on actual needs.

[0206] In addition, the functional units in the various embodiments of this application can be integrated into one processing unit, or each unit can exist physically separately, or two or more units can be integrated into one unit.

[0207] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A method for optimizing the condensation heat exchange process of a heat pump water heater, characterized in that, include: Collect refrigerant-side status data, water-side heat exchange data, and actuator operation data during the heating operation of heat pump water heaters, and align them with a unified sampling period to generate a condensation heat exchange process frame sequence. Based on the frame sequence of the condensation heat exchange process, the characteristics of heat release change on the refrigerant side, heat absorption response on the water side, adjustment of the actuator and energy consumption change are extracted to construct a condensation heat exchange state unit. The condensation heat exchange state unit is matched with the condensation heat exchange boundary rule to determine whether the current condensation heat exchange process is in the high-efficiency heating zone, the heat exchange attenuation zone, or the protection approach zone. The attenuation state of the final stage of condensation heat exchange is identified when the condensation pressure continues to rise, the effective temperature rise on the water side decreases, and the heat exchange per unit power consumption decreases. Based on the current condensation heat exchange process interval and the attenuation state of the final stage of condensation heat exchange, a phased adjustment path is generated. In the high-efficiency heating zone, the compressor heating output is maintained. In the heat exchange attenuation zone, the compressor frequency is limited and the opening of the electronic expansion valve and the circulating water flow are corrected in conjunction. In the protection approach zone, frequency reduction and water-side heat exchange enhancement control are implemented. Collect the condensing pressure drop status, water side temperature rise recovery status, energy consumption change status and protection action trigger status after control, generate control effect feedback, update condensing heat exchange boundary rules and output condensing heat exchange process optimization results; The condensation heat transfer boundary rules include pressure ramp-up boundary, temperature rise decay boundary, heat transfer per unit power consumption boundary, and protection margin boundary. When the rate of change of condensing pressure does not exceed the pressure ramp-up boundary, the rate of change of effective temperature rise on the water side is not lower than the temperature rise decay boundary, and the heat exchange per unit power consumption meets the heat exchange per unit power consumption boundary, the current condensing heat exchange process is divided into the high-efficiency heating zone. If the protection approach zone conditions are not met, when the rate of change of condensing pressure exceeds the pressure ramp-up boundary, the rate of change of effective temperature rise on the water side is lower than the temperature rise decay boundary, or the heat transfer per unit power consumption is lower than the heat transfer per unit power consumption boundary, the current condensing heat transfer process is divided into the heat transfer decay zone. When the condensing pressure, exhaust temperature, or compressor input power is close to the corresponding protection threshold and the protection margin is lower than the protection margin boundary, the current condensing heat exchange process is classified as the protection approach zone.

2. The method for optimizing the condensation heat exchange process of a heat pump water heater according to claim 1, characterized in that: The refrigerant-side status data includes condensing pressure, exhaust temperature, condenser refrigerant inlet temperature, condenser refrigerant outlet temperature, and refrigerant-side temperature difference. The water-side heat exchange data includes water-side inlet temperature, water-side outlet temperature, circulating water flow rate, water-side temperature rise, and water-side temperature rise change. The operating data of the actuator includes compressor operating frequency, electronic expansion valve opening degree, circulating water pump speed, compressor input power, and protection status flags.

3. The method for optimizing the condensation heat exchange process of a heat pump water heater according to claim 2, characterized in that: The step of generating a condensation heat transfer process frame sequence aligned according to a uniform sampling period includes: Using the compressor operating cycle or condensing pressure sampling cycle as a unified sampling cycle, timestamp correction is performed on the refrigerant-side state data, water-side heat exchange data, and actuator operating data; Data within the same sampling period are grouped into single frames according to the acquisition time, and frame status flags are set for missing data, abrupt data, and protection-triggered data. Arrange the data of each single frame in the order of sampling time to generate a condensation heat exchange process frame sequence containing refrigerant side field, water side field, actuator field, energy consumption field and frame status marker.

4. The method for optimizing the condensation heat exchange process of a heat pump water heater according to claim 3, characterized in that: The construction of the condensation heat exchange state unit includes: Using multiple consecutive condensation heat exchange process frames as analysis windows, the following parameters are extracted: condensation pressure change rate, exhaust temperature change rate, refrigerant side temperature difference change, water side effective temperature rise change rate, circulating water flow response, compressor frequency change, electronic expansion valve opening change, and compressor input power change. The heat exchange per unit power consumption is generated based on the water-side temperature rise, circulating water flow rate, and compressor input power. The above data are linked together in the same analysis window to generate a condensation heat exchange state unit that includes fields for refrigerant side heat release change, water side heat absorption response, actuator adjustment, and energy consumption change.

5. The method for optimizing the condensation heat exchange process of a heat pump water heater according to claim 4, characterized in that: The identification of the attenuation state at the end of the condensation heat exchange includes: If, within multiple consecutive analysis windows, the rate of change of condensing pressure is consistently higher than the pressure ramp-up boundary, the rate of change of effective temperature rise on the water side is consistently lower than the temperature rise decay boundary, and the heat exchange per unit power consumption decreases continuously, then it is determined that the current condensing heat exchange process has entered the decay state of the final stage of condensing heat exchange. Based on the effective temperature rise recovery range of the water side before and after the circulation water flow rate adjustment, the attenuation state of the final stage of the condensation heat exchange is categorized. When the effective temperature rise recovery range of the water side is lower than the preset recovery range after the circulation water flow rate increases, it is categorized as a refrigerant-side heat release-limited type attenuation. When the effective temperature rise recovery range of the water side reaches the preset recovery range after the circulation water flow rate increases, it is categorized as a water-side heat absorption-insufficient type attenuation.

6. The method for optimizing the condensation heat exchange process of a heat pump water heater according to claim 5, characterized in that: The generation of the phased adjustment path includes: Based on the current interval of the condensation heat exchange process and the type of attenuation state at the end of the condensation heat exchange, a high-efficiency heating section, an attenuation suppression section, and a protection and prevention section are generated. During the high-efficiency heating stage, the compressor maintains its current heating output and keeps the electronic expansion valve opening and circulating water flow rate stable. In the attenuation suppression section, the compressor frequency increment is limited, and the electronic expansion valve opening correction amount or circulating water flow rate adjustment amount is generated according to the attenuation of the last stage with limited heat release on the refrigerant side or the attenuation of the last stage with insufficient heat absorption on the water side. The protection and prevention section generates compressor frequency reduction, electronic expansion valve limit correction, and circulating water pump speed increase.

7. The method for optimizing the condensation heat exchange process of a heat pump water heater according to claim 6, characterized in that: The aforementioned frequency reduction and water-side heat transfer enhancement control in the protection approach zone includes: The protection margin is generated based on the difference between the condensing pressure, exhaust temperature, and compressor input power and the corresponding protection threshold. When the protection margin is lower than the preset protection margin boundary, the compressor is prohibited from continuing to increase its frequency, and protection and prevention control commands are output in the order of compressor frequency reduction, electronic expansion valve opening correction, and circulating water pump speed increase. If the controlled condensing pressure does not reach the preset drop condition, the compressor frequency will continue to be reduced while the circulating water flow rate is increased until the current condensing heat exchange process exits the protection approach zone.

8. The method for optimizing the condensation heat exchange process of a heat pump water heater according to claim 7, characterized in that: The generation of control effect feedback and updating of condensation heat transfer boundary rules include: A control effect feedback is generated based on the condensation pressure drop before and after the execution of the control command, the water side temperature rise recovery, the heat exchange recovery per unit power consumption, and the protection action trigger status. When the condensing pressure does not drop or the heat exchange per unit power consumption does not recover, tighten the pressure ramp-up boundary, the heat exchange per unit power consumption boundary, and the stage switching conditions. When the water-side temperature rise recovers and no protection action is triggered, maintain or relax the corresponding temperature rise attenuation boundary and protection margin boundary. Write the updated condensation heat exchange boundary rules into the boundary rule library for the next heating operation cycle.

9. A system for optimizing the condensation heat exchange process of a heat pump water heater, used to implement the method for optimizing the condensation heat exchange process of a heat pump water heater as described in any one of claims 1-8, characterized in that, include: The data acquisition module is used to collect refrigerant-side status data, water-side heat exchange data, and actuator operation data during the heating operation of heat pump water heaters, and generate a condensation heat exchange process frame sequence by aligning them according to a unified sampling period. The frame sequence generation module is used to extract the characteristics of heat release change on the refrigerant side, heat absorption response on the water side, adjustment of the actuator and energy consumption change based on the frame sequence of the condensation heat exchange process, and to construct a condensation heat exchange state unit. The state construction module is used to match the condensation heat exchange state unit with the condensation heat exchange boundary rules, determine whether the current condensation heat exchange process is in the high-efficiency heating zone, the heat exchange attenuation zone or the protection approach zone, and identify the attenuation state of the final stage of condensation heat exchange when the condensation pressure continues to rise, the effective temperature rise on the water side attenuates and the heat exchange per unit power consumption decreases. The attenuation identification module is used to generate a phased adjustment path based on the current interval of the condensation heat exchange process and the attenuation state of the end of the condensation heat exchange. In the high-efficiency heating zone, it maintains the compressor heating output, in the heat exchange attenuation zone, it limits the compressor frequency increase and links to correct the opening of the electronic expansion valve and the circulating water flow, and in the protection approach zone, it performs frequency reduction and water-side heat exchange enhancement control. The adjustment and control module is used to collect data on the condensing pressure drop status, water side temperature rise recovery status, energy consumption change status, and protection action trigger status after control, generate control effect feedback, update condensing heat exchange boundary rules, and output the optimization results of the condensing heat exchange process.

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