Air conditioner reversing control method and device, storage medium and electronic equipment

Abstract

The application provides a control method and device for reversing of an air conditioner, a storage medium and an electronic device. After a defrosting flag of the air conditioner is released and a compressor is stopped, an indoor coil temperature, an outdoor coil temperature and preset parameters are obtained, the preset parameters including a minimum reversing pressure difference threshold, a pressure difference decay rate gain and a delay compensation term; based on a preset saturated temperature and pressure comparison table, the indoor coil temperature and the outdoor coil temperature, an initial pressure difference is determined, the preset saturated temperature and pressure comparison table reflecting a first mapping relationship between a saturated temperature of a fluid on an evaporator side and a corresponding low saturated pressure, and a second mapping relationship between a saturated temperature of a fluid on a condenser side and a corresponding high saturated pressure; a reversing delay time of the air conditioner is determined according to the initial pressure difference and the preset parameters, and a four-way valve of the air conditioner is controlled to reverse based on the reversing delay time. The application solves the problems of abnormal sound and slow heating recovery caused by fixed delay reversing after defrosting of the air conditioner.

Description

Technical Field

[0001] This application relates to the field of air conditioning control technology, and more specifically, to a control method for air conditioning commutation, a control device for air conditioning commutation, a computer-readable storage medium, and an electronic device. Background Technology

[0002] Currently, after defrosting in heating mode, inverter air conditioners generally adopt a fixed delay reversing control strategy, which means that after the compressor stops, the four-way valve is driven to reverse after a fixed delay (such as 15 seconds, 25 seconds or 50 seconds) to resume heating operation.

[0003] The above-mentioned fixed delay control strategy has the problem of abnormal noise caused by excessive pressure difference when the four-way valve switches after defrosting, and the fixed delay strategy cannot adapt to changing operating conditions, resulting in slow heating recovery. Summary of the Invention

[0004] The main objective of this application is to provide a control method, control device, computer-readable storage medium, and electronic device for air conditioning reversal, so as to at least solve the problems of abnormal noise and slow heating recovery caused by fixed-delay reversal after defrosting in the prior art.

[0005] To achieve the above objectives, according to one aspect of this application, a control method for air conditioner reversing is provided, comprising: after the defrost flag of the air conditioner is released and the compressor stops, acquiring the indoor coil temperature, the outdoor coil temperature, and preset parameters, wherein the preset parameters include a minimum reversing pressure difference threshold, a pressure difference decay rate gain, and a delay compensation term, wherein the indoor coil temperature corresponds to the saturation temperature of the fluid on the condenser side, and the outdoor coil temperature corresponds to the saturation temperature of the fluid on the evaporator side; determining an initial pressure difference based on a preset saturation temperature and pressure lookup table, the indoor coil temperature, and the outdoor coil temperature, wherein the preset saturation temperature and pressure lookup table reflects: a first mapping relationship between the saturation temperature of the fluid on the evaporator side and the corresponding low saturation pressure, and a second mapping relationship between the saturation temperature of the fluid on the condenser side and the corresponding high saturation pressure; determining a reversing delay time of the air conditioner based on the initial pressure difference and the preset parameters, and controlling the reversing of the four-way valve of the air conditioner based on the reversing delay time.

[0006] Optionally, determining the initial pressure difference based on a temperature and pressure lookup table, the indoor coil temperature, and the outdoor coil temperature includes: matching a first saturation pressure corresponding to the indoor coil temperature and a second saturation pressure corresponding to the outdoor coil temperature from the temperature and pressure lookup table; and determining the difference between the first saturation pressure and the second saturation pressure as the initial pressure difference.

[0007] Optionally, determining the reversing delay time of the air conditioner based on the initial pressure difference and the preset parameters includes: obtaining the pressure difference margin between the initial pressure difference and the minimum reversing pressure difference threshold, wherein the pressure difference margin is the difference between the initial pressure difference and the minimum reversing pressure difference threshold; and determining the reversing delay time based on the pressure difference margin, the pressure difference attenuation rate gain, and the delay compensation term.

[0008] Optionally, determining the commutation delay time based on the differential pressure margin, the differential pressure attenuation rate gain, and the delay compensation term includes: multiplying the differential pressure margin and the differential pressure attenuation rate gain to obtain an intermediate value; and adding the intermediate value to the delay compensation term to obtain the commutation delay time.

[0009] Optionally, controlling the reversing of the four-way valve of the air conditioner based on the reversing delay time includes: limiting the reversing delay time to obtain a target reversing delay time; starting the timing from the moment the compressor stops, and controlling the four-way valve to reversing when the timing reaches the target reversing delay time.

[0010] Optionally, the reversing delay time is limited to obtain a target reversing delay time, including: obtaining a first preset time and a second preset time, wherein the first preset time is greater than the second preset time; determining the time with the smaller value between the reversing delay time and the first preset time as the target time; and determining the time with the larger value between the target time and the second preset time as the target reversing delay time.

[0011] Optionally, before determining the initial pressure difference based on the temperature-pressure comparison table, the indoor coil temperature, and the outdoor coil temperature, the method further includes: obtaining historical operating parameters of the air conditioner under multiple preset operating conditions, the historical operating parameters including historical indoor coil temperature and historical outdoor coil temperature, as well as corresponding historical low-pressure saturation pressure and historical high-pressure saturation pressure; fitting a first mapping curve of the historical indoor coil temperature and the historical low-pressure saturation pressure based on the correspondence between the historical indoor coil temperature and the historical low-pressure saturation pressure; fitting a second mapping curve of the historical outdoor coil temperature and the historical high-pressure saturation pressure based on the correspondence between the historical outdoor coil temperature and the historical high-pressure saturation pressure; and constructing the temperature-pressure comparison table based on the first mapping curve and the second mapping curve.

[0012] According to another aspect of this application, a control device for air conditioner reversing is provided, comprising: a first acquisition unit, configured to acquire indoor coil temperature, outdoor coil temperature, and preset parameters after the defrost flag of the air conditioner is released and the compressor stops, the preset parameters including a minimum reversing pressure difference threshold, a pressure difference decay rate gain, and a delay compensation term, wherein the indoor coil temperature corresponds to the saturation temperature of the fluid on the condenser side, and the outdoor coil temperature corresponds to the saturation temperature of the fluid on the evaporator side; a determination unit, configured to determine an initial pressure difference based on a preset saturation temperature and pressure lookup table, the indoor coil temperature, and the outdoor coil temperature, wherein the preset saturation temperature and pressure lookup table reflects: a first mapping relationship between the saturation temperature of the fluid on the evaporator side and the corresponding low saturation pressure, and a second mapping relationship between the saturation temperature of the fluid on the condenser side and the corresponding high saturation pressure; and a control unit, configured to determine the reversing delay time of the air conditioner based on the initial pressure difference and the preset parameters, and control the reversing of the four-way valve of the air conditioner based on the reversing delay time.

[0013] According to another aspect of this application, a computer-readable storage medium is provided, the computer-readable storage medium including a stored program, wherein, when the program is executed, it controls the device where the computer-readable storage medium is located to perform any of the aforementioned air conditioning commutation control methods.

[0014] According to another aspect of this application, an electronic device is provided, comprising: one or more processors, a memory, and one or more programs, wherein the one or more programs are stored in the memory and configured to be executed by the one or more processors, the one or more programs including a control method for performing any of the described air conditioning commutation methods.

[0015] Applying the technical solution of this application, after the defrost flag of the air conditioner is released and the compressor stops, the indoor coil temperature, outdoor coil temperature, and preset parameters are obtained. The preset parameters include a minimum reversing pressure difference threshold, a pressure difference decay rate gain, and a delay compensation term. The indoor coil temperature corresponds to the saturation temperature of the fluid on the condenser side, and the outdoor coil temperature corresponds to the saturation temperature of the fluid on the evaporator side. Based on the preset saturation temperature and pressure comparison table, the indoor coil temperature, and the outdoor coil temperature, the initial pressure difference is determined. The preset saturation temperature and pressure comparison table reflects: a first mapping relationship between the saturation temperature of the fluid on the evaporator side and the corresponding low saturation pressure, and a second mapping relationship between the saturation temperature of the fluid on the condenser side and the corresponding high saturation pressure. The reversing delay time of the air conditioner is determined according to the initial pressure difference and the preset parameters, and the reversing of the four-way valve of the air conditioner is controlled based on the reversing delay time. In this solution, after the air conditioner defrosts and the compressor stops, the high and low pressure saturation pressure difference (initial pressure difference) is calculated by using the indoor and outdoor coil temperatures and referring to a table based on the refrigerant saturation characteristics. Based on this pressure difference and preset pressure difference decay rate gain, safety threshold, and delay compensation, a reversing delay time that matches the current operating conditions is dynamically calculated. This avoids the problems of premature reversing (large pressure difference, abnormal noise) or late reversing (heating delay) caused by the traditional fixed delay due to failure to sense the pressure difference decay state. It ensures reliable reversing of the four-way valve, eliminates abnormal noise and indoor unit vibration, and shortens the heating recovery time, thus solving the problems of abnormal noise and slow heating recovery caused by fixed delay reversing after air conditioner defrost in the existing technology. Attached Figure Description

[0016] The accompanying drawings, which form part of this application, are used to provide a further understanding of this application. The illustrative embodiments and descriptions of this application are used to explain this application and do not constitute an undue limitation of this application. In the drawings:

[0017] Figure 1 A hardware structure block diagram of a mobile terminal for performing a control method for air conditioning commutation according to an embodiment of this application is shown.

[0018] Figure 2 A schematic flowchart of a control method for air conditioning reversing according to an embodiment of this application is shown;

[0019] Figure 3 A flowchart of a specific air conditioning commutation control method according to an embodiment of this application is shown;

[0020] Figure 4 A schematic diagram of an air conditioning commutation control system according to an embodiment of this application is shown;

[0021] Figure 5 A structural block diagram of an air conditioning reversing control device according to an embodiment of this application is shown.

[0022] The above figures include the following reference numerals:

[0023] 102. Processor; 104. Memory; 106. Transmission device; 108. Input / output device. Detailed Implementation

[0024] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. This application will now be described in detail with reference to the accompanying drawings and embodiments.

[0025] To enable those skilled in the art to better understand the present application, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present application, and not all embodiments. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative effort should fall within the scope of protection of the present application.

[0026] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for the embodiments of this application described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0027] As described in the background section, existing air conditioner reversing control methods suffer from abnormal noise caused by excessive pressure difference when the four-way valve reverses after defrosting, and slow heating recovery due to the inability of the fixed delay strategy to adapt to varying operating conditions. To address the problems of abnormal noise and slow heating recovery caused by fixed delay reversing after defrosting in existing air conditioners, embodiments of this application provide an air conditioner reversing control method, an air conditioner reversing control device, a computer-readable storage medium, and an electronic device.

[0028] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention.

[0029] The methods and embodiments provided in this application can be executed on a mobile terminal, computer terminal, or similar computing device. Taking running on a mobile terminal as an example, Figure 1This is a hardware structure block diagram of a mobile terminal for an air conditioning commutation control method according to an embodiment of the present invention. Figure 1 As shown, a mobile terminal may include one or more ( Figure 1 Only one is shown in the diagram. A processor 102 (which may include, but is not limited to, a microprocessor MCU or a programmable logic device FPGA, etc.) and a memory 104 for storing data are also shown. The mobile terminal may further include a transmission device 106 for communication functions and an input / output device 108. Those skilled in the art will understand that... Figure 1 The structure shown is for illustrative purposes only and does not limit the structure of the mobile terminal described above. For example, the mobile terminal may also include components that are more... Figure 1 The more or fewer components shown, or having the same Figure 1 The different configurations shown.

[0030] The memory 104 can be used to store computer programs, such as application software programs and modules, like the computer program corresponding to the air conditioning reversing control method in this embodiment of the invention. The processor 102 executes various functional applications and data processing by running the computer program stored in the memory 104, thereby implementing the above-described method. The memory 104 may include high-speed random access memory and non-volatile memory, such as one or more magnetic storage devices, flash memory, or other non-volatile solid-state memory. In some instances, the memory 104 may further include memory remotely located relative to the processor 102, and these remote memories can be connected to the mobile terminal via a network. Examples of the aforementioned networks include, but are not limited to, the Internet, corporate intranets, local area networks, mobile communication networks, and combinations thereof. The transmission device 106 is used to receive or send data via a network. Specific examples of the aforementioned networks may include wireless networks provided by the mobile terminal's communication provider. In one example, the transmission device 106 includes a network interface controller (NIC), which can be connected to other network devices via a base station to communicate with the Internet. In one example, the transmission device 106 may be a radio frequency (RF) module, which is used to communicate with the Internet wirelessly.

[0031] This embodiment provides a control method for air conditioning reversing that runs on a mobile terminal, computer terminal, or similar computing device. It should be noted that the steps shown in the flowchart in the accompanying drawings can be executed in a computer system such as a set of computer-executable instructions. Also, although the logical order is shown in the flowchart, in some cases, the steps shown or described can be executed in a different order than that shown here.

[0032] Figure 2 This is a flowchart illustrating the air conditioning reversing control method according to an embodiment of this application. Figure 2 As shown, the method includes the following steps:

[0033] Step S201: After the defrost flag of the air conditioner is released and the compressor stops, the indoor coil temperature, the outdoor coil temperature and preset parameters are obtained. The preset parameters include the minimum commutation pressure difference threshold, the pressure difference decay rate gain and the delay compensation term. The indoor coil temperature corresponds to the saturation temperature of the fluid on the condenser side and the outdoor coil temperature corresponds to the saturation temperature of the fluid on the evaporator side.

[0034] Specifically, the heating and defrosting functions of an air conditioner are achieved by changing the refrigerant flow direction through the reversing of a four-way valve. After the air conditioner completes the defrosting operation, it releases the defrost flag and stops the compressor. At this point, the air conditioner is in a critical transition phase from cooling mode to heating mode. Although the compressor has stopped, the four-way valve has not yet reversed, and the refrigerant circulation continues to maintain the cooling state during defrosting: the outdoor heat exchanger, acting as an evaporator, continuously absorbs heat to melt the frost layer, while the indoor heat exchanger, acting as a condenser, releases heat. Therefore, at the instant the compressor stops, the indoor coil temperature reflects the saturation temperature of the refrigerant on the condenser side, i.e., the thermodynamic state on the high-pressure side of the system; while the outdoor coil temperature corresponds to the saturation temperature of the refrigerant on the evaporator side, i.e., the thermodynamic state on the low-pressure side of the system.

[0035] At this moment, the real-time temperature values ​​of the indoor and outdoor coils are acquired, and three preset key control parameters are invoked: minimum switching differential pressure threshold, differential pressure decay rate gain, and delay compensation term. The minimum switching differential pressure threshold is the minimum pressure difference required to ensure reliable switching of the four-way valve. This value is typically slightly higher than the measured minimum operating differential pressure of the four-way valve to allow for a safety margin. The differential pressure decay rate gain characterizes the rate at which the pressure difference between the high and low pressure systems naturally decays after the compressor stops. This parameter is closely related to system characteristics such as pipe length, heat exchanger heat capacity, and refrigerant type. The delay compensation term is a correction for inherent system response delay, thermal inertia, or control errors, used to compensate for calculation deviations caused by environmental or model differences. These three parameters are constants calibrated through extensive experiments before leaving the factory and are fixed in the controller, independent of real-time sensing, thus requiring no additional hardware cost.

[0036] After the air conditioner defrost flag is released and the compressor stops, the indoor and outdoor coil temperatures are obtained. Based on the saturation temperatures of the condenser and evaporator sides, respectively, the initial pressure difference can be calculated. Combined with the minimum commutation pressure difference threshold, pressure difference decay rate gain, and delay compensation term, consistent and quantifiable core input parameters are provided for subsequent dynamic calculation of accurate commutation delay.

[0037] Step S202: Based on the preset saturation temperature and pressure comparison table, the indoor coil temperature and the outdoor coil temperature, determine the initial pressure difference. The preset saturation temperature and pressure comparison table reflects: the first mapping relationship between the saturation temperature of the evaporator-side fluid and the corresponding low saturation pressure, and the second mapping relationship between the saturation temperature of the condenser-side fluid and the corresponding high saturation pressure.

[0038] Specifically, in the transient phase after the air conditioner finishes defrosting and the compressor stops, the refrigerant inside is still in a residual state of the refrigeration cycle. At this time, the indoor heat exchanger acts as a condenser, and its coil temperature reflects the saturation temperature of the refrigerant on the high-pressure side; the outdoor heat exchanger acts as an evaporator, and its coil temperature corresponds to the saturation temperature of the refrigerant on the low-pressure side. To accurately calculate the current high-low pressure difference, the obtained indoor and outdoor coil temperatures are used in conjunction with a preset saturation temperature-pressure reference table for mapping calculation. This preset saturation temperature-pressure reference table is a mapping relationship established based on the thermodynamic properties of the refrigerant through experiments or standard data, recording the corresponding saturation pressure values ​​at different saturation temperatures, and is the core basis for sensorless pressure difference estimation.

[0039] The preset saturation temperature and pressure reference table includes two independent mapping relationships: the first is the mapping relationship between the saturation temperature of the fluid on the evaporator side and the corresponding low saturation pressure, which is used to convert the outdoor coil temperature into the saturation pressure on the low-pressure side of the system; the second is the mapping relationship between the saturation temperature of the fluid on the condenser side and the corresponding high saturation pressure, which is used to convert the indoor coil temperature into the saturation pressure on the high-pressure side of the system.

[0040] By consulting tables to obtain the corresponding high and low saturation pressures, the difference between the two yields the initial pressure difference at the moment defrosting ends. This initial pressure difference characterizes the energy difference between the high and low pressure of the refrigerant in the system at the instant the compressor stops. A larger initial pressure difference indicates a more drastic pressure difference in the refrigerant, resulting in a longer time required for natural pressure relief; conversely, a smaller initial pressure difference results in a shorter waiting time for reversal. This initial pressure difference serves as the basis for calculating the reversal delay, transforming the control strategy from a traditional fixed-delay empirical approach to a dynamic response based on actual thermodynamic states. This facilitates precise adaptive control of the four-way valve's reversal timing.

[0041] Step S203: Determine the reversing delay time of the air conditioner based on the initial pressure difference and the preset parameters, and control the reversing of the four-way valve of the air conditioner based on the reversing delay time.

[0042] Specifically, after determining the initial pressure difference at the moment defrosting ends, a model is constructed based on preset parameters (minimum switching pressure difference threshold, pressure difference decay rate gain, and delay compensation term) to calculate the optimal delay time required from compressor shutdown to four-way valve switching. The minimum switching pressure difference threshold ensures that the system maintains sufficient pressure difference to reliably drive the four-way valve during switching, preventing valve core jamming or switching failure due to excessively low pressure difference. The pressure difference decay rate gain describes the rate of natural pressure decay over time; this parameter is typically calibrated experimentally to reflect the combined effects of different compressor models' pipe volumes, refrigerant charge, and heat exchanger thermal inertia. The delay compensation term corrects for inherent system response delays, such as pipe heat conduction lag or valve body mechanical response hysteresis, ensuring the calculated results match the actual switching behavior. When the timer reaches the calculated switching delay time, a switching command is issued, driving the four-way valve to switch the flow path, and simultaneously restarting the compressor to resume heating operation. This control logic avoids the severe impact and abnormal noise caused by excessively short delays in traditional fixed-delay strategies, or the delay in heating recovery caused by excessively long delays, making the commutation process both smooth and reliable, as well as highly efficient and energy-saving.

[0043] The switching delay time is dynamically calculated based on the initial differential pressure and preset parameters, and the switching timing of the four-way valve is precisely controlled accordingly. This achieves the matching between the switching action and the actual differential pressure decay state, avoiding the switching shock or response lag caused by the fixed delay strategy. Thus, the reliability and stability of the switching process are improved without adding new hardware.

[0044] In this embodiment, after the air conditioner defrosts and the compressor stops, the high and low pressure saturation pressure difference (initial pressure difference) is calculated by using the indoor and outdoor coil temperatures and referring to a table based on the refrigerant saturation characteristics. Based on this pressure difference and preset pressure difference decay rate gain, safety threshold, and delay compensation, a reversing delay time matching the current operating condition is dynamically calculated. This avoids the problems of premature reversing (large pressure difference, abnormal noise) or late reversing (heating delay) caused by the traditional fixed delay due to failure to sense the pressure difference decay state. It ensures reliable reversing of the four-way valve, eliminates abnormal noise and indoor unit vibration, and shortens the heating recovery time, thereby solving the problems of abnormal noise and slow heating recovery caused by fixed delay reversing after air conditioner defrost in the prior art.

[0045] In the specific implementation process, the initial pressure difference is determined based on the temperature and pressure comparison table, the indoor coil temperature and the outdoor coil temperature, including: matching the first saturation pressure corresponding to the indoor coil temperature and the second saturation pressure corresponding to the outdoor coil temperature from the temperature and pressure comparison table; and determining the difference between the first saturation pressure and the second saturation pressure as the initial pressure difference.

[0046] Specifically, the temperature-pressure lookup table stores the equilibrium pressure values ​​of the target refrigerant at different saturation temperatures. The first and second saturation pressures, corresponding to the indoor and outdoor coil temperatures respectively, are retrieved from the table. This lookup and matching process converts temperature data into pressure parameters that directly reflect the high and low pressure states within the system, providing a physical benchmark consistent with thermodynamic laws for subsequent control decisions. After obtaining the first and second saturation pressures, the difference between them is calculated to obtain the initial system pressure difference at the moment defrosting ends.

[0047] By using a temperature-pressure comparison table, the real-time collected coil temperature is accurately mapped to the high and low pressure saturation pressures, and the initial pressure difference is quantified by the difference between the two pressures. This effectively overcomes the limitation that a single temperature parameter cannot directly reflect the true stress state of the system. This embodiment can quickly generate a pressure difference benchmark that conforms to the physical properties of the refrigerant during the compressor shutdown transient without the need for additional pressure sensors. This not only reduces the overall hardware cost and the difficulty of on-site calibration, but also ensures the certainty and anti-interference of the pressure difference data, providing a reliable data foundation for the accurate decision-making of subsequent control logic.

[0048] In some embodiments of this application, determining the commutation delay time of the air conditioner based on the initial pressure difference and the preset parameters includes: obtaining the pressure difference margin between the initial pressure difference and the minimum commutation pressure difference threshold, wherein the pressure difference margin is the difference between the initial pressure difference and the minimum commutation pressure difference threshold; and determining the commutation delay time based on the pressure difference margin, the pressure difference attenuation rate gain, and the delay compensation term.

[0049] Specifically, the core of this embodiment lies in introducing a differential pressure margin as a benchmark for dynamic adjustment. First, the initial differential pressure determined at the moment defrosting ends is subtracted from a preset minimum reversing differential pressure threshold; the resulting difference is the differential pressure margin. This margin represents the remaining pressure beyond the safe reversing threshold, reflecting the total pressure required for reliable switching of the four-way valve. By pre-setting a basic safety threshold, the focus can be placed on the variable pressure range under actual operating conditions, making subsequent time calculations more closely match the system's actual pressure relief requirements and avoiding benchmark offset issues that may arise from directly substituting absolute pressure values ​​into the formula.

[0050] By introducing differential pressure margin as a control benchmark, the absolute initial pressure is transformed into a relative pressure range that needs to be attenuated, making the calculation of the switching delay time closely match the actual pressure relief requirements, thus overcoming the limitations of the fixed delay strategy in adapting to varying operating conditions. By combining the synergistic calculation of differential pressure attenuation rate gain and delay compensation term, a precise mapping from the theoretical pressure relief cycle to the actual control command is achieved. This ensures that the system differential pressure is always higher than the safety threshold during the switching of the four-way valve, guaranteeing the reliability of the switching, while effectively avoiding the dual defects of high differential pressure impact noise and low differential pressure response hysteresis.

[0051] Further, determining the commutation delay time based on the aforementioned differential pressure margin, the aforementioned differential pressure attenuation rate gain, and the aforementioned delay compensation term includes: multiplying the aforementioned differential pressure margin and the aforementioned differential pressure attenuation rate gain to obtain an intermediate value; and adding the aforementioned intermediate value to the aforementioned delay compensation term to obtain the aforementioned commutation delay time.

[0052] Specifically, the differential pressure margin is multiplied by the differential pressure decay rate gain to obtain an intermediate value. Essentially, this step converts the pressure margin to be decayed into a theoretical natural pressure relief time using a calibration coefficient, establishing a direct mapping between the pressure physical quantity and the time dimension. Subsequently, the intermediate value is added to the delay compensation term to obtain the final commutation delay time. This step corrects inherent non-ideal delays, encompassing sensor sampling periods, microcontroller instruction scheduling time, drive circuit response time, and the inherent hysteresis of the four-way valve core's mechanical movement.

[0053] By multiplying the differential pressure margin by the differential pressure decay rate gain and adding a delay compensation term, the required pressure margin to decay is converted into a theoretical pressure relief time. Simultaneously, the compensation term accurately corrects inherent delays in signal sampling, drive response, and valve core mechanical movement. Through this embodiment, the four-way valve can accurately trigger switching in any operating state when the differential pressure falls back to the safe threshold, effectively ensuring the accuracy of the switching timing and the reliability of the operation.

[0054] In some embodiments of this application, controlling the reversing of the four-way valve of the air conditioner based on the reversing delay time includes: limiting the reversing delay time to obtain a target reversing delay time; starting the timing from the moment the compressor stops, and controlling the four-way valve to reversing when the timing reaches the target reversing delay time.

[0055] Furthermore, the aforementioned reversing delay time is subjected to a limiting process to obtain a target reversing delay time, including: obtaining a first preset time and a second preset time, wherein the first preset time is greater than the second preset time; determining the time with the smaller value between the aforementioned reversing delay time and the first preset time as the target time; and determining the time with the larger value between the aforementioned target time and the second preset time as the target reversing delay time.

[0056] Specifically, firstly, two preset thresholds are used as control boundaries: a first preset time as the upper limit threshold and a second preset time as the lower limit threshold, with the first preset time being greater than the second preset time. The smaller value between the commutation delay time and the upper limit threshold is taken as the target time, effectively intercepting abnormally long delays that may be caused by extreme operating conditions, sensor transient noise, or parameter calibration deviations. Then, the larger value between the target time and the lower limit threshold is taken as the target commutation delay time, completely eliminating excessively short delays that may cause commutation hydraulic shock and indoor unit vibration.

[0057] By limiting the upper and lower thresholds, the dynamically calculated reversing delay time is strictly restricted within a preset safe range, effectively preventing extreme values ​​from exceeding the limit due to sensor transient interference, extreme operating conditions, or parameter calibration deviations. The upper threshold ensures sufficient pressure relief time to prevent impacts and indoor unit vibration and abnormal noises during high-pressure differential reversal of the four-way valve; the lower threshold prevents excessively long waiting times, thus avoiding delays in heating recovery after defrosting.

[0058] After obtaining the target commutation delay time, a timer is started with the instant the compressor stops as the zero point. When the accumulated time reaches the target commutation delay time, a drive signal is immediately output to trigger the four-way valve coil. This timing triggering mechanism has clear timing control, which can ensure accurate synchronization between the commutation action and the natural decay process of the system pressure.

[0059] By employing amplitude limiting constraints and timed triggering mechanisms, the dynamically calculated commutation delay is transformed into a safe and controllable command, effectively preventing extreme value overflows caused by sudden changes in operating conditions or data noise. This avoids hydraulic shocks and abnormal noises caused by excessively short delays, as well as delayed heating recovery caused by excessively long delays. Using compressor shutdown as the timing starting point ensures synchronization between the timing reference and the system's natural depressurization process. Furthermore, the decision logic that executes upon reaching the target time provides clear determinism and real-time performance for the commutation action, eliminating the need for complex pressure closed-loop monitoring or lengthy state machine polling. This embodiment achieves a smooth transition of the system after defrosting and rapid heating response without requiring additional hardware, effectively improving the overall operational stability and end-user experience.

[0060] In some embodiments of this application, before determining the initial pressure difference based on the temperature-pressure comparison table, the indoor coil temperature, and the outdoor coil temperature, the method further includes: obtaining historical operating parameters of the air conditioner under multiple preset operating conditions, the historical operating parameters including historical indoor coil temperature and historical outdoor coil temperature, and corresponding historical low-pressure saturation pressure and historical high-pressure saturation pressure; fitting a first mapping curve of the historical indoor coil temperature and the historical low-pressure saturation pressure based on the correspondence between the historical indoor coil temperature and the historical low-pressure saturation pressure; fitting a second mapping curve of the historical outdoor coil temperature and the historical high-pressure saturation pressure based on the correspondence between the historical outdoor coil temperature and the historical high-pressure saturation pressure; and constructing the temperature-pressure comparison table based on the first mapping curve and the second mapping curve.

[0061] Specifically, the process begins by acquiring multiple sets of historical operating parameters for the air conditioner under typical cooling, heating, and defrosting conditions, simultaneously recording the actual indoor and outdoor coil temperatures and their corresponding high and low pressure saturation values. Then, the data from both sides are independently fitted: the indoor coil temperature and low pressure saturation pressure are mapped to a first mapping curve, and the outdoor coil temperature and high pressure saturation pressure are mapped to a second mapping curve. Through dual-channel curve fitting, the nonlinear temperature and pressure deviations caused by superheat, subcooling, pressure drop along the pipeline, and non-ideal heat transfer characteristics of the heat exchanger during actual circulation are accurately captured. Finally, the fitting results can be discretized into a high-dimensional lookup table, constructing a temperature and pressure comparison table specific to this model or production batch.

[0062] By introducing a historical data fitting mechanism, and using independently constructed first and second mapping curves to replace the traditional refrigerant thermodynamic property table, this effectively compensates for the nonlinear distortion of temperature and pressure caused by factors such as pipeline pressure drop, non-ideal heat transfer in heat exchangers, uneven distribution of superheat / subcooling, sensor installation deviation, and manufacturing tolerances in actual refrigeration cycles. This improves the physical accuracy and estimation precision of the initial pressure difference inversion at the end of defrosting. Furthermore, this purely software calibration method requires no additional hardware and can achieve specific calibration for different models and continuous optimization of parameters throughout the entire lifecycle, effectively avoiding the accumulation of lookup errors caused by changes in ambient temperature or equipment aging. This fundamentally ensures the accurate determination of the four-way valve's switching timing.

[0063] To enable those skilled in the art to better understand the technical solution of this application, the implementation process of the air conditioning commutation control method of this application will be described in detail below with reference to specific embodiments.

[0064] This embodiment relates to a specific air conditioning reversing control method, applicable to the intelligent reversing control of inverter split air conditioners, and particularly suitable for the four-way valve reversing process after defrosting in low-temperature heating mode. Figure 3 As shown, the method includes:

[0065] In the last second before defrosting ends, the controller reads the indoor coil temperature T_in (condenser temperature) and the outdoor coil temperature T_out (evaporator temperature). Based on the saturation temperature-pressure lookup table for the refrigerant (e.g., R32) (a preset saturation temperature-pressure lookup table), it looks up the corresponding saturation pressures P_low (first saturation pressure) and P_high (second saturation pressure), and calculates the initial pressure difference P_max = P_high - P_low. The defrost flag can be deactivated by monitoring the outdoor unit condenser coil temperature; for example, if the outdoor coil temperature reaches 12°C, the defrost flag can be deactivated. The compressor then stops, and the system enters the natural pressure relief phase. The controller calculates the commutation delay time using the following simplified linear formula based on preset parameters: t = K × (P_max - P_safe) + b, where P_safe = 0.15 MPa, the safety pressure difference (minimum commutation pressure difference threshold) to ensure commutation reliability; K = 40 s / MPa, representing the pressure difference decay rate gain; and b = 12 s, the delay compensation term. The reversing delay time t is limited after calculation: t = max(min(t, 60), 15). That is, the delay time is controlled between 15 and 60 seconds to prevent abnormal noise due to being too short or affecting comfort due to being too long. After the set time is reached, the controller outputs a signal to drive the four-way valve to reverse, and then starts the compressor to resume heating operation.

[0066] To directly verify the engineering feasibility and control accuracy of the technical solution proposed in this application, six typical defrosting conditions covering extreme cold, normal winter, and early spring transition were selected for whole-machine bench testing. The indoor and outdoor coil temperatures were recorded one second before the end of defrosting. The initial pressure difference P_max was obtained by converting the saturated pressure and then used to calculate the target reversing delay time using preset parameters. The timed reversing was then performed within the limited range of [15, 60] s. The key measured data are shown in Table 1.

[0067] Table 1

[0068]

[0069] As shown in Table 1, under different combinations of ambient temperature and set temperature, the adaptive delay command of 19-32s can be stably output. The measured pressure difference at the moment of commutation is concentrated in the range of 0.35-0.38MPa, and the corresponding acoustic test noise level is "slight". There is no "bang" impact sound or abnormal vibration of the indoor unit under the traditional fixed delay strategy. At the same time, the commutation pressure difference is strictly greater than the safety threshold of 0.15MPa under all operating conditions.

[0070] The above verification results show that the air conditioning commutation control method of this application achieves precise synchronization between commutation timing and system depressurization process. This solution completely solves the problem of abnormal noise during defrosting commutation while ensuring extremely high commutation reliability and excellent adaptability to operating conditions.

[0071] In the above embodiments of this application, the specific parameter values ​​listed (such as P_safe=0.15MPa, K=40s / MPa, b=12s, delay limit range [15, 60]s, etc.) are only engineering tuning results based on typical variable frequency air conditioner models and mainstream four-way valve characteristics. Those skilled in the art should understand that different refrigerant types, compressor displacement, four-way valve drive coil specifications, system piping layout, and target market noise standards will all lead to deviations in the optimal control parameters. Therefore, this application is not limited to the above fixed values; the following provides several equivalent parameter configuration schemes and their applicable boundaries:

[0072] (1) Alternative values ​​for the minimum commutation differential pressure threshold P_safe:

[0073] In practical applications, P_safe can be fine-tuned based on the operating characteristic curve provided by the four-way valve manufacturer. For example, when using a new type of proportional four-way valve with low starting torque, P_safe can be lowered to 0.14 MPa; if the system has significant pipeline resistance or the increased viscosity of the low-temperature refrigerant leads to an increased pressure drop, P_safe can be raised to 0.16 MPa or even higher. The core of setting this threshold is to reserve an engineering safety margin higher than the minimum differential pressure required for the actual operation of the valve core. As long as the system differential pressure at the moment of switching triggering always meets the physical requirements for reliable valve switching, the above numerical adjustments will not affect the core control logic of this application, which is "ensuring switching reliability based on differential pressure prediction".

[0074] (2) Regarding alternative configurations of coefficients K and b in the linear prediction model:

[0075] The gain coefficient K∈[30, 50]s / MPa and the basic compensation term b∈[10, 15]s constitute an effective parameter space. For high-end home models that emphasize extreme quietness, K=50s / MPa and b=15s can be used to extend the pressure relief time; for high-efficiency energy-saving models that focus on rapid heating recovery, K=30s / MPa and b=10s can be used to reduce the ineffective waiting period; for northern heating models or large commercial multi-split systems operating in ultra-low temperature environments, K and b can also be amplified simultaneously to match the longer system thermal inertia. The above-mentioned configurations can be achieved simply by presetting the parameter table in the controller firmware or by sending the calibration file via cloud OTA, which is entirely within the scope of the technical solutions covered by the claims of this application.

[0076] (3) Regarding the substitution range for the reversal delay time limit interval:

[0077] The aforementioned limiting window of [15, 60]s applies to conventional split-type household air conditioners. For applications in specialized models for extremely cold regions (-35℃) or large-capacity commercial chillers, due to the large refrigerant mass and significantly slower natural pressure relief rate, the delay limiting range can be widened to [10, 90]s or even further. This adjustment is merely an engineering adaptation to the system's physical response time and does not change the fundamental control architecture of "dynamic calculation + safety trimming + timed triggering."

[0078] (4) Implementation path of the simplified control strategy:

[0079] In some entry-level products where algorithmic computing power is limited or cost is extremely sensitive, the controller can also use the simplified formula t=K×P_max+b (without explicitly deducting P_safe) for delay calculation. In this case, although the anti-impact effect of P_safe is not directly reflected in the formula, it can be implicitly compensated by appropriately increasing the value of K or b through parameter tuning. Experimental verification shows that this simplified strategy can still achieve basic tracking of the differential pressure decay trend and adaptive adjustment of the commutation timing, and its technical effect is substantially the same as the main scheme of this application.

[0080] In summary, any equivalent substitutions or parameter optimizations made by those skilled in the art to the above thresholds, coefficients, amplitude limits, and formula structures without departing from the core inventive concept of "using the coil temperature at the end of defrosting to invert the system pressure difference and dynamically plan the switching timing accordingly" shall be considered as natural extensions of the technical solution of this application and shall be covered by the claims of this application.

[0081] This application also provides a control system for air conditioning reversing, the schematic diagram of which is shown below. Figure 4 As shown, the system mainly includes a compressor, an outdoor heat exchanger (acting as a condenser during defrosting), an indoor heat exchanger (acting as an evaporator during defrosting), an electronic expansion valve, and coil temperature sensors attached to the walls of the heat exchanger tubes on both sides. At the end of the heating defrosting cycle, the system temporarily switches to refrigeration cycle mode: the compressor compresses the refrigerant and discharges high-temperature, high-pressure gas, which flows through the pipeline to the outdoor heat exchanger, where it releases sensible and latent heat to melt the attached frost layer; subsequently, the liquid refrigerant flows through the electronic expansion valve for throttling and pressure reduction, enters the indoor heat exchanger to absorb heat and evaporate, and finally flows back to the compressor suction end to complete the cycle. At this time, the outdoor heat exchanger functions as a condenser, and the indoor heat exchanger functions as an evaporator. During defrosting, the refrigeration cycle mode is used. After the compressor compresses the refrigerant, it forms high-temperature, high-pressure gas, which passes through the outdoor unit condenser for defrosting. The outdoor unit condenser is equipped with coil temperature sensors; the detected temperature of the sensors can be estimated and converted into a pressure value, i.e., a high-pressure value.

[0082] This application also provides a control device for air conditioning reversing. It should be noted that the control device for air conditioning reversing in this application can be used to execute the control method for air conditioning reversing provided in this application. This device is used to implement the above embodiments and preferred embodiments; details already described will not be repeated. As used below, the term "module" can refer to a combination of software and / or hardware that implements a predetermined function. Although the device described in the following embodiments is preferably implemented in software, hardware implementation, or a combination of software and hardware, is also possible and contemplated.

[0083] The following describes the air conditioning reversing control device provided in the embodiments of this application.

[0084] Figure 5 This is a structural block diagram of an air conditioning reversing control device according to an embodiment of this application. Figure 5 As shown, the device includes a first acquisition unit 51, a determination unit 52, and a control unit 53. The first acquisition unit acquires the indoor coil temperature, the outdoor coil temperature, and preset parameters after the defrost flag of the air conditioner is released and the compressor stops. The preset parameters include a minimum reversing pressure difference threshold, a pressure difference decay rate gain, and a delay compensation term. The indoor coil temperature corresponds to the saturation temperature of the fluid on the condenser side, and the outdoor coil temperature corresponds to the saturation temperature of the fluid on the evaporator side. The determination unit determines the initial pressure difference based on a preset saturation temperature and pressure comparison table, the indoor coil temperature, and the outdoor coil temperature. The preset saturation temperature and pressure comparison table reflects a first mapping relationship between the saturation temperature of the fluid on the evaporator side and the corresponding low saturation pressure, and a second mapping relationship between the saturation temperature of the fluid on the condenser side and the corresponding high saturation pressure. The control unit determines the reversing delay time of the air conditioner based on the initial pressure difference and the preset parameters, and controls the reversing of the four-way valve of the air conditioner based on the reversing delay time.

[0085] In this embodiment, after the air conditioner defrosts and the compressor stops, the high and low pressure saturation pressure difference (initial pressure difference) is calculated by using the indoor and outdoor coil temperatures and referring to a table based on the refrigerant saturation characteristics. Based on this pressure difference and preset pressure difference decay rate gain, safety threshold, and delay compensation, a reversing delay time matching the current operating condition is dynamically calculated. This avoids the problems of premature reversing (large pressure difference, abnormal noise) or late reversing (heating delay) caused by the traditional fixed delay due to failure to sense the pressure difference decay state. It ensures reliable reversing of the four-way valve, eliminates abnormal noise and indoor unit vibration, and shortens the heating recovery time, thereby solving the problems of abnormal noise and slow heating recovery caused by fixed delay reversing after air conditioner defrost in the prior art.

[0086] In the specific implementation process, the determining unit shown includes a matching module and a first determining module. The matching module is used to match the first saturation pressure corresponding to the indoor coil temperature and the second saturation pressure corresponding to the outdoor coil temperature from the temperature and pressure comparison table; the first determining module is used to determine the difference between the first saturation pressure and the second saturation pressure as the initial pressure difference.

[0087] By using a temperature-pressure comparison table, the real-time collected coil temperature is accurately mapped to the high and low pressure saturation pressures, and the initial pressure difference is quantified by the difference between the two pressures. This effectively overcomes the limitation that a single temperature parameter cannot directly reflect the true stress state of the system. This embodiment can quickly generate a pressure difference benchmark that conforms to the physical properties of the refrigerant during the compressor shutdown transient without the need for additional pressure sensors. This not only reduces the overall hardware cost and the difficulty of on-site calibration, but also ensures the certainty and anti-interference of the pressure difference data, providing a reliable data foundation for the accurate decision-making of subsequent control logic.

[0088] In some embodiments of this application, the control unit includes an acquisition module and a second determination module. The acquisition module is used to acquire the pressure difference margin between the initial pressure difference and the minimum commutation pressure difference threshold, wherein the pressure difference margin is the difference between the initial pressure difference and the minimum commutation pressure difference threshold; the second determination module is used to determine the commutation delay time based on the pressure difference margin, the pressure difference attenuation rate gain, and the delay compensation term.

[0089] By introducing differential pressure margin as a control benchmark, the absolute initial pressure is transformed into a relative pressure range that needs to be attenuated, making the calculation of the switching delay time closely match the actual pressure relief requirements, thus overcoming the limitations of the fixed delay strategy in adapting to varying operating conditions. By combining the synergistic calculation of differential pressure attenuation rate gain and delay compensation term, a precise mapping from the theoretical pressure relief cycle to the actual control command is achieved. This ensures that the system differential pressure is always higher than the safety threshold during the switching of the four-way valve, guaranteeing the reliability of the switching, while effectively avoiding the dual defects of high differential pressure impact noise and low differential pressure response hysteresis.

[0090] Furthermore, the second determining module includes a first processing submodule and a second processing submodule. The first processing submodule is used to multiply the differential pressure margin and the differential pressure attenuation rate gain to obtain an intermediate value; the second processing submodule is used to add the intermediate value to the delay compensation term to obtain the commutation delay time.

[0091] By multiplying the differential pressure margin by the differential pressure decay rate gain and adding a delay compensation term, the required pressure margin to decay is converted into a theoretical pressure relief time. Simultaneously, the compensation term accurately corrects inherent delays in signal sampling, drive response, and valve core mechanical movement. Through this embodiment, the four-way valve can accurately trigger switching in any operating state when the differential pressure falls back to the safe threshold, effectively ensuring the accuracy of the switching timing and the reliability of the operation.

[0092] In some embodiments of this application, the control unit includes a processing module and a control module. The processing module is used to limit the reversing delay time to obtain a target reversing delay time; the control module is used to start timing from the moment the compressor stops, and control the four-way valve to reverse when the timing reaches the target reversing delay time.

[0093] Furthermore, the aforementioned processing module includes an acquisition submodule, a first determination submodule, and a second determination submodule. The acquisition submodule is used to acquire a first preset time and a second preset time, wherein the first preset time is greater than the second preset time; the first determination submodule is used to determine the time smaller between the reversing delay time and the first preset time as the target time; the second determination submodule is used to determine the time larger between the target time and the second preset time as the target reversing delay time.

[0094] By limiting the upper and lower thresholds, the dynamically calculated reversing delay time is strictly restricted within a preset safe range, effectively preventing extreme values ​​from exceeding the limit due to sensor transient interference, extreme operating conditions, or parameter calibration deviations. The upper threshold ensures sufficient pressure relief time to prevent impacts and indoor unit vibration and abnormal noises during high-pressure differential reversal of the four-way valve; the lower threshold prevents excessively long waiting times, thus avoiding delays in heating recovery after defrosting.

[0095] By employing amplitude limiting constraints and timed triggering mechanisms, the dynamically calculated commutation delay is transformed into a safe and controllable command, effectively preventing extreme value overflows caused by sudden changes in operating conditions or data noise. This avoids hydraulic shocks and abnormal noises caused by excessively short delays, as well as delayed heating recovery caused by excessively long delays. Using compressor shutdown as the timing starting point ensures synchronization between the timing reference and the system's natural depressurization process. Furthermore, the decision logic that executes upon reaching the target time provides clear determinism and real-time performance for the commutation action, eliminating the need for complex pressure closed-loop monitoring or lengthy state machine polling. This embodiment achieves a smooth transition of the system after defrosting and rapid heating response without requiring additional hardware, effectively improving the overall operational stability and end-user experience.

[0096] In some embodiments of this application, the above-mentioned apparatus further includes a second acquisition unit, a first processing unit, a second processing unit, and a construction unit. The second acquisition unit is used to acquire historical operating parameters of the air conditioner under multiple preset operating conditions before determining the initial pressure difference based on a temperature-pressure comparison table, the indoor coil temperature, and the outdoor coil temperature. These historical operating parameters include historical indoor coil temperatures, historical outdoor coil temperatures, and corresponding historical low-pressure saturation pressures and historical high-pressure saturation pressures. The first processing unit is used to fit a first mapping curve between the historical indoor coil temperature and the historical low-pressure saturation pressure based on the correspondence between them. The second processing unit is used to fit a second mapping curve between the historical outdoor coil temperature and the historical high-pressure saturation pressure based on the correspondence between them. The construction unit is used to construct the temperature-pressure comparison table based on the first mapping curve and the second mapping curve.

[0097] By introducing a historical data fitting mechanism, and using independently constructed first and second mapping curves to replace the traditional refrigerant thermodynamic property table, this effectively compensates for the nonlinear distortion of temperature and pressure caused by factors such as pipeline pressure drop, non-ideal heat transfer in heat exchangers, uneven distribution of superheat / subcooling, sensor installation deviation, and manufacturing tolerances in actual refrigeration cycles. This improves the physical accuracy and estimation precision of the initial pressure difference inversion at the end of defrosting. Furthermore, this purely software calibration method requires no additional hardware and can achieve specific calibration for different models and continuous optimization of parameters throughout the entire lifecycle, effectively avoiding the accumulation of lookup errors caused by changes in ambient temperature or equipment aging. This fundamentally ensures the accurate determination of the four-way valve's switching timing.

[0098] The aforementioned air conditioning reversing control device includes a processor and a memory. The first acquisition unit, determination unit, control unit, etc., are all stored as program units in the memory, and the processor executes the program units stored in the memory to achieve the corresponding functions. All of the above modules are located in the same processor; alternatively, the above modules may be located in different processors in any combination.

[0099] The memory may include non-permanent memory in computer-readable media, such as random access memory (RAM) and / or non-volatile memory, such as read-only memory (ROM) or flash RAM, and the memory includes at least one memory chip.

[0100] This invention provides a computer-readable storage medium including a stored program, wherein, when the program is executed, it controls the device containing the computer-readable storage medium to perform the air conditioning reversing control method.

[0101] This invention provides a processor for running a program, wherein the program executes the air conditioning reversing control method.

[0102] This invention provides a device including a processor, a memory, and a program stored in the memory and executable on the processor. When the processor executes the program, it implements the steps of the aforementioned air conditioning reversing control method. The device described herein can be a server, PC, PAD, mobile phone, etc.

[0103] This application also provides a computer program product that, when executed on a data processing device, is adapted to perform the steps of initializing the control method for the above-described air conditioning commutation.

[0104] It is obvious to those skilled in the art that the modules or steps of the present invention described above can be implemented using general-purpose computing devices. They can be centralized on a single computing device or distributed across a network of multiple computing devices. They can be implemented using computer-executable program code, and thus can be stored in a storage device for execution by a computing device. In some cases, the steps shown or described can be performed in a different order than those described herein, or they can be fabricated as separate integrated circuit modules, or multiple modules or steps can be fabricated as a single integrated circuit module. Thus, the present invention is not limited to any particular combination of hardware and software.

[0105] Those skilled in the art will understand that embodiments of this application can be provided as methods, systems, or computer program products. Therefore, this application can take the form of a completely hardware embodiment, a completely software embodiment, or an embodiment combining software and hardware aspects. Furthermore, this application can take the form of a computer program product embodied on one or more computer-usable storage media (including but not limited to disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.

[0106] This application is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of this application. It will be understood that each block of the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, special-purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, generate instructions for implementing the flowchart... Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0107] These computer program instructions may also be stored in a computer-readable storage medium that can direct a computer or other programmable data processing device to function in a particular manner, such that the instructions stored in the computer-readable storage medium produce an article of manufacture including instruction means, which are implemented in a process Figure 1 One or more processes and / or boxes Figure 1 The function specified in one or more boxes.

[0108] These computer program instructions may also be loaded onto a computer or other programmable data processing equipment to cause a series of operational steps to be performed on the computer or other programmable equipment to produce a computer-implemented process, thereby providing instructions that execute on the computer or other programmable equipment for implementing the process. Figure 1 One or more processes and / or boxes Figure 1 The steps of the function specified in one or more boxes.

[0109] In a typical configuration, a computing device includes one or more processors (CPU), input / output interfaces, network interfaces, and memory.

[0110] Memory may include non-persistent memory in computer-readable media, such as random access memory (RAM) and / or non-volatile memory, such as read-only memory (ROM) or flash RAM. Memory is an example of computer-readable media.

[0111] Computer-readable media include both permanent and non-permanent, removable and non-removable media that can store information using any method or technology. Information can be computer-readable instructions, data structures, modules of programs, or other data. Examples of computer storage media include, but are not limited to, phase-change memory (PRAM), static random access memory (SRAM), dynamic random access memory (DRAM), other types of random access memory (RAM), read-only memory (ROM), electrically erasable programmable read-only memory (EEPROM), flash memory or other memory technologies, CD-ROM, digital versatile optical disc (DVD) or other optical storage, magnetic tape, disk storage or other magnetic storage devices, or any other non-transferable medium that can be used to store information accessible by a computing device. As defined herein, computer-readable media does not include transient computer-readable media, such as modulated data signals and carrier waves.

[0112] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0113] It should also be noted that the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such process, method, article, or apparatus. Unless otherwise specified, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes that element.

[0114] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A control method for air conditioning commutation, characterized in that, include: After the defrost flag of the air conditioner is released and the compressor stops, the indoor coil temperature, the outdoor coil temperature, and preset parameters are obtained. The preset parameters include the minimum commutation pressure difference threshold, the pressure difference decay rate gain, and the delay compensation term. The indoor coil temperature corresponds to the saturation temperature of the fluid on the condenser side, and the outdoor coil temperature corresponds to the saturation temperature of the fluid on the evaporator side. Based on a preset saturation temperature and pressure comparison table, the indoor coil temperature and the outdoor coil temperature, the initial pressure difference is determined. The preset saturation temperature and pressure comparison table reflects: the first mapping relationship between the saturation temperature of the fluid on the evaporator side and the corresponding low saturation pressure, and the second mapping relationship between the saturation temperature of the fluid on the condenser side and the corresponding high saturation pressure. The reversing delay time of the air conditioner is determined based on the initial pressure difference and the preset parameters, and the reversing of the four-way valve of the air conditioner is controlled based on the reversing delay time.

2. The method according to claim 1, characterized in that, Based on the temperature and pressure comparison table, the indoor coil temperature, and the outdoor coil temperature, the initial pressure difference is determined, including: Match the first saturation pressure corresponding to the indoor coil temperature and the second saturation pressure corresponding to the outdoor coil temperature from the temperature and pressure comparison table; The difference between the first saturation pressure and the second saturation pressure is determined as the initial pressure difference.

3. The method according to claim 1, characterized in that, Determining the reversing delay time of the air conditioner based on the initial pressure difference and the preset parameters includes: Obtain the pressure differential margin between the initial pressure differential and the minimum commutation pressure differential threshold, wherein the pressure differential margin is the difference between the initial pressure differential and the minimum commutation pressure differential threshold; The commutation delay time is determined based on the differential pressure margin, the differential pressure attenuation rate gain, and the delay compensation term.

4. The method according to claim 3, characterized in that, The commutation delay time is determined based on the differential pressure margin, the differential pressure attenuation rate gain, and the delay compensation term, including: Multiply the differential pressure margin and the differential pressure attenuation rate gain to obtain an intermediate value; The intermediate value is added to the delay compensation term to obtain the commutation delay time.

5. The method according to claim 1, characterized in that, Controlling the switching of the four-way valve of the air conditioner based on the switching delay time includes: The commutation delay time is limited to obtain the target commutation delay time; The timing starts from the moment the compressor stops, and when the timing reaches the target reversing delay time, the four-way valve is controlled to reverse.

6. The method according to claim 5, characterized in that, The target commutation delay time is obtained by limiting the commutation delay time, including: Obtain a first preset time and a second preset time, wherein the first preset time is greater than the second preset time; The time that is smaller between the reversal delay time and the first preset time is determined as the target time; The time with the larger value between the target time and the second preset time is determined as the target reversal delay time.

7. The method according to claim 1, characterized in that, Before determining the initial pressure difference based on a temperature-pressure comparison table, the indoor coil temperature, and the outdoor coil temperature, the method further includes: The historical operating parameters of the air conditioner under multiple preset operating conditions are obtained. The historical operating parameters include historical indoor coil temperature and historical outdoor coil temperature, as well as the corresponding historical low-pressure saturation pressure and historical high-pressure saturation pressure. Based on the correspondence between the historical indoor coil temperature and the historical low-pressure saturation pressure, a first mapping curve between the historical indoor coil temperature and the historical low-pressure saturation pressure is obtained by fitting. Based on the correspondence between the historical outdoor coil temperature and the historical high-pressure saturation pressure, a second mapping curve between the historical outdoor coil temperature and the historical high-pressure saturation pressure is obtained by fitting. The temperature and pressure comparison table is constructed based on the first mapping curve and the second mapping curve.

8. A control device for air conditioning reversing, characterized in that, include: The first acquisition unit is used to acquire the indoor coil temperature, the outdoor coil temperature, and preset parameters after the defrost flag of the air conditioner is released and the compressor stops. The preset parameters include the minimum commutation pressure difference threshold, the pressure difference decay rate gain, and the delay compensation term. The indoor coil temperature corresponds to the saturation temperature of the fluid on the condenser side, and the outdoor coil temperature corresponds to the saturation temperature of the fluid on the evaporator side. The determining unit is used to determine the initial pressure difference based on a preset saturation temperature and pressure comparison table, the indoor coil temperature and the outdoor coil temperature. The preset saturation temperature and pressure comparison table reflects: a first mapping relationship between the saturation temperature of the evaporator-side fluid and the corresponding low saturation pressure, and a second mapping relationship between the saturation temperature of the condenser-side fluid and the corresponding high saturation pressure. The control unit is used to determine the reversing delay time of the air conditioner based on the initial pressure difference and the preset parameters, and to control the reversing of the four-way valve of the air conditioner based on the reversing delay time.

9. A computer-readable storage medium, characterized in that, The computer-readable storage medium includes a stored program, wherein, when the program is executed, it controls the device containing the computer-readable storage medium to perform the air conditioning reversing control method according to any one of claims 1 to 7.

10. An electronic device, characterized in that, include: One or more processors, a memory, and one or more programs, wherein the one or more programs are stored in the memory and configured to be executed by the one or more processors, the one or more programs including a control method for performing an air conditioning reversing control method according to any one of claims 1 to 7.

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