A vehicle air conditioning control method, electronic equipment and storage medium

Abstract

The application discloses a vehicle air conditioner control method, an electronic device and a storage medium, and relates to the technical field of vehicles. The method comprises the following steps: in response to an air conditioner starting instruction, collecting an outside environment temperature, and determining whether the outside environment temperature is in a preset working condition temperature interval; if yes, starting a compressor, and determining a target air outlet temperature of an indoor heat exchanger according to temperature control information contained in the air conditioner starting instruction; and determining the opening degree of a second expansion valve according to the actual air outlet temperature and the target air outlet temperature, so as to realize the control of the air outlet temperature. The application realizes the dynamic distribution of refrigerant circulation through the multi-heat exchanger collaborative architecture and the intelligent algorithm, and synchronously optimizes the evaporation temperature stability and the accurate control of the air outlet temperature without the intervention of a PTC.

Description

Technical Field

[0001] This application relates to the field of vehicle technology, and in particular to a vehicle air conditioning control method, electronic device and storage medium. Background Technology

[0002] With the rapid development of new energy vehicles, the demand for energy efficiency and comfort in vehicle air conditioning systems is increasing. Traditional single-cooling air conditioning systems rely on electric auxiliary heating devices (PTC, Positive Temperature Coefficient) for temperature regulation, which leads to problems such as excessive energy consumption in low-temperature environments. While heat pump systems can improve heating efficiency, they still require PTC auxiliary heating during high-temperature dehumidification, and there is an inherent contradiction in low-temperature dehumidification conditions, such as frequent switching between cooling and heat pump modes and difficulty in coordinating outlet air temperature and dehumidification efficiency.

[0003] Existing technologies generally employ fixed evaporation temperature thresholds and single expansion valve control strategies, which cannot dynamically balance the low-temperature evaporator operation required for dehumidification with the high outlet air temperature required for comfort, resulting in poor system stability and low energy efficiency. To address these issues, a novel control method is urgently needed. This method utilizes a multi-heat exchanger collaborative architecture and intelligent algorithms to achieve dynamic allocation of refrigerant circulation, simultaneously optimizing evaporation temperature stability and precise outlet air temperature control without the need for PTC intervention, fundamentally resolving the technical bottleneck of the difficulty in balancing energy efficiency and comfort. Summary of the Invention

[0004] In view of the above problems, this disclosure provides a vehicle air conditioning control method, electronic device, and storage medium to overcome or at least partially solve the above problems. The technical solution is as follows:

[0005] A vehicle air conditioning control method, applied to a vehicle air conditioning control system, the system comprising: an evaporator, a compressor, an indoor heat exchanger, an outdoor heat exchanger, an intermediate heat exchange device, a first expansion valve, and a second expansion valve, wherein the two ends of the first expansion valve are respectively connected to the cooling medium inlet of the evaporator and the cooling medium outlet of the intermediate heat exchange device connecting to the outdoor heat exchanger; the two ends of the second expansion valve are respectively connected to the cooling medium inlet of the outdoor heat exchanger and the cooling medium outlet of the indoor heat exchanger; the compressor is disposed between the intermediate heat exchange device and the indoor heat exchanger; the method comprising:

[0006] In response to the air conditioning turn-on command, the outside ambient temperature is collected, and it is determined whether the outside ambient temperature is within the preset operating temperature range.

[0007] If so, turn on the compressor and determine the target air outlet temperature of the indoor heat exchanger based on the temperature control information contained in the air conditioner start command;

[0008] The opening degree of the second expansion valve is determined based on the actual outlet air temperature and the target outlet air temperature in order to control the outlet air temperature.

[0009] This disclosure provides a vehicle air conditioning control method that, through a collaborative architecture of dual expansion valves and three heat exchangers, dynamically determines whether the vehicle has entered a preset operating temperature range based on the external ambient temperature, and adjusts the opening of the second expansion valve in conjunction with the target outlet air temperature, thereby achieving precise distribution of refrigerant circulation. This solution directly controls the outlet air temperature of the indoor heat exchanger through the second expansion valve, avoiding the energy waste caused by relying on PTC heating in traditional systems. Simultaneously, by utilizing the coordinated adjustment of the compressor and dual valves, it significantly improves the stability of the outlet air temperature while ensuring dehumidification efficiency, resolving the core contradiction in existing technologies where dehumidification requirements and comfort are difficult to balance.

[0010] Optionally, determining the opening degree of the second expansion valve based on the actual outlet air temperature and the target outlet air temperature specifically includes:

[0011] Based on the actual air outlet temperature and the target air outlet temperature, calculate the target air outlet temperature difference and determine whether the target air outlet temperature difference is within the preset stable range of air outlet temperature.

[0012] If not, determine the opening adjustment step of the second expansion valve according to the correspondence between the target temperature difference of the air outlet and the opening adjustment step of the second expansion valve, so as to adjust the opening of the second expansion valve according to the opening adjustment step.

[0013] After maintaining the adjusted opening for the first preset time interval, determine whether the current target temperature difference of the air outlet is within the preset stable range of the air outlet temperature.

[0014] If not, continue adjusting the opening of the second expansion valve until the current target temperature difference of the outlet air is within the preset stable range of the outlet air temperature.

[0015] In this embodiment, by establishing a correspondence between the target outlet temperature difference and the adjustment step size of the second expansion valve opening, and employing a phased maintenance control strategy, a differentiated step size adjustment and time-holding mechanism is used when the target outlet temperature difference exceeds the stable range. This mechanism can quickly converge to the target temperature when the temperature difference is large, and avoid over-adjustment oscillation when approaching the stable range. This control logic, through the combination of dynamically adjusting the step size and forcibly holding the time, effectively improves the response speed and steady-state accuracy of the outlet temperature control, while reducing the risk of system fluctuations caused by frequent adjustments.

[0016] Optionally, the method further includes:

[0017] The target evaporation temperature of the evaporator is obtained based on the dehumidification information contained in the air conditioner start command.

[0018] Based on the target evaporation temperature and the opening degree of the second expansion valve, the opening degree of the first expansion valve is controlled, and the actual evaporator temperature is obtained, so as to determine the speed of the compressor based on the evaporation target temperature difference between the actual evaporation temperature and the target evaporation temperature.

[0019] In this embodiment, a three-dimensional coordinated control system of evaporator temperature, outlet air temperature, and compressor speed is constructed by introducing the linkage control between the target evaporator temperature and the opening degree of the second expansion valve, combined with the dynamic adjustment of the compressor speed. This design enables the adjustment of the opening degree of the first expansion valve to respond synchronously to the dehumidification demand and changes in the outlet air temperature. While ensuring the low-temperature dehumidification efficiency of the evaporator, the real-time adaptation of the compressor speed suppresses evaporator temperature fluctuations, thus solving the technical problem of mutual interference between evaporator and heat exchanger temperature control in traditional systems.

[0020] Optionally, controlling the opening of the first expansion valve based on the target evaporation temperature and the opening of the second expansion valve specifically includes:

[0021] Based on the correspondence between the opening degree of the second expansion valve and the linkage opening degree, determine whether the current opening degree of the first expansion valve is within the corresponding opening degree range;

[0022] If not, adjust the current opening to the nearest upper limit or lower limit of the opening range based on the relative size relationship between the current opening and the opening range.

[0023] Determine whether the target evaporation temperature difference is within the preset stable evaporation temperature range;

[0024] If not, adjust the opening of the first expansion valve according to the preset first adjustment step size;

[0025] After maintaining the adjusted opening for the second preset time interval, determine whether the current evaporation target temperature difference is within the preset stable evaporation temperature range;

[0026] If not, continue to adjust the opening of the first expansion valve according to the preset first adjustment step size until the current evaporation target temperature difference is within the preset stable evaporation temperature range.

[0027] In this embodiment, the opening of the first expansion valve is adjusted in a range based on a preset linkage opening correspondence. By prioritizing the alignment of the opening range boundary values ​​and combining it with step-by-step fine-tuning, rapid matching of refrigerant distribution between the two expansion valves is achieved. This strategy avoids refrigerant flow conflicts during the dual-valve adjustment process by forcibly aligning the opening ranges. At the same time, combined with the graded feedback adjustment of the evaporation target temperature difference, it significantly shortens the evaporation temperature stabilization time and enhances the robustness of the system under varying operating conditions.

[0028] Optionally, determining the compressor speed based on the target evaporation temperature difference between the actual evaporation temperature and the target evaporation temperature specifically includes:

[0029] Based on the target evaporation temperature difference, calculate the PI adjustment value of the compressor speed;

[0030] The compressor target speed is generated based on the PI adjustment value, and it is determined whether the target speed exceeds the preset upper speed limit or preset lower speed limit corresponding to the current fan speed.

[0031] If the speed is not exceeded, adjust the compressor speed to the target speed.

[0032] If the speed is exceeded, the compressor speed will be limited to the preset upper speed limit.

[0033] If the target speed is lower than the preset lower speed limit, the compressor speed will be limited to the preset lower speed limit;

[0034] When the target evaporation temperature difference is within the preset stable evaporation temperature range, maintain the current compressor speed until the temperature difference exceeds the stable range.

[0035] In this embodiment, by combining compressor speed control with a PI regulation algorithm and fan speed limit constraints, the compressor speed is prioritized to adapt to evaporation demand during evaporation temperature regulation. Simultaneously, the impact of sudden speed increases on system stability is limited based on fan speed level. This design ensures both the dynamic response capability of evaporation temperature control and prevents compressor overload through the speed limiting mechanism, reducing mechanical losses and noise issues caused by high-frequency start-stop cycles.

[0036] Optionally, the method further includes:

[0037] Obtain the current air conditioner fan speed level and retrieve the corresponding maximum allowable compressor speed from the preset fan speed mapping relationship;

[0038] When the target speed of the compressor exceeds the maximum allowable speed, the actual speed of the compressor is limited to the maximum allowable speed;

[0039] If the compressor runs continuously at the maximum allowable speed for a period of time exceeding a preset threshold, a load reduction control is triggered; wherein, the load reduction control includes increasing or decreasing the target outlet air temperature or switching to a low fan speed operation mode.

[0040] In this embodiment, by establishing a mapping relationship between the fan speed setting and the compressor's maximum permissible speed, and triggering a load reduction control strategy when the limit is exceeded, a strong coupling between the compressor's operating state and the user-set fan speed is achieved. This mechanism effectively prevents the compressor from operating under continuous high load under extreme conditions through dual protection of speed limiting and mode switching, extending the equipment's service life. At the same time, by dynamically adjusting the target outlet air temperature or switching the fan speed mode, it ensures the system's continuous and stable operation within safe thresholds.

[0041] Optionally, the lower limit of the preset operating temperature range is a first preset temperature;

[0042] The upper limit of the preset operating temperature range is the second preset temperature;

[0043] The lower limit of the temperature range of the target evaporation temperature is the third preset temperature;

[0044] The upper limit of the temperature range for the target evaporation temperature is the fourth preset temperature.

[0045] In this embodiment, by defining the boundary between the preset operating temperature range and the target evaporation temperature range, the system can automatically adapt to the optimal evaporation temperature control threshold under typical ambient temperatures. This range-based design balances dehumidification efficiency in low-temperature environments with system stability in high-temperature environments, avoiding the risks of evaporator frosting or overheating caused by insufficient environmental adaptability in traditional fixed threshold control.

[0046] Optionally, the method further includes:

[0047] Real-time monitoring of in-vehicle humidity and determination of whether the current humidity exceeds the preset comfortable humidity range;

[0048] If the current humidity is higher than the upper limit of the comfortable humidity range, the target outlet air temperature will be reduced by the first correction value and the outlet air volume will be reduced by the second correction value.

[0049] If the current humidity is below the lower limit of the comfortable humidity range, the target outlet air temperature will be increased by the third correction value and the outlet air volume will be increased by the fourth correction value.

[0050] The first correction value and the second correction value are determined based on the frequency of the vehicle's historical dehumidification mode activation and / or the number of people in the vehicle.

[0051] In this embodiment, by monitoring the humidity inside the vehicle in real time and adjusting the target air outlet temperature and airflow parameters accordingly, coordinated temperature and humidity control is achieved. This design dynamically adjusts the air outlet temperature setpoint based on humidity deviation, compensates for the impact of humidity changes on perceived comfort by adjusting airflow, and optimizes the correction coefficient using historical dehumidification frequency and the number of passengers inside the vehicle. This allows the system to adapt to the personalized needs of different occupants, improving the intelligence level of environmental regulation.

[0052] An electronic device, the electronic device comprising:

[0053] At least one processor;

[0054] And, a memory communicatively connected to the at least one processor;

[0055] The memory stores instructions that can be executed by the at least one processor, which are executed by the at least one processor to enable the at least one processor to perform any of the above-described vehicle air conditioning control methods.

[0056] A computer-readable storage medium storing computer-executable instructions, which, when executed, implement a vehicle air conditioning control method as described in any of the preceding claims.

[0057] The above description is merely an overview of the technical solution disclosed herein. In order to better understand the technical means of this disclosure and to implement it in accordance with the contents of the specification, and to make the above and other objects, features and advantages of this disclosure more apparent and understandable, specific embodiments of this disclosure are described below. Attached Figure Description

[0058] Various other advantages and benefits will become apparent to those skilled in the art upon reading the following detailed description of preferred embodiments. The accompanying drawings are for illustrative purposes only and are not intended to limit the scope of this disclosure. Furthermore, the same reference numerals denote the same parts throughout the drawings. In the drawings:

[0059] Figure 1 A structural diagram of a vehicle air conditioning control system provided in this application embodiment;

[0060] Figure 2 A flowchart of a vehicle air conditioning control method provided in this application;

[0061] Figure 3 A schematic diagram of an evaporation temperature-outlet air temperature control system provided in this application;

[0062] Figure 4 This is a schematic diagram of the internal structure of an electronic device provided in an embodiment of this application.

[0063] Explanation of reference numerals in the attached figures:

[0064] 1-Evaporator, 2-Compressor, 3-Indoor heat exchanger, 4-Outdoor heat exchanger, 5-Intermediate heat exchange device, 6-First expansion valve, 7-Second expansion valve. Detailed Implementation

[0065] To make the objectives, technical solutions, and advantages of this application clearer, the technical solutions of this application will be clearly and completely described below in conjunction with specific embodiments and corresponding drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0066] As new energy vehicles increasingly demand higher energy efficiency and comfort from their air conditioning systems, the inadequacy of traditional air conditioning control solutions under complex operating conditions is becoming increasingly apparent. In existing technologies, single-cooling air conditioning systems rely on PTC auxiliary heating devices for temperature compensation, leading to a significant increase in energy consumption. While heat pump systems can improve heating efficiency, they face conflicts between cooling and heating modes during dehumidification, making it difficult to simultaneously meet both low-temperature dehumidification requirements and comfortable outlet air temperature requirements. More importantly, existing control strategies often employ fixed threshold adjustment or single expansion valve control, failing to achieve dynamic coordination between evaporation temperature, outlet air temperature, and compressor speed, resulting in poor system stability and low energy efficiency.

[0067] Specifically, traditional solutions suffer from the following technical bottlenecks:

[0068] 1. Imbalance between energy efficiency and comfort: The temperature control method that relies on PTC heating results in energy waste, while the compressor start-stop logic and expansion valve regulation lack linkage, leading to both evaporator temperature fluctuations and outlet air temperature overshoot, making it impossible to balance energy efficiency and human comfort when dehumidifying at low temperatures.

[0069] 2. Limited control dimensions: Existing systems are mostly based on a single parameter (such as evaporation temperature or outlet air temperature) for independent adjustment, without establishing a dynamic mapping relationship between the opening of the dual expansion valve, the compressor speed and the ambient temperature, resulting in refrigerant distribution mismatch and low heat exchange efficiency.

[0070] 3. System stability defects: The compressor speed control and airflow regulation are disconnected, which can easily lead to equipment vibration or thermal runaway caused by excessive speed under extreme operating conditions. In addition, the expansion valve regulation lacks step-by-step segmented control and holding time constraints, and frequent operation can easily cause sudden changes in refrigerant flow, further deteriorating system stability.

[0071] The technical solutions proposed in the embodiments of this application will be described in detail below with reference to the accompanying drawings.

[0072] To address the aforementioned problems, this application provides a vehicle air conditioning control system, such as... Figure 1As shown, the system mainly includes: an evaporator 1, a compressor 2, an indoor heat exchanger 3, an outdoor heat exchanger 4, an intermediate heat exchange device 5, a first expansion valve 6, and a second expansion valve 7. The first expansion valve 6 is connected at both ends to the cooling medium inlet of the evaporator 1 and the cooling medium outlet of the intermediate heat exchange device 5 connecting to the outdoor heat exchanger, respectively. The second expansion valve 7 is connected at both ends to the cooling medium inlet of the outdoor heat exchanger 4 and the cooling medium outlet of the indoor heat exchanger 3, respectively. The compressor 2 is located between the intermediate heat exchange device and the indoor heat exchanger 3.

[0073] Based on the above application system, this application provides a vehicle air conditioning control method, such as... Figure 2 As shown, Figure 2 A flowchart of a vehicle air conditioning control method provided in this application embodiment specifically includes the following steps:

[0074] Step 201: In response to the air conditioning turn-on command, collect the outside ambient temperature and determine whether the outside ambient temperature is within the preset operating temperature range.

[0075] In this embodiment, the triggering methods for the air conditioning start command include, but are not limited to, control signals initiated by the user through the in-vehicle touchscreen, physical buttons, or mobile terminal APP. When the system detects the air conditioning start command, it first collects the outside ambient temperature through an ambient temperature sensor located on the inside of the vehicle's front bumper or at the base of the rearview mirror. It should be noted that the sensor's installation location must avoid the heat radiation area of ​​the engine compartment and have a rainproof design to ensure the accuracy of the collected data.

[0076] For example, the preset operating temperature range is the temperature range for efficient system operation, with its lower limit set as a first preset temperature (selectable range 6℃-9℃) and its upper limit as a second preset temperature (selectable range 20℃-24℃). It is understood that this range is set based on the following technical considerations: when the ambient temperature is below the lower limit, the evaporator is prone to frosting due to excessively low evaporation temperature, leading to a sharp drop in dehumidification efficiency; when the ambient temperature is above the upper limit, the PTC auxiliary heating suffers significant energy efficiency degradation due to excessively high condensation temperature. Specifically, the system compares the collected external ambient temperature with the preset range using a lookup table method. If the temperature value is within the range, it is determined that the dual expansion valve collaborative control mode can be activated; if it exceeds the range, it switches to a backup control strategy (such as PTC auxiliary heating or single valve adjustment mode).

[0077] It should be noted that the boundary values ​​of the preset operating temperature range are not fixed. For example, in adapting to vehicles in high-altitude areas or special climates, the lower limit selectable range can be adjusted to 7℃-8℃ and the upper limit selectable range to 22℃-23℃ using software configuration tools to match typical local environmental conditions. Furthermore, the system incorporates hysteresis control logic during the judgment process: when the ambient temperature gradually rises from below the lower limit to 7℃, it delays for 30 seconds before switching to the dual-valve mode to avoid frequent mode switching due to temperature fluctuations.

[0078] Specifically, in a winter scenario with an ambient temperature of 5°C, the system determines that the outside temperature is below the lower limit of a preset range, automatically disables the dual-valve collaborative control, and activates the PTC heating mode. In a summer scenario with an ambient temperature of 25°C, the system closes the first expansion valve because the temperature exceeds the upper limit, and cools down only through the cooling cycle and the regulation of the second expansion valve. This design, through dynamic mode switching, ensures system safety under extreme conditions while avoiding unnecessary energy consumption.

[0079] It is understandable that determining the preset operating temperature range is a prerequisite for subsequent dual-valve coordinated control. Skipping this step and directly proceeding to temperature regulation may lead to evaporator frosting or compressor overload under unsuitable operating conditions. For example, forcibly activating dual-valve mode at an ambient temperature of 3°C may cause the evaporator temperature to drop below -5°C, resulting in freezing and blocking refrigerant flow, thus failing to achieve the purpose of dehumidification. Therefore, this step, through the ambient temperature threshold screening, provides a stable operating foundation for subsequent control logic.

[0080] Step 202: If so, turn on the compressor and determine the target air outlet temperature of the indoor heat exchanger based on the temperature control information contained in the air conditioner start command.

[0081] In this embodiment, the temperature control information includes a specific temperature value set by the user (e.g., 24°C) or a preset mode code. It should be noted that the preset mode code is converted into specific temperature control logic through a mapping table stored in the vehicle controller. For example, "Comfort Mode" corresponds to a dynamic temperature offset strategy, while "Rapid Cooling" corresponds to the maximum cooling power output mode.

[0082] Understandably, the generation of the target air outlet temperature needs to take into account both the influence of ambient temperature and the user's subjective needs. Specifically, the system achieves this through the following methods:

[0083] Mode Explanation: If the user selects a preset mode, the system will generate a target temperature baseline value based on the current ambient temperature. For example, when the ambient temperature is 15℃, the target air outlet temperature baseline value for "Comfort Mode" is 20℃; when the ambient temperature rises to 25℃, the baseline value is adjusted to 23℃ to avoid the discomfort of direct cold air blowing.

[0084] Dynamic offset: An ambient temperature compensation is added to the baseline value. For example, for every 1°C above the baseline ambient temperature (e.g., 20°C), the target outlet air temperature decreases by 0.5°C, but the total offset does not exceed 3°C. This design avoids sudden changes in perceived temperature through gradual temperature adjustment.

[0085] User-defined adaptation: If the user directly inputs a specific temperature value (such as 22℃), the system will use this value as the target air outlet temperature, but will also perform a reasonableness check in combination with the ambient temperature.

[0086] It should be noted that the generation process of the target air outlet temperature incorporates a fuzzy control algorithm. For example, the system uses ambient temperature, historical operating data (such as the recent average cooling rate), and the number of people in the vehicle as input variables, and calculates the optimal target temperature using a membership function. For instance, when ≥3 occupants are detected in the vehicle, the system lowers the target temperature by 1°C to compensate for the impact of heat dissipation from the human body.

[0087] Specifically, in the "rapid cooling" mode, the system ignores the ambient temperature compensation logic, directly sets the target air outlet temperature to the lowest value allowed by current technology (such as 16°C), and maximizes the opening of the second expansion valve and the compressor speed.

[0088] Understandably, the dynamic generation mechanism of the target air outlet temperature is the foundation of the dual-valve collaborative control. If a fixed temperature setpoint is used, the second expansion valve will frequently and significantly adjust when the ambient temperature fluctuates, exacerbating system oscillations. For example, in areas with large diurnal temperature differences, when the ambient temperature drops at night, the dynamic target temperature automatically rises by 2°C to reduce cooling demand and energy consumption, while maintaining consistent levels of human comfort.

[0089] For example, when the ambient temperature is 18°C ​​in spring, if a user selects "Comfort Mode," the system generates a target outlet air temperature of 22°C. If the user manually adjusts it to 20°C, the system will gradually lower the target temperature in three steps over 10 minutes (22°C → 21°C → 20°C), with each adjustment spaced 3 minutes apart. This gradual adjustment strategy responds to user needs while avoiding evaporation temperature fluctuations caused by sudden changes in refrigerant flow.

[0090] Furthermore, the system learns user preferences through historical data. For example, if a user frequently manually sets the target temperature to 24°C when the ambient temperature is 25°C, the system will automatically adjust the "comfort mode" baseline value from 23°C to 24°C under similar conditions, achieving personalized adaptation. This design, by integrating preset logic with adaptive learning, significantly improves the user experience.

[0091] Step 203: Determine the opening degree of the second expansion valve based on the actual outlet air temperature and the target outlet air temperature to achieve control of the outlet air temperature.

[0092] In one possible implementation of this application, determining the opening degree of the second expansion valve based on the actual outlet air temperature and the target outlet air temperature specifically includes: calculating the target outlet air temperature difference based on the actual outlet air temperature and the target outlet air temperature, and determining whether the target outlet air temperature difference is within a preset stable outlet air temperature range; if not, determining the adjustment step size of the second expansion valve opening based on the correspondence between the target outlet air temperature difference and the adjustment step size of the second expansion valve opening, and adjusting the opening degree of the second expansion valve according to the adjustment step size; maintaining the adjusted opening degree for a first preset time interval, and determining whether the current target outlet air temperature difference is within a preset stable outlet air temperature range; if not, continuing to adjust the opening degree of the second expansion valve until the current target outlet air temperature difference is within a preset stable outlet air temperature range.

[0093] In this embodiment, the adjustment of the opening degree of the second expansion valve is the core execution link for controlling the outlet air temperature. It should be noted that the two ends of the second expansion valve are respectively connected to the cooling medium inlet of the outdoor heat exchanger and the cooling medium outlet of the indoor heat exchanger. The change of its opening degree directly affects the refrigerant flow to the indoor heat exchanger, thereby changing the heat exchange efficiency and the outlet air temperature.

[0094] For example, the actual outlet air temperature is collected in real time by a temperature sensor placed at the outlet of the indoor heat exchanger, and the system calculates the difference between it and the target outlet air temperature (i.e., the target outlet air temperature difference). It can be understood that the positive or negative sign of the temperature difference indicates the direction of adjustment: when the actual temperature is lower than the target value, the opening of the second expansion valve needs to be reduced to reduce the refrigerant flow; conversely, the opening is increased.

[0095] In the embodiments of this application, the system dynamically selects the adjustment range according to a preset step size adjustment strategy. It should be noted that the upper and lower limits of the control opening of the compressor, the first expansion valve, and the second expansion valve, as well as the control methods, are shown in Table 1 below:

[0096]

[0097] Table 1

[0098] In this embodiment, the step size adjustment strategy is as follows:

[0099] 1. Rapid adjustment with large temperature difference: When the absolute value of the target temperature difference exceeds 13℃, a large step size (such as 200 steps) is used to quickly approach the target temperature.

[0100] 2. Medium temperature difference transition adjustment: When the temperature difference is within the range of 5℃-8℃, switch to a medium step size (such as 100 steps) to balance the adjustment speed and stability.

[0101] 3. Fine-tuning with small temperature differences: When the temperature difference is less than 5℃, use small step sizes (such as 50 steps) for fine-tuning to avoid overshoot and oscillation.

[0102] It should be noted that after each opening adjustment, the system forcibly maintains the current opening for at least a first preset time interval (e.g., 30 seconds). This design is based on the inertial characteristics of refrigerant flow changes: after the refrigerant flow is adjusted, it takes a certain amount of time to fully affect the temperature field distribution of the heat exchanger. For example, if the temperature difference is re-detected immediately after the adjustment, misjudgment may occur due to sensor response delay or thermal inertia, thereby triggering oscillation regulation.

[0103] Specifically, in a scenario of rapid cooling in high temperatures during summer, if the system detects that the target temperature difference of the outlet air is -10℃ (the actual temperature is higher than the target value), it will immediately increase the opening of the second expansion valve by 200 steps to increase the refrigerant flow and enhance the heat exchange efficiency. After maintaining this for 30 seconds, the temperature difference will be detected again. If the temperature difference shrinks to -5℃, it will switch to a small step size of 50 steps to continue adjusting until the temperature difference enters a stable range of ±2℃.

[0104] For example, the target temperature difference of the outlet air corresponds to the control of the second expansion valve, as shown in Table 2 below:

[0105]

[0106] Table 2

[0107] It is understandable that the step size adjustment strategy is similar to... Figure 1 The flow characteristics of the refrigerant are closely related. When the opening of the second expansion valve increases, more refrigerant flows from the indoor heat exchanger to the outdoor heat exchanger. At this time, the refrigerant flow rate of the evaporator is adjusted in conjunction with the first expansion valve to avoid runaway evaporation temperature.

[0108] Example 1:

[0109] In one possible implementation of this application, the method further includes: obtaining the target evaporation temperature of the evaporator based on the dehumidification information contained in the air conditioner start command; controlling the opening of the first expansion valve based on the target evaporation temperature and the opening of the second expansion valve, and obtaining the actual evaporator temperature, so as to determine the speed of the compressor based on the evaporation target temperature difference between the actual evaporation temperature and the target evaporation temperature.

[0110] In one possible implementation of this application, controlling the opening of the first expansion valve based on the target evaporation temperature and the opening of the second expansion valve specifically includes: determining, using a preset linkage opening table, whether the current opening of the first expansion valve is within a corresponding opening range based on the opening of the second expansion valve; if not, adjusting the current opening to the nearest upper or lower limit of the opening range based on the relative size relationship between the current opening and the opening range; determining whether the target evaporation temperature difference is within a preset stable evaporation temperature range; if not, adjusting the opening of the first expansion valve according to a preset first adjustment step size; maintaining the adjusted opening for a second preset time interval, determining whether the current target evaporation temperature difference is within a preset stable evaporation temperature range; if not, continuing to adjust the opening of the first expansion valve according to the preset first adjustment step size until the current target evaporation temperature difference is within a preset stable evaporation temperature range.

[0111] In one possible implementation of this application, the compressor speed is determined based on the target evaporation temperature difference between the actual evaporation temperature and the target evaporation temperature. Specifically, this includes: calculating a PI adjustment value for the compressor speed based on the target evaporation temperature difference; generating a target compressor speed based on the PI adjustment value and determining whether the target speed exceeds a preset upper or lower speed limit corresponding to the current fan speed; if not, adjusting the compressor speed to the target speed; if exceeding, limiting the compressor speed to the preset upper speed limit; if the target speed is lower than the preset lower speed limit, limiting the compressor speed to the preset lower speed limit; and maintaining the current compressor speed until the temperature difference exceeds the preset stable evaporation temperature range when the target evaporation temperature difference is within that range.

[0112] In this embodiment, the dehumidification information includes user-triggered dehumidification mode commands (such as "automatic dehumidification" or "powerful dehumidification") or dehumidification demand signals automatically generated by the system based on data from the in-vehicle humidity sensor. It should be noted that the target evaporation temperature of the evaporator is a key parameter for balancing dehumidification efficiency and system stability, and its setting needs to be dynamically adjusted based on the ambient temperature.

[0113] It is understandable that the dynamic range design of the target evaporation temperature resolves the contradiction between low-temperature frosting and high-temperature efficiency reduction in traditional fixed threshold control. It should also be noted that the generation process of the target evaporation temperature in this application can incorporate an anti-vibration protection mechanism. For example, when the ambient temperature fluctuates near the boundary of a preset operating range (e.g., 19℃-21℃), the system employs hysteresis control logic: if the temperature rises from 19℃ to 20℃, the target evaporation temperature range is switched after a 1-minute delay, avoiding frequent adjustments caused by short-term temperature fluctuations.

[0114] Understandably, skipping the dynamic setting of the target evaporation temperature and using a fixed value could easily lead to system imbalance under varying operating conditions. Therefore, this step provides a precise adjustment benchmark for subsequent dual-valve linkage and compressor speed control by establishing a dynamic mapping relationship between ambient temperature and target evaporation temperature.

[0115] In this embodiment, the opening adjustment of the first expansion valve and the state of the second expansion valve are strongly coupled. The core of this approach is to achieve dynamic balance between evaporation temperature stability and outlet air temperature control through coordinated refrigerant distribution. It should be noted that the two ends of the first expansion valve are connected to the cooling medium inlet of the evaporator and the outlet pipe of the intermediate heat exchange device, respectively. Changes in its opening directly affect the refrigerant flow rate and evaporation pressure of the evaporator.

[0116] For example, the system queries a preset linkage opening table based on the current opening degree of the second expansion valve to determine the reasonable opening degree range of the first expansion valve.

[0117] For example, the linkage opening table is shown in Table 3 below:

[0118]

[0119] Table 3

[0120] In this embodiment, after aligning the opening degree to the boundary of the range, the system performs step-by-step adjustment based on the deviation between the actual evaporator temperature and the target temperature (evaporation target temperature difference). For example, if the actual evaporation temperature is 1.5°C lower than the target value, the opening degree of the first expansion valve is gradually reduced in steps of 10 steps / time, and maintained for 20 seconds (second preset time interval) after each adjustment to observe the temperature response.

[0121] It is understandable that the essence of a linkage opening table is to establish a non-linear mapping relationship between the opening degrees of two valves. For example... Figure 2 As shown, when the opening of the second expansion valve increases (increasing the refrigerant flow rate to the indoor heat exchanger), the opening of the first expansion valve (6 degrees) needs to decrease simultaneously to limit the evaporator flow rate and prevent uncontrolled outlet air temperature due to excessive refrigerant distribution to the evaporator. For example, in "rapid cooling" mode, the opening of the second expansion valve increases to 800 steps to maximize the cooling power of the indoor heat exchanger. At this time, the opening of the first expansion valve is limited to below 300 steps to ensure that the evaporator evaporation temperature does not fall below the frosting threshold.

[0122] For example, in a dehumidification scenario with an ambient temperature of 10℃, the system sets the target evaporator temperature to 3℃. When the actual evaporation temperature is detected to be 5℃ (2℃ higher than the target value), the system gradually reduces the opening of the first expansion valve in steps of 20 until the evaporation temperature drops to a stable range of 3℃ ± 0.5℃. Simultaneously, the compressor speed is adjusted in real time using a PI algorithm. For instance, for every 1℃ increase in the target evaporation temperature difference, the compressor speed increases by 200 rpm, but this is limited by the current fan speed setting, as shown in Table 4 below. Table 4 displays the maximum compressor speed corresponding to each fan speed setting.

[0123]

[0124] Table 4

[0125] It should be noted that the compressor speed control incorporates a fan speed-speed coupling mechanism. For example, in low fan speed (level 1) mode, the compressor speed limit is 1500 rpm. If the PI algorithm calculates a target speed of 1800 rpm, the system will limit the actual speed to 1500 rpm and trigger load reduction control. This design, by integrating user input (fan speed selection) with equipment protection logic, prevents airflow noise or vibration issues caused by high speed under low airflow conditions.

[0126] Furthermore, the system dynamically switches control modes based on the stable evaporation temperature range (e.g., ±1℃). When the target evaporation temperature difference enters the stable range, the current compressor speed is maintained until the temperature difference exceeds the threshold. If the temperature difference continues to exceed the range for more than 2 minutes, the fine-tuning process of the first expansion valve is restarted. For example, when the outside temperature suddenly drops, the actual temperature of evaporator 1 may quickly deviate from the target value. In this case, the system prioritizes adjusting the compressor speed (rather than frequently adjusting the first expansion valve) to quickly converge the temperature difference.

[0127] It is understandable that ignoring the interlocking of the two valves and independently adjusting the first expansion valve will lead to refrigerant distribution conflicts. For example, if the opening of the second expansion valve increases significantly without simultaneously reducing the opening of the first expansion valve, excessive refrigerant flow into the evaporator will cause a sudden drop in evaporation temperature, potentially leading to frosting or compressor liquid slugging. Therefore, this step establishes a control system for evaporation temperature and outlet air temperature, such as... Figure 3 As shown. It should be noted that, Figure 3 In this context, EXV1 and EXV2 represent the first expansion valve and the second expansion valve, respectively.

[0128] Example 2:

[0129] In one possible implementation of this application, the method further includes: obtaining the current air conditioner fan speed level and obtaining the corresponding maximum allowable compressor speed from a preset fan speed mapping table; when the target speed of the compressor exceeds the maximum allowable speed, limiting the actual speed of the compressor to the maximum allowable speed; if the compressor runs continuously at the maximum allowable speed for a period of time exceeding a preset threshold, triggering load reduction control; wherein, triggering load reduction control includes increasing or decreasing the target air outlet temperature and switching to a low fan speed operation mode.

[0130] In this embodiment, the fan speed level is set via a user interface (such as a physical knob or touchscreen), and its value (such as levels 1-3) is mapped to the compressor's maximum speed. It should be noted that the fan speed-speed mapping relationship is based on a balance between airflow demand and noise control: a low fan speed (such as level 1) corresponds to a low speed to reduce airflow noise, while a high fan speed (such as level 3) allows for higher speeds to meet rapid temperature control requirements.

[0131] For example, such as Figure 2 As shown, the compressor is located on the main circulation path between the intermediate heat exchange unit and the indoor heat exchanger. Its speed directly affects the flow distribution of refrigerant from the indoor heat exchanger to the outdoor heat exchanger and evaporator. Specifically, the system looks up the maximum allowable compressor speed according to the current fan speed level: Level 1 (low fan speed): maximum speed 1500 rpm, suitable for quiet driving scenarios (such as night driving); Level 2 (medium fan speed): maximum speed 2000 rpm, balancing cooling speed and energy consumption; Level 3 (high fan speed): maximum speed 2500 rpm, used for rapid cooling or extreme humid and hot environments.

[0132] Understandably, the aforementioned speed limiting mechanism is closely related to the physical location of the compressor. When the compressor speed increases, the refrigerant flow rate from the indoor heat exchanger through the indoor heat exchanger accelerates. At this time, the flow rate needs to be adjusted by regulating the opening of the second expansion valve to avoid uncontrolled evaporator temperature due to sudden pressure changes. For example, at fan speed level 3, if the compressor is running at 2500 rpm, the opening of the second expansion valve 7 needs to be increased to 800 steps simultaneously to maintain a stable outlet air temperature.

[0133] It should be noted that when the target speed of the compressor exceeds the upper limit of the speed corresponding to the current fan speed, the system will limit the actual speed to the upper limit value.

[0134] Example 3:

[0135] In one possible implementation of this application, the humidity inside the vehicle is monitored in real time, and it is determined whether the current humidity exceeds the preset comfortable humidity range. If the current humidity is higher than the upper limit of the comfortable humidity range, the target air outlet temperature is reduced by a first correction value and the air outlet volume is reduced by a second correction value. If the current humidity is lower than the lower limit of the comfortable humidity range, the target air outlet temperature is increased by a third correction value and the air outlet volume is increased by a fourth correction value. The first correction value and the second correction value are determined based on the frequency of the vehicle's historical dehumidification mode activation and / or the number of people in the vehicle.

[0136] It should be noted that in dehumidification mode, reducing the airflow increases the contact between the air and the evaporator, thereby enhancing the dehumidification effect. Therefore, in this embodiment, when the current humidity is higher than the upper limit of the comfortable humidity range, the airflow is reduced to enhance the dehumidification effect; when the current humidity is lower than the lower limit of the comfortable humidity range, the airflow is increased to reduce the dehumidification effect. Furthermore, since lowering the target outlet air temperature will simultaneously lower the evaporator temperature, which is more conducive to enhancing the dehumidification effect, when the current humidity is higher than the upper limit of the comfortable humidity range, the target outlet air temperature is simultaneously lowered by a first correction value; when the current humidity is lower than the lower limit of the comfortable humidity range, the target outlet air temperature is simultaneously increased by a third correction value.

[0137] This embodiment collects real-time humidity data using humidity sensors placed in the vehicle's ceiling or under the seats, with a comfortable humidity range set at 40%-60%. When the humidity exceeds the upper limit, the system lowers the target air outlet temperature by 1-2°C and reduces the airflow by 10%-20% to alleviate the stuffiness caused by high humidity; when the humidity falls below the lower limit, the system adjusts the target air outlet temperature and airflow in the opposite direction. The correction value is dynamically adjusted based on historical dehumidification frequency and the number of passengers in the vehicle: if the vehicle has frequently used the dehumidification function recently or if there are ≥3 passengers, the temperature correction is increased by 0.5-1°C, and the airflow correction is increased by 5%-10%. For example, during the rainy season, if the system detects that the average daily dehumidification time has exceeded 2 hours in the past week, it automatically adjusts the temperature correction value for humidity exceeding the limit from 1°C to 1.5°C to enhance the dehumidification response.

[0138] Example 4:

[0139] In this embodiment, the compressor speed can be controlled by looking up a table based on the blower air volume, ambient temperature, internal and external circulation ratio, or evaporator inlet air temperature, and should be limited.

[0140] In this embodiment, the control architecture is as follows: Figure 1 As shown, the intermediate heat exchange device can be removed, or replaced with a liquid storage tank and coaxial tube. This can be regarded as a variation of the architecture corresponding to this control algorithm, and should also be subject to restrictions.

[0141] In this embodiment, the linkage control between the first expansion valve and the second expansion valve does not necessarily have to be done according to Table 2. It can be linked by the opening degree of the first expansion valve and the second expansion valve, and should also be limited.

[0142] The above are embodiments of the method proposed in this application. Based on the same inventive concept, embodiments of this application also provide an electronic device, the structure of which is as follows: Figure 4 As shown.

[0143] Figure 4 This is a schematic diagram of the internal structure of a device provided in an embodiment of this application. Figure 4 As shown, the device includes:

[0144] At least one processor 401;

[0145] And a memory 402 that is communicatively connected to at least one processor;

[0146] The memory 402 stores instructions executable by at least one processor, which are executed by at least one processor 401 to enable at least one processor 401 to:

[0147] In response to the air conditioning turn-on command, the outside ambient temperature is collected, and it is determined whether the outside ambient temperature is within the preset operating temperature range.

[0148] If so, turn on the compressor and determine the target air outlet temperature of the indoor heat exchanger based on the temperature control information contained in the air conditioner start command;

[0149] The opening degree of the second expansion valve is determined based on the actual outlet air temperature and the target outlet air temperature in order to control the outlet air temperature.

[0150] Some embodiments of this application provide corresponding to Figure 1 A computer-readable storage medium storing computer-executable instructions, wherein the computer-executable instructions are configured as follows:

[0151] In response to the air conditioning turn-on command, the outside ambient temperature is collected, and it is determined whether the outside ambient temperature is within the preset operating temperature range.

[0152] If so, turn on the compressor and determine the target air outlet temperature of the indoor heat exchanger based on the temperature control information contained in the air conditioner start command;

[0153] The opening degree of the second expansion valve is determined based on the actual outlet air temperature and the target outlet air temperature in order to control the outlet air temperature.

[0154] The various embodiments in this application are described in a progressive manner. Similar or identical parts between embodiments can be referred to mutually. Each embodiment focuses on describing the differences from other embodiments. In particular, the embodiments for IoT devices and media are basically similar to the method embodiments, so the description is relatively simple; relevant parts can be referred to the descriptions of the method embodiments.

[0155] The systems, media, and methods provided in this application are one-to-one correspondences. Therefore, the systems and media also have similar beneficial technical effects as their corresponding methods. Since the beneficial technical effects of the methods have been described in detail above, the beneficial technical effects of the systems and media will not be repeated here.

[0156] 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.

[0157] 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.

[0158] 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.

[0159] 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.

[0160] In a typical configuration, a computing device includes one or more processors (CPU), input / output interfaces, network interfaces, and memory.

[0161] Memory may include non-persistent storage 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.

[0162] Computer-readable media includes 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, magnetic magnetic 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.

[0163] 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 a process, method, article, or apparatus. Without further limitation, 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 said element.

[0164] The above description is merely an embodiment of this application and is not intended to limit the scope of 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 scope of the claims of this application.

Claims

1. A vehicle air conditioning control method characterized by, The application is applied to a vehicle air conditioner control system, the system comprises an evaporator, a compressor, an indoor heat exchanger, an outdoor heat exchanger, a first expansion valve and a second expansion valve, two ends of the first expansion valve are connected with a cooling medium inlet of the evaporator and a cooling medium outlet of an outdoor heat exchanger pipeline connected with an intermediate heat exchange device respectively, two ends of the second expansion valve are connected with a cooling medium inlet of the outdoor heat exchanger and a cooling medium outlet of the indoor heat exchanger respectively, and the method comprises the following steps: In response to an air conditioner opening instruction, an outside environment temperature is collected, and it is determined whether the outside environment temperature is in a preset working condition temperature interval; the preset working condition temperature interval is a temperature range for efficient operation of the system; If yes, the compressor is started, and a target air outlet temperature of the indoor heat exchanger is determined according to temperature control information contained in the air conditioner opening instruction; the temperature control information contains a specific temperature value set by a user or a preset mode code; the preset mode code is converted into specific temperature control logic through a mapping relationship table stored in a vehicle-mounted controller; According to the actual air outlet temperature and the target air outlet temperature, the opening degree of the second expansion valve is determined to realize control of the air outlet temperature; The method further comprises the following steps: According to dehumidification information contained in the air conditioner opening instruction, a target evaporation temperature of the evaporator is obtained; According to the target evaporation temperature and the opening degree of the second expansion valve, the opening degree of the first expansion valve is controlled, and an actual evaporation temperature is obtained, so as to determine the rotating speed of the compressor according to an evaporation target temperature difference between the actual evaporation temperature and the target evaporation temperature; the dehumidification information contains a dehumidification mode instruction actively triggered by a user or a dehumidification demand signal automatically generated by the system according to vehicle indoor humidity sensor data.

2. The vehicle air conditioning control method according to claim 1, characterized by The determination of the opening degree of the second expansion valve according to the actual air outlet temperature and the target air outlet temperature specifically comprises the following steps: According to the actual air outlet temperature and the target air outlet temperature, an air outlet target temperature difference is calculated, and it is determined whether the air outlet target temperature difference is in a preset air outlet temperature stable range; If not, an opening degree adjustment step of the second expansion valve is determined according to a corresponding relationship between the air outlet target temperature difference and the opening degree adjustment step of the second expansion valve, so as to adjust the opening degree of the second expansion valve according to the opening degree adjustment step; After the adjusted opening degree is maintained for a first preset time interval, it is determined whether the current air outlet target temperature difference is in the preset air outlet temperature stable range; If not, the opening degree of the second expansion valve is continuously adjusted until the current air outlet target temperature difference is in the preset air outlet temperature stable range.

3. The vehicle air conditioning control method according to claim 1, characterized by The control of the opening degree of the first expansion valve according to the target evaporation temperature and the opening degree of the second expansion valve specifically comprises the following steps: According to the opening degree of the second expansion valve and a linkage opening degree corresponding relationship, it is determined whether a current opening degree of the first expansion valve is in a corresponding opening degree interval; If not, the current opening degree is adjusted to an upper limit of the nearest opening degree interval or a lower limit of the nearest opening degree interval according to a relative size relationship between the current opening degree and the opening degree interval; It is determined whether the evaporation target temperature difference is in a preset evaporation temperature stable range; If not, the opening degree of the first expansion valve is adjusted according to a preset first adjustment step. After maintaining the adjusted opening for a second preset time interval, it is determined whether the current evaporation target temperature difference is within a preset evaporation temperature stable range; If not, the opening of the first expansion valve is continuously adjusted according to a preset first adjustment step until the current evaporation target temperature difference is within the preset evaporation temperature stable range.

4. The vehicle air conditioning control method according to claim 1, characterized by Specifically, the method comprises: Based on the evaporation target temperature difference, a PI adjustment value of the compressor speed is calculated; A target speed of the compressor is generated according to the PI adjustment value, and it is determined whether the target speed exceeds a preset upper limit or a preset lower limit of the speed corresponding to the current air outlet level; If not, the speed of the compressor is adjusted to the target speed; If yes, the speed of the compressor is limited to the preset upper limit of the speed; If the target speed is lower than the preset lower limit of the speed, the speed of the compressor is limited to the preset lower limit of the speed; When the evaporation target temperature difference is within the preset evaporation temperature stable range, the current speed of the compressor is maintained until the temperature difference exceeds the stable range.

5. The vehicle air conditioning control method according to claim 1, characterized by The method further comprises: The current air outlet level of the air conditioner is obtained, and a corresponding maximum allowable speed of the compressor is obtained from a preset air outlet level-speed mapping relationship; When the target speed of the compressor exceeds the maximum allowable speed, the actual speed of the compressor is limited to the maximum allowable speed; If the compressor continuously operates at the maximum allowable speed for a time period exceeding a preset threshold, a load reduction control is triggered, which comprises increasing or decreasing a target air outlet temperature or switching to a low air outlet level operation mode.

6. The vehicle air conditioner control method according to claim 1, wherein a lower limit of the preset working condition temperature interval is a first preset temperature; an upper limit of the preset working condition temperature interval is a second preset temperature; a lower limit of the temperature interval of the target evaporation temperature is a third preset temperature; an upper limit of the temperature interval of the target evaporation temperature is a fourth preset temperature.

7. The vehicle air conditioning control method according to claim 1, characterized by The method further comprises: The humidity in the vehicle is monitored in real time, and it is determined whether the current humidity exceeds a preset comfortable humidity range; If the current humidity is higher than an upper limit of the comfortable humidity range, the target air outlet temperature is decreased by a first correction value and the air outlet amount is decreased by a second correction value; If the current humidity is lower than a lower limit of the comfortable humidity range, the target air outlet temperature is increased by a third correction value and the air outlet amount is increased by a fourth correction value; The first correction value and the second correction value are determined based on a frequency of historical operation of a dehumidification mode of the vehicle and / or a number of people in the vehicle.

8. An electronic device, comprising: The device comprises: at least one processor; and a memory connected in communication with the at least one processor; wherein the memory stores instructions executable by the at least one processor, and the instructions are executed by the at least one processor to enable the at least one processor to perform the vehicle air conditioner control method according to any one of claims 1-7.

9. A vehicle characterized by comprising: The vehicle comprises: a memory for storing executable program code; a processor for calling and running the executable program code from the memory, so that the vehicle performs the method according to any one of claims 1-7.

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